阅读说明：本技术 具有能够运动地支承的工作工具的可移动的工具机器 (Mobile machine tool having a movably mounted working tool ) 是由 S·沙尔普夫 于 2019-05-15 设计创作，主要内容包括：本发明涉及可移动的工具机器(51),用于对工件或空间(RA)的表面(FL、FR、FF、FD)进行涂层的和/或研磨的加工,具有关于所述表面(FL、FR、FF、FD)可移动的工作装置(50),所述可移动的工作装置具有通过驱动马达(53)驱动的或能够驱动的用于工作工具(90A、90F)的工具容纳部(58)和/或带有用于对所述表面(FL、FR、FF、FD)进行涂层的涂层工具(981)的涂层机构(980),所述工作工具用于加工所述表面。设置成,所述工作装置(50)具有带有至少一个引导轮廓(65C)、尤其引导面的引导机构(65),以用于在所述表面(FL、FR、FF、FD)处引导,其中,所述工作工具(90A、90F)或所述涂层工具(981)关于所述引导机构(65)能够运动地进行支承。(The invention relates to a movable tool machine (51) for coating and/or grinding a surface (FL, FR, FF, FD) of a workpiece or a space (RA), comprising a working device (50) that is movable relative to the surface (FL, FR, FF, FD), said movable working device comprising a tool receptacle (58) for a working tool (90A, 90F) that is driven or drivable by a drive motor (53) and/or a coating means (980) having a coating tool (981) for coating the surface (FL, FR, FF, FD). It is provided that the working device (50) has a guide means (65) with at least one guide contour (65C), in particular a guide surface, for guiding at the surface (FL, FR, FF, FD), wherein the working tool (90A, 90F) or the coating tool (981) is mounted movably in relation to the guide means (65).)

1. Mobile tool machine (51) for coated and/or abrasive machining of a surface (FL, FR, FF, FD) of a workpiece or space (RA), having a working device (50) that is mobile in relation to the surface (FL, FR, FF, FD), having a tool receptacle (58) for a working tool (90A, 90F) that is driven or drivable by a drive motor (53) and/or a coating means (980) with a coating tool (981) for coating the surface (FL, FR, FF, FD), for machining the surface, characterized in that the working device (50) has a guide means (65) with at least one guide contour (65C), in particular a guide face, for guiding at the surface (FL, FR, FF, FD), wherein the working tool (90A, 90F) or the coating tool (981) is mounted so as to be movable relative to the guide mechanism (65).

2. Machine tool according to claim 1, characterised in that the working device (50) has a suction mechanism (70) for sucking the working device (50) at the surface (FL, FR, FF, FD) with at least one force component oriented in the normal direction (N) of the surface (FL, FR, FF, FD).

3. The machine tool according to claim 1 or 2, wherein the working device (50) has a disk-shaped tool (90) arranged or arrangeable at the tool receptacle (58), which has a machining surface (91) assigned to the machining of the workpiece and a machine side (92) opposite the machining surface (91).

4. The machine tool according to one of the preceding claims, wherein the working device (50) or the working tool (90A, 90F) or the coating means (980) is supported at the guide means (65) linearly and/or pivotably, in particular multi-axially, and/or floatingly, with respect to the at least one guide contour (65C) by means of a support means.

5. Machine tool according to claim 4, characterized in that the support means support the working device (50) or the working tool (90A, 90F) or the coating means (980) swingably about at least one swing axis transverse to the rotation axis of the working tool (90A, 90F) or transverse to a force component oriented in the normal direction (N) of the surface (FL, FR, FF, FD).

6. Machine tool according to claim 4 or 5, characterized in that said support means comprise at least one membrane (66A) where said working tool (90A, 90F) or said coating means (980) or said working device (50) are held at said guide means (65).

7. Machine tool according to any one of the preceding claims, characterized in that the working tool (90A, 90F) or a coating tool (981) of the coating mechanism (980) is adjustable with respect to the guide mechanism (65) relative to the guide profile (65C) between a working position provided for contact with the surface (FL, FR, FF, FD) and a rest position set back relative to the at least one guide profile (65C), in which rest position the guide profile (65C) bears against the surface (FL, FR, FF, FD) and the working tool (90A, 90F) or coating tool (981) has a spacing of the surface.

8. Tool machine according to any one of the preceding claims, characterized in that the working device (50) has a motorized or manual servo drive for adjusting the working tool (90A, 90F) or coating tool (981) between the rest position and the working position.

9. A tool machine according to any one of the preceding claims, characterized in that the working tool (90A, 90F) or coating tool (981) is loaded in relation to the guide mechanism (65) into a working position arranged for contact with a surface (FL, FR, FF, FD) by means of a spring assembly.

10. The machine tool according to one of the preceding claims, wherein the guide mechanism (65) has a guide carrier (65A) at which an abutment body (65B), in particular a sealing body, having the at least one guide contour (65C) and being provided for abutment at a surface (FL, FR, FF, FD) to be machined is movably supported.

11. Machine tool according to claim 10, characterised in that the abutment body (65B) is spring-loaded with respect to the guide carrier in the direction of the surface to be machined (FL, FR, FF, FD) by means of a spring assembly.

12. Machine tool according to any one of the preceding claims, wherein the guide means (65) have at least one suction area for suction at the surface (FL, FR, FF, FD).

13. Machine tool according to any one of the preceding claims, characterised in that the working device (50) is housed in an extraction housing (64A).

14. Machine tool according to claim 13, characterised in that the suction housing (64A) forms an integral part of the guide means (65).

15. Machine tool according to any one of the preceding claims, characterized in that the guide means are provided for guiding the machine tool along the surface (FL, FR, FF, FD) to be machined, wherein the guide profile (65C) bears against the surface (FL, FR, FF, FD) and the working tool (90A, 90F) undergoes a relative movement with respect to the guide profile bearing against the surface.

16. Machine tool according to one of the preceding claims, characterized in that at least one handle (800) and/or at least one traction means holder (67) are arranged at the guide means (65) for transmitting a guide force onto the guide means (65) such that the guide means (65) can be guided along the surface (FL, FR, FF, FD), wherein the working tool (90A, 90F) with the guide profile (65C) abutting at the surface (FL, FR, FF, FD) makes a relative movement away from and towards the guide profile abutting at the surface.

17. The machine tool according to any one of the preceding claims, characterized in that it forms a movable working device (50) of a surface machining system (10) for the coating and/or abrasive and/or cutting machining of a surface of a workpiece or space.

18. Machine tool according to claim 17, wherein the surface working system (10) has at least one holding means (20) which can be fixed in a fixed position with respect to the surface (FL, FR, FF, FD), said holding means being connected to the working device (50) by means of at least one flexurally flexible pulling means (30).

19. Machine tool according to claim 17 or 18, wherein the surface working system (10) has a positioning mechanism (13) with at least one positioning drive (40, 340) for positioning the working device (50) transversely to the normal direction (N) of the surface (FL, FR, FF, FD).

20. Machine tool according to any one of claims 17 to 19, characterized in that the surface machining system (10) has the at least one holding mechanism (20) or positioning drive (40, 340) for the at least one traction means (30).

21. The machine tool according to one of claims 17 to 20, wherein the at least one positioning drive (40, 340) comprises at least one traction means drive (41) for driving the traction means and/or at least one working device drive arranged on the working device (50) or is formed thereby.

22. Machine tool according to any one of claims 17 to 21, characterized in that the surface machining system (10) has at least two or at least three or at least four traction means (30) and/or at least two or at least three or at least four holding means (20), wherein the working device (50) is held at the traction means (30) or holding means (20).

23. The machine tool according to one of claims 17 to 22, characterised in that, at the working device (50), there are traction means holders arranged at in particular the same or approximately the same angular spacing relative to one another for holding at least one traction means (30).

24. Machine tool according to any one of claims 17 to 23, characterised in that the surface working system (10) has at least one motor-driven and/or spring-loaded winding mechanism (45) for winding up the pulling means (30).

25. Surface machining system (10) with a tool machine (51) according to any one of the preceding claims.

Technical Field

The invention relates to a movable tool machine for coating and/or grinding a surface of a workpiece or a space, comprising a working device that is movable relative to the surface and has a tool receptacle for a working tool (for machining the surface) that is driven or can be driven by a drive motor and/or a coating device with a coating tool for coating the surface.

Background

The machine tool is, for example, a grinding machine, for example a grinding machine with a grinding tool or a disk-shaped tool for machining a surface. The disk-shaped tool usually has a yielding mat, for example made of a foam material, so that the disk-shaped tool can be adapted to the respective surface contour to be machined. The guiding of the machine tool along the surface takes place through the working surface of the disk-shaped tool. A seal, for example a brush seal, can be arranged around the disk-shaped tool, which seal bears against the workpiece surface. Thereby, an efficient suction of dust is possible.

However, the guiding properties of the known machine tool at the workpiece surface or the spatial surface are nevertheless not optimal.

Disclosure of Invention

It is therefore an object of the present invention to provide an improved machine tool.

In order to solve this object, in a movable tool machine of the type mentioned at the outset, it is provided that the working device has a guide means with at least one guide contour, in particular a guide surface, for guiding at the surface, wherein the working tool or the coating tool is mounted movably with respect to the guide means.

The basic idea here is that the guide mechanism can be said to slide or guide along the workpiece surface, while the machining surface of the disk-shaped tool or other working tool is movable relative to the guide contour, so that it can, for example, compensate for irregularities at the machined surface. It is obviously possible that a disk-shaped tool with a working surface is applied at the tool machine, said working surface being yielding. However, the movable mounting of the working tool or the coating tool allows an additional degree of freedom and thus an optimal workpiece machining.

The coating means relate, for example, to rollers or rolling elements which are movable relative to the surface.

The working device expediently has a guide means, for example a guide surface, with at least one guide contour for guiding at a surface of the space or the workpiece. Suitably, the guide profile has a flat profile. The guide contour can, for example, lie in one plane. The guide profile can be an elastic or yielding guide profile. It is however also possible that the guide profile is or comprises a stiff, non-yielding profile.

The working tool or the coating tool is expediently mounted so as to be movable with respect to the guide. Thereby, the guide profile can follow the surface, for example, while the working tool or the coating tool can follow irregularities of the surface to be machined. It is obviously also possible for the disk-shaped tool to have a certain yield, for example with a foam layer which matches or follows the corresponding surface contour of the surface, as it were.

It is possible that only the working tool or the coating means, in particular the coating means, is mounted so as to be movable with respect to the guide means. However, it is also possible for the working device as a whole to be mounted so as to be movable with respect to the guide mechanism. The working device can thus be formed, for example, as a drive unit or as a drive head which is mounted so as to be movable with respect to the guide mechanism.

The movable mounting of the working device or of its working tool or of the coating means with respect to the guide means is realized, for example, in that the working device, the working tool or the coating means are mounted at the guide means by means of the mounting means linearly and/or pivotably, for example multi-axially, with respect to at least one guide contour. A floating bearing is to be understood to mean, in particular, a multi-axis pendulum motion. The working tool, the coating means or the working device as a whole is preferably mounted so as to be pivotable about at least one pivot axis, which extends transversely to the axis of rotation of the working tool or to a force component oriented in the direction of the normal of the surface, by the mounting means. A universal or ball-jointed bearing is advantageous, for example.

An advantageous support concept provides that the support means comprise at least one membrane at which the working tool, the coating means or the working device as a whole is held at the guide means. For example, the membrane is held with its edge region at the guide means and carries as a whole a working tool, a coating means or a working device which is arranged in the interior space of the guide means.

The movable mounting of the working tool and/or the coating means with respect to the guide means is also achieved in that it can be brought, for example, into a resting position which is meaningful if the working device is stationary with respect to the surface to be processed, for example for a prepositioning before the start of the actual working process or in the working pause. Then surface processing, such as coating, grinding or the like, is not feasible or meaningful. Both of which can cause damage or destruction of the surface.

A preferred concept therefore provides that the working tool or the coating tool of the coating means can be adjusted with respect to the guide contour of the guide means relative to said guide means between a working position provided for contact with the surface and a rest position adjusted rearward relative to the at least one guide contour. In the rest position, the guide contour, although bearing against the surface, has a spacing of the working tool or the coating tool relative to the surface. The rest position is suitable, for example, for prepositioning of the working device at the surface.

It is possible that the working tool or the coating tool can be manually adjusted by an operator between the rest position and the working position. Preferably, the working device has a servo drive for adjusting the working tool or the coating tool between the rest position and the working position. The servo drive can comprise, for example, a lever drive, which can be actuated manually. Preferably, however, the servo drive is motorized, in particular electric. Thereby, especially automation is possible.

The working tool or the coating tool is loaded with respect to the guide mechanism into a working position provided for contact with the surface by means of a spring assembly. Thereby, a spring assembly comprising one or more springs, in particular helical springs, leaf springs or the like, holds the working tool or the coating tool in contact with the surface to be machined. It is possible that the aforementioned servo drive actuates the working tool or the coating tool into the rest position counter to the force of the spring assembly.

