Machining system

Abstract

A machining system with an exchangeable holder (12) which serves as tool holder, and with a holder receptacle (10) for receiving the holder (12). The holder receptacle (10) has a compensation means (24) and a fixing means (16) which is movable by means of an actuating means (18). The compensation means (24) serves on the end side as an axial rest for the holder (12) and in the rearward direction as a spring for resilient support of the fixing means (16).

Description

[0001] processing system

[0002] The invention relates to a machining system, at least consisting of a drivable holder receptacle and a holder provided for receiving a machining tool, which holder has a holder shaft and which can be interchangeably secured in the holder receptacle by means of a securing device, wherein the securing device can be moved from a release position to a securing position and vice versa by means of an actuating device as part of a securing or release process, in which the holder can be inserted into the holder receptacle and removed again or is held in its inserted position in the holder receptacle and retracted with a predeterminable retraction force, wherein the holder has at least one clamping cam arranged on the holder shaft, which comes into contact with or out of contact with an assignable clamping surface of the securing device for a securing or release process.Machining systems of various types are known from the prior art. For example, DE 10 2018 007 084 A1 discloses a machining system comprising a tool holder with a stationary retractable part and a drive unit with a retractable part that can be rotated by means of a retraction device and can be brought into engagement with the retractable part. The tool holder and the drive unit are each provided with a toothing on adjacent, opposite contact surfaces that can be brought into engagement with one another. The axial distance between the toothings can be reduced by rotating the retractable part by means of the retraction device until they contact one another, whereby the tool holder and the drive unit can be axially clamped against one another.Such tool holders are also referred to in technical terms as spindle heads and are used to drive a machining tool in rotation via the tool drive of a tool turret (DE 10 2018 004 677 AI), whereby the disk-like tool turret as a whole can be pivoted to allow machining tools arranged on its outer circumference to be pivoted into a common machining position.

[0003] French patent no. 1 007 956 discloses a tool holder shank with two securing or clamping cams positioned diametrically opposite one another relative to the longitudinal axis of the holder, which have an axial recess between them directed toward a collar of the holder. Behind the clamping cams, each recess transitions into an undercut into which a securing ring, designed as a crown gear, engages. The crown gear can be pivoted via a bevel gearing by means of an actuating device. When the tool holder is mounted in an adapter, i.e., a spindle insert, it can be retracted further into the adapter receptacle by means of the rotatable securing ring via inclined clamping surfaces on the two segment-shaped clamping cams.

[0004] Based on this state of the art, the invention is based on the object of further improving the processing systems known in this regard.

[0005] A machining system having the features of patent claim 1 in its entirety solves this problem. The fact that, according to the characterizing part of patent claim 1, the holder receptacle has a resiliently flexible compensation device that enables tolerance compensation between the holder receptacle and the received holder, at least in the locking position, creates improved torque transmission between the drivable holder receptacle and the holder with the machining tool. In particular, the tolerance compensation always achieves the same elastic deformation during the locking process for a particular type of holder, so that a consistent, defined pull-in force is always generated, which helps improve torque transmission and contributes to relieving the load on the components that handle torque transmission.

[0006] Overall, a modular interface is created for clamping a tool adapter (Weldon, milling arbor, etc.) and a standard collet. The tool adapter, as a holder or carrier for a machining tool, can also be integrally connected to the cutting tool. This modular interface is part of a driven tool (AGW), particularly for use with tool turrets, with the holder mount representing part of a spindle drive for a corresponding spindle head as a whole. The modular clamping system or machining system can be operated manually; however, automated operation is also possible, allowing tool changes to be carried out automatically.

[0007] Due to the tolerance compensation mentioned between the holder mount and the holder being held, a functionally reliable connection is always achieved by means of the fixing device, even when using different machining tools with a standardized holder, using the machining system mentioned.

