JPH0215322B2 - - Google Patents

Description

DETAILED DESCRIPTION OF THE INVENTION [Industrial Application Field] The present invention provides a chuck body, a clamping pawl that is movable in a radial direction with respect to the chuck body, and an actuating member that is movable in an axial direction with respect to the chuck body. and a motion converting mechanism for causing a radial adjustment movement of a clamp pawl in response to an axial adjustment movement of said actuating member.

[Conventional technology]

A chuck or jog chuck of this type is described in German Patent Application No. 2903904. In this known chuck, the actuating member is a piston which is axially movable within the chuck body and which actuates the clamping pawl via a wedge-shaped hook device.

This and other chucks have wedge-shaped hooks, wedge-shaped bars or chevron-shaped drive members, as conventionally used for gripping workpieces during lathe machining. In this and other chucks, the radially movable clamping pawl is guided in a retaining groove in the chuck body. For these chucks, the point at which the clamping pawl engages the workpiece to be gripped during operation is the front face of the wedge-shaped connecting member between the clamping pawl and the actuating member, when viewed in the axial direction. It is located in That is, during gripping, a torque will act on the holding groove, the magnitude of which depends on the one hand on the gripping force and on the other hand on the distance between the gripping point and the wedge-shaped connecting member. do.

[Problem that the invention seeks to solve]

This torque increases the frictional forces within each retaining groove, and these forces significantly reduce the gripping forces acting on the workpiece, especially as a function of the lubrication conditions and the wear conditions of the chuck elements. The centrifugal force of the jaw, which increases significantly at higher torques, also acts to reduce the gripping force, and can only be reduced by reducing the mass or size of the jaw. A further drawback of known gripping devices is the play present in the jaw guideways, which play tends to reduce the machining precision achieved when using these chucks.

[Purpose of the invention]

In view of the above-mentioned problems of the prior art, an object of the present invention is to improve the chuck of the type described above to avoid the clamping pawl from tilting or seizing with respect to the chuck body, and to significantly increase the accuracy. be. At the same time, another object of the invention is to provide a chuck that is simple and inexpensive to manufacture, by omitting guide surfaces cooperating with the clamping pawls.

[Means for solving problems]

The present invention achieves the above object by providing a chuck body, a clamping pawl movable in a radial direction with respect to the chuck body, an actuating member movable in an axial direction with respect to the chuck body, and an axis of the actuating member. In a chuck comprising a motion converting mechanism for causing a radial adjustment movement of a clamp pawl in response to a directional adjustment movement, each clamp pawl is connected to the chuck body via a pair of arms extending generally in the axial direction. The connection point between the pair of arms and the clamp pawl and the connection point between the pair of arms and the chuck body are respectively located at vertices of a parallelogram, and the pair of arms are substantially radially aligned. can be elastically biased,
The motion converting mechanism has a two-arm lever pivotally mounted on the chuck body corresponding to each clamping pawl, the outer arm of the lever being operatively connected to the corresponding clamping pawl, and the inner arm of the lever being operatively connected to the corresponding clamping pawl. This is accomplished by a chuck operatively connected to the actuating member so that the lever can be pivoted about its pivot in response to axial movement of the actuating member.

[Effect]

According to the chuck of the present invention, the connecting point between the pair of arms and the clamp pawl and the connecting point between the pair of arms and the chuck body are located at the vertices of the parallelogram, and the connecting point between the pair of arms, the clamp pawl and the chuck A parallelogram link mechanism is formed by the main body. The pair of arms is substantially elastically biasable in a radial direction.

This structure allows the plurality of clamping pawls to perform the desired radial movement while always remaining parallel to each other, ie, parallel to a plane perpendicular to the axis of the chuck body.
Therefore, the clamp pawl is prevented from tilting or seizing against the chuck body, and its accuracy is significantly improved.

Additionally, the deflectable arm of the present invention has adequate torsional stiffness and can be easily designed to resist clamping pawl tilting and seizure. That is, the clamping pawl no longer needs to be guided between the guide surfaces, and therefore the inconveniences previously caused by cooperation between the clamping pawl and its guide surface do not occur at all, and the chuck of the invention is easy and inexpensive to manufacture.

