阅读说明：本技术 夹紧卡盘 (Clamping chuck ) 是由 E.毛雷尔 于 2019-09-12 设计创作，主要内容包括：本发明涉及一种夹紧卡盘(1),通过所述夹紧卡盘将工件(2)单独地且定心地支撑以用于通过机床加工所述工件,所述夹紧卡盘-带有卡盘体(3),-带有四个可径向运动地支承在所述卡盘体(3)处的夹紧钳(5、6、7、8),所述夹紧钳分别成对地布置在X平面或Y平面中,-并且带有可轴向运动地支承在所述卡盘体(3)中的驱动活塞(9),所述驱动活塞经由在所述驱动活塞(9)和相应的夹紧钳(5、6、7、8)处加工的倾斜面或倾斜齿部(10)与所述四个夹紧钳(5、6、7、8)传动地耦联并且所述四个夹紧钳同步地朝着待夹住的工件(2)的方向进给或远离所述工件地运动。(The invention relates to a clamping chuck (1) by means of which a workpiece (2) is individually and centrally supported for machining the workpiece by means of a machine tool, the clamping chuck comprises a chuck body (3), four clamping jaws (5, 6, 7, 8) which are radially movably mounted on the chuck body (3), said clamping jaws being arranged in pairs in the X-plane or Y-plane, respectively, and having drive pistons (9) axially movably supported in the chuck body (3), the drive piston is coupled in a driving manner to the four clamping jaws (5, 6, 7, 8) via inclined faces or inclined teeth (10) which are machined on the drive piston (9) and the respective clamping jaws (5, 6, 7, 8), and the four clamping jaws are synchronously moved in the direction of the workpiece (2) to be clamped or away from the workpiece.)

1. A clamping chuck (1) by means of which a workpiece (2) is individually and centrally supported for machining the workpiece by means of a machine tool,

-with a chuck body (3),

-with four clamping jaws (5, 6, 7, 8) which are radially movably supported at the chuck body (3) and which are arranged in pairs in the X or Y plane, respectively,

and with a drive piston (9) which is mounted in the chuck body (3) so as to be axially movable and which is coupled in a driving manner to the four clamping jaws (5, 6, 7, 8) via inclined faces or inclined teeth (10) which are machined at the drive piston (9) and the respective clamping jaws (5, 6, 7, 8) and which synchronously feeds in the direction of the workpiece (2) to be clamped or moves away from the workpiece to be clamped,

it is characterized in that the preparation method is characterized in that,

-between the drive piston (9) and the respective two adjacent clamping jaws (5, 7 or 6, 8) there is provided a rocker (11),

the rocker (11) has a center of symmetry (12) into which a pin (13) mounted so as to be pivotable on the drive piston (9) is inserted, the rocker (11) being pivotable about the pin as a function of the contact of the clamping jaws (5, 6 or 7, 8) on the workpiece (2),

-and laterally adjacent to the pin (13) there is provided a transfer pin (14, 15) which is drivingly coupled to the rocker (11), the respective clamping jaw (5, 6, 7 or 8) being supported and supported at the end of the transfer pin opposite the rocker (11).

2. The clamping chuck as set forth in claim 1,

it is characterized in that the preparation method is characterized in that,

the tilting of the rocker (11) results in a feed compensation for one of the two pairs of clamping jaws (5, 6 or 7, 8), which move in a common X or Y plane.

3. The clamping chuck according to claim 1 or 2,

it is characterized in that the preparation method is characterized in that,

two guide grooves (16) are incorporated in the rocker (11), into which a respective one of the transfer pins (14 or 15) is inserted with a slight linear movement, preferably perpendicular to the longitudinal axis (4) of the chuck body (3).

4. The clamping chuck as set forth in claim 3,

it is characterized in that the preparation method is characterized in that,

a head (17) is formed on each transmission pin (14, 15), said head engaging in one of the guide grooves (16) of the rocker (11), and the outer edge of the head (17) extending perpendicular to the advancing movement of the rocker (11) or the drive piston (9) is dimensioned to be smaller than the length of the guide groove (16).

5. The clamping chuck according to claim 3 or 4,

it is characterized in that the preparation method is characterized in that,

the head (17) bears against two opposite inner walls (18) of the guide groove (16) with respect to the feed direction of the rocker (11) and can be acted upon by a feed force.

