WO2000002720A1 - 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
WO2000002720A1
WO2000002720A1 PCT/EP1999/004691 EP9904691W WO0002720A1 WO 2000002720 A1 WO2000002720 A1 WO 2000002720A1 EP 9904691 W EP9904691 W EP 9904691W WO 0002720 A1 WO0002720 A1 WO 0002720A1
Authority
WO
WIPO (PCT)
Prior art keywords
pressure
valve
connection
control
hydraulic
Prior art date
Application number
PCT/EP1999/004691
Other languages
German (de)
English (en)
Inventor
Stefan Schmidt
Original Assignee
Mannesmann Rexroth 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 Mannesmann Rexroth Ag filed Critical Mannesmann Rexroth Ag
Priority to DE59903768T priority Critical patent/DE59903768D1/de
Priority to EP99932829A priority patent/EP1097039B1/fr
Publication of WO2000002720A1 publication Critical patent/WO2000002720A1/fr

Links

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 which is provided for actuating a clutch / brake combination of the drive shaft of a mechanical press and which has the features from the preamble of claim 1.
  • Such a hydraulic control is known from DE 35 23 163 A1.
  • a larger amount of pressure medium is primarily required when the hydraulic actuator moves when releasing the brake and closing the clutch and when the high clutch pressure is built up and the pressure medium is compressed.
  • the hydraulic fluid source includes a hydraulic accumulator, which is charged by the hydraulic pump within the cycle time in which little hydraulic fluid is required by the hydraulic actuator, and releases hydraulic fluid when a lot of hydraulic fluid is required.
  • the inlet connection of a 3/2-way safety valve is connected to the hydraulic pump via a check valve which blocks the hydraulic pump.
  • a branch line to the hydraulic accumulator in which a pressure-controlled shut-off valve sits, which is controlled in such a way that pressure medium can flow from the hydraulic accumulator to the inlet connection of the safety valve if a lot of pressure medium is required, and which is otherwise in its blocking position located.
  • the hydraulic accumulator is filled from the hydraulic pump via a further branch line which bypasses the shut-off valve and in which there is a further check valve which leads to the pressure line tion section between the first check valve and the inlet port of the safety valve blocks.
  • the safety valve also has a drain connection, which is connected to a tank, and a consumer connection, from which a line leads to the hydraulic actuator.
  • a pilot-operated pressure relief valve with two pilot valves is connected to the latter, which are set to different pressures. Depending on the position of a directional valve, neither of the two pilot valves or one or the other pilot valve is effective.
  • the directional control valve ' also controls the check valve between the hydraulic accumulator and the inlet connection of the safety valve. The control takes place in such a way that the check valve is open during the release of the brake and during the time in which the clutch pressure is kept low and is kept closed during the remaining times of a press cycle.
  • the aim of the invention is therefore to develop a hydraulic control with the features from the preamble of claim 1 so that the necessary functions can be obtained with less effort on components.
  • the hydraulic control is equipped with the features from the characterizing part of claim 1 in addition to the features from the preamble.
  • the inventive arrangement of the 3-way pressure control valve does not intervene in the line leading from the safety valve arrangement to the hydraulic actuator, so that it can be relieved of pressure to brake the drive shaft of the press even when the pressure control valve is in a position in which Control port connected to its pressure port remains stuck.
  • the pressure control valve thus also fulfills the function of the additional check valve from the prior art.
  • pressure medium always flows from the hydraulic accumulator to the hydraulic actuator via the pressure control valve and the safety valve arrangement if the pressure difference existing via the pressure control valve and the opening cross section of the pressure control valve result in a pressure medium flow which is greater than the pressure medium flow supplied by the hydraulic pump .
  • the connection between the pressure connection and the control connection of the pressure control valve is fully open.
  • the hydraulic actuator then reacts particularly quickly after the safety valve arrangement has been switched over, since pressure medium can immediately flow through the pressure control valve and this does not first move from one position in which its control connection is connected to the tank connection to the other position. must be brought. This is advantageously achieved by a configuration according to patent claim 3 or according to patent claim 4.
  • the outlay on hydraulic components is particularly low if, according to claim 5, the pressure control valve is adjustable by an electric actuator, in particular by a proportional magnet.
  • the pressure control valve can be set to different pressure values using the electric actuator.