Furthermore, by suitably selecting the transmission ratio of the lever according to the invention, large gripping forces can be generated on the clamping pawl even when the actuating member has a relatively small axial force. These gripping forces are no longer influenced by indeterminate frictional forces.

The motion conversion mechanism of the invention is also preferably configured as a wedge mechanism and can also be of self-centering design, in particular with the actuating member movable in an axially extending piston bore in the chuck body. When configured as a chuck piston, a very high precision can be achieved when aligning the workpiece gripped in this way.

During the development of the invention, it has been found to be advantageous for the arm to be configured as a flat, leaf-spring type arm that is very stiff in the direction transverse to the direction of radial deformation. .

In a particularly preferred embodiment of the invention, the arm is integrally formed with the clamping pawl and the chuck body. During manufacture, an integral projection is formed on the free end surface of the chuck body in a manner similar to the projection of a dog-mesh or jaw-joint joint. Each of these projections is then provided with a groove which separates the clamping pawl from the chuck body and away from the arm and forms the inner surface of the two arms carrying the corresponding clamping pawl. The grooves are preferably formed in the integrated structure consisting of the clamp pawl, the arm and the chuck body using a wire-cut electrical discharge machine. First, a substantially cord-shaped and extending hole is formed in the protrusion, and then a wire is passed through the hole and a groove shape is machined by the wire. This structure provides significant cost and productivity benefits. In particular, the high precision of the wire-cut electrical discharge machine allows the thickness of the leaf-spring arm to be maintained to close tolerances. The blocks which remain between the arms at the same time form a stop piece which prevents a radial deformation of the arms which would lead to permanent deformation.

When the clamp pawl, arm and chuck body are integrally formed, it has been found effective to fill the groove with a rubber elastic filler after completion. Filling with this filler prevents the groove from clogging, and in particular prevents shavings from drilling or turning from entering the groove and obstructing the free movement of the arm relative to other blocks. . It is not necessary to completely fill the grooves, it is sufficient to fill at least the inlet ends of these grooves. Alternatively, the free end of the groove may be closed by a lateral lid member.

Furthermore, it is also preferable that the connections between each lever of the wedge surface mechanism and the chuck body and the connection between each lever and the corresponding clamp pawl be ball joint connections to prevent the clamp pawl from tilting to a critical state or from seizing. It has been discovered.

It has also been found that a compression spring is preferably provided which exerts an inward spring force on the relatively long arm of the lever remote from the clamping pawl. When the actuating member is retracted,
These compression springs push the clamping pawls further outwards beyond their neutral position, thus doubling the effective radial path of the clamping pawls when the arms are fully radially deformed.

It has also been found advantageous to configure the actuating element of the actuating member as a roller which is rotatably mounted relative to the actuating member. These rollers cooperate with the wedge surface of the lever, eliminating interference due to frictional forces.

In carrying out the invention, it is particularly preferred that the axial cross-sectional shape of the arm is selected to provide a constant bending stress along the arm. In a preferred embodiment of the invention, the groove portions defining the arms are curved, not strictly axially, but radially inwardly or outwardly.
A constant bending stress along the arm is achieved.

In addition, it has also been found that it is preferable to bend the substantially radially extending groove portions along the underside of the corresponding clamping pawl forwardly or slightly outwardly towards the clamping pawl. With this construction, the pivot axis of the lever is particularly close to the clamping pawl, so that the front or outer arm of the lever is very short and the transmission ratio achieved by the lever is particularly high.

In carrying out the invention, it has been found to be advantageous if the central end face area of the chuck body located between the radially inner ends of the clamping pawl or the inner arm is configured as a planar stop. There is. This stop provides axial positioning of the gripped workpiece or tool. By superimposing the radial deformation of the clamping pawl, a weak axial element is effectively used to press the workpiece against the surface of the chuck body, which acts as a stop during gripping.

