ACTUATOR

Description

[0001] The invention relates to an actuating device by means of which, in particular, a device for fixing workpieces can be actuated.

[0002] It is known from various technical fields to move mechanical devices from one predetermined position to another by introducing a tensile or compressive force using an actuating device.

[0003] For example, a feed device for the translational movement of a strip-shaped workpiece is known from DE 10 2012 220 817 B3.

[0004] From DE 10 2005 056 449 A1 a workpiece holding device and a processing machine equipped with it are known.

[0005] From EP 0 306 737 A2, an actuator is known in which one element moves in a compressive direction while another element moves in the opposite direction. The actuator is permanently integrated into a housing.

[0006] The tensile or compressive force required to move the mechanical device from one position to another can sometimes be comparatively high. A bearing for the mechanical device that supports this tensile or compressive force is therefore massive and cannot always be implemented with acceptable technical and economic effort.

[0007] The present invention is therefore based on the objective of providing an actuating device by means of which the actuation of a mechanical device can be carried out completely or at least approximately without external reaction forces.

[0008] This problem is solved by the features of claim 1. Advantageous embodiments of the invention are described in the dependent claims.

[0009] According to the invention, the actuating device is provided for introducing a tensile force and an opposing compressive force into a device and comprises at least one tensile element for transmitting the tensile force to the device and at least one compressive element for transmitting the compressive force to the device. The at least one tensile element and the at least one compressive element are operatively connected via an actuator floating between them to generate a relative movement corresponding to the movement of the tensile element and the compressive element in opposite directions.

[0010] The device can be provided, for example, in the field of mechanical processing of workpieces, in particular in the manufacture of brake linings and the associated lining carrier plates, in the form of a workpiece holder in which a workpiece inserted therein can be secured by force and / or form locking.

[0011] The inventive design of the actuating device has proven particularly advantageous for actuating the aforementioned device for clamping workpieces, which is moved from its clamped state to the released state by introducing a tensile force that acts as a return force on the clamping means. With the inventive actuating device, an opposing compressive force is simultaneously exerted on the other device, so that the device into which the tensile force and the opposing compressive force are introduced remains practically free of external reaction forces. This allows for a simpler design of the transport device provided for the apparatus, since it does not have to support any reaction force opposing the return force.

[0012] The basic principle of the present invention is based on an opposing coupling of the tension member by a pressure member by means of an actuator floating between them, by which the relative positions between the tension member and the pressure member are automatically aligned to each other.

[0013] In this case, the actuating device can be part of a machining system or machining station for the mechanical processing of workpieces. One or more devices for holding the workpieces can be used within this system. For example, a machining station can be equipped with the actuating device and coupled to a workpiece clamping device to enable the removal or insertion of a workpiece.

[0014] Preferably, the actuator may be designed to generate a linear motion. This has proven advantageous because the actuator simultaneously generates a tensile force and a compressive force. Due to the linear motion, both forces are already aligned parallel to each other and therefore act in opposite directions.

[0015] It has also proven advantageous to guide the at least one tension member and the at least one compression member so that they are parallel and slidable relative to each other. This allows for the introduction of tensile and compressive forces with minimal or no external reaction force.

[0016] According to the invention, the actuator can be actuated according to at least one of the following operating principles: pneumatically, hydraulically, magnetically, or electromechanically. Pneumatic or hydraulic actuation of the actuator proves advantageous in industrial environments, since large machining systems generally have connections for compressed air or hydraulic fluid supplies. Alternatively, however, it is also conceivable that the actuator could be designed magnetically, for example in the form of an electromagnet, or electromechanically, for example in the form of a spindle drive.

[0017] In a pneumatically or hydraulically operated actuator, at least one working cylinder and at least one hydraulically or pneumatically displaceable working piston can be provided to generate a relative movement acting on the at least one tension member and the at least one compression member. The corresponding forces and the associated movements can be generated simply by this design, while at the same time the force acting on the tension member and the compression member can be very easily regulated by adjusting the hydraulic or pneumatic pressure.

[0018] According to the invention, the actuator is designed with at least two actuator elements movable in opposite directions within an actuator housing, wherein one actuator element is coupled to the at least one tension element and the other actuator element is coupled to the at least one compression element. In this way, the actuator housing itself only has to perform a relatively small movement on its floating bearing when the actuator is actuated, whereas the tension and compression elements connected to the actuator elements can undergo a larger movement. This results in a smoother transmission of forces to the other device. Furthermore, the distance along which the actuator must be mounted on a floating bearing can be reduced.