  • the pressure control valve can be set to different pressure levels by training according to claims 7 or 8.
  • FIG. 1 shows a first embodiment in which the pressure control valve is pilot-controlled and proportionally adjustable by means of an electromagnet
  • FIG. 2 shows a second embodiment with a pilot-controlled pressure control valve with two pilot valves set to different pressures
  • FIG. 3 shows the pressure control valve from FIG. 2 and FIG. 4 in a highly schematic manner the course of a press cycle in an angle diagram.
  • the ram 10 of a press can be seen, which is connected via a coupling rod 11 to a drive shaft 12 designed as a crankshaft.
  • 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 hydraulic cylinder 18 acting on one side can be pushed together in the axial direction and pressed against a stop plate 23 driven by the motor 14.
  • the interior of the hydraulic cylinder 18 is moved by a piston 19, to which the piston rod 17 is attached, into a fully cylindrical pressure chamber 20 on the piston rod side and in a ring-cylindrical piston chamber 21 for a screw
  • I O compression spring 22 divided. From this, the disks 16 of the brake 15 can be pushed together and pressed against a fixed stop plate 24.
  • the brake 15 is actuated with a force determined by the prestressing of the helical compression spring 22. If the pressure in the pressure chamber 20 rises, the braking force initially decreases until finally
  • the pressure assumes a value equivalent to the preload of the helical compression spring 22. Then the piston 19 and the piston rod 17 begin to move. The brake 15 is released. After a short stroke, during which the pressure in the pressure chamber 20 increases slightly due to the increasing tension of the helical compression spring 22, the slats 16 or part of the slats 16 lie against them
  • the hydraulic cylinder 18 is supplied with pressure medium from a pressure medium source 25, which essentially comprises a hydraulic pump 25 and a hydraulic accumulator 26.
  • the hydraulic pump 25 with a constant displacement is driven by an electric motor 27 and is located in a tank 28. From the tank, it sucks in a relatively small amount of pressure medium per unit of time, which it emits into an outlet channel 29. From there, the pressure medium can be transferred to the hydropump pe 25 blocking check valve 30 flow into a pressure line 31, which leads to the pressure connection 32 of a 3-way pressure control valve 33.
  • the hydraulic accumulator 26 is also connected to the pressure line 31.
  • a pressure limiting valve 34 is also provided, by means of 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 a pressure cut-off valve 35 connected to the outlet channel 29 of the hydraulic pump 25 and controlled by the pressure in the pressure line 31 switches the delivery flow of the hydraulic pump 25 to circulation and leads it back into the tank 28.
  • the pressure control valve 33 has a tank connection 40, which is connected to the tank 28 via a tank line 41, and a control connection 42, in which a specific pressure is regulated depending on a predetermined desired value.
  • the control connection is connected to the inlet connection 43 of a safety valve arrangement 44, which also has a consumer connection 45, which is connected via a consumer line 46 to the pressure chamber 20 of the hydraulic cylinder 18, and a tank connection 47, which is connected to the tank 28 via the aforementioned tank line 41 is.
  • the safety valve arrangement 44 consists of two 4/2-way valves 48 and 49, which are combined with the pressure control valve 33 to form a valve block which has a tank connection T, a pressure connection P, a consumer connection A and a leakage connection Y.
  • the connections between the individual valves are realized by channels within the valve block, which is made up of three plates.
  • the pressure control valve 33 of the embodiment according to FIG. 1 is a pilot-controlled pressure control valve, the pilot valve of which can be set to different pressure values by a proportional magnet 51.
  • the sequence of the pilot valve is connected to the leakage port Y.
  • the pressure in the control connection 42 of the valve is returned to a measuring surface of the control piston of the pressure control valve (not shown in more detail).
  • the control oil for the pilot valve can be taken from the pressure connection or the control connection.
  • each directional control valve 48 and 49 In the rest position, which the two directional control valves 48 and 49 each take under the action of a compression spring 53, they each connect the consumer line 46 to the tank connection T of the valve block and thus to 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. If, on the other hand, both directional control valves 48 and 49 are in their working position, there is a connection between the pressure chamber 20 and the control connection 42 of the pressure control valve 33 via the two further connections of the directional control valve 48 and the further connections of the directional control valve 49 in series. if only one of the two directional control valves is in its rest position, the pressure chamber 20 of the hydraulic cylinder 18 is relieved of pressure and the inlet connection 43 of the safety valve arrangement 44 is shut off.