Depending on the design of the motion conversion mechanism, the clamping pawls can be used to grip radially inwardly or radially outwardly or both radially inwardly and radially outwardly. The workpiece is thus gripped either at the outer diameter or at the inner diameter. In embodiments with an inclined wedge surface on the inner arm of the two-arm lever, the wedge surface faces the axis of rotation of the chuck or is turned outward, e.g. Depending on whether it is surrounded by elements, it can only be gripped radially inwards or radially outwards. As an alternative to the embodiment with an inclined wedge surface, it has an angle-shaped lever pivoted relative to the chuck body, operatively connected on the one hand to an axially movable actuating member and on the other hand to a two-armed lever. An embodiment equipped with a motion conversion mechanism is recommended. The simplest way to connect an actuating member or a two-arm lever to an angle-shaped lever so as to be effective in both directions is to engage the angle-shaped lever into a peripheral recess, particularly a peripheral groove, formed in the actuating member, thereby connecting the chuck body and the two-arm lever. It is to support both sides.

In the case of chucks with radially movable clamping pawls, the gripping force depends on the mass of the clamping pawls and the rotational speed of the chuck. If the chuck is gripped radially inwards, the gripping force applied, for example by hydraulic pressure, decreases as the rotational speed of the chuck increases. The gripping force reaches a point where it is no longer adequate. During radially inward gripping, the effective gripping force is increased by the centrifugal force acting on the clamping pawls.
Chucks with devices for compensating centrifugal forces are already known. These chucks, however, are not only relatively complex in construction, but also have different clamping jaws, in which case the clamping jaws, sometimes also called attachment jaws, are replaceable in actual use. It has become impossible to take into account the difference in mass. In this case, centrifugal force compensation is inadequate for at least some clamping pawls.

This drawback consists of a chuck body and a clamping pawl movable radially relative to the chuck body, with a bouncing weight attached to each clamping pawl movable radially relative to the chuck body; A two-armed lever pivoted to the opposite end and having a variable lever arm length ratio operatively connects the weight to the clamping pawl such that inward radial movement of the clamping pawl causes an outward movement of the springing weight. This is avoided by the chuck of the invention which accommodates radial movements. If the two-arm lever extends approximately parallel to the axis of rotation of the chuck, the product of the mass of the bouncing weight x the length of its corresponding lever arm is the mass of the clamping pawl x the length of its corresponding lever arm. Set approximately equal to the product of length to compensate for centrifugal force. This causes the bouncing weight to exert a radially inward force on the clamping pawl, which force is at least as great as the centrifugal force acting on the clamping pawl. In the configuration of the present invention, the length ratio of the two arms of the two-arm lever may be changed depending on the size of the clamp pawl. In this way, the centrifugal force compensation can be adjusted to suit the mass of the clamping pawl that can be attached to the chuck. In addition, centrifugal force compensation can be achieved at low manufacturing costs.

The two-arm lever can also have a nested structure. However, in a preferred embodiment of the invention, the position at which the two-arm lever tilts may be easily movable relative to the lever. this is,
In terms of construction, this is achieved in particular by providing the chuck body with a longitudinally adjustable pivot bearing of the two-armed lever to enable longitudinal movement of the lever. This pivot bearing can be shaped like a hemispherical ring, for example, attached to a bolt-like two-arm lever by screws or the like. Preferably, however, the pivot bearing is configured as a nut screwed onto the external thread of the two-arm lever.

〔Example〕

Hereinafter, the details and effects of the present invention will be explained in more detail with reference to the accompanying drawings.

1 and 2 show in detail the cylindrical chuck body 10 which is rotatably attached to the free end of a spindle 14 by a machine screw 12. The chuck body 10 is provided with an integrally formed projection 16 at its free end, which projection 16 is provided with a groove 18 which is C-shaped or U-shaped in the sectional view shown in FIG. (In addition,
In the following description, it will simply be referred to as chuck body 10. ), are separated into two arms 22 and another block 24, which is considered part of the chuck body 10 in the following description. Each groove 18 consists of two axially extending groove portions 18a and a substantially radially extending groove portion 18b connecting said groove portions 18a.

As seen in FIG. 1, the connection point between the pair of arms 22 and the clamp pawl 20 (the left end of the arm 22 in FIG. 1) and the connection point between the pair of arms 22 and the chuck body 10 (the arm 2
2) are located at the vertices of the parallelogram. As a result, a parallelogram link mechanism is formed by the pair of arms 22, the clamp claws 20, and the chuck body 10. The pair of arms 22 extending in the axial direction are substantially elastically biasable in the radial direction.
That is, the pair of arms 22 hold the clamp pawl 20 at the tip of the chuck body 10 like a parallelogram link mechanism.

