阅读说明：本技术 安装工具 (Mounting tool ) 是由 G.巴赫迈尔 P.弗雷泽 M.格利希 W.泽尔斯 M.西里亚克斯 G.埃贝尔斯贝格 R. 于 2018-04-20 设计创作，主要内容包括：本发明涉及一种具有驱动设备的安装工具,所述驱动设备具有：-杆状的挺杆(5),所述挺杆用于压入紧固器件,-管状的旋转体(4),-至少一个弹簧元件(3),-将所述弹簧元件(3)与所述旋转体(4)连接的第一缠绕绳索(1),所述第一缠绕绳索将所述弹簧元件(3)的线性运动转换为所述旋转体(4)的旋转运动(B),和-将所述旋转体(4)与所述挺杆(5)连接的第二缠绕绳索(2),所述第二缠绕绳索将所述旋转体(4)的旋转运动(B)转换为所述挺杆(5)的线性运动(A)。(The invention relates to an installation tool having a drive device, which has: -a rod-shaped tappet (5) for pressing in fastening means, -a tubular rotator (4), -at least one spring element (3), -a first winding cable (1) connecting the spring element (3) with the rotator (4), the first winding cable converting a linear movement of the spring element (3) into a rotational movement (B) of the rotator (4), and-a second winding cable (2) connecting the rotator (4) with the tappet (5), the second winding cable converting a rotational movement (B) of the rotator (4) into a linear movement (a) of the tappet (5).)

1. Installation tool for installing a fastening device, in particular a nail, into a substrate, in particular made of concrete, having a drive device,

The method is characterized in that:

A tappet (5) movable in the longitudinal direction (L), in particular rod-shaped, for pressing in the fastening means,

a rotary body (4) rotatable about an axis of rotation (R),

-at least one spring element (3),

-a first winding rope (1) connecting the spring element (3) with the rotator (4), the first winding rope being arranged and configured for converting a linear movement of the spring element (3) into a rotational movement (B) of the rotator (4), and

-a second winding rope (2) connecting the rotary body (4) with the tappet (5), which is arranged and configured for converting a rotational movement (B) of the rotary body (4) around the rotation axis (R) into a linear movement (a) of the tappet (5) in a longitudinal direction (L).

2. installation tool according to claim 1, characterized in that the axis of rotation (R) is substantially parallel to the longitudinal direction (L).

3. installation tool according to claim 2, characterized in that the tappet (5) is arranged in the rotary body (4).

4. Installation tool according to claim 1, characterized in that the axis of rotation (R) is substantially perpendicular to the longitudinal direction (L).

5. Installation tool according to claim 4, characterized in that the spring element (3) is arranged in the rotary body (4).

6. Installation tool according to one of the preceding claims, characterized in that the spring element (3) is compressible parallel to the axis of rotation (R), in particular coaxially.

7. installation tool according to one of the preceding claims, characterized in that the rotary body (4) is arranged substantially rigidly along the axis of rotation (R).

8. Installation tool according to one of the preceding claims, characterized in that the second winding rope (2) is configured for unwinding or winding the second winding rope (2) on the tappet (5) or on the rotary body (4) by means of a rotational movement (B) of the rotary body (4), whereby a linear movement (a) of the tappet (5) is achieved.

9. Installation tool according to one of the preceding claims, characterized in that the rotator (4) and the spring element (3) are connected by means of the first winding rope (1) in such a way that a spring force acts on the rotator (4) in both directions of rotation (B) of the rotator (4), in particular on the rotator (4) in such a way that a rotational movement of the rotator (4) causes a compression of the spring element (3), whereby the drive device is pretensioned.

10. Installation tool according to one of the preceding claims, characterized in that the rotary body (4) is tubular.

11. installation tool according to one of the preceding claims, characterized in that the spring element (3) has a gas spring (15).

12. Installation tool according to claim 11, characterized in that the gas spring (15) has a base plate (18) and a cover plate (17) oriented parallel thereto, and in particular a metal bellows (16) arranged between the cover plate (17) and the base plate (18), in particular the metal bellows (16) being coated with carbon fiber-reinforced plastic.

13. Installation tool according to claim 11 or 12, characterized in that the drive device has two gas springs (15) arranged one above the other, mirrored, in particular the base plates (18) of the two gas springs (15) are arranged one above the other, and in particular is configured with a compensation bore (19) through the base plate (18) for compensating the gas pressure between the two gas springs (15).

14. The installation tool of any one of the preceding claims, wherein:

-at least one holding film (6) which supports the tappet (5) and is arranged outside the rotational body (4), said holding film being designed to fix the tappet (5) in a laterally and torsionally stable manner.