The guide means expediently has a guide carrier, at which an abutment body, for example a sealing body, rubber seal, brush seal or the like, having at least one guide contour and being provided for abutment against the surface to be machined is mounted so as to be movable. In other words, the guide device can have a so-called hard or rigid guide carrier, on which the working tool, the coating device or the working device as a whole is movably supported. Expediently, the abutment body is spring-loaded by a spring assembly with respect to the guide carrier in the direction of the surface to be machined. However, it is also possible to support the contact body so to speak in a floating manner with respect to the guide carrier, so that the contact body can be pivoted about the guide carrier in a multi-axis manner. In this case, a spring loading is optionally possible, however, not absolutely necessary.

Expediently, the guide contour surrounds the working device in a ring shape. The guide profile can be a resilient guide profile, but can also be a stiff (feel) guide profile. The guide contour can be formed by one or more contact bodies, in particular plate-shaped bodies, sealing bodies or the like.

The guide means expediently has at least one suction region for suction to the surface to be processed. The suction area can be laterally next to the working tool or the coating tool, for example. The suction region can annularly or partially annularly enclose the working tool or the coating tool.

However, it is also possible to suck the working device with the aid of the working tool to the surface to be machined. The suction region of the guide means and the further suction region at the working tool or the coating tool are possible without problems.

Preferably, the tool machine forms a movable working device of a surface machining system for the coated and/or abrasive machining of the surface of a workpiece or space. The working device is movable with respect to the surface.

It is advantageously provided that the surface processing system has at least one holding means which can be fixed in a stationary manner with respect to the surface and which is connected to the work apparatus by means of at least one flexurally flexible pulling means.

The curved flexible retractor means can be, for example, a rope, a toothed belt or the like. The flexurally flexible pulling means are suitable, for example, for positioning and/or supporting the work device in relation to the surface to be processed. The flexurally flexible pulling means can, for example, prevent the working device from falling onto the base or in any case brake it.

Preferably, the working tool relates to a disk-shaped tool and/or a grinding tool. For example, a grinding belt, a grinding disk or the like can be provided as a working tool. The working tool can also be a milling tool or a similar other cutting tool.

Preferably, the drive motor is provided or designed for the rotational driving of the tool holder about the rotational axis and/or for the eccentric rotational driving of the tool holder, by means of which the tool holder is driven or can be driven. It is possible to switch the working device between an eccentric mode, in which the tool holder and thus the working tool undergo an eccentric movement, and a pure rotary mode, in which the working tool is rotated only about the axis of rotation, but without eccentricity.

The coating means can involve, for example, a spraying mechanism for spraying paint. The coating tool can, for example, also comprise a roller or similar other application body for applying a pigment or similar other coating to the surface of the workpiece or space.

Instead of or in addition to the tool holder or the coating device driven by the drive motor, the working device can also comprise a cleaning device. Thus, the working device can be said to form a cleaning device. The cleaning means can for example comprise a brush assembly for brushing the surface and/or one or more nozzles for leading off cleaning liquid or the like. It is possible that the cleaning means is, for example, a high-pressure cleaning means.

The holding device, which can be fixed in place with respect to the surface, is connected to the working device by means of one or more flexible traction means, which can be used, for example, to keep the working device from falling to the floor or to hold it at a wall or other surface. The pulling implement can be said to support the suction mechanism.

The traction means can, for example, provide weight compensation for the working device. The working device can thus be said to be suspended at the towing means, for example. The pulling means are spring-loaded, for example by means of a spring assembly, so that the spring assembly fully or partially compensates the weight of the working device. The spring assembly can act directly on the pulling means and/or act on the winding body in the sense of rolling up the pulling means onto the winding body.

Preferably, the surface processing system has a positioning mechanism with at least one positioning drive for positioning the working device transversely to the normal direction of the surface.

Preferably, a plurality of positioning drives are provided for a plurality of degrees of freedom of movement and/or directions of movement.

The at least one positioning drive can, for example, support an operator who otherwise manually manipulates the working device. The basic concept here is that the operator orients the working device transversely to the normal direction, in particular multi-axially or bi-axially transversely to the normal direction, with the aid of the support of the at least one positioning drive.

Advantageously, the at least one positioning drive is arranged on the working device. For example, the positioning drive comprises a drive roller driven by a drive motor for rolling over the surface to be machined of the workpiece or space.

Automatic processing of the surface, for example coating or grinding of the surface, is possible without problems by means of the at least one positioning drive. The surface-machining system operates autonomously, i.e. without direct presetting.

A preferred embodiment of the invention provides that one or more of the positioning drives are arranged on the holding means and actuate the traction means. Thus, the holding device has the positioning drive or a positioning drive for at least one traction means. The positioning drive of the holding means can be provided in addition to or instead of the positioning drive on the working device. It is furthermore advantageous if the surface-machining system has at least two or at least three, further even preferably at least four, traction means. It is also advantageous for two, at least three or even four retaining means to be provided in the retaining means. The holding means can be arranged, for example, in the corner regions of the surface to be machined, so that the working devices can be scheduled between the holding means. A respective traction means is associated with a holding mechanism. However, it is also possible for a plurality of traction means to be held at the holding means. This can provide a high traction force, for example. The work device can be easily positioned on the surface to be machined of the workpiece or of the space by means of a plurality of holding devices, for example three or four holding devices, and corresponding pulling devices, which extend between the holding devices and the work device.

Preferably, a plurality of traction means holders are present at the work device for holding at least one traction means, which traction means holders are preferably assigned to different force directions in which the traction means act on the work device. Preferably, for example, the same angular spacing exists between the traction means fastening elements. The traction means fastening can be provided or designed for a fixed non-releasable or releasable connection between the traction means and the work apparatus.

In the case of a fastening part of a traction means, it is advantageous if it makes possible a latching connection and/or a magnetic connection and/or a clamping connection and/or a hooking connection or the like with the respective traction means. Thus, for example, a catch receptacle and/or a catch projection and/or a magnet holder and/or a bayonet contour or the like can be provided at a respective traction means holder, which can be brought into a fixed, preferably releasable connection with a corresponding, complementary connecting means at a respective longitudinal end of the traction means. It is clearly advantageous for the traction means fastening to enable mobility, for example, pendability, of the respective traction means with respect to the work apparatus. For example, the pendulum support can be arranged at the traction means fastening. However, it is also possible for there to be other receptacle contours, for example snap rings or the like, which allow clearance for the movement of the respective towing means with respect to the work device.

Suitably, the at least one positioning drive comprises at least one traction means drive for driving the traction means. The traction means drive can be arranged, for example, on the working device, at a retaining mechanism or the like. It is possible that a traction means drive is respectively present both at the holding device and at the working device. Preferably, the traction means drive co-acts.

It is possible that the at least one positioning drive comprises or is formed by at least one working device drive arranged on the working device. In the last-mentioned configuration, it is possible, for example, for the traction means drive to be supported by the working device drive. However, it is also possible to assign the traction means drive and the work device drive to different directions of movement, for example directions of movement which are angled, in particular at right angles, with respect to one another. The traction means drive can thus, for example, be provided for a forward or backward movement of the working device along the surface to be machined, while the working device drive is provided and/or designed for a positioning movement transverse thereto.

In principle, it is possible for traction means which do not function with regard to their force direction to, for example, sag (durchh ä ngt). It is also possible that the pulling means is spring-loaded by a spring assembly, so that the pulling means is held under tension between the holding mechanism on the one hand and the working device on the other hand.

Preferably, however, there is a winding mechanism for winding up the pulling means. Preferably, the winding mechanism is motor driven or spring loaded. The winding mechanism can, however, in principle also be actuated manually, for example with a crank or similar other actuating handle.

Furthermore, it is advantageous if a positioning drive for actuating the traction means, respectively, is arranged between the working device and the at least one winding mechanism. When, for example, the traction means has a toothed belt or a toothed belt section, the positioning drive can precisely influence the respective longitudinal position of the traction means.

Alternatively, it is possible without problems to provide the positioning drive at the winding mechanism or to design it as a rotary drive for the winding roller.

It is possible to provide a path sensor in the winding body, for example a winding roller, of the winding mechanism by means of the positioning drive for detecting the respective wound or unwound section of the traction means.

For an exact length determination or path determination of the wound-up or unwound return section of the towing means by measuring the rotation of the winding body, in particular the winding rollers, a corresponding determination of the winding state is advantageously provided, so that the influence of the respective winding diameter on the length of the unwound section of the towing means is detected during the rotation of the winding body of the winding towing means. For example, an optical sensor, camera or the like can be provided for this purpose.

In terms of unrolling and rolling up of the pulling appliance, it has become clear that advantageously the pulling appliance does not sag. Advantageously, at least one tensioning means for tensioning the pulling means, for example a tensioning roller or the like, is present. The tensioning means is suitably spring loaded. The tensioning means can be arranged, for example, between the winding mechanism and the working device.

Furthermore, it is possible for a tensioning means, for example a tensioning roller, to be arranged between the traction means drive and the winding mechanism which winds up and unwinds the traction means. Thus, for example, precise winding and unwinding of the traction means by the rolling elements of the winding mechanism or other winding bodies is possible.

Furthermore, it is expedient to have a traction means guide mechanism for guiding a traction means guide body of at least one traction means. The traction means guide body can be arranged in a stationary or movable manner, for example, on the holding mechanism. The traction means guide body comprises, for example, a guide buckle, a guide roller, a guide groove or the like.

Furthermore, the towing means guide body is advantageously arranged on a joint, for example a ball joint, a pivot joint, a universal joint or the like, wherein the joint movably supports the towing means guide body. The traction means guide body can follow the respective movement of the traction means by means of the articulated bearing. For example, the hinge is arranged at the at least one retaining mechanism. The hinge can be provided, for example, at a longitudinal end region of the retaining mechanism. It is also possible that the articulated piece can be fixed in a fixed manner in relation to the surface to be processed, for example by means of a suction device, a screw, a catch or the like, independently of the holding device.

The traction means guide body is expediently arranged between the winding mechanism for the traction means and/or the drive for the traction means and the movable working device. The traction means guide body thereby guides the traction means, for example, between the winding mechanism and the work device or between a drive for the traction means and the work device.

Different types of methods are suitable for the stationary fixing of the holding means. Thus, for example, a vacuum tensioner or similar other vacuum holding means can be provided for fixing the holding means with respect to the space to be processed. Preferably, the holding means are clamped between the mutually opposite faces, for example the bottom and the top of the space. A holding mechanism, for example of the type with a support, can be clamped or can be clamped between the bottom and the top.

Preferably, the holding means can be longitudinally calibrated with respect to its longitudinal extension between at least two longitudinal positions, in which the longitudinal ends of the holding means have different spacings with respect to one another. The longitudinal ends are supported, for example, at the bottom and at the top of the space. In the respective longitudinal position, a holding means can be fixed, for example by means of a clamping means, a screw thread or similar other fixing means.

The holding device has, for example, a base or a support.

The holding mechanism has, for example, a holding base and a supporting body, which can be fixed to each other with respect to the longitudinal extension of the holding mechanism in at least two longitudinal positions of the supporting body relative to the holding base. For example, the support body can be telescopic at or with respect to the holding base. It is understood that a plurality of telescopically adjustable members of the holding mechanism can be provided.

The working device is preferably accommodated in the suction housing. The suction housing is arranged for suction to a surface. The suction housing can house or enclose the working device as a whole. For example, the already mentioned guide contour is arranged at an edge region or an end face of the suction housing for guiding at the surface to be machined. The suction housing can be designed, for example, in the type of a bell. A vacuum chamber is preferably provided in the intake housing, in which vacuum chamber the working device is accommodated.

Preferably, the surface treatment system has a vacuum generator separate from the working device, which vacuum generator is connected to the working device by means of a suction hose. The negative pressure generator is, for example, a dust aspirator. Advantageously, the controller of the surfacing system is on the negative pressure generator. The negative pressure generator can be arranged, for example, stationary in the space, while the working device is movable and positioned along the surface to be machined. The control or control means on the negative pressure generator can, for example, actuate a positioning drive on the working device or at one or more of the holding devices.

Preferably, the working device has a suction control or an adjusting mechanism or both for adjusting the underpressure in the suction region provided for sucking the working device to the surface. The negative pressure generator arranged on the working device can thus be actuated or regulated, for example, accordingly. For example, a pressure sensor is arranged in the suction region.

The suction device expediently has at least one valve for controlling a suction air flow and/or a vacuum in a suction region of the working device for suction to the surface, wherein the at least one valve has a valve member which can be adjusted between at least two valve positions, wherein the flow cross sections of the valves are different.

In order to solve this object, in a movable tool machine of the type mentioned at the outset, it is provided that the suction device has a suction control for adjusting the valve member between its valve positions during operation of the working tool or the coating device, depending on at least one physical variable.

The basic idea here is that the suction control, which can also be referred to as an adjusting mechanism, so to speak, dynamically readjusts the valve element, while the working tool or the coating tool machines, for example abrasively, or coats the surface. The valve member can be driven or actuated without direct influence from the operator, i.e. by the suction controller.

For adjusting the valve member, a valve drive, a spring assembly or both can be provided, for example. However, it is also possible without any problem for the valve to also have an actuating handle that can be manually actuated in order to actuate the valve member. In other words, the valve ring, which is itself driven by the motor or by the spring assembly, can furthermore be actuated manually.

The manual operating handle can also be used to change the pretension of the spring assembly, for example, to adjust the valve to other operating regions.

