EP2049282B1 - Keiltrieb mit zwangsrückholeinrichtung - Google Patents

Keiltrieb mit zwangsrückholeinrichtung Download PDF

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Publication number
EP2049282B1
EP2049282B1 EP07786526A EP07786526A EP2049282B1 EP 2049282 B1 EP2049282 B1 EP 2049282B1 EP 07786526 A EP07786526 A EP 07786526A EP 07786526 A EP07786526 A EP 07786526A EP 2049282 B1 EP2049282 B1 EP 2049282B1
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EP
European Patent Office
Prior art keywords
roller
wedge drive
set forth
positive
return device
Prior art date
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Active
Application number
EP07786526A
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German (de)
English (en)
French (fr)
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EP2049282A1 (de
Inventor
Harald Weigelt
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Individual
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Individual
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Priority to PL07786526T priority Critical patent/PL2049282T3/pl
Publication of EP2049282A1 publication Critical patent/EP2049282A1/de
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Publication of EP2049282B1 publication Critical patent/EP2049282B1/de
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    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B21—MECHANICAL METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
    • B21D—WORKING OR PROCESSING OF SHEET METAL OR METAL TUBES, RODS OR PROFILES WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
    • B21D28/00—Shaping by press-cutting; Perforating
    • B21D28/24—Perforating, i.e. punching holes
    • B21D28/32—Perforating, i.e. punching holes in other articles of special shape
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B30—PRESSES
    • B30B—PRESSES IN GENERAL
    • B30B1/00—Presses, using a press ram, characterised by the features of the drive therefor, pressure being transmitted directly, or through simple thrust or tension members only, to the press ram or platen
    • B30B1/40—Presses, using a press ram, characterised by the features of the drive therefor, pressure being transmitted directly, or through simple thrust or tension members only, to the press ram or platen by wedge means

