EP0543773A1 - Presse plieuse hydraulique - Google Patents

Presse plieuse hydraulique Download PDF

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Publication number
EP0543773A1
EP0543773A1 EP92810803A EP92810803A EP0543773A1 EP 0543773 A1 EP0543773 A1 EP 0543773A1 EP 92810803 A EP92810803 A EP 92810803A EP 92810803 A EP92810803 A EP 92810803A EP 0543773 A1 EP0543773 A1 EP 0543773A1
Authority
EP
European Patent Office
Prior art keywords
joint
hydraulic press
press brake
brake according
butt
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Ceased
Application number
EP92810803A
Other languages
German (de)
English (en)
Inventor
Waldemar Krumholz
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
M&S Brugg AG
Original Assignee
M&S Brugg AG
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by M&S Brugg AG filed Critical M&S Brugg AG
Publication of EP0543773A1 publication Critical patent/EP0543773A1/fr
Ceased legal-status Critical Current

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Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B30—PRESSES
    • B30B—PRESSES IN GENERAL
    • B30B15/00—Details of, or accessories for, presses; Auxiliary measures in connection with pressing
    • B30B15/06—Platens or press rams
    • B30B15/068—Drive connections, e.g. pivotal
    • 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
    • B21D5/00—Bending sheet metal along straight lines, e.g. to form simple curves
    • B21D5/02—Bending sheet metal along straight lines, e.g. to form simple curves on press brakes without making use of clamping means
    • 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
    • B30B1/32—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 plungers under fluid pressure

