EP0103250A1 - Soupape de contrôle pour contrôle hydraulique - Google Patents

Soupape de contrôle pour contrôle hydraulique Download PDF

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Publication number
EP0103250A1
EP0103250A1 EP83108731A EP83108731A EP0103250A1 EP 0103250 A1 EP0103250 A1 EP 0103250A1 EP 83108731 A EP83108731 A EP 83108731A EP 83108731 A EP83108731 A EP 83108731A EP 0103250 A1 EP0103250 A1 EP 0103250A1
Authority
EP
European Patent Office
Prior art keywords
valve
bore
bushing
inlet
liquid
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
EP83108731A
Other languages
German (de)
English (en)
Other versions
EP0103250B1 (fr
Inventor
Kenneth Dee Kramer
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.)
Deere and Co
Original Assignee
Deere and Co
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 Deere and Co filed Critical Deere and Co
Priority to AT83108731T priority Critical patent/ATE21147T1/de
Publication of EP0103250A1 publication Critical patent/EP0103250A1/fr
Application granted granted Critical
Publication of EP0103250B1 publication Critical patent/EP0103250B1/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
    • F15B13/01—Locking-valves or other detent i.e. load-holding devices
    • 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
    • Y10T137/2544—Supply and exhaust type
    • Y10T137/2554—Reversing or 4-way valve systems