15. the installation tool of any one of the preceding claims, wherein:

-at least one supporting element (10) arranged outside the rotary body (4), which supporting element is configured for longitudinally and laterally stable supporting of the rotary body (4).

16. the installation tool of any one of the preceding claims, wherein:

-an electric drive unit (7) arranged outside the rotational body (4), the electric drive unit being configured for rotating the rotational body (4), thereby extending or compressing the spring element (3).

17. The installation tool of claim 16, wherein:

-a driver unit (8) arranged between the electric drive unit (7) and the rotary body (4), the driver unit being configured for translating a rotational movement of the electric drive unit (7).

18. The installation tool of claim 17, wherein:

-a coupling unit (9) arranged between the driver unit (8) and the rotary body (4), the coupling unit being configured for activating a linear movement (a) of the tappet (5).

19. Installation tool according to one of the preceding claims, characterized in that the drive device comprises a trigger device (20) for holding the rotary body (4) against the torque exerted by the spring element (3), which has:

A first crown wheel (21) with a first tooth (22), which is connected in a non-positive manner to the rotational body (4),

-a second crown wheel (23) corresponding to the first crown wheel (21), which is movable along the crown wheel axis (K), non-rotatable, relative to the first crown wheel (21), the second tooth (24) of which can be non-positively engaged into the first tooth (22) in such a way that the rotary body (4) is fixed against rotational movement until a maximum torque is reached, and

-unlocking means (25) configured for moving the second crown wheel (23) out of engagement with the first crown wheel (21).

Technical Field

the invention relates to an installation tool for installing a fastening device, in particular a nail, into a substrate, in particular made of concrete.

Background

For mounting fastening means, such as nails or bolts, into a substrate, it has already been disclosed to use mounting tools in which a tappet is pushed forward suddenly or abruptly, wherein the tappet acts on the fastening means and presses or pushes it into the substrate. In order to be able to transmit a sufficient impulse for pressing in the fastening means, the tappet must be accelerated to a high speed on the one hand and must be provided with a large mass or be connected to a large mass on the other hand.

In order to achieve high speeds, different drive types have been disclosed, for example explosive drives in which the propellant is ignited. Likewise, tools are known in which a rotating flywheel mass is connected to a tappet via a coupling, as described, for example, in DE 102009021727 a 1.

in all types of drives, it is necessary to move the tappet back into its initial position again in order to then be able to start a new installation process. This return movement can be effected by means of a spring or, in the case of explosively operated tools, also by deflection of a portion of the drive gas in the drive gas, or, in the case of semi-automatic tools, manually.

the setting tool can also be referred to as a nail gun, a bolt pusher, a bolt setting tool or as a device for pressing in fastening means.

Disclosure of Invention

The object of the invention is to provide a drive solution for a setting tool which works reliably and enables continuous operation with high setting energy.

According to the invention, the proposed object is solved with a setting tool according to claim 1. Advantageous embodiments are given in the dependent claims.

The invention is based on an installation tool having a drive device in which the spring path of a spring element is converted into a rapid linear movement of a tappet via an inserted cable-rotation axis kinematic system. Here, for example, at a conversion ratio of 1:25, an impulse of more than 15Ns can be generated. The conversion is effected by a first and a second winding cable, which are wound and unwound on the rotary body or on the tappet. By means of such a drive device in the installation tool, the fastening means (e.g. a bolt or a nail) can also be pressed or pushed into the hard material (e.g. concrete).

The invention claims an installation tool for installing a fastening device, in particular a nail, into a substrate, in particular made of concrete, having a drive device with:

A tappet which is movable in the longitudinal direction, in particular in the shape of a rod, for pressing in the fastening means,

A rotating body rotatable about an axis of rotation,

-at least one spring element for the purpose of,

-a first winding cord connecting the spring element with the rotator, the first winding cord being arranged and configured for converting a linear movement of the spring element into a rotational movement of the rotator, and

-a second winding rope connecting the rotator with the tappet, the second winding rope being arranged and configured for converting a rotational movement of the rotator around the rotation axis into a linear movement of the tappet in a longitudinal direction.

The present invention provides the following advantages: the fastening device can be mounted safely, quickly and reliably at minimal expenditure.

The tappet can be one-piece or multi-piece. The term "cable" here also includes a single cable, i.e. a single first winding cable or a single second winding cable, even if, in particular, a plurality of cables are preferably provided for the first winding cable in order to transmit high forces symmetrically.

