EP3357640B1 - Module porte-outils à action translatoire destiné au finissage - Google Patents

Module porte-outils à action translatoire destiné au finissage Download PDF

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Publication number
EP3357640B1
EP3357640B1 EP18153211.0A EP18153211A EP3357640B1 EP 3357640 B1 EP3357640 B1 EP 3357640B1 EP 18153211 A EP18153211 A EP 18153211A EP 3357640 B1 EP3357640 B1 EP 3357640B1
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EP
European Patent Office
Prior art keywords
tool module
translation
fluid
module according
translation unit
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EP18153211.0A
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German (de)
English (en)
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EP3357640A1 (fr
Inventor
Steffen Nitschke
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Individual
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Individual
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Priority to SI201830095T priority Critical patent/SI3357640T1/sl
Publication of EP3357640A1 publication Critical patent/EP3357640A1/fr
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    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B24—GRINDING; POLISHING
    • B24B—MACHINES, DEVICES, OR PROCESSES FOR GRINDING OR POLISHING; DRESSING OR CONDITIONING OF ABRADING SURFACES; FEEDING OF GRINDING, POLISHING, OR LAPPING AGENTS
    • B24B47/00—Drives or gearings; Equipment therefor
    • B24B47/02—Drives or gearings; Equipment therefor for performing a reciprocating movement of carriages or work- tables
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B24—GRINDING; POLISHING
    • B24D—TOOLS FOR GRINDING, BUFFING OR SHARPENING
    • B24D7/00—Bonded abrasive wheels, or wheels with inserted abrasive blocks, designed for acting otherwise than only by their periphery, e.g. by the front face; Bushings or mountings therefor
    • B24D7/06—Bonded abrasive wheels, or wheels with inserted abrasive blocks, designed for acting otherwise than only by their periphery, e.g. by the front face; Bushings or mountings therefor with inserted abrasive blocks, e.g. segmental
    • B24D7/066—Grinding blocks; their mountings or supports

