EP0396876B1 - Turret punch press with rotatable tool - Google Patents

Description

The invention relates to a turret cutting press according to the preamble of claim 1.

In the manufacture of stamped parts by means of turret cutting presses, profiled tools are often used in the circumferential area, which are accommodated in the turret plate so as to be rotatable about their longitudinal axis and whose angular position can be controlled. Such turret cutting presses are known for example from DE 34 41 530 A1. It is characteristic of these that at least one special motor drive is required for driving the tools about their longitudinal axis, which is arranged in the peripheral region of the turret plate and can be coupled with individual tool sets. To transfer a specific tool set into its working position, which comprises rotating the turret plate into the respective punching position and rotating the tool set about its longitudinal axis into a specific angular position. the turret plates are first transferred to the punching position by actuating the drives assigned to them and fixed using special locking devices. The drive associated with the rotation of the tool about its longitudinal axis is then coupled to the respective tool and the tool is transferred to the desired angular position. To clearly position the tools with respect to their longitudinal axis, i.e. to set the angular position of the tools clearly, the tool sets must either be locked in their last rotational angle position before a turn of the plate, so that, starting from a given, stored rotational angle position, the rotation required to achieve a new rotational angle position can or must be calculated Before each change in the angle of rotation position, the exact zero position of the respective tool set must be set in order to reach the new angle position based on this.

These known turret cutting presses are therefore to be regarded as comparatively complicated in terms of the drive and control expenditure in relation to the system of turret adjusters and rotatable tools. In addition - due to the coupling process of the special drive associated with the rotation of the tool sets about their longitudinal axis - the synchronization of the rotational angle positions of the upper and lower tools must be closely monitored in order to avoid angle errors and thus tool damage. Furthermore, the coupling of a further drive in some cases causes further inaccuracies.

It is the object of the invention to construct a turret cutting press of the type mentioned in the introduction, in particular in terms of drive and control technology To simplify terms. This object is achieved in a generic turret cutting press by the features of the characterizing part of claim 1.

It is essential to the invention that the rotary movement required for driving a tool set about its longitudinal axis is now derived directly from an already controllable drive system which drives the turret plate about its axis of rotation. This only requires measures to selectively couple the drive mentioned either with the turret or with a specific tool set. In comparison to the prior art described at the outset, there is therefore no need to arrange a special drive, the sole purpose of which is to rotate a single tool set. Rather, use is made of an already available controllable drive for rotating the tool set. This entails a reduction in the structural, but also the control-related effort. If one assumes that in the known turret cutting press described at the outset, the drive for rotating individual tool sets about its longitudinal axis is located in the peripheral region of the turret plate, which inevitably entails a certain increase in the lateral space requirement, the result is obtained in the turret cutting press according to the invention Another advantage that their dimensions are not affected by the arrangement of individual tool sets, which can be rotated about their longitudinal axis, since drive elements, which serve for the couplable connection to the disk drive, and switchable functional elements, which serve for the optional transmission of a rotary movement to the turret plate or the tool set, in one the axis of the turret plate are arranged immediately adjacent area. This results in a compact design of the rotary drive of the tool sets, which does not impede the outside space.

The features of claims 2 and 3 are directed to alternative embodiments of the subject matter of the invention. According to this, each turret plate can have a single drive, from which the rotary movement of individual tool sets is derived. However, a common drive can also be provided for both turret disks, which are generally arranged one above the other, from which the rotary movements of all tool sets are derived. The latter makes a branching gear necessary to transmit rotary movements to both turret plates, but - as in the former case - eliminates the need for special synchronization devices to ensure the identical rotary movement of both turret plates. In this way, angle errors relating to the position of the upper and lower tools are avoided in the simplest way. Since the functional elements required for transferring a rotary movement to individual tool sets are each arranged on the sides of the turret plates facing away from one another, the often narrow space between the turret plates is not impaired by the rotary drive of individual tool sets.

The switchable functional elements of the drive consist, according to the features of claim 4, of a frictional torque transmission serving disc coaxially surrounding the axis of the turret and a controllable device for axial displacement of this disc. The latter device can in principle be of any design - especially However, their design as a pressure medium-operated device is advantageous. The other functional elements for actuating the tool drive consist of a gear transmission, by means of which a kinematic link can be established between a rotation of the disk drive shaft and the individual tool. If a frictional connection is established by means of the aforementioned disk, the entire turret plate, including the rotatable tool sets accommodated therein, moves like a rigid body. If, on the other hand, a frictional connection is not established via said disk and the respective turret plate is also locked, rotation of the disk drive shaft brings about a rotation of the tool set corresponding to the gear ratios of said gear transmission. Since all rotatable tool sets are coupled to the plate drive shaft in this sense, all the tool sets always rotate during a positioning movement of an individual tool set.

