US3556154A - Electrohydraulic control arrangement - Google Patents

Electrohydraulic control arrangement Download PDF

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Publication number
US3556154A
US3556154A US3556154DA US3556154A US 3556154 A US3556154 A US 3556154A US 3556154D A US3556154D A US 3556154DA US 3556154 A US3556154 A US 3556154A
Authority
US
United States
Prior art keywords
valve
chamber
slider
spool
piston
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
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English (en)
Inventor
Manfred Kramer
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Robert Bosch GmbH
Original Assignee
Robert Bosch GmbH
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 Robert Bosch GmbH filed Critical Robert Bosch GmbH
Application granted granted Critical
Publication of US3556154A publication Critical patent/US3556154A/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
    • F15B13/042—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor operated by fluid pressure
    • F15B13/043—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor operated by fluid pressure with electrically-controlled pilot 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
    • Y10T137/8593—Systems
    • Y10T137/86493—Multi-way valve unit
    • Y10T137/86574—Supply and exhaust
    • Y10T137/86582—Pilot-actuated
    • Y10T137/86614—Electric

Definitions

  • An electrohydraulic control valve has a slider spool valve body to connect, or disconnect a double-acting hydraulic power device from a source, or a drain, respectively; a spring maintains the spool valve in centered position.
  • the spool valve is further provided with a double-acting control piston having faces of unequal size, slidable in a chamber, and electromagnetic on-off valves interconnect the piston chambers formed by the two sides of the double faced piston, with the and drain of the hydraulic pressure fluid, respectively, to shift the position of the control piston and hence of the slider.
  • the power device When the spool slider is in a centered, neutral position, the power device is separated from the source of pressure fluid. Shifting the spool slider laterallyconnects the power device with a source of hydraulic pressure fluid,,or a drain, respectively.
  • the position of the spool-typeslider itself is controlled by hydraulic pressure fluid which is admitted to opposite sides of a double-acting piston by opening or closing of electromagnetic valves.
  • the control slider is provided with a differential piston having a larger anda smaller acting surface, on opposite sides.
  • the piston is slidable in a chamber, which is subdivided into two parts by the piston.
  • the smaller chamber is connected to a pressure source and further over an on-off electromagnetically operated valve with the chamber associated with the larger surface of the piston.
  • a second on-off electromagnetically operated valve connects the chamber to the return, or drain line of the hydraulic fluid.
  • the control arrangement can readily be made fail-safe with respect to electric power supply, andto accommodate various design requirements.
  • the arrangement canbe designed so that the spool slider will assume its neutral position upon interruption of electrical current, thus blocking the utilization device hydraulically; alternatively, the control slider can be held by the electromagnetic valves in its previous commanded position, thus maintaining the speed of 'theutilization device at a constant level.
  • FIGJ is a cross-sectional view through a hydraulic control arrangement, partly schematicall indicating a first position of the pilot valve
  • FIG. 2 illustrates, schematically, a second position of the pilot valves, moving the spool slider in one direction
  • FIG. 3 is a third position of the pilot valves, hydraulically blocking the spool slider.
  • FIG. 4 is a fourth position of the pilot valves, moving the spool slider in the opposite direction.
  • the electrohydraulic control arrangement comprises a housing 10 having a pressure duct 11 to be connected to a line 13 coming from a pump 12; housing 10 is further formed with a drain or return duct '14, as well as with two ducts 15, 16 connected to a utilization device 17, such as a double-acting piston 17.
  • the housing 10 is formed with a bore 18, in which a spool slider 19 can slide back and forth.
  • Bore 18 is formed with seven enlargements, forming chambers 21, 22, 23, 24, 25, 26 and 27; the central chamber 24 is connected with the inlet pressure duct 11.
  • Chamber 23 and 25, on both sides of inlet chamber 24, connect with ducts 15 and 16 leading to the utilization device 17; the outermost chambers 22 and 26 connect with the returnline I4 and serve as drainage chambers.
  • Control slider 19 is subdivided by a pair of circular grooves 28,29 into three sections 31, 32, 33.
  • the spool slider 19 When the spool slider 19 is in its neutral position, as indicated in FIG. 1, the chambers 22, 23, 24, 25, and 26 are separated from each other.
  • a double-acting centering'device 34 is inserted in one terminal chamber 21, maintaining the spool slider 19 in centered position.
  • the other end of slider 19 extends into a chamber 27, and is provided with a differential piston 36, Differential piston 36 subdivides chamber 27 into a space 37, at the side of differential piston 38 which is the smaller face, and into a chamber 39 at the side of the larger face 41 of the differential piston.
  • the free volume of chamber 37 will be less than the free volume of chamber 39.