Definitions

  • the invention relates to a translating tool module for fine machining according to the preamble of claim 1.
  • a force actuator is operated by means of pneumatics with which the contact pressure of the processing membrane is defined. This enables automatic compensation of the wear of the finishing element or of deviations in the surface profile and the inaccuracy of the robot control. A largely constant contact pressure can be achieved within one contact stroke using the air pressure in the pneumatics.
  • a tool module for fine machining of the type mentioned at the outset is known, in which a tool is connected via an eccentric device to a shaft which can be displaced in the axial direction relative to a hollow shaft.
  • the eccentric device translates a rotary drive by means of a spindle into a linear oscillation movement of an oscillation head carrying the tool.
  • the contact pressure on a workpiece is influenced by a pressure device which has at least one pneumatic cylinder.
  • the pneumatic cylinder is connected to a tool holder and acts on the entire oscillation head, whereby there is a relatively large mass between the pneumatic cylinder and the actual tool, for example a honing stone.
  • the JP 60186371 A discloses two variants of a tool module for fine machining, which can be connected to a spindle.
  • An eccentric device can be adjusted in its eccentricity by means of screws and serves to generate a linear movement component of a polishing tool.
  • a pneumatic or other influence on the contact pressure of the tool is not problematized.
  • the tool module comprises an eccentric device which is composed of an outer eccentric bushing driven by a motor and an inner eccentric.
  • the outer eccentric bushing and the inner eccentric can be rotated against each other in order to set different eccentricity in the inner surface of the inner eccentric.
  • an oscillation axis bush is mounted via roller bearings, in the bore of which an oscillation axis with a tool holder is in turn arranged.
  • the oscillation axis bush and the oscillation axis are mounted and guided in such a way that the oscillation axis only executes an oscillating translational movement when the eccentric device rotates.
  • the contact pressure of the tool on a workpiece is determined by means of a pneumatic system that does not follow the translational movement of the oscillation axis.
  • the oscillation axis is guided for the oscillation movement at one end of a piston of the pneumatics. This means that the pneumatics act indirectly on the tool via the oscillation axis.
  • a closed tool unit which is located within a system of further processing stations.
  • this unit which forms the preamble of claim 1, does not have a machine interface generating the translational movement of the tool for connection to a machine tool. It is an object of the invention to provide a tool module of the type mentioned at the outset, which has an alternative structure and enables a different processing method.
  • the tool module according to the invention is designed such that the contact pressure system comprises a fluid pressure system with a fluid line system for a fluid.
  • the contact pressure can thus be determined or co-determined by the pressure of the fluid.
  • the fluid pressure system has at least one pressure transmission device arranged in the at least one translation unit for transmitting the fluid pressure to the at least one finishing element.
  • the at least one pressure transmission device has a piston-cylinder system in which a fine machining element or a group of fine machining elements is coupled to a piston.
  • the pressure transmission device By arranging the pressure transmission device in the translation unit, the fluid responsible for the pressure can be guided very close to the associated fine-machining element, as a result of which the mass of the elements to be moved by the fluid pressure can be kept low.
  • the mechanism for transferring the fluid pressure to the finishing element can, for example, be limited to a piston of the piston-cylinder system which has a low mass.
  • a fluid supply line of the fluid line system with which the supply of the fluid to at least one of the pressure transmission devices is made possible, can be changed manually or mechanically in cross-section at at least one constriction point.
  • the changeability also includes the ability to completely separate a pressure transmission device from the rest of the fluid line system cordon off. In this way, the possibilities of distributing the fluid pressure to the various pressure transmission devices are increased.
  • the tool module according to the invention can be connected to an external pressure control unit or an external pressure control unit.
  • the fluid pressure can be controlled or regulated during workpiece machining and, if necessary, continuously and continuously adjusted.
  • the contact pressure of the fine machining element can thus be continuously adjusted according to the machining conditions.
  • the tool module according to the invention is designed such that the contact pressure system is electrically operated, the contact pressure system having at least one force transmission device arranged in the translation unit or in at least one of the translation units for transmitting a force to the precision machining element or at least one of the precision machining elements.
