GB2275631A

GB2275631A - Tool turret

Info

Publication number: GB2275631A
Application number: GB9318752A
Authority: GB
Inventors: Erhard Schalles; Reinhard Schroder
Original assignee: Gildemeister AG
Current assignee: DMG Mori AG
Priority date: 1992-10-17
Filing date: 1993-09-09
Publication date: 1994-09-07
Anticipated expiration: 2013-09-09
Also published as: FR2696962A1; GB2275631B; IT1262865B; ITGE930080A1; GB9318752D0; ITGE930080A0; DE4235095C2; DE4235095A1; FR2696962B1

Description

2275631 TOOL DIAL The invention relates to a tool dial.

Such a tool dial may have a dial housing and a dial plate, which, by means of a hollow shaft acted upon by a switch drive, is rotatably mounted in the dial housing and is able to be locked relative thereto in selected angular positions. More particularly, such a tool dial typically includes tool receiving means for stationary and rotatable tools, wherein the rotatable tools have tool shafts with drive pinions at their free end which are insertable into the tool receiving means and by means of which an output pinion of the gear of a tool drive is able to engage with a tool drive shaft provided in the hollow shaft.

Patent Specification EP-A2-461 357 discloses a tool dial in which a tool plate is locked by a gear rim to a locking member which engages two plane tooth configurations arranged concentrically to each other. One of the plane tooth configurations is fixedly connected to the tool plate and the other is fixedly connected to the dial housing. This means that the tool plate does not have to be moved in the direction of the switch axis for switching or for locking the tool plate. Such movement brings sealing problems owing to the cooling medium which wets the tool plate. The tool drive is fed through a bore in the switch shaft by way of two bevel gears into the tool plate. The driving bevel gear sits on a displaceable shaft which can be coupled to the tool shaft. With this tool dial, the tool is only ever driven in the operating position, and this results in improved utilisation of the installed tool drive capacity.

Such a tool dial however has the drawback that an additional drive has to be fitted for the coupling member. In the decoupled state the tool shaft is abandoned, so that the exact position of the tool is lost and uncontrolled rotational movement of the tool can occur. Finally, during the coupling operation. a search operation is necessary so that the drive shaft can be connected to the coupling pin.

Another tool dial is disclosed in German Patent Specification DE-C-37 30 561 cl, the dial plate of which can be switched about a dial axis by virtue of a hollow shaft. The dial plate is secured in its respective working position by means of two plane gear rims which are 2 oriented towards each other. For switching purposes, the dial plate must therefore be moved in the direction of the dial switch axis. This means that costly sealing measures have to be taken regarding the cooling medium and chips between the dial plate and the dial housing.

A tool plate which is fully equipped with tools is also very cumbersome and cannot therefore be shifted quickly.

The dial plate has radial spindles to which tools can be fixed. The respective spindle in the operating position is driven by a drive shaft which is mounted at a spacing away from the central switch axis.

The tool shaft carries a bevel gear which is engageable with, and disengageable from, a bevel gear of the drive shaft by axially moving the dial plate. The tool shafts which are not in use are prevented from rotating by a locking pin. The gear outside the switch shaft requires a lot of space in the dial housing, so that the dial housing is unnecessarily large and a locking device cannot be accommodated without axially moving the dial plate.

According to one aspect of the invention, there is provided a tool dial comprising a dial housing and a dial plate having tool receiving means for stationary and rotatable tools with the dial plate rotatably captive in the dial housing by way of a hollow shaft upon which a switch drive can act. wherein the dial plate is lockable in selected angular positions relative to the dial housing, the rotatable tools have tool spindles with drive members at their free ends which can be inserted into the tool receiving means to engage an output member of a tool drive which includes a tool drive shaft provided in the hollow shaft. a sleeve is disposed non-rotatably between the hollow shaft and the tool drive shaft, in which sleeve is mounted an intermediate shaft for the driven tools of each operating position. the intermediate shaft can be connected, by way of at least one gear wheel thereon, to the tool spindle and to the tool drive shaft and means are provided in the dial plate to prevent rotational movement of those tool spindles which are not to be driven.

Thus, there is provided. for a tool dial having a tool dial plate which is not lifted out during switching of the dial, a drive only for the tools which are being rotatingly driven and which are respectively disposed in the operating position, and the position of rotation of the 3 tool is known whatever the switching position of the dial plate and is guaranteed to be kept.

