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US3812675A - Hydraulic flow control valve assemblies - Google Patents

Hydraulic flow control valve assemblies Download PDF

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US3812675A
US3812675A US00257786A US25778672A US3812675A US 3812675 A US3812675 A US 3812675A US 00257786 A US00257786 A US 00257786A US 25778672 A US25778672 A US 25778672A US 3812675 A US3812675 A US 3812675A
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valve
pressure
outlet passage
passage
inlet passage
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US00257786A
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R Cochrane
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Girling Ltd
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Girling Ltd
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    • 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
    • F15B1/00—Installations or systems with accumulators; Supply reservoir or sump assemblies
    • F15B1/02—Installations or systems with accumulators
    • F15B1/027—Installations or systems with accumulators having accumulator charging 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
    • Y10T137/2559—Self-controlled branched flow systems
    • Y10T137/2562—Dividing and recombining
    • 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

Definitions

  • ABSTRACT In an hydraulic flow control valve assembly a valve is normally urged into a closed position by a return spring, and movement of the valve into an open position in opposition to the force in the return spring is effected by a differential piston working in a stepped bore. The end of the piston which is of smaller area acts on the second valve, and the end of greater area is exposed to the pressure in an inlet passage. The differential piston is operative to open the valve when the force applied to the piston by the pressure in a first outlet passage overcomes at least the force of the return spring.
  • This invention relates to improvements in hydraulic flow control valve assemblies of the kind comprising a housing having an inlet passage for connection to a source of hydraulic fluid under pressure, a first outlet passage for connection to pressure storage means, a first normally closed one-way valve for controlling communication between the inlet passage and the first outlet passage, the first one-way valve being adapted to open when the pressure in the'inlet passage exceeds a first predetermined value and being adapted to close when that pressure exceeds a second predetermined value'greater than the first, a second outlet passage for connection to pressure operable means, and a second normally closed valve for controlling communication between the inlet passage and the second outlet passage and adapted to open when the pressure in the second outlet passage attains at least said second predetermined value.
  • the second valve in an hydraulic flow control valve of the kind set forth the second valve is normally urged into its closed position by a return spring, and movement of the second valve into an open position in opposition to the force in the return spring is effected by a differential piston working in a stepped bore of which the end of smaller area acts on the second valve and the end of greater area-is exposed to the pressure in the inlet passage, the differential piston FIG. 1 is a longitudinal section through an hydraulic flow control valve on the line l-l of FIG.'2; and
  • FIG. 2 is a section on the line 2-2 of FIG. 1.
  • a housing 1 is provided with a longitudinal stepped bore comprising an inner portion 2 of smallest diameter, a intermediate portion 3 of greater diameter, and an outer portion 4 of greatest diameter.
  • a radial inlet passage 5 communicates with the outer bore portion 4, and a passage 6 in the housing parallel with the stepped bore leads from the radial passage 5 to a chamber 7 of enlarged diameter which is connected to the bore portion 2 through a radial passage 8.
  • the bore portion 2 is also connected to a first radial outlet passage 9.
  • the housing 1 is also provided with a further longitudinal bore 10 which defines a second outlet'passage communicating at its innermost end with being operative to open the second valve when the force applied to the differential piston by the pressure in the first outlet passage overcomes at least the force of the return spring.
  • the differential piston When pressure is present in the second outlet passage, that pressure acts on the end of the differential piston which is of smaller area.
  • the differential piston is operative to'open the second valve only when the force applied to it by the pressure in the first outlet passage is sufficient to overcome the combined force of the return spring and the force applied thereto from the pressure in the second outlet passage.
  • the differential piston moves in a direction to open the second valve the inlet passage is placed in communication with the second outlet passage.
  • the pressure operable means is adapted to be actuated by a supply of hydraulic fluid under pressure from source of hydraulic fluid under pressure.
  • the hydraulic flow control valve assembly may be incorporated into a vehicle hydraulic braking system in which fluid under pressure for operating the braking system is stored in an hydraulic accumulator connected to the first outlet passage.
  • a reservoir for supplying hydraulic fluid to the source of hydraulic fluid, conveniently a high pressure pump, is connected to the second outlet passage, and a connection for a power steering line of the vehicle is interposed between the second outlet passage and the reservoir.
  • the valve 11 comprises an annular valve seating 12 housed in a counterbored recess 13 at an adjacent end of the passage 6, and a valve member 14 for engagement with the seating 12 and guided for movement relative to the seating within a guide 15 provided with a plurality of radial outlet ports 16.
  • the valve 17 comprises an annular valve seating member 18 having an axially extending flange 19 which carries a radial seal 20 for sealing engagement with the wall of the bore portion 4.
