DE3807140A1 - Coupling device between a work or tool carrier and a manipulating device provided for it - Google Patents

Abstract

A coupling device between a tool system module, such as, for example, a basic tool holder, and a machine tool, such as, for example, a spindle, is described. To quickly produce and release the connection between these components while providing large axial forces, a clamping device with an actuating rod is provided via which a wedge mechanism is activated with which clamping elements provided in the one part to be coupled can be pressed essentially radially outwards into a recess of corresponding design at the other part to be coupled. The clamping elements are formed by at least three cramp-like clamping claws which are arranged at a uniform angular distance from one another, are arranged essentially parallel to a centring extension of the basic tool holder and can be swung into a groove-like recess of the centring extension while supported in a centring receptacle of the spindle with a claw section lying radially inside the centring extension in the coupled state. This coupling device is distinguished by high flexibility with regard to the possible uses while being economical to manufacture.

Description

The invention relates to a coupling device between a workpiece or tool carrier, e.g. a tool system module, for example in the form of a Basic tool holder, and an associated handle exercise facility, e.g. a machine tool, at for example in the design as drilling, turning or Milling machine, according to the preamble of claim 1. The coupling device is intended for both standing as well as for moving, e.g. rotating workpiece or Tool carriers, such as Tool system modules suitable be.

In the course of recent technical development automated machining centers the need arises after modular tool systems, which at must be exchangeable in the shortest possible time.  

There are already a number of coupling devices developed between individual tool system modules and have been proposed that stand for and also for rotating tools. You tried this modular couplings on the interface between Transfer machine tool and tool system module. It has been shown, however, that it is difficult to To design the coupling device so that it Stability, positioning requirements accuracy, lubricant supply to the tool and Automation of the tool change equally justice.

So from the magazine "Modern Manufacturing" Issue November 1986, a coupling device according to the The preamble of claim 1 is known, in which a the actuating rod of the tensioner connected Cone two diametrically offset clamping bodies radially outwards in correspondingly shaped recesses screwed radially from the outside into the spindle holder Presses screws. The recesses in the screws are just like the areas of the Clamping body designed conical, with a certain Axial offset between the cone of the screw recess and the cone of the clamping body is provided so that when radial outward pressing of the clamping body axially directed pressure force between the parts to be coupled is produced. The support is done via behaves radial large flat surfaces, resulting in a results in relatively high rigidity of the system. However, these plan areas cannot make up the whole to be used for pressure force transmission, as normal to driving pins aligned with these flat surfaces must be used for indexing the tool system module with respect to the machine tool or for a Carrying the tool system module by the werkzeugma  coupling part on the rail side, e.g. the spindle, to care. To counter the problem that a relatively cool tool system module to one already preheated coupling part on machine tool side can be connected without problems, it is advantageous if the tool system module has an interventional extension and the machine tool-side coupling part one for this has intended recording. In the known case must this advantage can be bought with the disadvantage that the tool system module with a relatively complex xen mechanics must be equipped, the wedge gear be, an operating rod, and the two clamping bodies includes.

To avoid this relatively large effort, is already proposed this known clutch system to reverse kinematically, i.e. the clamping elements together with the operating rod and the wedge gear to accommodate on the machine tool side. this leads to however, in the known case, that now a centering journal on the machine tool part of the coupling direction must be attached. However, this must be done an inner surface on the side of the tool system module Precision can be manufactured, resulting in relatively high costs leads. In addition, this system reversal means that when attaching a tool system module that has a low lower temperature than the one already preheated, for example Machine tool spindle has fit problems can, taking into account that for reasons of Positioning accuracy relatively narrow tolerances must be provided.

It has also been shown that the rigidity the interface between tool and machine tool is limited in that the bending resistance moment of  Coupling device in the area of the interface single Lich in the axes of the clamping body and the screws containing level is defined. With rotating loads this means that the coupling device is not effective is able to build tool vibrations counteract.

The invention is therefore based on the object Coupling device according to the preamble of the patent Proverb 1 to create the requirements regarding Positioning accuracy of the workpiece or tool carrier, such as of the tool system module, rigidity the connection, automation of the workpiece or Tool change, flexibility in terms of applications areas of application and economic efficiency to an improved degree justice.

This task is carried out in the characterizing part of the Features specified claim 1 solved.

According to the invention, it succeeds by creating a bracket-like tension between those to be coupled Divide the power flow between the coupling parts improve, i.e. about the scope of the interface between the tool system module and machine tool to keep as even as possible. Because of the homogeneous Force distribution over the circumference is in connection with the inventive design of the clamping claws in the form of essentially axially aligned bracket-like ele elements of the space required in the radial direction for the Clamping claws very small, which increases the possibility opened, which are in surface contact with each other Plan surfaces of the parts to be coupled very large ten. Because moreover by the inventive Design of the coupling device no moving part in Compatibility arises if the axis is required with different tool systems, for example also  those with a modular coupling with an axial tightening screw is built up. It is still ensured that temperature Conditional difficulties when changing the tool system module from Basic concept are excluded because the colder, if necessary Tool system module engages with an extension in a receptacle. The relatively complex inner surface is in the area of machine tool-side part formed, thereby reducing the cost of Tool system module can be reduced. The special results re advantage that there are no moving parts in the tool system module are present, which significantly reduces the manufacturing costs can be.

The advantages described above arise for each type of Coupling between a workpiece or tool carrier and a Handling device, for example, from a workpiece change system can be formed.

The structure of the coupling device according to the invention has especially if he is in the field of Interface between a machine tool spindle and a basic tool holder according to claim 2 applications finds. In this case there is an extreme simple spindle construction, since all parts are rotationally symmetrical can be designed. An additional advantage is thereby seeing that spindles from already on the market located machine tools with little effort the clutch system according to the invention can be converted, wherein the tie rod already provided in the spindle can be used and only a spindle attachment flange must be formed, the clamping claws records. The excavation path remains to be solved the coupling device significantly compared to one ago conventional clutch system with steep taper reduced. There only a plan on the part of the tool system module surface and a centering extension must be formed, it is also possible to use identical, standardized gripper grooves to provide for an automatic tool change where resulting in additional economic benefits,  taking advantage of cylinder fitting in terms of Positioning accuracy is still maintained.

The rotationally symmetrical design of the coupling direction also opens up in an advantageous manner the possibility of transferring the contact pressure without overhung loads gene and thereby the positioning accuracy and last Lich also to increase the stability of the tool. The clamp-like clamping claws nestle under the influence of the wedge gear extremely evenly on a flank the groove-like recess of the centering process, wherein by appropriate design of the ones in contact Wedge gear surfaces, e.g. through the training dung according to claim 4, a lossless as possible Initiation of the clamping force can take place. It is from further advantage that the by pushing the Small elastic deformation caused by clamping claws the centering process has a tendency to fit to be trained more precisely between the spindle and the tool system module the, i.e. to improve.

The generation of the axial contact force without lateral force is through the training according to claim 6 additionally improved. In this way, floating storage the actuating rod created, causing the thrust cone radial self-centering when the force is applied experienced within the jaws. The clamping claws themselves support themselves with their facing away from the claw section End in a radially defined position in the holder, see above that created a constraint-free gear with which the contact pressure is extreme over the circumference can be generated evenly.

If the thrust cone is radial within the claw sections is arranged, there is an immediate introduction  the cone force on the claw sections, whereby by the Wedge surfaces of the wedge gear a power transmission follows. Another level of power transmission is invented according to the pivoting of the claw sections in the groove-like recess in the centering process, so that very high axial clamping forces are applied can. The coupling device according to the invention is suitable accordingly almost for use at interfaces of all machine tool types.

Basically, it is possible to attach the clamping claws to any a location in the centering of a spindle stipulate that while maintaining a predetermined th radial position in and out of engagement with the brought groove-like recess of the centering extension can be. Everyone is particularly advantageous Training according to claim 7, according to the one for the clamping claws provided support groove in a driving ring is formed, which is used in the centering is.

The further training according to claim 2 advantage achieved with the help of at least one Driving claw in the front of the centering cylinder engages in a recess, which in the torque transfer occurring forces to initiate and the contact plane surfaces between those to be coupled Continuing education means that sharing remains unharmed maintained according to claim 8. Furthermore there is the manufacturing advantage that for the swiveling movement of the clamping claws and that for the Circumferential force transmission provided functional areas now formed on a single component and therefore with greater precision in terms of location assignment can be made to each other.  

As already mentioned at the beginning, the fiction opens moderate design of the coupling device a pure rotationally symmetrical structure, none near the axis Components needed. As a result, the Possibility opened, the tool system module over axis central supply channels with coolant or lubricant for to supply the tool. This is only necessary Lich that the actuating rod has a longitudinal bore for Receives lubricant. This lubricant is then in the Forwarded inside the thrust cone and over one Hollow pin according to claim 9 of a coaxial recess tion in the tool system module.

In this context it is possible, according to Patentan Say 34 in the thrust cone an axial central bore to be provided in the sealing in the tool system module attached hollow pin can engage. In this way can the lubricant supply without radial deflections continue to be done but it will be additional for that ensured that the excavation movement when releasing the clutch device on the axial length dimension of the centering cylinder remains limited.

A particularly advantageous design of the groove-like There is a recess in the centering extension or centering cylinder Subject of claim 11, since this groove in Puncture method can be made.

The construction of the coupling device according to the invention opens up the possibility of the functional surfaces between Clamping claws, receiving and centering cylinders too Design that contact areas as large as possible ent stand. This can be reliably ensured be that the clamping claws according to claim 16 are manufactured or trained.  

If a centering ring is provided according to claim 14 , the concentricity can also be made adjustable be, whereby the positioning accuracy of the Tool system module can be raised further.

