GB2133120A - Fluid flow control valve assemblies - Google Patents

Fluid flow control valve assemblies Download PDF

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Publication number
GB2133120A
GB2133120A GB08330620A GB8330620A GB2133120A GB 2133120 A GB2133120 A GB 2133120A GB 08330620 A GB08330620 A GB 08330620A GB 8330620 A GB8330620 A GB 8330620A GB 2133120 A GB2133120 A GB 2133120A
Authority
GB
United Kingdom
Prior art keywords
valve member
fluid flow
port
valve
flow control
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
GB08330620A
Other versions
GB8330620D0 (en
GB2133120B (en
Inventor
Desmond Henry James Reynolds
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.)
ZF International UK Ltd
Original Assignee
Lucas Industries Ltd
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 Lucas Industries Ltd filed Critical Lucas Industries Ltd
Publication of GB8330620D0 publication Critical patent/GB8330620D0/en
Publication of GB2133120A publication Critical patent/GB2133120A/en
Application granted granted Critical
Publication of GB2133120B publication Critical patent/GB2133120B/en
Expired legal-status Critical Current

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
    • F16K31/00—Actuating devices; Operating means; Releasing devices
    • F16K31/02—Actuating devices; Operating means; Releasing devices electric; magnetic
    • F16K31/06—Actuating devices; Operating means; Releasing devices electric; magnetic using a magnet, e.g. diaphragm valves, cutting off by means of a liquid
    • F16K31/0644—One-way valve
    • F16K31/0655—Lift valves
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60G—VEHICLE SUSPENSION ARRANGEMENTS
    • B60G17/00—Resilient suspensions having means for adjusting the spring or vibration-damper characteristics, for regulating the distance between a supporting surface and a sprung part of vehicle or for locking suspension during use to meet varying vehicular or surface conditions, e.g. due to speed or load
    • B60G17/02—Spring characteristics, e.g. mechanical springs and mechanical adjusting means
    • B60G17/04—Spring characteristics, e.g. mechanical springs and mechanical adjusting means fluid spring characteristics
    • B60G17/056—Regulating distributors or valves for hydropneumatic systems
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
    • F16K31/00—Actuating devices; Operating means; Releasing devices
    • F16K31/02—Actuating devices; Operating means; Releasing devices electric; magnetic
    • F16K31/06—Actuating devices; Operating means; Releasing devices electric; magnetic using a magnet, e.g. diaphragm valves, cutting off by means of a liquid
    • F16K31/0644—One-way valve
    • F16K31/0651—One-way valve the fluid passing through the solenoid coil
    • 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
    • Y10S—TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10S280/00—Land vehicles
    • Y10S280/01—Load responsive, leveling of vehicle