According to another aspect of the invention. there is provided a tool dial comprising a dial housing and a tool carrier with tool receiving means for stationary and rotating tools which is rotatably mounted relative to the dial housing about a switch axis and which can be locked in selected angular positions relative to the dial housing, wherein the rotating tools have tool spindles with drive pinions which can be inserted into the tool receiving means and by means of which an output pinion of the gear of a tool drive can be engaged, the tool carrier is mounted non-displaceably relative to the dial housing, nondisplaceably mounted in the dial housing in each operating position is an intermediate shaft for the driven tools, which shaft carries the output pinion. the axis of the tool spindle, the axis of the intermediate shaft and the switch axis intersect at a point, the axis of the intermediate shaft differs from the switch axis and the axis of the tool spindle. a gear rim provided concentrically to the switch axis engages all drive pinions of the tool spindles which are not disposed in the working position, and the gear rim has recesses in its tooth configuration for the drive pinions in the working positions.

When automatically changing rotatingly driven tools and for workpiece take-off chucks fixed to tool spindles in the tool dial for processing the backs of partially worked workpieces it is desirable to ensure that in every switching position of the tool dial plate a predetermined angular position of the tool spindle is guaranteed. This is made possible with a tool dial according to the invention which has a central tool drive, the dial plate of which exclusively performs a rotational movement about the switch axis relative to the dial housing.

To transmit the tool drive. it is generally sufficient to provide a gear wheel on the intermediate shaft if the tool drive shaft and the tool shaft can be connected directly to the gear wheel on the intermediate shaft. In instances where this is not possible because of space availability, two gear wheels preferably have to be arranged on the intermediate shaft, of which gear wheels one meshes with the tool spindle and the second meshes with the tool drive shaft. Tools of all known dial types can be driven using the same drive concept. By virtue 4 of the f act that the tool receiving means and switch axis can be oriented differently, slight differences may result in the gear.

Overloading of the drive wheels of the gear for driving the tool can be avoided by the switching process, if the engaging gear wheels are separated from one another prior to switching. To this end, the sleeve in which the intermediate shaf t is mounted is preferably axially displaceable. The axial displacement can be derived from the drive for the dial locking. For example. it is possible to use simply a toothed ring to prevent the tool spindle from rotating, on which toothed ring the gear wheels of the tool spindles roll down if the dial is switched. After the tool dial plate has been switched through 360 degrees, if the number of teeth of the toothed ring is a whole number multiple of the number of teeth of the drive wheel. the tool spindle reaches exactly the same position.

Overloading the gear wheels of the tool drive is also avoided if a simple roll-down movement between the gear rim and drive gear wheel of the tool spindle. on the one hand. and between the drive wheel and output wheel of the intermediate shaft, on the other hand, takes place. These conditions are given if the axes of the workpiece spindles, the intermediate shaft and the switch axis intersect at a point. A drum dial is a special case where thepoint of intersection is at infinity.

A switch drive for the tool dial is not required if the switching movement is derived from the tool drive. To that end, during the switching operation, an optional gear rim which is non-rotatably connectable to the dial plate may engage with a gear wheel on the intermediate shaft. The coupling can be effected by axially displacing the gear wheel which can be derived from the indexing drive. The invention is diagrammatically illustrated by way of example in the accompanying drawings, in which: 30 Figure 1 is a cross-section through a first embodiment of a tool dial according to the invention in the form of a star dial; Figure 2 is a cross-section through a second embodiment of a tool dial according to the invention also in the form of a star dial; 35 Figure 3 is a cross-section through a third embodiment of a tool dial according to the invention in the form of a drum dial; Figure 4 is a cross-section through a fourth embodiment of a tool dial according to the invention also in the form of a drum dial; Figure 5 is a cross-section through a fifth embodiment of a tool dial according to the invention in the form of a crown dial.

Referring to the drawings and firstly to Figure 1, mounted rotatably but non-displaceably in a dial housing 1 is a hollow shaft 2, to which a dial plate 3 is fixed. The hollow shaft 2 is driven by way of a gear wheel drive 4 and a drive belt 5 by a switch drive 6.