[0019] Preferably, in a hydraulic or pneumatic actuation method of the actuator, the at least two actuator elements moving in opposite directions within the actuator are designed as working pistons, which are movably guided in the actuator housing, which is designed as a working cylinder or which has at least one working cylinder. One piston is coupled to the at least one tension element, and the other working piston is coupled to the at least one pressure element. In this way, a single working pressure acting on the actuator can be used to actuate both working pistons simultaneously with the same pressure, and thus, with the same piston area, also with the same force, making the control of the actuating device particularly simple.In a magnetic actuator configuration, the actuator elements can be designed, for example, as two identical electromagnets coupled to a common soft iron core. For instance, the coils of these electromagnets can be connected in series so that the same current flows through both coils, thus generating the same magnetic force with the same number of turns.

[0020] If the actuator is designed as an electromechanical spindle drive, it is conceivable to equip the spindle drive with two spindles whose threads are designed in opposite directions to each other, so that actuation of an intermediate electric motor simultaneously generates a tensile force and a compressive force.

[0021] In a hydraulically or pneumatically actuated actuator, it may be possible to use the same hydraulically or pneumatically effective piston areas to generate both the tensile and compressive forces. This ensures that the tensile forces are equal in magnitude to the compressive forces, thus guaranteeing the application of tensile and compressive forces with minimal or no external reaction.

[0022] According to the invention, the actuator is guided in a linearly displaceable manner relative to a foundation to achieve the floating bearing, the foundation being fixed in position relative to the device into which the tensile or compressive force is to be introduced. This has proven particularly advantageous for the use of the actuating device in a machining system, so that a device into which the tensile or compressive forces are to be introduced is not subjected to forces that serve to guide the actuator in its floating bearing.

[0023] In a further embodiment of the invention, the actuator for generating opposing relative movements between the at least one tension member and the at least one compression member can be designed as a double-acting actuator or with at least one return spring. In this way, the actuating device can be used not only to introduce a tensile force via the tension member and a compressive force via the compression member, but also to introduce a compressive force via the tension member and a tensile force via the compression member. This proves particularly advantageous if the device into which the tensile or compressive forces are to be introduced does not have an automatic return mechanism. A device for fixing workpieces could, for example, have spring-driven clamping devices that automatically assume a specific position when released.Alternatively, a device for fixing workpieces can also include clamping elements that can be positioned and locked in different positions, so that a corresponding actuating device must apply not only a return force but also an opposing actuating force for the precise positioning of the clamping elements. A double-acting actuator can actively apply the corresponding tensile or compressive forces in both directions; in hydraulic or pneumatic actuators, for example, this occurs when the working cylinder or piston is designed to be double-acting.

[0024] In a simpler embodiment, it can alternatively be provided that the movements of the actuating device in one direction are effected by a return spring that is pre-tensioned to exert the opposing compressive and tensile forces. By adjusting the actuator's actuation with a smaller counterforce, for example by applying a lower hydraulic or pneumatic pressure, the compressive and tensile forces exerted by the return spring on the tension and compression elements can be adjusted.

[0025] In this context, the general principle of designing at least one tension member to transmit a compressive force and / or at least one compression member to transmit a tensile force has proven advantageous. For this purpose, it can be provided, for example, that the respective tension or compression member not only rests against the device for introducing a force, but also, if necessary, forms a positive-locking or friction-locking connection with the device, so that forces can be transmitted in both directions.

[0026] Furthermore, it has proven particularly advantageous to provide at least two tension members which are diametrically opposed to the at least one compression member, or to provide at least two compression members which are diametrically opposed to the at least one tension member, or to provide at least two tension members and at least two compression members which are arranged symmetrically to each other in such a way that the introduction of the tensile and compressive forces is essentially free of torques.

[0027] The problem underlying the invention is further solved according to claim 10 by a machining system comprising an actuating device as described above and a device for fixing workpieces for mechanical machining. Such a machining system can, for example, be a machining line for machining brake linings or lining backing plates for the production of brake linings for motor vehicles.