The at least one physical parameter comprises, for example, the angular position of the working device relative to the base. The suction control adjusts the valve member depending on the position of the working device relative to the base. That is, when, for example, the working device occupies an upright working position, for example for machining of the side wall surface, the valve ring segment has a different position than when machining the surface at the bottom or the surface of the top surface.

To determine the angular position, the suction control can have a position sensor. The position sensor is designed to detect the angular position of the working device relative to the base as at least one physical variable. The position sensor can relate to an acceleration sensor. The acceleration sensor is capable of performing three-axis acceleration measurements.

However, it is possible for the valve collar to detect the angular position of the work apparatus relative to the base, as it were, or to adjust it depending on the angular position itself. The valve collar is mounted in a valve housing of the valve, for example, so as to be movable between at least two valve positions as a function of the angular position of the working device relative to the base. The valve member takes over the valve position autonomously by adjusting the working device into the respective angular position. The valve member comprises, for example, balls or other rolling or roller bodies, which are mounted so as to be movable within a valve housing. Depending on the working device and thus the angular position of the valve, the valve collar moves within the valve housing, for example, in order to open or close the valve passage opening. It is possible to provide a plurality of such valve ring segments.

The at least one physical variable can also comprise the motor power or the motor current of the drive motor. The at least one physical variable can therefore also represent the grinding power or the polishing power of the working tool. The suction control is designed for actuating the valve or for adjusting the valve member depending on the motor power or motor current. That is to say, when the motor generates, for example, a higher power, this can be an indicator for a high grinding power, which in turn can be attributed to the negative pressure in the suction region being large.

However, the at least one physical variable can also comprise the pressure and/or the flow speed of the suction air flow in the suction region. For this purpose, the suction control device has, for example, a pressure sensor for detecting the pressure and/or a flow sensor for detecting the flow rate.

It is also possible for the valve ring to be actuated automatically, i.e. for example to be spring-loaded in the direction of the closed position and to be opened by vacuum or to be spring-loaded in the direction of the open position and to be closed by vacuum, by means of pressure or flow.

Preferably, the suction control device has an adjusting mechanism for adjusting the underpressure in the suction region as a function of the at least one physical variable. The regulation can, for example, comprise a pressure signal or a flow signal of a pressure sensor or a flow sensor as an input variable. On the output side, the actuating mechanism actuates, for example, a valve drive of the motor in order to actuate the valve element.

By means of the valve, the suction control device can, for example, set or regulate a suction air flow which is sucked through the suction region during operation of the machine tool. However, it is also possible to control the external air by means of a valve, i.e. for example to feed the external air into the suction region or another negative pressure region which is in flow connection with the suction region, in order to thus vary (for example increase or decrease) the negative pressure in the suction region or the flow rate of the suction air flow.

It is possible without problems for the suction device to have at least one further manually actuable valve for influencing the underpressure and/or the suction air flow in the suction region. That is, the valve is present in addition to a valve that can be manipulated by the suction controller. For example, by means of a valve, the outside air inlet can be opened or closed or partially opened by the operator of the tool machine. This makes it possible, for example, to change the working range of the valve that can be actuated by the suction controller.

The working device can have a support tool with a support surface or a machining surface for resting against a workpiece surface, for example a wall surface. The support means can be of identical design and can be provided as a disk-shaped tool as described below, i.e. with, for example, a suction air inflow opening and/or an additional air inflow opening and an associated outflow opening.

A machining head, for example a coating head of a coating device, a milling tool or a similar other cutting machining tool, can be arranged on the support tool for machining the workpiece to be machined.

Preferably, the machine tool is a disk tool having a machining surface for machining the surface and a drive motor for driving the disk tool, which has a machining surface assigned to the workpiece to be machined and a machine side opposite the machining surface, wherein a suction air inlet opening is arranged at the machining surface for the purpose of sucking the machining surface to the surface to be machined, which suction air inlet opening is in flow connection with at least one suction air outlet opening arranged next to the machining surface at the disk tool, wherein the disk tool has at least one additional air inlet opening for an additional air inlet, which additional air inlet opening is in flow connection with the at least one additional air outlet opening arranged next to the machining surface.

Preferably, the suction means are designed for generating a suction air flow and/or a negative pressure at the at least one suction air outflow opening and the at least one additional air outflow opening.

It is advantageously provided that the suction device has a suction control device for controlling the suction air flow and/or the underpressure in the region of the at least one additional air outflow opening.

The basic idea here is that it can be said that the suction air flow or the underpressure or both can be adjusted in the region of the additional air outflow opening, so that, for example, at least one additional air inflow opening can be activated as a further inflow opening for sucking the tool machine to the surface and/or in order to change the total suction power of the suction means between the at least one additional air inflow opening and the suction air inflow opening. For example, a greater suction power of the suction device is present in the region of the suction air inflow opening arranged at the processing surface.

At the machining surface, a grinding means for machining the workpiece or a holding means for releasably holding such a grinding means is preferably arranged. It is possible to provide both, that is to say there is a holding means at which the grinding means is held.

The grinding device and/or the holding device expediently have/has a through-flow opening corresponding to the suction air inflow opening, so that air can be sucked in from the front side or the machining side of the grinding device or the holding device through the through-opening into the suction air inflow opening. Suitably, the holding means for releasably holding the grinding means comprise a hook and loop assembly (klettardnung), such as a hook and loop (Kletthaken), a hook and loop felt (Klettfilz) or the like.

Preferably, a receptacle fixing part, such as a projection, a retaining pin, a snap profile or the like, is present at the machine side of the disk-shaped tool for fixing at the tool receptacle of the working device. It is therefore advantageous if the disk-shaped tool is detachably arranged on the working device. The disk-shaped tool can thus be replaced, for example, when the holding means or the grinding means wear out.

The tool holder or the disk-shaped tool is directly connected to the drive motor, for example in the form of a direct drive or a kinematic coupling, for example by means of a gear mechanism and/or an eccentric bearing or the like.

The suction control device is expediently designed for controlling the suction air flow and/or the underpressure in the region of the at least one suction air outflow opening. In this way, it is possible to directly adjust the negative pressure or the suction air flow in the region of the suction air inflow opening. For this purpose, for example, a valve is provided, which can adjust the negative pressure or the suction air flow in the region of the suction air outlet opening.

Furthermore, it is also possible, however, that the suction air flow and/or the underpressure in the region of the at least one suction air outflow opening cannot be influenced by the suction control or can only be influenced by the control of the suction air flow or the underpressure in the region of the at least one additional air outflow opening. In principle, the suction power used is thereby adjusted, so to speak indirectly, by adjusting the negative pressure or the suction air flow in the region of the at least one additional air inflow opening.

It is possible to provide a substantially constant or constant suction air flow or a substantially constant or constant underpressure in the region of the at least one suction air outflow opening. However, it is also possible to vary the flow and/or pressure conditions in the region of the suction air inflow opening, which preferably performs a preferential suction or main suction of the disk-shaped tool and thus of the tool machine, by varying the suction air flow or the underpressure in the region of the at least one additional air outflow opening and thus also the flow and/or pressure conditions in the region of the additional air inflow opening.

The suction device has, for example, a vacuum generator for generating a vacuum and/or a suction air flow, which is arranged on the working device, for example on a housing of the working device. However, it is also possible, in addition to or as an alternative to the already mentioned negative pressure generator, for the suction device to have a suction connection arranged at the working device for a negative pressure generator which is separate, in particular spatially remote, from the working device or the tool machine. The negative pressure generator is formed, for example, by a dust aspirator. A flexible flow line, for example a suction hose, can be connected to the suction connection. The suction connection can thus be provided, for example, as a suction hose for connecting a dust aspirator or a vacuum generator. Preferably, the suction connection is a connection socket or a socket.

Preferably, the suction control device has at least one valve for controlling the suction air flow and/or the vacuum in the region of the at least one suction air outflow opening and/or in the region of the at least one additional air outflow opening, wherein a valve inlet of the valve is connected to the at least one suction air outflow opening and/or the at least one additional air outflow opening and a valve outlet of the valve is connected or connectable to the vacuum generator. In this way, the pressure and/or flow conditions in the region of the at least one suction air outflow opening or the at least one additional air outflow opening can be adjusted by means of the valve without changing the suction power of the negative pressure generator.

The valve is arranged, for example, in the flow channel between the at least one suction air outflow opening or the additional air outflow opening or both and the negative pressure generator or the suction connection for the negative pressure generator and is thereby connected between the respective outflow opening and the negative pressure generator. The valve ring of the valve member can be adjusted between a blocking position, for example, in which the flow channel is closed, and a conducting position, in which the flow channel is released, and preferably at least one intermediate position between the blocking position and the conducting position.

The valves comprise, for example, control valves, shift valves or the like. The valve can be switched between a conducting position for conducting and a blocking position for blocking the flow connection between the vacuum generator and the outflow opening of the disk-shaped tool. However, the valve can also be switchable between an intermediate position between such a conducting position and the blocking position or can also be incompletely closed and/or can be incompletely opened. Thus, the valve can be or comprise a proportional valve, for example.

Preferably, the valve collar is mounted rotatably and/or displaceably and/or pivotably relative to a valve housing of the valve between at least two valve positions. The axis of rotation or pivot of the valve member can, for example, run parallel to the main flow axis of the valve, but also at a small inclination relative thereto, for example, up to 10 ° or 15 °. It is also possible for the axis of rotation or oscillation of the valve element to extend transversely, for example at right angles, to the main flow axis of the valve. The superimposed oscillating sliding movement of the valve element is possible without problems.

The valve ring comprises, for example, a cylinder body, at the outer circumferential wall of which at least one recess is arranged. A plurality of recesses can be provided at the circumferential wall, for example at a longitudinal and/or angular spacing. In order to change the flow cross section of the valve, the circumferential wall and thus the at least one recess at the circumferential wall can be adjusted with respect to the valve housing.

It is preferably provided that the valve has a motorized valve drive and/or a spring assembly and/or a manually actuable operating handle for adjusting the valve member. It is understood that a combination is possible, i.e. for example a manually actuable valve ring is additionally spring-loaded. The valve, which is itself driven by a motor or by a spring assembly, can also be actuated manually without problems.

Advantageously, the valve collar is or can be actuated depending on the angular position of the working device relative to the base. For example, the valve member can be mounted so as to be movable in a valve housing of the valve and can be actuated by earth attraction such that the valve member changes, for example opens or closes, reduces or increases the flow cross section of the valve depending on the angular position of the working device. The valve ring can be capable of opening the passage of the valve, for example when machining the top side, and partially or completely closing the passage of the valve when machining the side wall of the space. When the bottom surface should be machined, the valve is able to completely close the passage.

Advantageously, a fastening means, for example a latching means and/or a clamping means and/or at least one magnet, is provided for the fixed fastening of the valve ring in place in at least one valve position.

The latching mechanism can, for example, comprise latching contours on the valve member, in particular on its manual operating handle, and on a component fixed in place in relation to the valve housing of the valve. That is to say, when the operator actuates the operating handle, the latching contours can engage in one another at predetermined positions.

The clamping means can for example comprise a spring assembly or a clamping disk or be formed therefrom, so that for example the valve ring segments are correspondingly tight (schwerg ä ngig, sometimes interpreted as heavy).

The magnet holder can be provided, for example, with a magnet at the valve ring, which magnet together with a further magnetic element, for example a magnet or a ferromagnetic component, which is fixed in place with respect to the valve housing, effects a magnetic holding.

Preferably, the valve ring can be latched or can be fixed in a predetermined valve position in which, for example, a certain flow situation or negative pressure distribution between the suction air inlet opening on the one hand and the additional air inlet opening on the other hand can be set. Thus, for example, one predetermined position of the valve element can be provided for wall machining by a tool machine, while another position is provided for top or bottom machining. For the top machining, the valve collar is, for example, in a valve position in which the flow cross section of the valve is larger than in the wall machining.

In this way, for example, more suction air or negative pressure can be present in the region of the suction air inflow opening. However, it is also possible that, in the opposite case, i.e. when the additional air is to flow through an additional air inflow opening which is not arranged in the sense of sucking the disk-shaped tool to the surface, for example an inflow opening which is arranged at the outer periphery of the disk-shaped tool, the valve element releases a larger flow cross section during the top machining, so that the suction power in the region of the suction air inflow opening is correspondingly smaller.

In a preferred embodiment of the invention, the valve ring is spring-loaded in the direction of the closed position of the closing valve and can be actuated by means of a negative pressure in the direction of its open position. Thus, for example, the negative pressure in the region of the at least one additional air outflow opening can be such that the valve element can be opened in the direction of the open position of the valve element against the force of the spring assembly spring-loading the valve element into the closed position. However, it is also possible that a negative pressure (abstehender) present on the outflow side opens the valve element, so that a negative pressure can be generated in the region of the suction air outflow opening or the additional air outflow opening, for example, accordingly.

One embodiment of the invention provides that at least one bypass channel is provided which is connected to the at least one suction air outflow opening via the at least one valve. However, it is also possible for the suctioned air to be conducted from the at least one suctioned air outflow opening all the way through the bypass channel or the assembly of a plurality of bypass channels past the valve in the direction of the vacuum generator or the suction connection for the vacuum generator, i.e. the valve only influences the flow situation or the pressure situation in the region of the at least one additional air suction opening.