With this structure, the plurality of clamp claws 20 are
The desired radial movement can be carried out while always remaining parallel to each other, ie parallel to a plane perpendicular to the axis of the chuck body 10. Therefore, the clamp pawl 20 is attached to the chuck body 1.
Tilting and sticking with respect to 0 are avoided, and the accuracy is significantly improved. The width of the arms 22 in the circumferential direction and the distance between them are chosen accordingly so that the clamping pawl 20 has a sufficiently high positional rigidity against movements in all other directions.

The clamping pawls 20 of the chuck in this embodiment are actuated by a wedge mechanism which includes a two-arm lever 26 for each clamping pawl 20. Each of the two-arm levers 26 is pivotally supported on the chuck body 10 or on each other block 24 by an annular support surface 26a of spherical design. The two-arm lever 26 engages inside the corresponding hole of the clamp pawl 20 with a second spherical, annular support surface 26b. Clamp claw 20
The arm of the two-arm lever 26 facing the is relatively short, while the second lever arm remote from the clamp pawl 20 is relatively long and has an inclined surface 26c near its free end. This inclined surface 26c cooperates with a roller 28, which is rotatably seated on a rotating shaft 30 attached to the actuating member. In this embodiment, this actuating member is configured as a chuck piston 32, which is slidably guided in an axial bore formed in the chuck body 10 and the spindle 14. It is actuated by a pressure medium which acts to move the to the left (FIG. 1). The return spring 34 is
One end is supported by the chuck body 10, and the other end is mounted in a hole in the piston 32 and acts to return the piston 32 to its original position.

As the piston 32 moves to the left, the right long arm of the two-arm lever 26 is lifted and pivoted about its support surface 26a, while the short arm causes a radial inward movement of the clamping pawl 20. , thus the arms 22 are deformed radially inward. When the piston 32 returns, the spring effect of the arm 22 causes the clamp pawl 2 to
0 is returned radially outward to a neutral position. In carrying out the present invention, if a compression spring 36 is installed as shown in FIG. The clamping pawl 20 acts on the arm, with respect to its neutral position, when the spring force of the arm 22 transmitted through the two-arm lever 26 balances the spring force of the compression spring 36, or when the long arm is in its furthest position, the piston It is further moved radially outward until it hits roller 32. In this way, a greater radial movement of the clamping pawl 20 is achieved. In this regard, the spring force of the spring 36 can be adjusted from the outside of the chuck body 10 by means of an adjusting screw 40.

In this example, the attachment 4
2 is screwed onto the free end surface of each clamp pawl 20. A set of replaceable attachment jaws serves to adapt the shape or diameter of the workpiece to be gripped and can be easily replaced if they become damaged. 1 and 2, one of the clamping pawls 20 includes an attachment jaw 42. In FIGS. Note that during operation, the attachment jaws 42 are connected or screwed to each clamp pawl 20. As shown in FIG. 1, the inner surface of the attachment jaw 42 also serves as an axial stop for the short arm of the two-arm lever 26. Further, as shown in FIG. 4, undesirable rotation of the two-arm lever 26 is also avoided due to the cooperation between the inclined surface 26c and the roller 28.

As mentioned above, the grooves are preferably formed by a wire cut electrical discharge machine. However, by starting from the end face of the protrusion 16, the groove can also be formed by electrochemical machining using a C-shaped tool. The arm 22 and clamping pawl 20 may be manufactured as separate parts and screwed or otherwise connected together to the chuck body 10.
However, it is preferable to use an integral structure as in the embodiments described above. With this integrated structure, groove 1
It has been found that it is preferable to fill 8 with an elastic filler immediately after manufacture. If a suitable relatively flexible polymeric material is chosen, this will make the arm and clamping pawl structure slightly stiffer, but will be sufficient to prevent the ingress of dirt, cuttings, etc. during operation. Overall, the method described above makes the chuck of the invention very inexpensive, since the chuck body 10 can be completely finished and heat treated before the final groove formation by a wire-cut electrical discharge machine. can be manufactured.

An additional advantage of the invention is that the clamping pawls employ a parallelogram linkage, so that each radial deformation of these clamping pawls automatically causes a certain amount of axial element movement, which During the gripping, the tool or workpiece is pulled against the end face of the chuck, and the tool or workpiece is thus positioned axially. It is therefore preferable for the relevant end face area of the chuck to be suitably finished so as to serve as a stop surface for the tool or workpiece.

