WO2013026444A2

WO2013026444A2 - Chuck

Info

Publication number: WO2013026444A2
Application number: PCT/DE2012/000858
Authority: WO
Inventors: Klaus Matheis
Original assignee: Gühring Ohg
Priority date: 2011-08-24
Filing date: 2012-08-23
Publication date: 2013-02-28
Also published as: WO2013026444A3; DE102011081523A1

Abstract

The invention relates to a chuck (1) for the force-fit clamping of a rotating shaft tool (2), having an axial stop determining the clamping depth of the tool to be clamped. The axial stop is formed by a positioning member (20), which is arranged such as to be axially adjustable in a central receiving opening (14) communicating with a central receiving bore (15) for receiving the shaft tool (2). The positioning member (20) bears axially against the shaft tool (2) with the end face of the member projecting into the receiving bore (15). The chuck also has an actuator (30) for the axial adjustment of the positioning member (20). According to the invention, the positioning member (20) is arranged such as to be axially displaceable yet non-rotatable in the receiving opening (14) by a positive engagement of outer circumferential surface thereof with the inner circumferential surface of the receiving opening (14).

Description

description

chuck

The invention relates to a chuck for non-positive tension of a rotating shaft tool, for. B. a hydraulic expansion chuck or shrink chuck, with a clamping depth of the thrusting tool to be determined defining axial stop.

Chucks with a clamping depth of a thrust tool to be determined determining axial stop have long been known.

For example, DE 102009003805 A1 shows and describes a chuck with an axial stop, which is formed by an adjusting screw which is held axially adjustable in the main body. The acting as a coolant lubricant transfer point screw is screwed into a threaded hole in the body. It has on its tool-side end an inner recess in the form of an inner cone forming a conical surface against which abuts the conical shaft end of a tool inserted into the chuck. In the area of the confluence of a centric coolant lubricant supply line in the inner cone, the coolant supply line has a contour in the form of a hexagon socket over which the set screw can be rotated and thus adjusted axially by means of a socket wrench axially inserted into the chuck from the tool machine end.

A similar chuck is shown and described in DE 102010026557 A1. In the chuck described in this document a relative to the chuck in the axial direction of the chuck adjustable adjusting screw is arranged, which serves as a stop for a tool held in the chuck. The adjusting screw cooperates with a pipe element which can be actuated radially outside the chuck. The tubular element is rotatable in the chuck, but arranged axially fixed at least in the direction of the screw. The tubular element is rotatably connected to the screw, but axially slidably connected. The operation of the pipe element takes place at

Bestätigungskopiel For example, via a mechanism in the manner of a crown gear, wherein the tubular element has a comb-like outer toothing.

If the chuck has a Dehnspannmechanismus for frictional clamping of the tool, it may come with an excessive torque stress of the tool to an interruption of the frictional connection between the tool shank and the base body with the result that the tool in the receiving opening rotates relative to the base body. By still existing at the beginning of the relative rotation between the shaft end of the tool and the tool-side conical surface of the screw, it may happen that the screw is rotated with the tool, whereby the previously set axial position of the axial stop formed by the screw is negated.

DE 19836912 A1 shows and describes a chuck, in particular a stretch chuck, in which, in contrast to the chuck according to the above-discussed DE 102009003805 A1, the axial stop is formed by a sleeve-shaped stop piece, which is rotated by means of a worm gear operable from the outer peripheral side of the hydraulic chuck and onto it Way can be adjusted axially. The worm gear has a transverse to a tool receiving opening rotatably mounted worm and a coaxial with the tool on receiving opening arranged worm wheel. The stopper piece is non-rotatably but axially displaceably held on the worm wheel and has an external thread which is in engagement with an internal thread of the base body, whereby a rotational movement of the worm wheel is converted into an axial movement of the stop piece. The shank end of a tool clamped in the main body abuts against an annular end face on the tool-side end of the stop piece, whereby the axial position of the tool is determined.

In contrast to the above-discussed DE 102009003805 A1 may be given in the chuck according to DE 19836912 A1, the worm gear additional self-locking against rotation of the stop piece. Nevertheless, inadvertent rotation of the stopper can not be completely ruled out in the event of excessive torque loading on the tool. Besides that is the frictional connection between the annular end face of the stop piece and the unspecified shank end of the tool is much weaker due to the smaller surface pairing than in a conical surface support, as described in the above-discussed DE 102009003805 A1, whereby the probability of inadvertent rotation of the tool relative to Body is increased.