[0028] Such a machining system can further be characterized by the fact that at least one machining station is provided for the mechanical machining of a workpiece held in the device, into which the device can be fed and removed by means of a transport device. In addition, the machining system can be provided with a return device, such as the one described above, for moving the clamping elements to their rest position. In this way, a plurality of devices according to the invention can be used simultaneously in one system.

[0029] Further objectives, advantages, features, and applications of the present invention will become apparent from the following description of an exemplary embodiment with reference to the drawing. All features described and / or illustrated, individually or in any meaningful combination, constitute the subject matter of the present invention.

[0030] They show, in schematic representation: Fig. 1 shows a perspective view of a first embodiment of a device for fixing workpieces, Fig. 2 shows a perspective view of a partial section of a second embodiment of the device for fixing workpieces, Fig. 3 shows a perspective rear view of the embodiment. Fig. 2 Fig. 4 shows a perspective view of a third embodiment of the device for fixing workpieces, Fig. 5 shows a perspective view of the device according to Fig. 4 for fixing workpieces, Fig. 6 a schematic sectional view of the device according to the invention from the Fig. 4 and 5 Fig. 7 a perspective view of a fourth embodiment of a device for fixing workpieces, Fig. 8 a sectional view based on the Fig. 7 , Fig. 9 a top view of the device according to the Fig. 7 and 8Fig. 10 a perspective view of a machining system with an actuating device according to the invention, Fig. 11 a perspective bottom view of the device according to Figure 1 , and Fig. 12 a perspective view of an actuating device according to the invention.

[0031] Fig. 1 Figure 1 shows a device for fixing workpieces 10, which is designated by reference numeral 100. The device 100 serves to clamp the workpiece 10. The workpiece 10 is, for example, a brake lining, which has a carrier plate 6 and a friction lining 5 located thereon, and is arc-shaped, i.e., it has two opposing arc-shaped side parts 16, 17 and two opposing straight side parts.

[0032] The device 100 comprises a clamping support 11, which, like the other components of the device 100, is made of metal. The rectangular clamping support 11 is flat and defines the area of ​​the device 100 on which the workpiece 10 can be placed and clamped. Clamping guides 12 are formed within the clamping support 11, i.e., longitudinal openings extending within the clamping support 11. The clamping guides 12 are arranged parallel to and spaced apart from each other. They extend over a portion of the clamping support 11 and are spaced apart from a stop 13. The stop 13 extends along the end face of the device 100. The stop 13 is in the form of a strip, i.e., a straight, narrow, long component that rests on the device 100 and is fixedly or detachably connected to it. The stop 13 connected to the device 100 is screwed to the device 100, i.e.Interchangeable. Therefore, a suitable stop 13 can be used for different workpiece types.

[0033] As from Fig. 1 As further shown, the device has 100 clamping devices 14, which are slidably arranged longitudinally within the clamping device guides 12 and are made of metal. The clamping devices 14 extend longitudinally through the clamping device guides 12 and upwards relative to the workpiece 10, i.e., the clamping devices 14 project from the clamping support 11 and are approximately cylindrical or slightly conical and formed in one piece. The two ends of a clamping device guide 12 have a shape corresponding to the clamping device 14, i.e., they are arc-shaped, with in Fig. 1 Only one arc-shaped end 8 is shown graphically. Below the clamping support 11, as Fig. 1further clarified, in the longitudinal direction of the clamping guides 12 spring elements 15, which are connected at one of their ends to the clamping means 14 and at their other end to the side of the device 100 which is opposite the end face 9 of the device 100 i.e. the side of the device 100 on whose area the stop 13 is located.

[0034] As long as the workpiece 10 is not yet resting on the clamping support 11, the clamping devices 14 at the arc-shaped end of the clamping guides 12, which are opposite the stop 13, are in a rest position. In the rest position, the spring elements 15 are deflected to their maximum extent, building up their restoring force. To position the workpiece 10 on the clamping support 11, the clamping devices 14 are released and, under the influence of the spring force, move along the clamping guides 12 into a clamping position. In the clamping position, the clamping devices 14 conform to the contour of the workpiece 10, so that the spring elements 15 partially relax and come into contact with the workpiece under spring tension. In this process, the spring elements 15 store clamping energy in the form of potential energy, the magnitude of which increases with the contraction or extension of the spring elements 15.To ensure reliable clamping of the workpiece 10, it can be provided that the spring elements 15 are under permanent preload, i.e., preloaded with a predetermined force that is applied even when the clamping devices 14 are in the position closest to the stop 13.

