EP0304905A2 - Pièce hydraulique - Google Patents

Pièce hydraulique Download PDF

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Publication number
EP0304905A2
EP0304905A2 EP88113839A EP88113839A EP0304905A2 EP 0304905 A2 EP0304905 A2 EP 0304905A2 EP 88113839 A EP88113839 A EP 88113839A EP 88113839 A EP88113839 A EP 88113839A EP 0304905 A2 EP0304905 A2 EP 0304905A2
Authority
EP
European Patent Office
Prior art keywords
press
pressure
piston
cylinder
press according
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.)
Withdrawn
Application number
EP88113839A
Other languages
German (de)
English (en)
Other versions
EP0304905A3 (fr
Inventor
Horst Baltschun
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.)
Maschinenfabrik Lauffer GmbH and Co KG
Original Assignee
Maschinenfabrik Lauffer GmbH and Co KG
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 Maschinenfabrik Lauffer GmbH and Co KG filed Critical Maschinenfabrik Lauffer GmbH and Co KG
Publication of EP0304905A2 publication Critical patent/EP0304905A2/fr
Publication of EP0304905A3 publication Critical patent/EP0304905A3/fr
Withdrawn legal-status Critical Current

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Classifications

    • 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
    • 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
    • B21D28/02—Punching blanks or articles with or without obtaining scrap; Notching
    • B21D28/20—Applications of drives for reducing noise or wear
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B30—PRESSES
    • B30B—PRESSES IN GENERAL
    • B30B15/00—Details of, or accessories for, presses; Auxiliary measures in connection with pressing
    • B30B15/16—Control arrangements for fluid-driven presses
    • B30B15/24—Control arrangements for fluid-driven presses controlling the movement of a plurality of actuating members to maintain parallel movement of the platen or press beam
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B30—PRESSES
    • B30B—PRESSES IN GENERAL
    • B30B15/00—Details of, or accessories for, presses; Auxiliary measures in connection with pressing
    • B30B15/16—Control arrangements for fluid-driven presses
    • B30B15/24—Control arrangements for fluid-driven presses controlling the movement of a plurality of actuating members to maintain parallel movement of the platen or press beam
    • B30B15/245—Control arrangements for fluid-driven presses controlling the movement of a plurality of actuating members to maintain parallel movement of the platen or press beam using auxiliary cylinder and piston means as actuating members