6. The clamping chuck according to one of the preceding claims,

it is characterized in that the preparation method is characterized in that,

a centrifugal force weight (19) is arranged in the chuck body (3), said centrifugal force weight being displaceably mounted in the chuck body (3) perpendicularly to the feed direction of the drive piston (9), said centrifugal force weight (19) being drivingly coupled to one of the clamping jaws (5, 6, 7 or 8) via a lever (20).

7. The clamping chuck as set forth in claim 6,

it is characterized in that the preparation method is characterized in that,

the lever (20) is tilted in the direction of the longitudinal axis (4) of the chuck body (3) during the clamping state of the clamping jaws (5, 6, 7, 8), and the centrifugal force weight (19) is pressed radially outward by the rotation of the clamping chuck (1) in such a way that a radially acting clamping force is transmitted by the centrifugal force weight (19) via the lever (20) to the respective clamping jaw (5, 6, 7, 8).

8. The clamping chuck according to one of the preceding claims,

it is characterized in that the preparation method is characterized in that,

the distance between the two transfer pins (14, 15) and a pin (13) arranged in the center of symmetry (12) of the rocker (11) is dimensioned to be the same.

9. The clamping chuck according to one of the preceding claims,

it is characterized in that the preparation method is characterized in that,

two transmission pins (14, 15) which are fixed to an arm lever (11) extend in parallel and are mounted displaceably in the drive piston (9).

10. The clamping chuck according to one of the preceding claims,

it is characterized in that the preparation method is characterized in that,

the outer contour of the workpiece (2) to be clamped has an arbitrary shape, and the clamping jaws (5, 6, 7, 8) are adapted to the existing outer contour of the workpiece (2) and partially surround said outer contour.

Technical Field

The invention relates to a clamping chuck, by means of which a workpiece is individually and centrally supported for machining the workpiece by means of a machine tool, according to the preamble of patent claim 1.

Background

Clamping devices of this type (which are known in the generic term as clamping chucks) are known, for example, from DE 102015204502B 4. Between the basic pliers and the mechanically actuable drive unit, equal-armed levers and drivers are provided, which are each in driving connection with one of the equal-armed levers. Furthermore, a coupling ring is arranged centrally in the clamping chuck, on which four drivers are arranged in such a way that a movement gap exists between the structural parts in the radial direction. The coupling ring is mounted rotatably about a clamping axis in a chuck body or a housing of the clamping chuck. In this case, a radial feed movement of the basic gripper is generated by the rotation of the coupling ring, so that the workpiece is held by the four clamping grippers, since they are moved in the direction of the workpiece and generate a clamping force.

The clamping jaws of a pair of clamping jaws, which are arranged in a row, are moved relative to each other in such a way that they are moved relative to each other in the direction of the workpiece, and the workpiece is clamped in the clamping jaws of a pair of clamping jaws, wherein the clamping jaws are arranged in such a way that they are arranged in a plane parallel to the plane of the workpiece, and wherein the clamping jaws are arranged in a plane parallel to the plane of the workpiece.

However, due to the play required between the coupling ring and the driver (which is mechanically coupled to the basic or clamping jaw), considerable inaccuracies often occur, so that the positioning of the workpiece is incorrect. This in turn leads to machining errors at the workpiece itself, since the repeated accuracy of the clamping of a large number of identical workpieces cannot be ensured.

However, such movement possibilities are disadvantageously associated with frequently significant tolerance deviations in the clamping action, so that the required clamping force cannot be accurately predicted or predetermined.

That is to say that the movement play which exists between the structural components arranged in the force flow results in a relative movement between these structural components.

Disclosure of Invention

The object of the present invention is therefore to further develop a clamping chuck of the type mentioned at the outset in such a way that, with a high degree of repeatability for the subsequent clamping operation, a positionally accurate, i.e., centered, orientation can be achieved for a large number of differently designed workpieces.

This object is achieved according to the invention by the features of the characterizing part of patent claim 1.

Further advantageous developments of the invention emerge from the dependent claims.

By providing an isopar lever between the drive piston and the respectively two adjacent clamping jaws, which isopar lever has a center of symmetry into which a pin supported on the drive piston is inserted, which isopar lever is pivotably supported about the pin as a function of the contact of the clamping jaws on the workpiece, and laterally adjacent to the pin a transmission pin is provided, on the opposite end of which the respective clamping jaw is supported and supported, it is achieved that the distance of the two adjacent clamping jaws with respect to the distance to the workpiece is balanced, without movement gaps or other uncontrollable deviations occurring in the force flow, as a result of which an exact orientation of the respectively workpiece to be clamped can be ensured.

