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US3565110A - Control valves - Google Patents

Control valves Download PDF

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Publication number
US3565110A
US3565110A US3565110DA US3565110A US 3565110 A US3565110 A US 3565110A US 3565110D A US3565110D A US 3565110DA US 3565110 A US3565110 A US 3565110A
Authority
US
United States
Prior art keywords
pressure
valve
control valve
port
fluid
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
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English (en)
Inventor
Robert F Hodgson
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.)
Commercial Shearing Inc
Commercial Shearing and Stamping Co
Original Assignee
Commercial Shearing Inc
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 Commercial Shearing Inc filed Critical Commercial Shearing Inc
Application granted granted Critical
Publication of US3565110A publication Critical patent/US3565110A/en
Anticipated expiration legal-status Critical
Expired - Lifetime 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
    • F15B13/0401—Valve members; Fluid interconnections therefor
    • F15B13/0402—Valve members; Fluid interconnections therefor for linearly sliding valves, e.g. spool valves
    • F15B13/0403—Valve members; Fluid interconnections therefor for linearly sliding valves, e.g. spool valves a secondary valve member sliding within the main spool, e.g. for regeneration flow
    • 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
    • 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
    • Y10T137/7722—Line condition change responsive valves
    • Y10T137/7781—With separate connected fluid reactor surface
    • Y10T137/7784—Responsive to change in rate of fluid flow
    • Y10T137/7792—Movable deflector or 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
    • Y10T137/86493—Multi-way valve unit
    • Y10T137/86574—Supply and exhaust
    • Y10T137/8667—Reciprocating valve
    • Y10T137/86694—Piston valve
    • Y10T137/86702—With internal flow passage
    • 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
    • Y10T137/86493—Multi-way valve unit
    • Y10T137/86718—Dividing into parallel flow paths with recombining
    • Y10T137/86734—With metering feature
    • 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

