EP1529578B1 - Working machine, in particular bending machine for wire and/or strip - Google Patents

Description

The present invention relates to a working machine, in particular wire and / or strip bending machine, according to the preamble of claim 1.

Such machines are known as wire or strip bending machines from DE 1281381 A1 or from CH 441203 A. In these machines, the bending tool, which is arranged on a movable tool holder of a tool unit, is generally moved linearly toward and away from the bending point. Often, a plurality of tool units are provided on the work machine. The movement drive of the tool units is effected by an eccentric. The eccentric of each tool unit are connected to a common drive pulley of the machine. The drive pulley is driven by the working machine and transmits the movement to it via its coupling with the individual eccentrics. In the tool units, the rotational movement of the eccentric is converted into a feed and return movement of the tool holder.

An advantage of this structural design of machines lies in the possibility of a play-free motion transmission between the drive pulley and the individual eccentrics of the tool units. There are also known machine concepts in which the Bewegungsantresbs input part is designed as a gear which meshes with a central driven machine side driven gear of large diameter. In the latter machine concepts, backlash-free motion transmission from the prime mover to the tool units is more difficult to achieve. With regard to this drive concept, reference is made to EP 0 790 088 A2.

A disadvantage of the known from the above-mentioned publications work machines with drive pulley and eccentric motion drive input part is that the tool units are roller-mounted in a sleeve, which is welded to a flat plate as a tool unit receiving portion. Outer circumferential surfaces of outer rings of the rolling bearing are supported on inner peripheral surfaces of the sleeve and inner peripheral surfaces of inner rings of the rolling bearing are supported on a rotating shaft of the tool unit surrounding another sleeve. With this further sleeve of the eccentric is connected.

By trained as described above, the bearing of the rotating shaft of the tool unit on the work machine Umkonfigurleren the machine by arranging or rearranging tool units at different mounting locations on the machine only with great effort, often economically impossible. The known wire or strip bending machines are therefore usually built only for a specific purpose, which they then meet for the rest of their life. In view of ever shorter product life cycles and more specific customer requirements, such machines no longer meet today's economic requirements.

It is therefore an object of the present invention to provide a working machine of the type mentioned, which is designed to be easily and quickly reconfigured or converted from one purpose for another. This reconfiguration mainly involves exchanging tool units for different purposes or / and changing the locations of tool units of the work machine or / and changing the number of tool units used.

This object is achieved by a generic machine with all features of claim 1.

Unlike the prior art references cited above, such machines may not only be used as wire and / or strip bending machines can be used, but can also be used as a mounting device. However, the main application of the generic work machine is the wire and / or strip bending machine.

As a result of the construction according to the invention, the tool unit can simply be inserted with its insertion section into a corresponding insertion opening in the tool unit receiving section and pulled out of it again. It is therefore sufficient in the simplest case, to design the tool unit receiving portion as a perforated plate with a predetermined hole pattern, each insertion in the hole pattern corresponds to a possible mounting location of a tool unit.

According to the invention, the available installation space and the size of the insertion openings are to be designed such that a tool unit with movement drive input part already attached thereto can be inserted into the insertion opening in at least one rotational position of the movement drive input part, in other words that the movement drive input part is in at least one rotational position can be pushed through the insertion opening.

The push-through capability of the movement drive input part is realized independently of the rotational position of the movement drive input part by a design of the movement drive input part, wherein the diameter of an envelope of the movement drive input part rotating about the rotation axis is smaller than the diameter of the insertion opening. It is meant at conical insertion the smallest diameter available.

In general, the tool units are provided with a housing or at least a partial housing, so that it is particularly advantageous from a manufacturing point of view and from the point of view of production costs to form the insertion section on an outer peripheral portion of the housing of the tool unit. In addition, forces that occur particularly advantageously during operation of the work machine on the tool unit can be transferred via the housing into the tool unit receiving section of the work machine and received there become.