DE 1904536 A1 shows and describes a chuck with a depth of travel determining axial stop in the form of a stop body, which is arranged against rotation with a cylindrical guide portion in the base body axially displaceable. The rotation lock is achieved by the engagement of a journal projection of a screwed in a radial Gewindebohruhg in the main body stud in a formed in the cylindrical guide portion of the stopper body longitudinal groove. The axial adjustment of the stop body by means of a bevel gear. The stopper body is for this purpose via a threaded portion with an axially immovably arranged in the main body adjusting nut in the screw. The adjusting nut meshes via a bevel gear with a mounted in the transverse bore of the body and from the outside via a socket wrench adjustable bevel gear. A rotation of the adjusting nut caused by the adjusting bevel gear results, owing to the screw engagement between the adjusting nut and the threaded section of the non-rotatably mounted stopper body, in an axial adjustment of the stopper body relative to the main body. The stopper body forms at its tool-side end a conical tip, on which the tool inserted into the chuck finds its abutment with a centering bore located on its shaft end face. The tool used in the body is screwed over a shaft extending the threaded extension in a threaded hole in the body and also stretched against the stopper body. Due to the rotationally fixed arrangement of the stop body of the stop body remains in a certain rotational position relative to the main body. However, the provided with a conical tip stop body would not be able to prevent inadvertent rotation of the tool in the body. This is achieved only by the screwing of the threaded projection with the base body and by the additional voltage of the tool against the stopper body. Starting from the initially discussed prior art, in particular DE 19836912 A1, the invention has the object, a chuck for frictional tension of a rotating shaft tool, with a clamping depth of a tool to be exciting defining axial stop so that a better adhesion between the screw and get the shaft tool and even by the screw effected axial stop is maintained even if the shaft tool should rotate during a machining machining relative to the main body unimpeached.

This object is achieved by a chuck with the features of claim 1. Advantageous or preferred developments are the subject of dependent claims.

In a chuck according to the invention, for. B. a Hydrodehnspannfutter or shrink chuck, the recorded in a central receiving opening in the main body actuating body protrudes into the formed in the body centric receiving bore for receiving the tool shaft of an exciting shaft tool and defined by its tool-side end an axial stop for the shaft tool. The axial stop formed by the adjusting body thus determines the clamping depth of the tool to be clamped. In contrast to the prior art discussed at the outset, according to the invention, the adjusting body should be arranged so as to be axially displaceable, but non-rotatable, in the receiving opening. The axially displaceable, but non-rotatable arrangement is inventively achieved in that the outer circumferential surface of the actuating body forms a positive connection with the inner peripheral surface of the receiving opening. The positive engagement formed between the outer peripheral surface of the Stellkörpe.rs with the inner peripheral surface of the receiving opening prevents any rotation of the actuating body relative to the base body from the outset.

The actuating body can be formed by an adjusting screw as in DE 102009003805 A1. In contrast to the adjusting screw described therein, which is screwed into a threaded bore formed in the chuck and thus rotatable relative to the base body, according to the invention designed as a set screw Actuator in the receiving opening, although axially displaceable, but rotatably arranged. The receiving opening therefore has no meshing with the external thread of the adjusting body internal thread. The actuator is therefore not bolted to the main body of the chuck. Alternatively, the actuating body may be designed as an adjusting bolt which can be displaced axially in the receiving opening but is arranged non-rotatably.

Regardless of whether the actuator is formed as in the prior art as a set screw or, in contrast, as an adjusting bolt, it preferably has at least over the length of its arranged in the receiving opening guide portion an outer contour in the form of a regular polygon and has the receiving opening preferably a complementary shaped inner contour. The arranged in the receiving opening guide portion of the actuating body is formed, for example in the form of an outer hexagon and the receiving opening as a hexagon socket.

Since according to the invention the adjusting body is arranged rotationally fixed, even in the case of an unintentional interruption of the frictional connection between the tool shank and the main body during a machining machining of a rotation of the tool in the receiving opening to no rotation of the actuating body. The axial position of the axial stop determined by the adjusting body therefore remains intact even when the tool should unintentionally twist relative to the basic body.