The additional air inflow openings can be provided at different regions of the disk-shaped tool.

One embodiment provides, for example, that the at least one additional air inflow opening comprises or is formed by an additional air inflow opening arranged at the processing surface. Obviously, a plurality of additional air inflow openings can be arranged at the processing surface. With the aid of the additional air inflow opening, it is possible, at the machining face, to directly influence the suction force of the disk-shaped tool at the surface to be machined.

Preferably, at least one additional air inflow opening or all additional air inflow openings are arranged at the radial outer circumference of the disk-shaped tool. That is, the suction air inflow opening is preferably arranged in a central region of the disk-shaped tool, while the additional air inflow opening or inflow opening is arranged at an edge region of the disk-shaped tool.

In this connection it should also be mentioned that the disk-shaped tool preferably has a circular or elliptical circumference. The disk-shaped tool is provided in particular for manipulation by rotation of the drive motor. However, it is also possible for the disk-shaped tool to have, for example, a triangular, rectangular or square contour. The disk-shaped tool can be provided, for example, for machining in which the working device is designed as a vibration grinder or oscillation grinder or for the oscillating grinding of surfaces. However, the design of the working device as a rotary grinding machine and/or as an eccentric grinding machine is preferred.

Preferably, the at least one additional air inflow opening comprises or is formed by an additional air inflow opening arranged at the outer periphery of the disk-shaped tool, in particular at the outer edge region of the disk-shaped tool, between the machine side and the working surface. In this way, dust and similar further particles can be sucked out of the surroundings of the disk-shaped tool by the additional air inflow openings at the outer edge region of the disk-shaped tool, in particular at the outer peripheral region. The dust-free or dust-free operation is thereby simplified.

Preferably, the disk tool has an assembly of the inflow opening extending annularly about the rotational axis or about a central axis of the disk tool which is perpendicular to the machining surface. At least one additional air inflow opening and/or suction air inflow opening forms an integral part of the assembly of such an inflow opening. It is understood that a plurality of, in particular concentric, ring assemblies of inflow openings (that is to say additional air inflow openings or suction air inflow openings) can be provided.

Expediently, the inflow openings of the respective assemblies of inflow openings are arranged at the same angular spacing relative to one another. The annular arrangement of inflow openings has, for example, inflow openings which are spaced at the same angular distance.

In a preferred embodiment, the assembly of the additional air inlet opening and the suction air inlet opening is arranged concentrically with respect to the axis of rotation or the central axis of the disk-shaped tool.

The outflow opening is expediently at the machine side of the disk-shaped tool. For example, at least one suction air outflow opening and/or at least one additional air outflow opening are arranged here.

Preferably, one or more additional air inlet openings are associated with the additional air outlet openings. In this case, the suction air outlet opening is preferably assigned to a suction air inlet opening or to a suction air outlet opening.

It is furthermore preferred that there are a plurality of suction air outflow openings and/or a plurality of additional air outflow openings. The suction air outflow opening and/or the additional air outflow opening are designed or arranged, in particular, in a ring assembly. For example, it is advantageous if the disk-shaped tool has an assembly of outflow openings extending annularly about a rotational axis or about a central axis of the disk-shaped tool perpendicular to the machining surface, wherein the at least one suction air outflow opening and/or the at least one additional air outflow opening form a component of such an assembly of inflow openings.

It is also advantageous in the annular arrangement of outflow openings to have outflow openings which are arranged at the same angular spacing relative to one another. In addition, it is advantageous in the case of the assembly that the assembly for the additional air outflow openings and the assembly for the suction air outflow openings are concentric with respect to the axis of rotation or the center axis of the disk-shaped tool. The suction air outflow opening can thus be radially on the inside, for example with respect to the axis of rotation or the central axis, and the additional air outflow opening radially on the outside.

Preferably, the suction means have separate inlets for the additional air outflow opening and the suction air outflow opening or their respective components. For example, the suction means has a suction air inlet assigned to the at least one suction air outflow opening and an additional air inlet assigned to the at least one additional air outflow opening.

The suction air inlet or the additional air inlet or both can have an annular or partially annular geometry. It is possible that one of the inlets is configured as a chamber or inlet chamber, and the respective other inlet extends annularly or partially annularly around the chamber or inlet chamber.

Expediently, the suction air inlet and the additional air inlet extend annularly around the rotational axis of the disk-shaped tool or the central axis of the disk-shaped tool. Preferably, the additional air inlet and the suction air inlet are concentric about the axis of rotation or the central axis.

The suction air inlet and the additional air inlet can be at least partially in flow connection. For example, it is possible to say that the infiltration air flows from one inlet to the other. This can be acceptable in the case of sufficient suction power of the suction means or of the negative pressure generator.

Preferably, however, the suction air inlet and the additional air inlet are flow-separated from one another by at least one seal, for example an annular seal. The at least one sealing portion expediently extends annularly around the axis of rotation or the central axis of the disk-shaped tool. Preferably, the at least one sealing portion is in a sealing seat or sealingly abuts against the machine side of the disk-shaped tool. Seals concentric with one another are preferred, so that, for example, an annular additional air inlet or suction air inlet is delimited by the seals.

The at least one seal can be, for example, a rubber seal or an elastic seal. At least one seal can, however, also be a brush seal, for example.

A preferred concept provides that the at least one seal comprises a radially outer seal and a radially inner seal, which are arranged and/or designed to bear against the machine side of the disk tool, with respect to the axis of rotation or center axis of the disk tool. The two seals delimit an annular chamber extending around the axis of rotation or the center axis of the disk-shaped tool and a central chamber surrounded by the annular chamber and separated fluidically from the annular chamber by a radially inner seal. Here, it is possible that the annular chamber forms the additional inlet and the central chamber forms the suction air inlet. However, it is also possible for the annular chamber to form the suction air inlet and the central chamber to form the additional air inlet or to which a corresponding inlet is associated.

Preferably, the machine tool is a working device to be operated manually or to be grasped. One embodiment of the invention can provide that a handle, in particular in the form of a bar, is arranged on the working device for gripping by the operator. Preferably, the handle is mounted so as to be pivotable or rotatable at the work apparatus about at least one pivot axis, preferably about at least two pivot axes which are angled relative to one another. For example, a universal bearing or a ball bearing can be arranged between the handle and the working device.

A further concept provides that the machine tool has a positioning mechanism with at least one positioning drive for positioning the working device transversely to the normal direction of the surface. For example, an electric drive can be provided at the working device, by means of which the working device performs a movement along the surface. Thus, for example, drive rollers or drive wheels can be provided on the work apparatus. It is also advantageous if the working device has at least one holding means which can be fixed in a stationary manner with respect to the surface and which is connected to the working device by means of at least one flexurally flexible pulling means. The traction means can be, for example, a rope, a toothed belt or the like. Preferably, the working device can be positioned by means of the traction means. However, it is also possible that the towing means is used only for the purpose that the working device cannot fall to the ground in an uncontrolled manner. Furthermore, the towing means can also be used to support the operator in the case of an inherently manual actuation of the working device.

Preferably, a current carrying mechanism is arranged at the handle for carrying current to the working device. For example, the drive motor for the working tool can be capable of passing current through the current passing mechanism.

Suitably, the handle is capable of telescoping. Preferably, the handle has a base tubular body, which engages into the calibration tubular body or into which the calibration tubular body engages. Thus, the adjusting tubular body is accommodated in the base tubular body or vice versa. It is also advantageous if the two tubular bodies can be clamped by means of a clamping device, in particular a clamping collar, in at least two different longitudinal positions that the tubular bodies can have relative to each other. The clamping collar can for example comprise a clamping threaded fastener, a clamping bar or the like.

It is possible that the section between the current-carrying means and the working device has a predetermined length and/or is not telescopic. Suitably, the telescopic section of the handle has a support for support at the body of the operator. The longitudinal position of the current carrying mechanism can be adjusted by means of a telescopic handle. Suitably, the longitudinal extension of the support extends transversely to the longitudinal extension of the handle or the telescopic section of the handle.

Drawings

Subsequently, embodiments of the present invention are explained with the aid of the drawings. Wherein:

fig. 1 shows a perspective view of a surface-machining system, which is arranged in a space with at least one surface to be machined,

fig. 2 shows the side wall of the space according to fig. 1 at two holding means and the working device of the surface machining system according to fig. 1, in the case of machining for machining a wall surface,

figure 3 shows a schematic view from below onto the top of the space of the working device with a machining top according to figure 1,

figure 4 shows a schematic view of a holding mechanism of a surface-working system with a positioning drive and a flexible traction means according to the previous figures,

figure 5 shows the retention mechanism of the surface treating system in a first longitudinal position,

figure 6 shows the holding mechanism according to figure 5 in a second longitudinal position,

figure 7 shows a first schematic view of a winding mechanism of a surface working system according to the previous figures,

figure 8 shows a further winding mechanism of the surface finishing system according to the previous figures,

FIG. 9 shows a perspective oblique view of a working device of a surface treating system, the working device being at

From above and in fig. 10

As shown from below in figure 11 of the drawings,

figure 12 shows a cross-section through the working device approximately along section line a-a in figure 10,

figure 13 shows a further cross section through the working device according to figure 10 along the sectional line B-B,

figure 14 shows a valve for controlling the underpressure in the suction area of the working device,

figure 15 shows a movable tooling machine with a first type of valve configuration for controlling the suction air flow,

fig. 16 shows detail X1 from fig. 15, with the valve in the other valve position,

figure 17 shows a top view in partial section onto a tool machine according to the two previous figures,

figure 18 shows a detailed view of the valve of the machine tool according to the three preceding figures,

figure 19 shows a section through the tool machine according to the previous figures approximately along section lines S1-S1,

fig. 20 shows a machine tool with a further valve for controlling the suction air flow in the machine tool

Figure 21 shows in partial section and with the other suction controls of the valve,

figure 22 shows a section through the tool machine according to the previous figures approximately along section lines S2-S2,

figure 23 shows a valve ring of a valve of the machine according to the previous figures,

fig. 24 shows a further machine tool with a valve for controlling the suction air flow in

Fig. 25 is shown in a partial section in a first valve position of the valve

The same partial section is shown in fig. 26, however in other valve positions of the valve,

figure 27 shows a section through the tooling machine of the previous three figures approximately along a section line of a partial section,

fig. 28 shows a perspective oblique view of the power tool with a bar-shaped handle according to fig. 27, wherein

The telescopic section in fig. 29 is shown in perspective and is shown in

As shown from one side in figure 30 of the drawings,

figure 31 shows a longitudinal section through the assembly according to the previous figures approximately along the section lines S3-S3,

FIG. 32 shows a machine tool having additional valves for controlling exhaust gas flow in

In fig. 33, the valve is in the first valve position and in partial section from above

Shown in figure 34 in the second valve position of the valve,

fig. 35 shows a machine tool with a further valve for controlling the suction air flow in

Shown in partial cross-section in fig. 36, wherein the valve occupies a first valve position,

fig. 37 shows a detail X1 from a previous figure, with the valve in the other valve position,

FIG. 38 shows a sectional illustration approximately along the partial sectional plane in the two previous figures, wherein the valve assumes the conducting position and

fig. 39 shows a detail X3 from a previous figure, wherein the valve occupies a blocking position,

FIG. 40 shows a further working device with a position-dependent valve for controlling the suction air flow, an

Fig. 41 shows a working device with a cutting working tool and a coating mechanism.

Detailed Description

With the surface machining system 10 it is possible to machine surfaces of the space RA, such as the bottom surface FB or the side or wall surfaces FL, FR, FF, which are angled with respect to each other. But it is also possible to process the top surface FD of the top of the space RA by means of the surface processing system. The machining of the lateral surfaces FL, FR and FF of the side walls is already laborious for the operator, the machining of the top surface FD being still more laborious. I.e. the operator in this case has to hold the working device 50 by means of, for example, a stick or similar other handle, which is laborious in the long term and in any case time-consuming.

However, in the surfacing system 10, the finish of the surfaces FL, FR, FF, FD is more pronounced.

That is, the working device 50 is held at the flexible pulling means 30A, 30B, 30C, 30D and is additionally sucked by means of the vacuum generated by the vacuum generator 15 (e.g. dust extractor 15B) at the respective surface FL, FR, FF, FD to be machined with at least one force component in the normal direction N of the respective surface FL, FR, FF, FD.

The negative pressure generator 15 is a negative pressure generator that is separate and spatially separated from the working device 50. The vacuum generator 15 is connected in flow communication with the working device 50 by means of a flexible suction hose 11. Alternatively or in addition to the negative pressure generator 15, however, a negative pressure generator 15C arranged locally on the working device 50 may also be possible.

The pulling means 30A to 30D can serve merely as a safety measure, so that the working device 50 does not fall to the bottom, i.e. in the direction of the bottom surface FB, in the event of a pressure drop in the negative pressure provided by the negative pressure generator 15, but an automatic or partially automatic operation is also possible, i.e. the working device 50 can be positioned by means of the pulling means 30A, 30B, 30C and 30D with respect to the respective surface FL, FR, FF, FD to be processed.