In principle, a separate part may be provided on the work machine as a tool unit receiving section. However, in order to reduce the mounting effort as much as possible, it is advantageous to form the tool unit receiving portion of the working machine on a machine housing of the working machine. For example, according to a preferred embodiment of the invention, a machine housing of the working machine, which is generally present anyway, has a preferably planar section in which the insertion openings are provided.

It can be thought to form the insertion and the insertion with certain edge contours, so that the tool unit after insertion of the insertion into the insertion with respect to the machine can not be rotated. This can be achieved for example by insertion and insertion with polygonal or elliptical edge boundaries. However, such insertion openings are more expensive to produce than circular cylindrical insertion openings, which can be produced by a single Bohrarbeitsgang. On the other hand, it can often be more advantageous to finely adjust the tool unit after insertion into the tool unit receiving section in terms of its angular orientation with respect to the working machine and only then to definitively fix the at least one tool unit on the working machine. For this purpose, displaceable clamping means, such as clamping claws, can be provided on the working machine in the unstressed state. With such clamping means, the at least one tool unit can be secured against rotation as well as against detachment from the insertion opening. Due to the displaceability of the clamping means on the work machine flexibility is also given with respect to differently shaped and / or oriented tool units.

Against the background of a further flexibilization of a working machine, the manufacturer may be able to dispense with the provision of clamping devices in order to leave the selection of suitable clamping means to the customer and to allow the use of different, adapted to the individual applications clamping means. In such a case can be provided on the work machine at least engaging training for receiving displaceable in the unlocked state clamping means for fixing the at least one tool unit on the machine. Such engagement formations may be, for example, grooves, which may originate in a certain pattern from the insertion openings in the tool unit receiving portion, such as in the radial direction. The at least one groove may in turn have a cross-sectional shape, such as dovetail or T-shape, which allows the insertion and clamping of sliding blocks, which may be provided on clamping means.

As a rule, in the assembled state of the work machine, the movement drive input part and the movable tool receiver lie on different sides of the tool unit receiving section. This is because the movement drive of the tool units through the drive pulley should not interfere with the operations of the tool units.

For maintenance and also for assembly reasons, it may be advantageous if the motion drive input part is detachably connected to a rotary shaft of the tool unit. In such a case, the movement drive input part can be structurally optimally designed in terms of the best possible force and motion transmission from the drive pulley to the tool unit, since first the tool unit can be inserted into the insertion and then the motion drive input part can be attached to the rotary shaft.

The above-mentioned object of the simplest possible Umrüstbarkeit or reconfigurability of the machine according to the invention can be further improved by the coupling of moving input part and drive pulley is designed as a plug connection, wherein one of the parts: moving input part and drive pulley, a plug pin and the each other part a plug-in recess, in particular a plug-through opening, have. In this case, the connection between the drive pulley and moving input part can be done simply by inserting the plug into the plug hole. For this purpose, according to an advantageous development of the invention, the plug-in pin and / or the plug-in recess can be provided with an insertion aid, for example with a conical taper (plug-in pin) or with a conical extension (plug-in recess) at one longitudinal end.

It is particularly preferred if the connection between the drive pulley and the movement drive input part can be produced exclusively by inserting the plug-in pin into the plug-in recess. However, this should not preclude that the connection is not additionally securable or secured against loosening of the plug pin from the Steckaufnehmung, such as by attaching a corresponding fuse.

Thus, the prime mover can have a high efficiency in the drive, according to an advantageous embodiment of the invention between pin and drive pulley, a roller bearing can be arranged so that the relative rotation of plug-in pin and plug recess can be carried out as low friction. There is more space available for the accommodation of a rolling bearing in the drive pulley. By receiving the rolling bearing in the drive pulley, the above-mentioned push-through capability of the movement drive input part can furthermore be retained by the insertion opening, since a rolling bearing on the motion drive input part would expand its outer dimensions. Structurally particularly advantageous is therefore when the plug-in recess provided in the drive pulley and is formed by the inner wall of an inner ring of a roller bearing. In this case, the roller bearing is preferably a double-row roller bearing in order to minimize the occurrence of a Herz's pressure between the plug-in pin and the plug-in recess. This increases the life of the prime mover. It may also be thought according to an embodiment of the invention, at least partially form the lateral surface of the spigot as a running surface for rolling elements and thus to reduce the dimensions and the number of parts of the bearing.