  • the free end of the flange 19 is clamped against a shoulder 21 at a step in the change in diameter between the bore portions 3 and 4 by means of a sleeve nut 22 screwed into the open end of the bore portion 4.
  • the inner free end of the sleeve nut 22 is provided with at least a pair of radial openings 23 through which theinlet passage 5 communicates with theinterior of the sleeve nut 22.
  • a valve member 24 comprising a ball for engagement with a seating 25 surrounding a central opening in the seating member 18 is. located in a recess 27 in the inner endof a push-rod 28. Normally the'ball 24 is urged into engagement with the seating 25 by a helical spring 29
  • An annular plate 31 is clamped against a shoulder 32 at a step at the change in diameter between the bore portions 2 and 3 by means of an axially extending radially apertured sleeve 33 which engages between the seating member 18 and an annular seal 34 engaging with the plate 31.
  • the end of the differential piston 36 which is of greater diameter is exposed to hydraulic pressure in the radial passage 8.
  • the portion of the differential piston 36 is of smaller diameter projects through the plate 31 and the seal 34 and is adapted to engage at its free end with theball 24 to move the ball 24 away from its seating 25 when the pressure to which the end of the piston 36 of greater diameter is exposed is sufficient to apply to the piston 36 a force greater than that applied thereto in the opposite closing direction comprising the force in the spring 29 and a force from the pressure in the outlet passage 10 acting on the portion of the differential piston which is of smaller diameter and which engages with the ball 24.
  • the control valve assembly is adapted to be incorporated in a vehicle power operated hydraulic braking system.
  • the inlet passage 5 is connected to a source of hydraulic fluid under pressure, for example a high pressure pump 37 driven by the prime mover of the vehicle or another motor and the first outlet passage 9 is connected to an hydraulic accumulator 38 which is screwed into the outer end of an enlarged bore continuous with the passage 9.
  • the second outlet passage 10 is connected to a connection for a power steering line of the vehicle interposed between the second outlet passage 10 and a reservoir for fluid.
  • the pressure of fluid in the hydraulic accumulator 38 and in the first outlet passage 9 acts on the end of the differential piston 36 which is of greater diameter and applies to the piston 36 a force greater than that of the helical spring 29 and the pressure in the outlet passage l0 acting on the portion of the piston-36 which is'of smaller diameter;
  • the differential piston 36 moves to the right in FIG. 1 of the drawings towards the end of the stepped bore in which it works, thereby opening the second valve 17.
  • Fluid under pressure from the pump is then supplied'to the second outlet 10 through the seating and the apertures in the sleeve 34 with the result that fluid under pressure is supplied to the power steering line.
  • fluid in the inlet passage 5 actson the end of the differential piston 36 which is of smaller diameter to augment the force already applied to the valve memberr24 in a closing direction from the helical spring 29 and the pressure in the outlet passage 10.
  • the relative diameters of opposite ends of the differential piston 36 are therefore chosen to ensure that, under such conditions, the force applied to the ball 24 by the differential piston 36 is sufficient to hold it out of engagement with its seating 25.
  • a first normally closed one-way valve for controlling communication between said inlet passage and said first outlet passage, said first one-way valve being "adapted to open when pressure in said inlet passage exceeds a first predetermined value and being adapted to close when said pressure exceeds a second predeterminedvalue greater than the first, and a second normally closed valve for controlling communication between said inlet passage and said second outlet passage and adapted to open when pressure in the second outlet passage attains at least said second predetermined value, a spring for urging said second valve into a closed position, and a differential piston working in a stepped bore and having a first end of greater area exposed to pressure in said inlet passage and a second end of smaller area exposed to pressure in said second outlet passage and adapted to open said second valve when the force applied to said differential piston by pressure in said first outlet passage overcomes at least the force of said return spring.
  • An hydraulic system for a vehicle comprising a housing having an inlet passage for connection to a source of hydraulic fluid under pressure, a first outlet passage for connection to pressure storage means, and a second outlet'passage for connection to pressure operable means, a first normally closed one-way valve for controlling communication between said inlet passage and said first outlet passage, said first one-way valve mined value, a spring for urging said second valve into a closed position, and a differential piston working in a stepped bore and having a first end of greater area and exposed to pressure in said inlet passage and a second end of smaller area adapted to open said second valve when the force applied to said differential piston by pressure in said first outlet passage overcomes at least the force of said return spring, wherein a source of highpressure fluid is connected to said inlet passage, an hydraulic accumulator for operating a braking system is connected to said first outlet passage, and power voir from which the source receives fluid.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Safety Valves (AREA)
  • Hydraulic Control Valves For Brake Systems (AREA)
  • Fluid-Pressure Circuits (AREA)
  • Check Valves (AREA)
  • Multiple-Way Valves (AREA)
  • Supply Devices, Intensifiers, Converters, And Telemotors (AREA)
  • Valves And Accessory Devices For Braking Systems (AREA)