[0008] In a preferred embodiment of the machining system according to the invention, the compensating device comprises a receiving flange with at least one end-faced flat contact surface for engagement with a correspondingly designed flat contact surface of the holder, and with an engagement part that engages in the holder receptacle in the direction of the securing device and that is weakened by at least one groove along its wall. This receiving flange can be manufactured with a precise fit, with its respective flat contact surface and the respective weakening engagement groove, and only then can it be fixed in a defined manner, for example, by screwing, to one free end face of the holder receptacle, which helps facilitate the manufacture of the machining system as a whole.In this way, a higher degree of modularity can be achieved in the form of a modular system because there are more options for combining different types of holder mounts with different types of mounting flanges.

[0009] In a further preferred embodiment of the machining system according to the invention, the mounting flange is secured to the holder receptacle and, as part of the holder receptacle, has a further flat contact surface on its opposite end face for engagement with an adjacent flat contact surface of the holder receptacle. Due to the interaction of the various flat contact surfaces and fitting diameters, a high degree of concentricity and synchronism can be achieved for the holder. The flat contact surfaces, which are designed to be as large as possible, create an ideal support effect for machining tools arranged on a holder.

[0010] To ensure consistent concentricity, it is also advantageous if the holder has at least one fitting diameter that interacts with a centering surface on the inner circumferential side of the mounting flange.

[0011] In a preferred embodiment of the machining system according to the invention, the holder is circumferentially guided with play along inner circumferential surfaces in the holder receptacle toward its other free end face. This creates "space" between adjacent components of the holder receptacle and the holder to prevent unnecessary stress in the clamped state, which could otherwise lead to over-determination, with the result that the defined fastening process is impaired. In this respect, the adjacent surfaces in this rear region of the holder receptacle and the holder serve as guide surfaces, which help facilitate the insertion of the holder into the holder receptacle.

[0012] In a further preferred embodiment of the machining system according to the invention, the fixing device comprises a crown gear with a contact surface for engagement with the further flat contact surface of the receiving flange and with flat contact surfaces for engagement with a respectively assignable clamping surface of a clamping cam of the holder, which has a bevel for sliding up the flat contact surface of the crown gear and a flat clamping surface for clamping on the flat contact surface of the crown gear. Thus, with little effort, the clamping process is initiated when the crown gear is pivoted from its release position into the fixing position, and the holder with the respective machining tool is pulled towards the conical receptacle of the holder receptacle.

[0013] In a further preferred embodiment of the machining system according to the invention, it is provided that during the fixing process, when the respective clamping cam of the holder slides onto the flat contact surface of the crown gear, the compensating device is deformed, thereby initiating a clamping process between the holder and the holder receptacle. As the clamping process progresses, the compensating device on the receptacle flange and thus on the holder receptacle is noticeably deformed and provides a counterforce which generates the actual clamping force between the holder and the holder receptacle. In a further preferred embodiment of the machining system according to the invention, it is provided that the actuating device for the crown gear, which encloses the holder when the holder is inserted into the holder receptacle, has at least one pinion drive which, when received in the holder receptacle, engages through the latter.This way, the pinion drive for driving the crown gear is securely integrated into the holder, yet remains easily accessible from the outside for operation. This prevents incorrect operation.

[0014] In a further preferred embodiment of the machining system according to the invention, it is provided that, toward the other free end face of the holder, pressure pieces are embedded on the outer circumference. When the holder is in the fixed state, these pressure pieces engage in an associated annular groove in the holder receptacle. A ring seal is subsequently accommodated in the holder. When the pressure pieces are engaged, this results in secure positioning even in the area of ​​the rear part of the respective holder in the holder receptacle, while simultaneously providing reliable sealing in the area of ​​the other free end face of the tool holder.

[0015] The invention also relates to a holder receptacle, in particular for an actuating device as presented above, wherein the holder receptacle has on its one free end face a spring-elastically flexible compensating device which enables tolerance compensation between a holder receptacle and a received holder, at least in a fixing position.