It thus offers the possibility to make the axial stop forming end face of the actuating body so that a positive and / or non-positive connection with the shaft end of the tensioned tool is achieved in order to achieve an improved torque entrainment of the tool and thereby inadvertent rotation of the Counteract tool relative to the main body or to the actuating body. For example, the tool-side end face of the actuating body may have an inner recess in the form of a conical surface forming an inner cone for positive and / or non-positive torque entrainment of a tool with a conical shank end. Examples of such a frictional connection can be found, for example, in the initially discussed DE 102009003805 A1 but also in DE 102009003805 A1 or DE 202004021168 U1, which is based on the applicant. AI Ternatively, the tool-side end of the actuating body may have one or more, preferably two diametrically arranged, axially projecting Mitnehmerfortsätze for positive and / or non-positive torque driving a tool with a complementarily shaped shaft end.

Since the axial position of the actuating body is maintained in any case by the positive engagement with the main body of the chuck, even in the event that the tool should still rotate relative to the actuating body, the risk of an axial distance between the shank end of the tool and the actuator low. The chuck according to the invention is therefore suitable for minimal quantity lubrication. Minimum quantity lubrication (MQL) uses an air / oil mixture that prevents the generation of frictional heat on the tool during the machining process through optimum cooling lubrication. A MMS cooling lubricant supplied to the machine tool side is guided through the chuck or adjusting element, which has a central coolant lubricant channel for this purpose, and one or more channels within the tool up to the tool cutting edge (s).

The actuator driving actuator can be configured as an actuated from outside the body angle gear that converts an externally applied force or torque applied from the outside into an axial force acting on the actuator body.

In the event that the adjusting body is designed as an adjusting screw, the actuator may for example comprise an actuatable from outside the base drive wheel and cooperating with the external thread of the adjusting screw driven wheel. In terms of a compact design as possible with small radial extent the drive wheel and the driven gear are advantageously arranged so that intersect their axes of rotation in a longitudinal center plane of the body. The actuator may be formed, for example, in the manner of a bevel gear or in the manner of a crown gear. Such a transmission allows a particularly finely graduated translation from the drive wheel to the driven wheel. Alternatively, the actuating body may be designed as an adjusting bolt and the actuator in the manner of a wedge gear with an operable from outside the main body drive wedge, which acts on a wedge surface formed on the adjusting bolt. The drive wedge may for example be formed by a conical tip end face of a drive screw, which is screwed into a in the base body at an angle, for example at right angles, formed to the longitudinal central axis of the body threaded bore and acts on a provided on the adjusting bolt wedge surface. Alternatively, the drive wedge may be formed by a wedge surface which is formed on a pressure pin, which is arranged between the adjusting bolt and a drive screw which is screwed at an angle to the longitudinal central axis of the base body in a threaded bore formed in the base body. In this design, the drive screw therefore does not act directly on the wedge surface on the adjusting bolt but indirectly via the intermediate pressure pin. The drive screw and / or the pressure pin are / is preferably arranged relative to the adjusting bolt such that the rotational and / or displacement axis of the drive screw and / or pressure pin preferably intersect the displacement axis of the actuating bolt in a longitudinal center plane of the base body. Such wedge gear allows a simple and compact design of the chuck.

The chuck is preferably a hydraulic chuck or shrink chuck or generally a frictional clamping chuck. Of course, the invention also applies to other types of chucks such. B. a multi-jaw food application.

Preferred embodiments of the invention are illustrated in the drawings and are explained in more detail below. In the drawings shows:

1 shows a first embodiment of a chuck according to the invention in a perspective, partially cutaway view;

FIG. 2 shows the chuck of FIG. 1, in which an adjusting screw and a comb wheel cooperating with the adjusting screw have been omitted; FIG. and Fig. 3 shows a second embodiment of a chuck according to the invention in a perspective, partially cutaway view.

First embodiment

In the first embodiment described below, the chuck 1 is designed as a hydraulic expansion chuck and essentially consists of a base body 10, a control body 20 arranged in the main body 10, an actuator 30 which is arranged in the base body 10 and can be operated from outside the main body 10, and one in the base body 10 arranged cooling lubricant takeover sleeve 40 composed.

The main body 10 comprises a clamping section 11, a central section 12 and a coupling section 13, which extend along a common longitudinal central axis 2 of the chuck 1. The tensioning section 11 has a hydraulic tensioning mechanism known per se for the force-locking clamping of a continuously rotating shaft tool 2, for example a drilling tool, shown only schematically. By way of the coupling section 13, which is designed as a hollow shaft taper (HSK), the chuck 1 can be coupled to a clamping device (not shown) on a spindle of a machine tool (also not shown).