The negative pressure generator 15 is, for example, a dust extractor, i.e. it sucks in the dirt collection container 16 particles that have accumulated on the respective surface FL, FR, FF, FD of the process space RA. Thus, for example, a low-dust or dust-free processing of the surfaces FL, FR, FF, FD is possible. The vacuum generator 15 has a suction unit 17, for example a turbine with an electric drive motor. The suction unit 17 is accommodated in the housing 18, like the dirt collection container 16. The housing 18 can be arranged in a stationary manner on a base (untergrudd), for example on the surface FB, but can also be freely movable here, for example by means of rollers 19. The rolling elements 19 cannot be driven, so that the vacuum generator 15 is held stationary, for example stationary, around the space RA or can also be moved by the working device 50 when the working device is moved along the surface FL, FR, FF, FD to be processed in each case. It is also possible that one or more of the rolling elements 19 are driven, in particular controlled by a control mechanism 32, which will also be explained, in order to follow the movement of the working device 50.

Traction implements 30A-30D are retained by retention mechanisms 20A-20D. The holding means 20 are arranged stationary in the space RA, for example at respective corner regions of the surfaces FL-FD. In the exemplary embodiment shown in the drawing according to fig. 1, for example, the top of the space RA, that is to say the top surface FD, is machined. Accordingly, the holding means 20A to 20D are arranged in the respective interior angle, i.e. in the interior angle of the space a, i.e. in the corner region of the surface FD, so that a large working area or working space for the working device 50 is spanned, in which the working device 50 can be positioned freely, i.e. by manipulation of the traction means 30A to 30D or also by at least one positioning drive 340A, 340B on the working device 50. Positioning drives 40A, 40B, 40C, 40D and positioning drives 340A, 340B, which are provided for manipulating traction devices 30A-30D, form part of positioning mechanism 13.

The holding means 20 can be arranged in the space RA so as to be detachable, for example so as to be able to be clamped, so as to be able to be jammed or the like. The holding means 20 can be adjusted for a corresponding adaptation to the spatial conditions of the space RA, i.e. its respective longitudinal ends 23, 24 can be clamped, for example, against the mutually opposite faces of the space RA (for example the bottom face FB and the top face FD).

The holding means 20 are designed, for example, in the type of supports (Sprie beta en), telescopic longitudinal supports or the like. The holding mechanism has a holding base 21 on which a support body 22 is telescopically supported. The longitudinal ends 23, 24 can be adjusted, for example, into the longitudinal positions L1 and L2, where they can then be fixed by the fixing means 25 of the holding means 20. The fastening means 25 has, for example, a fastening base 26, at which a fastening body 26B, for example a clamping collar or the like, can be adjusted between a fastening position in which the support body 22 is fastened (for example locked or jammed) and a release position in which it is released, for example by means of an adjustment movement or a locking actuation LO. In the unlocked or disengaged state of the fastening mechanism 25, the support body 22 can be adjustable in the longitudinal direction, for example, which is indicated in the figures by the double arrow or the longitudinal adjustment LV. The fastening means 25 can be or comprise a tensioning means, i.e. for example the support body 22 can be adjusted with respect to the holding base 21 by means of a screw thread or similar other tensioning means, so that it can clamp the holding means 20, in particular its longitudinal ends 23, 24, between the mutually opposite faces FD and FB.

At the respective holding mechanism 20A, 20B, 20C, 20D, a traction appliance guide mechanism 27A, 27B, 27C, 27D is arranged respectively, in order to guide the traction appliance 30A-30D. The traction means guide mechanism 27 has, for example, a guide body 28, in particular a guide groove and/or a guide roller, at which the traction means 30 is guided. The guide body 28, which is mounted so as to be movable about at least one pivot axis, preferably a plurality of pivot axes, preferably at the joint 29, can thereby follow the movement of the respective pulling means 30A to 30D. Preferably, the hinge 29 relates to a ball hinge, a universal hinge or the like.

Positioning drives 40A, 40B, 40C, 40D, which respectively act on and actuate the traction means 30A-30D, are arranged on the holding means 20A-20D. For transmitting the tractive force, the traction means 30 can be designed, for example, as a rope. However, toothed belts are preferred, the respective length of which between the guide body 28 and the working device 50 can be precisely influenced or adjusted.

The positioning drive 40 has a drive motor 41, which forms the traction means drive. The drive motor 41 drives a drive roller, in particular a toothed roller 42, which rotates about a rotational axis D1. The traction means 30 is guided by the drive roller 42, so that a rotational actuation of the drive roller 42 by the drive motor 41 causes a longitudinal adjustment of the traction means 30 and thus a positioning of the work apparatus 50.

The pulling means drive 41 is arranged between the guide body 28 on the one hand and the winding body 43 of the winding mechanism 45 on the other hand. The winding mechanism 45 winds up, for example, the respective unwanted section or return portion of the pulling means 30. Preferably, the winding body 43 is spring loaded by a spring assembly 44, for example by a torsion spring. It is clear that the angle body 33, for example a winding roller or a winding drum, can be driven by the drive motor in order to wind up the section of the pulling means 30 between the pulling means drive 41 and the angle body 43. The winding body 43 rotates, for example, about the rotation axis D2.

For determining the length of the section of the pulling means 30, which is set by the pulling means drive 41 in the direction of the winding mechanism 45, i.e. the section in which the positioning drive 40 is pulled, as it were, at the work device 50, a rotational speed sensor 46 is preferably provided. The rotational speed sensor 46 can, for example, form part of the drive motor of the traction means drive, i.e. can measure the rotation of the drive motor. It is also possible for the rotational speed sensor 46 to be arranged, for example, directly at the towing means 30, for example, in the optical path there, and to measure or detect the corresponding longitudinal alignment of the towing means 30 by means of the running rollers and the like.

The control means 32 mentioned can, for example, actuate the positioning drives 40A to 40D as a function of rotational speed information, for example from a rotational speed sensor 46, or on the basis of length information about the traction means 30. The control means 32 can comprise control means arranged either on the negative pressure generator 15 and/or on the working device 50.

It is also possible for the control mechanism to be multi-part, that is to say that some parts of its components are arranged on the vacuum generator and other parts are arranged on the working device 50. These components of the respective control mechanisms can communicate with each other.

However, the control means 32 can also be or comprise a control means which can be positioned in the space RA separately from, for example, the underpressure generator 15, as schematically indicated in the drawing.

For example, the control mechanism 32 includes a computer. The control means 32 preferably comprise an input device 33, in particular a keyboard, a mouse, a touch-sensitive screen or the like, and an output device 34, for example a screen, a signal light or the like, or other optical and/or acoustic output devices, for example a voice output, a loudspeaker or the like. The control means 32 furthermore comprises a processor 35 for implementing a program, for example a program code of a control program 37, which is stored in a memory 36 of the control means 32. The control program 37 can be loaded into the processor 35 from the memory 36.

Control mechanism 32 communicates with positioning actuators 40A-40D via communication links 38A-38D, such as control lines and/or wireless links, such as a WLAN or the like. The wired communication connections 38A-38D can be bundled, for example, in sections, into a collective line or a collective communication connection 38.

In this way, the control unit 32 can actuate the positioning drives 40A to 40D, for example, in such a way that they can actuate the working device 50 between a plurality of positions with respect to the respective surface FL, FR, FF, FD to be machined. For example, traction implements 30A-30D pull work device 50 along top surface FD, where positions P1 and P2 are illustratively shown in the figures. It is possible without problems for the working device 50 to be moved here into the corner region and also along or at the edge region of the top surface FD toward the respective guide body 28 of the holding means 20. When, for example, the traction means 30D, 30C are particularly long between the working device 50 and the guide body 28 of the holding means 20D, 20C, the working device 50 can be moved between the holding means 20A, 20B, for example in the edge region of the surface FD, in order to machine the surface FD.

The working device 50 is freely movable at the surfaces FL, FR, FF, FD of the space RA. For example, the suction hose 11 connecting the working device 50 with the negative pressure generator 15 can follow the movement of the working device 50. The electrical supply lines 12, which are preferably arranged between the vacuum generator 15 and the working device 50, are correspondingly flexible and together provide the movement of the working device 50 at the surfaces FL, FR, FF, FD to be machined. The supply line 12 can be guided in the suction hose 11 or at the suction hose 11, for example forming an integral part of the suction hose. Supply line 12 is coupled to, for example, an electrical coupling portion 52A of work implement 50. Supply line 12 supplies work implement 50 with electrical energy. Thus, for example, an electrical current means 804A can be provided on the dust extractor 15, which supplies the working device 50, for example an electronically commutated (kommutierenten) motor thereof, with electrical energy via the supply line 12.

The negative pressure generator 15 can be connected to an energy supply network, for example an ac voltage network, via an electrical connection 14, for example, having a plug-in connection. The energy supply system can be used, for example, in the space RA by means of a socket into which the connecting line 14 or its plug-in connection can be inserted.

In order to position work apparatus 50 with respect to a side wall, for example wall surface FL, it is advantageous if traction means are applied to work apparatus 50 in each case via a stationary traction means guide mechanism, also in a plurality of corner regions of surface FL (for example in the upper and lower corner regions). A configuration may now be possible in which, for example, the holding means 20C, 20D are arranged in the space RA oppositely with respect to their horizontal position, so that their respective guide bodies 28 are arranged adjacent to the wall surface FL to be machined in the region of the bottom or bottom surface FB. For example, in addition to the holding means 20A and 20B, one of the holding means 20C, 20D can be arranged in each case, whose positioning drive 40 can then be pulled from below by means of the pulling device 30 at the work apparatus 50.

However, an advantageous concept is given when a second positioning drive, for example positioning drive 40U, is arranged, as it were, at the respective holding means 20, for example holding means 20A, 20B. When the working device is active at the side wall surfaces FL, FR, FF, the positioning driver 40U acts on the working device 50 through the traction devices 130A, 130B. For example, the positioning drive 40U also comprises identical or similar components to the positioning drive 40, so that, for example, the traction means drive 41U acts on the traction means 130 by means of the drive roller 42U, which can be wound up onto the winding body 43U, so to speak, downward along the winding of the traction means drive 41U or downstream of the traction means drive 41U. The winding body 43U forms part of a winding mechanism 45U and is spring-loaded, for example by means of a spring assembly 44U, in the direction of the winding-up of the pulling means 130 or is driven by a drive motor, not shown in the figures. The respective extended or adjusted length of the tractor 130, which is set by the tractor driver 41U, can be detected by means of the rotational speed sensor 46U.

The positioning drive has, for example, a communication interface 47, 47U, in particular a network interface (LAN, WLAN or the like), for communication with the control unit 32 via the communication link 38. The communication interface 47 can also be or comprise, for example, a bluetooth interface. The interface 39 of the control means 32 is designed for communication with a communication interface 47, that is to say, comprising for example a LAN, WLAN, bluetooth interface or the like.

The positioning drives 40, 40U are held or arranged, for example, at the carrier 48 or the housing 48, which is fixed in a stationary manner at the holding base 21 of the respective holding means 20.

Instead of the positioning drives 40, 40U, a positioning drive 140 can also be used. The positioning drive 140 comprises a drive motor 141 for driving a drive roller 142. The drive roller 142 is arranged between the angle body 143, the winding mechanism 145 and the guide body 28. The respective length of the section of the traction means 30 operated by the drive motor 141 can be detected, for example, by a rotational speed sensor 146, an encoder, which is arranged between the drive roller 142 and the guide mechanism 27.

Advantageously, the section of the pulling device 30 between the drive roller 142 and the winding mechanism 145 is tensioned, for example by means of a tensioning mechanism 149. The tensioning mechanism 149 comprises a tensioning means 148, for example a tensioning roller, by means of which the pulling means 30 runs. The section of the pulling means 30 extending between the drive roller 142 and the winding body 143 of the winding mechanism 145 is thereby held under tension. This optimizes the winding up of the winding device and the winding body 143.

The winding body 143 can also be driven by a spring assembly. Currently, a winding drive 144, for example an electric motor, is provided. By means of the extension of the pulling means 30 between the tensioning means 147 and the winding body 143, the winding drive 144 can be actuated, in particular adjusted, in order, for example, to hold the pulling means 30 in tension in this region.

In order to guide the pulling means 30 onto the winding body 143, a guide mechanism is preferably provided. In the example of the winding body 243 and the guide mechanism 248, this is illustrated in the drawings.

The positioning drive 240 is provided such that its winding mechanism 245 simultaneously forms a positioning drive or a traction drive for the traction means 30. The traction means 30 extends from the drive roller 242 past the rotational speed sensor 246 to a guide body 248A of a traction means guide mechanism 248. The rotational speed sensor 246 measures the length of the traction means 30 which is respectively unwound or wound onto the winding mechanism 245 and thus the adjustment path of the working device 50 during the actuation of the traction means 30 by the positioning drive 240.

The winding mechanism 245 has a winding drive 244 which simultaneously presents the pulling means drive 241. The traction mechanism drive 241 or the winding drive 244 comprises, for example, an electric motor, which can be controlled by the control unit 32 via the communication interface 247.

The guide mechanism 248 includes, for example, a slider or a traction instrument guide 248A that is guided at a guide 248B. The guide 248B is, for example, a linear guide extending parallel to the rotation axis D2 about which the winding body 243 rotates. That is, the pulling means guide 248A makes an oscillating back and forth movement along the linear guide 248B, so that the pulling means 30 is optimally wound up and unwound onto the winding 243A.

