US3550611A - Unitary combination of pressure-responsive flow control unidirectional valves for hydraulic systems - Google Patents

Unitary combination of pressure-responsive flow control unidirectional valves for hydraulic systems Download PDF

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Publication number
US3550611A
US3550611A US768110A US3550611DA US3550611A US 3550611 A US3550611 A US 3550611A US 768110 A US768110 A US 768110A US 3550611D A US3550611D A US 3550611DA US 3550611 A US3550611 A US 3550611A
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US
United States
Prior art keywords
pressure
pistons
valve
valves
fluid
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired - Lifetime
Application number
US768110A
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English (en)
Inventor
Johannes Vagn Baatrup
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Danfoss AS
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Danfoss AS
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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
    • 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
    • F15B21/00—Common features of fluid actuator systems; Fluid-pressure actuator systems or details thereof, not covered by any other group of this subclass
    • 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
    • Y10T137/2564—Plural inflows
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T137/00—Fluid handling
    • Y10T137/8593—Systems
    • Y10T137/87169—Supply and exhaust
    • Y10T137/87177—With bypass

Definitions

  • Spheres cooperating with the internal pistons form another pair of check valves which are pressure-responsive and can also be opened by a rigid control member, in the form of a rod, when the hollow pistonsare driven in axial directions toward each other by given fluid pressures.
  • the fluid under pressure is applied to the valves by entry into and out of two axially spaced spaces defined in the bore by the hollow transporting pistons and an intermediate space therebetween.
  • the moving parts of the fluid motor in the system are also freqq'ently subjected, during operation, to a hydraulic shockdue to an external impact, for example when a hydraulic piston is used in a fluid motor for guiding the wheels of a vehicle which strike an obstacle.
  • a hydraulic shockdue to an external impact for example when a hydraulic piston is used in a fluid motor for guiding the wheels of a vehicle which strike an obstacle.
  • Considerable excess fluid pressure then occurs on one side of the piston and too low a pressure on the iother, and this can be balanced out through the check valves
  • Control devices in known hydraulic; system usually incorporate a control member of some kind, e. g. a rotary slide, which, in a neutral position, provides a bypass to a motor in the system.
  • the control element is then under the influence of the pressure in a bypass on the one side, and on the other side it is under the influence of the pressure in lines connected to the motor. Even at quite small differences in pressure, the control member in such control devices can jam
  • Such fluid pressure difierences can arise, for example, if a second device, 'e.g. a control device for a second motor, is connected to the control device for the first motor.
  • a second device e.g. a control device for a second motor
  • the first control device is in its neutral operating position and sure in the system operates unilaterally on the control member of this control device.
  • the invention provides a valve combination of the initially described kind and provides, in both supply lines to a motor valves that are opened when a pressure obtains in both motor lines that exceeds the pressure in a return pipe by a prescribed amount.
  • a valve arrangement according to the invention two valves of two pairs of check valves 'open towards the motor and are able to equalize the pressure when a smaller or greater excess pressure obtains in a bypass of a control device in the hydraulic circuit.
  • the valves opening away from the motor on the other hand cannot be used to equalize excess pressure in the motor supply lines that, while giving trouble, has not yet reached the limit of safety, since these latter valves are biased under spring pressure such that they only open when a quite high safety value for fluid pressure has been exceeded.
  • the above-mentioned valves of the invention can be used since these open in a circumstance where a limiting value for pressure that can be considerably lower than the safe pressure is exceeded in both motorsupply lines.
