EP0015492A2 - Dispositif de commande hydraulique indépendant de la charge pour la régulation du débit - Google Patents

Dispositif de commande hydraulique indépendant de la charge pour la régulation du débit Download PDF

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Publication number
EP0015492A2
EP0015492A2 EP80100962A EP80100962A EP0015492A2 EP 0015492 A2 EP0015492 A2 EP 0015492A2 EP 80100962 A EP80100962 A EP 80100962A EP 80100962 A EP80100962 A EP 80100962A EP 0015492 A2 EP0015492 A2 EP 0015492A2
Authority
EP
European Patent Office
Prior art keywords
piston
pressure
pump
holding
balance
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.)
Granted
Application number
EP80100962A
Other languages
German (de)
English (en)
Other versions
EP0015492B1 (fr
EP0015492A3 (en
Inventor
Siegfried Dipl.-Ing. Hertell
Claus Kirchher
Horst Kahl
Siegfried Hoffmann
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.)
Oerlikon Barmag AG
Original Assignee
Barmag Barmer Maschinenfabrik 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
Family has litigation
First worldwide family litigation filed litigation Critical https://patents.darts-ip.com/?family=6064215&utm_source=google_patent&utm_medium=platform_link&utm_campaign=public_patent_search&patent=EP0015492(A2) "Global patent litigation dataset” by Darts-ip is licensed under a Creative Commons Attribution 4.0 International License.
Application filed by Barmag Barmer Maschinenfabrik AG filed Critical Barmag Barmer Maschinenfabrik AG
Publication of EP0015492A2 publication Critical patent/EP0015492A2/fr
Publication of EP0015492A3 publication Critical patent/EP0015492A3/de
Application granted granted Critical
Publication of EP0015492B1 publication Critical patent/EP0015492B1/fr
Expired legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B13/00—Details of servomotor systems ; Valves for servomotor systems
    • F15B13/02—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors
    • F15B13/04—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor
    • F15B13/0416—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor with means or adapted for load sensing
    • F15B13/0417—Load sensing elements; Internal fluid connections therefor; Anti-saturation or pressure-compensation valves
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T137/00—Fluid handling
    • Y10T137/2496—Self-proportioning or correlating systems
    • Y10T137/2559—Self-controlled branched flow systems
    • Y10T137/2574—Bypass or relief controlled by main line fluid condition
    • Y10T137/2579—Flow rate responsive
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T137/00—Fluid handling
    • Y10T137/2496—Self-proportioning or correlating systems
    • Y10T137/2559—Self-controlled branched flow systems
    • Y10T137/2574—Bypass or relief controlled by main line fluid condition
    • Y10T137/2579—Flow rate responsive
    • Y10T137/2589—Pilot valve operated
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T137/00—Fluid handling
    • Y10T137/2496—Self-proportioning or correlating systems
    • Y10T137/2559—Self-controlled branched flow systems
    • Y10T137/2574—Bypass or relief controlled by main line fluid condition
    • Y10T137/2579—Flow rate responsive
    • Y10T137/2594—Choke
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T137/00—Fluid handling
    • Y10T137/8593—Systems
    • Y10T137/87169—Supply and exhaust
    • Y10T137/87177—With bypass
    • Y10T137/87185—Controlled by supply or exhaust valve