Coaxially mounted in the hollow shaft 2 is a drive shaft 7 which can be displaced rotatably by a tool drive 8. At the dial plate end the central shaft 7 carries a bevel gear 9 which engages with a bevel gear 10 mounted at one end of an intermediate shaft 11. At its other end the intermediate shaft 11 has an output pinion 12 which meshes with the drive pinion 13 or a tool spindle 15 which is inserted into a tool 15 receiving means 14. The output pinion 12 and the drive pinion 13 are spur gears in the embodiment shown. The intermediate shaft 11 is mounted in a sleeve 16. which, in the example shown, is divided into two parts for assembly purposes and is in the form of a sleeve tube 16a and a sleeve head 16k. The sleeve 20 16 is provided with an annular groove 17 into which a journal 18 engages which passes through the hollow shaft 2, and engages another annular groove 19 of a piston 20 which has a plane toothed configuration 21 on its end face. The plane toothed configuration 21 engages two annular, coaxial companion toothed configurations 22, 23, of which one is fixedly connected to the dial housing 1 and of which the other is fixedly connected to the dial plate 3.

In this embodiment. the tool drive of one tool is shown in a different dial switching position which has been displaced through 180 degrees. The drive is derived from the same bevel gear 9 of the tool drive shaft 7 by a further intermediate shaft 24 connected to a further tool spindle. With this arrangement it is possible for more than one tool spindle 15, 25. to be driven by the same tool drive. This feature is included in embodiments used in, eg, companion spindle turning machines or when workpiece pick-up chucks are mounted in the tool dial to drive the workpiece which the rear face thereof is worked. Transmission to the tool spindle 25 is effected by way of spur gears 6 26, 27 which undergo translatory movement opposite and different to It that of the embodiment shown at the lef t side of Figure 1. This is obtained in that an axis 28 of a tool receiving means and thus that of the tool spindle 25 is at a greater spacing away from the dial housing 1 than the tool spindle 15 in the left-hand operating position. By suitably positioning the tool receiving means 14 it is possible for the' tool drive to be suited to requirements in respect of speed of revolution and torque. A milling tool 29 can be driven, for example, at a slower revolutionary speed and with a greater torque than a borer 30.

Cams 31, 32 are provided on the sleeve head 16h and act upon springloaded index bolts 33, 34. The index bolts 33. 34 are displaceably mounted in a cover 35 which closes off the dial plate 3. One index bolt 33, 34 is provided for each tool receiving means 14, the pin engaging the toothed configuration of the respective drive pinion 13 and thus preventing the tool spindle 15, 25 from rotating if it is not disengaged from the cams 31, 32 of the sleeve head 16h.

Switching of the dial is as follows: after a workpiece has been worked with a stationary or rotating tool. a pressure medium (eg a fluid) is forced into a pressure chamber 36 formed by the piston 20. The piston 20 moves axially downwardly and disengages the plane toothed configurations 21 of the piston 20 and from the toothed configurations 22, 23. Movement of the piston is transmitted by the journal 19 to the sleeve 16 which is displaced to the same extent and in the same direction. Sifice the intermediate shafts 11, 24 are mounted in the sleeve 16, the toothed configuration of the spur gears 12, 13, 26, 27 is disengaged. The tool drive shaft 7 can also be axially displaced by a ball bearing. The cams 31. 32 on the sleeve head 16h release the index bolts 33. 34 which fall into the toothed configuration of the drive pinions 13, 27 due to spring force.

During subsequent switching of the dial plate 3. the journal 19 slides in the annular groove 17 of the sleeve 16, on the one hand, and in the annular groove 19 of the piston 20, on the other hand. In this way, the sleeve 16 is prevented from having to rotate. Displacement of the sleeve 16 clearly must not be derived from the locking movement of 7 the spur gearing 21. In this case, a separate drive must be provided for displacement of the sleeve 16.

With the tool dial according to Figure 2, a hollow shaft 202 is also rotatably mounted in a dial housing 201, to which shaf t a dial plate 203 is fixed. The hollow shaft 202 can be rotated about an axis 204 by way of a drive belt 205 by a switch drive 206. The switch drive 206 and the gear are indicated by broken lines since the switching movement can also be derived from a tool drive 208. as will be mentioned later. The dial plate 203 is locked by plane toothed configurations 221, 222, 223 in its switching position wherein one plane toothed configuration 221 is arranged on the end face of a piston 220, whilst the companion toothed configuration 222 of a first spur gear is connected to the dial plate 203 and another companion toothed configuration 223 on a concentric gear rim is connected to the dial housing 201.