  • valves of both pairs of check valves of the invention with additional means which are influenced by the pressure in both motor supply lines and which enable the valves to open in a positive manner, i.e. independently of their usual mode of actuation.
  • additional means can act upon those valves of the two pairs that open toward the motor.
  • the unitary valve combination of the invention comprises two pistons displacable in response to fluid pressure symmetrically relative to a central common stop in a common bore which is closed at its opposite ends and near the end-faces of which spaces are formed for connection to motor supply lines and in the middle of which an intermediate space is in connection with a returnpipe.
  • the pistons each are hollow and have at their end-faces or crowns ,an inner seat for other hollow check valve elements comprising other pistons contained in the pistons.
  • These other pistons in turn have on their end-faces a first-mentioned hollow seat for a third pair of check valve elements.
  • the two first-mentioned pair of check valve elements are biased by a common spring supported on the two pistons and extending between them.
  • four valves having six pressure control functions are assembled in an extremely compact space and without need of three sets of separate unidirectional or check valves.
  • the pistons have valve openings in the crowns and comprise, outside of the inner pistons, adjacent their valve seats, extending in the axial direction, a guide passage, containing openings, for the second check valve elements, which, constitute simple spheres or balls.
  • the second check valve members, the first check valve I members and their springs and backing rings later described can be inserted into the bore from an open end, later closed, and the whole assembly locked in position by means of a circlip.
  • the arrangements rigid control rod has near both ends thereof a stop-face which bears against an opposed face on the first check valve hollow pistons. This rod causes positive opening of both of the second pair of check valves even when the pressures in the two motor supply and discharge lines are not exactly the same.
  • FIG. 1 is a schematic diagram of a valve arrangement of the invention connected in a hydraulic system
  • FIG. 2 is a longitudinal section view of a unitary valve combination according to the invention.
  • FIG. 1 illustrates a pump 1 delivering hydraulic fluid under pressure pressure from a supply source 1 by way of a discharge line 3 to a first control device 4 in a return line 5 in which is connected a second control device 6 from which the hydraulic fluid can return to the source 2 through a line 7.
  • the first control device 4 has a neutral position, in which the fluid is fed directly from the discharge line 3 into the return line 5 through a bypass 8, and has two working positions, in which the hydraulic fluid can be selectively delivered through two hydraulic motor junction lines 9, 10 into two chambers 11, 12 formed on both sides of a piston 13 of a hydraulic cylinder 14.
  • the junction lines 9, 10 are each both supply and discharge lines to and from the motor 14 and are referred to as junction lines for convenience.
  • the second control device 6 likewise has a bypass and at least one working position, not shown, in which this bypass is blocked.
  • the first control device 4 can control, for example, the motor 14 for guiding the wheels of an agricultural machine, and the device 6 may have a motor on the machine, not
  • Each connecting line 15, 16 also contains a check valve 22, 23 which is controlled by an additional actuating or control device 24 which, as indicated in dash-and-dot lines, is influenced by the pressure in the two junction lines 9, 10 and in the return line 5.
  • the last pair of valves open when the pressure in the two junction lines 9, 10 reaches a prescribed value in excess of the pressure in the return line 5.
  • a force K, acting on the piston 13 is too great, as result, for example, of the guided wheels on the vehicle, not shown, striking an obstacle. Excess pressure then occurs in the hydraulic cylinder chamber 11 and a pressure that is too low occurs in the hydraulic cylinder chamber 12. Hydraulic fluid under pressure passes from the one chamber 11 into the other chamber 12 through the connecting line 15, the check valve 18, which opens in this case, the check valve 21 and the connecting line 16.
  • the first control device 4 is in a neutral position, and the control device 6 in a working position.