  • the power transmission device thus takes over the function of the pressure transmission device described above in a fluid pressure system in a corresponding manner.
  • the tool module can also be designed such that the power transmission device or at least one of the power transmission devices is inductive, e.g. with a coil and a magnetic bolt that acts directly or indirectly on a finishing element.
  • the tool module according to the invention can be designed such that the linear guidance of the translation unit or at least one of the translation units is oriented perpendicular to the direction of the contact pressure.
  • a linear, ie translatory movement of the at least one fine machining tool arranged on the translation unit facilitates a uniform flat surface Processing of flat as well as curved surfaces.
  • the advantage over rotary finishing is, on the one hand, the possibility of a high, homogeneous surface quality by avoiding rounding on edges and by avoiding surface ripple. Line polishes can also be created. In contrast to rotating face grinding tools, full-surface contact with less wear on the tool is possible.
  • the advantages mentioned are especially in sheet metal forming tools for the automobile body and in injection molding tools, for. B. for paintable products, high-gloss plastic parts or optical lenses made with impact presses of concern.
  • the linear guide of the translation unit is preferably oriented perpendicular to the direction of the pressing stroke of the at least one fine machining element. A surface can thus be machined with a translatory direction of movement perpendicular to the axial force setting.
  • At least one rod-shaped guide element can be provided for the linear guide.
  • the translation unit can be directly or indirectly e.g. be mounted by means of a plain bearing or roller bearing.
  • the guide element can be round, non-round or angular in cross section. If only a single rod-shaped guide element is used, a non-circular or angular cross-sectional shape can be advantageous for the stability of the guide.
  • the tool module has conversion means for converting a rotational movement of a machine or robot part into a translation movement guided by the guide means.
  • the machine interface is also set up for connection to a spindle.
  • the conversion means can convert the rotation of the spindle into the translation movement.
  • the implementation of the implementation means can be such that the length of the path of the translation movement is fixed or adjustable, for example by a variable eccentricity of an eccentric.
  • the tool module according to the invention can also be designed in such a way that at least one pair of oppositely driven and linearly guided translation units is provided. In this way, a machining operation can be achieved in an effective and simple manner without imbalance.
  • the pair of counter-rotating and linearly guided translation units is driven by means of a gear acting on a common drive shaft, preferably a toggle lever drive with a guided knee joint.
  • a gear acting on a common drive shaft preferably a toggle lever drive with a guided knee joint.
  • one or more counterweights may be required to completely eliminate imbalances.
  • the tool module according to the invention can also be designed such that the pair of counter-driven and linearly guided translation units by means of a drive shaft with two oppositely oriented eccentrics, e.g. by means of a double thrust crank drive.
  • the pair of translation units can be designed in such a way that operation without unbalance is possible without a counterweight.
  • the tool module according to the invention can also be designed such that a translation stroke of the translation unit can be set in a defined manner. This can e.g. can be achieved by using one or more eccentrics by changing the eccentricity.
  • the means for linear guidance perform a second function, namely the forwarding of the fluid, for. B. to the pressure transmission device or to at least one of the pressure transmission devices.
  • the guide means for linear guidance at least one of the fluid channel or at least one of the Hollow tube having fluid channels.
  • the hollow tube can be round in circumference, but can also have other cross-sectional shapes.
  • the hollow tube can, for example, form a rod-shaped guide element, as described above. If several rod-shaped guide elements are used, a single one, a number of parts or all guide elements can be designed as a fluid channel.
  • a fine machining element can be a single block-like element, on which several fluid-operated pressure transmission devices or electrically operated force transmission devices act simultaneously.
  • pressure transmission devices are assumed below.
  • power transmission devices of an electrically operated contact pressure system can always be used in an analogous manner.
  • the fine machining element or at least one of the fine machining elements can also cooperate with a single pressure transmission device.
  • the connection between the at least one finishing element and the pressure transmission device (s) can be rigid.
  • the connection can also be movable, for example if the fine machining element or at least one of the fine machining elements is arranged on a rocker articulated on the pressure transmission device.
  • the fine machining element or at least one of the fine machining elements to be arranged on a lever which is held by a pressure transmission device or by a plurality of pressure transmission devices and which allows movement with an axial component, that is to say in the pressure direction, relative to the axial direction of the spindle.