Since the rocker is inserted between the drive piston and the respective clamping jaw to be moved, i.e. in the force flow, and transmits the relative movement of the drive piston directly via the transmission pin to the clamping jaw, a play-free and balanced clamping of the workpiece is achieved. In this case, pairs of diametrically opposed clamping jaws are assigned to a uniform length of the workpiece, so that in the case of a rectangular workpiece, a pair of the clamping jaws as a first one collides with the workpiece. The further advance movement of the clamping jaws is interrupted, more precisely until the pair of clamping jaws arranged perpendicularly thereto comes into abutment against the workpiece. In this case, the drive piston executes an axial movement, so that the rocker and the transmission pin also move parallel to the longitudinal axis of the chuck body. In this case, the axial feed movement of the drive piston is converted into a radial feed movement for the clamping jaws on the basis of the inclined toothing, the drive piston and the clamping jaws present.

It is particularly advantageous if a centrifugal force weight is arranged in the chuck body, which centrifugal force weight is mechanically coupled to the respective one of the clamping jaws via a lever. The lever is supported in the chuck body and, by virtue of the orientation of the lever, generates a centripetal force acting on the centrifugal weight during rotation of the chuck body, by means of which the centrifugal weight is pressed outward. As a result, the lever is moved in the direction of the longitudinal axis of the chuck body and generates a radial additional clamping force on the respective clamping jaw. The provided shape of the rocker and the transmission pin does not prevent this additional increase in the clamping force, since the force flow exerted by the drive piston acts directly on the clamping jaws and the centrifugal force weight generates an independent clamping force component on account of the rotation of the chuck body.

In order to allow the movement of the rocker to reach the respective transmission pins without tilting (verkannte) or jamming (Festsetzen), guide grooves are introduced into the rocker, into which guide grooves one of the transmission pins is movably inserted. The head molded on the respective transmission pin has no play with respect to the longitudinal axis with respect to the width of the guide groove, so that the two side walls of the head rest against the inner walls of the guide groove, as a result of which a play-free force transmission in the direction of movement between the rocker and the head of the transmission pin is achieved. When the isochoric lever is deflected to one side, the head linearly moves in the guide groove because the length of the head is determined to be smaller than that of the guide groove; at the same time, however, a force transmission in the direction of movement is possible, since the deflection of the rocker takes place in a very small measured angular range.

The suspension of the rocker in its center of symmetry at the drive piston takes place, and the distance of the guide groove from this center of symmetry is dimensioned to be the same, so that the deflection of the rocker at all four rockers is identical and is assigned in each case to the clamping jaw as the first one to be brought into contact with the workpiece to be clamped.

Drawings

The clamping chuck according to the invention is shown in the drawing, which is explained in more detail below. In detail:

fig. 1 shows a plan view of a clamping chuck with a chuck body, in which four clamping jaws oriented perpendicularly to one another are mounted so as to be radially displaceable, by means of which an at least partially rectangularly designed workpiece is held in a centered manner in a space,

fig. 2 shows the clamping chuck according to fig. 1 in a perspective view, partially cut away and with four centrifugal weights assigned to the respective clamping jaws, which are mechanically coupled thereto via levers,

FIG. 3 shows the drive piston of the clamping chuck according to FIG. 1, with the clamping jaws removed and the inclined faces required at the clamping jaws for the radial feed of the clamping jaws, and with four rocker levers arranged on the outside of the drive piston, which are drivingly coupled to one of the clamping jaws via a respective transfer pin,

figure 4a shows the drive piston of the clamping chuck according to figure 3 in an initial state and in cross section,

figure 4b shows the drive piston of the clamping chuck according to figure 4a in a deflected position of the rocker,

figure 5a shows the clamping chuck according to figure 1 in an initial state and partially cut away,

fig. 5b shows the clamping chuck according to fig. 1 in a position in which two diametrically opposed clamping jaws rest against the workpiece and a clamping jaw extending perpendicularly thereto is spaced apart from the workpiece, and

fig. 5c shows the clamping chuck according to fig. 5a with a workpiece clamped in a centered manner.

Detailed Description

Fig. 1 shows a clamping chuck 1, by means of which a partially rectangular workpiece 2 is supported in a centered manner in space for machining by a machine tool, not shown. The clamping chuck 1 is formed by a chuck body 3, on which four clamping jaws 5, 6, 7 and 8 are mounted so as to be displaceable.