[0035] In the Fig. 1 In the illustrated embodiment, the clamping means 14 lie tangentially against the contour of the workpiece 10 in the clamping position due to their cylindrical shape.

[0036] Fig. 2 Figure 1 shows another variant of the arrangement of the spring elements 15 below the clamping support 11 of the device 100. In this device 100, spring elements 15 designed as tension springs are provided, which are fixed at one end to the clamping means 14 and at the other end to the end face 9 of the device 100. In this device 100 as well, the clamping means 14 are located on a first, in Fig. 2The arc-shaped end of the clamping guides 12, located below the workpiece 10 and opposite the stop 13, is in a rest position as long as the workpiece 10 is not yet resting on the clamping support 11. The clamping guide 12 is bounded by a second arc-shaped end 7, which corresponds to the first in Fig. 2 opposite the arc-shaped end not shown and facing the opposite side 4, i.e. the rear of the device 100.

[0037] This illustrates in more detail Fig. 3 , which has a rear side equipped with fastening means 18 in Fig. 2 The illustrated device 100 shows the spring elements 15, as shown in the illustration. Fig. 3 as emerges, between the front face 9 of the device 100 and the in Fig. 3 non-visible clamping devices 14 arranged, i.e. also firmly connected to the front face 9 and the clamping devices 14.

[0038] To do this in Fig. 2To position the workpiece 10 shown on the clamping template 11, the clamping devices 14 are moved along the clamping device guides 12 by the application of an external force, so that the workpiece is in the clamping template 11. Fig. 3 The spring elements shown are pulled apart, i.e., lengthened, which is in Fig. 2 This is illustrated by arrow 21. This saves the data in Fig. 3 The spring elements 15 shown, designed as tension springs, possess potential energy, the magnitude of which increases or decreases with the extension or contraction of the spring elements 15. The workpiece 10 is thus pressed against the stop 13 by the clamping devices 12 attached to it and is thereby secured against displacements in the plane of the clamping support 11. This also applies to the... Fig. 2 In the illustrated device 100, the clamping means 14, due to their round shape, conform tangentially to the contour of the workpiece 10 in the clamping position.

[0039] To clamp the workpiece 10 more tightly onto the clamping support 11, the outer surface of the clamping device 14 facing the stop 13 is, as Fig. 4 It is clearly shaped at an angle. In the case of the Fig. 4 In the illustrated embodiment, no workpiece is yet placed on the clamping support 11, i.e., the clamping device 14 is in a rest position. The angle 20 enclosed between the inclined outer surface of the clamping device 12 and the clamping support 11 is approximately 87°.

[0040] Opposite the clamping devices 14, the stop 13 is arranged. It has an inclined outer surface facing the clamping devices 14 and forms an angle 19 of approximately 87° with the clamping support 11. This clamps the workpiece 10 even more tightly onto the clamping support 11.

[0041] In the Fig. 5The device 100 according to the third embodiment is shown in a perspective view. The clamping elements 14, designed as spring pins, are interchangeable on the device 100 and can be replaced. The clamping elements 14 are screwed to an underlying, movable unit. By simply grasping the clamping surface 23 and turning the clamping element 14, it can be detached from the device 100 and replaced by another clamping element 14.

[0042] In the Fig. 6 is a sectional view of the device from the Fig. 4 and 5The figure shows the movable unit located below the clamping support 11. This unit has a connecting part 27 with a threaded bolt extension 33, onto which the clamping device 14, which has an internal thread, is screwed. The connecting part 27 forms part of a guide carriage 26, which is longitudinally displaceable in the device below the clamping support 11. The guide carriage 26 has an internal mandrel 28 connected to the connecting part 27, which engages in a Fig. 6 The spring element 15 (not shown) is immersed. The spring element 15 is positioned in an installation position 30 within an elongated guide pocket 29. The inner pin 28 reduces or almost completely prevents the spring element 15 from buckling laterally under load.

[0043] The stop 13 is screwed to the end face of the clamping support 11 by means of threaded bolts 32. Additionally, the stop 13 may have bores into which pins 34 engage for aligning the stop 13 with the clamping support 11.