Definitions

  • the invention relates to a hydraulic press according to the preamble of the main claim.
  • Hydraulic presses are used, for example, for metalworking, metal being punched, deformed or otherwise processed with a high pressing force, which can be several kilonewtons.
  • the known presses have a press frame in which the upper press part with ram and the lower press part are arranged.
  • a tension corresponding to the press pressure is built up in the known presses in the press frame, which suddenly drops at the end of the operation.
  • there are short-term expansions during the working stroke in the press frame or in the press stand each of which requires an expansion work that suddenly disappears completely unused at the end of the respective working stroke.
  • the stretching that occurs can affect the precision of the pressing process.
  • a hydraulically driven press which has a press ram which is connected to piston rods which engage pistons in cylinder spaces which are mounted on the one hand on the lower press frame and on the other hand on a crosshead of the press. If pressure is built up in the cylinder chambers in this known arrangement, the press can be pretensioned, although the press frame in which the crosshead is mounted must absorb these clamping forces. The clamping forces that occur in the frame cannot be introduced into the press frame axially symmetrically to the piston rods. The result of this is that the prestressing forces lead to bending stresses in the press frame, as a result of which an exact pressing process is adversely affected.
  • the invention has for its object to provide a hydraulic press that can be preloaded and does not lose its tension even at the end of a working stroke and does not require a crosshead clamped in a circumferential press frame.
  • the solution to this problem is obtained in a press of the type mentioned by the features specified in the characterizing part of the main claim.
  • the press ram is connected to piston rods that protrude into cylinder spaces at both ends, which are preferably arranged in the area of the press columns.
  • the cylinder spaces are pressurized in such a way that the same forces act on both ends of the piston rods, which are directed in opposite directions.
  • the reaction forces result in tension in the press and thus tension in the columns.
  • the upper press part with the press ram can be moved in height with little effort and into an ar Bring the working position to the system with the workpiece.
  • the working stroke is initiated in that the lower cylinder spaces are relieved of pressure, so that there is no longer a balance of forces on the piston rods.
  • the press ram moves against the workpiece in accordance with the pressure relief, which in turn creates a counterforce there and thus maintains the bracing of the press.
  • the columns or corresponding tie rods that connect the upper part of the press to the lower part of the press remain pre-tensioned.
  • the pressure previously reduced in the lower cylinder chambers is increased again via controllable valves so that the pre-tensioning of the columns is maintained.
  • the effective piston surfaces of the piston rods can of course be of different sizes, but then correspondingly different pressures must be built up in the cylinder chambers in order to transmit equally large compressive forces to the piston rods in order to achieve an equilibrium of forces.
  • the piston areas are preferably of the same size, so that the same pressure forces can be obtained by coupling the cylinder spaces via pressure lines and connecting them to a common pressure generator. To initiate the working stroke, it is then sufficient to interrupt the connecting line between the upper and lower cylinder spaces and to lower the pressure in a defined manner in the lower cylinder space, as a result of which the press ram moves downward and thus deforms or otherwise processes the workpiece.
  • the piston rods are tubular, which enclose tie rods or columns running between the upper press part and the lower press part.
  • the piston surfaces are ring surfaces that protrude into cylinder spaces, which act as ring spaces for the tie rods or columns in the area of their enclose both ends.
  • the upper cylinder spaces can be connected to the lower cylinder spaces via a longitudinal bore in each column, which can be shut off by means of a controllable valve.
  • a controllable valve As a result, no additional external pressure lines are required to connect the pressure chambers and a very streamlined cylinder chamber connection can be realized, which allows the press ram to be moved before and after the working stroke with little effort by means of an additional actuating cylinder.
  • the one-sided pressure relief of the cylinder chambers is preferably achieved via controllable valves which are actuated by an electronic control.
  • This control can relieve the pressure as a function of sensor signals which, for example, recognize an eccentric load on the press ram due to the eccentric arrangement of the workpiece.
  • Pressure sensors which are assigned to the cylinder spaces can serve as sensors for this purpose.
  • angle sensors or displacement sensors as sensors, which can determine an inclined position of the press ram, so that individually assigned control valves can be actuated correspondingly via the control to the lower cylinder spaces.
  • the press can have mechanical adjustment devices in the area of the upper ends of the columns, which permits a height adjustment of the press ram in relation to the piston rods.
  • a plurality of hydraulic presses are arranged in a mechanical lifting frame in such a way that the upper press parts can be moved into the position in which the working stroke begins with a common rapid delivery device. This eliminates the need for several actuating cylinders, as these are replaced by a common express delivery.
  • FIG. 1 shows the left and middle part of a hydraulic press according to the invention in cross section, the illustration being simplified to clarify the function.
  • the press preferably has four tie rods or columns arranged at the corners of the press ram P, in each area of which a piston rod K connected to the press ram P is arranged. Only one of the four piston rods is shown in the drawing.
  • the press ram P can be lowered by means of an actuating cylinder 3 until a processing tool 4 mounted on it comes into contact with a workpiece 5 which is mounted on the lower press part 6.
  • the actuating cylinder 3 has two pressure chambers 7, 8 which can optionally be pressurized via pressure lines 9, 10. If pressure is applied to the pressure chamber 7, the press ram P moves downward, while when the pressure chamber 8 is pressurized, the press ram P is moved upward.
  • the working stroke is not carried out with the actuating cylinder 3, but rather via the piston rods K, which each protrude into the cylinder spaces 13, 14 with piston faces 11, 12 on the end face.
  • the cylinder spaces 13, 14 are acted upon by a common hydraulic pump 15 with the same pressure that the compressive forces acting on the piston surfaces 11, 12 of the same size are equal and do not cause any deflection of the press ram P.