Abstract

In an hydraulic flow control valve assembly a valve is normally urged into a closed position by a return spring, and movement of the valve into an open position in opposition to the force in the return spring is effected by a differential piston working in a stepped bore. The end of the piston which is of smaller area acts on the second valve, and the end of greater area is exposed to the pressure in an inlet passage. The differential piston is operative to open the valve when the force applied to the piston by the pressure in a first outlet passage overcomes at least the force of the return spring.

Description

United States Patent Cochrane [451 May 28, 1974 HYDRAULIC FLOW CONTROL VALVE ASSEMBLIES Inventor: Robin Adam Cochrane, l-laseley Knob, England Assignee: Girling Limited, Birmingham,
England Filed: May 30, 1972 Appl. No.: 257,786
Foreign Application Priority Data June 1, 1971 Great Britain 18236/71 US. Cl 60/413, 137/110, 137/494 Int. Cl. Fl5b 1/02 Field of Search 137/110, 494, 568, 599.1;
References Cited UNITED STATES PATENTS 6/1953 Jelinck 60/415 X 3,049,14l 8/1962 Beatty ct al 137/494 Primary Examiner-Edgar W. Geoghegan Attorney, Agent, or FirmScrivener Parker Scrivener & Clarke {57] ABSTRACT In an hydraulic flow control valve assembly a valve is normally urged into a closed position by a return spring, and movement of the valve into an open position in opposition to the force in the return spring is effected by a differential piston working in a stepped bore. The end of the piston which is of smaller area acts on the second valve, and the end of greater area is exposed to the pressure in an inlet passage. The differential piston is operative to open the valve when the force applied to the piston by the pressure in a first outlet passage overcomes at least the force of the return spring.
6 Claims, 2 Drawing Figures HYDRAULIC FLOW CONTROL VALVE ASSEMBLIES SPECIFIC DESCRIPTION This invention relates to improvements in hydraulic flow control valve assemblies of the kind comprising a housing having an inlet passage for connection to a source of hydraulic fluid under pressure, a first outlet passage for connection to pressure storage means, a first normally closed one-way valve for controlling communication between the inlet passage and the first outlet passage, the first one-way valve being adapted to open when the pressure in the'inlet passage exceeds a first predetermined value and being adapted to close when that pressure exceeds a second predetermined value'greater than the first, a second outlet passage for connection to pressure operable means, and a second normally closed valve for controlling communication between the inlet passage and the second outlet passage and adapted to open when the pressure in the second outlet passage attains at least said second predetermined value.
According to our invention in an hydraulic flow control valve of the kind set forth the second valve is normally urged into its closed position by a return spring, and movement of the second valve into an open position in opposition to the force in the return spring is effected by a differential piston working in a stepped bore of which the end of smaller area acts on the second valve and the end of greater area-is exposed to the pressure in the inlet passage, the differential piston FIG. 1 is a longitudinal section through an hydraulic flow control valve on the line l-l of FIG.'2; and
FIG. 2 is a section on the line 2-2 of FIG. 1.
In the control valve assembly illustrated in the drawings a housing 1 is provided with a longitudinal stepped bore comprising an inner portion 2 of smallest diameter, a intermediate portion 3 of greater diameter, and an outer portion 4 of greatest diameter.
A radial inlet passage 5 communicates with the outer bore portion 4, and a passage 6 in the housing parallel with the stepped bore leads from the radial passage 5 to a chamber 7 of enlarged diameter which is connected to the bore portion 2 through a radial passage 8. The bore portion 2 is also connected to a first radial outlet passage 9. The housing 1 is also provided with a further longitudinal bore 10 which defines a second outlet'passage communicating at its innermost end with being operative to open the second valve when the force applied to the differential piston by the pressure in the first outlet passage overcomes at least the force of the return spring.
When pressure is present in the second outlet passage, that pressure acts on the end of the differential piston which is of smaller area. Thus the differential piston is operative to'open the second valve only when the force applied to it by the pressure in the first outlet passage is sufficient to overcome the combined force of the return spring and the force applied thereto from the pressure in the second outlet passage. When the differential piston moves in a direction to open the second valve the inlet passage is placed in communication with the second outlet passage. As a consequence the pressure operable means is adapted to be actuated by a supply of hydraulic fluid under pressure from source of hydraulic fluid under pressure.