Definitions

  • the invention relates to a wedge drive with a first provided with a processing tool part and a second part, wherein both parts are arranged to move against each other, and at least one forced return means is provided, which is vulnerable to attack on both parts, and with a third with the first part connected part, wherein at least one means is provided for adjusting the forced return means for tolerance compensation.
  • a wedge is for example in the US-A-5269167 disclosed.
  • Wedge drives are used in particular in the automotive industry for deflecting a vertical pressing force in a horizontal movement.
  • deformations or trimming or punching of the body parts can be made, which is not possible by means of a vertical working movement, ie the normal direction of movement of a press.
  • Wedge drives must therefore be designed so that they can deflect very high working pressures of a press in the desired working direction, so for example in a horizontal direction, at the same time a linear guide is provided.
  • the occurring pressures can quickly exceed 5,000 kN.
  • a press tool can also several, in particular ten or more, such wedge drives are arranged, which perform different tasks and for this purpose with different inclination angles with respect to the working direction, work.
  • a drive wedge hereinafter referred to as a driver element
  • the slider element receives the tools required for processing, so performs the actual processing, and is driven in the linear guide of the press back and forth.
  • the tools that can be mounted on a slide element for cutting or deforming a workpiece, such as a body part, can be designed differently.
  • the design of the wedge drive is performed depending on the activities to be performed, so for example, depending on the sheet thickness and sheet quality of the workpiece to be machined, the respective working length and the type of processing, such as cutting or shaping. According to the specifications of the automotive industry, it must be ensured that a wedge drive has to reach at least 1,000,000 strokes with the required manpower and a running clearance, which ensures that the respective punch exactly hits a corresponding counter die or cutting bush.
  • a staggered impact of a punch or a cutting knife causes it to increased wear on the punch or cutting blade and the cutting bushings, which in the worst case leads to breakage of the cutting or molding tool in the form of a punch, cutting blade, etc.
  • the sliding clearance which is required for a reliable operation of the wedge drive in the area between the driver element and the forced return device, should not be greater than 0.02 mm. Since a plurality of individual parts is assembled in a wedge drive, the manufacturing tolerances taken together lead in each wedge drive to other dimensions and thus to a different sliding play, reworking is required in order to comply with the narrow tolerance range for the sliding play can. By a subsequent tuning of the items by grinding or touching the sliding surfaces could be remedied. Because of this resulting high manual and individual processing effort would result in a very costly solution. For this reason, the tight tolerances are currently dispensed with to avoid the high cost of manufacturing. However, this has the consequence that, although purely optically a security can be suggested by providing a forced return device, but this actually does not exist, because due to the high manufacturing tolerances no process-reliable forced return device can be provided.
  • a forced return device The purpose of a forced return device is to bring a slider element by means of a positive engagement by the forced return means to go back to its rearward position before lifting the driver element.
  • this proves to be meaningful only if it is not lying in the hundredths of a millimeter range gap (cutting clearance) between a cutting blade or punch that is attached to the slider element, to its Gegenmatrize, in which he or he , will be annulled. If this gap was removed in a rearward movement of the slide element, this led to destruction or at least to additional wear of the cutting blade or punch, since this or this touches the counter-die during the backward stroke of the 8chieberelements, rubbing or abuts. Therefore, it is desirable to form the forced retraction so that such contact no longer occurs and reach the cutting means or punch a predetermined or predetermined required life.
  • a wedge drive of the aforementioned type which has a device for easy replacement of a forced return device and for adjusting the forced return device in the event of wear.
  • the hook-shaped forced return device with a plurality of bolts is attached to the part provided with the machining tool, it must be removed by loosening the bolts of the relevant part and compensated to compensate for a game resulting from wear either replaced or suitably processed.
  • the forced return device can then be attached to the affected part again only at the same threaded holes for the bolt-containing areas.
  • the invention has for its object to provide a simple solution for setting the forced return device for tolerance compensation and to improve the required life of the tool and the wedge drive in total.
  • the force can be absorbed reliably in the backward movement of the slider element.
  • an optimal retraction force of about 10% ⁇ the actual working force of the slide element can be generated.
  • a wedge drive can be created in which the retraction force is applied by a device other than a return spring.
  • a device other than a return spring eliminates otherwise used in the prior art gas spring for retrieving the slide element completely.
  • gas springs tend to become hot during prolonged operation and then fail if necessary. In case of failure, they lead in the prior art to jamming of the wedge drive.
  • a gas pressure spring is omitted in the present invention, since a forced return already takes place or is assisted by the at least one other device, a great advantage can be achieved compared with the prior art due to the increased process reliability due to the gas spring which is no longer used.
  • the device according to the invention is advantageously designed so that it minimizes the return forces that can be applied when retrieving, so that retrieving the one part of the wedge drive is easily possible even without a return spring.
  • the means for effecting and / or assisting in retrieving and / or increasing the application retractable force may in particular comprise a friction-based connection between the two parts.
  • the forces to be applied to a friction-based connection are small, so that the forces required to retract one part of the wedge drive from the solutions of the prior art, in which the already mentioned Clamp connections and gas springs can be used, can be reduced.
  • a rolling motion proves by at least one roller or a roller-like element when driving over the sliding surfaces on the driver element by the forced return means to minimize wear when driving over the hinter constitutionalen clamping of the slider element and driver element.
  • the cross wedge as a means for setting the forced return means results in a forced return means with optimum effectiveness.
  • a wedge drive is created in which, in contrast to the prior art, a rolling friction on rolling body is used, which is much lower than a sliding friction on sliding surfaces.