[0016] In the following, the processing system according to the invention is explained in more detail using an exemplary embodiment according to the drawing. In this diagram, not to scale, the

[0017] Figure 1 shows the machining system as a whole in the form of an exploded view; Figure 2 shows a longitudinal section through the machining system according to Figure 1 in the assembled state;

[0018] Figures 3a and b show a perspective front view and a side view of a holder used in the machining system without a machining tool;

[0019] Figure 4 shows an enlarged view of a detail marked X in Figure 3b;

[0020] Figures 5 and 6 show components of the fixing device of the machining system;

[0021] Figure 7 is an enlarged view of a circular section marked Y in Figure 2 with parts of an actuating device;

[0022] Figure 8 shows a perspective view of a pinion drive as used for the machining system according to Figures 1, 2 and 7;

[0023] Figure 9 is a plan view of part of a holder receptacle with inserted pinion drive according to Figure 8 in the actuated operating position 1;

[0024] Figures 10 and 11 show, once in perspective top view and once in longitudinal section, a flange-like compensation device for maintaining tolerance compensation between the holder receptacle and the holder being held.

[0025] The machining system shown in Figure 1 consists of a drivable holder receptacle 10 and a holder 12 provided for receiving a machining tool (not shown), which holder has a holder shaft 14 and which can be interchangeably secured in the holder receptacle 10 by means of a securing device 16. The securing device 16 can be moved by means of an actuating device 18 as part of a securing or release process from a release position to a securing position and vice versa, in which the holder 12 can be inserted into the holder receptacle 10 and removed again or is held in its inserted position in the holder receptacle 10 and retracted with a predeterminable retraction force. For this purpose, the holder 12 has at least one, preferably several, clamping cams 96 arranged on the holder shaft 14, each of which is in contact with or pulled away from the holder for a securing or release process.comes out of contact with an assignable flat contact surface 22 of the fixing device 16 (see Figure 6). For this purpose, the holder receptacle 10 has a resiliently flexible compensation device 24, as shown in more detail in Figures 10 and 11, which enables tolerance compensation between the holding receptacle 10 and the received holder 12, at least in the fixing position.

[0026] The holder receptacle 10 represents the spindle or spindle insert of a driven tool (AGW). For clarity, an overall view of the driven tool, which is also technically referred to as the spindle head and is well known in this regard, has been omitted. The machining system according to Figure 1 provides a modular interface for clamping a tool adapter as a holder 12. According to the illustration, this chuck system is a Weldon-type chuck system with a cylindrical bore 26 for receiving the shank of a cutting tool, which can be connected to a coolant channel 28 on the bottom. Furthermore, the Weldon holder 12 has an engagement bore 30 on its outer circumference with an associated thread, which serves to engage a locking screw 32 (Figure 1) for clamping the holder of the cutting tool in the bore 26 of the holder 12.Such holder systems, such as Weldon and many more, are well known, so they will not be discussed in more detail here.

[0027] As can be seen in particular from Figures 10 and 11, the compensating device 24 has a receiving flange 34 in the manner of a disk-shaped body with a flat contact surface 36 on the free end face of the receiving flange 34. This flat contact surface 36 serves to ensure a precise fit against a correspondingly designed flat contact surface 38 of the holder 12. The disk part of the receiving flange 34 is provided with through-holes 40 through which individual engagement screws 42 (Figure 1) pass and serve to secure the receiving flange 34 to the free end face 44 of the holder receptacle 10. Furthermore, individual locating and stop pins 46 are provided, which also pass through holes 48 of the receiving flange 34 and serve to ensure a precise alignment of the receiving flange 34 on the holder receptacle 10 during fastening.

[0028] All holes 40, 48 are evenly distributed along the flange surface of the receiving flange 34, so that even with the insertion of the engagement screws 42 and the locating and stop pins 46, no imbalance can occur during the rotary drive. One of the pins 26 ensures that the flange 34 is securely aligned in the direction of rotation, and the other pin 46 ensures that a pinion shaft of a pinion drive has a stop. As can be seen from Figures 10 and 11, the receiving flange 34 has an annular engagement part 50 that is integrally connected to the flange plate of the receiving flange 34. When the machining tool is assembled as shown in Figure 2, the engagement part 50 engages in the free opening 79 of the holder receptacle 10. As the cross-sectional view according to Figure 11 shows in particular, the engagement part 50 is provided on the outer circumference and inner circumference by a groove 52 and 53, respectively.54, which are thus incorporated into the circumferential surrounding wall 56 of the engagement part 50, whereby the respective groove profile of a groove can also be interrupted. The receiving flange 34 is secured to the holder receptacle 10 at the end face and, as part of the latter, to the latter by means of the engagement screws 42. Furthermore, the receiving flange 34 has a further flat contact surface 58 on its opposite end face for the associated engagement with an adjacent, end-face flat contact surface 60 of the holder receptacle 10.

