EP1097039B1 - Commande hydraulique pour combinaison de frein d'embrayage a commande hydraulique pour l'arbre primaire d'une presse mecanique - Google Patents

Commande hydraulique pour combinaison de frein d'embrayage a commande hydraulique pour l'arbre primaire d'une presse mecanique Download PDF

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Publication number
EP1097039B1
EP1097039B1 EP99932829A EP99932829A EP1097039B1 EP 1097039 B1 EP1097039 B1 EP 1097039B1 EP 99932829 A EP99932829 A EP 99932829A EP 99932829 A EP99932829 A EP 99932829A EP 1097039 B1 EP1097039 B1 EP 1097039B1
Authority
EP
European Patent Office
Prior art keywords
pressure
control
valve
hydraulic
control valve
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.)
Expired - Lifetime
Application number
EP99932829A
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German (de)
English (en)
Other versions
EP1097039A1 (fr
Inventor
Stefan Schmidt
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.)
Bosch Rexroth AG
Original Assignee
Mannesmann Rexroth AG
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Filing date
Publication date
Application filed by Mannesmann Rexroth AG filed Critical Mannesmann Rexroth AG
Publication of EP1097039A1 publication Critical patent/EP1097039A1/fr
Application granted granted Critical
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Anticipated expiration legal-status Critical
Expired - Lifetime 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
    • B30B15/14—Control arrangements for mechanically-driven presses
    • B30B15/142—Control arrangements for mechanically-driven presses controlling the brake or the clutch