In a preferred first variant, the axis of rotation of the rotary body is substantially parallel to the longitudinal direction in which the tappet is movable. In this variant, the second winding wire is preferably designed to unwind or wind the second winding wire on the tappet by means of a rotational movement of the rotary body, thereby achieving a linear movement of the tappet. Preferably, the tappet is arranged in the rotary body, thereby resulting in a compact construction. "in the rotating body" means here that the tappet, over its entire length, does not have to be arranged within the envelope volume defined by the rotating body, but rather that it is at least partially surrounded by the rotating body.

In a preferred second variant, the axis of rotation of the rotary body is substantially perpendicular to the longitudinal direction in which the tappet is movable. In other words, the rotating body is arranged in such a manner as to be rotatable perpendicularly to the axial direction of the tappet. In this variant, the second winding cable is preferably designed to unwind or wind the second winding cable on the rotor by means of a rotational movement of the rotor, as a result of which a linear movement of the tappet in the axial direction is achieved.

Preferably, in this second variant, the spring element is arranged in the rotary body, thereby resulting in a compact construction. "in the rotational body" means here that the spring element does not have to be arranged over its entire length within the envelope volume defined by the rotational body, but rather that it is at least partially surrounded by the rotational body.

In a development of the first or second variant, the rotary body can have an inner rotor and an outer rotor arranged concentrically thereon in a rotatable manner, wherein the outer rotor can be rotated together with the inner rotor by means of a driving bolt or a driving projection of the inner rotor, which serves as a driving means and is arranged in a manner movable in an elongated hole, groove or recess of the outer rotor. The mentioned driver means can also be arranged in reverse at the inner rotor and the outer rotor.

In a development of the first or second variant, the drive device can have an electric drive unit which is arranged outside the rotary body and which is designed to rotate the rotary body, thereby extending or compressing and thus pretensioning the spring element.

in a development of this second variant, the drive system (antiribendardnung) has at least one pull-back cable which connects the rotary body to the tappet and which pulls the tappet back from the installed state into the starting state, wherein the pull-back cable is wound around the rotary body.

Preferably, the spring element is compressible parallel to the axis of rotation, in particular coaxially. "compressible" here means a compression of the spring element, but here also in particular includes an elongation.

Preferably, the rotary body is arranged substantially rigidly along its axis of rotation, wherein "rigidly" in this case refers to the one-piece or multi-piece housing and/or to the longitudinal axis of the tappet.

in a further embodiment, the rotor and the spring element are connected by means of the first winding cable in such a way that a spring force acts on the rotor in both rotational directions of the rotor, that is to say in particular acts on the rotor in such a way that a rotational movement of the rotor causes a compression of the spring element, thereby pretensioning the drive device.

preferably, the rotating body is tubular. This makes it possible to achieve a compact configuration in which, for example, the tappet or the spring element is arranged in the rotary body. "tubular" here also means annular, that is to say that the development along the axis of rotation is substantially insignificant.

Preferably, the spring element can be a gas spring. This gas spring is robust (robust) and safe in operation.

In one embodiment, the gas spring has a base plate and a cover plate oriented parallel thereto.

In a further embodiment, the gas spring has at least one metal bellows which can be filled with gas and is arranged between the cover plate and the base plate, wherein the metal bellows can be coated, in particular, with a carbon fiber-reinforced plastic.

In a further embodiment, one end of the first winding cable is fastened in the cover plate and the other end is fastened to the rotary body.

In another embodiment, the pressure of the gas in the metal bellows is at least 50 bar in a state where the gas spring is filled with the gas.

In a further embodiment, the system (Anordnung) can have two gas springs arranged on top of one another in a mirror-image manner, wherein in particular the base plates of the two gas springs can be arranged on top of one another.

In a further embodiment, compensation bores can be formed through the base plate for compensating the gas pressure of the two gas springs.

In one embodiment, the drive device can have at least one holding film which supports the tappet and is arranged outside the rotational body, which holding film is designed to fix the tappet in a laterally stable and rotationally fixed manner.

In one embodiment, the drive device can have at least one bearing element, which is arranged outside the rotational body and is designed to support the rotational body in a longitudinally stable and laterally stable manner.

In one embodiment, the drive device can have an electric drive unit which is arranged outside the rotary body and is designed to rotate the rotary body, thereby extending or compressing and thus pre-tensioning the spring element.

In one embodiment, the drive device can have a transmission unit arranged between the electric drive unit and the rotary body, which transmission unit is designed to convert a rotary movement of the electric drive unit.

In one embodiment, the drive device can have a coupling unit arranged between the driver unit and the rotary body, which is designed to activate the linear movement of the tappet.

In order to safely hold the drive device against the torque exerted by the spring element and against undesired triggering, the invention proposes a triggering device having:

A first crown wheel with a first tooth, which is connected with the rotational body in a non-positive manner,

a second crown wheel corresponding to the first crown wheel, which is movable relative to the first crown wheel along the crown wheel axis and is not rotatable, a second tooth of which can be non-positively engaged in the first tooth in such a way that the rotational body is fixed against rotational movement until a maximum torque is reached, and

-unlocking means configured for moving the second crown wheel out of engagement with the first crown wheel.