The grooves of the embodiments described above in connection with FIGS. 1-4 include a groove portion 18a extending in a substantially precise axial direction and a groove portion 18b extending in a substantially precise radial direction. The latter connects the outer ends of the axially extending groove portions 18a. In practicing the present invention, the axial groove portion 18a
It is also possible to obtain an H-shaped groove shape instead of a C-shaped groove shape by extending the outer or front ends of the grooves beyond their connection points with the radially extending grooves 18b. be. This method is useful when greater material strength is required, especially in the central part of the clamping pawl, for example to provide an outer lever end or to form a threaded connection in the attachment jaw. .

As shown in FIG. 5, the substantially axially extending groove portions 18a may also be curved radially inwardly or outwardly, respectively, in the practice of the present invention. The shape of the arm may be such that, when viewed in the axial direction, it is narrow at the center and widens at both ends, that is, near the chuck body 10 and near the clamp pawl 20. The longitudinal cross-section of the arms 22 can be varied in this way to select a constant bending stress for each radial arm cross-section.

Furthermore, as is clear from the above description, the difference in arm length of the two-armed lever of the chuck of the present invention can be utilized for effective transmission of axial forces generated by the actuating member or chuck piston. In this way, various forces are generated by applying forces at optimal points. A particular advantage of the wedge surface mechanism of the present invention is that the clamping pawl 2
The transmission ratio can be reduced to a ratio corresponding to the transmission ratio of a two-arm lever within a range that provides accurate positioning of zero.

Regarding the embodiment shown in FIGS. 6 to 8, only the differences from the embodiment shown in FIGS. 1 to 5 described above will be explained below.

In this embodiment, the chuck piston 32'
has a circumferential groove 28'. The chevron-shaped lever is generally indicated at 50', with an arm 52' of the lever 50' being provided in each main jaw or clamping pawl 42' and engaging said groove 28'. The chevron lever has two bearing pins 54' on the chuck body.
(see Figure 7).
It has a second arm 56', which arm is provided with a coupling pin 58'. As shown in FIG. 8, this pin passes through a hole 59' in the right arm (in FIG. 6) of the two-arm lever, designated generally at 26'. This lever is
Like the two-arm lever 26 in the embodiment of FIGS. 1 to 5, it is tiltably or swingably supported on the chuck body 10' and is operatively connected to the clamp pawl 20'. chuck piston 3
Any movement of 2' to the left in FIG. 6 will cause the chevron lever 50' to swing clockwise about the support pin 54'. As a result, the two-arm lever 26' is similarly tilted clockwise, and the clamp pawl 20' is moved radially outward.
In the opposite case, movement of the chuck piston 32' to the right in FIG. 6 causes the clamp pawl 20' to move radially inward. Note that movement is always relative to the axis of the chuck shown at 60' in FIG.

This second embodiment is further provided with a centrifugal force compensation device. For this purpose a bouncing weight 62'
is guided so as to be radially movable within the chuck body 10'. This further includes 2 arm lever 6
4' to the corresponding clamp pawl 20', and the centrifugal force acting on the bouncy weight 62' when the chuck rotates is radially inward, and
It is converted into a counterbalance weight that acts on 0'. This force is intended to compensate for the centrifugal force acting on the clamping pawl 20'. The two-arm lever 64', like the two-arm lever 26', is tiltably or swingably supported by a spherical, annular support surface formed by a nut 70' in a channel-like passage 68' of the chuck body 10'. Nut 70' is 2 arm lever 6
It is screwed onto an external thread 72' of 4', is supported on the wall of a channel-shaped passage 68' formed as a hole, and carries a small fixing pin 76'. The locking pin 72' engages a groove 78' extending along the passageway 68' to prevent rotation of the nut 70'. In order to change the ratio of the lever arm lengths of the two-armed lever 64' to each other, this lever is itself rotated about its longitudinal axis. For this purpose, a hexagonally shaped hole 80' is provided for the insertion of a spanner. The two-arm lever 64' has additional spherical, annular support surfaces 82', 82' at its two ends.
4', and by means of support surfaces 82', 84', the lever 64' is supported on the walls of the clamping pawl 20' and the holes 86', 88' in the chuck body 10'. Finally, the two-arm lever 64' is provided with a small borehole 90' in the region of the support surface 84', in which a blocking ball 94' is fitted with a compression spring 99'.
2' to prevent accidental rotation of the two-arm lever 64'.