[0029] As can be seen particularly from Figure 3b, the holder 12 has a fitting diameter 64 with a predeterminable diameter below a disc-shaped carrier plate 62 with the Weldon structure already described. This fitting diameter can be designed to be interrupted and otherwise interacts precisely with a machined, adjacent centering surface 66 on the inner circumferential side of the receiving flange 34. In this way, a precise positional alignment of the holder 12 in the holder receptacle 10 is achieved via the planar contact and fitting surfaces. In contrast, as shown in Figure 2 in particular, in the direction of its other free end face 68, the holder 12 is circumferentially guided with play ("clearance") along inner circumferential surfaces 70 in the holder receptacle 10. In particular, a predeterminable axial distance is also formed between the other free end face 68 and a base part 72 of the holder receptacle 10, which extends transversely to the longitudinal or drive axis 74 of the machining system.

[0030] The aforementioned inner circumferential surface 70 of the holder part 10 has two cylindrical sections 76, 78, wherein the cylindrical section 76 is smaller in terms of free diameter than the cylindrical section 78, which continuously widens conically in diameter along an inner wall section 80 towards the opening 79 of the holder receptacle 10. From the outer circumference, the holder receptacle 10 is constructed in a stepped manner like a conventional spindle body for accommodation in a housing with corresponding bearing points for a driven tool (AGW) in the manner of a spindle head (not shown). In this respect, for the intended material machining by means of a cutting tool in the holder 12, the coolant channel 28 is extended in the direction of the holder receptacle 10 via the associated base part 72 by a section 81 and opens into a transversely running channel section 82 in the holder receptacle 10.In the case of angled AGWs, the channel section 84 is not present; in this case, the section 82 is continuous up to the free rear end of the holder receptacle 10.

[0031] If a cylindrical wall section 84 on the holder shaft 14 engages with play or air into the cylindrical section 78 of the holder receptacle 10, individual spring-loaded pressure pieces 86 are present in this area on the outer circumference of the holder 12. These pressure pieces 86 are arranged relative to the longitudinal or drive axis 74, preferably diametrically opposite one another, with equal radial spacing from one another, and engage in a force-fitting and form-fitting manner in an associated annular groove 88 on the inner circumferential surface 70 of the holder receptacle 10, thus indirectly indicating the complete reception of the Weldon adapter or the holder 12 in the holder receptacle 10. The respective pressure piece 86 is preferably provided at its end with a spherical surface for releasable engagement in a locking or annular groove 88 on the inner circumferential surface 70 of the holder receptacle 10.On the subsequent, further cylindrical wall section 90 of the holder 12, a circumferential O-ring seal is inserted as an annular seal 92 in a receiving groove 94 in the holder shaft 14. This sealing ring 92 seals the channel sections 28, 81, 82 from the environment or the interior of an AGW housing in this area.

[0032] The holder 12 with its holder shaft 14 will now be explained in more detail with reference to Figures 3a, 3b and 4. Four clamping cams 96 are arranged along the cylindrical outer circumferential surface of the holder shaft 14. These cams are grouped in pairs with equal radial spacings between the pairs and are arranged diametrically opposite one another to the longitudinal or drive axis 74. One of the four clamping cams 96 is shown in an enlarged view in Figure 4, with one clamping cam 96 having a bevel 98 for sliding up the securing device 16 and a flat clamping surface 100 for defined securing to the respective clamping surface 22 of the securing device 16, which will be explained in more detail below.