Definitions

  • the invention relates to a control valve for fluid control between a pump, a collecting container and a double-acting fluid motor, the control valve having a housing with a valve bore, with two inlets connecting a section of the valve bore with the pump, with two the valve bore with the corresponding connections of the Outlets connecting liquid motor and with a collecting container connection connecting the valve bore with the collecting container.
  • the invention is based on the object of developing a control valve of the type described at the outset for controlling overflowing loads which does not "oscillate" under an overflowing load.
  • the two intake valves can be solenoid controlled. Furthermore, it is expedient if each check valve can be individually adjusted in relation to the return flow in order to change its throttling 3
  • the new valve does not "vibrate" when overloaded, it can be operated electrically and has independently controllable flow rates in both directions.
  • the valve is also suitable for controlling and locking a hydraulic load.
  • the new valve has a simple design and is inexpensive to manufacture; in addition, the new valve consumes little or no energy during operation. !
  • valve bore opens with its two ends into a hollow cylindrical screw plug screwed into the housing, which has an annular valve seat at its inner end, against which a locking ball arranged inside the screw plug is pressed by the resilient member which is inside a hollow guide part fixed in the end screw is arranged.
  • the flow is regulated by adjusting the stop screws of the check valves.
  • the solenoid valves are alternately energized to maintain three valve positions.
  • FIG. 1 shows an electro-hydraulic valve 10 for fluid control between a pump 12, a reservoir 14 and a fluid motor 16.
  • the valve 10 has a housing 18 through which a valve bore 20 extends.
  • the valve bore 20 has a central section 21 with an annular groove 23 which forms a section of a return path which is connected to the collecting container 14.
  • Two inlet bores 22, 24 open into the valve bore 20 via inlet chambers 26, 28 and connect the inlet chambers to the pump 12 via corresponding inlets 30, 32.
  • On-off fluid control is achieved by inlet valves 34,36, which are controlled by conventional on-off solenoids 38,40.
  • check valves 42, 44 are provided, each having a hollow cylindrical end screw 46, each of which is provided with an annular, inward-facing valve seat 48 for a check ball 50.
  • a spring guide 52 and a spring 54 are also provided in the check valves, which press the check ball 50 against the valve seat 48 for abutment.
  • the feather guides 52 are held by expansion rings 56.
  • the screw connection between the end screw 46 and the housing 18 makes it possible to screw the end screws 46 into the valve bore 20 at different depths and thus to achieve a variable measurement control of the return flow.
  • the end screws 46 are secured in the desired position by a clamping nut 58 and a spring ring 60.
  • a pilot valve 62 is arranged in the central section 21 of the valve bore 20 and has a hollow cylindrical bushing 64 which is guided in the bore section 21 in a displaceable and largely sealing manner.
  • This bushing 64 has two annular sliding surfaces 66, 68 which are separated from one another by a central section which has three flats 70 (see FIGS. 2 and 3). These flats 70 form a return path between the inlet chambers 26, 28 and the groove 23 when the bushing is displaced sufficiently far from its central position shown in FIG.
  • the sliding surfaces 66, 68 are provided with small pressure compensation grooves 67, 69 (see FIG. 4) which run axially within the surface of the corresponding sliding surface and allow the bushing 64 to be re-centered when both check valves 42, 44 are closed again.
  • the bushing 64 also comprises four balance ring grooves 71 between the sliding surfaces 66, 68. i
  • the pilot valve 62 further comprises two identically designed valve parts 72, each of which is displaceably guided in the opposite ends of the bushing 64 with a hollow cylindrical plunger 74.
  • the inner ends of the plungers 74 each form a valve seat 76 for the sealing contact of a valve ball 78, which is arranged within the bushing 64 between the two plungers 74.
  • Each valve part 72 has one! Flange 80, which can abut an end face of the bush 64.
  • Each flange 80 is provided with a through channel 82, which the interior of the hollow plunger 74 with the one lasshunt 26.28 connects.
  • the flange 80 forming the head of the valve part 72 also has a central, axially extending pin 84, the free end of which can act on the check ball 50 of the check valves 42, 44.
  • expansion rings 86 are provided which engage in grooves in the inner wall of the valve bore 20.
  • a spring 88 is provided between the locking ball 50 and the associated valve part 72, which press the locking ball 50 and the valve part 72 apart.
  • a spring 90 is provided in each tappet 74 and presses the valve ball 78 into a central position between the tappets 74.
  • the illustrated control valve operates as follows: If the liquid motor 16 is to be extended, the solenoid 38 is energized to pull up the inlet valve 34 (based on the illustration according to FIG. 1) and so open the inlet bore 22 and the inlet chamber 26 and liquid to pump through inlet 30. This pressure fluid flows from the inlet chamber 26 through the shut-off valve 42 to the head end of the liquid motor 16. The pressure fluid acts on the bushing 64 in the inlet chamber 26 and through the through channel 82 of the left valve part 72 also through the right valve part 72 via the valve ball 78, so that the bushing 64, valve ball 78 and right valve part 72 are shifted to the right (based on FIG. 1) until the flange 80 of the right valve part 72 abuts against the expansion ring 86.
  • the pin 84 of the right valve part 72 acts on the right locking ball 50 and lifts it from its seat 48. Due to this displacement of the bushing 64, the sliding surface 68 moves to the right and opens a connection between the inlet chamber 28 and the collecting container 14 via flats 70 and the annular groove 23 , Inlet chamber 28, flats 70 and annular groove 23rd
  • This backflow is metered by the variable and controllable space between the blocking ball 50 and seat 48.
  • This controlled metering creates a pressure drop in the return flow along the blocking ball 50, whereby the pressure in the chamber 28 is reduced to a pressure which is lower than that The case would be if the space between the locking ball 50 and the seat 48 were not so limited.
  • This reduced pressure in chamber 28 prevents the return flow from shifting pilot valve 62 to the left and check valve 44 closes under the effect of an overload.
  • the inlet valve 34 is closed by switching off the solenoid 38; the flow of flow from the pump 12 to the liquid motor 16 is interrupted.
  • the shut-off valve 46 closes and prevents backflow; the pressures in the inlet chambers 26, 28 begin to equalize. This pressure equalization allows the sleeve 64, the valve ball 78 and the right valve element 72 to return to their starting position (according to FIG. 1) under the influence of the springs 50, 88, whereby the locking ball 50 of the locking valve 44 rests against its seat can.
  • the valve 10 operates in the same way when the liquid motor 16 is to be retracted by energizing the solenoid 40.
  • the degree of throttling of the return flow can be changed independently of one another. So for example, according to FIG. 1, the end screw 46 of the check valve 44 can be screwed deeper into the locking hole 20 than the end screw 46 of the check valve 42. Therefore, the left valve part 72 cannot remove the check ball 50 of the check valve 42 from its seat as far as it does through the right one Valve part 72 with respect to the blocking ball 50 of the blocking valve 44 is possible. Therefore, the check valve 42 exerts a higher throttling when the motor 16 retracts on the return flow than the check valve 44 when the motor 16 extends.