Conveniently the hydraulic flow control valve assembly may be incorporated into a vehicle hydraulic braking system in which fluid under pressure for operating the braking system is stored in an hydraulic accumulator connected to the first outlet passage. A reservoir for supplying hydraulic fluid to the source of hydraulic fluid, conveniently a high pressure pump, is connected to the second outlet passage, and a connection for a power steering line of the vehicle is interposed between the second outlet passage and the reservoir.
Thus, after the hydraulic accumulator is fully charged. at which pressure the first valve closes, fluid under pressure from the source is supplied through the second valve to the power steering line.
One embodiment of our invention is illustrated in the accompanying drawings in which:
the bore portion 4 of greater diameter.
Communication between the inlet passage 5 and the first outlet passage 9 is controlled by a first valve 11 which is located in the chamber 7. The valve 11 comprises an annular valve seating 12 housed in a counterbored recess 13 at an adjacent end of the passage 6, and a valve member 14 for engagement with the seating 12 and guided for movement relative to the seating within a guide 15 provided with a plurality of radial outlet ports 16.
Communication between theinlet passage 5 and the second outlet passage 10 is controlled by a second valve 17. The valve 17 comprises an annular valve seating member 18 having an axially extending flange 19 which carries a radial seal 20 for sealing engagement with the wall of the bore portion 4. The free end of the flange 19 is clamped against a shoulder 21 at a step in the change in diameter between the bore portions 3 and 4 by means of a sleeve nut 22 screwed into the open end of the bore portion 4. The inner free end of the sleeve nut 22 is provided with at least a pair of radial openings 23 through which theinlet passage 5 communicates with theinterior of the sleeve nut 22.
A valve member 24 comprising a ball for engagement with a seating 25 surrounding a central opening in the seating member 18 is. located in a recess 27 in the inner endof a push-rod 28. Normally the'ball 24 is urged into engagement with the seating 25 by a helical spring 29 An annular plate 31 is clamped against a shoulder 32 at a step at the change in diameter between the bore portions 2 and 3 by means of an axially extending radially apertured sleeve 33 which engages between the seating member 18 and an annular seal 34 engaging with the plate 31. The bore portion 2 and the wall of a central opening 35in the plate 31, which is of a diameter smaller than that of the bore portion 2, together define a stepped bore in which works a differential piston 36. The end of the differential piston 36 which is of greater diameter is exposed to hydraulic pressure in the radial passage 8. The portion of the differential piston 36 is of smaller diameter projects through the plate 31 and the seal 34 and is adapted to engage at its free end with theball 24 to move the ball 24 away from its seating 25 when the pressure to which the end of the piston 36 of greater diameter is exposed is sufficient to apply to the piston 36 a force greater than that applied thereto in the opposite closing direction comprising the force in the spring 29 and a force from the pressure in the outlet passage 10 acting on the portion of the differential piston which is of smaller diameter and which engages with the ball 24. i
The control valve assembly is adapted to be incorporated in a vehicle power operated hydraulic braking system. In such an installation the inlet passage 5 is connected to a source of hydraulic fluid under pressure, for example a high pressure pump 37 driven by the prime mover of the vehicle or another motor and the first outlet passage 9 is connected to an hydraulic accumulator 38 which is screwed into the outer end of an enlarged bore continuous with the passage 9. The second outlet passage 10 is connected to a connection for a power steering line of the vehicle interposed between the second outlet passage 10 and a reservoir for fluid.
I Normally the second valve 17 is closed and the first valve 1 1 opens when subjected to a first predetermined pressure in .the inlet passage 5. Thus, fluid from the pump is supplied through the passages 5, 6, 8 and 9 to the hydraulic accumulator 38. When the hydraulic accumulator, 38 is fully charged, at a second predetermined pressure, the'first valve 11 closes automatically and cuts-off communication between the inlet passage 5 and the first outlet passage 9.