By way of a toothed belt drive 217 the tool drive 208 drives a tool drive shaft 207 of the tool drive which is rotatably mounted inside a sleeve 216 and carries a gear wheel 209 at the end facing the dial plate. The gear wheel 209 drives an output pinion 212 which is fixed to an intermediate shaft 211. The intermediate shaft 211 is rotatably mounted in the sleeve 216. The output pinion 212 can be engaged with a drive pinion 213 of a tool spindle 215. Arranged on the sleeve 216 is also a bevelled gear rim 218 which extends over all the tool spindles 215 of the dial plate 203 and which engages all the drive pinions 213, with the exception of those which are being rotated. To that end the bevelled gear rim 218 has, at the location(s) where tools 230 are being driven, recesses 210 in the toothed configuration which release the drive pinion 213 as soon as it has engaged the toothed configuration of the output pinion 212. This engagement takes place before the dial plate 203 has reached its final operating position.

Figure 2 shows a second switching position where a second tool 231 is to be driven rotatingly by an intermediate shaft 211 shown by broken lines.

The switching movement can also be derived from the tool drive 208. To that end, a piston 220 is always connected by way of an annular groove 232 to push rods 233 which are guided in the hollow 8 shaft 202. The push rods 233 are fixed to an inner toothed ring 234 which engages gear wheel(s) (219) when the dial plate 203 is released. Rotational movement of the tool drive shaft 207 is now converted into a switching movement of the hollow shaf t 202 by the gear wheel 209 and the gear wheel 219.

During the switching movement, the drive pinions 213 roll down on the bevelled gear rim 218. The number of teeth of the bevelled gear rim 218 should therefore be a whole number multiple of the number of teeth of the drive pinion 213 so that the tool spindle 215 returns to exactly the same position of rotation after the dial plate 203 has been switched through 360 degrees.

The inner toothed ring 234 can also be used to synchronise the drive pinion 213 and the output pinion 212 when the dial is being switched with its own switch drive 206. When one of the driven tool spindles 215 is switching through the operating position, the tool spindle 215 should not be held. Therefore, the output pinion 212 has to move at a synchronous revolutionary speed during engagement with the drive pinion 213. In this way, the rotational position of the tool spindle 215 is ensured with tool dials wherein the bevelled gear rim 20 218 and the output pinion 212 are disposed on opposite sides of the drive pinion 213. The rotational position of the tool spindle is also known at any time when the tool drive 208 is being controlled synchronously to the switch drive 206. Figure 3 shows a drum dial wherein a switch axis 304 and a tool receiving means 314 are parallel to each other. As in the preceding embodiments, a tool drive shaft 307, a sleeve 316 and a hollow shaft 302 are mounted in the dial housing 301. The tool drive shaft 307 is rotated by a tool drive 308 by a drive belt 310. A dial plate 303 is fixedly connected to the hollow shaft 302.

The dial plate 303 is fixed in its switching positions by plane toothed rings 321, 322. 323. one of which rings is screwed to the dial plate 303 and another of which, arranged concentrically thereto, is screwed to a dial housing 301, whilst the third plane toothed ring 321 which is oppositely disposed to the two others with its toothed configuration and which covers over the first two with its toothed configuration is integrally formed with a piston 320. The piston 320 9 and the dial housing 301 form two pressure chambers 324. 325 whereby the plane toothed configurations are engageable with, and disengageable from, the companion toothed configurations 322, 323.

A gear wheel 309 which engages with an output pinion 312 and which is carried by the tool drive shaft 307 drives a tool 330 disposed in the operating position. The output pinion 312 is rotatably mounted to an intermediate shaft 311 in a sleeve 316. A drive pinion 313 of a tool spindle 315 meshes with the output pinion 312. Therefore, only one tool 330 is driven. The number of output pinions 312 mounted in the sleeve 316 and engaging with the gear wheel 309 must equal the number of tools which are simultaneously to be driven. Preferably, in the case of drum dials, only one tool is in the operating position, so that only one output pinion 312 has to be provided. Both one driven tool 330 and a fixed tool can be inserted in each tool receiving means.

To change the tools automatically or to rotate workpiece take-off chucks inserted into the tool receiving means 314. the position of rotation of the tool 330 or of the take-off chuck has to be known at any time, and can be done by way of a rotational angle indicator on the tool drive 308. The known rotational position of the tool 330 must therefore not be lost when the tool 330 is switched by the dial from the operating position into the idle position. In order to ensure the rotational position of the tool 330. an inner gear rim 318 is provided with which all the tool spindles 314 engage by way of their drive pinions 313 which do not mesh with an output pinion 312 of the tool drive 308. The inner gear rim 318 is connected to the fixed sleeve 316. In the operating position where the tool spindle 315 is able to rotate, the toothed configuration of the inner gear rim 318 is at a spacing away. The recess 305 is selected therein in such a way that the drive pinion 313 engages with the toothed configuration of the inner gear rim 318 when the dial plate 303 is being switched, before the toothed configuration of the output pinion 312 is disengaged.