Definitions

  • the invention is based on a hydraulic control system for actuating a Clutch brake combination of the drive shaft of a mechanical press is provided and which has the features from the preamble of claim 1.
  • Such a hydraulic control is known from DE 35 23 163 A1. at This hydraulic control will primarily be a larger quantity Pressure fluid is required if the hydraulic actuator releases the brake and closing the clutch moves and when the high clutch pressure builds up and the pressure medium is compressed. During the rest of a press cycle little or no pressure fluid is required.
  • a hydraulic accumulator is part of the pressure medium source, that within the cycle time, in that of the hydraulic actuator little Pressure medium is needed, is charged by the hydraulic pump and then, if a lot of pressure medium is required, releases pressure medium.
  • the control is the inlet connection of a 3/2-way safety valve a non-return valve to the hydraulic pump connected to the hydraulic pump.
  • a branch line runs between the check valve and the inlet connection to the hydraulic accumulator, in which a pressure-controlled shut-off valve sits, that way is controlled that from the hydraulic accumulator to the inlet connection of the safety valve Pressure fluid can flow in if a lot of pressure medium is required, and that is otherwise in its locked position.
  • the hydraulic accumulator is filled from the hydraulic pump via another branch line that bypasses the check valve and in which there is another check valve that leads to the pressure line section between the first check valve and the inlet connection of the safety valve blocks.
  • the safety valve also has a drain connection, which is connected to a tank is, and a consumer connection, from which a line to the hydraulic Actuator leads.
  • a drain connection which is connected to a tank is, and a consumer connection, from which a line to the hydraulic Actuator leads.
  • On the latter line is a pilot operated pressure relief valve connected with two pilot valves that are set to different pressures are. Depending on the position of a directional valve, neither of the two pilot valves is or one or the other pilot valve effective.
  • the control is carried out so that the check valve during releasing the brake and during the time when the clutch pressure is low is held, is open and closed during the remaining times of a press cycle is held.
  • the aim of the invention is therefore a hydraulic control with the features to develop from the preamble of claim 1 so that the necessary Functions can be obtained with less effort on components can.
  • the arrangement of the 3-way pressure control valve according to the invention does not into the one leading from the safety valve arrangement to the hydraulic actuator Line intervened so that this to brake the drive shaft of the press can also be relieved of pressure when the pressure control valve is in a position in his control port is connected to his pressure port gets stuck.
  • the cost of hydraulic components is particularly low if according to Claim 5 the pressure control valve by an electric actuator, in particular is adjustable by a proportional magnet.
  • the pressure control valve can be set to different pressure values can be set.
  • the ram 10 of a press can be seen via a coupling rod 11 with a drive shaft designed as a crankshaft 12 is connected.
  • the drive shaft 12 can via a clutch 13 from one Electric motor 14 are driven.
  • the plates 16 of the clutch are from the piston rod 17 a single-acting hydraulic cylinder 18 together in the axial direction can be pressed against a stop plate 23 driven by the motor 14.
  • the inner of the hydraulic cylinder 18 is by a piston 19 on which the piston rod 17th is attached, in a fully cylindrical pressure chamber 20 remote from the piston rod and in an annular cylindrical piston-side receiving space 21 for a helical compression spring 22 divided.
  • the disks 16 of the brake 15 are composed of this and can be pressed against a fixed stop plate 24.
  • the pressure in the Pressure chamber 20 slightly due to the increasing tension of the helical compression spring 22 increases, the slats 16 or a part of the slats 16 lie against the Parts of the clutch which are connected to the output of the electric motor 14 in a manner fixed against relative rotation 13 on.
  • the torque that can be transmitted via the clutch 13 now depends on the Height of the pressure in the pressure chamber 20 from.
  • the hydraulic cylinder 18 is supplied with pressure medium from a pressure medium source which essentially comprises a hydraulic pump 25 and a hydraulic accumulator 26.
  • the hydraulic pump 25 with a constant displacement is operated by an electric motor 27 driven and is located in a tank 28. It sucks from the tank per unit of time to a relatively small amount of pressure medium, which they in an output channel 29 issues. From there, the pressure medium can be transferred to the hydraulic pump 25 blocking check valve 30 flow into a pressure line 31 leading to Pressure port 32 of a 3-way pressure control valve 33 leads.
  • the hydraulic accumulator 26 is also connected.
  • a Pressure relief valve 34 is provided through which the pressure in the pressure line 31 and thus in the hydraulic accumulator 26 is limited to a maximum value. This Value is greater than the value at which an output channel 29 of the hydraulic pump 25 connected and controlled by the pressure in the pressure line 31 pressure shut-off valve 35 switches the flow of the hydraulic pump 25 to circulation and back conducts into the tank 28.
  • the pressure control valve 33 has a tank connection in addition to the pressure connection 32 40, which is connected to the tank 28 via a tank line 41, and one Control port 42, in which a certain depending on a predetermined setpoint Pressure is regulated.
  • the control connection is with the inlet connection 43 connected to a safety valve assembly 44, which also has a consumer connection 45, the via a consumer line 46 with the pressure chamber 20 of the Hydraulic cylinder 18 is connected, and has a tank connection 47 which over the tank line 41 already mentioned is connected to tank 28.