  • a forced return device designed as a steel clamp or tab is fastened laterally on the wedge slide or slide element and hooks behind a sliding surface running parallel to the driver surface on the drive element.
  • the sliding surface provided on the forcible return means for sliding on the sliding surface of the driving member is exchanged with a roller or a roller-like member or supplemented with a roller or a roller-like member.
  • the surface pressure in the end region of the sliding surface on the driver element between the mutually sliding surfaces of the forced return device and the driver element does not occur in this area advantageous in providing a roller or a roller-like element.
  • the same linear contact and thus power transmission Canceling the end area of the surface on the driver element over which the roller unrolls is therefore no longer to be feared.
  • the forced return device with at least one roller or a roller-like element uses the otherwise unused force of the press to pull back the slider element as the first part on themaschineerelementschräge and the positive embrace of the corresponding surface on the driver element as a second part on the role or the on the upward stroke of the press roll-like element. This makes it possible to meet the minimum requirement of a withdrawal force of at least 12% of the worker. Further, a forced control of the wedge drive via the press movement, wherein the wedge drive in the working direction and the withdrawal direction in each case uses the pressing forces and thus a multiple of the recoil force that can be built up by a spring can be achieved.
  • the forced return device is advantageously formed like a clip and arranged on the outside of the wedge drive.
  • the forced-return device can have at least one first section acting on a slide element as a part bearing a tool and at least one second section provided with the roller or the roller-like element and acting on a surface of a driver element as a second part of the wedge drive.
  • the positive return device is preferably fastened with its first section to the slider element and with its second section provided with the at least one roller or the at least one roller-like element, is non-positively arranged on the driver element. Due to the Arranging the forced return device as Klammerartigem element on the outside of the wedge drive is easy to install and, if necessary, disassembly possible, for example, to replace a worn after several million stroke role or a roller-like element. Due to the one-sided fastening of the forced return device to the slider element, a precisely defined position on this and in comparison with the driver element is possible, so that a positive or non-positive clasp of the space provided for this purpose of the driver element is made possible.
  • the roller or the roller-like element is arranged asymmetrically on the forced return device, in particular its second section.
  • the roller or the roller-like element is arranged offset in the direction of the working direction of the slide element with respect to a center line of the forced return device. This makes it possible to compensate for a tilting of the slider element in the retraction movement particularly well or to allow, without the risk of jamming of the wedge drive is.
  • the forced return force of the forced return means is selected to be about 10% of the forward pressing force of the slider element. This corresponds approximately to the force that is required to pull a cutting means, in particular a cutting knife or a punch, out of a workpiece, ie the stripping of the cutting means on the workpiece, such as a sheet metal part, taking into account any deposits of zinc or aluminum etc. in the cutting gap.
  • the transverse wedge or the device for adjusting the fastener element is fastened or fastened.
  • a slot can be provided, via which the device for adjusting or the transverse wedge can be attached to the slide element.
  • the at least one surface on the driver element has a rounded end region over which the roller or the roller-like element can roll away without difficulty in order to come out of engagement with the surface of the driver element.
  • the at least one roller or the at least one roller-like element has a diameter corresponding to at least twice the radius of the rounded end region or corresponds to a larger diameter than half the width of the forced return device.
  • the roller or the roller-like element protrudes with its and its circumferential extent beyond the outer edge of the forced-return device. Due to the provision of such a large role, on the one hand, a particularly secure and good line contact on the surface the driver element for the role or the roll-like element possible. On the other hand, this is a large power consumption possible because the role is stable enough to intercept even large press forces or record. Canting-free rolling across the surface of the driver element can also be ensured, which results in avoiding the risk of jamming the wedge drive even without or just without providing a gas spring or other spring system.
  • the actual forced return path is not provided exclusively via the at least one roller or the at least one roller-like element, but rather a combination with a sliding guide is provided for receiving larger forces.
  • the at least one roller or the at least one roller-like element then serve primarily to minimize wear when driving over the rounded end region as entry and exit radius, so that an even longer service life of the forced return device can be created.
  • the actual force in the advanced state of the slide element of the wedge drive or the press ie in the working position or the bottom dead center of the press, can then be absorbed mainly via the slide, not on the at least one roller or at least one roller-like element also the applicable force compared to the provision of only the at least one roller or the at least one roller-like element can be significantly increased, which show their particular advantage in the withdrawal movement.
  • FIG. 1 shows a perspective view of an embodiment of a wedge drive 1 with a slider guide element 10, a slider element 20 and a driver element 30.
  • Slide guide element 10 and slider element 20 are connected to each other via two guide brackets 40.
  • the guide brackets are in each case via retaining projections 41, 42 which engage in corresponding grooves of slide guide element and slide element, connected thereto.
  • the guide brackets are also connected via only indicated screws 43, which is better FIG. 2 can be removed.
  • the slider element 20 is seated displaceably on the driver element 30 via a prismatic guide 50. Furthermore, the slider element and the driver element are connected to one another via two positive return devices 60.
  • the respective forced return device 60 is formed like a clamp. This has in each case a first portion 61 which acts on the slider element 20 and a second portion 62, which is provided with a respective roller 63. The roller is rotatably mounted on an axis, not shown, on the second portion 62 of the forced return device.
  • the forced return device 60 engages an outer surface 31 of the driver element 30.
  • This can be the FIGS. 1 and 3 be taken very well.