In the coupling device according to the invention a homogeneous force distribution over the circumference and an exact Positioning of the parts to be coupled to each other from Condition of the fitable engagement Functional areas depending on the parts to be coupled. It is therefore of advantage to use these functional surfaces Coupling device even under harsh conditions, i.e. in use with maximum cutting performance and also with unfavorable chip formation, clean and necessary for this as little as possible to keep possible. This need is met by the Further development of claim 17 taken into account. The functional surfaces of the parts of the Coupling device are in the released state of the Coupling preferably continuously with compressed air rinses, so that dirt, grinding dust and the like cannot stick to the fit surfaces. Damage Therefore, the fit surfaces can be used effectively be closed, so that the life of the clutch direction is additionally raised.

With a rotationally symmetrical structure of the coupling device the rinsing channel system is easily supplied with compressed air. To the flat surface contact between the plant effective cleaning of the tool system module and spindle is the key Training according to claim 18 of particular Advantage. The compressed air flushing channels in the radial ring surfaces chensegmenten ensure that when the Tool system module in the area of the fit surfaces ever more accelerated compressed air flow between the  mating surfaces that are moved towards one another are generated, whereby even the finest grinding dust is reliably removed from the Fit surface is removed. The grooves between the Radial ring surface segments also act as Dirt chambers, so that this fit is kept acidic areas is further simplified.

Further training is an advantage in terms of manufacturing technology according to claim 19 or 21, since in this way only axial machining of the machine tools side part, for example the machine tool spin del, must be done.

It has been shown that the prism-like shape tion of the entrainment process on the entrainment ring is very large Circumferential forces can be transmitted, the effective Diameter of the entrainment process be relatively can stay bordered. For the design of the take away In principle, every regular polygon can serve as the basis. However, it has been shown that based on a triangular prism with round ground Edges and convexly curved prism surfaces give good results can be achieved. This results in a Positive connection in the form of a so-called K-profile, whereby however, the one between the rounded edges flat surfaces are replaced by convex surfaces.

The training according to claim 24 increases additional Lich the use value of the coupling according to the invention direction. With this design it is not only possible to achieve the peripheral forces occurring during torque transmission transfer symmetrically, but it will go beyond that created the conditions for indexing of the tool system module relative to the machine tool in Partial steps of 30 ° can be done.  

For additional stabilization of the clamping claws, the Training according to claim 25 is an advantage. In the Training according to claim 26 is the leadership cylinder simultaneously transfer the function, the Mitnah mering defined to fix in the centering fixture, whereby the number of components can be reduced.

With the training according to claim 27 is by the inventive design of the supply with compressed air available annulus with the available compressed air low losses directed to the important points that it must be kept clean or cleaned. These Continuing education is particularly in connection with the Design according to claim 29 advantageous because it is on this way, the one flowing through the branch channels succeeds To keep compressed air so large in terms of mass flow rate that not only the flat surface, but also the cylindrical one Fit surface can be rinsed or cleaned.

Further development is particularly simple in terms of production technology dung according to claim 29, since the notch in the area of Thread is very easy to manufacture.

With the training according to claim 30 with simple means ensured that even a more targeted Compressed air flow to the functional areas between the thrust cone and clamping claws.

The design of the guide cylinder according to claim 33 creates the prerequisite for above-mentioned floating mounting of the operating rod in the area of the wedge gear, which enables self-centering effect is realized, but at the same time the Coupling process itself is not difficult because of elastic sealing ring for sufficient pre-centering  of the coupling parts.

If the compressed air flushing channels are formed in the centering ring are, there is a very inexpensive Deployment the flushing channel system, since the compressed air flushing channels in can be accommodated in a separate component. This has the additional advantage that Use of the centering ring, which is statically determined th holder in the spindle only on a flat surface and on a cylindrical mating surface with the spindle is in contact, an annular space on the rear side of the centering ring arises over the the compressed air evenly on the individual rinsing channels can be distributed. The training according to Patentan saying 14 is especially in connection with the shape tion according to claim 31 of additional advantage. The Annular gap for cleaning the cylindrical fit surface between spindle and tool system module can on this Be generated simply by a suitable Matching the diameter of the driving ring and the centering all around.

With the training according to claim 32 results the possibility of a very simple, central compressed air supply for the flushing channel system.

By designing the claw sections according to Patentan Say 35 can the structure of the coupling device can also be simplified. The tool system module falling wedge flank causes the centering cylinder which when inserted into the machine tool recess Claw sections displaced radially inwards.

An additional advantage of those described above Coupling device can still be seen in that with a single interface succeeds in reducing the diameter  stanchions, i.e. Transitions from a relatively large Spindle diameter to a relatively small Tool system module diameter, without magnification the axial length. For that purpose it is only required one in the centering use appropriately designed reducing ring and accordingly, radially inwardly cranked clamping claws To be provided with something if necessary modified thrust cone can be brought into functional engagement are.

It has been shown that particularly good results with six or eight clamping claws can be achieved.

With the training according to claim 37 device-related effort reduced.

The development according to claim 38 opens up the possibility of forming the particularly highly stressed areas of the support groove in the attachment flange, which is removably attached to the machine tool-side coupling part, for example to the machine tool spindle. The attachment flange can - like the centering ring mentioned above - either be made entirely of wear-resistant material or have inserts made of material to increase the service life.

Advantageous options for organizing the take-away in Circumferential ring between the parts of the coupling to be coupled lungs device are the subject of claims 39 to 54.

To make it easier to attach the tool system module, a pre-centering device for the part to be coupled of the tool system module. An easy one  The form of the pre-centering is the subject of the patent claim 56.

Another or additional possibility of pre-centering tion is the subject of claim 57. With this Continuing education succeeds when moving the to coupling parts, i.e. in the extended state of the Actuating rod, the latter for pre-centering the coupling part. Through suitable design of the counter surfaces on the stroke of the operating rod is coordinated, it is ensured that the actuation rod together with the thrust cone during the clamping process radial guidance has more, so that the thrust cone in Interaction with the clamping claws during the clamping process can center yourself.

The training according to claim 59 leads to a further simplification of the construction of the clutch device tion by the coupling approach of the thrust cone to lateral stabilization of the clamping claws used becomes.

The training according to claim 63 has the additional Lichen advantage that in the disengaged state of the actuator a forced swiveling of the claw inwards Sections take place, which opens up the possibility the flank angle in the groove-shaped recess on the one hand and the claw section interacting with it te steeper to the center axis of the coupling device to train.

Similar advantages result from further training according to Claim 64.

Further advantageous embodiments of the invention are  Subject of the other subclaims.

Several are shown below with the aid of schematic drawings re embodiments of the invention explained in more detail. It demonstrate:

Figure 1 is an axial section of a first embodiment of the coupling device.

Fig. 2A is an end view of the tool system module in the embodiment of a basic tool receptacle;

Figure 2B is a side view, partially in section, of the tool base receptacle.

3A is a sectional view of the tool takeover ground up facing end portion of a machine tool spindle.

Fig. 3B is an end view of the machine tool spindle in accordance with "IIIB" in FIG. 3A;

4A is a view, partially in axial section of a driver ring.

FIG. 4B is a view of the driver ring according to "IVB" in Fig. 4A;

FIG. 4C shows a view of the driving ring according to FIG. 4A according to "IVC" in FIG. 4A;

Fig. 5A in the upper part a longitudinal section of a clamping claw and in the lower part a side view of a Hülsenkör pers, from which the clamping claw can be produced;

Fig. 5B in the upper part of end views of three equally spaced clamping jaws and in the lower section an end view of the sleeve-shaped body shown in Fig. 5A;

6A is a longitudinal section of a guide cylinder.

Fig. 6B is a view of the guide cylinder in accordance with "VIB" in Fig. 6A;

FIG. 7 shows a longitudinal section of the thrust cone according to FIG. 1;

FIG. 8 shows a side view of the hollow pin according to FIG. 1;

Fig. 9 is a compilation of the individual elements shown in Figures 2 to 8 to illustrate the assembly process.

FIG. 10 is a side view of the coupling device at the beginning of Ankupplungsvorgan partially in section, ges;

Fig. 11 is a view similar to Figure 10 of the coupling device, wherein the centering cylinder is just inserted into the machine tool machine.

Fig. 12 is a side view similar to Figure 11 of the coupling device with fully inserted Zen trier cylinder. and

FIG. 13 shows a view corresponding to FIG. 1 of a modified embodiment of the coupling device;

FIG. 14 is an axial section of a further embodiment of the coupling device in the released condition;

FIG. 15 is an end view of the side facing the basic tool receiving end portion of a machine tool spindle according to II in Fig. 14;

FIG. 16 is an end view of the tool system module in the embodiment of a basic tool according recording XVI in Fig. 14;

FIG. 17 is a section according to XVII-XVII in FIG. 14;

18A is a view, partially in axial section of a driver ring.

FIG. 18B is a view of the driving ring according to "XVIII B" in FIG. 18A;

FIG. 18C is a view of the driver ring in accordance with "XVIIIC" in Fig. 18A;

FIG. 19A an axial half section of a further exporting approximate shape of the coupling device at a Schnittfüh tion according XIXA-XIXA in Fig. 19B;

FIG. 19B shows a radial section according to XIXB-XIXB in FIG. 19A;

Fig. 19C is the half section XIXC in Fig. 19B;

FIG. 19D shows the half section XIXD according to FIG. 19B;

FIG. 20A is a Figure 19A is similar to the half-section view of a further embodiment of the coupling device according to XXA in Fig 20B..;

FIG. 20B is a front view according to the XXB werkzeugmaschi nenseitigen coupling portion of the embodiment of FIG. 20A;

FIG. 20C shows a half section according to XXC in Fig 20B.

FIG. 21A is a half section of a further embodiment of a machine tool side coupling part of the Kupp averaging device at a cutting guide according XXIA in Fig 21B.