The drive pulley must perform a circular motion for transmitting motion to a trained as an eccentric motion drive input part. The circular movement can be ensured if the drive pulley is mounted on at least three bearing points of the working machine for the execution of the circular motion.

Advantageously, the bearings themselves are in turn formed by functional units of the working machine. Thus, one of the three fixed bearing points can be an eccentric drive device for moving drive the drive pulley. At least one of the other bearings, preferably both bearings, may be of motion drive input parts of a device and / or a tool unit or devices of the work machine. If the working machine is, for example, a wire and / or strip bending machine in which bending material in the form of wire or strip is bent into a specific shape, then as a further fixed bearing point of the drive disk a movement drive input part of a bending material feed device or / and designed as an eccentric motion drive input part of a Biegefertigteil-output device serve. Namely, in bending machines of this type, regardless of the configuration of the tool units necessary for bending the bending material, there is always a bending material feed and a pre-bent part dispensing device. If the drive disk is supported on the movement drive input parts of functional units and on a drive device as the third bearing point, then the drive disk is kinematically mounted without bearing itself being provided on the work machine.

In particular, in wire and / or strip bending machines, the tool units are often arranged around a central mandrel on which the bent part is formed. In order not to hinder a movement of the mandrel, which may be the above-mentioned Biegefertigteil- output device, the drive disk may advantageously be formed with a central passage. Required movement of the mandrel may then occur in the central passage of the drive pulley.

Furthermore, the drive disk is preferably a flat component, so that with a flat tool unit receiving portion similar tool units can be used at any location of the tool unit receiving section. Due to increased rigidity, the design of the drive disk with a closed ring structure is particularly advantageous. However, this should not preclude a horseshoe-like design of the drive pulley, if, for example, movement space is required for further devices.

When using a designed as an eccentric motion drive input part due to the asymmetric mass distribution of the eccentric in its rotation inertia forces due to an imbalance occur, regardless of whether the eccentric has a plug-in pin or a plug-in recess. To avoid this phenomenon, the tool unit may have a counterweight. In order not to impair the push-through capability of the movement drive input part through the insertion opening, the counterweight may be provided according to an advantageous development of the present invention on the rotary shaft such that it is inserted in the working machine on the state of the tool unit on the opposite side of the movement drive input part the tool unit receiving portion is located.

Fig. 1

eine Vorderansicht einer Drahtbiegemaschine gemäß der vorliegenden Erfindung in einer ersten Konfiguration,

Fig. 2

die Drahtbiegemaschine von Fig. 1 in einer Seitenansicht, teilweise im Schnitt,

Fig. 3

eine Detailansicht der Kopplung von Antriebsscheibe und Werkzeugeinheit,

Fig. 4

eine zweite Konfiguration der Arbeitsmaschine von Fig. 1, sowie

Fig. 5

eine dritte Konfiguration der Arbeitsmaschine von Fig. 1.

In the following, the present invention will be explained in more detail with reference to the accompanying drawings. It shows:

Fig. 1

a front view of a wire bending machine according to the present invention in a first configuration,

Fig. 2

the wire bending machine of Fig. 1 in a side view, partially in section,

Fig. 3

a detailed view of the coupling of drive pulley and tool unit,

Fig. 4

a second configuration of the working machine of Fig. 1, as well as

Fig. 5

a third configuration of the working machine of Fig. 1.

In Fig. 1, a working machine according to the invention is shown in front view. As an example of a work machine, a wire bending machine is selected. The wire bending machine of FIG. 1 is indicated generally at 10.