  • the safety valve arrangement 44 consists of two 4/2-way valves 48 and 49, which with the pressure control valve 33 to a valve block are summarized, the tank connection T, a pressure connection P, has a consumer connection A and a leakage connection Y.
  • the Connections between the individual valves are through channels within the valve blocks made up of three plates.
  • the pressure control valve 33 of the embodiment according to FIG. 1 is a pilot operated one Pressure control valve, the pilot valve by a proportional solenoid 51 to different Pressure values can be set.
  • the sequence of the pilot valve is connected to the leakage port Y.
  • On a measuring surface of the not shown Control piston of the pressure control valve is, as through the control line 52 indicated, the pressure in the control port 42 of the valve is returned.
  • the Control oil for the pilot valve can be taken from the pressure connection or the control connection become.
  • the two directional control valves 48 and 49 each under the effect a compression spring 53, they each connect the consumer line for themselves 46 with the tank connection T of the valve block and thus with the Tank line 41.
  • the two further connections of each directional control valve 48 and 49 are shut off in the rest position of the valves. Both are against it Directional control valves 48 and 49 in their working position, so there are two more Connections of the directional valve 48 and the other connections in series the directional control valve 49 a connection between the pressure chamber 20 and the control port 42 of the pressure control valve 33.
  • the safety valve arrangement 44 is the same as that from Figure 1, but shown in a highly simplified manner compared to Figure 1.
  • the pilot operated pressure control valve 33 of the embodiment according to FIG. 2 is two designed as pressure relief valves and to different pressure values set pilot valves 60 and 61 and a directional control valve 62 with three switching positions assigned. Are in a spring-centered central position of the directional valve 62 a control chamber 63 of the pressure control valve 33 and the inputs of the two pilot valves 60 and 61 cordoned off from each other. With one electromagnet each 64 or 65, the directional control valve 62 in a first working position in which the Control room 63 is connected to the input of pilot valve 60, or in a second working position in which the control room 63 with the entrance of the pilot valve 61 set at a lower pressure is connected.
  • control line 66 67 of the pressure control valve 33 is subjected to the pressure on one end face, which prevails in control output 42.
  • This pressure works in the sense of a connection of the control port 42 with the tank port 41 in the opposite direction and in In the sense of a connection of the control connection 42 with the pressure connection 31 the control piston 67 from the pressure in the control chamber 63 and from a weak one Compression spring 68 acted upon.
  • the control oil for the pilot control is via a Control line 69 taken from the pressure port 31.
  • the ram 10 of the press is close by the brake 15 with maximum braking force held at its top dead center when the pressure chamber 20 of the hydraulic cylinder 18 through the safety valve arrangement 44 via its tank connection 47 is relieved to the tank.
  • Figure 1 is in the rest position of the plunger 10 of the proportional magnet 51 set to a pressure setpoint that is higher than the maximum storage pressure, so that the control port 42 of the Pressure control valve is wide open connected to the pressure port 32.
  • the safety valve arrangement is switched at the beginning of a press cycle.
  • the setpoint of the pressure control valve is also the same 33 set to a value that corresponds to a soft dome.
  • the directional control valve 62 by excitation of the electromagnet 64 brought into its first switching position, in which the pilot valve 60 is effective is also on a pressure value corresponding to a soft dome is set.
  • the setting of the respective pressure control valve is maintained as long as the drive shaft 12 of the press is designated 75 in FIG Angular range.
  • the electromagnet 51 is energized more and the pressure setpoint is increased so much, that the torque required for the pressing process via the clutch can be transferred.
  • the pressure setpoint can be determined by the pressure in the hydraulic accumulator 26 are placed so that this pressure is effective as a clutch pressure.
  • the electromagnet 64 is switched off and thereby the directional valve 62 brought into its central position, in which the control room 63 of the pressure control valve 33 is shut off.
  • the clutch pressure rises memory pressure.
  • After passing through the angular range 76 is the largest Coupling force reached.
  • the pressing process now takes place in the angular range 77 instead, before the plunger 10 is raised again, the clutch pressure is maximum.
  • the electromagnet 51 is then opened set a pressure setpoint that is less than the pressure setpoint for the soft Is domes.
  • FIG. 1 the pressure setpoint that is less than the pressure setpoint for the soft Is domes.
  • the directional valve 62 is activated by excitation brought the electromagnet 65 into its second switching position, in which the Pilot valve 61 is effective, which is set to a lower pressure than the pilot valve 60 is.
  • the brake 15 now engages softly after passing through the angular range 78 switches the safety valve arrangement 44 so that in the angular range 79 maximum braking force is effective and the tappet is stopped at top dead center becomes.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Fluid-Pressure Circuits (AREA)
  • Control Of Presses (AREA)
  • Braking Arrangements (AREA)
  • Hydraulic Clutches, Magnetic Clutches, Fluid Clutches, And Fluid Joints (AREA)