[0033] The four clamping cams 96 protrude at a predeterminable distance above the outer circumferential surface of the holder shaft 14 and are arranged between the carrier plate 62 with the fitting diameter 64 and the individual pressure pieces 86 and are thus in a central region between the aforementioned components. In addition to the four clamping cams 96, there are also two contact cams 102, of which only one is shown in Figure 3b. The two identically designed contact cams 102 are arranged at the same radial distance from one another diametrically to the longitudinal or drive axis 74 and protrude in a cuboid shape above the outer circumference of the holder shaft 14. Furthermore, their central longitudinal axis is arranged in congruent extension with the parting plane 104, which separates the bevel 98 from the flat clamping surface 100 of an adjacent clamping cam 96.In this respect, the two contact cams 102 are mounted, viewed in the axial direction, between adjacent clamping cams 96 and the fitting diameter 64 on the holder shaft 14 with a projection which approximately corresponds to the projection of the respective clamping cam 96.

[0034] Returning to Figure 10, four through-grooves 106 are provided on the inner circumferential side of the engagement part 50, which, in pairs, are passed through by both the clamping cams 96 and the contact cams 102, specifically during a fixing process of the holder 12 in the receptacle 10 until the clamping cams 96 come out of engagement with the through-grooves 106, wherein the two contact cams 102, however, remain received in an associated rectangular through-groove 106 with play, so that a torque is transmitted to the holder 12 via the combination of the through-groove 106 and the respectively engaged contact cam 102 via the receptacle flange 34, which is firmly coupled to the holder receptacle 10, as soon as the receptacle 10 is driven in rotation. Preferably, only one through-passage groove 106 needs to be precisely formed, so that an assignable system cam 102 with this precisely fitting through-passage groove 106 carries out the torque transmission.

[0035] The cams 96 and 102 are arranged rotationally symmetrically on the holder 12 so that no imbalance occurs. Furthermore, the symmetry allows the (Weldon) adapter or holder 12 to be inserted regardless of the spindle position (0° / 180°) or the position of the holder receptacle 12. The number of cams 96 and 102 can vary depending on the available space and the torques to be transmitted. Thanks to the symmetrical arrangement of the four clamping cams 96, a uniform degree distribution of 60° and 120° is achieved along the circumference. Differently designed gripper grooves 108, particularly with an asymmetric structure, can be introduced along the outer circumference of the carrier plate 62, one of the gripper grooves 108 being shown as a recess in Figures 1, 3a and 3b.In this respect, the gripper grooves 108, which are diametrically opposed to the longitudinal or drive axis 74, are arranged on a flat end face of the carrier plate 62, which faces the other free end face 68 of the holder 12. This enables automated alternating operation for the respective holder 12 by means of the two symmetrical, opposing gripper grooves 108 and bearing-oriented gripping for the tool adapter 12. For the cams 96, the force is constant regardless of the number of cams 96. For the cams 102, only the precisely fitting cam 102 is engaged, and thus the maximum transmittable torque is constant. In this respect, the individual cams 102 are designed as parallel keys.

[0036] The fixing device 16 is explained in more detail below. This comprises a crown gear 110, as shown in more detail in Figures 5 and 6. The crown gear 110 has a contact surface 112 for a flat contact with a further flat contact surface 113 of the receiving flange 34. The flat contact surface 113 is formed from four arcuate partial surfaces 115, which extend on the inner circumferential side of four individual webs 117. Each partial surface 115 is part of a clamp- or bow-like guide, the free ends of which open in pairs towards a cylindrical central opening 119 of the engagement part 50. The projecting ends of the guide, as part of each partial surface 115, delimit an opening between them, the free width of which corresponds to the width of each through-groove 106 and is otherwise aligned axially parallel to the latter.All partial surfaces 115 span a common, interrupted contact surface that runs transversely to the longitudinal or drive axis 74. Furthermore, the partial surfaces 115 running along a fictitious inner ring 121 form the free end face of the engagement part 50. Further partial surfaces extend along the outer circumference, spanning an outer fictitious ring surface 123, which is axially offset from the front-most partial surfaces 151.