The wire bending machine 10 has a frame 12 made of sectional steel. The frame 12 rests on a foundation 14. The section steel frame 12 is additionally covered with metal plates, which form a machine housing. By way of example, the metal plates 16, 18 and 20 are designated in FIG. Only schematically, a supply unit 22 is arranged on the metal plate 18, which comprises in this example a pneumatic pressure regulator and a hydraulic tank.

At the machine housing portion formed by the metal plate 20, various functional devices of the wire bending machine 10 are arranged. In Fig. 1 on the right side of a bending material feeding device 24 is provided, which is followed by a punch press 26 in the material feed direction V. After the punch press 26 in the material feed direction V, four substantially similar tool units 28 are arranged on the metal plate 20. The metal plate 20 thus forms a tool unit receiving portion of the wire bending machine 10.

Each tool unit 28 has a substantially linearly movable tool holder 30. At her can be a tool, in the present case, for example, a bending tool, arranged and brought by a feed movement of the tool unit 28 with the bending material in contact. The generation of the advancing movement of the tool holder 30 of the tool unit 28 will be described in more detail below.

Between two mutually facing tool holders 30 in the illustrated in Fig. 1 configuration of the work machine 10 through holes 32 and 34 are provided in the metal plate 20, through which device parts, such as bending mandrels (not shown), in the direction of the arrow D orthogonal to the plane 1 can be moved through.

Furthermore, the metal plate 20 has a plurality of insertion holes 36, in which tool units 28 can be inserted or are inserted. In the configuration shown in FIG. 1, a total of six insertion holes 36 are occupied, two from the punch press 26 and four from the tool units 28. A majority of the insertion holes 36 are arranged such that the respective center axes 36a of the insertion holes 36 rest on a placement circle 37.

Viewed from the viewer of FIG. 1 behind the metal plate 20, and therefore shown in phantom, a drive pulley 38 is rotatably mounted to perform a circular motion.

On an arm 38a of the drive pulley 38, an eccentric 40 is provided, which transmits via a lever linkage 42 a feed motion to the feed unit 24.

In Fig. 2, the working machine-side drive 44 of the drive pulley 38 is also shown. The drive 44 includes one on the machine housing mounted electric motor 46 which drives a rotary shaft 48 to which an eccentric 50 is connected. The eccentric 50 has an eccentric pin, which is inserted into the inner ring of a rolling bearing 52, which is received in a recess in the drive pulley 38 and secured against falling out. In addition, the eccentric pin of the drive 44 is secured by a front side screwed plate with a larger diameter than the eccentric pin against slipping out of the eccentric pin from the inner ring of the bearing 52.

Due to the small size of these components in Fig. 2 has been omitted to give this reference numerals. Also, the eccentric 40 for transmitting the feed movement to the feed unit 24 is coupled in this manner with the drive pulley 38.

In Fig. 2 at the upper end of the working machine 10, a third eccentric 54 on the metal plate 20 opposite metal plate 56 is arranged. The eccentric 54 may serve, for example, for tapping the movement of a mandrel, not shown, in the direction of the double arrow D. In the example shown in FIGS. 1 and 2, the drive 44, the eccentric 40 and the eccentric 54 form the three bearing points which are required to support the drive pulley 38 in such a way that it carries out a defined circular path. The defined circular path is necessary in order to be able to couple further output eccentrics with the drive pulley 38, since an eccentric system can perform only one predetermined by its structural design curve movement.

In Fig. 3, the coupling of a tool unit 28 with the drive pulley 38 is shown in detail. The kinematic coupling of the tool units 28 with the drive pulley 38 substantially corresponds to that of the eccentrics 40, 50 and 54. A flange 60 with a circular cylindrical outer surface, which is formed on a housing 62 of the tool unit 28, is inserted into an insertion hole 36 on the metal plate (FIG. tool-unit receiving section) 20 inserted. The outer diameter of the flange 60 is dimensioned and tolerated with respect to the inner diameter of the insertion opening 36 so that the first rests with sliding fit in the latter. The tool unit 28 is also fixed to the metal plate 20 with clamping means, not shown.