Preferably, the number of teeth of the inner gear rim 318 should be a whole number multiple of the number of teeth of the drive pinion 313.

since then the workpiece spindle 315 adopts exactly the same position as before, after the dial plate 303 has performed one complete rotation.

If the dial switching is derived from the tool drive 308, the piston 320 is connected to push rods 317 in such a way that the push rods transmit the stroke movement of the piston 320 to the toothed ring 319, but are freely movable in the peripheral extent relative to the piston 320. The toothed ring 319 engages with a gear wheel 328 on the intermediate shaft 311. The tool drive 308 therefore rotates the dial plate 303. The inside of the tool dial is closed by a cover 326, on the one hand. and by a base 327, on the other hand. Since the dial plate 303 does not have to move in the direction of the switch axis 304 during the switching operation, all the sliding faces are able to be sealed efficiently and the results of suction are avoided due to alternating cavities.

To secure the position of the tool spindle both an internal- and external toothed gear rim can be used. Figure 4 shows an outer toothed gear rim 418 with a drum dial corresponding to Figure 3. representative of the rest of the dial designs. Fixed to tool spindles 415 are drive pinions 413 which in width are such that their toothed configuration can mesh both with that of the output pinion 412 and with that of the gear rim 418. The arrangement requires its own switch drive for dial switching. This is effected by a switch drive 403 which transmits rotation by way of a toothed belt 404 and a stepped gear 405 onto a hollow shaft 402 mounted in a dial housing 401. Provided in the switching position in which a tool 417 is driven is a recess 411 in the gear rim 418. Indexing of the dial plate and of the tool drive is the same as in Figure 3.

When the gear rim 418 and the output pinion 412 are arranged on the same side of the tool spindle 415 the drive pinion 413 is able to roll down on the gear rim 418 and the output pinion 412 freely on the gear rim 418 and the output pinion 412, so that synchronisation is not necessary.

The crown dial according to Figure 5 likewise has a tool carrier 503 which is not deployed and which is rotatably mounted in the dial housing 501 and which is indexed relative thereto by three concentrically arranged plane toothed rings 521. A tool spindle 515 disposed in the operating position is then the only one to be driven so that the output of a tool drive 508 is transmitted totally by way of an intermediate shaft 511 to the tool spindle 515 in a processing station 522. The position of rotation of all the other tool spindles 515 is kept by way of a gear rim 518 on which the tool spindles 515 roll down during switching of the dial, by virtue of the synchronisation wheels 517.

The tool carrier 503 is switched by a switch shaft 502, the axis of which is transverse to the switch axis and a tapered toothed configuration 519 is switched through a predetermined angle. A switch drive 506 is connected by way of a gear 505. not shown fully, to the switch shaft 502. The tool is driven by way of a tool drive shaft 507, a central wheel 509 and a bevel gear 510 onto the intermediate shaft 511. The intermediate shaft 511 is mounted in the dial housing 501 and transmits an output pinion 512 which meshes with the drive pinion 513 on the tool spindle 515. A switching axis 504 and also the axes of the tool spindles 515 and of the intermediate shaft 511 intersect at a point. The drive pinion 513 and the synchronisation wheels 517 therefore freely engage with the output pinion 512 or the gear rim 518.

When the output pinion 512 and the gear rim 518 are arranged appropriately adjacent to each other on the same side of the tool spindle 515, engagement can be effected into the two toothed configurations by way of one single broad bevel gear 516.

References herein to a "tool dial" may be taken to embrace equivalent terminology such as "turret". Terms such as "dial plate" and "dial housing" should be construed accordingly.

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Claims

1. A tool dial comprising a dial housing and a dial plate having tool receiving means for stationary and rotatable tools with the dial plate rotatably captive in the dial housing by way of a hollow shaf t upon which a switch drive can act, wherein the dial plate is lockable in selected angular positions relative to the dial housing, the rotatable tools have tool spindles with drive members at their free ends which can be inserted into the tool receiving means to engage an output member of a tool drive which includes a tool drive shaf t provided in the hollow shaft, a sleeve is disposed non-rotatably between the hollow shaf t and the tool drive shaf t, in which sleeve is mounted an intermediate shaft for the driven tools of each operating position, the intermediate shaft can be connected, by way of at least one gear wheel thereon, to the tool spindle and to the tool drive shaft and means are provided in the dial plate to prevent rotational movement of those tool spindles which are not to be driven.