  • the tie rod 16, which is part of the press frame, connects the upper Zy Linderraum 13 with the lower cylinder chamber 14, so that the pressures occurring in the cylinder chambers 13, 14 tension the tie rod 16, ie the tie rod 16 is slightly stretched.
  • the press ram P can now be brought into contact with the workpiece 5 by means of the actuating cylinder 3.
  • the working stroke can now be initiated in this position, a first controllable valve 17 being brought into the other position, as a result of which the pressure line 18 is interrupted.
  • a controllable servo valve 19 can then be opened by means of a control S, so that a pressure drop occurs in the cylinder space 14.
  • the press ram P now moves downwards.
  • a counterforce corresponding to the pressing pressure occurs on the workpiece, which has the consequence that the tie rod 16 remains biased unchanged despite a drop in pressure in the cylinder chamber 14.
  • the valves 17, 19 are brought back into the position shown, so that the same pressure is present in the cylinder space 14 as in the cylinder space 13.
  • the tie rod 16 thus remains prestressed even at the end of the working stroke.
  • the control S can be operated via a keyboard 20 and is connected to a read-write memory 21. Data for different press programs, which the controller S can access, can be stored in the memory 21, depending on the operation via the keyboard 20.
  • the control of servo valves is general prior art, which is why a detailed description of the controller is not given here.
  • FIG. 1 A further exemplary embodiment is shown in principle in FIG.
  • the piston rod has K. their two ends have pistons 22, 23 which engage in cylinders 24, 25 mounted on the press.
  • the cylinder spaces 13, 14 formed in this way correspond in their function to the cylinder spaces 13, 14 designated by the same reference numerals in FIG. 1.
  • the upper part of the press 26 is connected to the lower part of the press 27 via columns or tie rods or the like, but this is shown in FIG 2 are not shown.
  • Figure 3 shows a first preferred embodiment of the press in more detail.
  • the press ram P is here in the upper starting position. All control valves 28, 29 and 30 are in switch position 0 and the cylinder spaces 13, 14 are pressurized by the pressure medium source 15.
  • the pressure medium source 15 is hydraulically connected to the cylinder spaces 13, 15 via pressure lines 31, 32 and via longitudinal bores 33, 34 which run in the tie rods 35, 36.
  • the pressure medium source 15 is hydraulically connected to the cylinder spaces 13, 15 via pressure lines 31, 32 and via longitudinal bores 33, 34 which run in the tie rods 35, 36.
  • transverse bores 37, 38 which lead to the cylinder spaces 13, 14.
  • the piston rods K1 are tubular and enclose the tie rods 35, 36, which can form the columns of the press.
  • the piston K1 forms an annular piston surface 39 which faces the cylinder space 13 designed as an annular space.
  • a piston surface 40 of the same size is formed, which faces the cylinder chamber 14, which is designed as an annular chamber.
  • the lower cylinder spaces 14 are connected to each other via through holes 41 and pressure lines 42, so that in the press position shown in all Chen cylinder spaces 13, 14 the same pressure prevails. In this state, the press ram P can be brought down into the working position by means of the actuating cylinder 3 without great effort, which is shown in FIG. 4.
  • the valve 28 can be opened and closed in a defined manner, as a result of which a defined pressure reduction in the cylinder spaces 14 and thus a controlled initiation of the working stroke can take place.
  • the press ram is supported on the workpiece 5 so that the reaction forces thereby generated continue to maintain the pretension in the tie rods 35, 36.
  • FIG. 5 shows the position of the press ram P at the end of the working stroke. Exactly in this position, the valves 28, 29 are brought back into the position 0, so that the piston valves 44 open again and the pressure in the lower cylinder spaces 14 is again the same as the pressure in the upper cylinder spaces 13. The constant preload of the tie rods 35, 36 is thus retained.
  • the valve 30 can now be brought into the position 2, so that a pressure increase in the pressure chamber 8 occurs and the piston 47 of the actuating cylinder 3 is brought into the position according to FIG. 3. This completes a work cycle and further cycles can follow in a corresponding manner, the tension of the press always being maintained.
  • This function can be described as a constant, dynamic preload.
  • FIG. 6 shows an exemplary embodiment in which the pressing force can be regulated separately in each lower cylinder chamber 14.
  • pressure valves 50, 51 are provided which can be actuated separately from the control S.
  • This particularly preferred embodiment is particularly of great advantage when eccentric loads occur, as is the case with an eccentrically arranged tool 54.
  • Such an eccentric load triggers an inclined position of the press ram P without balancing the forces in the cylinder chambers. This can be determined by means of suitable sensors by angle measurement or differential path measurement. Such measuring methods for determining angles or distances are general prior art, for which reason a description in this regard is not given here.
  • control S controls the pressure valves 50, 51 in such a way that different pressures during the working stroke are realized in the lower cylinder spaces 14, with which the inclination of the press ram P is minimized.
  • the inclination of the press ram P is measured by means of two sensors 52, 53, the sensor signals of which are fed to the control S.
  • Four linear displacement sensors can be used as sensors 52, 53.
  • the lower cylinder spaces 14 have a very low height during the working stroke, which reaches their minimum value at the end of the working stroke, for example in the millimeter range. This can also be seen from the illustration in FIG. 5. In this position (working stroke end), the piston rods K1 rest against a fixed stop F (FIG. 5). By minimizing the cylinder spaces 14, very good control properties and effective cut impact damping are achieved.
  • FIG. 7 shows an adjustment device 55 with which the press ram P can be moved longitudinally along the piston rods K1.
  • threads 56 are formed at the upper end of the tubular piston rods K1, onto which an adjusting nut 57 is screwed.
  • the adjusting nuts have molded flanges 58 which engage in corresponding grooves 59 on the upper press part 60.
  • FIG. 8 and FIG. 9 each show three presses of the type according to the invention which have a common rapid delivery device 61 instead of separate actuating cylinders. In Figure 8, this is in the upper position, while in Figure 9 the lower position is shown, in which the working stroke can be initiated as described above.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Press Drives And Press Lines (AREA)
  • Control Of Presses (AREA)
EP88113839A 1987-08-26 1988-08-25 Pièce hydraulique Withdrawn EP0304905A3 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE19873728418 DE3728418A1 (de) 1987-08-26 1987-08-26 Dynamisch vorgespannte druckmittelbetaetigte presse
DE3728418 1987-08-26

