EP3357640B1 - Translatory tool module for finishing - Google Patents

Description

The invention relates to a translating tool module for fine machining according to the preamble of claim 1.

During shaping, e.g. NC milling or NC eroding could be automated to a large extent, a final surface finishing of the workpiece is usually done manually, e.g. fine grinding and polishing. Manual finishing is often the last process step and is therefore crucial for product quality. The quality and the time required depend exclusively on the individual skill of the craftsman.

Great efforts have so far been made to automate fine machining, with the developed solutions only being able to automatically grind, hon and polish simple, slightly curved surfaces. Against this background, there is a particular need from the end user's perspective to provide new tool systems for machining complex geometric elements. From the article " High-gloss free-form surfaces on steel tools "(F. Klocke et al .; wt Werkstattstechnik online volume 100 (2010) H. 6, pp. 480-486 ) a tool module of the type mentioned at the outset is known, which has a spindle interface for a machining spindle of a robot system. The mechanical rotary movement of the machining spindle is converted into a rotary movement of a fine machining element in the tool module. In order to set a contact pressure or normal force with which a processing membrane of the fine machining element is pressed onto the workpiece surface to be processed, 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.

From the DE 10 2012 108 594 A1 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.

From the DE 39 19 359 C1 a tool module, for example for a grinding machine, is known. 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. In the eccentric device, 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.

From the DE 690 09 890 T2 a closed tool unit is known, which is located within a system of further processing stations. However, 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.

This object is achieved in a tool module of the type mentioned at the outset with the characterizing features of claim 1. Advantageous exemplary embodiments are given by the dependent claims.

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. 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.

It can be provided that 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.

It can be advantageous to provide at least two pressure transmission devices. Several pressure transmission devices increase the adaptability of the tool module in terms of its contact pressure.

In a preferred embodiment, the tool module according to the invention can be connected to an external pressure control unit or an external pressure control unit. In this way, 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.

In a second alternative of the invention, 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. Along such a guide element, the translation unit can be directly or indirectly e.g. be mounted by means of a plain bearing or roller bearing. For reasons of stability, it can be advantageous to provide at least two rod-shaped guide elements. 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.

According to the invention, 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.

Thus, it can be provided that 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. In this case, 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.

Furthermore, 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.

In particular, it is advantageous to design the tool module such that the means for linearly guiding the translation unit have at least one fluid channel of the fluid pressure system. Thus, 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. It can be provided that 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. For the sake of simplicity, pressure transmission devices are assumed below. However, 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. However, 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. However, it is also possible for 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.

Finally, 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. For this purpose, 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. Analogously, the holder can have elements of an electrically operated contact pressure system.

Advantageous exemplary embodiments of the invention are illustrated below with the aid of figures.

Fig. 1:

ein erstes Werkzeugmodul im Querschnitt mit fünf Feinbearbeitungssegmenten und einstellbarem Translations-Hub,

Fig. 2:

das Werkzeugmodul gemäß Fig. 1 in einer perspektivischen Ansicht,

Fig. 3:

ein zweites Werkzeugmodul im Querschnitt mit fünf Zylindern , einer Schleifsteinwippe und einstellbarem Translations-Hub,

Fig. 4:

ein drittes Werkzeugmodul im Querschnitt mit fünf Zylindern, einem Polierhebel und einstellbarem Translations-Hub,

Fig. 5:

perspektivische Schnittansicht des Werkzeugmoduls gemäß Fig. 1 mit Darstellung von Fluidkanälen,

Fig. 6:

ein viertes Werkzeugmodul im Querschnitt mit zwei Zylindern, einer Schleifsteinwippe und festem Translations-Hub,

Fig. 7:

perspektivische Schnittansicht des Werkzeugmoduls gemäß Fig. 6 mit vergrößertem Ausschnitt zur Druckluftführung im Bereich des Schlittens und der Zylinder,

Fig. 8:

ein fünftes Werkzeugmodul in Seitenansicht mit fünf Zylindern, einer Schleifsteinwippe, einstellbarem Translations-Hub und einer eine Abwinklung aufweisenden Halterung,