  • Chamber 37 is connected by means of a duct 42, having a constriction in the form of a choke 43 therein with the inlet pressure line 11.
  • Chamber 39 is connected over a duct 44, in which an electromagnetically controlled valve 45 is inserted, with the return or drain line 14.
  • Valves 45, 47 are of the type that is open when not energized. Springs 48, 49 respectively, permit adjustment of the operation of the valves. When the magnet is energized, the valve closes. Valves 45, 47 can be energized independently by respectively associated switches 50, 51, v a
  • the electromagnetically operated valves 45,47 are not energized so that the valves are maintained open by their springs.
  • the spool slider 19 is thus maintained in a centered position only by the centering device 34, independent of any hydraulic pressure, and thereby seals the chambers 23, 25 connected to the utilization device from the inlet as well as the drainage ducts l1, 14, by sealing against chamber 24 and return line chambers 22, 26.
  • FIG. 2 Interconnection of chamber 39 with the drainage line 14 over duct 44 is interrupted; pressure fluid will thus pass from supply 11 over constriction 43 into chambers 37' and 39, on both sides of the differential piston 36. Due to the unequal volume of the chambers, and the unequal size of the faces of the piston, the piston 36 and thus the spool slider 19 will move towards the left (with respectto FIG. 1) counter the spring pressure of the centeringdevice 34. Portions 31 and 32 of thespool slider then connect the central inlet chamber 24 with the utilization chamber 25, and further interconnect the return from the utilization device 17 to chamber 23 and then to return chamber 22.
  • Fluid under pressure can thus reach the utilization device, and fluid can be drained from the utilization device, and piston 17 will move towards the left (FIG. 1) with increasing acceleration. If piston 17' has reached a desired speed which is to be maintained, valve 47 is additionally ener gized and the fluid path will be as seen in FIG. 3. Chamber 39 is then isolated by both valves 45 and 47, blocking further movement of spool slider 19, and maintaining the existing position thereof, so that the piston 17' of the utilization device will move towards the left with"'uniform speed.
  • both valves 45 and 47 are deenergized so that they will open. They will thus again assume the position illustrated in FIG. 1, the centering device 34 will quickly center the spool slider 19 in its central, neutral position, and hydraulically blocking piston 17' in its position.
  • valve 47 If it is desired to move the utilization piston 17' towards the right, valve 47 is operated and the fluid path will be as illustrated in FIG. 4. Fluid under pressure will flow from pressure line 11 only into chamber 37. Accelerating movement of piston 17 can be changed to movement at uniform speed as above described.
  • the hydraulic control arrangement according to the present invention thus enables remote control of an utilization piston at uniform speed, at accelerating speed, or at decelerating speed, as well as maintaining the piston in any particular desired position.
  • Fine control arrangements well known in the art, may additionally be used.
  • valves 45, 47 Ordinary commercially available on-off valves, having positively seating movable valve bodies, seating against conical valve seats are suitable for the valves 45, 47. They are simple and provide better sealing with respect to slider-type valves or gate valves. Instead of constriction 43, a fluid flow limiting valve can also be used.
  • the present invention has been described in connection with a double-acting utilization device.
  • the control arrangement of the present invention can also be used with single-acting utilization element.
  • the control arrangement as illustrated blocks if the electrical current should be interrupted, so that a fail-safe arrangement is provided.
  • the electrically operated valves can be of the type which is normally closed and opens only when energized so that, upon failure of electrical power, the fluid flow arrangement will be as illustrated in H0. 3.
  • Electrohydraulic control valve for a hydraulic power device (17, 17' said valve having:
  • valve housing formed with a slider bore (18) and a control piston chamber (37, 39); 2. a spool slider l9) slidable in said bore;
  • a differential control piston (36) having a larger (41) and a smaller (38) acting surface connected to said spool slider, said piston being slidable in said control piston chamber (37, 39) and subdividing said chamber into a first, smaller chamber (37) and a second, larger chamber (39);
  • valve means (45) and a second duct (44) connected to and controlling flow from said secondlarger chamber (39) to the return line whereby, when both electromagnetic valve means (45, 47) are closed, the second, larger chamber is isolated from the supply line (11) by the closed first valve means (47) and from the return line (14) by the closed second valve means (45) and the differential control piston (36) will remain in the position commanded by said hydraulic fluid admitted to the respective chambers before closing of both said valve means.
  • said centering means (34) and said differential piston are connected to said spool slider (19) at opposite ends thereof.
  • Valve according to claim 1 wherein said electromagnetic valves are normally open and close when electrically enerized.
  • Valve according to claim 1 including a constriction (43) in the first duct (42) connecting said smaller chamber (37) to said pressure line (11),