[0044] To reset the clamping devices 14 to their rest position, a release mechanism 2 is provided, which is longitudinally displaceable on the device 100 in sync with the clamping devices 14. The release mechanism 2 has two jaws 35 that laterally engage the clamping support 11, between which a return element (not shown in the figures) is inserted. This return element engages the connecting parts 27 of the respective clamping devices 14 when the return mechanism 25 is pulled in the return direction 36. A return jaw 37 is provided to introduce a tensile force into the release mechanism 2, into which a return mechanism 25 of a machining system 200, in which the device 100 is used, can engage.

[0045] Generally, in the Figs. 2 to 6 The trigger 2 shown introduces a tensile force to retrieve the clamping devices 14 from their respective clamping positions.

[0046] In the Fig. 7A fourth embodiment of the device 100 is shown, in which, unlike the embodiments described above, the trigger 2 exerts a compressive force, directly or indirectly, on the respective clamping devices 14 instead of a tensile force when moved in the return direction 36. This returns the clamping devices 14 from their respective clamping positions to their rest positions. For this purpose, the trigger 2, as described in the Fig. 7 The illustrated trigger 2 has several return fingers 38 which engage the respective guide carriages 26 on the front face 9 of the device 100.

[0047] In the Fig. 8 is a sectional view of the device according to Fig. 7 shown, in which the interaction between the respective finger 38 and the associated guide carriage 26 can be seen.

[0048] As in the Figs. 7 to 9As can be seen, according to the fourth embodiment, laterally or end-projecting sections of a trigger 2 can be omitted. Instead, the trigger 2 is part of a return mechanism 25 designed separately from the device 100, which is only activated as needed and at specific locations on a processing unit 200, for example, before or after processing stations 201. Thus, according to the fourth embodiment, the device consists of fewer components than the other embodiments.

[0049] In the Fig. 10The previously mentioned machining system 200 with a machining station 201 is shown schematically. Machining station 201 can, for example, be a grinding station that forms part of a production line. The individual fixtures 100 for fixing workpieces 10 for machining in the machining stations 201 are conveyed to the respective machining stations 201 by means of a transport device 202.

[0050] In the present example according to Fig. 10 The processing station 201 is a removal station in which the finished workpiece 10, in this case a support plate, is to be removed from the device 100. For this purpose, the fixation of the workpiece 10 must be released by returning the respective clamping devices 14 from their respective clamping positions to their rest positions, so that the workpiece 10 is released.

[0051] The trigger 2 of the device 100 is moved in the return direction 36 by means of a return device 25 in the form of an actuating device 49. This must be accomplished with a relatively large return force in the return direction 36, which is greater than the sum of the spring forces of the individual spring elements 15. The return device 25 has pressure elements 52 in the form of support pins 39, which support the device 100 against the return force introduced via the trigger 2 as a tensile force 53. A return pin 40 engages the trigger 2, and its disc-shaped expansion 41 engages the return jaw 37. The return pin 40 is simultaneously a tensile element 51 of the actuating device 49 and is connected to an actuator 50 that applies the return force.

[0052] When the device 100 is moved into the processing station 201 by means of the transport device 202 in transport direction 48, the return jaw 37 and the expansion 41 come into alignment in the return direction 36, so that a simple retraction of the return plunger 40 in the return direction 36 causes the trigger 2 to be carried along.

[0053] In the Fig. 12 The actuating device 49 is shown, which is in Fig. 10The illustrated return device 25 forms the actuating device 49. The actuating device 49 has an actuator 50, which in this case has a centrally arranged tension member 51 and two diametrically opposed compression members 52 with respect to the tension member 51. The tension member 51 serves to introduce a tensile force 53 into the device 100. The compression members 52 support the actuating device 49 against the device 100 with a compressive force in the opposite direction, so that the introduction of the tensile force 53 and the compressive forces 54 essentially cancel each other out. As a result, the device 100 remains essentially free of external reaction forces.