2. A tool dial comprising a dial housing and a tool carrier with tool receiving means for stationary and rotating tools which is rotatably mounted relative to the dial housing about a switch axis and which can be locked in selected angular positions relative to the dial housing, wherein the rotating tools have tool spindles with drive pinions which can be inserted into the tool receiving means and by means of which an output pinion of the gear of a tool drive can be engaged, the tool carrier is mounted non-displaceably relative to the dial housing, nondisplaceably mounted in the dial housing in each operating position is an intermediate shaft for the driven tools, which shaft carries the output pinion. the axis of the tool spindle. the axis of the intermediate shaft and the switch axis intersect at a point, the axis of the intermediate shaft differs from the switch axis and the axis of the tool spindle, a gear rim provided concentrically to the switch axis engages all drive pinions of the tool spindles which are not disposed in the working position, and the gear rim has recesses in its tooth configuration for the drive pinions in the working positions.

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3. A tool dial according to claim 1 or claim 2, wherein the intermediate shaft has two gear wheels. of which a first meshes with the drive pinion of the tool spindle and of which a second meshes with a gear wheel of the tool drive shaft.

4. A tool dial according to claim 1. wherein the sleeve is mounted nonrotationally but axially displaceably in the dial housing.

5. A tool dial according to claim 4. wherein the tool drive shaft is mounted together with the sleeve so that it is axially displaceable in the dial housing.

6. A tool dial according to claim 3. wherein the tool receiving means and the tool spindles are oriented radially to the switch axis of the tool dial, an intermediate shaft is arranged parallel to each tool spindle disposed in the working position. and the drive pinion and the output pinion of the intermediate shaft are spur gears.

7. A tool dial according to claim 4. wherein the sleeve is connected to the drive of the locking device.

8. A tool dial according to claim 7. wherein the locking device comprises two concentric plane toothed rings into which a third plane toothed ring engages, which is axially displaced by a piston, and the sleeve is connected to the piston of the locking device.

9. A tool dial according to claim 4, wherein the means for preventing rotational movement comprises arresting pins which engage into the tool spindles or their drive wheel. the arresting pins being released by axial displacement of the sleeve.

10. A tool dial according to claim 1 or claim 2, wherein a gear rim is arranged stationarily concentrically to the switch axis. the toothed configuration of which engages with the drive pinions of the tool spindles and which in the respective operating positions of the tool spindles has recesses in the toothed configuration. in such a way that 14 the drive pinion is disengaged from the toothed configuration of the gear rim when it meshes with the output pinion of the intermediate shaft.

11. A tool dial according to claim 10, wherein the tool spindle and the intermediate shaft are disposed at an angle to each other and the drive pinion and the output pinion of the intermediate shaft are bevel gears and the stationary gear rim has a complementary tapered toothed configuration.

12. A tool dial according to claim 10, wherein the number of teeth of the gear rim is a whole number multiple of the number of teeth of the drive pinion.

13. A tool dial according to claim 2. wherein provided coaxially to the stationary gear rim is a further toothed ring which engages with a toothed wheel arranged on the intermediate shaft during the switching movement of the dial plate and rotates with the dial plate.

14. A tool dial according to claim 10, wherein the output pinion and the stationary gear rim engage with the drive pinion on mutually oppositely disposed sides.

15. A tool dial according to Claim 10, wherein the output pinion and the stationary gear rim engage into the drive pinion on the same side. and the toothed configuration of the drive pinion covers over the width of the toothed configuration of the output pinion and of the stationary gear rim.

16. A tool dial according to claim 10. wherein fixed to the tool spindle additionally to the drive pinion is another gear wheel which engages with the stationary gear rim.

17. A tool dial according to claim 2, wherein the axis of the tool spindle the axis of the intermediate shaft and the switch axis intersect at infinity.

18. A tool dial according to claim 1 or claim 2, wherein the tool spindle the intermediate shaft and the tool drive shaft are arranged parallel to each other and the output wheel. the drive wheel, the gear wheel of the tool drive shaf t and the stationary gear rim are spur 5 gears.

19. A tool dial according to claim 6, wherein the tool receiving means are distanced from the intermediate shaft(s) at different radial spacings and the output wheel(s) of the intermediate shaft together with the drive wheels of the tool spindles form various translatory movements.

20. A tool dial having a dial housing and a dial plate with tool receiving means for stationary and rotatable tools substantially as hereinbefore described and illustrated with reference to the accompanying drawings.