Description

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GB 2 133 120 A 1
SPECIFICATION
Improvements in fluid flow control valve assemblies
This invention relates to a fluid flow control valve assembly of the kind having a housing with first and second ports, and valve means for controlling fluid flow between the ports, the valve means being movable to close either the first or the second port, or to permit communication between the ports.
In control valve assemblies of the kind set forth it is desirable to have simple construction and operation, and to provide positive closure of the ports by the valve means.
According to our invention, the valve means comprises two relatively movable valve members, a first valve member for controlling fluid flow through the first port, movement of the first valve member being controlled by first biassing means urging the first valve member to close the first port, a valve-operating means for producing a force urging the first valve member to open the first port, and the pressure differential across the first valve member, and a second valve member for controlling fluid flow through the second port, movement of the second valve member being controlled by the first valve member, the pressure differential across the second valve member, and second biassing means urging the second valve member to close the second port.
In this arrangement the biassing means provide positive closure of each port by the respective valve member and the construction and operation of the assembly are simple.
The valve-operating means conveniently comprises a solenoid.
The first and second biassing means preferably comprise first and second springs.
The second valve member preferably works in a bore in the first valve member. The valve members may be connected by a mechanism providing limited relative movement between the valve members, this mechanism may comprises a pin and slot connection.
When the solenoid is de-energised, operation of the valve means depends on the pressure differential and the biassing means. When the pressure differential acts with the first biassing means, the first valve member closes the first port, while the second port is open. When the pressure differential is reversed, it acts against the first biassing means to move the first valve member to open the first port, without closing the second port, to allow communication between the ports.
On energisation of the solenoid the first valve member moves to open the first port, and the position of the second valve member depends on the pressure differential and the second biassing means. When the pressure differential acts with the second biassing means the second port is closed by the second valve member. When the pressure differential is reversed, it acts against the second biassing means to move the second valve member to open the second port, allowing communication between the ports.
The solenoid may be chosen so that energisation of the solenoid produces a force which is unable to move the first valve member against a significant pressure differential.
However, once the first valve member is moved in response to energisation of the solenoid to open the first port, it remains open as long as the solenoid remains energised, regardless of the pressure differential. This may be useful if the assembly is incorporated in a high pressure system, as it reduces the force required to operate the solenoid.
One embodiment of out invention is illustrated in the accompanying drawings of which the single Figure is a longitudinal section through a fluid flow control valve assembly.
The assembly 1 shown in the drawing has a housing 2 with first and second ports 3, 4 for connection into an hydraulic system (not shown). The first port 3 may be connected to a pressure source, and the second port 4 to a slave unit. The assembly 1 also has a valve means 5 controlling flow between the ports 3, 4, and comprising first and second valve members 6, 7 for controlling flow through the respective ports.
The housing 2 has a cylindrical housing portion 8 in which is located a valve-operating means comprising a solenoid winding 9. Two housing end portions 10, 11 of stepped outline are also provided. The first of these, 10, is a non-magnetic material and has a stepped bore 12, part of which forms the first port 3. A seal 13 seals the connection between the first port 3 and the system. The second end portion 11 is of magnetic material, and has a stepped bore 14, an inner portion of which forms the second port 4. At its outer end the bore 14 is screw-threaded for connection to the system. A seal 15 seals between the two end portions 10, 11. A cavity 16 is defined between the two end portions 10, 11, in which is located the valve means 5.
The two valve members 6, 7 are relatively movable. The first valve member 6 has a rubber seat 1 7 to provide a substantially leakproof seal when the first port 3 is closed by the first valve member. Any other suitable elastomeric material may be used for the seat 17. The valve member 6 is urged to close the first port 3 by first biassing means comprising a spring 18, which acts between the end portion 11 and an abutment ring 19 located round the first valve member 6. The abutment ring 19 is attached to the first valve member 6 by a pin 20 which passes through a diametral hole 21 in the valve member 6. The first valve member 6 is of magnetic material so that its is responsive to energisation and de-energisation of the solenoid 9, and is also responsive to the pressure differential across it. In this embodiment the arrangement is such that energisation of the solenoid 9 magnetises the statationary end portion 11 and the valve member 6, which produces a force urging the valve member 6 inwardly in order to open the first port 3, but this
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GB 2 133 120 A 2
force is not sufficient to move the valve member 6 against a significant pressure differential.
The second valve member 7 is adapted to control fluid flow through the second port 4. The 5 second valve member 7 slides in a blind bore 22 at the inner end of the first valve member 6, and is urged towards the second port 4 by second biassing means comprising a spring 23 acting between the first and second valve members. The 10 second valve member 7 is connected to the first valve member 6 by a pin 24 working in a slot 25 in the first valve member, to provide limited relative movement between the valve members. The second valve member 7 is therefore 15 controlled by the first valve member 6 and the spring 23, and also by the pressure differential acting across it. However, the solenoid 9 does not affect the second valve member 7, which is of non-magnetic material.
20 The assembly 1 is arranged so that when the . solenoid 9 is de-energised the position of the valve means 5 depends on the pressure differential and the biassing means. If the pressure acting at the second port 4 is greater 25 than the pressure acting at the first port 3 the assembly is in the position shown, with the pressure differential and the first spring 18 acting to ensure that the first valve member 6 closes the first port 3. The second port 4, however, remains 30 open. If the pressure differential is the other way round, the pressure differential acts against the first spring, and the valve members move into a balanced state in which both the first and second ports 3 and 4 are open, thus permitting fluid flow. 35 Energisation of the solenoid 9 moves the first valve member 6 into abutment with the inner end of the housing end portion 11 and opens the first port 3, provided that there is no significant pressure differential opposing the solenoid force. 40 On the first valve member 6 is in this position it remains there as long as the solenoid is energised, regardless of the pressure differential. The position of the second valve member 7 is then dependent on the pressure differential and 45 the second spring 23. When the pressure acting at the first port 3 is greater than the pressure acting at the second port 4 the pressure differential and the second spring 23 ensure that the second port 4 is closed. When the pressure 50 differential is the other way round the pressure differential acts against the spring 23, moving the second valve member 7 relative to the first to open the second port 4, permitting fluid flow between the ports.
55 The assembly 1 can therefore operate to allow fluid flow in either direction by appropriate control of the solenoid 9 and the pressure differential.
The assembly 1 has a simple and light construction as it has only one solenoid, which 60 also has the advantage of simplifying the control of the assembly. Further, in the arrangement shown, the valve-operating forces can be minimised, as the solenoid does not move the first valve member 6 if a significant pressure 65 differential is acting against it. The use of the biassing means provides positive closure of the two ports by their respective valve members.
The control valve assembly can be used in any hydraulic systems where these features are advantageous, in particular, in high pressure systems. The relative forces provided by the solenoid and the biassing means may be altered to suit the operating pressure and operation of the system.

