US3885583A - Pressure compensating valve mechanism for hydraulic control valves - Google Patents

Pressure compensating valve mechanism for hydraulic control valves Download PDF

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Publication number
US3885583A
US3885583A US463098A US46309874A US3885583A US 3885583 A US3885583 A US 3885583A US 463098 A US463098 A US 463098A US 46309874 A US46309874 A US 46309874A US 3885583 A US3885583 A US 3885583A
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United States
Prior art keywords
fluid
plunger
valve
pressure
passage
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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
US463098A
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English (en)
Inventor
Francis H Tennis
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.)
HYDRAULIC INDUSTRIES
HYDRAULIC INDUSTRIES Inc
VITAS THOMAS 158 LAKEFIELD COURT RACINE WI 53402-3103
Lear Corp EEDS and Interiors
Original Assignee
HYDRAULIC INDUSTRIES
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Filing date
Publication date
Application filed by HYDRAULIC INDUSTRIES filed Critical HYDRAULIC INDUSTRIES
Priority to US463098A priority Critical patent/US3885583A/en
Priority to GB16127/75A priority patent/GB1493991A/en
Priority to DE19752517135 priority patent/DE2517135A1/de
Priority to CA225,007A priority patent/CA1019222A/en
Priority to IT68016/75A priority patent/IT1032705B/it
Priority to FR7512301A priority patent/FR2268212B1/fr
Priority to PL1975179816A priority patent/PL96325B1/pl
Priority to JP4823975A priority patent/JPS5533481B2/ja
Application granted granted Critical
Publication of US3885583A publication Critical patent/US3885583A/en
Assigned to VITAS THOMAS, 158 LAKEFIELD COURT, RACINE, WI. 53402-3103 reassignment VITAS THOMAS, 158 LAKEFIELD COURT, RACINE, WI. 53402-3103 ASSIGNMENT OF ASSIGNORS INTEREST. Assignors: TOMCO, INC.
Assigned to UNITED TECHNOLOGIES AUTOMOTIVE, INC. reassignment UNITED TECHNOLOGIES AUTOMOTIVE, INC. ASSIGNMENT OF ASSIGNORS INTEREST. Assignors: B.R. HOLDINGS, LTD., TOMCO ACQUISITION, INC.
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
    • F15B13/0416—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor with means or adapted for load sensing
    • F15B13/0417—Load sensing elements; Internal fluid connections therefor; Anti-saturation or pressure-compensation 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
    • Y10T137/2496—Self-proportioning or correlating systems
    • Y10T137/2559—Self-controlled branched flow systems
    • Y10T137/2574—Bypass or relief controlled by main line fluid condition
    • Y10T137/2605—Pressure responsive
    • Y10T137/2612—Common sensor for both bypass or relief valve and other branch valve
    • Y10T137/2615—Bypass or relief valve opens as other branch valve closes
    • 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
    • Y10T137/2574—Bypass or relief controlled by main line fluid condition
    • Y10T137/2605—Pressure responsive
    • Y10T137/2622—Bypass or relief valve responsive to pressure downstream of outlet valve
    • Y10T137/2627—Outlet valve carried by bypass or relief valve
    • 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
    • Y10T137/7832—Plural valves biased closed
    • 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
    • Y10T137/86879—Reciprocating valve unit
    • 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