Fig. 9:

ein sechstes Werkzeugmodul mit perspektivischer Darstellung der Antriebskinematik "Kniehebeltrieb" mit gegenläufigen Translationseinheiten, fünf Zylindern und festem Translations-Hub,

Fig. 10:

Seitenansicht der Antriebskinematik des Werkzeugmoduls nach Fig. 9,

Fig. 11:

perspektivische Darstellung des Werkzeugmoduls gemäß Fig. 9, jedoch mit Modulgehäuse und Spindel,

Fig. 12:

perspektivische Darstellung eines siebten Werkzeugmoduls mit außermittiger Anordnung der Feinbearbeitungselemente,

Fig. 13:

ein achtes Werkzeugmodul mit perspektivischer Darstellung der Antriebskinematik "doppelter Schubkurbeltrieb" mit gegenläufigen Translationseinheiten, fünf Zylindern und festem Translations-Hub

Fig. 14:

Schnittansicht der Antriebskinematik des Werkzeugmoduls nach Fig. 13.

It shows

Fig. 1:

a first tool module in cross-section with five finishing segments and adjustable translation stroke,

Fig. 2:

the tool module according to Fig. 1 in a perspective view,

Fig. 3:

a second tool module in cross section with five cylinders, a grindstone rocker and adjustable translation stroke,

Fig. 4:

a third tool module in cross section with five cylinders, a polishing lever and adjustable translation stroke,

Fig. 5:

perspective sectional view of the tool module according to Fig. 1 with representation of fluid channels,

Fig. 6:

a fourth tool module in cross section with two cylinders, a grindstone rocker and a fixed translation stroke,

Fig. 7:

perspective sectional view of the tool module according to Fig. 6 with enlarged cutout for compressed air routing in the area of the slide and the cylinder,

Fig. 8:

a fifth tool module in side view with five cylinders, a grindstone rocker, adjustable translation stroke and a bracket having an angle,

Fig. 9:

a sixth tool module with a perspective view of the drive kinematics "toggle lever drive" with opposing translation units, five cylinders and a fixed translation stroke,

Fig. 10:

Side view of the drive kinematics of the tool module according to Fig. 9 ,

Fig. 11:

perspective view of the tool module according to Fig. 9 , but with module housing and spindle,

Fig. 12:

perspective view of a seventh tool module with eccentric arrangement of the fine machining elements,

Fig. 13:

an eighth tool module with a perspective view of the drive kinematics "double slider crank drive" with opposing translation units, five cylinders and a fixed translation stroke

Fig. 14:

Sectional view of the drive kinematics of the tool module according to Fig. 13 .

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. 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. When the interface 2 rotates, 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.

In the carriage 8, five cylinder bores 10 are made, in each of which a piston 11 is arranged. For better clarity, only one of the five cylinder bores 10 shown and only one of the five pistons 11 are provided with a reference symbol. 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. For each cylinder bore 10 there is the possibility of influencing the fluid supply individually. In the example of the Fig. 1 this is done by means of setscrews 13 in feed bores, with which a supply line of the fluid from the respective guide element can be narrowed in cross section or closed entirely. The possibility of manipulating the fluid supply is shown in more detail below.

Fig. 2 shows the tool module Fig. 1 without spindle14 in a perspective view. In Fig. 2 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. At the same time, 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. In this regard, reference is made to the above description. 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.

In the embodiments according to the 1 to 3 are in particular 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. There is therefore a modular structure that allows easy replacement of components of the tool module for different types of machining and workpieces. This interchangeability is with the exception of Figures 6 and 7 also given in the exemplary embodiments presented below.

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. Instead of the finishing segments 12 ( Fig. 1 ) or the whetstone rocker 32 ( Fig. 3 ), 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. Four 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. Alternatively, 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. On the one hand, there is the possibility the fluid via only one of the sliding guide tubes 9 to the cylinder bores 10 (see Fig. 1 ) respectively. In this case, 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. On the other hand, there is also the possibility of applying different pressures in the individual sliding guide tubes 9 and feeding them to the respective cylinder bores 10. 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. Between the sliding guide tubes 9 are the cylinders 10 (not shown here) in the slide 8 (see Fig. 1 ) arranged. Via leads, not shown here, which are connected to the setscrews 13 (see Fig. 1 ) can be influenced, 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. Here, too, a grindstone rocker 52 with a grindstone 54 is provided on the translation unit 61. In the fourth tool module 50, however, 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. Compared to the embodiments in the Figures 1 to 3 the translation stroke in the third tool module 40 is realized via the exchangeable but not non-adjustable eccentric element 64 and the grinding stone rocker is guided via the two pistons 51 in the cylinders 60.