Definitions

  • a pressure-compensated directional control valve capable of supplying a constant volume of fluid having a directional control valve with inlet and outlet ports and first and second motor ports for connection to opposite sides of a fluid motor, a pressure-compensating valve having an axial bore, an inlet port connected to the inlet port of the control valve, an outlet port connected to the outlet port of the control valve, a pressure-sensing port, a valve member movable in the bore and biased to a position normally blocking the inlet from the outlet port, said valve member having opposite surfaces thereon exposed respectively to the fluid pressure at said inlet port and to fluid pressure at said pressure-sensing port acting with the biasing means and being movable in response to a fluid pressure differential between its in
  • VALVES This invention relates to control valves and particularly to pressure-compensated control valves for fluid-actuated systems.
  • the present invention provides a valve structure which automatically regulates the position of the valve depending upon the load so as to maintain a constant volume flow of fluid.
  • a directional control valve for selectively operating a fluid motor at a controlled speed, said valve having inlet and outlet ports and first and second motor ports for connection to opposite sides of said fluid motor, a pressure-compensating valve having an axial bore, an inlet port connected to the inlet port of said control valve, an outlet port, a pressure-sensing port, a valve member movable in said axial bore, means biasing said valve member to a position normally blocking said outlet port from said inlet port and partially blocking said inlet port from the inlet port of the control valve, said valve member having opposits surfaces thereon exposed to respectively the fluid pressure at said inlet port and to fluid pressure at said pressure sensing port acting with said biasing means, said valve member in the pressure-compensating valve being movable in response to a fluid pressure differential between its inlet port and pres sure-sensing port through the directional control valve to connect said inlet port to said return port for bypassing input pressure fluid from said directional control valve to thereby regulate the input flow
  • the directional control valve is provided with a valve member movable in a bore therein, said valve member being hollow at each end to form chambers therein adapted selectively to communicate through the valve member walls with the inlet port, work ports and outlet port and the pressure-sensing port of the pressurecornpensating valve.
  • FIG. 1 is a schematic section through a directional control valve and pressure-compensating valve according to my invention
  • FIG. 2 is a section on the line II-II of FIG. 1;
  • FIG. 3 is a section on the line III-III of FIG. 1;
  • FIG. 4 is a section on the line IV-IV of FIG. 1.
  • a directional control valve housing having an axial bore 11 carrying a valve member 12.
  • the housing is provided with spaced exhaust chambers 13 and 14 adjacent each end and intersecting bore 11, a pair of work chambers 15 and 16, one adjacent each exhaust chamber and each adapted to be connected to the opposite sides of a fluid motor. Between the two work chambers are spaced inlet chambers 17 and 18.
  • the valve member 12 is hollow at each end to provide a pair of spaced internal chambers 19 and 20 extending axially of the valve member and connected by an axial passage 21 and ball chambers 22 and 23 at each end of said passage.
  • the ball chambers are provided with freely movable balls 24 and 25 held in place by plugs 26 and 27 threaded into the ends of chambers 22 and 23 and each provided with a passage 26a and 27a respectively.
  • Each of chambers 22 and 23 is provided with passages 22a and 23a extending radially to the periphery of the valve member.
  • the chamber 20 is provided with two sets of radial openings 20a and 20b and chamber 19 is provided'with a corresponding set of radial openings 19a and 19b.
  • the openings 19a and 20a lie on a helical line so that their center lines are not on the same circumferential line.
  • Openings 19b and 20b are separated from opening 190 and 200 respectively by check valves 19c and 20c within the chamber operated by springs 19d and 20d.
  • a pair of spaced annular grooves 28 and 29 surround the valve member in alignment with inlet chambers 17 and 18 when the valve is in neutral position.
  • openings 20a are one after another opened to work chamber 16 while openings 20b are open to outlet or exhaust chambers 14.
  • openings 19a are opened to inlet chamber 17 and openings 1% are opened to work chamber 15.
  • the openings 19a and 20a are opened to the appropriate chamber one after another to provide slowly increased flow of fluid into the corresponding chamber in a throttling manner.
  • This fluid then opens the corresponding check valve 190 and 19d permitting fluid in chamber 19 to flow to work chamber 15 and thence to one side of a fluid motor (not shown).
  • the fluid in the opposite side of the fluid motor is discharged to work chamber 16 thence through openings 20a, check valve 200 and into outlet chamber 14.
  • the pressure in chamber 19 passes through passages 26a forcing ball 24 to close passage 21 and its corresponding radial passages 21a. Passage 23a is isolated at this point. Moving the valve in the opposite direction from neutral reverses the flow of fluid.
  • the valve housing is provided with annular grooves 30, 31 and 32 which when the valve is in neutral are open to radial passages 22a, 21a and 23a respectively.
  • the groove 31 is connected to a radial passage 33 which extends to the outside of housing 10.
  • Grooves and 32 are connected respectively to passages 34 and 35 which extend angularly to the outside of housing 10 and connect at the outside of the housing to a common port 36.
  • the pressure compensating valve housing has a bore 41 closed at one end by a cap 42 threaded into the bore at one end and by a cap 43 threaded into the bore at the opposite end.
  • the bore 41 is intersected by outlet or exhaust chambers 44 and 45 at each end connected together by a U-shaped passage 46.
  • Inlet or high-pressure chambers 47 and 48 intersect the bore intermediate the outlet chambers.