The features of claim 5 are directed to a specific embodiment of the controllable device for axially displacing the disk. This represents a particularly simple embodiment, which only presupposes the arrangement of an annular groove receiving the annular piston in the turret plate and the arrangement of pressure medium bores in the plate drive shaft. While the disk used for frictional torque transmission on the plate drive shaft is axially displaceable but non-rotatably connected to it, the ring piston mentioned only rotates the plate drive shaft when the pressure is applied, i.e. in the case where torque is transmitted to the turret plate.

The features of claim 6 are directed to an alternative embodiment of the controllable device, according to which the annular piston is formed in one piece with said disk. This results in a reduction in the number of components used overall and thus a simpler design of the turret plate, but at the same time the mass of the rotating parts with each rotation of the plate drive shaft is increased by the mass of the annular piston.

The features of claims 7 and 8 are directed to the design of the direct coupling of individual rotatable tool sets. It can be seen that all the drive elements of a single tool set are always arranged on the top or bottom of the respective turret plate, so that the space between the turret plates, which is narrow per se, is not impaired by the rotatable arrangement of individual tool sets. The upper tool can consist, in a manner known per se, of a stamp and stamp holder, the latter of which is axially displaceable but non-rotatably received in a bushing inserted in a bore in the upper turret plate, the latter being drivable via a toothing formed in the edge thereof. However, the socket can also be formed in one piece with the stamp holder, so that the number of components used overall is also reduced here.

The measures of claims 9 to 11 serve to largely eliminate any backlash in the area of the gear train serving to drive the tool sets and thus to increase the accuracy when adjusting the angle of rotation of a tool set. These measures, insofar as they relate to the adjustable configuration of the toothing of the bushes, serve for precise adjustment one zero position common to all rotatable tool sets. In conjunction with a largely gear-free gear transmission, synchronization errors between the rotational angle positions of the upper and lower tools are also avoided in this way, and at the same time the control engineering effort for positioning the tool sets is kept low.

Depending on the space required to accommodate the gear drives above and below the turret plate, any number of tool sets can be driven about their longitudinal axis. The gear transmission can also be replaced by another switchable transmission device that is true to the angle of rotation between the disk drive shaft on the one hand and the socket on the other hand.

• Fig. 1 eine perspektivische Darstellung einer Revolverschneidpresse;
• Fig. 2 eine Seitenansicht einer Revolverschneidpresse;
• Fig. 3 einen Axialschnitt des oberen Revolvertellers;
• Fig. 4 einen Axialschnitt des unteren Revolvertellers;
• Fig. 5 eine Draufsicht auf die Oberseite des oberen Revolvertellers;
• Fig. 6 eine Detaildarstellung des oberen Revolvertellers - in einer Draufsicht gesehen.

The invention will be explained in more detail below with reference to the embodiment shown in the drawings. Show it:

• Figure 1 is a perspective view of a turret cutting press.
• 2 is a side view of a turret cutting press;
• 3 shows an axial section of the upper turret plate;
• 4 shows an axial section of the lower turret plate;
• 5 shows a plan view of the upper side of the upper turret plate;
• Fig. 6 is a detailed view of the upper turret plate - seen in a plan view.

1 shows a turret cutting press according to the invention in its entirety. This consists of a standing C-shaped base frame 1, at the end region of which can be rotated about axes that run coaxially and vertically to one another and two turret disks 2, 3 are arranged at a distance from one another. The revolver plates 2, 3 carry a number of complete tool sets 4, 5 on their circumferential area, the structure of which will be explained in more detail below and which each consist of at least one stamp arranged in the upper revolver plate 2 together with the stamp holder and a die arranged in the lower revolver plate. The tool sets 4, 5 of the upper and lower turret plates 2, 3 are each in an axially aligned arrangement.

The base frame 1 serves, among other things, to accommodate the storage and drive of the turret plate and elements for actuating the press drive, which each interacts with a tool set located in the work station 6. 7 denotes a coordinate table which is known per se and which, by means of aids not shown in the drawing, serves for the exact positioning of the generally planar workpiece, for example a sheet metal, relative to the work station 6.

A DNC control 8, which is accommodated in a control cabinet placed next to the base frame, is used for programming or controlling the cutting press.

The punches of at least individual tool sets 4 are profiled in the peripheral area and these tool sets 4 are about their respective longitudinal axes 9 in their receptacles rotatably received in the turret adjusters 2, 3 and for this purpose the turret adjusters are provided with special drive elements 10, which will be explained below and serve to individually drive these individual tool sets about their tool axes 9.