Definitions

  • a control device for load-independent flow control is known in which a so-called "pressure differential balance" is used to maintain a constant but adjustable pressure difference between a pump pressure line and a respective connected consumer.
  • the differential pressure balance consists of a piston which is movable in a cylinder chamber and which is connected on one side to the pump pressure line o It is possible that this is not a direct connection, but that the pump pressure is initially increased or reduced by suitable hydraulic devices, if this seems appropriate to achieve better functioning of the differential pressure balance. It is only important that one side of the piston is pressurized, which follows the pump pressure according to a defined function.
  • the other side of the piston is connected to the load pressure, ie the pressure that prevails in the consumer line.
  • the piston is additionally supported on this so-called “load pressure side” against the pressure on the pump pressure side by a spring. This causes the piston to be in an equilibrium, which is determined on the one hand by the pump pressure and on the other hand by the sum of spring force and load pressure.
  • the balance cylinder is connected to the tank through an opening which is opened and closed by a control edge of the balance piston. The opening and closing should preferably take place continuously.
  • the consumer pressure does not have to be given directly to the load pressure side either. It is also sufficient here that a pressure is exerted which follows the load pressure according to a certain function.
  • This described device which is referred to in the aforementioned DE-OS as "pressure differential balance" serves the purpose of maintaining a certain constant pressure difference between the pump line and the consumer line. This will cause. the flow from the pump to the consumer, which is dependent in particular on the pressure difference, is kept constant. This creates the possibility of operating the consumer at a predetermined constant speed regardless of its load.
  • pressure differential balance continues to serve the purpose of shutting off the consumer line for a "pressureless” oil circulation, i.e. Ensure oil circulation against a low residual pressure when a pump with a constant flow is used.
  • the invention allows on the one hand a practically lossless idling of the oil pump, but on the other hand also the adaptation of the residual pressure to the respective requirements of the circuit.
  • the measure according to claim 2 serves the further purpose of avoiding that the large piston surface also on its surface facing away from its load pressure side, i.e. the ring area with which the load pressure is applied, which can result from leakage. Furthermore, the measure according to claim 2 also has the particular advantage that through a targeted leakage, which is completely irrelevant for the performance of the pump and the hydraulic system because of its insignificance, the load pressure side can be relieved when the consumer is switched off by when the consumer is switched off, the oil escapes from the load pressure side of the pressure differential balance through a leak to the tank.
  • the measure according to claim 3 ensures that when the consumer is switched on, the pressure differential balance quickly comes into operation by first bringing the spring to its operating voltage before the load pressure side of the pressure differential balance is pressurized.
  • the measures according to claim 5 and claim 6 serve the purpose of adjusting the switching path of the holding piston (differential piston) close.
  • the spring force of the spring acting on the differential pressure balance during operation and / or when idling can be set as required by the control behavior of the connected consumer or is desirable in order to achieve the lowest possible power loss when idling.
  • the differential piston sits in a cylinder different from the cylinder of the differential pressure compensator, in such a way that a relative movement between the two cylinders is possible and the axial distance between the two cylinders is adjustable.
  • the invention according to claim 7 also makes use of the idea that the balance piston of the differential pressure balance is rendered inoperative in order to produce a circulation of the delivery flow that is as unpressurized as possible.
  • the proposal according to claim 7 serves the purpose of increasing the force exerted by the pump pressure when idling and therefore compensating for the spring force acting on the balance piston to a far greater extent than during operation.
  • the holding piston supporting the pressure compensating piston is acted upon in idle with the pump pressure or a pressure corresponding to this.
  • the holding piston is switched back to a position facing away from the weighing piston.
  • the holding cylinder, in which the holding piston is movable is hydraulically separated from the balance cylinder, any pressure present in the system can be used for this.
  • the balance cylinder and holding cylinder preferably merge into one another. In this case, the holding piston is switched back when the consumer is switched on by the pressure on the pump pressure side of the balance piston.
  • the balance piston 2 is movable in the cylinder housing 1.
  • the cylinder housing has the pump pressure channel 3, wel cher is connected to the delivery side of the pump, not shown here, delivering a constant flow.