Definitions

  • the invention relates to a hydraulic press brake, with a bar-shaped or cheek-shaped plunger, which is articulated at both ends to the piston rod of a power cylinder, with an articulated butt connection being provided for transmitting the pressing force from the piston rod to the plunger.
  • the butt joints are designed as simple butt joints and bridged by supporting members, which are each articulated to the piston rods and the plunger. These support elements take up the ram weight when the ram is empty and hold the elements of the butt joints together. In the operation of the ram, the higher-load butt joints take over the power transmission, while the support elements with their less resilient spherical bearings are largely relieved.
  • the aim of the invention is to create a hydraulic press brake of the type mentioned, which does not have the disadvantages described and is characterized in particular by the fact that it operates with a play-free ram drive in every operating case and still enables a simpler frame structure with less machining effort and that it also allows an operational inclination of the ram with a relatively large angle of inclination.
  • butt connection is formed by a double joint consisting of two butt joints which are effectively arranged in series with equally oriented degrees of freedom.
  • Cylinder joints with joint axes or ball joints running perpendicular to the plane of movement of the plunger are suitable as butt joints.
  • the double joints allow a play-free connection between piston rods and tappet, so that an unintentional inclination of the tappet in the working stroke is avoided. Furthermore, a greater tolerance with regard to the parallelism of the force vectors is permissible, which means that with regard to the positioning of the force cylinders with respect to the parallelism of their lines of action, less high accuracy is sufficient and an expensive reworking of the mounting surfaces in question may even be dispensed with. In addition, the presence of the double joints also prevents excessively high managers.
  • an operational inclination of the ram with a relatively large angle of inclination can be achieved without a significant increase in the number of executives, and because the guides are free from play, an inclination once set in the working stroke of the ram is retained regardless of the degree of uniformity of the load.
  • each double joint is made up of a joint head connected to the piston rod or the tappet and a double-sided joint socket arranged freely movable between the two joint heads, the joint heads being made of brass, for example, and the joint sockets being made of steel, in particular cast steel consist.
  • the double joint can be designed in such a way that the joint heads and the piston rods or the plungers abut each other loosely on flat surfaces running transversely to the direction of the joint and are fixed in their mutual transverse position by means of fitting bolts.
  • a preferred embodiment consists in the fact that the center of the rod ends on the piston rods or on the tappet with the respective center of the articulated axes on the piston rods or on the tappet the supporting organs collapse. This is in contrast to the well-known simple butt joint, the center of which has no functional relationship to the joint axes of the supporting members.
  • the support members preferably have a freewheel which is effective during the press stroke of the ram in order to relieve the support members of impact forces during the operation of the ram.
  • the support members can include spring elements that are switched on in the frictional engagement thereof and dampen the force peaks acting on the support members at the beginning of the empty stroke of the ram.
  • the spring elements are also expediently dimensioned such that, under their action, the elements of the butt joints are held together loosely when the plunger is empty.
  • each support member consists of a bolt which is fixedly connected to the one articulation axis in the direction of force and which passes freely through the other articulation axis in a bore and has a support element at the end.
  • the ram can have a central swivel joint at the height of the power cylinder, which can be moved vertically in a straight guide.
  • this straight guide ensures that the ram always assumes a defined position in this regard, despite the horizontal displacement made possible by the double joints.
  • the frame of the press brake is essentially composed of two vertical side walls 1 and a yoke beam 2 connecting the side walls 1 to one another on the upper side.
  • the yoke beam is box-shaped and consists of two vertical longitudinal plates 3 and 4, which are connected to one another at the ends by a vertical transverse plate 5.
  • the side walls 1 are each formed from two upstanding plates 6 and 7, which are arranged at a distance from one another leaving a space 8 and are connected to one another on the upper side by the yoke beam 2 and on the underside by an intermediate piece 9.
  • the active parts of the press brake form a fixed lower beam 10 and an upper beam 11 forming the vertically movable ram, both of which are in the horizontal direction extend between the two side cheeks 1 of the frame into the respective intermediate space 8 thereof and to which the bending tools can be fastened in a manner not shown.
  • each intermediate piece 9 rests on a shoulder 13 of the plates 6 and 7 which is thickened by a shoulder 12 and at the same time serves as a bearing block for the lower beam 10 designed as a free-floating beam.
  • each intermediate piece 9 has two supports 14 spaced from one another, each with a semi-cylindrical pan 15 are provided.
  • a cylindrical pin 16 is anchored at both, stepped ends of the lower beam 10 which reach between the supports 14 and which rests with their projecting ends in the relevant pans 15 of the supports 14.
  • the upper cheek 11 hangs at its two remote ends on two supporting members 17, which are articulated on the one hand to the upper cheek 11 and on the other hand to the piston rod 18 of a power cylinder 19.
  • the hinge axis located on the upper cheek 11 being designated 20 and the hinge axis located on the piston rod 18 being designated 21.
  • Each power cylinder 19 is fastened to the adjacent cross plate 5 of the yoke beam 2 with a mounting flange 22.
  • an articulated butt joint in the form of a double joint 23 is provided for the transfer of the pressing force from the piston rods 18 to the upper cheek 11, an articulated butt joint in the form of a double joint 23 is provided. Details regarding the formation of the double joints 23 and the support members 17 are shown in FIGS. 3 and 4.
  • FIG. 3 shows one of the butt connections in section, the section plane running parallel to the plane of movement of the upper cheek 11.
  • the double joint 23 which forms the butt joint consists of two butt joints which are effectively arranged in series and is constructed from a joint head 24 connected to the piston rod 18, a joint head 25 connected to the upper cheek 11 and a two-sided joint socket 26 arranged between the two joint heads 24 and 25. Due to the selected position of the sectional plane, FIG. 3 applies both to cylindrical joints with joint axes running perpendicular to the plane of movement of the upper cheek 11 and to ball joints.
  • the abutting surfaces are either cylindrical or spherical.
  • the joint heads 24, 25 are preferably made of brass and the joint sockets 26 are made of steel, in particular cast steel.
  • the joint heads 24 and 25 abut on flat surfaces 27 and 28 running transversely to the direction of impact loosely on the piston rod 18 and on the upper cheek 11 and are secured against lateral displacement by means of locating bolts 29 and 30.
  • the contact surface 28 is adapted to the circumference of the joint head 25 by a thickening 31 of the upper cheek 11 provided at the connection point.
  • the centers of the butt joints fall with the associated joint axes of the support members 17 together, that is, the center of the joint head 24 and the adjoining socket side of the two-sided socket 26 coincides with the center of the joint axis 21 on the piston rod 18, and the center of the joint head 25 with the adjoining it
  • the socket side of the socket 26 coincides with the center of the joint axis 20 on the upper cheek 11. This ensures that the distance between the joint axes 20 and 21 remains constant with each adjustment of the double joint. Accordingly, when the double joint is adjusted, the supporting members 17 assigned to it are not subjected to additional tensile or compressive forces, as would be the case without the fixed distance between the joint axes.
  • FIG. 4 A first embodiment of the support members 17 bridging the butt connections is shown in FIG. 4.
  • the support member 17 is divided in the direction of force into an upper part 32 connected to the hinge axis 21 and a lower part 33 connected to the hinge axis 20.
  • the upper part 32 and the lower part 33 are loosely connected to one another by supporting bolts in the form of screws 34 which secure the push through sideways directed leg 35 of the upper part 32 in a free-running manner and are screwed into the lower part 33.
  • spring elements 37 for example plate springs, are used, which are dimensioned such that the elements 24, 25, 26 of the Hold the butt joints loosely together.
  • the free running of the support members 17 ensures that the pressing force is transmitted exclusively through the double joints 21 forming the butt connections in the working step of the ram, and consequently the support members 17 and their articulated connections are not additionally stressed by the pressing force.
  • each support member 40 consists of a bolt 41 which is fixedly connected to a sleeve 42 surrounding the hinge axis 21, e.g. is screwed and welded and which passes freely through the other joint axis 43 in a bore 44 and has a support element in the form of a nut 45 screwed onto the bolt end.
  • the spring elements 46 are arranged on the bolt 41 between the nut 45 and a part 47 of the joint axis 43 flattened at the connection point.
  • the articulated axis 43 is rotatably arranged in the upper cheek 11, while in the case of the articulated axes 20 and 21 the pivot bearing can optionally be located on the upper cheek 11 or on the support members 17 or on the bushing 42 of the support member 40.
  • the articulated connections formed by a double joint 23 and the support members 17 and 40 respectively assigned to them can be designed absolutely free of play. This ensures a high level of working accuracy for the press brake. A high manufacturing accuracy is only for these joint connections and required for the means not shown here for the parallel guidance of the upper beam 11.
  • the positioning of the power cylinders 19 does not require such a high level of accuracy, since inaccuracies in the mounting means in this regard do not necessarily affect the position of the upper beam 11, but are compensated for by the double joints 23. This considerably simplifies the structure of the frame.
  • the guide means for the upper beam 11 can be easily adjusted on the fully assembled press brake thanks to the double joints 23 until the upper beam 11 is precisely aligned with the lower beam 10.
  • the spherical design of the butt joint proves to be particularly advantageous in contrast to a likewise possible cylindrical joint design, because the plane of the upper cheek 11 can be adjusted in all directions due to the additional degree of freedom and regardless of the accuracy of the position of the power cylinder 19 by adjusting the 11 guides for the path of the upper beam can be brought into the desired operating position with high accuracy.
  • FIG. 6 shows schematically the mutual displacement of the elements 24, 25 and 26 of each double joint 23 with an inclined upper beam 11.
  • this Figure shows the moving parts with horizontal position of the upper cheek 11 with dash-dotted lines and with an inclined position thereof with solid lines, and the names of these parts refer to the inclined position.
  • a swivel joint 38 provided on the upper cheek 11, which is arranged at the height of the power cylinders 19 and can be moved vertically in a straight guide (not shown).