With 11 the axis is schematically indicated, about which the turret plates 2, 3 can be rotated in the base frame 1.

In FIG. 2, 12 denotes an electric motor which serves to drive both the turret plates 2, 3 around their axes 11 and the tool sets 4 around their axes 9 in a manner to be described in more detail below. For this purpose, the motor 12 fixedly mounted in the base frame 1 is connected via a toothed belt 13 to an intermediate shaft 14 mounted in the base frame 1. The connection is made via belt wheels 15, 16 arranged on the output shaft of the motor 12 on the one hand and the intermediate shaft 14 on the other hand. The motor 12 is designed to be NC-controllable in a manner known per se and is operatively connected to the DNC controller 8 in a manner not shown in the drawing.

The intermediate shaft 14, which is mounted vertically in the base frame 1, is in turn connected via toothed belts 17, 17 'to pulleys 18, 18', the latter of which are each arranged on the disk drive shafts 19, 19 'running in the direction of the axes 11. The toothed belts 17, 17 'are connected to the intermediate shaft 14 again via belt wheels 20, 20' arranged on the latter. The belt drives which can be defined by the pulleys 19, 20 in connection with the belt drive 17 on the one hand and by the belt pulleys 19 ', 20' in connection with the belt drive 17 'on the other hand each serve the drive of the upper turret plate 2 and of the lower turret plate 3 and, moreover, as will be explained in the following, the rotary drive of individual tool sets 4.

The plate drive shafts 19, 19 'are each received in bearings whose bearing housings 21, 21' are held in the base frame 1. Locking devices 22, 22 'are used to lock the turret plates 2, 3 in certain rotational angle positions, which are also shown in more detail below. Another motor, which serves the actual press drive and is operatively connected via a cardan shaft 23, an eccentric 24 to the press ram 25, to the latter to which the punch located in the work station 6 is coupled, is not shown in the drawing.

Fig. 3 shows the structure of the upper turret 2 in an axial section. The disk drive shaft 19 is mounted on the one hand via the bearing housing 21 accommodated in the base frame 1 or the radial bearing 26 associated therewith, and on the other hand via a radial axial bearing 27 which is only shown schematically, the latter being fastened to the underside of the turret plate 2 by means of screws 28 29 cooperates.

The tool set 4 of the upper turret plate 2, partially shown in section, consists of a stamp holder 30 containing a stamp 30 ', which is guided non-rotatably within a bush 32. The stamp 30 'can be displaced in the direction of the arrows 31 in a manner known per se. For the non-rotatable guidance of the stamp holder 30 is used in the periphery of the same spring 33, which within a, in the Groove 34 incorporated into the inside of the bushing 32 slides in the peripheral direction with as little play as possible. The socket 32 is in turn inserted into a corresponding bore 35 of the turret plate 2 and within it axially on the one hand by a ring body 36 attached to its upper end for gripping over the bore 35 and on the other hand by a, in the outside of, on the underside of the turret plate 2 protruding part of the socket 32 engaging locking ring 37 secured. In its peripheral region, the annular body 36 has a toothing 38 which, in a manner still to be explained, serves to drive the tool set 4 about its axis 9.

The punch 30 'is provided on the upper side with a T-shaped head part 39 which is received in a correspondingly designed receptacle of the press ram 25.

In the outer edge 40 of the turret plate, holes 41 are arranged in uniform positions corresponding to the positions of the tool sets, which run parallel to the axis 9 of the tool sets and into each of which a receptacle bushing 42 is inserted, which interacts with the locking bolt 43 of the stationary locking device 22 is determined.

Numeral 44 denotes a gear wheel which is in engagement with the toothing 38 and which is freely rotatably mounted on a bearing bush 45 by means of a radial bearing 46, which bearing bush 45 is fastened to the turret plate by means of a screw 47. The axis of the gear 44 runs parallel to the axis of the plate drive shaft 19.

Said gear 44 is also in engagement with a gear 48 arranged on the disk drive shaft 19 so as to be secure against rotation.

49 denotes an insert ring which is inserted in a recess 50 which is arranged near the axis of the turret plate 2 and is open on the upper side and towards the axis of the plate. The insert ring 49 is connected at its radially outer end to the turret plate 2 by means of screws 51. The underside 52 of the recess 50 is provided in the vicinity of the axis with an annular groove 53, which runs coaxially to the disk drive shaft 19 and is open in the direction of the insert ring 49 and into which an annular piston 54 is inserted. The annular piston 54, which is provided with seals 55 radially on the inside and outside, is thus slidable within the annular groove 53 in the direction of the arrows 56.