  • the tool module can be designed such that the translation unit or at least one of the translation units is at an angle to the direction of the pressing stroke.
  • the translation module can comprise a holder holding the at least one fine machining element, the orientation of which can be changed so that the machining surface of the at least one fine machining element can assume different angles to the longitudinal axis of the tool module.
  • a Different orientation of the holder can be achieved, for example, by designing fixing elements for the holder, such as screwing surfaces, differently, for example with different angles.
  • the holder can be a cylinder block, the cylinders of which are part of a cylinder-piston system for a pressure transmission device.
  • the orientation of the bracket can be achieved, for example, by the design of the cylinder block.
  • the holder can have elements of an electrically operated contact pressure system.
  • Fig. 1 shows in cross section a first tool module 1 with an interface 2 for receiving a spindle 14, of which a spindle cover 14a and a piece of a spindle housing 14b are shown here.
  • the tool module 1 is fixed on the spindle cover 14a.
  • the interface 2 is designed here, for example, as a hollow shaft taper (HSK) into which a spindle shaft, not shown here, engages.
  • the interface 2 is mounted in a roller bearing 3 and connected to an eccentric element 4 which can be set in, for example, 0.5 mm steps. Via a further roller bearing 5, a crank rod 6 is mounted on the eccentric element 4, in which a pin 7 engages.
  • HSK hollow shaft taper
  • the bolt 7 is fixed to a translation unit 19 comprising a slide 8, which is guided linearly via two sliding guide tubes 9. Of the sliding guide tubes 9 is in the Fig. 1 to recognize only one.
  • the eccentric element 4 the crank rod 6 and the bolt 7 cause the carriage 8 to translate back and forth along the sliding guide tubes 9.
  • each piston 11 holds, for example by means of an adhesive connection, a fine machining element 12 at its lower end, which serves for machining a workpiece surface, not shown here.
  • the fine machining elements 12 can be designed, for example, for grinding, polishing or honing.
  • the contact pressure of the fine machining elements 12 on the workpiece surface is determined by means of the cylinders 10 and the pistons 11 via an applied fluid pressure of the fluid pressure system, preferably a compressed air system, which can preferably be permanently adjusted to the machining conditions by a control and regulating unit.
  • Fig. 2 shows the tool module Fig. 1 without spindle14 in a perspective view.
  • ends 16 of the two sliding guide tubes 9 fixed with grub screws can be seen in an outer wall 15.
  • the carriage 8 has a side cover 18 fixed with screws 17, with which access to the cylinder bores 10 and the pistons 11 is protected.
  • the side cover 18 can have suitable elements, such as protrusions, which prevent the pistons 11 holding the finishing elements 12 from falling out.
  • Fig. 3 shows in cross section a second tool module 20, which with regard to the interface 2 for a spindle, the roller bearing 3, the eccentric element 4, the crank rod 6, the roller bearing 5, the bolt 7, the slide 8, the Sliding guide tubes 9 (only one visible) and the cylinder bores 10 with the first tool module 1 according to the Figures 1 and 2 essentially matches.
  • a fine machining element 12 instead of a plurality of fine machining elements 12 (see Fig. 1 ) there is a fine machining element in the second tool module 20 in the form of a grindstone 34 fixed to a grindstone rocker 32.
  • the grindstone rocker 32 is fixed to the two outer pistons 21 by means of fitting screws 35 and a base plate 36.
  • the inner pistons 22 rest only on the base plate 36 for power transmission.
  • the rocker 32 is mounted on an axis 38 fastened in the base plate 36.
  • the contact pressure exerted by the grinding stone 34 on a workpiece surface, not shown here, is determined by the pressure in the fluid pressure system and the sum of the individual piston surfaces.
  • the entirety of the pistons 21 and 22 with the base plate 36 is guided on the inner walls 37 of the carriage 8.
  • the supply of the fluid to the individual cylinder bores 10 is here, for. B. can be influenced via grub screws 33.
  • the fluid supply can optionally take place via one or more of the sliding guide tubes 9 or can also be completely prevented.
  • the pistons 11 and 21 and 22 and the components attached thereto such as. B. the finishing elements 12 and the grindstone rocker 32 with grindstone 34, 20 interchangeable, for example to adapt to differently machined surface contours.
  • the finishing elements 12 and the grindstone rocker 32 with grindstone 34, 20 interchangeable, for example to adapt to differently machined surface contours.
  • Fig. 4 shows in cross section a third tool module 40, which with regard to the interface 2 for a spindle, the roller bearing 3, the eccentric element 4, the crank rod 6, the roller bearing 5, the bolt 7, the slide 8, the sliding guide tubes 9 (only one visible), and according to the cylinder bores 10 with the first tool module 1 1 and 2 as well as the second tool module Fig. 3 essentially coincides, which is why on the relevant description is referred.
  • the third tool module 40 has a polishing lever 44 on the translation unit 43 as a processing element.