[0037] The crown gear 110 further comprises groove-like through-openings 114, which, in an initial state designated 0 (Figure 9), are aligned with the upstream through-grooves 106 of the receiving flange 34. Between the through-openings 114, grouped in pairs, two curved toothed sections 116 are arranged, which project axially beyond the contact surface 112. On the opposite side of the crown gear 110, four webs 118 are arranged, each with a different circumference in pairs, which have the flat contact surfaces 22 along their free end faces, which interact with the surfaces 98, 100 of the clamping cams 96, as will be explained in more detail below.Furthermore, the crown gear 110 has, on its side opposite the toothing 116, an annular or support surface 120 which is in contact with a shoulder-like annular surface 122 (Figure 1) on the inside of the holder receptacle 10, which is set back by a predeterminable axial distance from the opening 79 of the holder receptacle 10. The crown gear 110 can be pivoted back and forth about the longitudinal or drive axis 74 along this annular surface 122 of the holder receptacle 10. As can also be seen from Figure 6, each flat contact surface 22 is provided with a radius at the transition point to one of its free end faces for sliding up the respective bevel 98 of a clamping cam 96, wherein the sliding process takes place until the flat clamping surface 100 of the respective clamping cam 96 comes into surface contact with the flat contact surface 22 of each web 118.For better illustration, the radius in question is surrounded by a circle labeled Z.

[0038] Each toothing section 116 of the crown gear 110 is assigned a pinion drive 144 with a pinion toothing 146 that engages with the respective toothing 116 of the crown gear 110, for which purpose the pinion toothing 146 only needs to be arranged partially along the outer circumference of the pinion drive 144. As viewed in the direction of Figure 8, the respective pinion drive 144 has, above it in a further circumferential surface, a groove-shaped recess 148 that serves for the engagement of one of the two stop pins 46 that hold the respective pinion drive 144 in its position in the receiving flange 34 and in bores 150 along a flange-like widened outer circumference 151 of the holder receptacle 10. In this way, when the holder receptacle 10 is driven by the holder 12, the respective pinion drive 144 cannot fall out of its associated recess.The relevant installation conditions are partially reproduced in an enlarged form in Figure 7, which shows a circular section designated Y in Figure 2. In particular, the two stop pins 46 can be unscrewed from the threaded parts of the associated bores 48 to release the respective pinion drive 144. As can also be seen from Figure 8, the respective pinion drive 144 has a handle 152 on its free end face, which serves to engage an operating tool (not shown in detail), for example in the form of an Allen key. Furthermore, the pinion drive 144 has a blocking nose 154 protruding on the outer circumference, which, as shown in Figure 9, is guided in a slotted guide 156 in the outer circumference flange 151 of the holder receptacle 10.The 0 represents an unactuated position and position 1 an actuated position in which the crown gear 110 is pivoted such that the flat clamping surfaces 100 of the clamping cams 96 are in flat contact with the contact surfaces 22 of the crown gear 110. The pinion drive 144 shown in Figure 8, provided it is inserted into the associated recess in the holder receptacle 10 and also passes through two half-shell-shaped recesses 158 in the receiving flange 34, forms the actuating device 18 as a whole for the desired pivoting of the crown gear 110 from an unactuated position 0 into an actuated position 1 and vice versa.

[0039] Advantageously, two pinion drives 144 are provided for the machining system, allowing holder changes from different, particularly opposite, positions. Accordingly, any positional ambiguity of the spindle in the form of the holder receptacle 10 is limited to two positions (0° / 180°). In this respect, the machining system is constructed with two drive points offset by 180° in the form of pinion drives 144. The toothing engagement between the respective pinion toothing 146 and the toothing sections 116 of the crown gear 110 is selected such that one gear pair is always the driving gear, while the second pinion shaft, which is not subjected to torque, is the driven gear, i.e., is driven in its respective position. In this way, within the framework of automation, the Weldon adapter or the holder 12 can be inserted and the clamping mechanism actuated regardless of the position (0° / 180°).The mentioned pitch can be extended as desired using any even divider, so that automation can basically take place with dividers 2, 4, 6, 8, etc. For cost reasons, however, it is particularly economical to opt for a divider 2, as in this case, which requires the least amount of machining while offering the maximum advantage that the system can always be operated or operated at the desired position, largely independent of the position. Ultimately, not only can the holder 12 be used in any position (0° / 180°), but the AGW or the spindle position can also be used.