  • the safety valve arrangement 44 is the same as that from FIG. 1, but is shown in a greatly simplified manner compared to FIG.
  • the pilot-controlled pressure control valve 33 of the embodiment according to FIG. 2 is assigned two pilot valves 60 and 61 designed as pressure limiting valves and adjusted to different pressure values, as well as a directional control valve 62 with three switching positions.
  • a control chamber 63 of the pressure control valve 33 and the inputs of the two pilot valves 60 and 61 are shut off from one another.
  • the directional control valve 62 can be moved into a first working position in which the Control room 63 is connected to the input of pilot valve 60, or brought into a second working position in which control room 63 is connected to the input of pilot valve 61 set to a lower pressure.
  • control piston 67 of the pressure control valve 33 Via a control line 66, the control piston 67 of the pressure control valve 33, which is shown schematically in FIG. 3, is acted upon on one end face by the pressure prevailing in the control outlet 42. This pressure acts in the sense of connecting the control port 42 to the tank port 41. In the opposite direction and in the sense of connecting the control port 42 to the pressure port 31, the control piston 67 is acted upon by the pressure in the control chamber 63 and by a weak compression spring 68.
  • the control oil for the pilot control is taken from the pressure connection 31 via a control line 69.
  • the plunger 10 of the press is held close to its top dead center by the brake 15 with maximum braking force when the pressure chamber 20 of the hydraulic cylinder 18 is relieved to the tank by the safety valve arrangement 44 via its tank connection 47.
  • the proportional magnet 51 in the rest position of the plunger 10, is set to a pressure setpoint which is higher than the maximum storage pressure, so that the control connection 42 of the pressure control valve is connected to the pressure connection 32 in a widely open manner.
  • the latter is also the case in the embodiment according to FIG. 2, since the directional valve 62 shuts off the control chamber 63 in its central position.
  • Another way to ensure an open connection between the control connection and the pressure connection of the pressure control valve 33 in the rest position of the plunger 10 is to tap the pressure acting on the measuring surface of the control piston between the safety valve arrangement 44 and the hydraulic cylinder 18. Because the line 46 is relieved to the tank via the safety valve arrangement 44, then no force acting on the control piston acts in the sense of a connection of the control connection to the tank connection.
  • This alternative of pressure tapping by the dotted control line 70 is indicated in FIG.
  • the safety valve arrangement is switched at the beginning of a press cycle.
  • the setpoint of the pressure control valve 33 is at the same time set to a value which corresponds to a soft coupling.
  • FIG. 1 Another way to ensure an open connection between the control connection and the pressure connection of the pressure control valve 33 in the rest position of the plunger 10 is to tap the pressure acting on the measuring surface of the control piston between the safety valve arrangement 44 and the hydraulic cylinder 18. Because the line 46 is relieved to the tank via the safety valve arrangement 44, then no force acting on the control piston acts in the
  • the directional valve 62 is brought into its first switching position by excitation of the electromagnet 64, in which the pilot valve 60 is effective, which is also set to a pressure value corresponding to a soft coupling.
  • the setting of the respective pressure control valve is maintained as long as the drive shaft 12 of the press is in the angular range designated 75 in FIG.
  • the electromagnet 51 is then supplied with more current and the pressure setpoint is increased so much that the torque required for the pressing process can be transmitted via the clutch.
  • the pressure setpoint can be placed over the pressure in the hydraulic accumulator 26, so that this pressure is effective as a clutch pressure.
  • the electromagnet 64 is switched off and, as a result, the directional valve 62 is brought into its central position, in which the control chamber 63 of the pressure control valve 33 is shut off.
  • the clutch pressure thus rises to the accumulator pressure.
  • the electromagnet 51 is then set to a pressure setpoint which is smaller than the pressure setpoint for the soft coupling.
  • the directional valve 62 is brought into its second switching position by excitation of the electromagnet 65, in which the pilot valve 61 is effective, which is set to a lower pressure than the pilot valve 60.
  • the brake 15 now engages softly.
  • the safety valve arrangement 44 switches over, so that maximum braking force is effective in the angular range 79 and the tappet is stopped at top dead center.