The clamping jaws 5 and 6 are arranged in an X-plane, i.e. completely opposite each other, and the clamping jaws 7 and 8 are arranged in a Y-plane extending perpendicularly to the X-plane. The four clamping jaws 5, 6, 7 and 8 are advanced radially in the direction of the center of the chuck body 3, i.e. in the direction of the longitudinal axis 4 of the chuck body, and in the direction of the workpiece 2 (zugestellt). However, if the workpiece 2 to be clamped has a trapezoidal or star-shaped outer contour, the clamping jaws 5, 6, 7, 8 can be arranged in any desired position, so that although one of the x or y planes extends through two of the four clamping jaws 5, 6 or 7, 8, these planes are not oriented perpendicular to one another.

When the workpiece 2 has different edge lengths or other different outer contours (this is schematically indicated by Δ S1 and Δ S2), pairs of clamping jaws 5, 6 or 7, 8 collide with the surface of the workpiece 2 at different time intervals. That is, if the distance Δ S1 is dimensioned between the clamping jaws 5, 6 or 7, 8 to be greater than the distance Δ S2, temporally different points in time of collision (auftrefffzeitpunkt) result. However, the four clamping jaws 5, 6, 7 and 8 are moved synchronously by means of the drive piston 9, so that the spatial or temporal offset is compensated.

Furthermore, it is problematic to position the workpiece 2 in exact alignment relative to the longitudinal axis 4 manually or mechanically. Therefore, the centers of symmetry of the workpieces 2 are often not aligned with respect to the longitudinal axis 4 of the chuck body 3. By the advance of the clamping jaws 5, 6, 7 and 8, the problem should be eliminated not only in the X plane but also in the Y plane, in that the existing distance difference (distanzterschiede) is compensated for by displacing the workpiece 2. This is achieved in that the clamping jaws 5, 6 or 7, 8, which are arranged diametrically opposite one another, displace the workpiece 2 in the X-plane and/or Y-plane in order to orient the center of symmetry of the workpiece 2 in alignment with respect to the longitudinal axis 4 of the chuck body 3. As soon as the workpiece 2 is clamped between two opposing clamping jaws 5, 6 or 7, 8, the workpiece is positioned in the respective X-plane or Y-plane.

However, if the clamping jaws 5, 6, 7 and 8 are moved synchronously by the drive piston 9, the time difference between the clamping jaws 5, 6, 7 and 8 and the workpiece 2 is compensated for. The time or geometry balance can be gathered in detail from fig. 2 to 5 c.

As can be seen from fig. 2, the drive piston 9 has an inclined toothing 10 which interacts with the inclined toothing 10 machined (angelbeitenen) at the clamping jaws 5, 6, 7 and 8. I.e. when the drive piston 9 is moved away from the workpiece 2 to be clamped and the drive piston 9 is pressed between the clamping jaws 5, 6, 7 and 8 against the oblique toothing 10 of the clamping jaws, respectively, the force transmission displaces the clamping jaws 5, 6, 7, 8 radially in the direction of the longitudinal axis 4, i.e. in the direction of the workpiece 2.

Furthermore, a centrifugal weight 19 is displaceably mounted in the chuck body 3, which is in each case drivingly (trieblich) coupled to one of the clamping jaws 5, 6, 7 or 8 via a lever 20. The lever 20 is swingably supported in the chuck body 3. The initial position of the clamping chuck 1 depicted in fig. 2 shows that the centrifugal force weight 19 is arranged closer to the longitudinal axis 4 and thus the lever 20 extends obliquely outward in relation to the direction of the workpiece 2 to be clamped. However, once chuck body 3 is set in rotation, centrifugal force weights 19 are pressed outward due to the centripetal force acting thereon, so that the distance between centrifugal force weights 19 and longitudinal axis 4 increases. As a result, the free end of the lever 20 assigned to the centrifugal weight 19 is also moved away from the longitudinal axis 4, and the free end of the lever 20 assigned to the respective clamping jaw 5, 6, 7 or 8 is moved in the direction of the longitudinal axis 4, as a result of which an additional clamping force is generated in order to fix the workpiece 2.

As can be seen from fig. 3, four free spaces 23 are contained in the drive piston 9, into which four equi-armed levers 11 are inserted or arranged, which have a center of symmetry 12. In the center of symmetry 12, a receiving opening is contained, into which the pin 13 engages. In this case, the pin 13 is supported on the drive piston 9. Furthermore, the rocker 11 is mounted so as to be pivotable on the pin 13.