Claims (8)

  1. Une commande hydraulique pour une combinaison (13, 15) d'embrayage et de freinage à actionnement hydraulique pour l'arbre (12) d'entraínement d'une presse mécanique,
    dotée d'une source de fluide de pression, qui présente une pompe (25) hydraulique et un accumulateur (26) hydraulique et qui est destinée à l'alimentation en fluide de pression d'un actionneur (18) hydraulique,
    dotée d'un dispositif (44) de valve de sécurité, qui présente un raccord (43) d'alimentation permettant un cheminement du flux de la source (25, 26) de fluide de pression vers l'actionneur (18) hydraulique,
    et dotée d'une valve (33) de pression réglable, en fonction du réglage de laquelle l'actionneur (18) hydraulique peut être soumis à des pressions de travail variables, caractérisée en ce que
    la valve de pression est un régulateur (33) de pression à trois voies doté d'un raccord (32) de pression, qui peut être relié à la source (25, 26) de fluide de pression, d'un raccord (40) de réservoir et d'un raccord (42) de régulation, qui est relié au raccord (43) d'alimentation du dispositif (44) de valve de sécurité.
  2. Une commande hydraulique conforme à la revendication n° 1, caractérisée en ce que la liaison entre le raccord (32) de pression et le raccord (42) de régulation du régulateur (33) de pression est commandée de façon à être entièrement ouverte, lorsque le dispositif (44) de valve de sécurité est dans sa position de repos, où le dispositif (44) de valve de sécurité décharge l'actionneur (18) hydraulique de toute pression et où le raccord (43) d'alimentation est fermé.
  3. Une commande hydraulique conforme à la revendication n° 2, caractérisée en ce que la liaison du raccord (32) de pression vers le raccord (42) de régulation du régulateur (33) de pression est commandée de façon à ouvrir, lorsqu'une consigne de pression, qui dépasse la pression du système maximum, est donnée.
  4. Une commande hydraulique conforme à la revendication n° 2, caractérisée en ce que une chambre de commande au niveau d'une surface (71) de mesure du régulateur (33) de pression est raccordée par voie fluide à une conduite (46), qui mène du dispositif (44) de valve de sécurité vers l'actionneur (18) hydraulique.
  5. Une commande hydraulique conforme à une revendication précédente, caractérisée en ce que le régulateur (33) de pression peut être régulé à l'aide d'un organe de réglage électrique, en particulier au travers d'un solénoïde (51) à effet proportionnel.
  6. Une commande hydraulique conforme à une revendication précédente, caractérisée en ce que le régulateur (33) de pression est piloté.
  7. Une commande hydraulique conforme à la revendication n° 6, caractérisée en ce que plusieurs valves de pilotage (60, 61), qui sont calibrées sur des pressions de valeurs différentes, sont dédiées au régulateur (33) de pression et que, en fonction de la position de moyens (62) de distribution, une valve (60, 61) de pilotage différente, selon le cas, agit pour limiter la pression dans une chambre (63) de pilotage du régulateur (33) de pression.
  8. Une commande hydraulique conforme à la revendication n° 6 ou n° 7, caractérisée en ce que, pour une position de moyens (62) de distribution, une chambre (63) de pilotage du régulateur (33) de pression est fermée contre un écoulement d'huile de pilotage et, pour une autre position des moyens (62) de distribution, une valve (60, 61) de pilotage limite la pression de pilotage dans la chambre (63) de pilotage.
EP99932829A 1998-07-11 1999-07-06 Commande hydraulique pour combinaison de frein d'embrayage a commande hydraulique pour l'arbre primaire d'une presse mecanique Expired - Lifetime EP1097039B1 (fr)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE19831144A DE19831144A1 (de) 1998-07-11 1998-07-11 Hydraulische Steuerung für eine hydraulisch betätigbare Kupplungsbremskombination für die Antriebswelle einer mechanischen Presse
DE19831144 1998-07-11
PCT/EP1999/004691 WO2000002720A1 (fr) 1998-07-11 1999-07-06 Commande hydraulique pour combinaison de frein d'embrayage a commande hydraulique pour l'arbre primaire d'une presse mecanique

Publications (2)

Publication Number Publication Date
EP1097039A1 EP1097039A1 (fr) 2001-05-09
EP1097039B1 true EP1097039B1 (fr) 2002-12-11

Family

ID=7873752

Family Applications (1)

Application Number Title Priority Date Filing Date
EP99932829A Expired - Lifetime EP1097039B1 (fr) 1998-07-11 1999-07-06 Commande hydraulique pour combinaison de frein d'embrayage a commande hydraulique pour l'arbre primaire d'une presse mecanique

Country Status (4)