  • the polishing lever 44 is fastened to the carriage 8 via a pivot axis 45 and two carrier elements 46.
  • pistons 41 are articulated on the polishing lever 44 via a bolt 47 located on each piston 41.
  • the number of pistons 41 used for articulation on lever 44 can vary as required.
  • Unused cylinder bores 10 (only one in the figure) can be closed by additional pistons 42.
  • a fine machining element 48 is fixed by means of a joint socket 49 to a joint head 49a at the front end of the polishing lever 44 and permits fine machining of small, narrow and narrow tool surfaces, not shown.
  • the finishing element 48 is fixed to the lever via the joint head 49a in such a way that the finishing element 48 can assume different orientations.
  • the joint head 49a and the joint socket 49 are designed such that the fine machining element 48 can only pivot in the direction of the translation stroke of the translation unit 43. With the design of the lever 44, difficult or inaccessible workpiece contours can be machined. By applying different pressures such as Negative pressure, the contact pressure can be controlled differently up to the lifting of the polishing lever.
  • Fig. 5 relates to the first tool module 1 according to FIGS Figures 1 and 2 , the illustration being cut and individual components not being shown in order to clarify the fluid pressure system and the guidance of the fluid.
  • the slide 8 is shown with the side covers 18 and the finishing elements 12.
  • the fluid supply takes place via fluid channels (not shown) in the spindle 14 (see Fig. 1 ), which transfer the fluid to the fluid channels 24 of the tool module 1 with the aid of the seals 23, which run through the housing of the tool module 1 and open into the hollow slide guide tubes 9.
  • the slide 8 slides over the slide guide tubes 9 by means of slide bushings 25 having slide seals 25.
  • the slide 8 forms a closed cavity above the covers 18 around each of the slide guide tubes 9.
  • the slide guide tube 9 not used for the fluid can be made of solid material, a cavity for the fluid guide not having to be provided around this slide guide tube 9.
  • the slide guide tube 9 not used for the fluid can be made of solid material, a cavity for the fluid guide not having to be provided around this slide guide tube 9.
  • Via outlet openings 27, of which in Fig. 5 only for the front sliding guide tube 9 two can be seen the fluid from the sliding guide tubes 9 enters the aforementioned cavities of the carriage 8.
  • the cylinders 10 (not shown here) in the slide 8 (see Fig. 1 ) arranged.
  • the setscrews 13 see Fig. 1
  • the compressed air enters the cylinders 10 from the cavities surrounding the sliding guide tubes 9.
  • Fig. 6 shows in cross section a fourth tool module 50, which compared to the tool modules 1 and 20 of the Figures 1 to 3 has a slightly different structure.
  • a grindstone rocker 52 with a grindstone 54 is provided on the translation unit 61.
  • a slide 68 has only two, however enlarged cylinder bores 60, each with a piston 51.
  • the grindstone rocker 52 is fixed to the piston 51 by means of a base plate 56 and two screws 55, only one of which is shown here.
  • the pistons 51 are also supplied with fluid in the cylinder bores 60 via slide guide tubes 69, of which only one can be seen here.
  • the contact pressure with which the grindstone 54 acts on a workpiece (not shown here) is also determined via the pressure given in the fluid pressure system.
  • the movement of the carriage 68 along the slide guide tubes 69 is effected by means of an eccentric element 64 which is driven by a spindle, not shown here.
  • the eccentric element 64 can be replaced, for example in order to change the translation stroke of the translation unit 61.
  • the spindle engages in an interface to the spindle 62, which is mounted in the housing of the fourth tool module 50 via roller bearings 63.
  • the eccentric element 64 in turn engages in a crank rod 66, with a further roller bearing 65 for the bearing of the Eccentric element 64 in the crank rod 66 provides.
  • the carriage 68 is connected to the crank rod 66 via a pin 67.
  • Fig. 7 shows a perspective section through part of the fourth tool module 50 according to FIG Fig. 6 to provide an alternative routing of the fluid to the cylinder bores 60.
  • Fig. 7 shows cut open the slide 68, one of the cylinders 60 with the piston 51 located therein, the grindstone rocker 52 with grindstone 54.
  • the grindstone rocker 52 is fixed to the piston 51 of the slide 68 by means of screws 55 by means of screws 55.
  • Fig. 7 only an inner part of a slide housing with cavities 58 for the sliding guide tubes 69 is shown.
  • the fluid passes through openings 59 from the slide guide tubes 69 into the cavities 58 and via a connecting space 74 and a cylinder opening 75 opening into the cylinder bore 60.
  • Fig. 8 shows a perspective view of a fifth tool module 80, in which a slide 88 of a translation unit 81 has a preferably interchangeable angled cylinder block 83 on which a grindstone rocker 82 is mounted.
  • the bend of the cylinder block 83 is provided by its geometry and is therefore firmly incorporated.
  • the angle on the translation unit 81 can be changed in order, for. B. differently aligned, difficult to access workpiece surfaces.
  • parts of the translation unit 81 that are changeable in their orientation are conceivable as an alternative.
  • the grindstone rocker 82 other fine machining elements can also be provided.