In this case, it is possible for the control mechanism 32 to also actuate the guide mechanism 248 for the pulling means 30. It is also possible for the winding mechanism 245 to have a local control for the guide mechanism 248 or for the guide mechanism 248 to function so to speak automatically, i.e. the guide mechanism together with the movement of the pulling means 30 so to speak automatically and takes care that the winding 243A of the pulling means 30 wound up on the winding body 243 is wound up precisely.

It is also possible for the work device 50 to be positioned with respect to the workpiece surfaces or space surfaces FL, FR, FF, FD to be processed by means of positioning drives located on the work device 50. Thus, for example, positioning drives 340A, 340B with drive motors, for example, work device drives 341A, 341B, can be provided on work device 50. The work device drivers 341A, 341B drive, for example, wheels or drive rollers 342, which can roll along the surface FL, FR, FF, FD to be machined. The work device drives 341A, 341B are assigned to different movement directions or movement axes, for example, which are angled, in particular at right angles, with respect to one another. The control device 32 can thus also actuate the positioning drives 340A, 340B for positioning the work apparatus 50 relative to the surfaces FL, FR, FF, FD to be machined, for example.

The working device 50 includes a tool machine 51. The machine tool 51 can also be understood as a working device 50. The working device 50 or the machine tool 51 comprises a drive aggregate 52 with a drive motor 53. The stator 54 of the drive motor 53 is arranged in a stationary manner with respect to the carrier 60 of the drive unit 52. The rotor 55 of the drive motor 53 rotates about the motor rotation axis DM.

The drive motor 53 drives a tool receptacle 58, at which a working tool 90A, for example a disk tool 90, can be arranged or is arranged.

The driven end 56 of the rotor 55, at which, for example, a gear is arranged, drives the eccentric 57, in particular a drive 57B, for example a gear, of the eccentric 57. The eccentric 57 has a tool receptacle 58 for a disk tool 90. The tool receiving portion 58 is arranged at the rotary support 59 of the eccentric 57, so that the tool receiving portion 58 can rotate about the tool rotation axis DW. The tool rotational axis DW and the motor rotational axis MD have an eccentricity EX with respect to each other. Thus, that is to say, the disk tool 90 is carried eccentrically about the motor axis of rotation DM and in a supercycloidal movement about the tool axis of rotation DW. In this way, a quiet operation of the disk tool 90 is obtained, which simplifies the manual operation of the working device 50, but also the actuation by means of the positioning drive 40.

The carrier 60 has a top wall 61 which covers the disk-shaped tool 90 at least at the upper side, preferably also at its outer periphery 93.

The motor housing 62, in which the drive motor 53 is housed, protrudes forward of the top wall 61. At its side facing away from the disk tool 90, the drive motor 53 has a fan 63, by means of which a cooling air flow can be generated through the drive motor 53.

The cooling air flow KL can flow out through the suction coupling 71 of the suction mechanism 70 of the working device 50. For example, the suction hose 11 is coupled to the suction coupling 71.

The disk tool 90 has a machining surface 91 for machining one of the surfaces FL, FR, FF, FD of the space RA, wherein of course also other surfaces, for example surfaces of wood or metal workpieces, can be machined by means of the machining surface 91. A grinding device, a polishing device or the like can be arranged directly at the machining surface 91. An adhesive layer 98 is provided in the present case, at which a grinding means 99, for example a grinding disk, is releasably held. The adhesive layer includes, for example, hook and loop devices, hook and loop fasteners, and the like.

The machining surface 91 is currently planar, but can also have other contours, for example grooves or the like.

The disc-shaped tool 90 has a machine side 92, wherein the machine side 92 and the machining face 91 face away from each other or are arranged at opposite sides of the disc-shaped tool 90.

The machine side 92 is arranged at the disc-shaped tool carrier 100 and faces the top wall 61 of the carrier 60. At the disk-shaped tool carrier 100, which is substantially resistant to bending, for example made of a respectively loadable plastic material, an elastic layer 101, for example a so-called grinding pad or carrier pad, is arranged. The machining face 91 is arranged at the side of the layer 101 facing away from the disc-shaped tool carrier 100.

At the processing surface 91, a suction air inlet opening 94 is provided, which is in flow connection with a suction air outlet opening 95 at the machine side 92. For example, the flow channels pass through the layer 100 and the disc-shaped tool carrier 101. By the suction-air inflow opening 94, the suction air AL can flow into the suction-air inflow opening 94. The suction air AL is shown in the figure by hatched arrows.

The suction air AL serves to suck the disk tool 90 and thus also the working device 50 to the workpiece surface to be machined.

The intake air inflow opening 94 is annularly provided at the processing surface 91. For example, a plurality, in particular at least two, in the present case four concentric ring assemblies 94A, 94B, 94C, 94D of intake air inflow openings 94 are provided.

The intake air inlet opening 94 extends annularly around a central axis of the disk-shaped tool 90, which currently corresponds to the tool rotation axis DW.

Meanwhile, a suction air outflow opening 95 is arranged annularly around the tool rotation axis DW. It is possible to provide a plurality of annular assemblies of the suction air outflow opening 95, in particular concentric with respect to one another. The only annular component of the suction air outflow opening 95 is regularly shown in the drawing.

Furthermore, an additional air inflow opening 96 is provided at the disk tool 90, through which additional air ZL can flow into the disk tool 90. The additional air ZL is symbolically shown in the drawing by white arrows. The additional air inflow opening 96 is in flow connection with an additional air outflow opening 97 at the machine side 92 of the disk tool 90, for example by means of a flow channel which is not labeled in more detail, which passes through the adhesive layer 98, the elastic layer 101 and the disk tool carrier 100.

In principle, it is possible that the additional air ZL is also responsible for sucking the disk-shaped tools 90 to the surfaces FL, FR, FF, FD to be machined. For example, an additional air inflow opening 196 is provided for this purpose at the disk tool 190.

In contrast, in the case of the disk tool 90, the additional air inflow opening 96 is arranged at its outer periphery 93. That is to say, the additional air inflow opening 96 is oriented radially to the outside with respect to the central axis of the disk tool 90, in the present case the tool rotation axis DW. The additional air ZL can thus convey particles, dust or the like out of the surroundings of the disk-shaped tool 90 in the direction of the disk-shaped tool 90 and out through the additional air outflow opening 97.

The suction means 70 has a suction-air inlet 72, which is assigned to the suction-air outflow opening 95 and is in flow connection therewith. Furthermore, the suction means 70 comprise an additional air inlet 73, which is in flow connection with an additional air outflow opening 97.

The suction air inlet 72 is limited by a seal 74, for example an annular seal, which abuts against the machine side 92 of the disk tool 90. The seal 74 is designed as an annular seal, like the seal 75, wherein the seal 75 is radially outward of the seal 74. Thereby, an annular chamber is defined between the seals 74, 75, said annular chamber delimiting the additional air inlet 73. A radially outer seal 75 seals the additional air inlet 73 against atmospheric pressure.

The suction air inlet 72 can still be said to form a central suction chamber which is in the inner space of the seal 74. Through the bypass channel 76, the suction air inlet 72 communicates directly with the suction coupling 71 and thus with the negative pressure generator 15.

The additional air inlet 73 communicates with the suction connection 71 via a valve 85, the valve collar 86 of which can be adjusted between at least two, preferably a plurality of, valve positions.

The valve 85 forms part of the suction control 80 or can be actuated by it. The valve member 86 can be adjusted within the valve housing 87 of the valve 85, for example, can be pivoted about a pivot axis SW 1. By means of the valve member 86, the valve passage 88 can be opened or closed at the valve housing 87, intermediate positions also being possible. On the input side, the valve 85 communicates with the additional air inflow opening 96, i.e. with the additional air inlet 73. Valve passage 88 and thus the output of valve 85 are in flow connection with suction connection 71. As a result, depending on the valve position of the valve ring 86, more or less suction air is sucked out of the additional air outflow opening 97 and transported away through the suction connection 71.

The valve member 86 has a cylindrical peripheral wall 86A which can be moved past the inner periphery of a likewise cylindrical peripheral wall 87A of the valve housing 87. The peripheral walls 86A, 87A substantially sealingly abut against each other. A seal 88A is arranged between the end side of the peripheral wall 86A and the top wall 61 of the carrier 60 (which carrier forms part of the valve housing 87 in this respect). The sealing portion 88A also functions as a clamping mechanism 88B to clamp the valve ring 86 in the respective valve position.

The peripheral wall 86A projects forward of the top or bottom wall 86B of the valve member 86. A peripheral wall 87A of the valve housing 87 extends between the top wall 86B and the top wall 61 of the carrier. Thus, that is, the valve ring segment 87 is accommodated in a sandwich manner between the top walls 61, 86B.

To support the valve member 86 with respect to the valve housing 87, a rotary support 86C is provided. For example, a bearing projection 86D projects from the top wall 61, which engages into a bearing receptacle 86E of the valve ring 86. A securing element 86G, such as a threaded fastener, is used to secure the valve ring 86 at the support tab 86D. The fastening element 86G preferably generates a pretensioning of the valve element 86 in the direction of the seal 88A. The fixing element 86G extends, for example, parallel to the pivot axis SW 1.

At the side facing away from the interior of the valve 85, the valve ring 86 has an actuating handle 86F for gripping by an operator.

The actuating handle is simultaneously designed as an index element, which can be adjusted, for example, in the direction of the markings 89A-89D, which indicate the respective valve position of the valve 85.

One or more of the markings 89A-89D can have, for example, a latching projection 89E, by means of which the valve element 86, in particular the actuating handle 86F, can be latched, for example, by means of a latching projection or latching projection 89F at its free end region. The latching projections 89E can be provided, for example, in each case in pairs in at least one of the markings 89A to 89D, so that the actuating handle 86F can be snapped in between the latching projections 89E.

The marking portions 89A, 89D correspond to, for example, the on position and the off position of the valve 85. The mark portions 89B, 89C indicate the mixing ratio of the suction air flowing through the additional air inflow opening 96 to the suction air flowing through the suction air inflow opening 94, which is optimally suitable for the side wall processing (mark portion 89B) or for the top processing (mark portion 89C), for example. In the case of a top machining, for example of the top surface FD, as little additional air as possible is sucked in, so that the suction power or the suction force in the normal direction N, which can be generated by the suction air flowing through the suction air inflow opening 94, is as large as possible.

The working device 50A and the disk-shaped tool 90 thereof correspond substantially to the working device 50 in which a valve 185 is provided instead of the valve 85. The valve 185 forms, for example, a component of the suction controller 180 or can be actuated by said suction controller. The valve 185 serves to control the underpressure in the region of the additional air outflow opening 97, but oscillates about an oscillation axis SW2 which is transverse to the flow direction of the suction air flow which flows through the suction connection 71. Preferably, valve ring 186 of valve 185 is arranged below suction coupling 71. Valve element 186 has a peripheral wall 186A, for example, partially cylindrical, extending between end walls 186B, 186C. End walls 186B, 186C can be said to be the bottom and top sides of an imaginary cylinder of valve collar 186. At the end walls 186A, 186B, for example, support projections 186D are arranged, which engage in corresponding receptacles of the valve housing 187 and enable a pivot support of the valve link 186 about the pivot axis SW 2.

Before the actuating handle 186F, for example an actuating lever or an actuating projection, on which the operator can adjust the valve collar 186, projects into the end wall 186B, the valve passage 188 provided on the peripheral wall 186, i.e. the interruption of the peripheral wall 186 by a predetermined corner section, can be brought into a conducting position in which the outlet of the additional air inlet 73, i.e. for example the opening between the seals 74, 75, is open. However when the peripheral wall 186A closes the opening 189.

In the schematically illustrated working device 50B, a valve 285 is provided in place of the valve 85 or 185. The valve 285 has a valve ring 286 which can be actuated manually by means of an actuating handle 286 f. A manipulation knob 286F is disposed at the valve collar 286 of the valve 285. Valve element 286 has a plate-shaped wall 286A. The wall 286 has a part-annular shape so that it can close or open a likewise part-annular opening at the top wall 61, which top wall delimits the valve passage 288 of the valve 285.

Valve passage 288 extends within valve housing 287 of valve 285. The valve housing 287 has a side wall 287A which projects from the top wall 61 and is closed by a top wall 287B. A suction coupling portion 71 is arranged at the top wall 287B. Further, the valve housing 287 communicates with a suction air outflow opening 95, which is arranged in an inner space of the peripheral wall 287C of the valve housing 287. In an inner space limited by the peripheral wall 287C, which inner space delimits, as it were, the suction air inlet 72, for example, a drive motor 53 (schematically shown) is arranged.

The actuating grip 286F can engage, for example, with a clamping or latching section that cannot be seen in the figures, into a guide recess 289 (which is, for example, an extension of the valve passage 288) in order to latch, latch or latch the valve ring segment 286 in one or more valve positions with respect to the valve housing 287 (that is to say the top wall 61 at present), or the like. The clamping or latching section can, for example, engage into the guide recess 289 and be in the rear grip therewith.