Country Link
EP (1) EP1097039B1 (fr)
DE (2) DE19831144A1 (fr)
ES (1) ES2189441T3 (fr)
WO (1) WO2000002720A1 (fr)

Families Citing this family (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE10062229A1 (de) * 2000-12-02 2002-06-13 Mannesmann Rexroth Ag Hydraulische Steuerung für eine hydraulisch betätigbare Kupplungsbremskombination insbesondere an der Exzenterwelle einer mechanischen Presse
ES2267653T3 (es) * 2000-12-02 2007-03-16 Bosch Rexroth Ag Mando hidraulico para una combinacion de freno-embrague accionado hidraulicamente, especialmente en el arbol de excentrica de una prensa mecanica.
DE10155050A1 (de) * 2001-11-09 2003-05-22 Porsche Ag Kraftfahrzeug-Antriebsstrang mit wenigstens einer unter Vermittlung von Druckmedium betätigbaren und unter Einwirkung eines Betriebsmediums laufenden Kupplungsanordnung und einem unter Vermittlung von Druckmedium betätigbaren Getriebe sowie entsprechendes Kupplungssystem
US6922991B2 (en) * 2003-08-27 2005-08-02 Moog Inc. Regulated pressure supply for a variable-displacement reversible hydraulic motor
DE102006050300B4 (de) * 2006-10-23 2013-05-08 Ortlinghaus-Werke Gmbh Druckmittelbetätigte Schaltung
DE102012022086B4 (de) * 2012-11-09 2023-05-11 Volkswagen Aktiengesellschaft Hydraulische Steuerungsvorrichtung
US10183852B2 (en) * 2015-07-30 2019-01-22 Danfoss Power Solutions Gmbh & Co Ohg Load dependent electronic valve actuator regulation and pressure compensation
CN105257605B (zh) * 2015-11-06 2017-05-10 杨贝贝 一种压力控制液压系统节能方法及其节能装置
CN105485067B (zh) * 2016-01-28 2017-09-29 佛山市佛锐达机电科技有限公司 一种压力控制液压系统节能装置
CN105697436B (zh) * 2016-04-12 2017-07-28 浙江大学 一种流量优先供给的小容积盲腔压力控制液压系统

Family Cites Families (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CH638721A5 (en) * 1979-07-13 1983-10-14 Seitz Eugen Ag Device for controlling a press
DE2935702A1 (de) * 1979-09-04 1981-03-12 Herion-Werke Kg, 7012 Fellbach Schaltungsanordnung.
GB2068823A (en) * 1980-02-12 1981-08-19 Arosverken Ab Hydraulic control device for a mechanical press
EP0051684B1 (fr) * 1980-10-31 1984-02-15 L. SCHULER GmbH Commande d'embrayage et/ou de frein d'une presse
EP0216776B1 (fr) * 1984-07-19 1988-10-19 Zf-Herion-Systemtechnik Gmbh Systeme de reglage de pression pour un embrayage et/ou un frein a commande hydraulique pour l'arbre d'entrainement d'une presse
DD256851A1 (de) * 1986-12-31 1988-05-25 Warnke Umformtech Veb K Einrichtung zur steuerung des momentenverlaufes druckmittelbetaetigter reibungskupplungen bzw. -bremsen an pressen
DE4221756C2 (de) * 1992-07-02 2003-06-12 Bosch Rexroth Ag Sicherheitsschaltung für hydraulische Verbraucher
US5511082A (en) 1994-05-10 1996-04-23 General Instrument Corporation Of Delaware Punctured convolutional encoder
US5668820A (en) 1995-01-23 1997-09-16 Ericsson Inc. Digital communication system having a punctured convolutional coding system and method
US5680915A (en) * 1996-01-31 1997-10-28 Midwest Brake Bond Company Brake and clutch control system

Also Published As

Publication number Publication date
DE19831144A1 (de) 2000-01-13
ES2189441T3 (es) 2003-07-01
DE59903768D1 (de) 2003-01-23
EP1097039A1 (fr) 2001-05-09
WO2000002720A1 (fr) 2000-01-20

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