  • a stepped projection 32 is provided in this area, which has on its underside the outer surface 31 for engaging the roller 63. Due to the fact that the step-shaped protrusion 32 engages under the attachment of the forced return device 60 in the region of the first section 61 on the slide element, a secure grip is possible for forwarding the force (force-locking connection) exerted by the press or its movement.
  • a sliding surface 68 is provided on a respective projecting portion 69 on the respective forced return device 60.
  • the forced-return device 60 is fastened, for example, by means of screws 64, as in FIGS Figures 2 and 3 and 5 and 6 indicated. These screws engage in openings 21, 22 laterally in the slider element 20. This is especially good FIG. 4 refer to. In this figure, the forced return means 60 are not yet mounted, so that also the step-shaped projection 32 with the outer surface 31 on the driver element 30 is particularly well recognizable.
  • the press movement is used in the upward direction, wherein the forced return means 60 along the outer surface 31 of the stepped projection 32 in the representation from right to left, ie opposite to the working direction 70, the indicated by an arrow is running. Another arrow indicates this withdrawal direction 71.
  • the forced return device was moved along the outer surface 31 of the stepped projection 32 in the withdrawal direction 71. In this case, the roller 63 rolls on the outer surface 31 of the driver element.
  • the roller 63 As in particular in the Figures 5 and 6 seen offset relative to an imaginary center line 72 of the staple-shaped positive return device 60.
  • the offset V between the arrangement of the axis 65 of the roller 63 and the center line 72 is particularly in the Figures 5 and 6 to see very clearly.
  • the roller has a diameter which is greater than half the width b of the forced return device in the region of the second section 62 FIG. 5 however, the diameter of the roller corresponds to about half the width b of the forced return device.
  • roller 63 projects beyond the outer edges 66, 67 of the second section 62 of the forced return device 60, in particular in FIG Figures 5 and 6 to see. Characterized in that the roller 63 is formed as large as possible, is a given particularly good stability of the forced return device. According to the embodiment in FIG. 5 is the sliding surface 68 is provided except the roller 63, which also increases the stability. The more stable the forced-return device is formed, the better, of course, high forces of the press can be absorbed and endured. With appropriate design of the forced return means an otherwise provided spring return can be omitted, since alone by rolling the rollers 63 of the forced return means 60 can be used on both sides of driver element and slide element of the upward stroke of the press to retract the slide element.
  • the stepped projections 32 have a rounded end portion 33.
  • the roller 63 rolled out there properly as can be seen from the FIG. 6 can be derived.
  • the roller is located in front of the rounded end portion 33 and can roll on this subsequent, without destroying or wearing it, so that the problem of the prior art of high wear in this area can be solved here.
  • a problem-free reentry of the roller 63 on the rounded end portion 33 on the outer surface 31 of the stepped projection 32 of the driver element 30 is also easily possible, so that when providing the forced return means 60 is provided a substantially maintenance-free durable forced return device, the already taking place press movement for a forced withdrawal of Slider element after processing of a workpiece uses.
  • the radius r of the rounded end region is selected so that the roll can roll off optimally there.
  • the forced return device 60 is attached to the slider element and mounted on the driver element unrollable.
  • the forced return device is attached to the moving part of the wedge drive to here a tilting of this and thus avoid jamming as safe as possible, which can be done more easily when the roller rolls on a fixed element of the wedge drive and not on a likewise moving element, as on the slide element in the FIGS. 1 to 6 ,
  • such an arrangement is possible, with the in the FIGS. 1 to 6 shown, however, proves to be more advantageous.
  • the slider element is notched in its side surface or provided with a groove or recess designed to accommodate the forced return device 60 with its first portion 61 there.
  • This notch 23 is advantageously adapted to the shape and size of the forced return device 60.
  • the stop on the slider element is even better possible, since a lateral support of the staple-like forced return device 60 within this notch 23 is possible.
  • a cross wedge 80 is arranged within the Notch.
  • the transverse wedge 80 engages under the first portion 61, which protrudes directed to the slider element and is located with this projecting portion above the cross wedge 80.
  • the cross wedge 80 is used to allow adjustment of the forced return means to compensate for tolerance differences occurring during manufacture can.
  • the sliding clearance between the driver element and the forced return device can be set to 0.02 mm and less in order to ensure reliable operation of the wedge drive.
  • the cross wedge 80 is provided with a slot 81 and attached via this to the slider element via a screw 82 or other fastening means. As a result, a transverse displacement of the cross wedge 80 is possible, so that the desired sliding clearance can be adjusted even after the assembly of the slider element.
  • After setting the forced return device it is fixed in the set position on the slider element. This is particularly the perspective view of the forced return device 60 and the top view of these in the FIGS. 8 and 9 seen. From these figures, further, all portions and parts of the positive repeating device 60 can be detailed. In particular, the formation of roller 63 and sliding surface 68 on the projecting portion 69 results from these figures.
  • the forced return means is designed so that the force provided by this makes about 10% of the pressing force of the slider element, which is the force that is required to extract a cutting means, such as a punch, from a workpiece, also taking into account possibly. Deposits in the cutting gap, which further complicate withdrawal.
  • the at least one forced return device without a return spring, in particular a gas spring
  • the forced return means at least one other device which minimizes the applied retraction forces, such.
  • rollers or roller-like elements can be dimensioned in a corresponding manner and arranged on the forced return device, in order to secure the clasping of the mutually moving parts ensure the wedge drive to securely forcibly moved back to its working position moving part of the wedge drive back to its original position.
  • roller (s) or roller-like elements other means may be provided which, instead of a return spring, assist in forcibly restoring at least a portion of the wedge drive serve or increase the applicable retracting force and can be used.
  • a return spring assist in forcibly restoring at least a portion of the wedge drive serve or increase the applicable retracting force and can be used.
  • Such a device may, for example, use low rolling force requiring rolling friction instead of sliding friction in the retracting movement.