FIG. 21B shows an end view of the coupling part according to FIG. 21A;

FIG. 21C shows a half section according to XXIC in FIG. 21B;

FIG. 22A is a radial half section of a further exporting approximate shape of the coupling device;

FIG. 22B is a partial view of the end portion of the tool system module shown in Fig. 22A;

Fig. 23 is an axial half-section of another embodiment of the coupling device;

FIG. 24A and 24B axial half-sections of two further embodiments of the coupling device;

FIG. 25A an axial half section of a further embodiment of the coupling device abgewan punched with pre satzflansch;

FIG. 25B is a partial view according to XXVB in FIG. 25A;

. Figs. 26A and 26B of Figure 25 are similar views of a further embodiment of the coupling device; and

FIG. 27A and 27B are axial sections of a final execution form of the coupling device, wherein in Fig. 27A and dissolved in Fig. 27B, the locked position of the coupling device is shown.

In Fig. 1, reference number 2 denotes a tool system module, such as a basic tool holder, and reference number 4 denotes a machine tool spindle, such as the spindle of a grinding machine. The coupling device to be described in more detail below relates to the interface between these two components, one of which represents any tool system module and the other represents a supporting part of a machine tool.

To enable an automatic change of the tool system module, this has a gripper groove 6 , which can be designed in a conventional manner. The clutch device to be described in more detail below must be able to press the components firmly against one another in predetermined radial and axial positioning. Another important criterion is that the coupling can be easily released while achieving the smallest possible excavation distances. For this purpose, the coupling device has the following structure:

The tool base holder 2 , which is shown in detail in FIGS. 2A and 2B, has a radial ring surface 8 and a centering surface 10 , which is formed on the outside of a centering cylinder 12 . The surfaces 8 and 10 have corresponding counter surfaces 14 and 16 on the spindle side, which are shown in detail in FIG. 3. The surface 14 is in turn formed as a radial ring surface and the surface 16 is part of a centering receptacle for the centering cylinder 12 . In this way, a pair of flat surfaces is created, which can be formed continuously or uninjured.

The release and press-in of the clutch is carried out as in a large number of conventional coupling devices by a centrally received in the spindle 4 actuating rod 20 , which can be pressed to the left against the force of a spring assembly, not shown, in the illustration according to FIG. 1. Via the actuating rod 20 , a wedge gear 22 is actuated via the clamping elements 24 are controlled. As clamping elements 24 , six clamping claws are provided at a uniform angular distance of 60 ° to each other, which clamp-like bridge the joint between the parts 2 and 4 to be coupled. The clamping claws have a claw section 26 lying radially inside the centering cylinder 12 , an adjoining rod section 28 and a hook-shaped end section 30 which engages in a groove which is axially fixed with respect to the spindle. By attacking a thrust cone 34 , the clamping elements 24 can be pivoted with their claw sections 26 into a groove-like recess 36 in the centering cylinder 12 while supporting their hook-shaped end sections 30 in the groove 32 and thereby generate an axially directed contact force between the basic tool holder 2 and the spindle 4 .

To transmit torques between the spindle 4 and the tool system module 2 , a claw toothing is provided, which will be described in more detail below. 2A and 2B as seen from the Fig., Is incorporated relieving a diametrically extending drive slot 38 in the Zentrierzy 12, that is ground so that two plane surfaces Passungs- built 40. In this groove-like recess correspondingly shaped driving claws 42 engage, which are formed on a driving ring 44 in the embodiment shown.

The driving ring is shown in detail in FIG. 4.

It has a cylindrical fit surface 46 for the fit engagement with the cylindrical surface 16 of the spindle 4 , a radial surface 48 for flat contact with a shoulder surface 50 of the centering receptacle 18 of the spindle 4 and a driving extension 52 for engagement in an axial recess adjoining the shoulder 50 54 in the centering fixture 18 . The entrainment extension 52 essentially has a polygonal profile, and it has been shown that it is advantageous to lean the entrainment extension against a prism design with three edges. The entrainment me just like the recess 54 has three convexly curved outer surfaces 56 which merge into each other via rounded portions 58 . In this way, the driving extension 52 is given a design which is similar to a K-profile which is used in mechanical engineering as a form-fitting shaft-hub connection.

For axially fixing the driving ring 44 , this has a radial inner shoulder 60 , against which sections 62 of a clamping body 64 (see FIG. 6) can be pressed. For this purpose, the clamping body has a threaded section 66 with which it can be screwed into the spindle 4 . The holding section 62 is essentially sleeve-shaped in order to leave enough space inside for the actuating rod 20 . In the end portion facing away from the thread 66 , the clamping body 64 has a hexagon recess 68 in order to facilitate screwing ben into the spindle 4 .

It can be seen from the illustrations according to FIGS. 1 and 6 that the clamping jaws are guided in the clamping body 64 24. For this purpose, a number of Füh approximately 70 recesses are provided between the holding portions 62 corresponding to the number of clamping claws, in which the clamping claws 24 are guided radially movable with a clearance fit. For this purpose, the groove base of the guide recesses 70 slopes down toward the tool system module 2 , so that the clamping claws can carry out a limited pivoting movement in the radial direction within the guide recesses 70 . The groove base 72 is indicated by the dashed line in FIG. 6A.

In order to fix the clamping claws 24 in the axial direction on the spindle 4 , a support groove 74 is provided in the driving ring 44 , the front groove wall 74 of which - as can be seen from FIG. 1 - in the coupled state of the parts 2 and 4 in flat contact with the hook-shaped end section 30 the respective clamping claw 24 stands. To enable the above-mentioned restricted pivoting movement of the clamping claws 24 , the support groove 74 is formed wider than the hook-shaped end section 30 .

In FIG. 5, details of the design of the clamping jaws 24 are removed. A sleeve-shaped, rotationally symmetrical body 78 serves as a blank in the production of such clamping claws, from which the corresponding clamping claws 24 are then cut out, as can be seen in the upper part of FIG. 5B. The hook-shaped end section 30 has two conical surfaces 80 and 82 in order to enable the pivoting movement in the guide recess 70 of the clamping body 64 . The claw section 26 is also formed on its outside by two conical surfaces 84 and 86 , of which the conical surface 86 can be brought into flat contact with a flank 88 (see FIG. 2B) of the groove-like recess 36 in the centering cylinder 12 . The other conical surface 84 of the claw portion 26 drops to the tool system module 2 from out, whereby it is achieved that, in particular in cooperation with a chamfer 90 on the end face of the centering cylinder during insertion of the centering cylinder in the center mount 18 forcibly Nachinnenschwenken the clamping jaws 24 it follows 12th

It can be seen from the illustration according to FIG. 1 that the dimensions of the clamping claws 24 are adapted to the design of the groove-like recess 36 and the support groove 74 , which creates the largest possible contact between the functional surfaces. From Fig. 1 it is also ersicht Lich that the hook-shaped end portion 30 of the respective clamping elements 24 in cooperation with the guide Ausneh tion 70 is constantly fixed in the radial direction, whereby tilting of the clamping claws 24 is effectively counteracted.

The size of the axial force to be generated can be influenced by the inclination of the conical surface 86 . A further possibility of influencing exists through the design of the thrust cone 34 in cooperation with the associated support surface 92 on the part of the clamping claws 24 . In this way, a two-stage translation of the tensile force of the actuating rod 20 introduced in the axial direction is possible. In the embodiment shown, the support surface 92 is convex, so that a line-shaped contact between the thrust cone 34 and support surface 92 takes place. This design enables the thrust cone 34 to be self-centered and thus a lateral force-free introduction of the axial pressure force into the two components to be coupled. In order to give the thrust cone 34 the radial degree of freedom required for this, the actuating rod 20 is not fixed radially in the region of the interface. It extends with radial play through an inner recess 94 (see FIG. 6A) of the clamping body 64 . The inner recess 94 has a groove 96 for receiving an elastic ring, for example an O-ring 98 , which is preferably linearly supported on a cylindrical coupling projection 100 of the thrust cone 34 . The outer diameter of the coupling projection 100 is thus also smaller than the inner diameter of the inner recess 94 in the clamping body 64 , so that a damped radial mobility of the thrust cone 34 relative to the spindle 4 remains. Via the coupling set 100 there is also the connection to the actuating rod 20 , for which purpose an internal thread 102 is provided. On the side facing away from the internal thread 102 , the thrust cone 34 has a flat surface 104 in which a plurality of recesses 106 are provided for the engagement of a suitable tool.

Coaxial to the internal thread 102 , a further internal thread 108 is provided for receiving a threaded section 110 of a hollow pin 112 , which can engage with a fit in a bore 114 in the basic tool holder 2 . On the outside of the hollow pin 112 , two annular grooves 116 are provided for receiving sealing rings 118 in order to prevent lubricant or coolant from penetrating into the space 124 radially inside the centering cylinder when a lubricant is supplied through a longitudinal recess 120 and an inner recess 122 of the hollow pin 112 To prevent 12 .

From the foregoing description it is apparent that 26 is accomplished under the control of the operating rod 20 forcibly thrusting the claw sections in the groove-like recess 36 into it, whereby a multi-translated axial pressing force in the area of the radial ring surfaces can be produced 8 and fourteenth When the operating rod 20 according to Fig. 1 moves to the left, the clamping claws 24 are free of forces, the clamping jaws 24 can radially pivot so far inward that the respective radially outermost point of the claw portion inner half of the internal diameter D ₁₂ of the centering cylinder 12 (see Fig comes to lie. 2A). The conical surfaces 84 and 86 on the claw section 26 ensure that when the centering cylinder 12 is pulled out, the clamping claws are forced to pivot inwards. To additionally support this movement of the clamping claws, an elastic ring 126 is indicated in FIG. 1, which is received in grooves 128 (see FIG. 5A) and prestresses the clamping claws 24 radially inwards.

From the above description it is apparent that the coupling device is not only able to apply large axial clamping forces evenly distributed over the circumference, but also that the functional surfaces required for this purpose are optimized by the spatial separation of the components for transmitting the axial forces and the circumferential forces can be done. This has the further advantage that the coupling device can also be used to index a tool system module in predetermined angular increments with respect to the machine tool. For this purpose, reference is again made to FIG. 4, from which it can be seen that the plane of symmetry E _{S of} the catch claws 42 includes an angle of 30 ° with an axial plane E _A through an edge cutting tel 130 of the driving extension 52 . This means that the basic tool holder can be positioned in partial steps of 30 ° with respect to the spindle 4 .