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. In 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. The supply of the fluid from the openings 59, which due to the cut is only hinted at half here can be seen to the cylinder bores 60 in the illustration Fig. 7 cannot be influenced. In other configurations, a (partial) closability, for example by means of screws, is conceivable.

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. By replacing the cylinder block 83 by a cylinder block with a different bend in the area of the fixation, the angle on the translation unit 81 can be changed in order, for. B. differently aligned, difficult to access workpiece surfaces. Of course, parts of the translation unit 81 that are changeable in their orientation are conceivable as an alternative. Instead of 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. In the same way, 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.

In order to generate an opposing translation movement of the two translation units 91 and 92, these are driven via an eccentric 111 toggle lever drive 102 and the spindle interface 2 mounted in a roller bearing 3 (not shown here, cf. Fig. 1 ) with the spindle 93 (see Fig. 11 ) connectable. 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. At their ends facing away from the respective pivot axes 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. 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. Like the seventh tool module 90, it 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. In this regard, reference is therefore made to the previous description. In contrast to the seventh tool module 90, the embodiment according to FIGS Fig. 13 and 14 however, 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. The connection of the thrust crank drive 120 to the spindle, not shown here, takes place via an interface 2 for spindles 14 mounted in roller bearings 3 (not visible here, cf. Fig. 1 ), on which the eccentric shaft 122 is fixed with the aid of the positioning element 121. 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.

In the exemplary embodiments of the seventh tool module 90 and the eighth tool module 119, too, the fluid for the cylinders 100 is supplied via the slide guide tubes 95 to 97.

The external structure of the module with the kinematics of 13 and 14 is comparable to that of Fig. 11 <b> List of reference symbols </b> 1 First tool module 34 Grindstone 2nd Interface for spindle 35 screw 3rd roller bearing 36 Base plate 4th Eccentric element 37 Inner wall of the sled 5 roller bearing 38 axis 6 Crank rod 40 Third tool module 7 bolt 41 piston 8th carriage 42 piston 9 Sliding guide tube 43 Translation unit 10th Cylinder bore 44 Polishing lever 11 piston 45 Swivel axis 12th Finishing element 46 Carrier element 13 Grub screws 47 bolt 14 spindle 48 Finishing element 14a Spindle housing 49 Joint socket 14b Spindle cover 49a Rod end 15 Outer wall 50 Fourth tool module 16 Guide tube end 51 piston 17th screw 52 Whetstone rocker 18th cover 54 Grindstone 19th Translation unit 55 screw 20th second tool module 56 Base plate 21st piston 57 Carriage housing 22 piston 58 cavity 23 poetry 59 openings 24th Fluid channel 60 Cylinder bores 25th Sliding seal 61 Translation unit 26 Sliding bush 62 Interface for spindle 27th Outlet opening 63 roller bearing 32 Whetstone rocker 64 Eccentric element 33 Grub screw 65 roller bearing 66 Crank rod 103 first leg 67 bolt 104 first connection plate 68 carriage 105 second connection plate 69 Sliding guide tube 106 second leg 70 cylinder 107 Swivel axis 71 piston 108 Scissors joint 74 Connecting room 109 Crank rod 75 Cylinder opening 110 Positioning element 80 Fifth tool module 111 Eccentric element 81 Translation unit 112 Counterweight 82 Whetstone rocker 113 Sled base 83 Cylinder block 114 Sled top 88 carriage 115 Intermediate plate 87 Carriage housing 116 Sled base 88 carriage 117 Sled top 89 Sliding guide tube 118 Intermediate plate 90 sixth tool module 119 eighth tool module 90a seventh tool module 120 Crank drive 91 Translation unit 121 Positioning element 92 Translation unit 122 Eccentric shaft 93 spindle 123 Eccentric disc 95 Sliding guide tube 124 Eccentric disc 96 Sliding guide tube 125 Crank rod I 97 Sliding guide tube 126 Crank rod II 98 Whetstone rocker 127 bolt 99 Whetstone rocker 100 piston 101 Base plate 102 Toggle drive