Landscapes

  • Mechanical Engineering (AREA)
  • Engineering & Computer Science (AREA)
  • Portable Nailing Machines And Staplers (AREA)
  • Braking Arrangements (AREA)
  • Bending Of Plates, Rods, And Pipes (AREA)
  • Transmission Devices (AREA)
  • Machine Tool Units (AREA)
  • Devices For Conveying Motion By Means Of Endless Flexible Members (AREA)
  • Clamps And Clips (AREA)
  • Vending Machines For Individual Products (AREA)
  • Ropes Or Cables (AREA)
  • Electrical Discharge Machining, Electrochemical Machining, And Combined Machining (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)
  • Mounting, Exchange, And Manufacturing Of Dies (AREA)
  • Rolls And Other Rotary Bodies (AREA)
EP07786526A 2006-08-03 2007-08-02 Keiltrieb mit zwangsrückholeinrichtung Active EP2049282B1 (de)

Priority Applications (1)

Application Number Priority Date Filing Date Title
PL07786526T PL2049282T3 (pl) 2006-08-03 2007-08-02 Mechanizm klinowy z urządzeniem do przymusowego ściągania

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102006036654A DE102006036654B4 (de) 2006-08-03 2006-08-03 Keiltrieb mit Zwangsrückholeinrichtung
PCT/EP2007/006856 WO2008015000A1 (de) 2006-08-03 2007-08-02 Keiltrieb mit zwangsrückholeinrichtung

Publications (2)

Publication Number Publication Date
EP2049282A1 EP2049282A1 (de) 2009-04-22
EP2049282B1 true EP2049282B1 (de) 2010-11-10

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Family Applications (1)

Application Number Title Priority Date Filing Date
EP07786526A Active EP2049282B1 (de) 2006-08-03 2007-08-02 Keiltrieb mit zwangsrückholeinrichtung

Country Status (14)

Country Link
US (1) US8689600B2 (pt)
EP (1) EP2049282B1 (pt)
JP (1) JP5116766B2 (pt)
KR (1) KR101083483B1 (pt)
CN (1) CN101500725B (pt)
AT (1) ATE487550T1 (pt)
BR (1) BRPI0715086B1 (pt)
CA (1) CA2659906C (pt)
DE (2) DE102006036654B4 (pt)
ES (1) ES2356268T3 (pt)
MX (1) MX2009001256A (pt)
PL (1) PL2049282T3 (pt)
RU (1) RU2424120C2 (pt)
WO (1) WO2008015000A1 (pt)

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WO2014090264A1 (de) * 2012-12-13 2014-06-19 Bernd Klug Vorrichtung mit zumindest einer einrichtung zum einstellen eines führungsspiels
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DE102018111366B4 (de) * 2018-05-14 2024-03-07 F I B R O Gmbh Keiltrieb mit justierbarer Führungsvorrichtung
JP1631354S (pt) * 2018-10-16 2019-05-13
DE102019100687B4 (de) 2019-01-11 2021-05-20 Fraunhofer-Gesellschaft zur Förderung der angewandten Forschung e.V. Keiltriebwerkzeug
DE102020121142B4 (de) 2020-08-11 2022-03-10 Uniflex - Hydraulik GmbH Radialpresse
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Publication number Publication date
RU2009106131A (ru) 2010-09-10
DE502007005623D1 (de) 2010-12-23
BRPI0715086B1 (pt) 2019-04-09
US8689600B2 (en) 2014-04-08
CN101500725B (zh) 2011-07-13
CN101500725A (zh) 2009-08-05
EP2049282A1 (de) 2009-04-22
KR20090034922A (ko) 2009-04-08
RU2424120C2 (ru) 2011-07-20
CA2659906A1 (en) 2008-02-07
BRPI0715086A2 (pt) 2014-07-22
MX2009001256A (es) 2009-04-07
CA2659906C (en) 2012-04-24
KR101083483B1 (ko) 2011-11-16
US20100107722A1 (en) 2010-05-06
DE102006036654B4 (de) 2008-12-04
ATE487550T1 (de) 2010-11-15
DE102006036654A1 (de) 2008-02-07
ES2356268T3 (es) 2011-04-06
PL2049282T3 (pl) 2011-04-29
JP5116766B2 (ja) 2013-01-09
JP2009545448A (ja) 2009-12-24
WO2008015000A1 (de) 2008-02-07

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