The pressure of fluid in the hydraulic accumulator 38 and in the first outlet passage 9 acts on the end of the differential piston 36 which is of greater diameter and applies to the piston 36 a force greater than that of the helical spring 29 and the pressure in the outlet passage l0 acting on the portion of the piston-36 which is'of smaller diameter; Thus the differential piston 36 moves to the right in FIG. 1 of the drawings towards the end of the stepped bore in which it works, thereby opening the second valve 17. Fluid under pressure from the pump is then supplied'to the second outlet 10 through the seating and the apertures in the sleeve 34 with the result that fluid under pressure is supplied to the power steering line.
When'the second valve .17 is opened, fluid in the inlet passage 5 actson the end of the differential piston 36 which is of smaller diameter to augment the force already applied to the valve memberr24 in a closing direction from the helical spring 29 and the pressure in the outlet passage 10. The relative diameters of opposite ends of the differential piston 36 are therefore chosen to ensure that, under such conditions, the force applied to the ball 24 by the differential piston 36 is sufficient to hold it out of engagement with its seating 25.
Should the pressure in the hydraulic accumulator 38 which is of greater area is reduced and the second valve 17 closes to cut-off communication between the inlet passage 5 and the second outlet passage 10. Thereafter is at all times vented to atmosphere through a passage 39. This ensures that there is no pressure trapped between the seal and a seal 40 in the piston 36 during assembly, and that a vacuum is not produced during operation. r
I claim:
erable means, a first normally closed one-way valve for controlling communication between said inlet passage and said first outlet passage, said first one-way valve being "adapted to open when pressure in said inlet passage exceeds a first predetermined value and being adapted to close when said pressure exceeds a second predeterminedvalue greater than the first, and a second normally closed valve for controlling communication between said inlet passage and said second outlet passage and adapted to open when pressure in the second outlet passage attains at least said second predetermined value, a spring for urging said second valve into a closed position, and a differential piston working in a stepped bore and having a first end of greater area exposed to pressure in said inlet passage and a second end of smaller area exposed to pressure in said second outlet passage and adapted to open said second valve when the force applied to said differential piston by pressure in said first outlet passage overcomes at least the force of said return spring. 7
2. A valve assembly as claimed in claim 1, wherein said differential piston is adapted to open said second valve only when the force applied to said second valve by the pressure in said first outlet passage acting on said first end of said differential piston is sufficient to overcome the combined force of said return spring and said force applied to the second valve from the pressure in said second outlet passage acting on said second end of said differential piston. 3. A valveassemblyas claimed in claim 1 wherein-a valve seating is disposed between said inlet passage and said second outlet passage, and said second end of said piston projects through said seating, and said return spring comprises a compression spring for urging said valve member towards said seating, said compression spring acting between said valve member and an abutment in said housing on the side of said seating remote from said stepped bore.
4. A valve assembly as claimed in claim 3, including a push-rod, wherein said valve member is located in a recess in one end of said push-rod, and said compression spring acts between an abutment on said push-rod and said abutment on said housing.
5. An hydraulic system for a vehicle comprising a housing having an inlet passage for connection to a source of hydraulic fluid under pressure, a first outlet passage for connection to pressure storage means, and a second outlet'passage for connection to pressure operable means, a first normally closed one-way valve for controlling communication between said inlet passage and said first outlet passage, said first one-way valve mined value, a spring for urging said second valve into a closed position, and a differential piston working in a stepped bore and having a first end of greater area and exposed to pressure in said inlet passage and a second end of smaller area adapted to open said second valve when the force applied to said differential piston by pressure in said first outlet passage overcomes at least the force of said return spring, wherein a source of highpressure fluid is connected to said inlet passage, an hydraulic accumulator for operating a braking system is connected to said first outlet passage, and power voir from which the source receives fluid.