  • a conventional pressure compensated control valve of the type to which this invention pertains is disclosed in Tennis US. Pat. No. 3,718,159 which issued Feb. 27, 1973.
  • the control valve of that patent is provided with a plurality of control sections assembled in a bank, and its pressure compensating valve mechanism is embodied in an inlet section at one end of the bank.
  • the pressure compensating mechanism comprises a spool type valve plunger which operates in a bore closed at its ends to define inlet and feedback chambers into which the ends of the plunger extend.
  • Source fluid, feed, and bypass ports open to the bore at axially spaced locations, and the plunger is movable back and forth in the bore to regulate communication of the source fluid port with the feed and bypass ports in accordance with variations in the pressure differential of said chambers.
  • the pressure of source fluid manifested in the inlet chamber tends to move the plunger in one direction toward an unloading position at which all source fluid entering the mechanism flows to the bypass port.
  • the compensating plunger occupies this unloading position whenever the motor control spools of all the valve sections are in neutral positions.
  • the pressure of signal fluid in the feedback chamber tends to move the plunger in the opposite direction, toward a feed position at which it closes off the bypass port from the source fluid port and communicates the latter with the feed port. In this way, pressure fluid in the source fluid port is compelled to flow to a feeder passage which connects with the feed port, and which extends through all of the valve sections in the bank.
  • Such motion of the plunger to its feed position occurs as a consequence of actuation of one of the control spools to a Working position communicating one of its service passages with the feeder passage.
  • the pressure of fluid in the selected service passage is manifested in the feedback chamber, through a control or signal port, to cause the compensating plunger to move in the bypass closing direction a distance determined by the extent of displacement of the control spool out of its neutral position.
  • the compensating plunger will maintain a substantially uniform pressure drop across the orifice defined by the motor control spool in any working position thereof at which it meters flow of source fluid to the motor governed thereby.
  • the pressure compensating plunger will function to maintain the fluid motor in operation at a substantially constant speed corresponding to the metering position of the control spool. Any source fluid in excess of that needed for motor operation at the desired speed is directed to the bypass port by the compensating plunger.
  • the desired plunger stability is achieved by the incorporation of substantially small diameter orifices in the fluid control passages through which the inlet and feedback chambers are communicated with the source fluid and signal ports.
  • the best damping effect on compensating plunger movement is achieved when these oriflees are quite small in cross sectional area. With such small orifices, however, the plunger was incapable of fast response to any new modulating position demanded by readjustment of the motor control spool. Nor could the plunger move quickly to its bypass position at times when conditions demanded such response thereof.
  • control passages connecting with the inlet and feedback chambers should be severely restricted; while for fast response of the plunger to variations in pressure differential across its ends, these same control passages should be relatively unrestricted.
  • the present invention has as its principle objective the provision of a compensating valve mechanism which is constructed in a way that assures the desired stability of its compensating plunger under any given operating conditions, and which also assures exceptionally fast response of the plunger to changes in pressure differential across its ends.
  • this invention to provide a pressure compensating mechanism of the character described wherein substantially unrestricted control passages lead respectively to its inlet and feedback chambers, and wherein pressure actuatable means not only compels substantially restricted discharge of fluid out of the feedback chamber to assure the desired damping of the compensating plunger during normal modulating movement thereof but also assures substantially unrestricted discharge of fluid from the feedback chamber at times when faster response of the compensating plunger to changing pressure conditions becomes necessary.
  • FIG. I is a sectional view of a pressure compensating valve mechanism of this invention.
  • FIG. 2 is a fragmentary sectional view of a conventional control valve for a hydraulic motor, shown connected with the compensating mechanism of FIG. 1 for purposes of illustration;
  • FIG. 3 is a top view of the valve mechanism seen in FIG. 1, with portions broken away and shown in section in order to illustrate internal construction;
  • FIG. 4 is an enlargement of a portion of the mechanism seen in FIG. 3.
  • valve mechanism of this invention.
  • the valve mechanism is housed in a body 11 that is here shown by way of example as comprising the inlet section of a stacked control valve.
  • the control valve comprises at least one control section 12 such as seen in FIG. 2, which is adapted to be secured to the inlet section 11 with a flat surface thereof in mating engagement with a flat surface 13 on the underside of the inlet section.
  • inlet and control sections 11 and 12 are comparable to those disclosed in Tennis US. Pat. No. 3,718,159, to which reference may be had for a complete description of said components.
  • the control section 12 is of the type adapted to govem a reversible fluid rrlotor, such as a double-acting hydraulic cylinder (not shown). It has a pair of service passages 14 and 15 for connection with the opposite ends of the cylinder, and a valve spool 16 which is actuatable from a neutral position shown to working positions at opposite sides of neutral to communicate a selected one of the service passages with a feeder passage 17, and to communicate the nonselected service passage with a return passage 18.
  • a reversible fluid rrlotor such as a double-acting hydraulic cylinder (not shown). It has a pair of service passages 14 and 15 for connection with the opposite ends of the cylinder, and a valve spool 16 which is actuatable from a neutral position shown to working positions at opposite sides of neutral to communicate a selected one of the service passages with a feeder passage 17, and to communicate the nonselected service passage with a return passage 18.
  • Source fluid in the feeder passage 17 flows to the selected service passage through substantially large inner ports 19 in the wall of hollow portions of the spool, located adjacent to but at opposite sides of a solid center portion 20 thereof, and through outer ports 21 in the wall of the hollow portions of the spool.