  • the pump pressure is transmitted to the pump pressure side of the balance piston 2 through the overflow channel 4. This is pushed to the right by the pump pressure in the drawing.
  • the cylinder housing 1 also has the consumer channel 9, which can be connected to the hydraulic consumer and is used via throttle 19 to transmit the consumer pressure to the load pressure side 8 of the balance piston 2.
  • the balance piston 2 is still loaded by the spring 10 on the load pressure side.
  • the load pressure on the load pressure side 8 builds up via leakage bore 24, tank connection channel 17 and tank connection 7.
  • the balance piston 2 is now pressed to the right against the spring 10 and thus releases the connection between the pump pressure channel 3 and the tank outlet 7 via the control edge 6.
  • the pump therefore only pumps into the tank (idle). It is desirable that the power required (idle power) is as low as possible. It is therefore desirable to have the lowest possible residual pump pressure when idling, which can only be achieved if the spring force 10 is as low as possible.
  • the exemplary embodiment according to the invention has the holding element 11, which supports the spring 10 during the operation of the consumer.
  • the holding element 11 is movable from the stop 12 to the left.
  • the holding element on its back - i.e. against stop 12 - has oil passages and does not have a sealing effect against stop 12.
  • the holding element 11 is supported by the differential piston 13.
  • the differential piston consists of the small piston side 15 and the large piston side 14.
  • the large piston side 14 is connected to the consumer pressure channel 9 on the load pressure side 16.
  • the annular surface side 18 of the differential piston 13 is connected to the tank outlet 7 through the tank outlet channel 17.
  • the small piston side 15 is acted upon by the pressure on the load pressure side 8.
  • the differential piston 13 executes a defined switching path 21.
  • the switching path 21 can be adjusted by means of the wedge-shaped stop 22 by means of the adjusting screw 23. This also sets the spring force 10.
  • the pressure relief takes place on the load pressure side 8 and the load pressure side 16 of the differential piston.
  • the throttle 19 has the effect that when the consumer pressure channel 9 is connected to the consumer 28, the pressure on the load pressure side 16 of the differential piston 13 is initially established and the spring 10 is thus switched into its operating position.
  • differential piston 13 and its circuit is thus caused that the spring 10 receives its optimum voltage during operation of the consumer 28 and is relaxed to such an extent when the pump 26 is idle that an acceptable residual pump pressure is established.
  • Fig. 2 also shows a so-called "pressure differential balance" with cylinder housing 1, balance piston 2, pump pressure channel 3, pump pressure side 5, control edge 6, tank drain 7, load pressure side 8, consumer pressure channel (load pressure channel) 9, spring 10.
  • This pressure differential balance can also in a hydraulic circuit can be included, as shown with the pump 26, valve 27 and consumer 28 in Fig. 1.
  • the balance piston 2 has the same functions as discussed in FIG. 1.
  • the connection between pump pressure channel 3 and pump pressure side 5 of the pressure differential balance is made through the overflow channel 29, in which the valve 30 is switched on.
  • a holding piston 31 is provided in a holding cylinder 32.
  • the holding piston has a plunger 33, which supports the balance piston 2 on the pump pressure side 5 ′.
  • the piston area of the holding piston 31 on the working side 34 of the holding piston is substantially larger than the piston area of the balance piston on the pump pressure side 5.
  • the holding cylinder 32 and pump pressure chamber 5 of the pressure differential balance 2 merge into one another. However, it is also possible that both are sealed against one another on the tappet 33.
  • the valve 30 is provided for switching the functions of the holding piston 31 and the balance piston 2.
  • the valve 30 is a two-position valve.
  • the pump pressure channel 3 is connected to the working side 34 of the holding piston 31 via channel 37 and channel 38, and the pump pressure side 5 is connected to the tank discharge channel 7 via channel 29 and channel 36.
  • the working side 34 of the holding piston 31 is acted on by the pump pressure.
  • an increased force is therefore opposed to the spring 10, so that the balance piston 2 extends further to the right when idling and thus releases a larger flow at the control edge 6 between the pump and the tank. This can result in a low residual pump pressure.
  • valve 30 If there is a consumer pressure on the consumer pressure side 8 of the differential pressure balance, i.e. In the operating positions of valve 27 according to FIG. 1, this consumer pressure via channel 35 is used to actuate valve 30. The valve 30 then releases a connection of the pump pressure channel 3 via channel 37 and channel 29 to the pump pressure side 5 of the balance piston 2 and on the other hand connects the working side 34 of the holding piston 31 via channel 38 to the tank drain 7. This means that when the pressure differential is applied to the load differential Holding piston 31 is moved away to the left and is deactivated.