In the structure shown in FIGS. 6 to 8, 2
By changing the pivot point position of the arm lever 64' and thereby changing the ratio of the lever arm, especially the attachment jaw 42', depending on the mass of the clamp pawl 20', the centrifugal force acting on the bouncy weight 62' can be reduced. The forces can be compensated at all times by centrifugal forces acting on the jaws 20', 42'.

The ball blocking member for the two-arm lever 64' is 2
Since partial rotations of the arm lever 26 can be counted, there is an advantageous effect that the position of the pivot point formed by the nut 70' is determined by the pitch of the external thread.

In principle, it is possible to engage a bouncing weight in a two-armed lever 26' acting on the clamping pawl 20' and to provide this lever with an adjustable rotational position in a suitable manner. However, since the specific travel distance of the chuck piston 32' no longer gives the clamp pawl 20' the same travel distance as before, in this case the rotation of the two-arm lever or the pivot point for machine control is During adjustment, changes in transmission ratio need to be taken into account.

Reference numeral 100' indicates silicone rubber filled in the groove 18'. This material is intended to prevent dirt, particularly shavings and cuttings, from entering the groove and interfering with the free movement of the arm 22'.

〔Effect of the invention〕

According to the chuck of the present invention, it is possible to avoid the clamp pawl from tilting or seizing with respect to the chuck body, and the accuracy can be significantly improved, and at the same time, the guide surface that cooperates with the clamp pawl is omitted. Production is simple and inexpensive.

[Brief explanation of drawings]

1 is a longitudinal sectional view of a preferred embodiment of a chuck according to the invention; FIG. 2 is a front view of the chuck of FIG. 1; and FIG. 3 is a radial section taken along line 3--3 in FIG. 4 is a partial radial sectional view taken along the line 4-4 in FIG. 1, FIG. 5 is a partial longitudinal sectional view of an embodiment in which the outer shape of the groove or the shape of the arm is modified, and FIG. The longitudinal sectional views of the second embodiment of the present invention, FIGS. 7 and 8, are respectively 7 of FIG.
FIG. 3 is a radial cross-sectional view taken along lines -7 and 8-8. 10, 10'...Chuck body, 18...Groove,
18a, 18b...Groove portion, 20...Clamp pawl, 22...Pair of arms, 26, 26', 6
4'...2 arm lever, 26a, 26b...ball joint connection, 28...roller, 32, 32'...
...Operating member, 36... Compression spring, 50'... Angular lever, 62'... Bouncing weight, 70'... Pivoting bearing, 90', 94', 92'... Blocking member.

Claims (1)