  • a high pressure obtains in the return line 5.
  • This pressure may be substantially in excess of the pressure in the motor junction lines 9, 10.
  • the control member, e.g. the rotary slide, in the first control device 4 is loaded from the discharge line 3 and return line 5. This excess pressure is rapidly equalized by way of the two check valves 20, 21 opening toward the hydraulic motor 14.
  • a high pressure obtains in the entire hydraulic system.
  • the first control device 4 is in its neutral position, and the second control device 6 is placed in its neutral position.
  • the pressure in the return line then falls considerably below the pressure in the junction lines 9, 10.
  • the control member in the first device 4 is loaded from the junction lines. ln this case, the check valves 18, 19 are unaffected, since they are too heavily biased and the other check valves 20, 21 are not influenced because their opening direction is not the right one.
  • the third set of check valves 22, 23 do open, because their actuating or control device 24 determines that the pressure in the two junction lines 9, has exceeded that in the return line 5 by a predetermined amount.
  • the check valves and control device 18-24 with the corresponding connections are grouped together with connections to the fluid lines -17.
  • a single bore 25 in a housing is sealed at both ends by means of caps or plugs 26.
  • the connecting lines 15, 16 are connected to ports near the ends of the bore and the return line 17 in the middle of the bore.
  • Two pistons 27, 28 are disposed in the bore and can move in the bore axially, from a stationary position illustrated, up to a central stop 29.
  • Each piston is hollow and has on the inside of its end-face or crown a valve seat 20, 30, 31, about a valve opening, for a valve member or element 32, 33 of the first pair of check valves which are acted upon by relatively strong springs 34. 35 which bear against backing rings 38, 39 secured by circlips 36, 37.
  • valve elements or members 32, 33 are hollow pistons reciprocable relative to their transporting pistons 27, 28 and their outwardly directed end-faces 40, 41 constitute valve seats for a third pair of check valve members 42, 43 of the second pair of check valves. These latter members or elements are formed as balls or spheres. Beyond their valve seats, the pistons comprise guide passages 46, 47 for these spheres. The passages are provided with openings 44, 45. Thus spaces of varying volume are formed at extremities of the bore in communication with the connecting lines 15, 16 through respective portsfor inward and outward flow of fluid. A space intermediate these extremity spaces is formed between the transporting pistons 27, 28 and it is in communication with the return line 17 for inward and outward flow of fluid.
  • a spring 48 extends between the first pair of valve pistons 32, 33. Also, on the bore longitudinal axis is disposed a control rod 49 having ends 50, 51 coaxial with valve openings in the pistons 27. 28, 32 and 33 and are able to lift the ball valve elements or members 42, 43 from their seats.
  • the rod is provided with axial groves 52, 53 and can bear on terminal or ends of the inner bores of the valve members or inner pistons 32, 33 by means of stop-faces 54, 55.
  • a unitary valve combination comprising, means defining a housing having a bore closed at opposite ends, a first pair of individually reciprocable valve elements in said bore reciprocable in said bore in response to fluid under pressure defining a central space of varying volume in said bore and two axially spaced extremity spaces of varying volume defined by said first pair of valve elements adjacent opposite ends of said bore and separate from said central space, said housing having two ports each in communication with said extremity spaces for fluid flow under pressure alternatively into and out of said extremity spaces and a port in communication with said central space forfluid flow alternatively into and out of said central space, a second pair of valve elements each transported by an associated one of said first pair of valve elements and reciprocable relative to the transporting first pair of valve elements and jointly defining therewith unidirectional check valves allowing fluid from said extremity spaces to said central space, means determining the fluid pressure at which said first and second pairs of valve elements are relatively reciprocable determining the pressure at which said check valves will open, a third pair of valve elements each cooperative with a respective one of