By definition, the crown gear is a gear whose teeth are arranged on the end face of a cone or a cylinder. The gears are typically used to transmit rotational motion between shafts that are angled relative to each other. The crown gears each have one or more sprocket teeth.

"non-rotatable" means here that the second crown gear is either fixedly connected to the housing or fixedly connected to the drive.

in one embodiment, the tooth flanks of the first and second teeth can be designed in an inclined manner with respect to the crown gear axis. This ensures the required static friction during engagement.

In a further embodiment, the second crown wheel can be formed partially from a ferromagnetic material.

In a further embodiment, the unlocking means can have at least one electromagnet which is designed to release or displace the second crown wheel from engagement with the first crown wheel when an electric current flows through the electromagnet.

Preferably, the mounting tool has a one-piece or multi-piece housing in which the drive device is arranged.

In a further embodiment, the mounting tool has a trigger button which is designed to activate the mounting process by controlling the electric drive unit and/or the coupling unit.

in one embodiment, the mounting tool has a mounting opening in the housing through which the fastening means can be fed out.

in a further embodiment, the mounting tool has a handle section in the housing, which is designed to hold the mounting tool by a user.

Further features and advantages of the invention will be apparent from the following description of two embodiments with reference to the exemplary drawings.

Drawings

The figures show:

FIG. 1: the spatial view of the drive device of the first embodiment in the initial state,

FIG. 2: a spatial view of the drive device in the mounted state,

FIG. 3: a cross-section of the installation tool with the drive device,

FIG. 4: a sectional view of a gas spring as a spring element arranged on a rotary body of the drive device,

FIG. 5: a plan view of the gas spring disposed on the rotating body,

FIG. 6: a top view of the rotating body with the gas spring arranged thereon rotated by 45 degrees,

FIG. 7: a cross-sectional view of two gas springs symmetrically arranged on the rotating body,

FIG. 8: the spatial view of the triggering device of the drive device in the locked position,

FIG. 9: the spatial view of the same trigger device in the trigger position,

FIG. 10: a side view of the driving apparatus of the second embodiment in the initial state,

FIG. 11: a side view of the drive device in the mounted state,

FIG. 12: a sectional view of a drive device with a gas spring as spring element,

FIG. 13: a side view of a two-piece swivel body, an

FIG. 14: cross section of an installation tool with a drive device.

Detailed Description

Detailed description of the first embodiment

fig. 1 and 2 show a spatial view of a driving apparatus in an initial state (fig. 1) and in an installation state (fig. 2), respectively, as part of an installation tool of a first embodiment. The drive device has a one-part or multi-part tappet 5, with one end of which a fastening element, not shown, can be pressed directly or indirectly into a base, also not shown. In order to generate the necessary impulse, a cable-rotating shaft kinematics is used, which consists of a tubular rotating body 4, a second winding cable 2, a spring element 3 and a first winding cable 1.

The tappet 5 is linear, i.e., can be displaced in a translatory manner, wherein it is guided along its longitudinal axis C, i.e., in the longitudinal direction L, but does not rotate here. Above the tappet 5, the tubular rotary body 4 is supported so as to be rotatable concentrically, i.e., the rotary body 4 is rotatable relative to the tappet 5. The rotation axis R is parallel to the longitudinal direction L. For this purpose, the rotary body 4 is hollow and a rod-shaped tappet 5 protrudes through it. The tappet 5 is arranged in the rotary body 4. The rotary body 4 is axially supported (not shown) in such a way that the rotary body 4 rotates as frictionless and with low losses as possible and is rigidly arranged along the axis of rotation R.

The first winding cable 1 connects the spring element 3 to the rotation body 4 such that the spring element 3 is tensioned when the rotation body 4 rotates, wherein the winding cable 1 is wound at least partially around the rotation body 4 or is inclined relative to the rotation body 4. The rotating body 4 is connected to the first winding rope 1 in such a way that the spring force acts on the rotating body 4 in both directions of rotation of the rotating body 4.

The second winding wire 2 connects the rotary body 4 to the tappet 5, wherein the second winding wire 2 winds around the tappet 5 by rotation of the rotary body 4 in the rotational direction B about the rotational axis R and, by the "apparent wire shortening" resulting therefrom, causes a linear movement of the tappet 5 in the direction a, i.e. in the longitudinal direction L.