Landscapes

  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Fluid-Pressure Circuits (AREA)
  • Control Of Positive-Displacement Pumps (AREA)
  • Safety Valves (AREA)
EP80100962A 1979-03-01 1980-02-27 Dispositif de commande hydraulique indépendant de la charge pour la régulation du débit Expired EP0015492B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE2908018 1979-03-01
DE19792908018 DE2908018A1 (de) 1979-03-01 1979-03-01 Hydraulische steuervorrichtung fuer lastunabhaengige durchflussregelung

Publications (3)

Publication Number Publication Date
EP0015492A2 true EP0015492A2 (fr) 1980-09-17
EP0015492A3 EP0015492A3 (en) 1981-02-18
EP0015492B1 EP0015492B1 (fr) 1984-01-04

Family

ID=6064215

Family Applications (1)

Application Number Title Priority Date Filing Date
EP80100962A Expired EP0015492B1 (fr) 1979-03-01 1980-02-27 Dispositif de commande hydraulique indépendant de la charge pour la régulation du débit

Country Status (3)

Country Link
US (2) US4303091A (fr)
EP (1) EP0015492B1 (fr)
DE (1) DE2908018A1 (fr)

Families Citing this family (17)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3146322A1 (de) * 1981-11-23 1983-06-01 Danfoss A/S, 6430 Nordborg Steuerventileinrichtung fuer einen hydraulischen verbraucher
US4693272A (en) * 1984-02-13 1987-09-15 Husco International, Inc. Post pressure compensated unitary hydraulic valve
JPS60147574U (ja) * 1984-03-13 1985-10-01 自動車機器株式会社 動力舵取装置
US4663936A (en) * 1984-06-07 1987-05-12 Eaton Corporation Load sensing priority system with bypass control
DE3690051C1 (de) * 1985-02-23 1997-09-18 Barmag Barmer Maschf Proportionalventil mit einem einstellbaren Drosselventil zwischen Pumpe und Last sowie einer Druckwaage
US4738104A (en) * 1985-03-23 1988-04-19 Barmag Ag Hydraulic power system
DE3521579A1 (de) * 1985-06-15 1986-12-18 J.M. Voith Gmbh, 7920 Heidenheim Steuerventil
DE3625222A1 (de) * 1986-07-25 1988-02-04 Index Werke Kg Hahn & Tessky Druckregler fuer hydraulisch gesteuerte werkzeugmaschinen
US4798126A (en) * 1987-03-23 1989-01-17 Caterpillar Inc. Load responsive system using load responsive pump control of a bypass type
IT1213973B (it) * 1987-07-17 1990-01-05 Oleostar Srl Valvola di controllo del flusso per circuito idraulico prioritario di potenza
DE4421357A1 (de) * 1994-06-18 1995-12-21 Bosch Gmbh Robert Pneumatisches Wegeventil
KR100208732B1 (ko) * 1996-05-21 1999-07-15 토니헬샴 가변 재생기능이 구비된 중장비용 콘트롤밸브
DE19725472A1 (de) * 1997-06-17 1998-12-24 Bosch Gmbh Robert Mengenregelventil
US10007276B2 (en) * 2014-05-20 2018-06-26 Hamilton Sundstrand Corporation Pressure-regulating valves
US9791062B2 (en) 2014-10-13 2017-10-17 Fema Corporation Of Michigan Hydraulic valve having pressure compensated flow control
CN110477999B (zh) * 2019-08-29 2021-07-02 湖南瀚德微创医疗科技有限公司 一种输出恒定夹持力的手术夹钳
CN113108102B (zh) * 2021-03-30 2023-02-03 中国船舶重工集团公司第七0四研究所 一种用于提高大型海工波浪补偿装置安全性的限速切断阀

Family Cites Families (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CH444601A (de) * 1966-12-13 1967-09-30 Beringer Hydraulik Gmbh Steuervorrichtung für hydraulisch betriebene Einrichtungen
US3631890A (en) * 1970-04-06 1972-01-04 Borg Warner Flow extending bypass valve
CH534816A (de) * 1972-02-18 1973-03-15 Beringer Hydraulik Gmbh Steuervorrichtung für lastunabhängige Durchflussregelung
US3777773A (en) * 1972-02-22 1973-12-11 Koehring Co Pressure compensating valve mechanism
US4178962A (en) * 1972-10-30 1979-12-18 Tomco, Inc. Control valve with flow control means
DE2320935B1 (de) * 1973-04-25 1974-06-12 Heilmeier & Weinlein, Fabrik Fuer Oel-Hydraulik, 8000 Muenchen Leerlaufventil
US3971216A (en) * 1974-06-19 1976-07-27 The Scott & Fetzer Company Load responsive system with synthetic signal
US3937129A (en) * 1974-10-23 1976-02-10 The Scott & Fetzer Company Load responsive system with area change flow extender

Also Published As

Publication number Publication date
US4303091A (en) 1981-12-01
EP0015492B1 (fr) 1984-01-04
US4355655A (en) 1982-10-26
EP0015492A3 (en) 1981-02-18
DE2908018A1 (de) 1980-09-11

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