The middle section 12 has a stepped centric receiving opening 14 which connects the tool receiving bore 15 of the clamping section 11 with the cavity 16 formed in the coupling section 13. The central receiving opening 14 can be functionally subdivided into a guide section 14a opening into the tool receiving bore 15, a threaded section 14c opening into the cavity 16 of the coupling section 13 and a drive receiving section 14b connecting the guide opening 14a to the threaded bore section 14c. The guide section 14a has an inner contour in the form of an inner hexagon (see FIG. 2) in an axial plan view, while the drive receiving section 14b is designed as a cylinder bore and the threaded section 14c as a threaded bore. The adjusting body 20 accommodated in the central receiving opening 14 of the main body 10 is formed from a set screw with a shank portion 21 and a head portion 22. The shank portion 21 provided with an external thread has an outer contour in the form of an external hexagon when seen in an axial plan view. The provided with the external thread shaft portion 21 of the actuating body is therefore has a hexagonal profile corresponding lateral flattening. In contrast to the set screw described in DE 102009003805 A1, however, the adjusting body 20 is not screwed to the base body 10 via its shaft portion 21 provided with an external thread, but by a positive fit of the outer contour of the shaft portion 21 with the inner contour of the guide portion 14a of the central receiving opening 14 Although axially displaceable, but rotatably received in the central receiving opening 14. The external thread of the sheep-tabschnitt 21 cooperates with the actuator 30 described later to adjust the actuator body 20 in the main body 10 axially. The head section 22 of the actuating body 20 forms an axial stop for the shaft tool 2 clamped in the chuck 1.

Due to the positive arrangement in the main body 10 of the actuator body 20 even in the case of an unintentional interruption of the frictional connection between the abutting against the actuator body 20 shaft tool 2 during machining and a relative rotation of the tool relative to the actuator body 20 maintains its rotational position in the main body 10 at all times. As a result, the once set axial position of the axial stop formed by the adjusting body 20 is maintained.

Thus, it is possible to design the end stop 23 forming the axial stop of the head section 22 of the adjusting element 20 such that a good positive and / or non-positive connection with the shaft end 3 of the shaft tool 2 is achieved. In the first embodiment, the tool-side end face 23 of the head portion of the actuating body 20 has two diametrically arranged, axially projecting Mitnehmerfortsätze 24 which are positively engageable with complementarily shaped recesses 5 on the shaft end 3 of the shank tool 2.

By the actuator 20 runs along the longitudinal medium axis 6 a of the chuck 1 a central through hole. The right in Fig. 1 end of the through hole forms an inlet opening into which the cooling lubricant coming from the cooling lubricant take-up sleeve 40 is fed. The left in Fig. 1 end of the through hole forms an outlet opening from which the cooling lubricant flows into one or more cooling lubricant channels in the shaft tool 2. The feeding of the coolant lubricant coming from the coolant lubricant transfer sleeve 40 into the central through-bore of the actuating body 20 takes place via a sleeve-like transfer piece 26 arranged between the actuating body 20 and the coolant lubricant transfer sleeve 40.

The sleeve-like transfer piece 26 has, on its side oriented toward the coolant lubricant transfer sleeve 40, an enlarged diameter cylinder portion 26a, whose inlet opening may be formed by a conical inner recess. On its side oriented toward the actuating body 20, the sleeve-like transfer piece 26 has a cylindrical section 26b, which dips into the central passage bore in the actuating body 20. The transfer piece 26 is axially supported toward the adjusting body 20 at a radial step 14d formed between the threaded portion 14c and the drive receiving portion 14b. The transfer piece 26 thus holds a later-described output gear 32 of the actuator in the drive receiving portion 14b of the central receiving opening 14 rotatably, but it limits the axial mobility of the driven gear 32 a.

The coolant lubricant transfer sleeve 40 is stretched axially against the transfer piece 26 via a threaded sleeve 41 in the central receiving opening 14. The threaded sleeve 41 has for this purpose an external thread which is screwed into an internal thread of the threaded portion 14c of the central receiving opening 14 in the base body 10. With regard to the further structure and the attachment of the coolant lubricant transfer sleeve 40, reference is made to the corresponding information in DE 102010026557 A1.

Through the coolant lubricant transfer sleeve 40 runs along the longitudinal center axis 6 of the chuck 1 in alignment with the central through hole of the actuator body 20 arranged centrally through hole 43. The right in Fig. 1 end of the through hole 43 forms an inlet opening into which the (not ge showed) machine tool coming coolant is fed. The left in Fig. 1 end of the through hole 43 forms an outlet opening, from which the cooling lubricant flows into the actuating body 20.