  • the carriage 88 is the same as in the other tool modules 1, 20, 40 and 50 guided over slide guide tubes 89 and is supplied with fluid via the slide guide tubes 89.
  • the grindstone rocker 82 is also fixed here to pistons, not shown, the contact pressure of the grindstone rocker 82 on a workpiece being determined by the pressure in the fluid pressure system.
  • Fig. 9 shows the internal structure and the kinematics of a sixth tool module 90 with two translation units 91 and 92 which are separate from one another and operate in opposite directions.
  • Fig. 10 shows the internal structure of the sixth tool module 90 in a side view and Fig. 11 the complete sixth tool module 90 with part of a spindle 93.
  • the first translation unit 91 has a slide lower part 113 and a slide upper part 114, between which an intermediate plate 115 is arranged.
  • the lower carriage part 113 here has five non-visible cylinders for pistons 100.
  • the intermediate plate 115 takes over the function of cylinder heads and closes the cylinder bores (not visible here) of the lower part 113 of the slide, even where the opposite upper part 117 of the slide overlaps the intermediate plate 115.
  • the second translation unit 92 is constructed accordingly with the lower carriage part 116, the upper carriage part 117 and the intermediate plate 118.
  • the first translation unit 91 is mounted on a first sliding guide tube 95 and the second translation unit 92 on a second sliding guide tube 97 for a linear movement. Both translation units 91 and 92 are also mounted on a third sliding guide tube 96 for the linear movement and each carry a grindstone rocker 98 and 99.
  • the second translation unit 92 is constructed correspondingly to the first translation unit 91.
  • the pistons 100 of the first translation unit 91 are connected to the first grindstone rocker 98 via a base plate 101, as already shown in FIG Fig. 3 for the second tool module 20 is explained.
  • the second whetstone rocker 99 is mounted on the second translation unit 92 via cylinders and pistons (not visible here).
  • the invisible cylinders of the first translation unit 91 and the invisible cylinders of the second translation unit 92 are connected to a fluid pressure system, as is already shown in the tool modules described above.
  • the fluid is fed via the slide guide tubes 95, 96 and 97 to the translation units 91 and 92 mounted thereon.
  • a first leg 103 of the toggle lever drive 102 is connected via a first connecting plate 104 to the first translation unit 91 and a second leg 106 via a second connecting plate 105 to the second translation unit 92 via a pivot axis 107.
  • the two legs 103 and 106 of the toggle lever drive 102 are articulated to a knee joint 108, which in turn is connected to a crank rod 109.
  • the crank rod 109 Driven by an eccentric element 111 mounted on a drive shaft (not shown here), the crank rod 109 carries out a back and forth movement in the direction of its longitudinal extent, so that the pivot axes 107 and thus the translation units 91 and 92 along the slide guide tubes 95, 96 and 97 likewise perform a translational backward movement. and carry out movement, the movement of the two translation units 91 and 92 being opposite to one another.
  • the knee joint 108 must be guided linearly / translationally and moves at right angles to the translation units 91 and 92.
  • the eccentric element 111 is positioned and connected to a positioning element 110 in an interface (not shown) for spindles, on which the spindle 93 ( Fig. 11 ) can be connected.
  • the eccentric element 111 has a counterweight 112 to compensate for a possible imbalance.
  • the crank rod 109 can in principle be of any length, so that the translation units 91 and 92, shown here with grindstone rockers 98 and 99, but can also be equipped with alternative finishing elements, can be arranged laterally offset to the central longitudinal axis of the spindle 93.
  • the central longitudinal axis of the spindle 93 thus runs past the translation units 91 and 92.
  • This situation is in Fig. 12 shown using a seventh tool module 90b. In this way, for example, different geometrical conditions can be reacted to when a workpiece is accessible.
  • the Fig. 13 shows in perspective view and Fig. 14 in cross-section the inner structure and the kinematics and an eighth tool module 119.
  • the seventh tool module 90 has two opposing translation units 91 and 92, the structure of which corresponds to the translation units 91 and 92 according to the seventh tool module 90.
  • a double thrust crank drive 120 for transmitting the rotary movement of a spindle, not shown here, into an opposite translational movement of the translation units 91 and 92.
  • On the eccentric shaft 122 two eccentric disks 123 and 124 are arranged, with which a rotational movement of the eccentric shaft 122 is converted into translational movements of crank rods 125 and 126, which are each connected to the first translation unit 91 or the second translation unit 92 via a bolt 127.
  • the translation movement of the translation units 91 and 92 in the longitudinal direction of the crank rods 125 and 126 is mounted on the slide guide tubes 95 to 97.
  • the eccentric discs 123 and 124 are aligned so that an unbalance cannot occur.
  • the fluid for the cylinders 100 is supplied via the slide guide tubes 95 to 97.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Finish Polishing, Edge Sharpening, And Grinding By Specific Grinding Devices (AREA)