[0040] For a fastening process, the holder 12 must be inserted into the holder receptacle 10 as described. The holder 12 is inserted by means of a purely linear movement coaxial with the longitudinal or drive axis 74. The through-grooves 106 in the receiving flange 34 and the groove-like through-openings 114 in the crown gear 10 must be aligned with one another when the pinion drive 144 is in position 0 so that the clamping cams 96 lie on the side of the webs 118 of the crown gear 110. Once the holder 12 is inserted into the holder receptacle 10 in this way, the crown gear 110 is pivoted by means of a pinion drive 144 provided for this purpose.The pinion drive 144 shown in Figure 9 is pivoted clockwise from position 0 to position 1, with the result that the associated pinion toothing 146 is also moved clockwise and the corresponding rotary movement is equally transmitted to the crown gear 110 via the respective toothing section 116, which is in engagement with the pinion toothing 146 of the actuated pinion drive 144. During the corresponding pivoting movement of the crown gear 110, the bevel 98 of each clamping cam 96 then slides over the radius designated Z onto the associated web 118 until the subsequent flat clamping surface 100 of the clamping cam 96 comes into contact with the flat contact surface 22 of the associated web 118 in order to lock the holder 12 in the holder receptacle 10.For the respective fixing process, the respective web 118 is pushed with its flat contact surface 22 over the clamping cam 96 adjacent to the rotational or pivoting movement of the crown wheel 110, first over the bevel 98 and then over the flat clamping surface 100.

[0041] The possible clamping travel is limited by the blocking lug 154 on the pinion drive 144, which then strikes a limit within the link guide 156 in the holder receptacle 10. In addition to limiting the clamping travel, excess torque during handling is also diverted, so that the torque support formed for this purpose protects the tooth pairing 146, 116 from overloading. The crown gear 110 is thus rotated further until it stops, whereby the respective clamping surface 22 of the crown gear 110 slides over the associated flat clamping surface 100 of the tool adapter or holder 12. The flat surfaces 22, 100 in contact with this generate a defined clamping force, and the holder 12 is secured in the holder receptacle 10 with a predeterminable pull-in force.The torque support mentioned can be effected both by the actuating device 18 in conjunction with the blocking lug 154 and by means of a stop pin 46 in conjunction with the actuating device 18.

[0042] The clamping process and the generation of the clamping force are made possible by the fact that the dimension A between the outer boundary of the receiving flange 34 and the crown gear 110 in the released actuation position 0 is greater than the dimension B between the flat contact surface 36 of the receiving flange 34 and the flat surface 100 of each cam 26 in the fixed actuation position 1. When the two bevels in the form of the web radius on the web 118 and the bevel 98 of the respective clamping cam 96 slide up against each other, the receiving flange 34 is elastically deformed, with the radial grooves 52, 54 provided supporting this deformation process.Because at the end of the turning process for the crown gear 110 the clamping surfaces 22 of crown gear 110 and the clamping surfaces 100 of the cams 26 lie flat on one another with a preload force, the same elastic deformation is always achieved, which always generates a defined pull-in force, whereby in the sense of "action" = "reaction" the pull-in force acting on the holder receiving base also simultaneously acts as a deformation force on the receiving flange 34 and due to the spring effect mentioned, the clamping or pull-in force is increased within the framework of an elastic clamping by means of the receiving flange 34. The release process for the holder 12 then runs in the opposite direction to the clamping process, i.e. by turning the pinion drive 144 in the opposite direction of rotation the two clamping surfaces 22, 100 of crown gear 110 andfrom each cam 26 and the release of the corresponding connection causes the receiving flange 34 to return to its original shape due to its inherent elasticity.

[0043] When the crown gear 110 is returned to its open position via the respective pinion drive 144, i.e., at stop 0, the recesses 114 of the crown gear 110 and the through-grooves 106 of the mounting flange 34 are again aligned, and the holder 12 can be removed from the holder receptacle 10 in the spindle head by a purely linear movement along the axis 74. The aforementioned release and removal process can also be performed both manually and automatically. With the machining system according to the invention, a multitude of different spindle heads can be provided with holders 12 for the purpose of holding a machining tool or a collet in order to perform machining within the desired scope. This has no equivalent in the prior art.