  • a pressure sensing passage 49 intersects the bore 41 between the inlet chambers 47 and 48.
  • the cap 43 extends through the exhaust or outlet chamber 45 and is provided with a groove 43a which permits free movement of fluid around it in chamber 45.
  • a valve member 50 is freely movable in bore 41 and is biased toward cap 42 by spring 51 which bears on cap 43 at one end and on the valve member 50 with the other.
  • the valve member is hollow from the end adjacent cap 42 to a point spaced from its opposite end to form an inner axial chamber 52.
  • An annular groove 55 surrounds the valve member 50 in communication with passage 49. Groove 55 is connected to the area between cap 43 and valve member 50 by an axially extending passage 56 which parallels the chamber 52.
  • Outlet section 60 has a bore 61 closed at one end by threaded cap 62 which holds relief valve base member 63 in place.
  • This base member 63 has an axial bore 64 which communicates with outlet chamber 65 through radial passage 66.
  • Relief valve 67 in bore 61 is biased to base member 63 by spring 68.
  • the body of relief valve 67 is provided with parallel bores 69 which provide communication between inlet chambers 70 and 71.
  • the relief valve 67 is pilot operated and controlled by pilot valve 72 which opens into outlet chamber 73.
  • Outlet chambers 65 and 73 are connected by U-shaped passage 74.
  • An angular passage 75 extends from port 76 to outlet passage 73.
  • the port 76 is designed to communicate with port 36 of the directional control valve.
  • valve structure of this invention is as follows. Referring to FIG. 1, I have shown the assembly of directional control valve 10, inlet pressure compensating valve 40 and outlet section 60 in their position with no fluid pressure applied.
  • fluid pressure is applied to input port 100 from a pump (not shown) the chambers 48, 18, 71, 70, 17 and 47 are pressurized along with the interior chamber 52 of valve element 50.
  • the pressure with chamber 52 causes the valve 50 to shift to the left viewing FIG. 1 to discharge out of the open end of chamber 52 into chamber 44 and thence through chambers 14 and 73 to the outlet and back to tank (not shown).
  • the control valve is shifted, as for example to the right viewing FIG.
  • valve member 12 in bore 11 controls the amount of volume initially by the amount and number of openings 19a opened to chamber 17.
  • Return fluid from the work chamber 16 enters openings 20a, past check valve 200 and exhausts through openings 20b to exhaust or outlet chamber 14.
  • passage 22a comes into communication with passage 49 as the valve member is moved to the right so that the area behind valve 50 in which spring 51 operates is pressurized at the same pressure as chamber 19in valve 12.
  • valve member 50 moves to the right cutting off the amount of fluid dumping through the valve end to chamber 44 increasing the pressure of input fluid in chamber 17 to maintain a constant flow through work chamber 15. If, on the other hand, the pressure drops in chamber 19 then the pressure behind valve 50 drops and the valve moves leftward increasing the amount being bypassed to chamber 44.
  • the change in pressure drop controls the amount of fluid being dumped in valve 40 so that the amount of fluid going to the work port is constant. When the control valve 12 is completely opened, that is, at its left or right extreme one hundred percent of the oil goes to the work port and the valve 50 is in its extreme right position with no oil being bypassed. When so pressurized, both ball checks 24 and 25 close the passage 21 from chamber 19 to chamber 20.
  • the valve of the present invention is the first which can be used in conjunction with more than one directional control valve. Assuming two identical control valves corresponding to valve and assuming 50 gallons of available hydraulic at a pressure of 3,000 p.s.i. and that 20 gallons at 1,000 p.s.i. is being used at work chamber of the first valve from inlet 100, then assuming that the next succeeding valve is operated and it requires 2,000 psi. on work chamber 16 of this second valve, this will cause fluid in chamber to pass through passage 23a to port 36 of the previous valve.
  • valve 50 maintains a constant volume through it while the second valve is manually operated.
  • control valve operating at highest pressure automatically becomes pressure compensated and the other valve or valves in the system are manually operated.
  • a pressure-compensated directional control valve comprising a directional control valve for selectively operating a fluid motor at controlled speed, said valve having inlet and outlet ports and first and second motor ports for connection to opposite sides of a fluid motor, a pressure compensating valve having an axial bore, an inlet port connected to the inlet port of said control valve, an outlet port connected to the outlet port of said control valve, a pressure sensing port, a valve member movable in said axial bore, means biasing said valve member to a position normally blocking said outlet from said inlet port, said valve member having opposite surfaces thereon exposed respectively to fluid pressure from said inlet port and to fluid pressure at said pressure-sensing port acting with said biasing means, said valve member being movable in response to fluid pressure differential between its inlet port and pressure-sensing port through the directional control valve to connect said inlet and outlet ports for bypassing input pressure fluid to thereby regulate the input flow through said directional control valve to one of said work ports.
  • a control valve as claimed in claim 1 wherein the pressure-compensating valve member is hollow and open at one end, said hollow portion communicating with the inlet port of both the directional control valve and the pressure compensating valve through openings in the sidewalls and discharging through its open end to the outlet port when the pressure in the chamber exceeds the biasing means and pressure-sensing pressures.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Fluid-Pressure Circuits (AREA)
  • Multiple-Way Valves (AREA)
  • Safety Valves (AREA)
US3565110D 1969-08-04 1969-08-04 Control valves Expired - Lifetime US3565110A (en)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
US84729369A 1969-08-04 1969-08-04