Guide recess 289 and valve passage 288 extend annularly about a pivot axis SW3, about which valve ring 286 can pivot. In this case, valve collar 286 is adjusted about pivot axis SW3 in a sliding movement along valve passage 288. The swing axis SW3 and the motor rotation axis DM are preferably coaxial.

Valve 385 of work implement 50C substantially corresponds to valve 285. Components of the same type are therefore provided with reference numerals which are 100 greater than the valve 286. As long as identical components are present, they are provided with the same reference numerals.

A valve ring 386 of the valve 385 closes off a valve passage 388, which extends arcuately or annularly about the pivot axis SW3 as the valve passage 388. However, the actuating handle 386F for the manual actuating valve element 386 is not guided at the valve passage 388 but at a guide 385G separate therefrom. The guide portion 386G extends annularly about the swing axis SW3 as do the valve passages 288, 388. By means of the separate guide 386G, any clamping, latching or similar means can be realized for latching or latching the actuating handle 386B and thus the valve element 386 in the predetermined valve position.

Preferably, valve 385 includes valve driver 82, such as drive motor 382, which is in driving engagement with, for example, top wall 61 or other member fixed in position with respect to carrier 60. For example, the drive motor 382 can have a pawl at its driven end that engages into teeth fixed in place at the carrier 60. To manually operate the valve 385, the pawl and teeth can be brought out of engagement or the drive motor 382 run together with little resistance, for example. Thus, in other words, for manual actuation of the valve, a decoupling of the valve drive is possible within the scope of the invention.

Work implement 50D is configured similarly to work implements 50B, 50C and has valve 485 in place of valves 285, 385. The valve 485 has a valve housing 487, which is constructed analogously to the valve housing 287 and has the same reference numerals in the figures accordingly. The valve passage 488 of the valve 485 communicates with the additional air inlet 73 and can be closed by a valve element 486.

The valve element 486 has a wall-like or plate-like shape, for example a plate-like body 486A, which can be pivoted about a pivot axis SW4 between a conducting position DS, in which the valve passage 488 is in flow connection with the suction connection, and a closed position SS, in which the valve passage 488 is closed.

By the negative pressure occurring at the suction connection 71, the valve element 486 is acted upon by a force in the direction of its open position DS and can be acted upon by an actuating mechanism having an actuating element 486B into its closed position SS.

Instead of or in addition to the actuating element 468B, a spring 468K can also be provided without any problem, which loads the valve element 486 into its closed position SS. The valve 485 is operated under pressure control in this case, i.e. the valve 485 opens when the negative pressure at the suction connection 71 is greater than the spring force of the spring 468K, so that the negative pressure in the suction region or at the machining surface 91 of the disk tool 90 decreases, since it can be said that external air can flow through the additional air inflow opening 96.

The actuating element 486B is mounted so as to be pivotable on the valve housing 487, for example on one of the side walls 487. Actuating element 486B comprises, for example, a rocker lever, the free end region of which can act on valve element 486 in order to adjust the latter into closed position SS. That is, the actuating element 486 has, for example, a rod-like shape or rod.

Connected to the actuating element 486B is an actuating handle 486F, for example a rocker lever, which is arranged on the outside of the valve housing 487, for example also on one of the side walls 487A or 487B. The lever handle 486B comprises, for example, a joystick that can be grasped by an operator. The actuating handle 486F can be latched by means of a latching mechanism 486H in different latching positions (which correspond to the valve positions of the valve 485, for example the positions DS or SS), for example in the open position and/or the latched position and preferably one or more valve positions located therebetween. The latching mechanism 486H has, for example, a latching projection 486I, by means of which the actuating lever 486G can be latched. The latch tab 486I protrudes forward of one of the side walls 487A.

The valve 585 of the operating device 50E, which can be said to be automatic and in any case operates as a function of position, has a valve collar 586 in the form of rolling bodies, in particular balls or the like. Valve link 586 is freely movably received in valve housing 587 of valve 585. The valve housing 587 has, for example, peripheral walls or side walls 587A which may be narrowed or oriented toward one another, as it were, relative to an outlet 587B of the valve housing 587. Thus, that is to say, the valve housing 587 is narrower in the region of the outlet 587B than in the region of one or more valve passages 588 provided at the wall 588A which, as it were, closes off the additional air inlet 73. That is, air flowing through the additional air inlet 73 can flow through one or more of the valve passageways 588 to the outlet 587B, which is itself in flow connection with the suction coupling 71.

When the working device 50 occupies the overhead position (Ü berkopf-Lage), that is, for example, when the top surface FD is machined, the valve ring 386 is moved away from the valve passage 588 into a position closing off the outlet 587B, which is indicated in the drawing by a continuous line of the valve ring 586. As a result, air flowing through the additional air inflow opening 96, which air is present as if it were infiltration air (sometimes referred to as excess air), can no longer reach the suction connection 71, as a result of which the suction force in the region of the suction air inflow opening 94 is increased. However, when the working device 50 assumes a vertical orientation, for example, that is to say the processing surface 91 extends vertically, the valve collar 586 can reach away from the outlet 587B, for example sliding or rolling along an inclined portion of the side wall 587A, so that the outlet 587B becomes free and thus the inlet air (Zuluft) or infiltration air can flow in through the additional air inflow opening 96.

Furthermore, it is shown in the figures that the valve ring 586 can also be brought into a position (shown in dashed lines) closing off at least one valve passage 588.

In the exemplary embodiment of the disk tool 190, it is also indicated that an additional air inflow opening 196 can also be arranged at the machining surface 91, so that the valve 585 can be used, for example, directly to influence the air flow through the machining surface 91 or the underpressure present there.

Apart from the so-to-speak automatically acting concept of the negative pressure effect by the valve to be actuated manually or by the position-dependent valve (585), the servomotor or regulated concept is also possible without problems:

for example, the suction controller 80 includes an adjusting mechanism 81. The adjusting mechanism 81 can, for example, actuate a valve drive 82 of a motor, in particular a servomotor. Valve driver 82 can, for example, directly drive one of valve segments 86, 186, 286, 386, or 486.

Valve driver 82 can also include, for example, a magnetic driver 582, such as an electrical coil, to manipulate valve ring 586 into one or more valve positions.

Suction controller 80 can actuate valve actuator 82 by means of sensor signals of one or more sensors of sensor assembly 83, for example by means of position sensor 83A, whose output signal indicates the angular position of work apparatus 50 relative to a base, for example surface FD. The motor sensor 83B is in turn, for example, a current sensor or comprises a current sensor, the output signal of which or a sensor signal, for example, is indicative of the power of the drive motor 53. Depending on the suction of the working device 50 at the surface to be machined, the friction of the machining surface 91 at the surface to be machined changes, wherein then the drive power of the drive motor 53 and thus its motor current also changes, which can be detected by the motor sensor 83B. The control device 81 can then actuate the valve drive 82 of the motor, for example, with increased motor output, in the sense of reducing the negative pressure in the suction region and with reduced motor output, in the sense of increasing the negative pressure.

However, direct pressure or flow measurement is also possible, i.e. by means of pressure sensor 83C and/or flow sensor 83D. For example, the pressure sensor 83C is arranged in a vacuum region or suction region and directly measures the vacuum with which the disk tool 90 and thus the working device 50 are sucked onto the surface to be processed.

Possible examples are force sensors 83F, 83G, for example strain gauges or the like, which measure the pressing force with which the contact body 65B and/or the disk tool 90 is pressed against the surface to be machined. The force sensor 83G can be arranged, for example, at the drive train of the work apparatus 50, for example, at a support. When the contact force of the contact body 65B becomes too great, for example, the suction controller 80, in particular the adjusting mechanism 81, can actuate the valve drive 82 in the sense of reducing the negative pressure or, in the case of too small a pressing force, actuate the valve drive 82 in the sense of increasing the pressing force.

The working devices 50, 50A, 50B, 50C, 50D, 50E, 50F can be provided for manual operation, that is to say operation guided by an operator. It is also possible, however, to apply it to a robot operation in the case of the positioning means 13.

For example, the working device 50 is subsequently described in a mounted position in the housing 64, which can be actuated by the positioning mechanism 13. The carrier 60 of the other working devices 50A, 50B, 50C, 50D, 50E, 50F can also be actuated by the pulling device 30 and can preferably also be accommodated in the housing 64.

It is recognized that work apparatus 50 can be used automatically or guided manually. For example, the traction means 30 but can also act directly on the working device. Currently, however, the working device 50 is designed such that the carrier 60, including all the components held at it (i.e. the drive aggregate 52 and the disk tool 90/working tool 90A), is accommodated in the housing 64. The housing 64 forms a suction housing 64A, and an internal space 64E of the suction housing forms a negative pressure space, as it is. The housing 64 has a peripheral wall 64B that is covered by a top wall 64C. The top wall 64C has a dome or hood 64D in which a flow channel or chamber for cooling air KL is formed, which flows out of the drive motor 53 or its ventilator 63. The cooling air KL can be sucked away through the suction coupling 64F, for example, to which the suction hose 1 can be directly coupled. The suction connection 64F is fluidically connected to a suction connection 71 of the drive aggregate 52, which is arranged in the interior 64E, so that air flowing out of the suction connection 71, which represents the exhaust air connection, can be sucked away via the suction connection 64F.

A traction means fastening 67 is provided on the housing 64, to which the traction means 30A-30D can be detachably fastened, for example can be connected in a snap-in manner by means of a socket assembly, can be connected by means of a magnetic fastening, or the like. Thus, although the traction means 30 can be easily detached from the fastening portion 67 or easily fastened thereto by the operator, it then has a fixed hold so that the traction force of the positioning mechanism 13 or the positioning drive 40 can be transmitted to the working device 50.

The fastening portions 67 are arranged at the housing 64 at the same angular distance, for example at an angular distance of correspondingly 90 °, so that the tractive force of the traction means 30 can be optimally transmitted to the housing 64.

Furthermore, the housing 64 carries a guide mechanism 65 for guiding at the surface FL, FR, FF or FD to be machined respectively. The guide means 65 comprise a guide carrier 65A which is fixed at the housing 64 or forms an integral part of the housing 64. The guide carrier 65A supports at least one abutment 65B, for example an annular abutment 65B or an assembly of a plurality of abutments arranged in an annular manner, which extend around the working tool 90A. The guide carrier 65A has a guide contour 65C, for example a guide surface, which is preferably in the same plane as the machining surface 91 when the tool machine 51 is in abutment against one of the surfaces FL-FD, as is schematically shown in the figures. The abutment 65B preferably comprises a seal, in particular a sealing ring, which delimits a suction region 65G of the housing 64. Within the suction area 65G, a disk tool 90 or a working tool 90A is arranged.

It is recognized that both the disk tool 90 and the entire housing 64 are thereby sucked onto the surface to be machined of the workpiece or of the space. However, the guide of the working device 50 is primarily performed by the abutment 65B with respect to the surface to be machined.

The abutment body 65B is mounted so as to be movable with respect to the guide carrier 65A and is spring-loaded by a spring 65D in the direction of an abutment position in which the guide contour 65C abuts against the surface to be machined. The spring 65D, like the abutment 65B, is accommodated in a spring chamber 65E, where it can move linearly in the normal direction with respect to the machining surface 91 or in the normal direction with respect to the guide contour or guide surface 65C, preferably also in an oscillating movement transversely to said direction. That is, the contact body 65B is preferably mounted on the guide carrier 65A not only in a linearly displaceable manner parallel to the motor axis of rotation DM or the tool axis of rotation DW, but also transversely thereto about at least one pivot axis. Thus, the contact body 65B is mounted in a floating manner in the spring chamber or bearing receptacle 65E.

Preferably, the disk-shaped tool 90 is nevertheless flexible with respect to the surface to be machined, for example due to the elastic layer 101. The optimum adaptation to the contour of the surface to be machined is also improved in that the drive unit 52 is mounted so as to be movable relative to the guide 65 by means of a bearing 66.

The support means 66 comprise, for example, a membrane 66A, which is fixed in place with respect to the housing 64, i.e. for example in a sandwich-like manner between holding sections 66B, 66C, which are provided on the one hand by the housing 64 (i.e. the peripheral wall 64B of the housing) and on the other hand by the valve carrier 64H. The valve carrier 64H extends annularly around the working tool 90A and is accommodated in a sandwich-like manner, as it were, between the guide means 65, in particular the guide carrier 65A, and the peripheral wall 64B.

That is, the diaphragm 66A effects a floating, multi-axis oscillating movement of the drive assembly 52 relative to the housing 64 or the guide 65, so that the working tool 90A can easily follow the surface contour of the surface to be machined. Furthermore, the working tool 90A can be linearly adjusted with respect to the guide mechanism 65, i.e. parallel to the tool rotation axis DW.

Instead of the diaphragm 66A, for example, a pivot bearing, in particular a universal pivot bearing and/or a sliding bearing, can also be provided.