Landscapes

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

Abstract

L'invention concerne une commande hydraulique utilisée pour une combinaison de frein d'embrayage (13, 15) à commande hydraulique pour l'arbre primaire (12) d'une presse mécanique. Une commande connue de ce type comprend une source de fluide hydraulique présentant une pompe hydraulique (15) et un accumulateur hydraulique (26), servant à alimenter un actionneur (18) hydraulique en fluide hydraulique, ainsi qu'un système de soupape de sécurité (44) comportant un raccord d'alimentation (43) par l'intermédiaire duquel une voie d'écoulement mène de la source de fluide hydraulique à l'actionneur hydraulique. Cette commande comprend en outre une soupape de pression (33) ajustable, en fonction de l'ajustement de laquelle différentes pression de travail peuvent être appliquées à l'actionneur hydraulique. Afin de réduire le nombre d'éléments constitutifs qu'implique ce type de commande, la soupape de pression (33) est une soupape de régulation de la pression à trois voies comportant un raccord de pression (32) pouvant être connecté à la source de fluide hydraulique, un raccord de réservoir (40) et un raccord de régulation relié au raccord d'alimentation (43) du système de soupape de sécurité (44). Ce type de soupape de régulation de la pression et son mode de commutation permettent de ne pas intervenir dans la connexion entre le système de soupape de sécurité et l'actionneur hydraulique. En outre, l'accumulateur hydraulique (26) est bloqué lorsque la pression régnant au niveau du raccord d'alimentation doit être abaissée et qu'une voie d'écoulement allant du raccord de régulation au raccord du réservoir est ouverte à cet effet.
PCT/EP1999/004691 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 WO2000002720A1 (fr)

Priority Applications (2)

Application Number Priority Date Filing Date Title
DE59903768T DE59903768D1 (de) 1998-07-11 1999-07-06 Hydraulische steuerung für eine hydraulisch betätigbare kupplungsbremskombination für die antriebswelle einer mechanischen presse
EP99932829A 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

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE19831144.3 1998-07-11
DE19831144A DE19831144A1 (de) 1998-07-11 1998-07-11 Hydraulische Steuerung für eine hydraulisch betätigbare Kupplungsbremskombination für die Antriebswelle einer mechanischen Presse

Publications (1)

Publication Number Publication Date
WO2000002720A1 true WO2000002720A1 (fr) 2000-01-20

Family

ID=7873752

Family Applications (1)

Application Number Title Priority Date Filing Date
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

Country Status (4)

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

Cited By (2)

* 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
US7351175B2 (en) * 2001-11-09 2008-04-01 Dr. Ing. H.C.F. Porsche Aktiengesellschaft Drive train for a motor vehicle

Families Citing this family (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1211059B1 (fr) * 2000-12-02 2006-08-16 Bosch Rexroth AG Commande hydraulique pour combinaison embrayage-frein à actionnement hydraulique en particulier pour l'arbre excentrique d'une presse mécanique
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
CN107327426B (zh) * 2016-01-28 2018-10-19 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方法及其节能装置
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

Citations (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3019408A1 (de) * 1979-07-13 1981-01-22 Seitz Eugen Ag Einrichtung zur steuerung einer presse
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
WO1986000849A1 (fr) * 1984-07-19 1986-02-13 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
US4580674A (en) * 1980-10-31 1986-04-08 L. Schuler Gmbh Control arrangement for the actuating pressure applied to a clutch and/or brake of a mechanical press
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

Family Cites Families (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
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

Patent Citations (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3019408A1 (de) * 1979-07-13 1981-01-22 Seitz Eugen Ag Einrichtung zur steuerung einer presse
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
US4580674A (en) * 1980-10-31 1986-04-08 L. Schuler Gmbh Control arrangement for the actuating pressure applied to a clutch and/or brake of a mechanical press
WO1986000849A1 (fr) * 1984-07-19 1986-02-13 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
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

Cited By (2)

* 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
US7351175B2 (en) * 2001-11-09 2008-04-01 Dr. Ing. H.C.F. Porsche Aktiengesellschaft Drive train for a motor vehicle

Also Published As

Publication number Publication date
ES2189441T3 (es) 2003-07-01
EP1097039B1 (fr) 2002-12-11
DE59903768D1 (de) 2003-01-23
DE19831144A1 (de) 2000-01-13
EP1097039A1 (fr) 2001-05-09

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