Claims (6)

1. An hydraulic flow control valve assembly comprising a housing having an inlet passage for connection to a source of hydraulic fluid under pressure, a first outlet passage for connection to pressure storage means and a second outlet passage for connection to pressure operable means, a first normally closed one-way valve for controlling communication between said inlet passage and said first outlet passage, said first one-way valve being adapted to open when pressure in said inlet passage exceeds a first predetermined value and being adapted to close when said pressure exceeds a second predetermined value greater than the first, and a second normally closed valve for controlling communicatIon between said inlet passage and said second outlet passage and adapted to open when pressure in the second outlet passage attains at least said second predetermined value, a spring for urging said second valve into a closed position, and a differential piston working in a stepped bore and having a first end of greater area exposed to pressure in said inlet passage and a second end of smaller area exposed to pressure in said second outlet passage and adapted to open said second valve when the force applied to said differential piston by pressure in said first outlet passage overcomes at least the force of said return spring.
2. A valve assembly as claimed in claim 1, wherein said differential piston is adapted to open said second valve only when the force applied to said second valve by the pressure in said first outlet passage acting on said first end of said differential piston is sufficient to overcome the combined force of said return spring and said force applied to the second valve from the pressure in said second outlet passage acting on said second end of said differential piston.
3. A valve assembly as claimed in claim 1 wherein a valve seating is disposed between said inlet passage and said second outlet passage, and said second end of said piston projects through said seating, and said return spring comprises a compression spring for urging said valve member towards said seating, said compression spring acting between said valve member and an abutment in said housing on the side of said seating remote from said stepped bore.
4. A valve assembly as claimed in claim 3, including a push-rod, wherein said valve member is located in a recess in one end of said push-rod, and said compression spring acts between an abutment on said push-rod and said abutment on said housing.
5. An hydraulic system for a vehicle comprising a housing having an inlet passage for connection to a source of hydraulic fluid under pressure, a first outlet passage for connection to pressure storage means, and a second outlet passage for connection to pressure operable means, a first normally closed one-way valve for controlling communication between said inlet passage and said first outlet passage, said first one-way valve being adapted to open when pressure in said inlet passage exceeds a first predetermined value and being adapted to close when said pressure exceeds a second predetermined value greater than the first, and a second normally closed valve for controlling communication between said inlet passage and said second outlet passage and adapted to open when pressure in the second outlet passage attains at least said second predetermined value, a spring for urging said second valve into a closed position, and a differential piston working in a stepped bore and having a first end of greater area and exposed to pressure in said inlet passage and a second end of smaller area adapted to open said second valve when the force applied to said differential piston by pressure in said first outlet passage overcomes at least the force of said return spring, wherein a source of high pressure fluid is connected to said inlet passage, an hydraulic accumulator for operating a braking system is connected to said first outlet passage, and power steering means is connected to said second outlet passage whereby when said hydraulic accumulator is fully charged said first valve closes and, thereafter, fluid under pressure from said source is supplied through said second valve to said power steering means.
6. An hydraulic system for a vehicle as claimed in claim 5, wherein said power steering means is interposed between said second outlet passage and a reservoir from which the source receives fluid.
US00257786A 1971-06-01 1972-05-30 Hydraulic flow control valve assemblies Expired - Lifetime US3812675A (en)