Claims (11)

1. Translationally acting tool module for finishing, comprising

   a) at least one finishing element (12, 34, 48, 54) having a pressing stroke,

   b) at least one pressing force system for influencing a pressing force from the at least one finishing element (12, 34, 48, 54) on a workpiece surface to be worked, and

   c) drive means for driving the at least one finishing element (12, 34, 48, 54),

   d) the at least one finishing element (12, 34, 48, 54) being arranged on at least one translation unit (19, 43, 61, 81, 91, 92) which is driven and linearly guided by means of the drive means,
   further comprising

   e) at least one transmitting device, arranged in the translation unit (19, 43, 61, 81, 91, 92) or in at least one of the translation units (19, 43, 61, 81, 91, 92) and intended for transmitting a force onto the finishing element (12, 34, 48, 54) or onto at least one of the finishing elements (12, 34, 48, 54), the transmitting device being

   - a pressure transmitting device, which comprises a piston-cylinder system and is operated by fluid pressure, or

   - an electrically operated force transmitting device, characterized by

   f) a machine interface (2) for connection to a machine, in particular a machine tool or a robot,

   g) the drive means comprising conversion means for converting a rotational movement of a machine element into the linearly guided translational movement of the at least one translation unit (19, 43, 61, 81, 91, 92),

   h) the machine interface (2) being set up for connection to a spindle (14, 93) and the conversion means being provided for converting a rotation of the spindle (14, 93).
2. Tool module according to claim 1, characterized in that the linear guidance of the translation unit (19, 43, 61, 81, 91, 92) or at least one of the translation units (19, 43, 61, 81, 91, 92) is oriented perpendicularly to the direction of the pressing stroke.
3. Tool module according to any of the preceding claims, characterized by at least one pair of contradirectionally driven and linearly guided translation units (19, 43, 61, 81, 91, 92).
4. Tool module according to claim 3, characterized in that the at least one pair of contradirectionally driven and linearly guided translation units (19, 43, 61, 81, 91, 92) is driven by means of a toggle lever drive (102) acting on a common drive shaft.
5. Tool module according to claim 3, characterized in that the at least one pair of contradirectionally driven and linearly guided translation units (19, 43, 61, 81, 91, 92) is driven by a drive shaft having two counter-oriented eccentrics (123, 124).
6. Tool module according to any of the preceding claims, characterized in that a translational stroke of the at least one translation unit (19, 43, 61, 81, 91, 92) can be set in a defined manner.
7. Tool module according to any of the preceding claims, characterized in that at least one fluid supply line (24) of a fluid line system, which fluid supply line is provided for supplying a fluid to the pressure transmitting device or to at least one of the pressure transmitting devices, can be adjusted in cross section manually or by machine at least at a contraction point.
8. Tool module according to any of the preceding claims, characterized in that means for linear guidance of the translation unit (19, 43, 61, 81, 91, 92) or at least one of the translation units (19, 43, 61, 81, 91, 92) have at least one fluid channel.
9. Tool module according to claim 8, characterized in that the means for linear guidance comprise at least one hollow tube (9) having the fluid channel (24) or at least one of the fluid channels (24).
10. Tool module according to claim 9, characterized in that the translation unit (19, 43, 61, 81, 91, 92) or at least one of the translation units (19, 43, 61, 81, 91, 92) is guided so as to indirectly or directly slide along the hollow tube (9, 69, 89, 95, 96, 97) or along at least one of the hollow tubes (9, 69, 89, 95, 96, 97).
11. Tool module according to any of the preceding claims, characterized in that the translation unit (19, 43, 61, 81, 91, 92) or at least one of the translation units (19, 43, 61, 81, 91, 92) has an angle with respect to the direction of the pressing stroke.

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