The manner in which the coupling device described above is assembled is described in detail below with reference to FIG. 9. First, the clamping claws 24 are threaded with their hook-shaped end sections 30 into the supporting groove 74 of the driving ring 44 and roughly positioned at an even angular distance from one another. This is preferably done in a vertical position. Then the clamping body 64 with its threaded section 66 is pushed radially inside the clamping claws 24 through the driving ring 44 , to the extent that the star-shaped holding section 62 abuts against the inner shoulder 60 of the driving ring 44 . In this state, the clamping claws 24 are already held positively in the driving ring 44 . Now the entirety of the driving ring 44 clamping claws 24 and clamping body 64 is inserted into the centering receptacle 18 and fastened by screwing in the threaded section 66 into a corresponding internal thread 132 of the spindle 4 in such a way that the driving extension 52 engages positively in the recess 54 and a flat contact between the shoulder surface 50 of the spindle 4 and the radial surface 48 of the driving ring 44 is formed. After inserting the elastic ring 98 into the groove 96 , the actuating rod (not shown in FIG. 9) is screwed to the coupling extension 100 of the thrust cone 34 , whereupon the hollow pin 112 shown in FIG. 8 is in turn connected to the thrust cone 34 . When the operating shaft against the aforementioned spring assembly in the representation according to FIGS. 1 and 9 is displaced to the left, the thrust cone reaches 34 out of engagement with the support surfaces 92 of the jaws 24, whereupon the tool base holder 2 can be attached to the spindle 4 .

In Fig. 10, the state of the coupling device at the beginning of Ankupplungsvorgangs is illustrated. For reasons of simplification, the actuating rod is omitted. The sealing rings 118 on the hollow pin 112 are also not shown in the drawing. The thrust cone 34 assumes its left end position in this position, so that the clamping claws 24 can be pivoted radially inward far enough that the centering cylinder 12 of the basic tool holder 2 can be pushed over the claw sections 26 , as shown in FIG. 11 is. At the same time, when inserting the centering cylinder 12 into the centering receptacle 18 of the hollow pin 112 into the bore 114 of the basic tool holder 2 , a fluid-tight sealing of the space 124 to the bore 114 takes place via the (not shown) sealing rings. Under the centering action of the surface 10 , the radial ring surfaces 8 and 14 are pushed towards one another in a plane-parallel orientation. Finally, the driving claws 42 engage in the driving groove 38 , whereupon the ring surfaces 8 and 14 can be brought into contact with one another.

This state is shown in the illustration according to FIG. 12. By releasing the actuating rod, which is not shown, the spring assembly, which is also not shown, takes effect and attempts to move the actuating rod together with the thrust cone 34 to the right according to FIG. 12. Here, the thrust cone slides onto the support surface 92 and presses the claw portions 26 radially outward evenly. During the pivotal movement of the clamping claws 24 in the guide recesses 70 of the clamping body 64 , the hook-shaped end sections 30 are constantly held in position in the support groove 74 of the driving ring 44 . Preferably, the coordination of the geometric conditions is such that, in the tensioned state, a flat contact of both the hook-shaped end section 30 and the claw section 26 takes place on the respective counter surfaces 76 and 36 , respectively.

Finally, the components of the coupling device in the coupled state assume the position according to FIG. 1, the thrust cone having a self-centering effect due to the radially elastic mounting of the coupling projection 100 in the clamping body 64 .

In Fig. 13 a further embodiment of the coupling device is shown, which, however, differs only in a few points from the previously described embodiment. For this reason, only those reference numerals are included in this figure that are required to explain this variant. Those components of the coupling device that are directly comparable with the components described above are provided with corresponding reference numbers, which are supplemented by a "/".

The first modification of the embodiment shown in Fig. 13 is that on the side of the spindle 4 'a centering ring 140 is provided, which is preferably fixed in the radial direction adjustable on the end face of the spindle 4 . This is indicated by the stichpunktier te line 142 . This design makes it possible to adjust the concentricity of the tool system module 2 '. The centering ring 140 is preferably made of hardened steel or hard metal in order to keep wear and tear as low as possible.

A further modification compared to the embodiment shown in FIGS . 1 to 12 is in the region of the hollow pin 112 '. Deviating from the previously described embodiment, the hollow pin 112 is now firmly connected to the tool system module in the form of a basic tool holder 2 '. The projecting end is received with a fit in an inner bore 144 of the thrust cone 34 ', in turn sealing rings 118 ' can be used. It can be seen that with this design the excavation path for releasing the parts 2 'and 4 ' can be limited to the length of the centering cylinder 12 '.

Deviating from the illustrated embodiment, it is also possible to work with radially inwardly cranked clamping claws 24 , in order to be able to engage in this way while maintaining the support of the hook-shaped end sections 30 in a groove-like recess of a centering cylinder 12 which has a reduced diameter. In this case, it is useful to work with an intermediate ring which is inserted into the centering receptacle 18 of the spindle 4 and has an inner diameter which corresponds to the outer diameter of the reduced centering cylinder. This variant makes it possible to couple tool system modules of very different diameter levels in a small space at one and the same interface to the machine.

In a further modification of the embodiment shown it is of course also possible that Coupling system for coupling other machines or Pull tool parts. So is the system with stationary tools, e.g. for turning tools, applicable.

In the described embodiment, six clamping claws 24 are provided. Of course, it is also possible to vary the number of clamping claws, but the number "3" should not be undercut in order to distribute the axial force as evenly as possible over the circumference.

From the description it is clear that the coupling device described is also suitable for retrofitting conventional machine tools. All that is required for this is that a spindle attachment flange is attached, which is then equipped with the centering receptacle 18 .

Another embodiment of the Coupling device described, which additionally with a  Flushing channel system is equipped. For the sake of simplicity are used for those components that work with the parts of the Comparable embodiment described above are used, identical reference numerals.

In FIG. 14, reference number 2 denotes a tool system module, such as a basic tool holder, and reference number 4 denotes a machine tool spindle, such as the spindle of a grinding machine.

The clutch is released and engaged in the same way Way as in the embodiment described above men.

To transmit torques between the spindle 4 and the tool system module 2 , a claw toothing is provided, which will be described in more detail below. In the centering cylinder 12 16 a diametrically extending drive slot 38 is shown in FIG. Incorporated, that is ground so that two Passungs-planar surfaces to form 40. In this groove-like recess correspondingly shaped te driving claws 42 engage, which are formed on a driving ring 44 in the embodiment shown.

For the design of the driving ring, reference can be made to the description of FIG. 4. Fig. 18 reveals the common structural details.

Fig. 14, it does not recognize from the illustration in detail, that the clamping jaws are guided in the clamping body 64 24. For this purpose, a number of guide claws corresponding to the number of clamping claws are provided between the holding sections 62 , in which the clamping claws 24 are guided in a radially movable manner with a clearance fit. Furthermore, a groove base 70 of the recesses for the tool system module 2 is sloping so that the clamping claws can carry out a limited pivoting movement in the radial direction within the guide recesses. The bottom of the groove is indicated by the dashed line in FIG. 14.

Details of the design of the clamping claws 24 result from the description of FIGS. 5A and B.

A hollow pin 112 is fixedly connected to the tool system module 2 . The projecting end is received with a fit in an inner bore 144 of the thrust cone 34 , with sealing rings 118 being provided on the side of the hollow pin 112 . It can be seen that with this design the excavation path for releasing the parts 2 and 4 can be limited to the length of the centering cylinder 12 .

From the foregoing description it is seen that in accordance with the above-described exporting approximately, for example under the control of the operating rod 20 a forced thrusting of the claw portions 26 takes place in the groove-like recess 36 into it, thereby generating a multi-translated axial pressing force in the region of the radial annular surfaces 8 and 14 can be.

The further embodiment is assembled accordingly chend the coupling device described above.

In a departure from the embodiment already described, a centering ring 140 is provided on the spindle 4 side, which is preferably fastened in the radial direction in an adjustable manner on the end face of the spindle 4 . This design makes it possible to adjust the concentricity of the tool system module 2 . The centering ring 140 is preferably made of hardened steel or hard metal in order to keep wear and tear as low as possible.

In order to achieve a cleaning effect of the functional surfaces of the coupling parts which can be brought into engagement with one another, a compressed air flushing channel system to be described in more detail below is provided. Here, compressed air from a source, not shown, is fed to an annular channel 300 between the pull rod 20 and the spindle 4 . The annular channel 300 opens into a compressed air supply space 302 , as is shown by the arrows in FIG. 14. A compressed air purge flow is generated in two branches from the common compressed air supply space 302 . The one compressed air branch flow passes through an intermediate space 304 between the tie rod 20 and the guide body 64 into several longitudinal recesses 306, preferably evenly distributed over the circumference, on the outside of the coupling projection 100 of the thrust cone 34 . From there, the flow reaches the front of the guide body 64 and escapes between the guide body 64 and the back of the thrust cone 34 in the radial direction to the outside, whereby the claw sections 26 can be cleaned with compressed air.

The other compressed air branch flow arrives from the compressed air supply space 302 in preferably a plurality of axial notches 308 in the area of the thread of the guide body 64 . Via the axial notches 308 , an annular space 310 is supplied, which is sealed via a sealing ring 312 between the guide body 64 and the driving ring 44 to the clamping claws 24 . From the annular space 310 preferably run in the circumference evenly distributed discrete branch channels 314 , each opening into a longitudinal groove 316 on the outside of the driving ring 44 . The compressed air flow branches again at the front end of the longitudinal groove 316 . Compressed air passes through a ring array 318 through a plurality of compressed air flushing channels 320, which are preferably uniformly distributed over the circumference, to radial ring surface segments 14 A ( FIG. 15), via which the tool system module 2 is supported on the spindle 4 . The compressed-air rinsing channels 320 are designed so that the Mündungsöff openings 322 substantially in the middle of the radial ring surface segments 14 A emerge. It can be seen from the depicting lung shown in FIG. 14 in that the radial annular surface segments 14 A are formed by diametrically extending grooves are introduced into the end faces of the spindle 324th In this way, lead to dirt chambers which counteract a contamination of the functional surfaces 14 A.