Landscapes

  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Fluid-Driven Valves (AREA)
  • Check Valves (AREA)
  • Valve Device For Special Equipments (AREA)
  • Magnetically Actuated Valves (AREA)
  • Safety Valves (AREA)
  • Valve Housings (AREA)
  • Lift Valve (AREA)
  • Control Of Positive-Displacement Pumps (AREA)
  • Fluid-Pressure Circuits (AREA)
EP83108731A 1982-09-13 1983-09-05 Soupape de contrôle pour contrôle hydraulique Expired EP0103250B1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
AT83108731T ATE21147T1 (de) 1982-09-13 1983-09-05 Steuerventil zur fluessigkeitssteuerung.

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
US416836 1982-09-13
US06/416,836 US4461314A (en) 1982-09-13 1982-09-13 Electrohydraulic valve

Publications (2)

Publication Number Publication Date
EP0103250A1 true EP0103250A1 (fr) 1984-03-21
EP0103250B1 EP0103250B1 (fr) 1986-07-30

Family

ID=23651508

Family Applications (1)

Application Number Title Priority Date Filing Date
EP83108731A Expired EP0103250B1 (fr) 1982-09-13 1983-09-05 Soupape de contrôle pour contrôle hydraulique

Country Status (9)

Country Link
US (1) US4461314A (fr)
EP (1) EP0103250B1 (fr)
JP (1) JPS5973605A (fr)
AT (1) ATE21147T1 (fr)
AU (1) AU552257B2 (fr)
CA (1) CA1195206A (fr)
DE (1) DE3364958D1 (fr)
DK (1) DK415983A (fr)
ES (1) ES8406656A1 (fr)

Cited By (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2563585A1 (fr) * 1984-04-28 1985-10-31 Bosch Gmbh Robert Distributeur, notamment distributeur hydraulique pour verin a simple effet
GB2218783A (en) * 1988-05-17 1989-11-22 Teves Gmbh Alfred Hydraulic unit
EP0618372A3 (fr) * 1993-03-18 1995-03-01 Bosch Gmbh Robert Dispositif hydraulique de commande avec au moins un clapet anti-retour piloté.
WO1996020348A1 (fr) * 1994-12-23 1996-07-04 Robert Bosch Gmbh Commande hydraulique de structure monobloc pour elever et abaisser une charge, avec au moins deux elements distributeurs proportionnels a commande electromagnetique
US7913714B2 (en) 2007-08-30 2011-03-29 Perlick Corporation Check valve and shut-off reset device for liquid delivery systems
US8869824B2 (en) 2007-08-30 2014-10-28 Perlick Corporation Check valve and shut-off reset device for liquid delivery systems

Families Citing this family (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4506700A (en) * 1983-10-07 1985-03-26 Deere & Company Poppet valve with float function
DE3446134A1 (de) * 1984-12-18 1986-06-26 G. Düsterloh GmbH, 4322 Sprockhövel Reversierbare hydraulische maschine
US5349818A (en) * 1993-08-11 1994-09-27 Teleflex (Canada) Limited Low deadband marine hydraulic steering system
US5481871A (en) * 1995-03-02 1996-01-09 Teleflex (Canada) Ltd. Hydraulic steering system with spool pressure equalization
JP3778634B2 (ja) * 1996-11-22 2006-05-24 Ｓｍｃ株式会社 パイロットチェック弁付スピードコントローラ
DE29810860U1 (de) * 1998-06-17 1998-08-13 Heilmeier & Weinlein Fabrik für Oel-Hydraulik GmbH & Co KG, 81673 München Hydraulische Steuervorrichtung
US6095187A (en) * 1998-11-05 2000-08-01 Interface Devices, Inc. Solenoid-actuated zero-leakage fail-safe three-position poppet-style four-way hydraulic directional control valve
US6871574B2 (en) * 2003-05-28 2005-03-29 Husco International, Inc. Hydraulic control valve assembly having dual directional spool valves with pilot operated check valves
FR2933471B1 (fr) * 2008-07-03 2013-02-15 Vianney Rabhi Vanne electro-hydraulique a levee de bille pour centrale hydraulique de moteur a taux de compression variable
US9068322B2 (en) 2010-05-18 2015-06-30 Volvo Construction Equipment Ab Double check valve for construction equipment