By rotating the rotary body 4, a rotary shaft is prestressed, which is tensioned or compressed via the first winding cable 1 and thus stores energy, which, when the rotary body 4 is released, is suddenly converted into a rotary motion of the rotary body 4 and thus into a linear motion of the tappet 5.

By selecting the diameters of the rotary body 4 and of the tappet 5, a conversion ratio can be determined which converts the spring path of the spring element 3 into the path of the tappet 5.

Fig. 3 shows a strongly simplified installation tool with a first exemplary embodiment of the drive device according to fig. 1 and 2 in a housing 11. The housing 11 has a front end portion in which a mounting opening 14 for a fastening device to be mounted (e.g., a bolt or a nail) is disposed. The housing 11 has a handle section 12, which a user grips and can hold an installation tool. At the upper end of the handle section 12, a trigger button 13 is arranged, by means of which a user can trigger and thus carry out an installation process. A battery, a battery or a mains adapter can be mounted in the handle section 12 for supplying the installation tool with electrical power.

The drive device has a tappet 5 which carries fastening means, not shown, out through the mounting opening 14. A sudden linear movement of the tappet 5 is achieved by the kinematics illustrated in fig. 1 and 2, wherein the pretensioned spring element 3 converts its energy via the first winding cable 1 into a rotational movement of the tubular rotary body 4 in the rotational direction B, which rotary body 4 in turn converts its rotational movement B via the second winding cable 2 into a linear movement of the tappet 5 in the direction a. This allows a small spring path to be suddenly converted into a large linear movement of the tappet 5. The rotary body 4 is rotatably mounted in the bearing element 10, wherein it cannot be displaced in the longitudinal direction. Thereby, the rotary body 4 is rigidly arranged relative to the housing 11 along the rotation axis R.

The tappet 5 must be reliably supported in a manner that prevents rotation. A torsionally rigid and transversely rigid retaining membrane 6 at the end of the tappet 5 facing away from the mounting opening 14 is used for this purpose, alternatively also at the other end. This ensures that the tappet 5 converts the rotational movement of the rotary body 4 into a linear movement only.

An electric drive unit 7, which rotates the rotary body 4 via a transmission unit 8 and a coupling unit 9 and thereby pretensions the spring element 3, serves to "load" or "tighten" the installation tool. The coupling unit 9 can also hold the rotary body 4 in a tensioned position (page) which is released by the trigger button 13. Alternatively, the electric drive unit 7 can be switched off in the maximally loaded state, thereby triggering the mounting process without triggering a holding of the spring tension during this time.

by means of the chosen transformation ratio and by means of the kinematics of the second winding rope 2, the rotator 4 only needs to be able to perform a rotational movement of about +/-45 degrees in order to mount the fastening means.

a gas spring 15 serves as the spring element 3. Fig. 4 shows a cross section of a gas spring 15, which is composed of two concentrically arranged metal bellows 16, which are closed by a common base plate 18 and cover plate 17 and form a gas-tight container for gas. The container can be filled with gas via a valve, not shown, mounted in the cover plate 17. The effective radii of the two metal bellows 16 are dimensioned in such a way that, for example, a force of approximately 20kN is generated on the base plate or cover plate 17, 18 at a gas pressure of 50 bar.

The rotary body 4 of the rope-and-rotation-shaft kinematic system shown in fig. 1 and 2 extends through the gas spring 15 in a concentric arrangement. One end of the first winding rope 1 transmitting the biasing force to the rope-rotation shaft kinematic system is hung on the cover plate 17 of the gas spring 15, and the other end is hung on the rotating body 4. In the unpressurized state of the gas spring 15, the first winding cable 1 is inserted in such a way that it is straight and slightly pretensioned after being hung. The first winding cable 1, after being suspended in the cover 17 of the gas spring 15 and in the rotating body 4 of the cable-rotating shaft kinematics, is oriented radially when looking down on the cover 17, as shown in fig. 5.

For the description of fig. 5 and 6, it should again be mentioned that the movement of the rotary body 4 in the direction of the longitudinal axis C is blocked by suitable bearings. More precisely, the rotary body 4 can now only rotate about a longitudinal axis C, which is concentric with the axis of rotation R. If the gas spring 15 is filled with gas, a pressure builds up which acts on the cover 17 in the direction of the longitudinal axis C and thus exerts a traction force on the first winding cable 1.

If the rotator 4 is rotated by a predefinable angle from the initial position by corresponding means (not shown), for example a motor, as shown in fig. 6, the gas spring 15 under pressure generates a force acting on the first winding rope 1, which force generates a torque at the suspension point of the first winding rope 1, which torque corresponds to the product of the tangential component of the force transmitted by the first winding rope 1 to the rotator 4 and the radius of the suspension point at the rotator 4. The tappet 5 located inside the rotating body 4 can be moved longitudinally according to fig. 1 and 2 by means of the second winding rope 2.