Publications (1)

Publication Number Publication Date
US3565110A true US3565110A (en) 1971-02-23

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ID=25300282

Family Applications (1)

Application Number Title Priority Date Filing Date
US3565110D Expired - Lifetime US3565110A (en) 1969-08-04 1969-08-04 Control valves

Country Status (5)

Country Link
US (1) US3565110A (de)
JP (1) JPS536374B1 (de)
DE (1) DE1959764B2 (de)
FR (1) FR2057616A5 (de)
GB (1) GB1293550A (de)

Cited By (13)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3718159A (en) * 1971-01-20 1973-02-27 Hydraulic Industries Control valve
DE2600776A1 (de) * 1975-01-13 1976-07-15 Commercial Shearing Steuerschieber
DE2604181A1 (de) * 1975-02-06 1976-08-19 Commercial Shearing Steuerschieber
US4095617A (en) * 1976-05-06 1978-06-20 Commercial Shearing, Inc. Control valves
DE2916575A1 (de) * 1978-09-08 1980-03-13 Jidosha Kiki Co Durchflussregelschieber
DE3035511A1 (de) * 1979-02-21 1982-04-08 Mac Valves, Inc., 48096 Wixom, Mich. Vierwege-luftventil
US4457341A (en) * 1982-03-04 1984-07-03 Vickers, Incorporated Variable pressure drop proportional motor controlled hydraulic directional valve
FR2544405A1 (fr) * 1983-04-13 1984-10-19 Linde Ag Installation d'entrainement hydrostatique de recepteurs, notamment de groupe piston-cylindre
US5218992A (en) * 1991-06-28 1993-06-15 Dana Corporation Check valve retainer
US5471839A (en) * 1989-03-24 1995-12-05 Hitachi Construction Machinery Co., Ltd. Valve apparatus and hydraulic drive system
CN100348352C (zh) * 2006-01-25 2007-11-14 杨秀勇 一种液压控制阀的平面滑合付结构的加工方法
WO2009062572A1 (de) * 2007-11-14 2009-05-22 Hydac Filtertechnik Gmbh Hydraulische ventilvorrichtung
EP2163770B1 (de) * 2008-09-10 2013-11-06 HAWE Hydraulik SE Interner Lastdruckabgriff für ein Mehrwege-Mehrstellungs-Schieberventil

Families Citing this family (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CA964163A (en) * 1972-03-08 1975-03-11 Ford Motor Company Of Canada Tractor hydraulic lift control valve
DE2248486C2 (de) * 1972-10-03 1985-10-24 Friedrich Dipl.-Ing. 7770 Überlingen Tuschka Hydraulischer Steuerschieber
DE2306461A1 (de) * 1973-02-09 1974-08-15 Parker Hannifin Corp Absperrorgananordnung
DE2420242C2 (de) * 1974-04-26 1982-12-23 Robert Bosch Gmbh, 7000 Stuttgart Hydraulische Steuerschiebervorrichtung
JPS5422068A (en) * 1977-07-19 1979-02-19 Kawasaki Heavy Ind Ltd Control valve for machine
DE2801689C2 (de) * 1978-01-16 1982-11-11 Heilmeier & Weinlein Fabrik für Oel-Hydraulik GmbH & Co KG, 8000 München Steuerventileinrichtung
DE2804045A1 (de) * 1978-01-31 1979-08-09 Bosch Gmbh Robert Steuervorrichtung fuer einen hydraulisch betriebenen verbraucher
JPS555951U (de) * 1978-06-29 1980-01-16
DE3047499C2 (de) * 1980-12-17 1983-08-04 Integral Hydraulik & Co, 4000 Düsseldorf Durch hydraulische Druckimpulse steuerbares Auf-Zu-Ventil in Sitzventilbauweise
FR2517791B1 (fr) * 1981-12-03 1986-02-28 Rexroth Sigma Perfectionnements apportes aux distributeurs hydrauliques
JP2557000B2 (ja) * 1990-05-15 1996-11-27 株式会社小松製作所 操作弁装置
CN105402468B (zh) * 2015-09-16 2018-06-29 中国船舶重工集团公司第七0七研究所九江分部 一种电磁阀箱油路切换装置