The tool unit 28 has a rotary shaft 64 which is rotatably received in the tool unit housing 62 via a roller bearing 66 and a further roller bearing 68. The rotary shaft 64 penetrates the insertion opening 36 and projects therethrough. At its free longitudinal end 64 a, the rotary shaft 64 is formed with a slightly conical portion to facilitate connection and release of an eccentric ring 70.

A torque transmission between the eccentric ring 70 and the rotary shaft 64 via a feather key 72, which engages in a groove, not shown, of the eccentric ring 70 and thus rotatably connecting shaft 64 and eccentric ring 70 torque transmitting. The eccentric ring 70 is secured in the axial direction on the rotary shaft 64 by a cover 74 and a central screw 76. Thus, it is in principle possible to insert the machine tool unit with the flange 60 without eccentric ring 70 into the insertion opening 36 and then to fasten the eccentric ring 70 to the longitudinal end 64 on the rotary shaft 64. However, this is not advantageous because of the small existing construction and mounting space, as can be seen in Fig. 2.

For this reason, the eccentric ring 70 is formed such that its outer diameter is the same size or slightly smaller, at least not greater than the inner diameter of the insertion opening 36. As a result, the eccentric ring 70 can be pushed through the insertion opening 36. This can be such that the eccentric ring can only be pushed through in a certain or several specific rotational positions. For a quick installation, however, it is advantageous if the eccentric ring 70 in any Rotary positions can be pushed through the insertion opening 36. This is achieved in that the eccentric ring 70 is designed such that an envelope of the eccentric ring, which envelops the eccentric ring 70 rotating about the axis of rotation 64b of the rotary shaft 64 with eccentric pin 78, can be pushed through the insertion opening 36 or a smaller or at best equal size Diameter has as the insertion opening 36th

At its free longitudinal end 78a, the eccentric pin 78 has an insertion bevel, which makes it easier to insert the eccentric ring 70 with eccentric pin 78 into the plug-in recess 80 on the drive disk 38. The plug-in recess 80 of the drive disk 38 is formed by the inner recess of an inner ring 82a of a double-row roller bearing 82, which is fastened in a manner known per se to the drive disk 38.

The plug-in recess 80 may, as in the case shown in Fig. 3, be a through-hole, but it may also be a bag recess. A double-row roller bearing is used to minimize the stress on the contact surface of the eccentric pin 78 and the inner ring 82a of the rolling bearing 82, which increases the life of the assembly.

Overall, the roller bearing 82 ensures a low-friction and therefore low-efficiency drive. It may also be thought to use a rolling bearing without an inner ring and to use the lateral surface of the eccentric pin 78 or a portion thereof as a running surface for the rolling elements of the bearing.

The drive pulley 38 is provided with a central passage 90, which allows an undisturbed movement of devices approximately at the openings 32 and 34 in the direction of the double arrow D.

In FIGS. 4 and 5, the machine tool receiving unit 20 is the Work machine 10 of Figures 1 to 3 shown, wherein the tool units 28 are arranged differently on the tool unit receiving portion 20 as in the previous example. The tool units 28 are mounted in other insertion openings and / or with other angular orientation with respect to the working machine 10 at this. As a result, the working machine 10 can be used for different tasks, wherein due to the advantageous coupling between the drive pulley and tool unit a very fast conversion of the drive machine is possible.

With the machine concept presented in this application, a high flexibility of the working machine with respect to the tasks it can perform is combined with the advantages of a backlash-free drive.