At a pressure of 50 bar and at a rotation of 45 degrees of the rotator 4 around the longitudinal axis C, the exemplary design provides an initial torque of 300Nm, which acts on the rope-rotation shaft kinematics via the rotator 4. Since the cable length does not change during dynamic operation, the cover 17 is pulled downward in the direction of the base plate 18 (fig. 4) by the rotation and thus compresses the gas spring 15. This results in a slight modulation of the gas pressure due to the oscillating movement of the rotary body 4.

in the arrangement according to fig. 4, as soon as the gas spring 15 is charged to its nominal pressure, a resultant, significant force acts on the bearing for damping the movement of the rotary body 4 in the axial direction. In the example, the nominal pressure is 50 bar, which results in a force of approximately 20kN acting on the bearing (not shown) when the gas spring 15 has a predefined geometry.

such bearings, which are subject to high forces, can be completely avoided when a symmetrical arrangement is achieved, as shown in fig. 7. As can be inferred from the schematic illustration, there are two gas springs 15 whose force directions are opposite when the pressure is applied, and there are two symmetrical arrangements of the first winding cord 1, which are referred to below as "lower winding cord arrangement and upper winding cord arrangement". When the two gas springs 15 are the same size and the gas pressure is the same, the forces exerted by the two gas springs 15 on the respective cover plates 17, which are exerted on the rotating body 4 via the first winding rope 1, are oppositely the same and therefore cancel each other out. Thus, bearings for compensating axial forces are no longer required. In contrast, the torques of the lower and upper winding rope arrangements act in the same direction, i.e. they are superimposed on each other.

In order to create a pressure equalization in the two gas springs 15, a compensation bore 19 can be provided, if appropriate, through which pressure compensation takes place.

The compensation bore 19 can have a choke (not shown) for damping pressure fluctuations between the two gas springs 15.

As shown in fig. 5 and 6, the number of the first winding ropes 1 does not necessarily have to be four. However, for reasons of stability with respect to longitudinal bending of the metal bellows 16, at least three first winding cords 1 should be used per gas spring 15 at an angular spacing of 120 °. Otherwise, it is possible, of course taking into account a meaningful construction, to use an arbitrary number n of ropes, the angular spacing of which is given by the following formula:=360°/n。

in order to suppress longitudinal vibrations or bending vibrations of the metal bellows 16, they can be surrounded by a CFK jacket. The vibration is damped due to the characteristics of the fiber synthetic resin cast. Furthermore, this can constitute a protection against high dynamic loads which occur in the material of the metal bellows 16 when the switching time of the rope-rotation axis kinematics is very short.

The gas spring 15 formed by the metal bellows 16 has significant advantages over other springs. The pressure of the gas in the gas spring 15 formed by the metal bellows 16, the base plate 18 and the cover plate 17 follows a known relationship for an ideal gas:

Where p is pressure and V is volume.

as has been found, for example, from simulation calculations and experiments, the vibration of the metal bellows 16 has a negligible effect on the volume V of the metal bellows 16 of the gas spring 15, and thus has no effect on the pressure acting as a source of the torque acting on the rotating body 4 via the first winding rope 1. Thus, disturbances due to unavoidable resonances are effectively eliminated.

A further advantage results from the concentric arrangement of the gas spring 15 around the rotor 4. This allows a compact design of the central drive unit.

In order to fix the rotary body 4 against the maximum torque exerted by the spring element 3 in the tensioned state against rotation, the triggering device 20 is used as a coupling unit 9 according to fig. 8 and 9.

Fig. 8 and 9 show a spatial view of a triggering device 20 for fixing (fig. 8) against rotation and for triggering (fig. 9) a rotational movement of the rotary body 4. For this purpose, the triggering device 20 has a first crown wheel 21, which is rigidly connected to the rotary body 4 at the end face and whose first teeth 22 are beveled at least on one side, i.e. the tooth flanks are inclined relative to the crown wheel axis R. The crown gear axis K coincides with the rotation axis R of the rotary body 4. The first crown gear 21 can alternatively also be arranged at the location of the side of the rotary body 4.

A second, non-rotatable crown wheel 23, which is arranged in a mirror image, is used to fix the first crown wheel 21, the second tooth 24 of which can mesh with the first tooth 22 in such a way that the first crown wheel 21 is fixed against rotation. By a suitable choice of the inclination of the tooth flanks, it is ensured that a reaction force is exerted by the static friction between the inclined tooth flanks which is sufficiently large to overcome the tangential force component acting via the torque, so that the second crown wheel 23 slips out of engagement involuntarily. Preferably, the crown gears 21, 23 are made of steel.