Laterally next to the pin 13, two guide grooves 16 are incorporated into the rocker 11, which are oriented perpendicular to the longitudinal axis 4 in the state in which the rocker 11 is not actuated. This means that the rocker 11 is not deflected in the non-actuated state, but rather extends perpendicularly to the longitudinal axis 4.

Fig. 4a and 4b show the actuation of the rocker 11 and the transmission of force between the rocker and the respective clamping jaw 5, 6, 7 or 8. That is to say the first and second transmission pins 14 or 15 are inserted into the respective guide grooves 16. In this case, the first transmission pin 14 is assigned to the clamping jaws 5 and 6 and the second transmission pin 15 is assigned to the clamping jaws 7 and 8 and is in each case coupled in a driving manner thereto.

In addition, a head 17 is provided at the free ends of the transmission pins 14 and 15 assigned to the rocker 11, which head is inserted in a linearly displaceable manner into the respective guide groove 16, wherein the outer contour of the head 17 is adapted to the inner contour of the guide groove 16 in such a way that the end face extending in the direction of the longitudinal axis 4 comes into contact with the inner wall of the guide groove 16 and a free space or gap exists between the end faces of the head 17 extending perpendicularly to the longitudinal axis 4, whereby the head 17 can be moved perpendicularly to the longitudinal axis 4 relative to the guide groove 16 when the rocker 11 is moved about the pin 13 into one of two possible deflections, as shown in fig. 4b, i.e. the clamping jaw 7 as the first comes into contact with the workpiece 2, so that the clamping jaw 5 is moved further in the direction of the workpiece 2, whereby the rocker 11 is balanced by the shown deflection α in the two pairs of clamping jaws 7 and 8 on the one hand and the clamping jaws 5 and 6 on the other hand, and the difference between the two pairs of clamping jaws can be kept away from the workpiece by the pivoting movement Δ S32, so that the clamping jaw 11 can be kept in the position of the pivoting Δ S32, so that the clamping jaw 3 can be kept away from the workpiece by the clamping jaw.

In addition, transmission wedges 22 are arranged in each of the four free spaces 23 as distance bridges between the rocker 11 and the respective clamping jaw 5, 6, 7 or 8. A through-opening 24 is contained in the respective transmission wedge 22, through which the respective transmission pin 14, 15 passes or through which it protrudes.

The transmission wedge 22 serves as a buffer or force transmission between the rocker 11 and the clamping jaws 5, 6, 7 or 8 and is mounted so as to be linearly movable in a displaceable manner in the chuck body 3.

This movement is illustrated in detail in fig. 5a, 5b and 5c with regard to different operating or clamping states of the clamping chuck 1. As can be seen from fig. 5a, the clamping jaws 5, 6, 7 and 8 are spaced differently far from the workpiece to be clamped. The initial position of the clamping chuck 1 is therefore referred to here. As soon as the actuating force acts on the drive piston 9, this force is transmitted via the pin 13 to the rocker 11 and via the two transmission pins 14 and 15 to the respective clamping jaw 5, 6, 7 or 8. The linear return movement of the drive piston 9 is converted by the presence of the angled toothing 10 into a radial feed movement of the clamping jaws 5, 6, 7 and 8, so that the clamping jaws can be moved toward the workpiece 2 to be clamped.

Fig. 5b shows that the diametrically opposite clamping jaws 7 and 8 first collide with the workpiece 2 and are thus oriented in the Y-plane relative to the longitudinal axis 4. The rocker 11 is not yet actuated in this position of the clamping jaws 5 and 6.

Fig. 5c shows how the difference between the clamping jaws 5 and 6 relative to the workpiece 2 is bridged or compensated by the deflection α of the rocker 11, the drive piston 9 is moved further in the actuating direction, and the clamping jaws 7 and 8 are held in their position according to fig. 5b by pivoting the rocker 11 and only the clamping jaws 5 and 6 arranged perpendicularly thereto are advanced further until they come into contact with the workpiece 2.

As soon as all four clamping jaws 5, 6 or 7 and 8 have reached their contact position on the workpiece 2, the drive piston 9 generates a real clamping force. The more the drive piston is driven, the higher the clamping force that is generated. The different arrangement of the rocker 11 and the transfer pins 14, 15 is thus not changed, so that it remains in the occupied equilibrium position.

Thus, with the clamping chuck 1 according to the invention, a workpiece 2 can be held in space in a centered manner and supported for machining by a machine tool, which workpiece has an arbitrary outer contour, since the inner contour of the clamping jaws 5, 6, 7, 8 is adapted to the outer contour of a differently designed workpiece 2 and can partially surround the workpiece.