The adjusting body 20 and the cooling lubricant take-over sleeve 40 form a device for taking over and guiding the cooling lubricant coming from the side of the machine tool into the internal coolant lubricant channel (s) of the shaft tool 2 clamped in the chuck 1.

The actuator 30 driving the actuator 30 is formed as an externally of the body 10 to be actuated angle gear, which converts an externally applied force or an externally applied torque in an actuating body 20 acting on axial force.

In the first embodiment, the actuator 40 is formed by a crown gear, which has an actuatable from outside the body 10 from drive wheel 31 in the form of a crown wheel and cooperating with the actuator 20 output gear 32 in the form of a comb wheel. The drive wheel 31 is rotatably but axially fixed by means of a locking ring in a central receiving opening 14 of the base body 10 intersecting radial bore 17 in the base body 10. The output gear 32 is formed like a sleeve. It has on its outer circumference a standing with the Kronradverzahnung of the drive wheel 31 Kammradverzahnung. The inner circumference is formed by a meshing with the external thread of the shank portion 21 of the actuating body 20 internal thread. The axes of rotation of the drive wheel and driven wheel 31, 32 intersect in the longitudinal center plane of the main body 10.

Second embodiment

In Fig. 3, a second embodiment of the chuck according to the invention is shown. The second embodiment differs from the first embodiment only in the design of the actuating body 20. As in the first embodiment, the actuating body 20 is formed by a set screw. In Fig. 3, the shaft portion 21, however, is shown only schematically in the form of a hexagon. Not to be seen is the external thread incorporated in the hexagon. In contrast to the first embodiment, the tool-side end face 23 of the head portion 22 of the actuating body 20 has an internal recess in the form of an inner cone forming a conical surface 25 for positive and / or non-positive torque driving a tool with a conical shaft end. Examples of such a frictional connection can be found, for example, in the initially discussed DE 102009003805 A1 but also in DE 102009003805 A1 or DE, which is based on the applicant

202004021168 U1.

Further embodiments (not shown)

In the first and second embodiments, the actuator 30 is formed by a crown gear. Alternatively, the actuator may be formed as a bevel gear, are formed in the drive and driven gears 31, 32 each having a bevel gear with a bevel gear. Analogous to the comb wheel the abortive bevel gear is sleeve-like and has a with the external thread of the shank portion 21 of the actuating body 20 meshing internal thread.

In the first and second embodiments or the alternative embodiment described above, the adjusting body 20 is formed by an adjusting screw with an externally threaded shank portion 21. The output gear 32 is sleeve-like and is connected via an internal thread with the external thread of the shaft portion 21 of the actuating body 20 in engagement. Alternatively, the adjusting body 20 may be formed as an adjusting bolt and the actuator 30 in the manner of a wedge gear with an operable from outside of the main body 10 from drive wedge, which acts on a formed on the actuating body 20 wedge surface. The drive wedge may for example be formed by a conical tip end face of a drive screw, which is screwed into a in the base body 10 at an angle, for example at right angles to the longitudinal central axis 6 of the base body 10 formed threaded bore and acts on a provided on the actuating body 20 wedge surface. Alternatively, the drive wedge may be formed by a wedge surface, which is formed on a pressure pin, which is arranged between the adjusting body 20 and a drive screw, which at an angle to the longitudinal center axis 6 of the main body 10 in a basic body 10 ausge-. formed threaded hole is screwed. In this configuration, the drive screw therefore does not act directly on the wedge surface on the actuating body 20 but indirectly via the intermediate pressure pin. The drive screw and / or the pressure pin are / is preferably arranged relative to the setting body 20 such that the rotational and / or displacement axis of the drive screw and / or pressure pin preferably intersect the displacement axis of the setting body 20 in a longitudinal center plane of the base body 10.

Furthermore, the adjusting body 20 - whether it is designed as a set screw or adjusting bolt - deviating from the outer contour in the form of an external hexagon an outer contour in the form of any regular polygon and the guide portion of the receiving opening 14 have a complementarily shaped inner contour, if between the outer peripheral surface of the Adjusting body 20 and the Innenumfangsflä- surface of the guide portion 14a of the receiving opening 14 is achieved a form fit such that the actuating body 20 in the guide portion 14a of the Aufnahmeöff- 14 of the main body 10 rotationally fixed but axially displaceable. In this respect, the actuator body 20 does not have over its entire length or over the entire length of its shaft portion 21 have a constant cross-section. It is sufficient if the adjusting body 20 is guided positively at least over the length of its arranged in the guide portion 14a of the receiving opening 14 in the base body 10 portion.