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE1207749B (de) * 1961-04-28 1965-12-23 Istag A G Suhr Hydrostatisches Getriebe
US3587630A (en) * 1969-05-02 1971-06-28 Deere & Co Pressure-compensated flow control valve
EP0025107A1 (fr) * 1979-08-30 1981-03-18 Caterpillar Tractor Co. Clapet de blocage avec piston à longueur variable et système hydraulique pour une machine de travail muni de ce clapet

Family Cites Families (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3274902A (en) * 1965-10-22 1966-09-27 Deere & Co Hydraulic control system
US3587399A (en) * 1969-05-02 1971-06-28 Deere & Co Control valve means for a two-way hydraulic cylinder
US3543647A (en) * 1969-05-02 1970-12-01 Deere & Co Control valve means for a two-way hydraulic cylinder
US3792710A (en) * 1972-05-22 1974-02-19 Safe Way Hydraulics Pump and valve means
US4343153A (en) * 1980-03-21 1982-08-10 Eltra Corporation Anti-supercharge pressure valve

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE1207749B (de) * 1961-04-28 1965-12-23 Istag A G Suhr Hydrostatisches Getriebe
US3587630A (en) * 1969-05-02 1971-06-28 Deere & Co Pressure-compensated flow control valve
EP0025107A1 (fr) * 1979-08-30 1981-03-18 Caterpillar Tractor Co. Clapet de blocage avec piston à longueur variable et système hydraulique pour une machine de travail muni de ce clapet

Cited By (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2563585A1 (fr) * 1984-04-28 1985-10-31 Bosch Gmbh Robert Distributeur, notamment distributeur hydraulique pour verin a simple effet
GB2218783A (en) * 1988-05-17 1989-11-22 Teves Gmbh Alfred Hydraulic unit
GB2218783B (en) * 1988-05-17 1992-02-26 Teves Gmbh Alfred Hydraulic unit
EP0618372A3 (fr) * 1993-03-18 1995-03-01 Bosch Gmbh Robert Dispositif hydraulique de commande avec au moins un clapet anti-retour piloté.
WO1996020348A1 (fr) * 1994-12-23 1996-07-04 Robert Bosch Gmbh Commande hydraulique de structure monobloc pour elever et abaisser une charge, avec au moins deux elements distributeurs proportionnels a commande electromagnetique
US7913714B2 (en) 2007-08-30 2011-03-29 Perlick Corporation Check valve and shut-off reset device for liquid delivery systems
US8869824B2 (en) 2007-08-30 2014-10-28 Perlick Corporation Check valve and shut-off reset device for liquid delivery systems

Also Published As

Publication number Publication date
AU552257B2 (en) 1986-05-22
ATE21147T1 (de) 1986-08-15
DK415983A (da) 1984-03-14
ES525530A0 (es) 1984-07-01
JPS5973605A (ja) 1984-04-25
ES8406656A1 (es) 1984-07-01
AU1802483A (en) 1984-03-22
DE3364958D1 (en) 1986-09-04
CA1195206A (fr) 1985-10-15
US4461314A (en) 1984-07-24
EP0103250B1 (fr) 1986-07-30
DK415983D0 (da) 1983-09-13

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