  • the ports 21 also serve to connect the service passages with the return passages 18 in a manner deemed obvious from a consideration of FIG. 2.
  • actuation of the control spool 16 to either working position results in subjection of a signal passage 23 in section 12 to load" pressure at the selected service passage.
  • the load pressure is detected at enlargements 24 of the bore containing valve spool 16, through a connecting groove 25 in the face of the control section 12.
  • the enlargements 24, of course, are communicated with the selected service passages 14 or 15 through the adjacent hollow interior portions of the valve spool.
  • the body of Said section is provided with a bore 28, the opposite ends of which are closed by plugs 29 and 30.
  • An elongated spool-type pressure compensating plunger 32 is slidable axially back and forth in the bore between limits which can be defined by the engagement of its ends with the plugs 29 and 30.
  • a pair of axially spaced circumferential grooves 33 and 34 in the plunger define between them a land 35.
  • One end portion of the plunger has a deep well 36 to accommodate a substantially strong coil spring 37.
  • This spring is confined between the bottom of the well and the adjacent plug 29, and it urges the plunger toward its right hand limit of motion, in what can be considered the feed direction.
  • the compensating valve mechanism 10 comprises a number of ports that open to its bore 28 at axially spaced locations. Reading from left to right in FIG. 1, there is provided a feed port 39 which opens through the surface 13 at the underside of the body 11 at a location to register with the feeder passage 17 in a control section 12 secured to the body 11; an inlet port 40 for source fluid which opens to one side of the body as at 41; and a bypass port 42 which can be communicated with an outlet or tank port 43 for fluid to be returned to a reservoir. Communication between the bypass port 42 and the tank port 43 is provided by passage means in the interior of the body 11, including a passageway 44.
  • a duct 39' is shown connecting feed port 39 with feeder passage 17.
  • the signal passage 23 in control section 12 is shown connected by a duct 23' with a portion 45 of said signal passage in the body of the inlet section 11. It is to be understood, however, that the signal passage portion 45 opens through surface 13 at the underside of the inlet section, in register with passage 23 in the control section 12.
  • the opposite end portions of the plunger 32 cooperate with the plugged end portions of the bore 28 to define a pair of plunger actuating chambers 46 and 47.
  • the chamber 46 is at the left hand end of the plunger and can be considered as a feedback chamber which is communicated with the signal passage portion 45 to receive pressurized signal fluid therefrom.
  • the other chamber 47 can be considered as an inlet chamber which is connected with the inlet port 40 to receive source fluid therefrom. Pressure fluid flowing into either chamber tends to move the plunger toward the other chamber.
  • the valve plunger 32 is movable axially back and forth between a bypass position and a full feed position such as seen in FIG. 1 and which, if desired, can be defined by the engagement of its right hand end with adjustable stop 50 screw threaded into the plug 30.
  • the groove 33 therein establishes full flow communication between the feed and inlet ports 39 and 40, respectively; while the land 35 between the plunger grooves 33 and 34 closes off communication between the inlet and bypass ports 40 and 42, respectively.
  • Source fluid in port 40 is led into the inlet chamber 47 through a control passage 52 comprising a coaxial blind bore 53 in the right hand end portion of the compensating plunger. a radial port 54 in the plunger opening outwardly from the inner end of the blind bore to the plunger groove 33, and a counterbore 56 to which the outer end of bore 53 opens. As will be understood by those skilled in the art, the plunger port 54 will be in communication with the inlet port 40 at all times.
  • control passage 52 Contrary to past pressure compensating valve constructions wherein the control passage 52 was severely restricted, as by a small diameter radial port at its inner end, the control passage here shown provides a substantially unrestricted flow path from the inlet port 40 to the inlet chamber 47, for substantially free transfer of pressure fluid therebctween.
  • the radial port 54 at the inner end of the bore 53 is here provided by a hole substantially larger in diameter than was the practice heretofore.
  • the adjustable stop 50 projects into the counterbore 56 for engagement with the bottom thereof, and its exterior is suitably spaced from the wall of the counterbore.
  • a cross slot 57 in the inner end of the stop assures communication between the bore 53 and the counterbore 56 at times when the plunger 32 is in its limit of motion defined by said adjustable stop.
  • the compensating plunger 32 is shown in the operating position it will occupy whenever the control spool 16 in valve section 12 is in a full operating position at one side or the other of its neutral (hold) position seen in FIG. 2.
  • the compensating plunger is held in this full feed position by the force of its spring 37 augmented by a fluid pressure force imposed thereon by signal fluid at a pressure substantially corresponding to that which is present in the service passage then in communication with the feeder passage 17.
  • signal passage 23 is communicated with the feedback chamber 46 of the pressure compensating valve mechanism through control passage portion 45 in the inlet section, and a branch of the latter generally designated 60 formed in the body 11 of the compensating valve mechanism.
  • the branch 60 extends outwardly from its junction with passage portion 45 to the feedback chamber 46, in spaced relation to the plunger 32 but parallel to the latter and to the underside 13 of the body.
  • the branch passage 60 comprises a terminal portion of the signal passage.
  • the branch passage 60 is provided by a bore 61 in body 11, an axial passage 62 in the body of a hollow check valve 63 located in said bore, a counterbore 64 in the check valve to which passage 62 opens, and a bore 65 in a plug 66 threaded into the body at a location alongside the plug 29.
  • the plug 66 closes the mouth of a counterbore 67 to which the bore 61 opens, and it has a radial port 68 therein to communicate the branch 60 of the signal passage with the feedback chamber 46.
  • the inner end of the plug 66 is formed with a coaxial conically surfaced seat 69 for engagement by a conically surfaced head 70 on the adjacent end of the check valve 63.