From the annular space 318 , a further cleaning pressure flows from the air to the inner cylinder surface 16 , as shown by the arrows in FIG. 14. This partial flow is generated in that a coordination of the inside diameter of the centering ring 140 is carried on the outer diameter of the Mitnah merings 44, so that an annular gap is formed 326th

From the description it is clear that when the parts 2 and 4 to be coupled are brought together, the compressed air emerging from the compressed-air flushing channels 320 is accelerated more and more as the parts 2 and 4 approach each other, which increases the cleaning effect of the flat surface segments 14 A and the annular surface 8 becomes. In the completely moved-together state of parts 2 and 4 , the orifices 322 are closed by the flat surface 8 , so that a further escape of compressed air is prevented and energy is thus saved. After completing the coupling process, the compressed air supply is switched off.

Deviating from the illustrated embodiment, it is also possible to work with radially inwardly cranked clamping claws 24 , in order to be able to engage in this way while maintaining the support of the hook-shaped Endabschnit 30 in a groove-like recess of a centering cylinder 12 , which has a reduced diameter. In this case, it is useful to work with an intermediate ring which is inserted into the centering receptacle 18 of the spindle 4 and has an inner diameter which corresponds to the outer diameter of the reduced centering cylinder. This variant makes it possible to couple tool system modules of very different diameter levels in a small space at one and the same interface to the machine.

Subsequently to FIGS. 19A to 19D made reference, in which a further embodiment of the Kupplungsvor shown direction. For the sake of simplicity, those components of the coupling device, which essentially correspond to the components of the above-described embodiment, are identified with identical reference numerals. The essential difference between the embodiment of FIG. 19 and the embodiments described above is that no driving ring 44 is provided, that the driving in the circumferential direction is carried out by specially designed driver blocks and that a Vorzentrierungsein direction is provided.

An undercut support groove 474 is provided in the spindle 4 for a hook-shaped end section 430 of the clamping elements 424 , of which eight deviate from the exemplary embodiments described above. The clamping elements 424 are stabilized in the axial direction by means of radial webs 435 in a coupling projection 500 of a thrust cone part 434 , which is firmly screwed to the actuating rod 20 and secured by means of a countersunk hollow screw 433 . The thrust cone body 434 forms on the outside between the coupling projection 500 and a hollow cylindrical extension 512 , which cooperates with a Passungsboh tion 514 in the tool system module 2 , two conical surfaces 434 A and 434 B at an angle to one another, the latter of which forms a smaller angle with the central axis than the area includes 434 A. With this design, the actuating path of the actuating rod 20 can be reduced by a relatively rapid outward movement of the claw sections 426 via the surface 434 A before the actual contact pressure is generated via the surface 434 B.

The thrust cone part 434 has in the region of its two end sections cylindrical fitting surfaces 513 and 501 , of which the former cooperates with the fitting bore 514 and the latter with a bore section 401 of the spindle, which on the side facing away from the tool system module 2 into a recess 403 expanded. Correspondingly, the fitting bore 514 widens into a recess section 515 . The hollow cylindrical extension 512 is in engagement with the fitting bore 514 via a seal. Another seal 498 is provided between the bore portion 401 and the coupling boss 500 .

FIG. 19A shows the components of the Kupplungsvorrich tung in the released state of the clutch by the Actuate the supply rod 20 is displaced to the left. About the surface pairing 401 and 501 , the thrust cone part 434 and thus the hollow cylindrical extension 512 to the spindle 4 is centered, so that the mating surface 513 , which is preferably spherical or spherical, can form a centering aid for coupling the tool system module 2 . When the actuating rod 20 is released and thus shifted to the right as shown in FIG. 19A, the cylindrical fitting surface 501 disengages from the bore section 401 , so that no more constraining forces are exerted on the thrust cone part 434 because the fitting surface 513 comes to rest in the recess section 515 . The actuating rod 20 is thus mounted together with the thrust cone part 434 floating freely in the tool spindle 4 when the clamping force is applied. The positive centering of the thrust cone part 434 is preferably canceled at the start of the generation of the pressing force.

An additional centering aid is provided in the embodiment according to FIG. 19 by a special design of the end region of the centering cylinder 12 of the tool system module 2 . The centering surface 10 merges via a notch into a spherical end section 412 , which is preferably spherical, the diameter of the ball enveloping section 412 being slightly, for example a few 1/100 mm smaller than the inner diameter of the mating surface on the machine tool-side coupling part 4 .

The entrainment between the parts 4 and 2 in the circumferential direction takes place via a pair of diametrically arranged driver bodies or driver blocks 550 , which are received in a radial groove 552 of the spindle 4 and are screwed there. In the driver bodies 550 , slots 554 are formed radially on the outside, through which the shaft of the fastening screw 556 in question extends. With the radially inner areas, the driving bodies 550 engage in driving grooves in the centering cylinder 12 , which are not specified. The driver body 550 he also extend through an axial extension 562 of a centering ring 560 , which serves as a wear ring and for this purpose can be made of wear-resistant material, such as hard metal. The centering ring 560 is firmly screwed to the spindle and forms the above-described, raised radial ring surface segments 14 A , against which the radial ring surface 8 of the tool system module 2 is pressed. In alignment with the fastening screws 556 , the centering ring 560 has threaded bores 564 which can be closed by means of grub screws 566 . With the tool system module 2 removed and the grub screw 566 removed, this construction makes it possible to replace the driver blocks 550 without having to remove the centering ring 560 .

526 in turn denotes an elastic ring, for example in the form of a worm spring, with which the claw sections 426 are biased radially inwards.

It can be seen from the illustration according to FIG. 19 that a rinsing channel system for cleaning the functional surfaces which can be brought into engagement is formed on the components of the coupling device to be coupled. For this purpose, a radial channel 570 is formed between the driver block 550 and the centering cylinder 12 on the one hand and an opening in the centering ring 560 on the other. This radial channel opens into an annular space 572 (Fig. 19C and 19D) to the Radialringflächenseg elements of the plurality of branch channels 574 emanate 14 A. Furthermore, additional Leckölbohrun gene 576 to pockets between the radial ring surface segments 14 A are performed.

In Fig. 20, a further embodiment of the coupling device is described, which differs from the previously described embodiment according to FIG. 19 only in that the entrainment between the spindle 4 and the tool system module 2 takes place in a radially outer area, with no additional Zen trier ring is provided. With regard to the parts which correspond to the embodiment according to FIG. 19, reference is made to the above description. As in the following, identical functional parts are provided with the same reference symbols.

For entraining between de 18861 00070 552 00004 18742n 001000280000000200012000285911875000040 0,002,003,807,140 parts 2 and 4 4 T-nuts 580 are provided on sides of the spindle, the th in Radialnu 582 Passungs an end face 584 are received and screwed there. These sliding blocks can be designed as is the case with steep taper couplings according to DIN 2080 or DIN 69871. The fit end face 584 in turn has raised radial ring surface segments 14 A , against which the radial flange of the tool system module 2 rests. With 586 branch channels are referred to, which start from the radial annular surface segments 14 A and lead to an annular space 588 , which can be fed with a flushing pressure medium. From this annular space 588 , further channels 589 extend radially within the sliding blocks 580 , which provide an outlet for leakage oil and via which air-congestion ventilation can take place.

The embodiment according to FIG. 21 differs from that according to FIG. 20 basically only in that an additional centering ring 590 is incorporated between sliding block 580 and spindle 4 . Radial grooves 592 for receiving the sliding blocks 580 are formed in the end face of the centering ring. 596 denotes compressed air flushing channels which extend essentially axially through the centering ring 590 and emerge in the region of the radial ring surface segments 14 A of the centering ring 590 . 599 denotes channels which correspond to channels 589 in the embodiment according to FIG. 20.

In the embodiment according to FIG. 22, entrainment between spindle 4 and tool system module 2 takes place via recesses 38 in the region of the end face of centering cylinder 12 . For driving 4 driver bodies 604 are attached to a shoulder 602 of the spindle, which engage with a fit in the driving grooves 38 of the centering cylinder 12 . A plurality of radial bores 606 extend from the shoulder 602 , from which branch channels 608 are guided to radial ring surface segments (not shown in detail) of the end face 614 of the spindle 4 , in order to form the pressure medium flushing system for cleaning the functional surfaces of the coupling device. Only one of the radial bores 606 is open to the outside for the supply of pressure medium.

In the embodiment according to FIG. 23, entrainment takes place in the direction of rotation between spindle 4 and tool system module 2 by means of a driver ring 620 , which has at least two radially inwardly facing driver lugs 622 which engage in correspondingly shaped grooves on the connecting flange of the tool system module 2 . The Zentrie tion takes place with the aid of a centering ring 630, which is overlapped by the catch lugs 622nd Instead of a ring, two hook-shaped driver blocks can also be provided.

The embodiment according to FIGS. 24A and 24B corresponds essentially to the embodiment according to FIG. 19 in terms of entrainment between the parts to be coupled in the circumferential direction . Comparable parts in this regard are provided with identical reference numerals as in FIG. 19. In this embodiment too, driver blocks 550 are exchangeably fastened by means of fastening screws 556 in a groove 552 of the connecting flange of the spindle 4 . The centering cylinder 12 is extended by means of the centering ring 560 , which in turn can be made of wear-resistant material.

In the embodiment according to FIG. 24A, the centering cylinder 12 is formed on a base receiving part 640 for a modular tool 650 , whereas in the embodiment according to FIG. 24B the centering cylinder 12 is part of a solid tool 660 . The modular tool 650 can be tensioned with the aid of a pendulum pin 652 against the base receiving part 640 by a fastening screw 654 being brought into press contact with a wedge surface 656 of the pendulum pin 652 , which is supported on a cone 659 via a spherical surface 658 .