Preferably, the drive assembly 52 and thus the working tool 90A are spring-loaded into a contact position in which they are in contact with the workpiece surface to be machined, for example, a spring assembly 69 being provided for this purpose. The spring arrangement 69 comprises an assembly of one or more springs 69A which are supported on the one hand at the housing 64 or carrier 60 and on the other hand at the membrane 66A, i.e. by means of spring mounts 69B, 69C. A spring fixing portion 69C is arranged at the diaphragm 66A, and a spring fixing portion 69B is fixed in place with respect to the guide mechanism 65, that is, with respect to the housing 64. Since the housing 64 is fixed in position with respect to the guide mechanism 65, the spring fixing portion 69B supports the spring 69A, the bearing mechanism 66 and the drive unit 52 held thereby with respect to the guide mechanism 65.

Furthermore, the support mechanism 66 provides that the working tool 90A is displaced from a working position, shown in the drawing, in which the working tool 90A is in contact with the surface to be machined, into a rest position adjusted away from the working position. For this purpose, a servo drive 68, for example a servomotor or the like, is provided. The servo drive 68 has a drive means 68A, such as a rod, roller or the like, by means of which it acts on a transmission element 68B, such as a traction means, a traction cable, a rod-shaped element or the like. The transmission element 68B is connected to the drive 68A and the drive unit 52, i.e. to the diaphragm 66A, which is itself connected to the drive unit 52. The transmission element 68B therefore pulls the diaphragm 66A, so to speak, away from the guide contour 65C in order to adjust the working tool 90A into the rest position. The rest position is advantageous, for example, when the working tool 90A is not in use, in particular when it is pre-positioned before the actual surface machining. Thus, the disk tool 90 may not be able to cause injury, but is set inactive or held in a rest position for so long until actual surface machining is started.

Preferably, the servo drive 68 acts on the diaphragm 66A or on the drive unit 52 at least two points lying opposite one another or at a plurality of points having the same angular spacing relative to one another.

In this case, it is possible to set the basic suction force by means of the valves 85 to 585, by means of which the disk tool 90 is sucked in each case at the surface to be machined. It is also possible, however, that the valves 85-585 are fully opened. In both scenarios, the suction force control or negative pressure influence explained below can be advantageously used:

i.e. the additional air flowing through the additional air inflow opening 96 can be influenced not only at the machine side 92 of the disk tool 90, but so to speak also from the outside.

That is, a valve 685 is disposed at the housing 64, particularly the valve carrier 64H, of the working device 50. The valve 685 has a valve passage 688 arranged, for example, at a wall 687 of the valve carrier 64B. The wall 687 extends annularly alongside the peripheral wall 64B of the suction housing 64A and forms a step. It is preferably provided that a plurality of valve passages 688 spaced apart, in particular angularly, from one another are provided at the wall 687. The valve passageway 688 has an annular shape, for example, and thus follows the outer peripheral contour of the peripheral wall 64B. Valve passageway 688 is in flow connection with an annular space 689 that extends around work tool 90A. Furthermore, the annular space 689 is flow-open at the radial outer circumference of the working tool 90A relative to the additional air inflow opening 96, so that the air flowing in through the valve passage 688 can reach the additional air inflow opening 96 and thereby reduce the suction force in the region of the suction air inflow opening 94, as it were. Then, the infiltration air is sucked in, so to speak, through the suction coupling 71 or 64F, i.e., through the valve passage 688 and the additional air inflow opening 96.

Valve 685 has a valve ring segment 686. The valve element 686 is plate-shaped and has a carrier layer 686A, at which a sealing layer 686B is arranged. The sealing layer 686B faces the wall 687 and is adapted for sealing closure of the corresponding valve passageway 688.

The valve link 686 is mounted so that it can move on bearing projections 686C, 686D which project in front of the wall 687. For example, support tabs 686C, 686D relate to latches, threaded fasteners, or the like along which valve link 686 can slide and/or swing.

In the closed position SS, the valve ring 686 closes the valve passage 688, which is released in the conducting position DS of the valve ring 686.

Linear adjustment of the valve link 686 with respect to the longitudinal axis of the bearing projection 686C, 686D is possible, for example. However, currently, oscillatory motion of the valve link 686 at one of the support protrusions 686C, 686D is desired. The pivoting movement is triggered or effected, for example, in that springs 686F, 686G, which are arranged on the bearing projections 686C, 686D and are supported on their support projections 686H and on the valve ring 686, are prestressed with different strengths or with different strengths. Thus, for example, the spring 686F has a smaller spring force than the spring 686G, since the spring 686F is less pre-tensioned.

Springs 686F, 686G load valve link 686 into closed position SS. By means of the negative pressure in the intake region 64G, the valve collar 686 can be adjusted into its conducting position DS. That is, when the atmospheric pressure is greater than the negative pressure in the suction area 64G by a predetermined magnitude, it acts on the valve link 686 in the sense of opening the valve 685. The automatic negative pressure control is thus realized, as it were, by the spring assembly.

Additionally, the operator, however, can also flow outside air or additional air into suction area 64B through valve 685M. The valve 685M includes a valve passage 688B disposed at a radially outer peripheral edge of the valve carrier 64H. The valve passage 688 is in flow connection with the suction region 64G and can be closed off by at least one valve link 686M. The valve element 686M is, for example, an annular body, in particular an annular body with a plate-like outer shape, which can be pivoted about an axis of rotation parallel to the motor axis of rotation MD. A plurality of actuating knobs 686H, for example actuating projections, are arranged on the valve link 686M, so that an operator can adjust the valve link 686M by actuating one of the actuating knobs 686H between a closed position, in which the valve passage 688B is released, and a closed position, in which the valve passage is closed, and preferably one or more valve positions located therebetween.

The working devices 50, 50A, 50B, 50C, 50D, 50E, 50F can be adjusted with respect to the surface to be machined by the positioning mechanism 13. But also by means of a handle, which will become clear later.

Preferably, the bar-shaped handle 800 is pivotally hinged to the working device 50, 50A, 50B, 50C, 50D, 50E, 50F to be capable of multi-axis swinging. For example, a pivot joint 801 is provided, which pivotably supports the handle 800 about a pivot axis SQ, which extends transversely to the longitudinal axis LL of the handle 800. The additional ability to pivot about an additional pivot axis (which extends, for example, transversely to pivot axis SQ) is achieved by means of a pivot joint 801, which is only schematically illustrated in the drawings. The pivot joints 801, 802 together form a universal pivot joint.

The fixed rod section 803 of the handle 800 extends from the swing hinge 801 along the longitudinal axis LL. At the longitudinal end region of the rod section 803 remote from the working device 50, a current-carrying mechanism 804 is provided for carrying current to, for example, the drive motor 53. It should also be mentioned in this connection that the drive motor 53 is preferably an electronically or electrically commutated drive motor.

The current-carrying mechanism 804 is disposed between the wand section 803 and the telescopic section 805 of the handle 800. The telescopic section 805 comprises a base tubular body 806, which is fixedly connected to the current-carrying means 803. At the base tubular body 806, the calibration tubular body 807 is displaceably supported about the longitudinal axis LL. For example, the tuning tubular body 807 is engaged into the inner space of the base tubular body 806.

At the free end region of the adjusting tubular body, a support 808 is present, which preferably extends transversely to the longitudinal axis LL. The support 808 is suitable, for example, as a support for supporting at the body of the operator, for example as a kind of shoulder support or the like. Thus, the handle 800 can be used extremely ergonomically.

The calibration tubular body 807 can be calibrated with respect to the base tubular body 806 along a calibration path limited by longitudinal stops 809, 810 arranged at the base tubular body 806 or at the calibration tubular body 807.

In the respective longitudinal position of the adjusting tubular body 807 with respect to the base tubular body 806, it can be fixed by means of a fixing mechanism 811. The fastening means 811 comprises, for example, a fastening portion which is fastened to a base tubular body 806 of the sleeve or collar type, for example clamped by means of radially projecting holding projections 815 (which are screwed to one another, for example) or the like. The fastening part 812 has a clamping collar 813 which can be adjusted by means of a handling grip 814, for example a clamping threaded fastener, a clamping rod or the like, between a position in which the adjustment body 807 is clamped or fixed with respect to the base body 806 and a disengaged position in which it is released with respect to the base body 806 and can thus be adjusted.

The working device 50F is to be understood as an example in which the coating means or a working device suitable for machining of a workpiece surface, for example a surface, can also be actuated and positioned by means of the positioning means 13.

The working device 50F has a coating mechanism 980 with coating heads 981A, 981B as a coating tool 981. The coating heads 981A, 981B are designed for coating a surface to be processed or coated, that is to say they can apply, for example, a coating fluid, in particular a pigment liquid, pigment particles, onto the surface. The coating fluid is contained in a reservoir 983A, 983B of the working device 50F and/or is supplied to the working device 50F from a stationary device, for example a reservoir at the dust extractor 15B, via a flexible line. For example, paint or similar further coating fluids can be contained in the storage containers 983A, 983B, which can flow via lines 982A, 982B to the coating heads 981A, 981B in order to coat the surface to be processed, for example with a dye and/or to provide a protective layer or the like.

Furthermore, the coating means 980 can also comprise, for example, a wiping means 985, in particular a wiping head, by means of which at least some of the coating applied by means of the coating heads 981A, 981B can be wiped off again.

The erasing means 985 or erasing head and the coating tool 981 or coating heads 981A, 981B are connected or can be connected to the control means 32, for example, via a communication line 984. Instead of the communication line 984, it is also possible to provide a wireless connection, for example a radio connection, of the control means 32 and to the control means 32. Via a communication line 984, the control unit 932 can control, for example, the extraction of color or the like, or else further coating by means of a coating tool 981 or coating heads 981A, 981B, or also cause or control the wiping by means of a wiping mechanism 985, which comprises, for example, a wiping mechanism, a grinding head or the like.

The coating means 980 is arranged at a support 990, in particular plate-shaped. The support 990 has, for example, a base 998, at which a machining surface 991, for example a support surface for supporting at a surface to be machined, is arranged. The processing surface 991 is provided, for example, on a slide body or slide layer 999, which is arranged on the end face on the base body 998.

The coating heads 981A, 981B and the wiping head 985 are arranged, for example, in a cavity of the substrate 998, which cavity is set back behind the machining surface 991.

To the base body 998, additional air inflow openings 96, suction air inflow openings 94 and the like can be arranged, which are, for example, already explained and communicate with the additional air inlets 73 and the suction inlets 72, for example, already explained. Suction control is possible, for example, by means of a valve 585, so that the processing surface 991 can be sucked in an optimal manner, as the already explained processing surface 91, onto the surface to be processed.

That is, all the previously mentioned embodiments are possible in the case of the working devices 50 to 50E also in the case of the working device 50F with regard to suction control or vacuum control at the working surface 991, which is or forms the support surface for this purpose.

Further, the working device 50F can include or form a tooling machine 951. Which can be provided alternatively or in addition to the coating means 980.

The tool machine 951 includes a drive motor 953 that drives the tool receptacle 958 via a tool shaft 956. A working tool 90F, for example a milling head, is arranged or can be arranged at the tool receptacle 958.

The machining surface 991 forms, for example, a guide profile 965C of the guide mechanism 965.

The milling head or other working tool 90F can permanently project ahead of the machining surface 991 or guide contour 965C or can advantageously be adjusted by means of the servo drive 994 between a position projecting far ahead of the machining surface 991 or guide contour 965C (drawn in dashed lines) and a working position or depth setting position projecting less far ahead of the machining surface 951 or guide contour 965C, in particular even after the machining surface 991 has been retracted. As a result, the working tool 90F can penetrate far or less far into the workpiece to be machined. In particular during the positioning by the positioning means 13, in which case the working tool 90F does not machine the surface to be machined or is inoperative, it is possible for the working tool 90F to be set back behind the guide contour 965C, so that it is not in contact with the workpiece.

The servo drive 954 and the drive motor 953 are connected or connectable via a communication connection 955, for example a communication line or a wireless connection, to a control unit 32 which actuates the drive motor 953 and the servo drive 954 in accordance with the workpiece surface to be machined.

In the same way, it is also possible in principle for example for the coating tool 981 and/or the wiping mechanism 985 to be adjustable into a position projecting farther ahead of the guide contour 965C or into a position adjusted back to the guide contour, in particular back to the guide contour, in such a way that, for example, the servo drive 986 is arranged at the coating tool 981 and/or the wiping mechanism 985. The servo drive 986 can be actuated in a manner not shown, wirelessly or by wire, by the control device 32.

A further embodiment is illustrated in connection with fig. 12. The cutting tool and/or the coating means can also be held, for example, by a support means 66, at the housing 64, so to speak floating and/or movable relative to the guide means 65, in particular relative to the guide contour 65C.

Thus, instead of the disk-shaped working tool 90, a milling head or a similar other cutting working tool can also be driven, for example, by the drive motor 53. Instead of the connection to the eccentric 57, a tool receptacle 58F can be provided, for example, directly at the drive motor 53, to which a working tool 90F, for example, a milling head, a drilling machine or the like, can be directly fastened. In order to adjust the working tool 90F relative to the carrier 60, a servo drive 954 can be provided, which is already explained and is shown schematically in the figures.

Alternatively or additionally, at least one coating tool 981 can also be arranged at the carrier 60. The coating tool 981, for example one of the coating heads 981A and/or 981B, can be arranged in a stationary manner on the carrier 60 or can be adjusted by means of a servo drive 986 in a movable manner between a position remote from the guide contour 65C or remote from the guide contour 65C, in particular rearward to the guide contour 65C.