An unlocking means 25 is used to release the engagement, which unlocking means is preferably configured as an electromagnet, the coils of which exert a force in the direction of the crown wheel axis K and in the direction of the unlocking means 25 when an electric current flows, said force overcoming the static friction or sliding friction pulling the second crown wheel 23 out of engagement with the first crown wheel 21. Thereby, the rotational movement of the first crown gear 21 and, consequently, the rotational movement of the rotary body 4 is released. This release can take place suddenly and in a particularly short time (several milliseconds) when the electromagnet is correspondingly dimensioned and arranged.

The guiding of the second crown wheel 23 back into engagement with the first crown wheel 21 can be achieved by any (not shown) adjusting means.

Detailed description of the second embodiment

Fig. 10 and 11 show side views of a driving apparatus in an initial state (fig. 10) and in an installation state (fig. 11), respectively, as a part of the installation tool of the second embodiment. The same names and reference numerals as in the first embodiment are used in the second embodiment for the corresponding members.

The drive device has a one-piece or multi-piece tappet 5, with one end of which a fastening element, not shown, can be pressed directly or indirectly into a base, also not shown. In order to generate the necessary impulse, a cable-rotator kinematic system is used, which consists of a tubular rotator 4, a second winding cable 2, a spring element 3 and a first winding cable 1.

The tappet 5 is linearly, i.e., translationally displaceable in a linear movement direction a, wherein the tappet 5 is guided in a longitudinal direction L along its longitudinal axis C. Above the tappet 5, the tubular rotary body 4 is mounted so as to be rotatable about a direction of rotation B, wherein a rotational axis R (see also fig. 12) of the rotary body 4 is oriented perpendicular to the linear direction of movement a, i.e. also perpendicular to the longitudinal direction L. The rotor 4 is hollow and is supported (not shown) in such a way that the rotor 4 rotates as frictionless and with low losses as possible.

the first winding cable 1 connects the spring element 3 arranged inside the rotating body 4 to the rotating body 4, so that upon rotation of the rotating body 4, the spring element 3 is tensioned, wherein the first winding cable 1 changes its angle or inclination relative to the rotating body 4.

the second winding rope 2 is wound onto the rotating body 4 by the rotation of the rotating body 4. The second winding rope 2 connects the outer side of the rotating body 4 with the tappet 5, wherein the tappet 5 is moved in the linear movement direction a by the second winding rope 2 by rotation of the rotating body 4 in the rotation direction B. By this "apparent rope shortening", the rotational movement of the rotary body 4 in the rotational direction B causes the tappet 5 to perform an axial movement in the linear movement direction a.

By rotating the rotary body 4, the cable-rotary body kinematics is prestressed, the spring element 3 is tensioned via the first winding cable 1 and energy is stored, which, when the rotary body 4 is "released", is suddenly converted into a rotational movement of the rotary body 4 and thus into a linear movement of the tappet 5.

By selecting the inner diameter of the rotary body 4 and the position of the suspension point of the first and second winding cables 1, 2, a conversion ratio can be determined which converts the spring path of the spring element 3 into the path of the tappet 5. The tappet 5 can be pulled back into its initial state by means of the pull-back cable 26. The pull-back cable 26 is fastened to the outside of the rotary body 4 and with its other end to the tappet 5. The pullback cables 26 are deflected by means of deflection rollers 29 into the axial direction a.

alternatively, the function of the pullback cord 26 can be interchanged with the second winding cord 2. Then, an abrupt movement of the tappet 5 occurs in the opposite direction (to the left in fig. 10), i.e. fig. 10 shows the mounted state.

Fig. 12 shows a sectional view of a drive device with a gas spring 15 as spring element 3. For the sake of clarity, the first and second winding ropes 1, 2 are not shown. Inside the rotator 4 is located a gas spring 15 which can be compressed by means of the first winding rope 1 when the rotator 4 rotates. The first winding rope 1 is connected to an end surface of the gas spring 15 and an inner side of the rotating body 4. The tappet 5 and a deflecting roller 29 for the not shown pull-back cable 26 can be seen. The rotary body 4 is located in the accommodating case 32 together with the gas spring 15.

In terms of construction and mode of action comprising a symmetrical arrangement of two gas springs 15, reference is made to the embodiment of the first embodiment.

When the gas spring 15 is released, the tappet 5 is moved in a translatory manner by rotation of the rotary body 4 by means of the second winding rope 2, as explained in relation to fig. 10 and 11.