In contrast to the previously described exemplary embodiments, no double pre-centering takes place in the embodiments shown in FIG. 24. Derogation is also the design of the thrust body - or cone part and the clamping elements, which will be discussed in more detail below.

The one denoted 734 thrust cone part has radially inwardly of the functional surfaces 734 A and 734 B is a zylin derförmige recess 736 in which a hollow piston is guided 738 sealingly, which constantly by a spring 740 with its spherical sealing surface 742 against a cone 744 either in the shuttle pin 652 or in the solid work tool 660 is pressed. This design allows a central lubricant supply to the tool system module through the interior of the operating rod 20th

Instead of the elastic ring 26 , 126 and 526 provided in the embodiments described above, in the embodiments according to FIGS. 24A and 24B, a forced movement control of the clamping elements denoted by 724 takes place , in order to ensure that the claw sections 726 are displaced when displaced the actuating rod 20 to the left, ie when releasing the coupling device, reliably move out of engagement with the groove-like recess 36 in the centering cylinder 12 . For this purpose, on the side facing away from the tool system module 2 of a coupling projection 800 of the thrust cone part 734, a stabilizing body 746 is guided, which can be pressed by means of a spring 748 against a rear oblique control surface 750 of the clamping elements 724 . The clamping elements 724 are supported with their hook-shaped end sections 730 in a support groove 774 of the spindle 4 and with a spherical section 731 on the coupling projection 800 . In the stabilizing body, a number of slots 747 corresponding to the number of clamping elements 724 are formed, into which fitting-side guide ribs 725 of the clamping elements 724 engage. It can be seen from the illustration in Fig. 24A and 24B that, by displacement of the actuating rod 20 and thus the thrust cone part 734 to the left (Fig. 24A) under the action of the spring loaded stabilization body 746 a Nachuntenschwenken of the claw portion 726 is carried out.

Another embodiment is shown in FIG. 25. In this embodiment, a support groove 874 for the hook-shaped end sections 830 of clamping elements 824 is formed between the spindle 4 and an attachment flange 880 , which engages with corresponding lugs 882 in corresponding recesses 884 in the tool system module 2 . The thrust cone part is formed on the left end side in accordance with the embodiments according to FIGS. 19 to 23, so that the tool system module to be coupled can be precentered.

In order to form a flushing channel system which serves at the same time for ventilation, a helical groove 886 is formed in the attachment flange 880 in the area of the cylindrical fitting area and can be fed via an air channel bore 888 . The helical groove 886 is in communicating connection with a spiral groove 890 in the flat surface 814 of the attachment flange 880 , so that at least one cleaning channel is formed via the air duct bore 888 and the grooves 886 and 890 .

In contrast to the previously described embodiments, in the embodiment according to FIG. 25 the clamping elements 824 are stabilized by means of a positioning pin 825 attached at the end, which engages in an axial slot 827 on the coupling attachment 900 of the thrust cone part 834 . With 829 an elastic ring is designated, through which the radial prestressing of the clamping elements 824 takes place.

The embodiment according to FIG. 26 differs from the embodiment according to FIG. 25 only in the configuration of the device for the entrainment in the circumferential direction. In this embodiment, the tool system module 2 rests directly on the spindle 4 . The entrainment takes place via driver body 950 , for which a recess 952 is provided in the tool system module 2 and which are formed in one piece with a centering cylinder section 954 . With this centering cylinder section, the centering cylinder 12 fits into engagement. From an annular space 956 , which is fed with cleaning compressed air via at least one radial bore 958 , branch channels 960 emanate from them, which - as described several times above - emerge at the mating surfaces to be cleaned between components 2 and 4 .

The cleaning of the cylindrical fitting surfaces between centering cylinder 12 and centering cylinder section 954 is carried out by a helical groove 962 in the centering cylinder section 954 .

Finally, reference should also be made to the embodiment according to FIG. 27, which corresponds to the embodiment according to FIG. 24 with regard to the entrainment between the parts to be coupled in the circumferential direction. Different is the design of the clamping elements 924 , and the intended Stabilisierungseinrich device and the training of the central lubricant supply channel.

With 934 a thrust cone part is designated, which in turn is connected to a coupling approach 1000 with the hollow actuating rod 20 . The thrust cone part 934 has a fitting bore 936 on the side facing the tool system module 2 , into which a hollow pin 938 can be inserted in a sealing manner and which is fastened to the tool system module 2 .

The clamping elements 924 are supported with their hook-shaped end sections 930 in a supporting groove 974 of the machine tool spindle 4 . On the side of the clamping elements 924 facing away from the claw portions 926 , guide ribs 925 are formed which engage with a fit in slots 947 of a stabilizing body 946 . In the area of the guide ribs 925 , a cam surface 948 is formed on the outside of the coupling set 1000 , along which a control section 949 of the guide ribs 925 can slide. In the coupling state, the control section 949 is completely accommodated in a recess 945 of the coupling attachment 1000 (see FIG. 27B). When the operating rod 20 according to Fig. 27A moves to the left, the cam surface 948 passes in operative engagement with the Steuerab section 949, whereby the claw portions 926 pivoted out of the groove-like recess 36 forcibly.

Of course, further modifications of the coupling device are possible. In particular, combinations of details of the above-described embodiments are possible with one another. It is in particular possible to provide the pre-centering of the embodiments according to FIGS . 19 to 23 without simultaneously using the hollow cylindrical extension for sealing the coolant supply channel. Rather, instead of this seal according to FIGS . 19 to 23, a coolant transfer bolt according to FIG. 13 can also be provided.

Taking the parts to be coupled in the circumferential direction can also be done or improved that the opposite flat surfaces via a spur gear that are either centering or cannot be self-centering. A such spur toothing can on the touching Radial fit surfaces and / or on the only opposite Radial surfaces can be provided, with toothing Intermediate rings can be used.

Deviating from the previously described Ausführungsbeispie len, it is also possible to flush the flushing channel system with media other than compressed air. The extension 12 , 12 'on the tool system module-side part of the clutch device is also not limited to a design in which only cylindrical fitting surfaces are provided. It is also possible to work with conical surfaces in this area. Finally, it is also possible to work in the area of the engagement of the extension with a positive connection to the counterpart on the coupling part on the machine tool side. Here is a cross-sectional shape of the mutually engaging parts any cross-sectional design deviating from the circular cross-section possible.

The actuating body referred to above as the thrust cone per for the clamping elements can of course also one of the illustrated embodiments deviate have the correct shape. Instead of the tapered actuator other surfaces on the thrust cone can also be suitable  nete curve surface find the application either directly with the contact surfaces on the clamping elements or indirectly with the interposition of a suitable other actuator pers acts on the clamping elements. That way any control of the travel for the Spannele elements are achieved, so that, for example, at the beginning of the Return strokes of the actuating rod are relatively quick the claw sections are pivoted outwards, after which a flatter rise in the contact surface pair tion a changed, in terms of high pressure power generation stopped motion ratio is present.

Instead of the variant, according to which the coolant transfer body firmly with the tool system module-side coupling part of it is connected, of course possible such a coolant transfer body to connect firmly to the thrust body, then the Coolant transfer body sealing in a corre sponding appropriately trained inner recess on the part of the factory machine system module engages.

The contact surface portion of the coolant transfer body pers is of course not on a spherical cal, i.e. spherical outer surface limited. It are other surface designs, such as the Formation of a conical surface conceivable, it being advantageous can be in the area of the sealing contact surfaces with additional sealing devices, for example one O-ring to work.

Instead of using a centering ring or attachment it is also made of wear-resistant material conceivable, these components only in the area of Functional surfaces with wear-resistant coatings to provide. In the event that with such wear solid coatings can be worked in different cases also a separate centering ring spare.  

The invention was based on an interface between Tool system module and a machine tool described ben. In an equally advantageous manner, the However, the invention also for an interface between a workpiece, a workpiece carrier, or a work tool carrier and a designated handling unit direction, such as a workpiece or tool Use exchange or transport system, where especially when handling heavy systems Make the most of the benefits.

The invention thus creates a coupling device between a workpiece or tool carrier part, such as e.g. a tool system module, for example in the form a basic tool holder, and a handling unit direction, such as a machine tool, in particular a spindle. For quick production and release of the Connection between these components under provision large axial forces is a clamping device with an actuating rod is provided over which a wedge drives is driven, with the one to be coupled Partly provided clamping elements essentially radially outside in a correspondingly designed recess on other part to be coupled can be pressed. The Spannele elements are at a uniform angle from at least three stood together, clamp-like clamping claws formed essentially parallel to a centering Continuation of the basic tool holder arranged and under Support in a centering of the spindle with a radially inside the centering when coupled continued lying claw section in a groove-like Recess of the centering extension are pivotable. These Coupling device is characterized by high flexibility bility with regard to the possible uses at wirt economic producibility.