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DE2802977A1 (en) * 1977-01-26 1978-07-27 Girling Ltd HYDRAULIC SYSTEM
DE2748146A1 (en) * 1977-10-27 1979-05-03 Teves Gmbh Alfred PRESSURE DEPENDENT SWITCHING VALVE
US4471806A (en) * 1982-06-14 1984-09-18 Strock Dennis J Fuel delivery system having thermal contraction compensation
CN104192200A (en) * 2014-08-29 2014-12-10 长城汽车股份有限公司 Steering pressure accumulator, hydraulic power assisted steering system and automobile

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DE2324059C2 (en) * 1973-05-12 1982-10-28 Alfred Teves Gmbh, 6000 Frankfurt Pressure controlled directional valve
DE2404519C2 (en) * 1974-01-31 1986-02-20 Robert Bosch Gmbh, 7000 Stuttgart Hydraulic braking system for a towing vehicle with a trailer
US3968729A (en) * 1974-10-29 1976-07-13 United Technologies Corporation Fluid-operated apparatus exhibiting hysteresis effect
IT1097555B (en) * 1977-07-29 1985-08-31 Fritzmeier Ag HYDRAULIC BRAKING SYSTEM FOR TRAILERS OF ROAD TRAIN TRUCKS
JPS5461788A (en) * 1977-10-21 1979-05-18 Mitsubishi Heavy Ind Ltd Cellular structure of container ship
DE3101906A1 (en) * 1981-01-22 1982-09-02 Alfred Teves Gmbh, 6000 Frankfurt Pressure-relief-valve arrangement for two working circuits

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US2641106A (en) * 1952-01-03 1953-06-09 Cleveland Automatic Machine Co Electrohydraulic system having a safety shutoff valve for its accumulator
US3049141A (en) * 1959-05-18 1962-08-14 Chrysler Corp Accumulator charging mechanism

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Publication number Priority date Publication date Assignee Title
US2641106A (en) * 1952-01-03 1953-06-09 Cleveland Automatic Machine Co Electrohydraulic system having a safety shutoff valve for its accumulator
US3049141A (en) * 1959-05-18 1962-08-14 Chrysler Corp Accumulator charging mechanism

Cited By (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE2802977A1 (en) * 1977-01-26 1978-07-27 Girling Ltd HYDRAULIC SYSTEM
US4173866A (en) * 1977-01-26 1979-11-13 Girling Limited Hydraulic systems
DE2748146A1 (en) * 1977-10-27 1979-05-03 Teves Gmbh Alfred PRESSURE DEPENDENT SWITCHING VALVE
FR2407376A2 (en) * 1977-10-27 1979-05-25 Teves Gmbh Alfred PRESSURE SENSITIVE VALVE
US4471806A (en) * 1982-06-14 1984-09-18 Strock Dennis J Fuel delivery system having thermal contraction compensation
CN104192200A (en) * 2014-08-29 2014-12-10 长城汽车股份有限公司 Steering pressure accumulator, hydraulic power assisted steering system and automobile

Also Published As

Publication number Publication date
ZA723407B (en) 1973-02-28
ES403323A1 (en) 1975-05-01
GB1382593A (en) 1975-02-05
FR2141142A5 (en) 1973-01-19
DE2226610C3 (en) 1978-07-27
DE2226610A1 (en) 1973-01-04
DE2226610B2 (en) 1977-12-08
JPS5241887B1 (en) 1977-10-21
AU4258072A (en) 1973-07-26

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