Publications (2)

Publication Number Publication Date
EP0304905A2 true EP0304905A2 (fr) 1989-03-01
EP0304905A3 EP0304905A3 (fr) 1989-09-20

Family

ID=6334491

Family Applications (1)

Application Number Title Priority Date Filing Date
EP88113839A Withdrawn EP0304905A3 (fr) 1987-08-26 1988-08-25 Pièce hydraulique

Country Status (3)

Country Link
US (1) US4890475A (fr)
EP (1) EP0304905A3 (fr)
DE (1) DE3728418A1 (fr)

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5076083A (en) * 1989-06-28 1991-12-31 Yoshikazu Kuze Device for performing press work in sequence
DE19643396B4 (de) * 1996-10-21 2008-09-11 Dieffenbacher Gmbh + Co. Kg Hydraulische Steuereinrichtung
WO2009026893A1 (fr) * 2007-08-24 2009-03-05 Christian Wieber Système d'entraînement pour presses hydrauliques
CN103521593A (zh) * 2013-09-26 2014-01-22 芜湖环球汽车配件有限公司 一种钣金件自动冲裁模具
CN104085128A (zh) * 2014-06-30 2014-10-08 南京迪威尔高端制造股份有限公司 组合式双向预应力承载机架

Families Citing this family (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
AT399785B (de) * 1991-05-06 1995-07-25 Hoerbiger Fluidtechnik Gmbh Gleichlaufmesseinrichtung
DE19642635A1 (de) * 1996-03-28 1997-10-02 Horst Baltschun Feinschneidpresse mit hydraulisch gekoppeltem Ringzacken- und Gegenhalterzylinder
DE10005023C2 (de) * 2000-02-04 2002-11-21 Feintool Internat Holding Ag L Feinschneidpresse
DE10116917A1 (de) * 2001-04-05 2002-10-10 Kramski Gmbh Führungsvorrichtung für Werkzeugmaschinen
US7765844B2 (en) * 2007-12-20 2010-08-03 Intergrated Industrial Systems, Inc. Prestressed rolling mill housing assembly with improved operational features
EP3010709B1 (fr) * 2013-06-19 2022-06-01 Bruderer Ag Procédé pour courber le socle de machine et/ou le coulisseau de presse d'une presse à découper et presse à découper
CN104226694B (zh) * 2014-09-30 2017-02-15 中色科技股份有限公司 一种铸轧机预应力控制系统
DE102015105400B4 (de) * 2015-04-09 2022-06-02 Langenstein & Schemann Gmbh Umformmaschine, insbesondere Schmiedehammer, und Verfahren zum Steuern einer Umformmaschine
CN106015124A (zh) * 2016-07-22 2016-10-12 中聚信海洋工程装备有限公司 一种液压泵与高压蓄能器叠加供压的液压快锻机组

Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE2512822A1 (de) * 1975-03-22 1976-09-30 Horst Schenk Vorrichtung zur schnittschlagdaempfung in pressen
DE2248024B2 (de) * 1972-09-29 1976-12-09 L. Schuler GmbH, 7320 Göppingen Schnittschlag-daempfungseinrichtung an schnitt-pressen
DE2739340A1 (de) * 1977-09-01 1979-03-15 Smg Sueddeutsche Maschinenbau Hydraulisch angetriebene presse
DE2824176A1 (de) * 1978-06-02 1979-12-06 Thyssen Industrie Hydraulische presse mit servohydraulischer regelung der stoesselbewegung
DE3039667A1 (de) * 1980-10-21 1982-05-19 Hans 4320 Hattingen Schoen Hydraulische presse, insbesondere stanzpresse
DE3233860A1 (de) * 1982-09-11 1984-03-15 Schoen, Hans, 4320 Hattingen Einrichtung zur parallelhaltung des stoessels an hydraulischen stanzpressen