Claims (75)

1. Coupling device between a workpiece or tool carrier part, such as a tool system module, for example in the form of a basic tool holder, and a handling device, such as a machine tool, with a holder provided on the machine tool side for an extension of the tool system module and a clamping device for generating a contact pressure between flat surfaces of the parts to be coupled, the tensioning device having an actuating rod via which a wedge gear can be actuated, with which the tensioning elements provided in one part to be coupled can be pressed essentially radially outward into a correspondingly designed recess on the other part to be coupled, characterized in that the clamping elements are formed by at least three clamp-like clamping claws ( 24 ; 424 ; 724 ; 824 ; 924 ) which are arranged at a uniform circumferential spacing and are essentially parallel to the extension ( 12 ; 12 ') of the tool system module ( 2 ; 2 ') arranged and supported in the receptacle ( 18 ) with a in the coupled state radially inside the extension ( 12 ; 12 ') lying claw portion ( 26 ; 426 ; 726 ; 826 ; 926 ) in a groove-like recess ( 36 ) of the extension ( 12 ; 12 ') are pivotable. 2. Coupling device according to claim 1, characterized in that the extension of a Zentrierzylin ( 12 ; 12 ') is formed, for the machine tool tig a centering ( 18 ) of a spindle ( 4 ; 4 ') is provided, and that on the side of the tool system module ( 2 ; 2 ') carrying the centering cylinder of ( 12 ) at least one recess ( 38 ) for at least one driver claw ( 42 ; 550 ; 580 ; 604 ; 622 ; 882 ; 950 ) provided on the receptacle ( 18 ). 3. Coupling device according to claim 1 or 2, characterized in that the flat surfaces ( 8 , 14 ) over which the parts to be coupled can be pressed against one another, are formed by radial ring surfaces ( 14 ; 14 A ). 4. Coupling device according to one of claims 1 to 3, characterized in that the wedge gear ( 22 ) a radially inside the claw sections ( 26 ; 426 ; 726 ; 826 ; 926 ) and with the actuating rod ( 20 ) verbun those thrust body ( 34 ; 434 ; 734 ; 834 ; 934 ), which can be brought into contact with adapted contact surfaces ( 92 ) of the clamping claws. 5. Coupling device according to claim 4, characterized in that the thrust body ( 34 ; 434 ; 734 ; 834 ; 934 ) on the tool system module ( 2 ; 2 ') facing end of the actuating rod ( 20 ) is attached, the stroke provided for releasing the clutch is adapted to the immersion dimension of the claw sections ( 26 ; 426 ; 726 ; 826 ; 926 ) in the groove-like recess ( 36 ) and to the wedge angle design ( 434 A , 434 B ) of the thrust cone. 6. Coupling device according to one of claims 1 to 5, characterized in that the actuating rod ( 20 ) at least during the clamping process ( 20 ) has a radial play in the machine tool-side coupling part ( 4 ; 4 '). 7. Coupling device according to one of claims 2 to 6, characterized in that the clamp-like clamping claws ( 24 ; 424 ; 724 ; 824 ; 924 ) with their claw section opposite end sections ( 30 ; 430 ; 730 ; 830 ; 930 ) in one Support groove ( 74 ; 474 ; 774 ; 874 ; 974 ) of the receptacle ( 18 ) engage, the support groove being adapted to the design of the end sections such that the clamping claws with their claw sections in the groove-like recess ( 36 ) of the centering cylinder ( 12 ; 12 ') and are pivotable out of this. 8. Coupling device according to one of claims 4 to 7, characterized in that the thrust body ( 34 ; 434 ; 734 ; 834 ; 934 ) on the side facing away from the tool system module ( 2 ; 2 ') has a cylindrical coupling projection ( 100 ; 500 ; 800 ; 900 ; 1000 ), via which it can be connected to the actuating rod ( 20 ), preferably can be screwed ver. 9. Coupling device according to one of claims 4 to 8, characterized in that the thrust body ( 34 ; 434 ; 834 ) on the side facing away from the actuating rod ( 20 ) carries a hollow cylindrical extension ( 112 ; 512 , 912 ) which seals in a coaxial Recess ( 114 ; 514 , 515 ; 914 , 915 ) can be inserted in the tool system module ( 2 ). 10. Coupling device according to one of claims 1 to 9, characterized in that the actuating rod ( 20 ) has a continuous longitudinal bore ( 120 ). 11. Coupling device according to one of claims 1 to 10, characterized in that the groove-like recess ( 36 ) in the extension ( 12 ; 12 ') is formed by an annular groove with a V-cross section. 12. Coupling device according to one of claims 1 to 11, characterized in that the clamping claws ( 24 ; 424 ; 724 ; 824 ; 924 ) in the coupled state flat on a flank of the groove-like recess ( 36 ) in the extension ( 12 ; 12 ') invest. 13. Coupling device according to one of claims 7 to 12, characterized in that the clamping claws ( 24 ; 424 ; 724 ; 824 ; 924 ) flat in the coupled state on a flank ( 76 ) of the support groove ( 74 ; 47 ; 774 ; 874 , 974 ). 14. Coupling device according to one of claims 2 to 13, characterized in that the centering receptacle ( 18 ) in the engagement region of the centering cylinder ( 12 ', 12 ) is formed by a centering ring ( 140 ; 560 ; 590 ; 630 ; 880 ; 960 ) which optionally radially adjustable on the spindle ( 4 ', 4 ) is fixed. 15. Coupling device according to claim 14, characterized in that the centering ring ( 140 ; 560 ; 590 ; 630 ; 880 ; 960 ) consists of wear-resistant material, such as hard metal or hardened steel. 16. Coupling device according to one of claims 1 to 15, characterized in that the clamping claws ( 24 ; 424 ; 724 ; 824 ; 924 ) are produced by radially separating a hülsenför shaped body ( 78 ), the radially outwardly projecting annular beads on its end faces ( 26 , 30 ). 17. Coupling device according to one of claims 1 to 16, characterized by a preferably supplied by compressed air flushing channel system ( 300 to 326 ; 570 to 576 ; 586 to 589 ; 596 , 599 ; 604 to 608 ; 886 to 890 ; 956 to 960 ) for cleaning the engageable functional surfaces on the components of the coupling device to be coupled. 18. Coupling device according to claim 17, characterized in that the flat surfaces over which the parts to be coupled can be pressed together, on the tool system module side by a radial ring surface ( 8 ) and on the spindle ( 4 ) side by radial ring surface segments ( 14 A ) or sections are formed, which are preferably separated from each other by diametrically extending grooves ( 324 ) and each have at least one opening ( 322 ) of compressed air flushing channels ( 320 ; 574 ; 586 ; 596 ; 608 ; 960 ). 19. Coupling device according to one of claims 7 to 18, characterized in that the supporting groove ( 74 ) is formed in a in the centering ( 18 ), the circumferential forces on the tool system module ( 2 ; 2 ') transmitting driving ring ( 44 ). 20. Coupling device according to claim 19, characterized in that the driving ring ( 44 ) carries the at least one driving claw ( 42 ) for which a recess ( 38 ) is provided in the end face of the centering cylinder ( 12 ). 21. Coupling device according to claim 19 or 20, characterized in that the centering receptacle ( 18 ) via a radial shoulder ( 50 ) merges into a recess ( 54 ) into which to create a rotationally fixed connection between the machine tool spindle ( 4 ; 4 ') and driving ring ( 44 ) a correspondingly designed entrainment extension ( 52 ) of the entrainment ring ( 44 ) engages in a form-fitting manner. 22. Coupling device according to claim 21, characterized in that the driving extension ( 52 ) is designed like a prism with preferably convexly curved outer surfaces ( 56 ). 23. Coupling device according to claim 21 or 22, characterized in that the driving extension ( 52 ) has a substantially K-profile. 24. Coupling device according to one of claims 20 to 23, characterized in that the driving ring ( 44 ) carries two diametrically arranged driving claws ( 42 ) whose plane of symmetry ( E _S ) with one of the three axial planes ( E _A ) through the edges ( 130 ) of the entraining extension ( 52 ) encloses an angle of 30 °. 25. Coupling device according to one of claims 7 to 24, characterized in that the clamping claws ( 24 ) are guided in the radial direction in axial grooves ( 70 ) of a guide body ( 64 ) which is firmly connectable to the machine tool part of the coupling device. 26. Coupling device according to claim 25, characterized in that the guide body ( 64 ) presses the driving ring ( 44 ) against the radial shoulder ( 50 ) in the centering receptacle ( 18 ). 27. Coupling device according to claim 26, characterized in that the driving ring ( 44 ) in the region of the driving extension ( 52 ) with the guide body ( 64 ) defines a sealed to the clamping claws ( 24 ) with compressed air supplyable annular space ( 314 ), from which vorzugwei se three evenly distributed branch channels ( 314 ) run outwards, each opening in a longitudinal groove ( 316 ) on the outside of the driving ring ( 44 ), with an annular space ( 318 ) for supplying the compressed air flushing channels ( 320 ) in flow connection stand. 28. Coupling device according to one of claims 25 to 27, characterized in that the guide body ( 64 ) in the machine tool-side part ( 4 ; 4 ') of the coupling can be screwed. 29. Coupling device according to claim 28, characterized in that the guide body ( 64 ) in the region of the thread has at least one substantially axially extending notch ( 308 ) for supplying the annular space ( 314 ) with compressed air. 30. Coupling device according to one of claims 17 to 29, characterized in that the thrust cone ( 34 ) on the side facing away from the tool system module ( 2 ) has a cylindrical coupling projection ( 100 ) via which it can be connected, preferably screwed, to the actuating rod ( 20 ) is and that the coupling projection ( 100 ) on its outside has longitudinal recesses ( 306 ) in order to define a further rinsing channel between it and the cylindrical inner surface of the guide body ( 64 ), which has an intermediate space ( 304 ) between the pull rod ( 20 ) and guide body ( 64 ) is fed and is open to the claw sections ( 26 ) of the clamping claws ( 24 ). 31. Coupling device according to one of claims 27 to 30, characterized in that the respective longitudinal grooves ( 316 ) in the driving ring ( 44 ) run radially inside the annular space ( 318 ) and in a cylindrical fitting surface ( 16 ) open, preferably circumferential ring pass over gap ( 326 ). 32. Coupling device according to claim 30 to 31, characterized in that the at least one longitudinal notch ( 308 ) and the intermediate space ( 304 ) between the tie rod ( 20 ) and guide body ( 64 ) emanate from a common compressed air supply space ( 302 ), which via a Ring channel ( 300 ) between the tie rod ( 20 ) and spindle ( 4 ) is supplied with compressed air. 33. Coupling device according to one of claims 25 to 32, characterized in that the cylindrical inner surface of the guide body ( 64 ) has an annular groove ( 96 ) for receiving a radially elastic ring ( 98 ) via which the thrust cone ( 34 ) radially is stabilizable. 