[0054] The actuator 50 has several working cylinders 55 in which several working pistons 56, 58 are slidably guided. In this case, the working pistons 56 serve to apply the tensile force 53 to the device 100, and the working pistons 58 serve to apply the compressive force 54 to the device 100. In this case, the working pistons 56, 58 are each guided in the same working cylinder 55 with identical piston areas 57, 59, so that applying a defined pneumatic or hydraulic pressure to the working cylinder 55 results in the respective working pistons 56, 58 being simultaneously actuated with the same force. The working pistons 56, 58 move in opposite directions into the working cylinder 55, so that a force transmission plate 67, 68 connected to each working piston 56, 58 moves towards the actuator housing 64 located between them. The power transmission plates 67, 68 are each equipped with the tensile orThe force transmission plate 67 is connected to the pressure members 51 and 52, such that the tensile movement exerted on the force transmission plate 67 leads to a movement of the pressure member 52 in the direction of the device 100. In this sense, the force transmission plate 67 is designed such that the tensile force 65 transmitted to it is redirected into a compressive force transmitted by the pressure member 52.

[0055] The actuator 50 thus generates a relative movement 62 between the tension member 51 and the compression member 52, which is indicated by a double arrow. During the execution of this relative movement 62, it can happen that the tension member 51 or the compression member 52 comes into contact with the device 100 first, so that the actuator 50 must perform a compensating movement 69 to prevent a one-sided introduction of a tensile or compressive force into the device 100. For this purpose, the actuator 50 has a guide carriage 60, which forms part of or is connected to the actuator housing 64. The guide carriage 60 is mounted linearly on guide rails 61 and can move on the guide rails 61 between end-mounted clamping pieces 63. The clamping pieces 63 form a stationary foundation 66.

[0056] The actuator 50, designed here to generate a linear motion, can alternatively also be designed as a magnetically actuated or electromechanically actuated actuator. For example, the working pistons 56, 58 can be connected to two identical electromagnets, i.e., electromagnets with the same number of turns, which are movable on a common soft iron core, so that the working pistons 56, 58 then act as actuator elements to apply the respective tensile or compressive force.

[0057] The actuator 50 can also be designed as an electromechanical spindle drive, whereby the actuator elements can be designed as oppositely wound spindle rods, so that a motor arranged centrally in the actuator housing 56 generates a counter-clockwise movement at the spindle taps.

[0058] In all variants of the actuators, it can be provided that they are double-acting, i.e., designed to generate both tensile and opposing compressive forces alternately in both directions, so that not only a return movement for the clamping means 14 required in connection with the device 100 described here, but also an opposing actuation can take place.

[0059] Overall, the actuating device 49 can be used to introduce tensile or compressive forces into other devices with no or minimal external reaction force for a wide variety of applications. The actuating device 49 has proven particularly advantageous for use in brake pad manufacturing.

[0060] Finally, in the Fig. 11 the perspective bottom view of the device 100 according to a variant of the first embodiment according to Figure 1Figure 2 shows a release mechanism 2 with a crankshaft-like design. A rotatable shaft 43 is provided on the underside 44 of the device 100 opposite the clamping support 11. This shaft engages the respective guide carriage 26 of the clamping device 14 with a connecting rod 45. An actuating lever 46 is non-rotatably connected to the shaft 43 and has a connecting bore 47 by means of which it can be connected to an actuator 50. This design of the release mechanism 2 allows for a reduction or reduction of the return movement relative to the clamping device 14 from its respective clamping position, so that the clamping can be released as needed, either with small actuating strokes for the return mechanism 25 or with small return forces. Reference symbol list 1 brake pad 32 Threaded bolts 2 Retrieval device 33 Threaded bolt extension 3 Direction of rotation 34 Pen 4 opposite side 35 jaw 5 Friction lining 36 Return direction 6 carrier plate 37 Retrieval jaw 7 arc-shaped end 38 Retrieval finger 8 arc-shaped end 39 Support stamp 9 Front 40 Retrieval stamp 10 workpiece 41 Expansion 11 clamping support 43 Wave 12 clamping device guide 44 bottom 13 stop 45 connecting rod 14 Clamping device 46 Actuating lever 15 spring element 47 Connecting hole 16 arched side panel 48 Direction of transport 17 arched side panel 49 Actuating device 18 Fasteners 50 actuator 19 angle 51 Tension member 20 angle 52 Pressure element 21 Arrow 53 traction 22 workpiece contour 54 Pressure 23 Clamping surface 55 Working cylinder 24 Stop surface 56 Working piston, tensile force 25 Retrieval device 57 Piston area 26 Guide carriage 58 Working piston, pressure force 27 Connecting part 59 Piston area 28 inner spine 60 Guide sled 29 guide bag 61 Guide rail 30 Installation position 62 Relative motion 31 spring element 63 Clamping piece 64 actuator housing 100 device 65 traction 66 foundation 200 Processing plant 67 power transmission plate 201 Processing station 68 power transmission plate 202 Transport equipment 69 Compensatory movement