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Bending Of Plates, Rods, And Pipes (AREA)
  • Braking Arrangements (AREA)
  • Automatic Assembly (AREA)
  • Presses And Accessory Devices Thereof (AREA)
  • Press Drives And Press Lines (AREA)
EP92810803A 1991-11-21 1992-10-20 Presse plieuse hydraulique Ceased EP0543773A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE4138285 1991-11-21
DE4138285A DE4138285C2 (de) 1991-11-21 1991-11-21 Hydraulische Abkantpresse

Publications (1)

Publication Number Publication Date
EP0543773A1 true EP0543773A1 (fr) 1993-05-26

Family

ID=6445282

Family Applications (1)

Application Number Title Priority Date Filing Date
EP92810803A Ceased EP0543773A1 (fr) 1991-11-21 1992-10-20 Presse plieuse hydraulique

Country Status (5)

Country Link
US (1) US5272904A (fr)
EP (1) EP0543773A1 (fr)
JP (1) JPH05212444A (fr)
CN (1) CN1072357A (fr)
DE (1) DE4138285C2 (fr)

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO1995004643A1 (fr) * 1993-08-11 1995-02-16 Engel Maschinenbau Gesellschaft M.B.H. Machine de moulage par injection
EP2581144A1 (fr) * 2011-10-12 2013-04-17 Weinbrenner Maschinenbau GmbH Cintreuse
ITMI20120052A1 (it) * 2012-01-19 2013-07-20 Unimec S R L Attuatore elettrico, particolarmente per presse piegatrici e simili.