In the first and second embodiments, the cooling lubricant transfer takes place from the coolant lubricant transfer sleeve 40 into the actuating body 20 via a sleeve-like transfer piece 26 connected therebetween. The transfer piece 26, however, is not absolutely necessary. The coolant lubricant transfer can take place from the coolant lubricant transfer sleeve 40 to the actuating body 20 via any tubular element. The cooling lubricant transfer can also take place directly from the coolant lubricant transfer sleeve 40 to the actuating body 20, ie without the interposition of a further element. For this purpose, the Endabchnitt of the shaft portion oriented toward the Kuhelschmiermittelübernahmehülse 40 toward, for example, be cylindrical and the cooling lubricant takeover sleeve 40 dip. As an alternative to a hydraulic expansion chuck, the chuck according to the invention can be designed as a shrink chuck or any other force-fit clamping chuck.

Claims

claims

1. chuck (1) for non-positive tension of a rotating shaft tool (2), with a clamping depth of exciting tool defining axial stop, which is formed by a control body (20) in a central receiving opening (14) with a centric Receiving bore (15) for receiving the shank tool (2) communicates, is arranged axially adjustable and axially abuts with its in the receiving bore (15) projecting end face against the shank tool (2), and with an actuator (30) for axial displacement of the actuating body ( 20), characterized in that

the adjusting body (20) in the receiving opening (14) by a positive connection of its outer peripheral surface with the inner peripheral surface of the receiving opening (14) is axially displaceable, but rotatably disposed.

2. chuck (1) according to claim 1, characterized in that the adjusting body (20) at least over the length of its in the receiving opening (14) recorded portion has an outer contour in the form of a regular polygon and the receiving opening (14) has a complementarily shaped inner contour ,

3. Chuck (1) according to claim 1 or 2, characterized in that

the adjusting body (20) is designed as a set screw, and

the actuator (30) is designed as an angular gear with a drive wheel (31) which can be actuated from laterally outside the main body (10) and a driven wheel (32) which cooperates with an external thread of the actuating body (20).

4. Chuck (1) according to claim 3, characterized in that the axes of rotation of the drive wheel (31) and the driven gear (32) intersect in a longitudinal center plane of the chuck (1).

5. Chuck according to claim 4, characterized in that the actuator (30) is designed in the manner of a crown gear.

6. Chuck (1) according to claim 1 or 2, characterized in that the adjusting body (20) is designed as an adjusting bolt, and

the actuator (30) is designed as a wedge gear with a drive wedge which can be actuated from laterally outside the main body (10) and acts on a wedge surface formed on the adjusting bolt.

7. chuck (1) according to claim 6, characterized in that the drive wedge is formed by a conical tip end face of a drive screw which is screwed at an angle to the longitudinal central axis (6) of the base body (10) in a base body (10) formed threaded hole and acting on a wedge surface provided on the adjusting body (20).

8. chuck (1) according to claim 6, characterized in that the drive wedge is formed by a wedge surface which is formed on a pressure pin which is arranged between the actuating body (20) and a drive screw which is at an angle to the longitudinal central axis (6). of the base body (10) is screwed into a threaded bore formed in the base body (10).

9. chuck (1) according to one of claims 6 to 8, characterized in that intersect the displacement axes of the drive wedge and the actuating body (20) in a longitudinal center plane of the Grundköpers (10).

10. Chuck (1) according to one of the preceding claims, characterized in that the tool-side end face of the actuating body (20) for a positive and / or non-positive torque driving of the chuck (1) to exciting shaft tool (2) is designed.

11. chuck (1) according to claim 10, characterized in that the tool-side end face of the actuating body (20) has an internal recess in the form of an inner cone forming a conical surface (25) for positive and / or non-positive torque driving a shank tool (2) with a conical Shank end has.

12. chuck (1) according to claim 10, characterized in that the tool side end face of the actuating body (20) has one or more axially projecting Mitnehmerfortsätze (24) for positive and / or non-positive torque driving a shank tool (2) with a complementary shaped Shank end has.

13. Chuck (1) according to claim 12, characterized by two diametrically opposite Mitnehmerfortsätze (24).

14. Chuck (1) according to one of the preceding claims, characterized in that the actuating body (20) has a central through-bore guide a cooling lubricant to the in the chuck (1) to exciting shaft tool (2).

15. Chuck (1) according to any one of the preceding claims, characterized by a Dehnspannmechanismus for clamping the shaft of a chuck to exciting in the chuck tool (2) in the receiving bore (15).