Claims

1. Activating device (49) for introducing a tensile force (53) and a compression force (54) opposing the tensile force (53) into a device (100), having at least one traction member (51) for transmitting the tensile force (53) to the device (100) and at least one compression member (52) for transmitting the compression force (54) to the device (100), and having a base (66), wherein the at least one traction member (51) and the at least one compression member (52) for generating a relative movement (62) between the traction member (51) and the compression member (52), corresponding to the movement of the traction member (51) and the compression member (52) in opposite directions, are operatively connected by way of a floating actuator (50) mounted therebetween, and wherein the actuator (50) for achieving the floating mounting is guided so as to be displaceable linearly relative to the base (66), wherein the base (66) is fixed so as to be stationary relative to the device (100) into which the tensile force or compression force is to be introduced, and wherein the actuator (50) by means of a guide slide (60) formed thereon or connected thereto is mounted on a guide rail (61) of the base (66), and wherein the actuator (50) is activatable according to at least one of the following functional principles: pneumatically, hydraulically, magnetically or electro-mechanically, and wherein the actuator (50) is formed with at least two actuator members which are movable in opposite directions in an actuator housing (64), wherein the one actuator member is coupled to the at least one traction member (51) and the other actuator member is coupled to the at least one compression member (52).

2. Activating device (49) according to Claim 1, characterized in that the actuator (50) is designed to generate a linear movement.

3. Activating device (49) according to one of the preceding claims, characterized in that the at least one traction member (51) and the at least one compression member (52) are guided so as to be mutually displaceable in parallel.

4. Activating device (49) according to one of Claims 1 to 3, characterized in that when the actuator (50) is activatable pneumatically or hydraulically, the latter has at least one working cylinder (55) and at least one working piston (56), which is hydraulically or pneumatically displaceable therein, for generating a relative movement (62) acting on the at least one traction member (51) and the at least one compression member (52).

5. Activating device (49) according to Claims 3 and 4, characterized in that the at least two actuator members which are movable in opposite directions in the actuator housing (64) are designed as working pistons (56, 58) which are guided so as to be movable in the actuator housing (64) designed as a working cylinder (55) or comprising the at least one working cylinder (55), wherein the one working piston (56) is coupled to the at least one traction member (51), and the other working piston (58) is coupled to the at least one compression member (52).

6. Activating device (49) according to one of Claims 1 to 5, characterized in that in the case of a hydraulically or pneumatically activatable actuator (50), a hydraulically or pneumatically effective piston surface (57) for generating the tensile force (53) corresponds substantially to a hydraulically or pneumatically effective piston surface (59) for generating the compression force (54).

7. Activating device (49) according to one of Claims 1 to 6, characterized in that the actuator (50) for generating opposite relative movements (62) between the at least one traction member (51) and the at least one compression member (52) is designed so as to be dual-action, or so as to have at least one restoring spring.

8. Activating device (49) according to one of the preceding claims, characterized in that the at least one traction member (51) is furthermore designed to transmit a compression force (54), and / or the at least one compression member (52) is furthermore designed to transmit a tensile force (53).

9. Activating device (49) according to one of Claims 1 to 7, characterized in that a. provided are at least two traction members (51) which are diametrically opposite in terms of the at least one compression member (52), or in that b. provided are at least two compression members (52) which are diametrically opposite in terms of the at least one traction member (51), or in that c. provided are at least two traction members (51) and at least two compression members (52) which are disposed so as to be mutually symmetrical in such a manner that the introduction of the tensile and compression forces (53, 54) takes place substantially without a momentum.

10. Machining system (200) having an activating device (49) according to one of the preceding claims and a device (100) for fixing workpieces (10) for mechanical machining.

11. Machining system (200) according to Claim 10, characterized in that provided is at least one machining station (201) for the mechanical machining of a workpiece (10) held in the device (100), into which the device (100) is able to be fed and discharged by means of a transport device (202).

12. Machining system (200) according to one of Claims 10 or 11, characterized in that the machining system (200) has a restoring device (25) for displacing clamping means (14) of the device (100) to a resting position, wherein the restoring device (25) is formed by the activating device (49) according to one of Claims 1 to 9.