Claims (10)

Claims
1. A fluid flow control valve assembly of the kind set forth in which the valve means comprises two relatively movable valve members, a first valve member for controlling fluid flow through the first port, movement of the first valve member being controlled by a first biassing means urging the first valve member to close the first port, a valve-operating means for producing a force urging the first valve member to open the first port, and the pressure differential across the first valve member, and a second valve member for controlling fluid flow through the second port, movement of the second valve member being controlled by the first valve member, the pressure differential across the second valve member and second biassing means urging the second valve member to close the second port.
2. A fluid flow control valve assembly as claimed in claim 1, in which the valve-operating means comprises a solenoid.
3. A fluid flow control valve assembly as claimed in claim 1 or claim 2, in which the first and second biassing means comprise first and second springs.
4. A fluid flow control valve assembly as claimed in any preceding claim, in which the second valve member works in a bore in the first valve member.
5. A fluid flow control valve assembly as claimed in any preceding claim, in which the valve members are connected by a mechanism providing limited relative movement between the valve members.
6. A fluid flow control valve assembly as claimed in claim 5, in which the mechanism comprises a pin and slot connection.
7. A fluid flow control valve assembly as claimed in any of claims 2 to 6, in which communication between the ports is permitted when the solenoid is de-energised and the pressure differential acts against the first biassing means to move the first valve member to open the first port without closing the second port.
8. A fluid flow control valve assembly as claimed in any of claims 2 to 7, in which communication between the ports is permitted when the solenoid is energised to cause the first valve member to open the first port, and the pressure differential acts against the second biassing means to move the second valve member to open the second port.
9. A fluid flow control valve assembly as claimed in claim 8, in which energisation of the solenoid produces a force which is unable to
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GB 2 133 120 A 3
move the first valve member against a significant kind set forth substantially as described herein pressure differential. 5 with reference to and as illustrated in the
10. A fluid flow control valve assembly of the accompanying drawings.
Printed for Her Majesty's Stationery Office by the Courier Press, Leamington Spa, 1984. Published by the Patent Office, 25 Southampton Buildings, London, WC2A 1 AY, from which copies may be obtained.
GB08330620A 1982-11-24 1983-11-16 Fluid flow control valve assemblies Expired GB2133120B (en)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
GB8233554 1982-11-24

Publications (3)

Publication Number Publication Date
GB8330620D0 GB8330620D0 (en) 1983-12-21
GB2133120A true GB2133120A (en) 1984-07-18
GB2133120B GB2133120B (en) 1986-03-19

Family

ID=10534488

Family Applications (2)

Application Number Title Priority Date Filing Date
GB08330620A Expired GB2133120B (en) 1982-11-24 1983-11-16 Fluid flow control valve assemblies
GB08330555A Expired GB2134459B (en) 1982-11-24 1983-11-16 High pressure hydraulic systems

Family Applications After (1)

Application Number Title Priority Date Filing Date
GB08330555A Expired GB2134459B (en) 1982-11-24 1983-11-16 High pressure hydraulic systems

Country Status (4)

Country Link
US (2) US4508012A (en)
EP (2) EP0110619A1 (en)
JP (2) JPS59110984A (en)
GB (2) GB2133120B (en)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB2216990A (en) * 1988-03-29 1989-10-18 Festo Kg Override check valve