Family Cites Families (10)

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Publication number Priority date Publication date Assignee Title
FR856289A (fr) * 1939-02-22 1940-06-10 Outil Mec Usinage Artillerie Presse hydraulique de grande puissance
DE1858838U (de) * 1960-01-11 1962-09-20 Erwin Baas Hydraulische mehrkolbenpresse od. dgl. mit kolbenartig ausgebildeten fuehrungssaeulen.
AT286070B (de) * 1969-04-22 1970-11-25 Haemmerle Ag Maschf Blechbearbeitungsmaschine
CA959309A (en) * 1972-10-24 1974-12-17 Igor G. Fedosenko High-speed counterstroke hammer
SU548352A1 (ru) * 1974-12-11 1977-02-28 Московский Авиационный Технологический Институт Имени К.Э.Циалковского Гидравлический молот
DE2852303A1 (de) * 1978-12-02 1980-06-04 Schloemann Siemag Ag Schmiedepresse, insbesondere freiform- schmiedepresse, in unterflurbauart
DE2901768A1 (de) * 1979-01-18 1980-07-24 Schoen & Cie Gmbh Einrichtung zur begrenzung des hubweges an schwenkamrstanzmaschinen
DE2905559A1 (de) * 1979-02-14 1980-08-28 August Laepple Gmbh & Co Werkz Tuschiervorrichtung
DE3112393C2 (de) * 1981-03-28 1985-08-08 Hans 4240 Emmerich Feldhaus Hydraulische Presse und ein Verfahren zu ihrem Betrieb
US4809535A (en) * 1987-06-15 1989-03-07 Williams-White Company Hydraulic press and process for molding or forming an article including incrementally variable positioned slide

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE2248024B2 (de) * 1972-09-29 1976-12-09 L. Schuler GmbH, 7320 Göppingen Schnittschlag-daempfungseinrichtung an schnitt-pressen
DE2512822A1 (de) * 1975-03-22 1976-09-30 Horst Schenk Vorrichtung zur schnittschlagdaempfung in pressen
DE2739340A1 (de) * 1977-09-01 1979-03-15 Smg Sueddeutsche Maschinenbau Hydraulisch angetriebene presse
DE2824176A1 (de) * 1978-06-02 1979-12-06 Thyssen Industrie Hydraulische presse mit servohydraulischer regelung der stoesselbewegung
DE3039667A1 (de) * 1980-10-21 1982-05-19 Hans 4320 Hattingen Schoen Hydraulische presse, insbesondere stanzpresse
DE3233860A1 (de) * 1982-09-11 1984-03-15 Schoen, Hans, 4320 Hattingen Einrichtung zur parallelhaltung des stoessels an hydraulischen stanzpressen

Cited By (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5076083A (en) * 1989-06-28 1991-12-31 Yoshikazu Kuze Device for performing press work in sequence
DE19643396B4 (de) * 1996-10-21 2008-09-11 Dieffenbacher Gmbh + Co. Kg Hydraulische Steuereinrichtung
WO2009026893A1 (fr) * 2007-08-24 2009-03-05 Christian Wieber Système d'entraînement pour presses hydrauliques
CN103521593A (zh) * 2013-09-26 2014-01-22 芜湖环球汽车配件有限公司 一种钣金件自动冲裁模具
CN104085128A (zh) * 2014-06-30 2014-10-08 南京迪威尔高端制造股份有限公司 组合式双向预应力承载机架
CN104085128B (zh) * 2014-06-30 2015-11-25 南京迪威尔高端制造股份有限公司 组合式双向预应力承载机架
WO2016000535A1 (fr) * 2014-06-30 2016-01-07 南京迪威尔高端制造股份有限公司 Cremaillere a paliers de precontrainte bidirectionnelle combinee

Also Published As

Publication number Publication date
DE3728418A1 (de) 1989-03-09
US4890475A (en) 1990-01-02
DE3728418C2 (fr) 1990-10-25
EP0304905A3 (fr) 1989-09-20

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