  • the check valve is yieldingly held in a closed position of engagement with seat 69 by a spring 71 confined in the bore 61 inwardly of the check valve.
  • Communication between the axial passage 62 in the check valve and its counterbore 64 is controlled by a ball check 73, which is engageable with an outwardly facing seat at the bottom of said counterbore.
  • the spring seat member is confined in the counterbored interior of the check valve 63 with its outwardly facing end in engagement with the valve seat 69 on the inner end of the plug 66.
  • the exterior of the spring seat member 75 is spaced from the wall of the counterbore 64 in which it is received, and that said space cooperates with a cross slot 76 in the outer end of the spring seat member to provide communication between the axial passage 62 and the bore 65 in plug 66.
  • the signal passage branch 60 in the inlet section 11 comprises the passage portion 45, the adjacent portion of bore 61, axial passage 62 in check valve 63, counterbore 64 in said check valve, the space between the wall of said counterbore and the exterior of the spring seat member 75, the bore in plug 66, and port 68 which communicates with the feedback chamber.
  • signal passage branch 60 is designed to provide a path controlled by ball check 73 along which signal fluid can flow substantially unrestrictedly to the feedback chamber 46. This is to say that none of the passage portions defining the signal passage branch 60 offers any appreciable restriction to the flow of signal fluid to the feedback chamber 46.
  • the check valve 63 in which the ball check 73 is located governs communication between the feedback chamber 46 and a venting passage 80, here shown communicating with tank port 43.
  • This venting passage opens to the space in counterbore 67 surrounding the outer portion of check valve 63. Hence, when check valve 63 is moved off of its seat, it communicates the feedback chamber with the venting passage 80.
  • venting passage 80 is also of a size to permit fluid from the feedback chamber 46 to flow substantially freely to the tank 43 whenever check valve 63 is caused to open in response to force exerted on its seat engaging end by pressure fluid in feedback chamber 46.
  • the spring 71 which yeildingly holds the check valve 63 seated is strong enough to withstand pressure pulsations which are manifested in the feedback chamber 46 during normal modulating operation of the compensating plunger.
  • the motions of the plunger in response to such pulsations are damped through the provision of substantially restricted passage means by which the feedback chamber 46 is communicated with the tank port 43 or any other low pressure passage in the body of the inlet section 11.
  • such restricted venting passage means can be provided either by a small orifice in the plunger communicating the well 36 therein with the tank port 43; or by bore clearance around the exterior of the plunger at its left hand extremity.
  • this invention provides a restricted venting passage comprising a narrow shallow notch 82 in the conically surfaced head of the check valve 63, as seen in FIG. 4.
  • the notch 82 is effective to afford such restricted communication between the feedback chamber 46 and the tank port as is necessary for the desired damping of compensating plunger motions occurring as a consequence of signal pressure pulsations in a first range of pressures manifested in the feedback chamber.
  • check valve 63 opens to allow substantially unrestricted communication of the feedback chamber with the tank port.
  • This last condition can arise at times, for example, when the valve spool lo in control section 12 is returned to its neutral position from a working position such as described; or as a consequence of adjustment of said spool to a new working position.
  • the compensating plunger will respond in an exceptionally prompt manner by movement to a full bypass position if the main spool 16 is returned to neutral; or to whatever new modulating position is demanded by the readjusted working position of the main spool.
  • the inlet section H is also provided with a relief valve mechanism 85 like that disclosed in the aforesaid Tennis patent.
  • the relief valve functions as a pilot valve for the compensating plunger 32. For that reason, it is connected with the feedback chamber 46 through a passage 86, so as to be opened in consequence of excessively high system pressure manifested in the feedback chamber.
  • the relief valve opens, of course, it communicates the feedback chamber with the tank port 43; and it is set to open whenever pressure in the feedback chamber 46 rises to a value considerably in excess of that at which check valve 63 opens.
  • the pressure of inlet fluid in chamber 47 becomes effective to actuate the compensating plunger 32 to its full open position at which all source fluid entering the inlet 41 flows to the bypass port 42.
  • the full feed position of the plunger can be so determined by the adjusting screw 50 as to assure that bypass of source fluid will begin substantially immediately upon opening of the relief valve, after only a very slight leftward movement of the plunger out of its full feed position seen in FIG. 1.
  • B a one way valve arranged to open under signal fluid pressure to allow signal fluid to flow to the feedback chamber
  • C. means defining a restricted first venting passage which connects with the feedback chamber and is at all times effective to damp pulsations of moderate pressure therein such as occur during normal modulating operation of the plunger;
  • D. means defining a substantially unrestricted second venting passage connecting with the feedback chamber to provide for rapid flow of fluid therefrom;
  • valve member governing fluid flow through said second venting passage, said valve member being movable to a passage open position under force which pressure fluid in the feedback chamber imposes thereon;
  • said last named means comprising a surface on the valve member upon which signal fluid exerts passage closing force.
  • valve mechanism of claim I wherein said last named means further comprises a spring which augments the closing force exerted upon said valve member by pressure of signal fluid.
  • valve mechanism of claim 3 further characterized by:
  • valve member being located in the signal duct and engaging an annular seat therein coaxial with the signal duct;
  • valve member B and said valve member having an axial passage therethrough comprising part of the signal duct.
  • valve mechanism of claim 3 wherein said one way valve is located in said axial passage in the valve member and is cooperable with an annular seat on the latter, coaxial with said axial passage.
  • valve mechanism of claim 4 further characterized by:
  • valve mechanism of claim 5 wherein another part of said signal duct is provided by a space around the exterior of the spring seat member.