34. Coupling device according to one of claims 4 to 33, characterized in that the thrust cone ( 34 '; 934 ) has an axial, central bore ( 144 ; 936 ) into which a coaxial sealing in the tool system module ( 2 '; 2 ) during the coupling process. attached hollow pin ( 112 '; 938 ) is insertable. 35. Coupling device according to one of claims 1 to 34, characterized in that the claw section ( 26 ) has on its outside a wedge flank ( 84 ) which slopes towards the tool system module ( 2 ; 2 '). 36. Coupling device according to one of claims 7 to 35, characterized in that the clamping claws ( 24 ; 424 ; 824 ) are biased inwards by an elastic ring ( 118 ; 118 ';526; 829 ), the ring preferably in one of the Claw portion ( 26 ) adjacent groove ( 128 ) is added. 37. Coupling device according to one of claims 7 to 18, characterized in that the supporting groove ( 474 ; 774 ; 874 ; 974 ) is ausgebil det in a machine tool spindle ( 4 ). 38. Coupling device according to one of claims 7 to 18, characterized in that the supporting groove ( 874 ) of a machine tool spindle ( 4 ) with an attachment flange ( 880 ) is defined. 39. Coupling device according to claim 37 or 38, characterized in that for driving between the parts to be coupled ( 2 ; 4 ) at least two, preferably diametrically opposite driver claws ( 550 ; 580 ; 604 ; 622 ; 882 ; 950 ) are provided in Fit function intervention with correspondingly designed recesses ( 38 ) can be brought in the other coupling part. 40. Coupling device according to claim 39, characterized by a front toothing between the opposite radial surfaces of the parts to be coupled ( 2 ; 4 ). 41. Coupling device according to one of claims 39 or 40, characterized in that the driver claws ( 550 ; 580 ; 604 ; 622 ; 882 ; 950 ) are provided on the coupling part ( 4 ) of the machine tool side. 42. Coupling device according to claim 41, characterized in that the driver claws ( 550 ; 604 ) cooperate with recesses ( 38 ) in the end face of the centering cylinder ( 12 ). 43. Coupling device according to claim 42, characterized in that the driver claws have two in Radialnu th ( 552 ) of the machine tool spindle ( 4 ) received and preferably screwable driver blocks ( 550 ), which are by corresponding, preferably front end recesses ( 571 ) a centering ring ( 560 ), which is attached to the machine tool spindle ( 4 ). 44. Coupling device according to claim 43, characterized in that in the centering ring ( 560 ) openings ( 564 ) are formed through which the fastening screws ( 556 ) of the driver blocks ( 550 ) are accessible. 45. Coupling device according to claim 43 or 44, characterized in that between the centering ring ( 560 ) and driver block ( 550 ) is formed a substantially radially extending flushing channel ( 510 ) which machines in an annular space ( 572 ) between the centering ring ( 560 ) and Werkzeugma -Spindle ( 4 ) opens, from which branch channels ( 574 ) extend to the radial ring surface sections ( 14 A ) to be cleaned. 46. Coupling device according to claim 41, characterized in that the driver claws ( 580 ; 622 ; 882 ; 950 ) cooperate with recesses ( 884 ) in a connecting flange for the tool system module. 47. Coupling device according to claim 46, characterized in that the driving claws have two in Radialnu th ( 582 ) of the connecting flange of the machine tool spindle ( 4 ) and preferably ver screwable driving stones ( 580 ; 950 ). 48. Coupling device according to claim 47, characterized in that the driver blocks ( 950 ) are integrally formed with a centering ring ( 954 ) for the centering cylinder ( 12 ). 49. Coupling device according to claim 48, characterized in that the cylindrical fitting surface of the centering ring ( 954 ) has a helical groove ( 962 ) for guiding the flushing flow and / or a pressure relief or venting flow. 50. Coupling device according to claim 46, characterized in that the driver claws have two in Radialnu th ( 592 ) of a on the connecting flange of the machine tool spindle ( 4 ) centering ring ( 590 ) received driver blocks ( 580 ). 51. Coupling device according to claim 50, characterized in that in the centering ring ( 590 ) substantially axially extending rinsing channels ( 596 ) are formed, which emerge at radial ring surface segments ( 14 A ), via which the surface contact between the parts to be coupled takes place. 52. Coupling device according to claim 46, characterized in that the driver claws are formed by radially inwardly projecting driver lugs ( 882 ) of a spindle front flange ( 880 ) on which the centering surfaces ( 814 ; 816 ) for the tool system module to be coupled ( 2 ) are trained. 53. Coupling device according to claim 52, characterized in that in the centering surfaces ( 814 ; 816 ) with each other communicating grooves ( 890 ; 886 ) are incorporated in order to form at least one flow channel for a rinsing flow and / or relief flow. 54. Coupling device according to claim 46, characterized in that the driver body of radially inwardly facing lugs ( 622 ) of a machine tool spindle ( 4 ) attached driver ring ( 620 ) are formed, which overlaps a centering ring ( 630 ) with its approaches . 55. Coupling device according to one of claims 7 to 18 or 37 to 54, characterized by a pre-centering device ( 412 ; 401 , 501 , 513 , 514 ) for the part of the tool system module to be coupled ( 2 ). 56. Coupling device according to claim 55, characterized in that the pre-centering device has a spherical surface section ( 412 , 513 ) formed at the front end of the centering cylinder ( 12 ) and / or on the thrust body, which is preferably designed spherically with a diameter which is slightly smaller than the diameter of the cylinder fitting surfaces ( 10 , 16 ; 514 ). 57. Coupling device according to claim 55 or 56, characterized in that the pre-centering device has a pair of axially spaced outer surfaces ( 501 , 513 ) of a cone part ( 434 , 500 ) connected to the actuating rod ( 20 ), the tool system module ( 2 ) facing outer surface ( 501 ) can only be brought into mating engagement with an inner recess ( 401 ) of the machine tool spindle ( 4 ) when the actuating rod ( 20 ) assumes a position releasing the coupling, and the other outer surface ( 513 ) remains out of engagement with an inner cylindrical surface ( 514 ) of the tool system module ( 2 ) during the clamping process. 58. Coupling device according to one of claims 8 to 57, characterized in that the coupling projection ( 500 ; 800 ; 1000 ) of the thrust cone is sealed in an interior recess of the machine tool spindle ( 4 ). 59. Coupling device according to one of claims 8 to 58, characterized in that the coupling attachment ( 500 ; 800 ; 900 ; 1000 ) means ( 435 ; 746 ; 827 ; 945 ; 948 ) for lateral stabilization of the clamping claws ( 424 ; 724 ; 824 ; 924 ) carries. 60. Coupling device according to claim 59, characterized in that the stabilizing device is formed by projections ( 435 ) arranged at a uniform circumferential distance on the outside of the coupling attachment ( 500 ). 61. Coupling device according to claim 59, characterized in that the stabilizing device is formed by a plurality of radial slots ( 747 ; 827 ; 947 ) into which guide sections ( 725 ; 825 ; 925 ) of the clamping claws engage with a fit. 62. Coupling device according to claim 61, characterized in that the radial slots ( 827 ) in the coupling approach ( 900 ) are formed. 63. Coupling device according to claim 61, characterized in that the radial slots ( 747 ) are formed in a pressure body ( 746 ) which, via a spring device ( 748 ) presses against a control surface ( 750 ) of the clamping claws, around whose claw sections in the released state Swivel the coupling device out of the groove-like recess ( 36 ). 64. Coupling device according to claim 61, characterized in that the radial slides are formed in a stabilizing body ( 946 ) which is located behind the clamping claws ( 924 ) and into which a cam-like extension ( 925 ) of the clamping claw protrudes, for the approach in the coupling ( 1000 ) a control surface ( 948 , 945 ) is provided in order to cause the claw sections ( 926 ) to pivot out of the groove-like recess when the coupling device is decoupled. 65. Coupling device according to one of claims 58 to 64, characterized in that the thrust body ( 734 ; 934 ) on the side facing the tool system module ( 2 ) has an inner recess ( 736 ; 936 ) in which a coolant transmission body ( 738 ; 938 ) is sealed. is included. 66. Coupling device according to claim 65, characterized in that the coolant transmission body ( 938 ) is fixedly connected to the tool system module-side coupling part ( 2 ), for example screwed. 67. Coupling device according to claim 65, characterized in that the coolant transmission body is formed by a hollow piston ( 738 ) guided in the thrust cone, which is tensioned via a spring ( 740 ) in the direction of the tool system module ( 650 ; 660 ). 68. Coupling device according to claim 67, characterized in that the hollow piston ( 738 ) has a preferably spherical sealing surface ( 742 ) for connection to a central coolant bore in the region of the tool system module ( 2 ). 69. Coupling device according to one of claims 9 and 58 to 64, characterized in that the hollow cylindrical extension ( 512 ; 912 ) has at the end a guide lug ( 513 ; 913 ), behind which a sealing ring ( 518 ; 918 ) is arranged. 70. Coupling device according to one of claims 5 to 69, characterized in that two thrust cone surfaces ( 434 A ; 434 B ) are formed on the thrust cone, of which the thrust cone surface ( 434 A ) which is more distant from the tool system module ( 2 ) has a larger angle with the central axis of the coupling device than the other thrust cone surface ( 434 B ). 71. Coupling device according to one of claims 15 to 70, characterized in that the centering ring ( 560 ; 590 ; 630 ; 880 , 950 ) consists of wear-resistant material. 72. Coupling device according to one of claims 1 to 71, characterized in that the clamping claws ( 424 ; 824 ) are biased radially inwards by an elastic ring ( 526 ; 829 ). 73. Coupling device according to one of claims 1 to 72, characterized in that the extension ( 12 ; 12 ') has cylindrical fitting surfaces, in particular is cylindrical. 74. Coupling device according to one of claims 1 to 72, characterized in that the extension ( 12 ) has tapered fitting surfaces, preferably designed as a cone. 75. Coupling device according to claim 73 or 74, characterized in that the extension ( 12 ) has a cross-sectional design deviating from the circle, via which entrainment takes place in the circumferential direction.