Claims

P a t e n t a n s p r ü c h e 1. Machining system, at least consisting of a drivable holder receptacle (10) and a holder (12) provided for receiving a machining tool, which holder has a holder shaft (14) and which can be interchangeably secured in the holder receptacle (10) by means of a securing device (16), wherein the securing device (16) can be moved by means of an actuating device (18) during a securing or release process from a release position to a securing position and vice versa, in which the holder (12) can be inserted into the holder receptacle (10) and removed again or is held in its inserted position in the holder receptacle (10) and is retracted with a predeterminable retraction force, wherein the holder (12) has at least one clamping cam (96) arranged on the holder shaft (14), which clamping cam can be brought into contact with or into engagement with the holder for a securing or release process.comes out of contact with an assignable clamping surface of the fixing device (16), characterized in that the holder receptacle (10) has a spring-elastically flexible compensating device (24) which, at least in the fixing position, enables tolerance compensation between the holder receptacle (10) and the received holder (12).

2. Machining system according to claim 1, characterized in that the compensating device (24) has a receiving flange (34) with at least one end-side arranged planar contact surface (36) for contact with a correspondingly designed planar contact surface (38) of the holder (12), and with an engagement part (50) which engages in the holder receptacle (10) in the direction of the fixing device (16) and which is weakened in its wall profile by at least one groove (52, 54).

3. Machining system according to claim 1 or 2, characterized in that the receiving flange (34) on the holder receptacle (10) and fixed thereto as part of the same, has on its opposite end face a further flat contact surface (58) for contact with an adjacent flat contact surface (60) of the holder receptacle (10).

4. Machining system according to one of the preceding claims, characterized in that the holder (12) has at least one fitting diameter (64) which cooperates with a centering surface (66) on the inner circumferential side of the receiving flange (34).

5. Machining system according to one of the preceding claims, characterized in that the holder (12) is guided in the direction of its other free end face (68) circumferentially with play along inner circumferential surfaces (70) in the holder receptacle (10).

6. Machining system according to one of the preceding claims, characterized in that the fixing device (16) has a crown gear (110) with a contact surface (112) for contact with a further flat contact surface (113) of the receiving flange (34) and with flat contact surfaces (22) for contact with a respectively assignable clamping surface (100) of a clamping cam (96) of the holder (12), which has a bevel (98) for sliding up on the flat contact surface (22) of the crown gear (110) and a flat clamping surface (100) for clamping on the flat contact surface (22) of the crown gear (110).

7. Machining system according to one of the preceding claims, characterized in that during the fixing process when the respective clamping cam (96) of the holder (12) slides onto the flat contact surface (22) of the crown wheel (110), the compensating device is deformed and a clamping process is initiated between the holder (12) and the holder receptacle (10).

8. Machining system according to one of the preceding claims, characterized in that the actuating device (18) for the crown wheel (110), which in the inserted state of the holder (12) in the holder receptacle (10) comprises the holder (12), has at least one pinion drive (144) which, received in the holder receptacle (10), passes through it.

9. Machining system according to one of the preceding claims, characterized in that in the direction of the other free end face (68) of the holder (12) pressure pieces (86) are embedded on the outer circumference side, which in the fixed state of the holder (12) engage in an associated annular groove (88) in the holder receptacle (10) and that subsequently an annular seal (92) is accommodated in the holder (12).

10. Machining system according to one of the preceding claims, characterized in that a torque support is achieved by the interaction of the actuating device (18) with a stop pin (46) on the receiving flange (34) and / or with a blocking nose (154) of the pinion drive (144). 11 . Holder receptacle, in particular for an actuating device according to one of the preceding claims, characterized in that it has on its one free end face (68) a spring-elastically flexible compensating device (24) which enables tolerance compensation between a holder receptacle (10) and a received holder (12) at least in a fixing position.

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