Claims (17)

1. An operating machine, in particular a wire and/or strip-bending machine, which comprises at least one tool unit (28) with a movable tool socket (30), wherein the tool unit (28) has a motion drive input part (70) which is rotatable about an axis of rotation (64b) and which is in the form of an eccentric which for the motion drive of the tool socket (30) is coupled to a drive disc (38) of the operating machine (10), wherein the drive disc (38) is supported so that it carries out a defined circular trajectory while the machine is running, and wherein the at least one tool unit (28) is accommodated on a tool-unit receiving portion (20) of the operating machine (10),
   characterised in that the at least one tool unit (28) has a insert portion (60) with which, for detachable mounting on the operating machine (10), it can be inserted into and withdrawn from a corresponding insert opening (36) in the tool-unit receiving portion (20), wherein the motion drive input part (70) is designed so that the diameter of an envelope curve of the motion drive input part (70) rotating about the axis of rotation (64b) is smaller than the diameter of the insert opening (36), in the tool-unit receiving portion (20) of the operating machine (10).
2. An operating machine according to Claim 1, characterised in that the insert portion (60) is formed by an outer circumferential portion (60) of a housing (62) of the tool unit (28).
3. An operating machine according to Claim 1 or 2, characterised in that the tool-unit receiving portion (20) of the operating machine (10) is formed on a machine housing (12,16,18,20) of the operating machine.
4. An operating machine according to any one of the preceding Claims, characterised in that clamping means, such as clamping straps, which can be shifted on the operating machine (10) in the unclamped condition, are provided for locating the at least one tool unit (28) on the operating machine (10).
5. An operating machine according to any one of Claims 1 to 3, characterised in that engagement formations are provided on the tool-unit receiving portion (20) to receive clamping means, which can be shifted in the unclamped condition, for locating the at least one tool unit (28) on the operating machine (10).
6. An operating machine according to any one of the preceding Claims, characterised in that the motion drive input part (70) is releasably connected to a rotary shaft (64) of the tool unit (28).
7. An operating machine according to any one of the preceding Claims, characterised in that the coupling of the motion drive input part (70) and the drive disc (38) is in the form of a plug-and-socket connector, in which one (70) of the parts: motion drive input part (70) and drive disc (38) has a plug-type spigot (78) and the respective other part (38) has a plug-type recess (80), in particular a plug-type through-opening (80).
8. An operating machine according to Claim 7, characterised in that the plug-type recess (80) is formed by the inner wall of an inner ring (82a) of a rolling bearing (82).
9. An operating machine according to Claim 8, characterised in that the rolling bearing (82) is a double-row rolling bearing (82).
10. An operating machine according to any one of Claims 7 to 9, characterised in that the plug-type spigot (78) is provided on the motion drive input part (70) and the plug-type recess (80) is provided on the drive disc (38).
11. An operating machine according to any one of the preceding Claims, characterised in that the drive disc (38) is mounted on the operating machine (10) at three bearing points (at 40,50,54) so as to carry out a circular movement.
12. An operating machine according to Claim 11, characterised in that one of the bearing points (at 50) is an eccentric (50) of a drive device (44).
13. An operating machine according to Claim 11 or 12, characterised in that at least one of the bearing points (at 40 and 54), preferably two bearing points, is a motion drive input part (70) of one or more devices (40,54) and/or of a tool unit (28) of the operating machine.
14. An operating machine according to Claim 13, characterised in that it is a wire and/or strip-bending machine, in which the drive disc (38) is mounted on a motion drive input part of a bending material feed device (4) in the form of an eccentric and/or on a motion drive input part (54) of a bending finished part output device in the form of an eccentric.
15. An operating machine according to any one of the preceding Claims, characterised in that the drive disc (38) is formed with a central passage (90).
16. An operating machine according to any one of the preceding Claims, characterised in that the drive disc (38) is formed as an essentially flat component, preferably with a closed annular structure.
17. An operating machine according to any one of the preceding Claims, characterised in that the tool unit (28) has a counterweight to compensate for any asymmetrical weight distribution in respect of the axis of rotation (64b) of the motion drive input part (70) arising because of the motion drive input part (70) in the form of an eccentric.

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