Fig. 13 shows a tubular rotor 4 in a two-part embodiment, wherein the inner rotors 27 are mounted concentrically in the outer rotors 28 so as to be rotatable relative to one another. In order to enable the outer rotor 28 to rotate with the inner rotor 27 and vice versa, the oblong holes 30 are designed as a driver in the outer rotor 28 on the housing side. The driver bolt 31 arranged on the inner rotor 27 engages in the slot 30 and can thus "couple" the outer rotor 28 at the stop. Alternatively, for example, instead of the elongated hole 30 on the housing side, a groove can be provided on the end side, into which a driving projection arranged on the inner rotor 27 engages instead of the driving screw 31 (not shown). Conversely, the driver can also be arranged at the inner and outer rotors 27, 28 (not shown).

With such a construction, for example, the outer rotor 28 can be rotated independently of the length of the inner rotor 27 corresponding to the elongated hole 30, due to its inertia, until the driver bolt 31 comes to rest at the other end of the elongated hole 30. Therefore, the momentum of the tappet 5 connected to the outer rotor 28 via the second winding rope 2 can be continuously reduced. When this stop is reached, the outer rotor 28 is braked again by the spring element 3, which is not shown in fig. 13. Thereby, excess energy can be absorbed by the spring element 3, which excess energy is not consumed by the mounting process. This is necessary in particular in the absence of fastening means for the press-in.

Fig. 14 shows a strongly simplified installation tool with a drive device according to fig. 10 to 13 in a housing 11. The housing 11 has a front end portion in which a mounting opening 14 for a fastening device to be mounted, such as a bolt or a nail (not shown), is disposed. The housing 11 has a handle section 12, which a user grips and can hold an installation tool. At the upper end of the handle section 12, a trigger button 13 is arranged, by means of which a user can trigger and thus carry out an installation process. A battery, a battery or a network adapter can be installed in the handle section 12.

The drive device has a tappet 5 which drives out a fastening means, not shown, through a mounting opening 14. A sudden linear movement of the tappet 5 is achieved by the kinematics illustrated in fig. 10 and 13, wherein the pretensioned gas spring 15 converts its energy via the first winding cable 1 into a rotational movement of the rotary body 4 in the direction B, which in turn converts its rotational movement in the direction B via the second winding cable into a linear movement of the tappet 5 in the direction a. This allows a small spring path to be suddenly converted into a large linear movement of the tappet 5. The tappet 5 can be pulled back into its initial position again by means of the pull-back cable 26.

An electric drive unit 7, which rotates the rotary body 4 and thereby pretensions the gas spring 15 by means of the first winding cable 1, serves to "load" or "tighten" the installation tool. The mounting operation is released by the trigger button 13 by switching on the electric drive unit 7, rotating the rotary body 4 and switching off the electric drive unit 7 in the maximum load state. This enables the installation process to be triggered without the spring tension having to be maintained during this time.

Preferably, this is achieved by a coupling element, such as the coupling unit 9 described for the first exemplary embodiment, which, when the loaded state is reached, releases the form-locking or force-locking connection between the rotary body 4 and the drive unit 7. This can be, for example, a toothing which closes the toothing counterpart via a spring and which opens via a shaping element (for example a spring) when a predefinable angle of the rotary body 4 is reached, as has been explained according to the first exemplary embodiment.

By means of the chosen transformation ratio and by means of the kinematics of the first winding rope 1 and of the second winding rope 2, the swivel body 4 only needs to be able to perform a rotational movement of about +/-45 degrees in order to mount the fastening means. In the embodiment with inner and outer rotors 27, 28 (fig. 13), for acceleration, the inner rotor 27 is rotated, for example, only 20 degrees, the remaining 50 degrees of the outer rotor 28 being purely ballistic (long holes 30 |), and at 70 degrees the outer rotor 28 is driven together with the inner rotor 27 into the spring element 3 again and is braked in this way.

although the invention is further shown and described in detail by way of embodiments, the invention is not limited to the examples disclosed, and other variants can be derived therefrom by the person skilled in the art without departing from the scope of protection of the invention.

Reference numerals

1 first winding rope

2 second winding rope

3 spring element

4 rotating body

5 tappet

6 holding film

7 electric drive unit

8-transmission unit

9 coupling unit

10 support element

11 casing

12 handle section

13 trigger button

14 mounting opening

15 gas spring

16 metal corrugated pipe

17 cover plate

18 bottom plate

19 compensating hole

20 triggering device

21 first crown gear

22 first tooth

23 second crown gear

24 second tooth

25 unlocking means

26 pullback rope

27 inner rotor

28 outer rotor

29 turning roll

30 long hole

31 carrying bolt

32 accommodating case

A direction of linear motion

Direction of rotation B

Longitudinal axis of C tappet 5

K crown gear axis

L longitudinal direction

R axis of rotation