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Analytical Chemistry (AREA)
  • Fluid-Pressure Circuits (AREA)
  • Safety Valves (AREA)
  • Multiple-Way Valves (AREA)
US768110A 1967-10-17 1968-10-16 Unitary combination of pressure-responsive flow control unidirectional valves for hydraulic systems Expired - Lifetime US3550611A (en)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE19671650352 DE1650352B2 (de) 1967-10-17 1967-10-17 Ventilkombination fuer hydraulikanlagen

Publications (1)

Publication Number Publication Date
US3550611A true US3550611A (en) 1970-12-29

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Family Applications (1)

Application Number Title Priority Date Filing Date
US768110A Expired - Lifetime US3550611A (en) 1967-10-17 1968-10-16 Unitary combination of pressure-responsive flow control unidirectional valves for hydraulic systems

Country Status (10)

Country Link
US (1) US3550611A (fr)
AT (1) AT288806B (fr)
CH (1) CH478347A (fr)
DE (1) DE1650352B2 (fr)
DK (1) DK126870B (fr)
ES (1) ES359167A1 (fr)
FR (1) FR1589551A (fr)
GB (1) GB1207027A (fr)
NL (1) NL157690B (fr)
SE (1) SE340224B (fr)

Cited By (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4405030A (en) * 1981-03-16 1983-09-20 Deere & Company Steering system and compensating valve
US4463775A (en) * 1983-03-23 1984-08-07 Deere & Company Compensating valve
US6257268B1 (en) 1999-12-01 2001-07-10 Gilmore Valve Company Pressure biased shuttle valve
US6318400B1 (en) 1999-12-01 2001-11-20 Gilmore Valve Company Low interflow hydraulic shuttle valve
EP1217201A2 (fr) * 2000-11-23 2002-06-26 Juan Fierro Aguirre Tuyau pour alimenter en carburant un moteur à combustion interne
US6655405B2 (en) 2001-01-31 2003-12-02 Cilmore Valve Co. BOP operating system with quick dump valve
US20100032036A1 (en) * 2007-06-30 2010-02-11 Festo Ag & Co. Kg Valve with an and-function
US20100154896A1 (en) * 2008-12-20 2010-06-24 Dtl Engineering And Design, L.P. Shuttle valve
US9638341B1 (en) * 2014-05-16 2017-05-02 Hydro-Gear Limited Partnersip Loop flushing valve
US20180238471A1 (en) * 2017-02-21 2018-08-23 The Boeing Company Shuttle Valve with Damping

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2492941A1 (fr) * 1980-10-29 1982-04-30 Renault Dispositif limiteur de pression differentielle a clapets
DE3245288A1 (de) * 1982-12-03 1984-06-14 O & K Orenstein & Koppel Ag, 1000 Berlin Verfahren zur einsparung von energie beim stellen eines ausruestungszylinders an einem hydraulikbagger durch eine hydraulikschaltung
US4993921A (en) * 1989-04-21 1991-02-19 Vickers, Incorporated Power transmission

Cited By (18)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4405030A (en) * 1981-03-16 1983-09-20 Deere & Company Steering system and compensating valve
US4463775A (en) * 1983-03-23 1984-08-07 Deere & Company Compensating valve
US6257268B1 (en) 1999-12-01 2001-07-10 Gilmore Valve Company Pressure biased shuttle valve
US6318400B1 (en) 1999-12-01 2001-11-20 Gilmore Valve Company Low interflow hydraulic shuttle valve
EP1217201A2 (fr) * 2000-11-23 2002-06-26 Juan Fierro Aguirre Tuyau pour alimenter en carburant un moteur à combustion interne
EP1217201A3 (fr) * 2000-11-23 2003-07-16 Juan Fierro Aguirre Tuyau pour alimenter en carburant un moteur à combustion interne
US6779543B2 (en) 2001-01-31 2004-08-24 Gilmore Valve Co., Ltd. BOP operating system with quick dump valve
US20040107991A1 (en) * 2001-01-31 2004-06-10 Gilmore Valve Co., Ltd. Bop operating system with quick dump valve
US6655405B2 (en) 2001-01-31 2003-12-02 Cilmore Valve Co. BOP operating system with quick dump valve
US20100032036A1 (en) * 2007-06-30 2010-02-11 Festo Ag & Co. Kg Valve with an and-function
US8171951B2 (en) * 2007-06-30 2012-05-08 Festo Ag & Co. Kg Valve with an AND-function
US20100154896A1 (en) * 2008-12-20 2010-06-24 Dtl Engineering And Design, L.P. Shuttle valve
US8397742B2 (en) 2008-12-20 2013-03-19 Dtl Technologies, L.P. Shuttle valve
US9638341B1 (en) * 2014-05-16 2017-05-02 Hydro-Gear Limited Partnersip Loop flushing valve
US10197174B1 (en) 2014-05-16 2019-02-05 Hydro-Gear Limited Partnership Loop flushing valve
US20180238471A1 (en) * 2017-02-21 2018-08-23 The Boeing Company Shuttle Valve with Damping
US10344890B2 (en) * 2017-02-21 2019-07-09 The Boeing Company Shuttle valve with damping
US10914402B2 (en) 2017-02-21 2021-02-09 The Boeing Company Shuttle valve with damping

Also Published As

Publication number Publication date
CH478347A (de) 1969-09-15
DE1650352B2 (de) 1971-08-12
ES359167A1 (es) 1970-05-16
AT288806B (de) 1971-03-25
FR1589551A (fr) 1970-03-31
NL157690B (nl) 1978-08-15
DE1650352A1 (de) 1970-09-17
NL6814274A (fr) 1969-04-21
GB1207027A (en) 1970-09-30
SE340224B (fr) 1971-11-08
DK126870B (da) 1973-08-27

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