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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)
  • Servomotors (AREA)
  • Fluid-Driven Valves (AREA)
US3556154D 1968-04-24 1969-01-30 Electrohydraulic control arrangement Expired - Lifetime US3556154A (en)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE1750358A DE1750358B2 (de) 1968-04-24 1968-04-24 Elektrohydraulische Steuereinrichtung

Publications (1)

Publication Number Publication Date
US3556154A true US3556154A (en) 1971-01-19

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Family Applications (1)

Application Number Title Priority Date Filing Date
US3556154D Expired - Lifetime US3556154A (en) 1968-04-24 1969-01-30 Electrohydraulic control arrangement

Country Status (4)

Country Link
US (1) US3556154A (de)
DE (1) DE1750358B2 (de)
FR (1) FR1597888A (de)
GB (1) GB1231935A (de)

Cited By (17)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3987702A (en) * 1970-08-21 1976-10-26 Messerschmitt-Bolkow-Blohm Gmbh Method and device for electrohydraulic control of a hydraulic actuator
US4066102A (en) * 1975-04-18 1978-01-03 Danfoss A/S Hydraulic regulator
US4072169A (en) * 1975-07-29 1978-02-07 Robert Bosch Gmbh Hydraulic control system
US4215723A (en) * 1976-06-11 1980-08-05 Hitachi, Ltd. Fluid pressure servo valve assembly
US4220074A (en) * 1977-05-25 1980-09-02 Vapor Corporation Switching valve
US4282901A (en) * 1978-07-18 1981-08-11 Diesel Kiki Co., Ltd. Proportional control type remote-control direction switching control valve device
US4303003A (en) * 1977-05-25 1981-12-01 Vapor Corporation Switching valve
US4566530A (en) * 1983-05-11 1986-01-28 United Aircraft Products, Inc. Pressure operated shuttle valve
US4638720A (en) * 1980-12-01 1987-01-27 Deere & Company Electro-hydraulic control system
US4770200A (en) * 1985-10-28 1988-09-13 Johnson Service Company Pneumatic interface apparatus
US4804009A (en) * 1982-06-08 1989-02-14 Johnson Service Company Pneumatic interface apparatus for control of process systems
US4934143A (en) * 1987-04-29 1990-06-19 Vickers, Incorporated Electrohydraulic fluid control system for variable displacement pump
US5046397A (en) * 1987-04-29 1991-09-10 Vickers, Incorporated Electrohydraulic and hydromechanical valve system for dual-piston stroke controller
US5633593A (en) * 1991-05-22 1997-05-27 Wolff; George D. Apparatus for sensing proximity of a moving target
US20070181196A1 (en) * 2006-02-07 2007-08-09 Sturman Digital Systems, Llc Spool valve
US20150020905A1 (en) * 2013-07-19 2015-01-22 Dresser, Inc. Valve assembly having dual functionality for directional control of a piston on a fluid actuated device
US9546737B1 (en) * 2015-09-09 2017-01-17 James Wang Solenoid valve

Families Citing this family (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE2112813C3 (de) * 1971-03-17 1981-04-30 Robert Bosch Gmbh, 7000 Stuttgart Elektrohydraulische Steuereinrichtung
JPS5630883Y2 (de) * 1973-05-09 1981-07-23
US4199942A (en) * 1978-09-28 1980-04-29 Eaton Corporation Load sensing control for hydraulic system
IT1119444B (it) * 1979-10-30 1986-03-10 Fiat Ricerche Distributore idraulico
EP0054619A1 (de) * 1980-12-22 1982-06-30 GebràœDer Sulzer Aktiengesellschaft Servomotor mit Differentialkolben
DE3246738C2 (de) * 1982-09-28 1987-02-05 Dr. H. Tiefenbach Gmbh & Co, 4300 Essen Mit Eigenmedium gesteuertes Hydraulikventil mit einstellbarem Durchlaßquerschnitt
DE3817122A1 (de) * 1988-05-19 1989-11-30 Herion Werke Kg Sicherheitsventil