Claims (11)

  1. Module d'outil à action translatoire destiné au finissage, comprenant
    a) au moins un élément de finissage (12, 34, 48, 54) présentant une course de pression,
    b) au moins un système de force de pression destiné à influencer une force de pression de l'au moins un élément de finissage (12, 34, 48, 54) sur une surface de pièce à usiner, et
    c) des moyens d'entraînement destinés à entraîner l'au moins un élément de finissage (12, 34, 48, 54),
    d) l'au moins un élément de finissage (12, 34, 48, 54) étant disposé sur au moins une unité de translation (19, 43, 61, 81, 91, 92) entraînée et guidée linéairement au moyen des moyens d'entraînement,
    le module d'outil comprenant en outre
    e) au moins un dispositif de transmission disposé dans l'unité de translation (19, 43, 61, 81, 91, 92) ou dans au moins l'une des unités de translation (19, 43, 61, 81, 91, 92), servant à transmettre une force à l'élément de finissage (12, 34, 48, 54) ou à au moins l'un des éléments de finissage (12, 34, 48, 54), le dispositif de transmission
    - étant un dispositif de transmission de pression comprenant un système piston-cylindre et fonctionnant avec une pression de fluide,
    ou
    - étant un dispositif de transmission de force fonctionnant électriquement,
    caractérisé par
    f) une interface machine (2) destinée à être connectée à une machine, en particulier à une machine-outil ou à un robot,
    g) les moyens d'entraînement comprenant des moyens de conversion destinés à convertir un mouvement de rotation d'un élément de machine en un mouvement de translation à guidage linéaire de l'au moins une unité de translation (19, 43, 61, 81, 91, 92),
    h) l'interface machine (2) étant conçue pour être connectée à une broche (14, 93), et les moyens de conversion étant prévus pour convertir une rotation de la broche (14, 93).
  2. Module d'outil selon la revendication 1, caractérisé en ce que le guidage linéaire de l'unité de translation (19, 43, 61, 81, 91, 92) ou au moins de l'une des unités de translation (19, 43, 61, 81, 91, 92) est orienté perpendiculairement à la direction de la course de pression.
  3. Module d'outil selon l'une des revendications précédentes, caractérisé par au moins une paire d'unités de translation à entraînement opposé et à guidage linéaire (19, 43, 61, 81, 91, 92).
  4. Module d'outil selon la revendication 3, caractérisé en ce que l'au moins une paire d'unités de translation à entraînement opposé et à guidage linéaire (19, 43, 61, 81, 91, 92) est entraînée au moyen d'un mécanisme à levier à genouillère (102) sollicitant un arbre d'entraînement commun.
  5. Module d'outil selon la revendication 3, caractérisé en ce que l'au moins une paire d'unités de translation à entraînement opposé et à guidage linéaire (19, 43, 61, 81, 91, 92) est entraînée au moyen d'un arbre d'entraînement comportant deux excentriques orientés en sens contraire (123, 124).
  6. Module d'outil selon l'une des revendications précédentes, caractérisé en ce qu'une course de translation de l'au moins une unité de translation (19, 43, 61, 81, 91, 92) est réglable de façon définie.
  7. Module d'outil selon l'une des revendications précédentes, caractérisé en ce qu'au moins une conduite d'alimentation en fluide (24) d'un système de conduite de fluide, laquelle est prévue pour l'amenée d'un fluide vers le dispositif de transmission de pression ou vers au moins l'un des dispositifs de transmission de pression, peut être modifiée manuellement ou mécaniquement au moins au niveau d'une zone de rétrécissement dans la section transversale.
  8. Module d'outil selon l'une des revendications précédentes, caractérisé en ce que des moyens destinés au guidage linéaire de l'unité de translation (19, 43, 61, 81, 91, 92) ou au moins de l'une des unités de translation (19, 43, 61, 81, 91, 92) présentent au moins un canal de fluide.
  9. Module d'outil selon la revendication 8, caractérisé en ce que les moyens destinés au guidage linéaire comprennent au moins un tube creux (9) présentant le canal de fluide (24) ou au moins l'un des canaux de fluide (24).
  10. Module d'outil selon la revendication 9, caractérisé en ce que l'unité de translation (19, 43, 61, 81, 91, 92) ou au moins l'une des unités de translation (19, 43, 61, 81, 91, 92) est guidée par glissement indirectement ou directement le long du tube creux (9, 69, 89, 95, 96, 97) ou le long d'au moins l'un des tubes creux (9, 69, 89, 95, 96, 97).
  11. Module d'outil selon l'une des revendications précédentes, caractérisé en ce que l'unité de translation (19, 43, 61, 81, 91, 92) ou au moins l'une des unités de translation (19, 43, 61, 81, 91, 92) forme un angle en direction de la course de pression.
EP18153211.0A 2017-02-02 2018-01-24 Module porte-outils à action translatoire destiné au finissage Active EP3357640B1 (fr)