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DE3611045A1 (en) * 1986-04-02 1987-10-08 Bosch Gmbh Robert ANTI-BLOCKING BRAKE SYSTEM
US4794947A (en) * 1986-11-29 1989-01-03 Kabushiki Kaisha Nippon IC (also trading as Nippon IC, Inc.) Mass flow controller
DE3709530C2 (en) * 1987-03-23 1998-05-20 Mannesmann Ag Running gear with wheels
US5064166A (en) * 1990-09-20 1991-11-12 Ford Motor Company Solenoid valve with high flow capacity and low energy consumption
US5188017A (en) * 1991-06-18 1993-02-23 The Consumers' Gas Company, Ltd. Natural gas cylinder fitting and solenoid valve
US5609400A (en) * 1993-09-27 1997-03-11 Sumitomo Electric Industries, Ltd. Three position solenoid controlled valve
FR2750652B1 (en) * 1996-07-04 1998-11-13 Peugeot SYSTEM FOR CONTROLLING A HYDROPNEUMATIC SUSPENSION OF A MOTOR VEHICLE
FR2784333B1 (en) * 1998-10-13 2001-01-05 Peugeot REGULATION SYSTEM FOR MOTOR VEHICLE SUSPENSION
US8361018B2 (en) 2007-06-12 2013-01-29 Becton, Dickinson And Company Syringe with disabling mechanism
NL2001471C2 (en) * 2008-04-11 2009-02-23 Asco Controls Bv Electromagnet valve, has second seat for sealing ring formed by annular edge protruding from wall of groove in which ring is held
CN102927340B (en) * 2011-08-12 2014-07-02 邹燕 Gas emergency cut-off valve
CN106931192B (en) * 2017-03-17 2019-04-12 奉化鑫益气动工程有限公司 A kind of automobile air suspension electromagnetic control system
CN106931226A (en) * 2017-03-17 2017-07-07 奉化鑫益气动工程有限公司 A kind of air suspension integrated magnet valves
EP4067127A1 (en) * 2021-03-31 2022-10-05 BeijingWest Industries Co. Ltd. Suspension hydraulic lift actuator for axle trim height control

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CA659206A (en) * 1963-03-12 D. Polhemus Von Quick centering control mechanism
US2623541A (en) * 1948-11-20 1952-12-30 Alfred B Seppmann Lock and hill holder valve for hydraulic brakes
US3071393A (en) * 1957-09-13 1963-01-01 Bendix Westinghouse Automotive Load control valve for vehicle air springs
DE1530531C3 (en) * 1965-01-12 1974-03-14 Daimler-Benz Ag, 7000 Stuttgart Hydropneumatic auxiliary suspension with level control for vehicles
US3446246A (en) * 1966-01-18 1969-05-27 Dole Valve Co Flow adjustment valve
US3589391A (en) * 1968-05-06 1971-06-29 Ettore Pagliaro Electrically operated fluid flow control valve device
US3521851A (en) * 1968-08-23 1970-07-28 Skinner Precision Ind Inc Floating valve seal
DE2124542A1 (en) * 1971-05-18 1972-11-30 Hoesch Ag, 4600 Dortmund Control electronics for level regulating devices, in particular for motor vehicles
DE2817465A1 (en) * 1978-04-21 1979-10-31 Concordia Fluidtechnik Gmbh Magnetic valve venting noise damper - has spiral air guide with central inlet for air relief valve and distributed peripheral outlets
GB2045177B (en) * 1979-03-16 1982-10-20 Lucas Industries Ltd High pressure hydraulic systems
US4403765A (en) * 1979-11-23 1983-09-13 John F. Taplin Magnetic flux-shifting fluid valve
DE3172192D1 (en) * 1980-04-19 1985-10-17 Lucas Ind Plc Improvements in high pressure hydraulic systems
US4390188A (en) * 1980-05-03 1983-06-28 Lucas Industries Limited High pressure hydraulic systems

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB2216990A (en) * 1988-03-29 1989-10-18 Festo Kg Override check valve
US4905730A (en) * 1988-03-29 1990-03-06 Festo Kg Override check valve
GB2216990B (en) * 1988-03-29 1992-05-13 Festo Kg An override check valve

Also Published As

Publication number Publication date
JPS59113384A (en) 1984-06-30
EP0110619A1 (en) 1984-06-13
GB8330555D0 (en) 1983-12-21
GB2134459A (en) 1984-08-15
JPS59110984A (en) 1984-06-27
EP0110620A1 (en) 1984-06-13
US4541610A (en) 1985-09-17
GB8330620D0 (en) 1983-12-21
GB2134459B (en) 1986-01-15
GB2133120B (en) 1986-03-19
US4508012A (en) 1985-04-02

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Legal Events

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PCNP Patent ceased through non-payment of renewal fee