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2898936A (en) * 1957-04-17 1959-08-11 Int Basic Economy Corp Pilot actuated fluid control valve
US2916051A (en) * 1958-03-12 1959-12-08 Elizabeth H Taylor Fluid pressure operated valve
US2993510A (en) * 1956-11-28 1961-07-25 Int Basic Economy Corp Fluid control valve
US3129645A (en) * 1962-05-02 1964-04-21 Double A Prod Co Electrically modulated fluid valve
US3434390A (en) * 1966-04-25 1969-03-25 Bosch Arma Corp Valve control apparatus

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2993510A (en) * 1956-11-28 1961-07-25 Int Basic Economy Corp Fluid control valve
US2898936A (en) * 1957-04-17 1959-08-11 Int Basic Economy Corp Pilot actuated fluid control valve
US2916051A (en) * 1958-03-12 1959-12-08 Elizabeth H Taylor Fluid pressure operated valve
US3129645A (en) * 1962-05-02 1964-04-21 Double A Prod Co Electrically modulated fluid valve
US3434390A (en) * 1966-04-25 1969-03-25 Bosch Arma Corp Valve control apparatus

Cited By (21)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3987702A (en) * 1970-08-21 1976-10-26 Messerschmitt-Bolkow-Blohm Gmbh Method and device for electrohydraulic control of a hydraulic actuator
US4066102A (en) * 1975-04-18 1978-01-03 Danfoss A/S Hydraulic regulator
US4072169A (en) * 1975-07-29 1978-02-07 Robert Bosch Gmbh Hydraulic control system
US4215723A (en) * 1976-06-11 1980-08-05 Hitachi, Ltd. Fluid pressure servo valve assembly
US4220074A (en) * 1977-05-25 1980-09-02 Vapor Corporation Switching valve
US4303003A (en) * 1977-05-25 1981-12-01 Vapor Corporation Switching valve
US4282901A (en) * 1978-07-18 1981-08-11 Diesel Kiki Co., Ltd. Proportional control type remote-control direction switching control valve device
US4638720A (en) * 1980-12-01 1987-01-27 Deere & Company Electro-hydraulic control system
US4804009A (en) * 1982-06-08 1989-02-14 Johnson Service Company Pneumatic interface apparatus for control of process systems
US4566530A (en) * 1983-05-11 1986-01-28 United Aircraft Products, Inc. Pressure operated shuttle valve
US4770200A (en) * 1985-10-28 1988-09-13 Johnson Service Company Pneumatic interface apparatus
US4934143A (en) * 1987-04-29 1990-06-19 Vickers, Incorporated Electrohydraulic fluid control system for variable displacement pump
US5046397A (en) * 1987-04-29 1991-09-10 Vickers, Incorporated Electrohydraulic and hydromechanical valve system for dual-piston stroke controller
US5633593A (en) * 1991-05-22 1997-05-27 Wolff; George D. Apparatus for sensing proximity of a moving target
US20070181196A1 (en) * 2006-02-07 2007-08-09 Sturman Digital Systems, Llc Spool valve
US20100200090A1 (en) * 2006-02-07 2010-08-12 Sturman Digital Systems, Llc Spool Valve
US7775240B2 (en) * 2006-02-07 2010-08-17 Sturman Digital Systems, Llc Spool valve
US7958909B2 (en) 2006-02-07 2011-06-14 Sturman Digital Systems, Llc Spool valve
US20150020905A1 (en) * 2013-07-19 2015-01-22 Dresser, Inc. Valve assembly having dual functionality for directional control of a piston on a fluid actuated device
US10202987B2 (en) * 2013-07-19 2019-02-12 Dresser, Llc Valve assembly having dual functionality for directional control of a piston on a fluid actuated device
US9546737B1 (en) * 2015-09-09 2017-01-17 James Wang Solenoid valve

Also Published As

Publication number Publication date
DE1750358A1 (de) 1971-02-11
DE1750358B2 (de) 1974-09-19
FR1597888A (de) 1970-06-29
GB1231935A (de) 1971-05-12
DE1750358C3 (de) 1975-04-30

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