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2651324A (en) * 1949-11-01 1953-09-08 New York Air Brake Co Multiple control valve
US3112764A (en) * 1960-10-28 1963-12-03 Bendix Corp Flow-regulating valve
US3215160A (en) * 1962-12-28 1965-11-02 New York Air Brake Co Valve
US3255777A (en) * 1963-11-26 1966-06-14 New York Air Brake Co Directional control valve
US3481364A (en) * 1967-11-30 1969-12-02 Commercial Shearing Hydraulic valves

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2651324A (en) * 1949-11-01 1953-09-08 New York Air Brake Co Multiple control valve
US3112764A (en) * 1960-10-28 1963-12-03 Bendix Corp Flow-regulating valve
US3215160A (en) * 1962-12-28 1965-11-02 New York Air Brake Co Valve
US3255777A (en) * 1963-11-26 1966-06-14 New York Air Brake Co Directional control valve
US3481364A (en) * 1967-11-30 1969-12-02 Commercial Shearing Hydraulic valves

Cited By (17)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3718159A (en) * 1971-01-20 1973-02-27 Hydraulic Industries Control valve
DE2600776A1 (de) * 1975-01-13 1976-07-15 Commercial Shearing Steuerschieber
DE2604181A1 (de) * 1975-02-06 1976-08-19 Commercial Shearing Steuerschieber
US4058135A (en) * 1975-02-06 1977-11-15 Commercial Shearing, Inc. Compensated work port fluid valves and work port compensators
US4095617A (en) * 1976-05-06 1978-06-20 Commercial Shearing, Inc. Control valves
DE2916575A1 (de) * 1978-09-08 1980-03-13 Jidosha Kiki Co Durchflussregelschieber
DE3035511A1 (de) * 1979-02-21 1982-04-08 Mac Valves, Inc., 48096 Wixom, Mich. Vierwege-luftventil
US4457341A (en) * 1982-03-04 1984-07-03 Vickers, Incorporated Variable pressure drop proportional motor controlled hydraulic directional valve
FR2544405A1 (fr) * 1983-04-13 1984-10-19 Linde Ag Installation d'entrainement hydrostatique de recepteurs, notamment de groupe piston-cylindre
US4617798A (en) * 1983-04-13 1986-10-21 Linde Aktiengesellschaft Hydrostatic drive systems
US5471839A (en) * 1989-03-24 1995-12-05 Hitachi Construction Machinery Co., Ltd. Valve apparatus and hydraulic drive system
US5218992A (en) * 1991-06-28 1993-06-15 Dana Corporation Check valve retainer
CN100348352C (zh) * 2006-01-25 2007-11-14 杨秀勇 一种液压控制阀的平面滑合付结构的加工方法
WO2009062572A1 (de) * 2007-11-14 2009-05-22 Hydac Filtertechnik Gmbh Hydraulische ventilvorrichtung
US20100300552A1 (en) * 2007-11-14 2010-12-02 Rueb Winfried Hydraulic valve device
US8464757B2 (en) * 2007-11-14 2013-06-18 Hydac Filtertechnik Gmbh Hydraulic valve device
EP2163770B1 (de) * 2008-09-10 2013-11-06 HAWE Hydraulik SE Interner Lastdruckabgriff für ein Mehrwege-Mehrstellungs-Schieberventil

Also Published As

Publication number Publication date
DE1959764A1 (de) 1971-02-25
JPS536374B1 (de) 1978-03-07
GB1293550A (en) 1972-10-18
FR2057616A5 (de) 1971-05-21
DE1959764B2 (de) 1972-06-15

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