Families Citing this family (20)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2682321B1 (fr) * 1991-10-15 1993-11-12 Commissariat Energie Atomique Dispositif de compression d'echantillon a temperature elevee notamment pour materiaux avances a resistance mecanique.
DE4235971C1 (de) * 1992-10-26 1994-04-07 M & S Brugg Ag Brugg Abkantpresse
KR100229130B1 (ko) * 1996-08-16 1999-12-01 윤종용 냉장고의 외상 벤딩장치
US6758664B1 (en) * 2001-01-12 2004-07-06 Seagate Technology Llc Self-leveling stamper module
DE10232098B4 (de) * 2002-07-15 2004-05-06 Sms Meer Gmbh Vorrichtung zum Herstellen von Rohren aus Blechtafeln
DE10300722B3 (de) * 2003-01-11 2004-04-08 Johann Anderl Werkzeugführungsvorrichtung
JP4497895B2 (ja) * 2003-11-10 2010-07-07 隆久 山本 脱着式金属板曲げ角度精度調整装置
US7134314B1 (en) * 2005-08-26 2006-11-14 Fci Americas Technology, Inc. Hydraulic tool automatic adjusting die holder
FR2908684B1 (fr) * 2006-11-20 2009-11-27 Amada Europ Liaison mecanique pour transfert de forces tout en assurant une isolation
CN102080999B (zh) * 2009-11-30 2012-07-25 徐州重型机械有限公司 工程车辆及其支腿受力检测装置
JP5531878B2 (ja) * 2010-09-15 2014-06-25 村田機械株式会社 プレス機械
FR2965495B1 (fr) * 2010-10-01 2013-08-02 Commissariat Energie Atomique Dispositif d'estampage et/ou de percage comprenant une tete support de substrat dont l'orientation est commandee en continu
DE102010048795B4 (de) 2010-10-20 2019-03-28 Wolfram Hochstrate Schwenkbiegemaschine und Verfahren zum Umformen von Sandwichblechen
DE102012010767A1 (de) * 2012-05-31 2013-12-05 Fette Compacting Gmbh Presse
JP6061607B2 (ja) * 2012-10-17 2017-01-18 株式会社アマダホールディングス 油圧式プレスブレーキ
AT513150B1 (de) * 2012-12-06 2014-02-15 Trumpf Maschinen Austria Gmbh Abkantpresse
US9774159B2 (en) 2015-01-16 2017-09-26 Ridge Tool Company Deflection compensating press tools
AT516493B1 (de) * 2015-02-25 2016-06-15 Trumpf Maschinen Austria Gmbh & Co Kg Abkantpresse
CN104614086B (zh) * 2015-03-06 2017-05-03 上海新微技术研发中心有限公司 气压式温度传感器及其制作方法
CN107695140A (zh) * 2017-11-13 2018-02-16 北京天立成信机械电子设备有限公司 一种u形工件液压成型设备

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3163105A (en) * 1962-06-11 1964-12-29 Pacific Ind Mfg Co Pivotal drive connection
DE1955421U (de) * 1966-10-13 1967-02-16 Wilhelmsburger Maschf Pressbalkenfuehrung einer presse, insbesondere einer abkantpresse.
DE2344432A1 (de) * 1972-10-06 1974-04-11 Verrina Spa Abkantpresse mit hydraulischem oberantrieb
FR2650770A1 (fr) * 1989-08-08 1991-02-15 Montaigne Michel Cisaille a guillotine a usages multiples

Family Cites Families (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE275139C (fr) *
US2377007A (en) * 1941-09-29 1945-05-29 American Steel Foundries Equalizing hydraulic ram travel
US4873923A (en) * 1986-05-16 1989-10-17 Manning Douglas E Hydraulic press platon support

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3163105A (en) * 1962-06-11 1964-12-29 Pacific Ind Mfg Co Pivotal drive connection
DE1955421U (de) * 1966-10-13 1967-02-16 Wilhelmsburger Maschf Pressbalkenfuehrung einer presse, insbesondere einer abkantpresse.
DE2344432A1 (de) * 1972-10-06 1974-04-11 Verrina Spa Abkantpresse mit hydraulischem oberantrieb
FR2650770A1 (fr) * 1989-08-08 1991-02-15 Montaigne Michel Cisaille a guillotine a usages multiples

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO1995004643A1 (fr) * 1993-08-11 1995-02-16 Engel Maschinenbau Gesellschaft M.B.H. Machine de moulage par injection
US5556656A (en) * 1993-08-11 1996-09-17 Engel Maschinenbau Gesellschaft Gmbh Injection moulding machine
EP2581144A1 (fr) * 2011-10-12 2013-04-17 Weinbrenner Maschinenbau GmbH Cintreuse
ITMI20120052A1 (it) * 2012-01-19 2013-07-20 Unimec S R L Attuatore elettrico, particolarmente per presse piegatrici e simili.

Also Published As

Publication number Publication date
JPH05212444A (ja) 1993-08-24
DE4138285C2 (de) 1994-04-07
CN1072357A (zh) 1993-05-26
DE4138285A1 (de) 1993-05-27
US5272904A (en) 1993-12-28

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