For the supply of pressure medium to the annular piston 54, a bore 57 runs coaxially within the disk drive shaft 19, from which a plurality of radial bores 58 branch off, which establish a connection between the bore 57 on the one hand and an annular space 59 on the other hand, which between the outside of the disk drive shaft 19 on the one hand and the Inside of the turret 2 on the other hand. Said annular space is in turn connected via a series of radially extending channels 60 to the underside of the annular groove 53 in order to act on the annular piston 54.

With 57 '' (Fig. 2) rotary connections for the pressure medium supply are designated.

Designated at 61 is an annular disk which is slidably inserted into a recess 63 machined into the underside 62 of the insert ring 49 and also coaxial to the axis of the disk drive shaft 19. The washer 61 is placed on the plate drive shaft 19 in a rotationally secure manner via a splined connection 64 and, due to this connection, is slightly axially slidable.

It can be seen from the preceding illustration that by pressurizing the annular piston 54 through the bores 57, 58, 60, the annular piston 54 slides upward in the direction of the arrow 56 and in this way presses the disk 61 against the insert ring 49, so that the turret plate 2 is frictionally coupled to the disk drive shaft 19. On the other hand, without pressurization, the disk 61 is freely rotatable relative to the insert ring 49, so that when the turret plate 2 is locked, rotation of the plate drive shaft 19 in this case results in the bushing 32 rotating via the gear wheels 48, 44.

With 65, a further radial bore inside the turret plate 2 is designated, which connects the annular groove 53 with the inside of the bore 35, so that leakage liquid occurring within the annular groove 53 is used to lubricate the bushing 32.

FIG. 4 shows a representation of the lower turret plate corresponding to the representation of FIG. 3, wherein comparable functional elements are denoted by a 'on the otherwise identical reference number, with no repeated description in this regard.

With 66 a die is designated, which is arranged axially immovable on the bushing 32 ', but is in a non-rotatable connection with this.

The areal workpiece to be machined is designated by 67 only as an example. In deviation from the upper turret plate 2, the drive elements 10 for rotating the tool, here the die 66, are now on the underside of the lower turret plate. However, the arrangement is otherwise a mirror image of the upper turret plate, so that the recess 50 'and the annular groove 54' are accordingly open towards the underside of the turret plate 3. Since the mode of operation of the optional coupling of the disk drive shaft 19 'with the turret plate 3 or the bush 32' and thus the tool, here the die 66, otherwise corresponds to the corresponding mechanisms of the upper turret plate 2, a repeated description of the same can be dispensed with.

The representation of Fig. 5, which - apart from the nature of the respective tool - can be interpreted either as a top view of the top of the upper turret plate 2 or as a view of the bottom of the lower turret plate 3, reveals that all tool sets in the peripheral area of the Revolver plates are arranged on a common pitch circle 60. In the exemplary embodiment shown, four tool sets 4 are rotatably mounted about their axes, while the other, mutually different tool sets, which are collectively designated by the reference number 69, are not arranged rotatably about their respective longitudinal axes. The intermediate gears 44, 44 ', which mediate the connection between the central gear 48, 48', are in turn also located on a common pitch circle 70.

6 shows a top view of the upper turret plate 2 shows a further embodiment of the drive elements 10 according to the invention, which is also used in an identical manner in the lower turret plate 3. The central gear 48 is fastened to the disk drive shaft 19 by means of two tongue and groove connections which are offset by 180 ° relative to one another.

The bearing bush 45 is provided for receiving the screw 47 with an elongated hole 71, so that a certain adjustability of the exact position of the gear 44 is made possible in accordance with the dimensions of the elongated hole 71. The toothing 38 is located on a toothed ring 72 which is screwed onto a circular ring carrier (not shown in the drawing), the latter forming an integral part of the bushing 32. The link between the toothed ring 72 and the said ring carrier is made via screws 73, which in turn penetrate slots 74 of the toothed ring 72. The elongated holes 74 are located along a common pitch circle and thus extend essentially coaxially with the axis of the tool set 4.

The adjustability of the central gear 44 and the toothed ring 72 resulting from FIG. 6 enables on the one hand an almost play-free coupling of the rotary movements of the gear 48 with the bushing 32 and on the other hand the setting of a precisely defined initial angular position of the bushing 32, for example in such a way that the The center of the tongue and groove connection 33, 34 is aligned with the center of the plate drive shaft 19. This results in a highly precise, backlash-free drive for the individual tool sets 4, and at the same time the control effort required for the exact positioning of an angle of rotation position can be kept low, since all the tool sets the same zero position is assigned.