Priority Applications (1)

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SI201830095T SI3357640T1 (sl) 2017-02-02 2018-01-24 Translantorno delujoč orodni modul za fino obdelavo

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Application Number Priority Date Filing Date Title
DE102017102093.4A DE102017102093B4 (de) 2017-02-02 2017-02-02 Translatorisch wirkendes Werkzeugmodul zur Feinbearbeitung

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EP3357640A1 EP3357640A1 (fr) 2018-08-08
EP3357640B1 true EP3357640B1 (fr) 2020-05-13

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EP (1) EP3357640B1 (fr)
DE (1) DE102017102093B4 (fr)
PT (1) PT3357640T (fr)
SI (1) SI3357640T1 (fr)

Family Cites Families (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2095438A (en) * 1935-05-18 1937-10-12 Gardner Machine Co Work support oscillating mechanism
JPS60186371A (ja) 1984-03-06 1985-09-21 Toshiba Corp 研磨装置
DE8812160U1 (de) * 1988-09-26 1990-01-25 Supfina Maschinenfabrik Hentzen Gmbh & Co Kg, 42859 Remscheid Automatische spitzenlose Feinstbearbeitungsvorrichtung für oberflächenrotationssymmetrische Körper in einer Durchlaufmaschine
ES2056448T3 (es) * 1989-02-23 1994-10-01 Supfina Maschf Hentzen Procedimiento y aparato para el trabajo de afino o microacabado.
DE3919359C1 (en) 1989-06-14 1990-02-22 Maschinenfabrik Ernst Thielenhaus Gmbh, 5600 Wuppertal, De Grinding machine tool support with linear tool holder - has inner eccentric bush, holding vibration axis bush in its bore

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
None *

Also Published As

Publication number Publication date
DE102017102093B4 (de) 2018-12-20
SI3357640T1 (sl) 2020-09-30
EP3357640A1 (fr) 2018-08-08
PT3357640T (pt) 2020-08-25
DE102017102093A1 (de) 2018-08-02

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