Claims: 1. A chuck body, a clamping pawl movable radially relative to the chuck body, an actuating member movable axially relative to the chuck body, and an axial adjustment movement of the actuating member. In the chuck, each clamp pawl 20 has a pair of arms 2 extending generally in the axial direction.
It is connected to the chuck body 10 via 2,
The connection point between the pair of arms 22 and the clamp claw 20 and the connection point between the pair of arms 22 and the chuck body 10 are located at the vertices of a parallelogram, and the pair of arms 22 are substantially connected to each other. The motion converting mechanism includes a two-arm lever 26 pivotally supported on the chuck body 10 corresponding to each clamp pawl 20.
, the outer arm of the lever 26 is operatively connected to a corresponding clamping pawl 20 and the inner arm of the lever 26 is operatively connected to an actuating member 32 in response to axial movement of the actuating member 32. A chuck characterized in that the lever 26 is adapted to be pivoted about its pivot. 2 Each arm is a flat, leaf spring type arm 2
2. The chuck according to claim 1, wherein the chuck is configured as 2. 3. The chuck according to claim 1 or 2, wherein the axial cross-sectional shape of the arm 22 is selected so as to provide a constant bending stress along the arm 22. 4 The clamp claw 20 is attached to the chuck body 10.
Claim 1 The check described in any one of paragraphs 3 to 3. 5. Each groove 18 comprises two substantially axially extending groove portions 18a and one substantially radially extending groove portion 18b connecting the groove portions 18a. The chuck according to claim 4. 6. A chuck according to claim 5, wherein said radially extending groove portion (18b) is curved outwardly towards a corresponding clamping pawl (20). 7. A chuck according to any one of claims 4 to 6, wherein at least the open end region of each groove 18 is filled with an elastically deformable filler. 8. The chuck according to claim 1, wherein the open end of the groove 18 is closed by a lid member. 9. The chuck according to any one of claims 1 to 8, wherein the lever 26 for performing the motion conversion and force transmission function is connected to the chuck body 10 via a ball joint connection 26a. 10. A chuck according to any one of claims 1 to 9, wherein said lever 26 is connected to a corresponding clamping pawl 20 via a ball joint connection 26b. 11. A chuck according to any one of claims 1 to 10, wherein a replaceable attachment jaw is removably connected to each of the clamping pawls 20. 12 The clamp claw 20 or inner arm 2
Claims 1 to 11, characterized in that the central end face area of the chuck body 10 located between the radially inner ends of the chuck body 10 is configured as a planar stop.
The check listed in any one of the preceding paragraphs. 13. the motion conversion mechanism is configured as a wedge surface mechanism, each of the levers 26 being pivotally mounted within the chuck body 10, the outer arm of each lever 26 being connected to a corresponding clamping pawl 20; The inner arm of each lever 26 is inclined and extends in the axial direction, and the actuating member 3 is movable in the axial direction.
13. The chuck according to claim 1, further comprising a wedge surface 26c cooperating with the chuck 2. 14. A chuck according to claim 13, wherein said actuating member 32 carries a rotatably mounted roller 28 for co-operating with each wedge surface 26c. 15. A chuck according to claim 13 or 14, wherein the inner arms of the levers (26) are each subjected to a radially inward spring force. 16. A chuck according to claim 15, wherein a compression spring (36) is provided in a corresponding hole in the chuck body (10) for generating a radially inward spring force. 17. The motion converting mechanism comprises an angled lever 50' which is pivotable relative to the chuck body 10' and which connects the actuating member 32' at one end and the lever 2 at the other end.
6'. 18. The chuck of claim 17, wherein said chevron lever 50' engages a peripheral recess in actuating member 32' and is pivotally supported by both chuck body 10' and lever 26'. 19 a chuck body, a clamping pawl movable radially relative to the chuck body, an actuating member movable axially relative to the chuck body, and a clamping pawl responsive to axial adjustment movement of the chuck body; In the chuck comprising a motion converting mechanism for causing adjustment movement in the radial direction, each clamp pawl 20 is connected to the chuck body 10 via a pair of arms 22 extending substantially in the axial direction, and the pair of arms 22 and the clamp pawl 20
The connection points between the pair of arms 22 and the chuck body 10 are located at the vertices of the parallelogram, and the pair of arms 22 can be elastically deflected substantially in the radial direction. The motion converting mechanism has a two-arm lever 26 pivotally supported on the chuck body 10 corresponding to each clamp pawl 20, the outer arm of the lever 26 being operatively connected to the corresponding clamp pawl 20. The inner arm of the lever 26 is also operatively connected to an actuating member 32 such that in response to axial movement of the actuating member 32, the lever 26 is pivoted about its pivot axis. attached to each clamp pawl 20' is a bouncing weight 62' movable radially relative to the chuck body, and a second two-arm having a variable lever arm length ratio; A lever 64' operatively connects the weight to the clamping pawl 20' such that inward radial movement of the clamping pawl corresponds to outward radial movement of the bouncing weight. Check. 20 The longitudinally adjustable pivot bearing 70' of the second two-arm lever 64' is attached to the chuck body 1.
20. The chuck according to claim 19, wherein the chuck is mounted movably in the lengthwise direction of the lever at 0'. 21. The chuck according to claim 20, wherein said pivot bearing 70' is a nut screwed onto an external thread 72' of said second two-arm lever 64'. 22. The invention of claim 21, wherein said nut 70' is guided against rotation within chuck body 10' and said second two-arm lever 64' is rotatable about its longitudinal axis. Check. 23 In order to prevent rotation of the second two-arm lever 64', spring-type blocking members 90', 9
4' and 92' are provided in claim 2.
Check described in Section 2.