In practice, the locking devices 22, 22 'can be connected in terms of control technology to the said annular pistons 54, 54' so that the turret plates can always be freely rotated when the latter is pressurized.

Claims (11)

1. Turret punch press having at least one rotating plate (2, 3) comprising a plurality of complete tool sets, (4, 5) in the rotation region, the said rotating plate being rotatable about its axis (11) by means of a drive, furthermore having at least one tool set (4, 5) which is rotatable about its axis (9) running perpendicular to the plane of the revolving plate (2, 3), characterised in that

   - the tool set (4, 5) which is rotatable about its axis (9) can be coupled to the drive of the rotating plate (2, 3) and

   - switchable functioning elements are arranged in a region directly adjacent to the axis (11) of the rotating plate (2, 3) for the purpose of optionally transmitting a rotational movement to the rotating plate (2, 3) or to the tool set (4, 5).
2. Turret punch press according to claim 1,
   characterised in that

   - the drive is formed by means of a controllable motor (12) which is operatively connected by way of a gear to two rotating plates (2, 3) which are arranged coaxial to each other and

   - in each case functioning elements for the purpose of connecting the tool set (4, 5) to the drive or to the motor (12) are arranged on the sides facing away from each other on the rotating plate (2, 3).
3. Turret punch press according to claim 1,
   characterised in that two rotating plates (2, 3) which are arranged coaxially to each other and which are each provided with a motor as a drive, wherein in each case functioning elements for the purpose of connecting the tool set (4, 5) to the respective drive or motor are arranged on the sides facing away from each other on the rotating plate (2, 3).
4. Turret punch press according to one of the aforementioned claims 1 to 3, characterised in that

   - the switchable functioning elements are formed in each case by means of a disc (61, 61') which is allocated to a rotating plate (2, 3) and is coaxial to the said rotating plate, is axially slightly displaceable and is non-rotatable with respect to the respective plate drive shaft (19, 19') and which is intended to transmit frictionally engaged a turning moment from the plate drive shaft (19, 19') to the rotating plate (2, 3) and a controllable device for axially displacing this disc (61, 61') and

   - for the purpose of connecting the tool set (4, 5) to the drive of the rotating plate(s) (2, 3) the remaining functioning elements are formed by means of a gear wheel (44, 44') arranged on/below the rotating plate (2, 3), the said gear wheel engaging on the one side a gear wheel (48, 48') which rotates with the plate drive shaft (19, 19') and on the other side with the gear-tooth system (38, 38') of the respective tool set.
5. Turret punch press according to claim 4,
   characterised in that the controllable device for the purpose of axially displacing the disc (61, 61') is formed by means of an annular piston (54, 54') axially guided in a coaxial annular groove (53, 53') of the rotating plate (2, 3) and the said annular piston can be acted upon by the pressure medium by way of a bore hole (57) running axially within the plate drive shaft (19, 19') and bore holes (58, 58'); (60, 60') running radially to the plate drive shaft (19, 19').
6. Turret punch press according to claim 5,
   characterised in that the annular piston (54, 54') is formed as one piece with the disc (61, 61').
7. Turret punch press according to one of the aforementioned claims 4 to 6, characterised in that the

   - gear-tooth system (38) of the upper tool set (4) is worked in the outer edge, of a rotatable lining (32), protruding from the upper plane of the upper rotating plate (2), the punch holder (30) being non-rotatably inserted in the said lining (32) and

   - the gear-tooth system (38') of the lower tool set (5) is worked in the outer edge of a rotatable lining (32'), wherein the outer edge protrudes out of the underside plane of the lower rotating plate (3) and the said lining (32') supports the matrix (66).
8. Turret punch press according to claim 7,
   characterised in that the lining (32) is formed as one piece with the punch holder (30).
9. Turret punch press according to one of the aforementioned claims 4 to 8, characterised in that the gear wheels (44, 44') are displaceably arranged on/below the respective rotating plate (2, 3) with respect to eliminating as far as possible any play in the gears.
10. Turret punch press according to one of the aforementioned claims 4 to 9, characterised in that the gear-tooth systems (38, 38') are formed in each case by gear rings (72) which can be adjusted at an angle relative to the lining (32, 32').
11. Turret punch press according to claim 9 or 10, characterised in that:

    - the gearing (44, 44') are mounted on bearing bushes (45, 45') which are attached by way of elongated holes (71) on/below the respective rotating plate and

    - the gear rings (72) are attached to the linings (32, 32') by way of elongated holes (74) which extend in the direction of the periphery.

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