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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)
  • Control Of Fluid Pressure (AREA)
  • Flow Control (AREA)
  • Multiple-Way Valves (AREA)
US463098A 1974-04-22 1974-04-22 Pressure compensating valve mechanism for hydraulic control valves Expired - Lifetime US3885583A (en)

Priority Applications (8)

Application Number Priority Date Filing Date Title
US463098A US3885583A (en) 1974-04-22 1974-04-22 Pressure compensating valve mechanism for hydraulic control valves
DE19752517135 DE2517135A1 (de) 1974-04-22 1975-04-18 Druckkompensationsventil fuer hydraulische steuerschieber
CA225,007A CA1019222A (en) 1974-04-22 1975-04-18 Pressure compensating valve mechanism for hydraulic control valves
GB16127/75A GB1493991A (en) 1974-04-22 1975-04-18 Pressure compensating valve mechanism for hydraulic control valves
IT68016/75A IT1032705B (it) 1974-04-22 1975-04-21 Valvola di comando a pressione compensata
FR7512301A FR2268212B1 (enrdf_load_stackoverflow) 1974-04-22 1975-04-21
PL1975179816A PL96325B1 (pl) 1974-04-22 1975-04-22 Mechanizm zaworu do sterowania dzialania silnika hydraulicznego
JP4823975A JPS5533481B2 (enrdf_load_stackoverflow) 1974-04-22 1975-04-22

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
US463098A US3885583A (en) 1974-04-22 1974-04-22 Pressure compensating valve mechanism for hydraulic control valves

Publications (1)

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US3885583A true US3885583A (en) 1975-05-27

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Application Number Title Priority Date Filing Date
US463098A Expired - Lifetime US3885583A (en) 1974-04-22 1974-04-22 Pressure compensating valve mechanism for hydraulic control valves

Country Status (8)

Country Link
US (1) US3885583A (enrdf_load_stackoverflow)
JP (1) JPS5533481B2 (enrdf_load_stackoverflow)
CA (1) CA1019222A (enrdf_load_stackoverflow)
DE (1) DE2517135A1 (enrdf_load_stackoverflow)
FR (1) FR2268212B1 (enrdf_load_stackoverflow)
GB (1) GB1493991A (enrdf_load_stackoverflow)
IT (1) IT1032705B (enrdf_load_stackoverflow)
PL (1) PL96325B1 (enrdf_load_stackoverflow)

Cited By (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
USD297256S (en) 1985-09-04 1988-08-16 Victaulic Company Of America Alarm test valve body
US6439257B1 (en) * 1998-07-01 2002-08-27 Hydac Fluidtechnik Gmbh Pressure control valve with hydrodynamic damping
US20050211296A1 (en) * 2004-03-24 2005-09-29 Norikazu Ide Flow control valve
CN104235098A (zh) * 2013-12-23 2014-12-24 江苏恒立液压有限公司 液压阀装置
US9121397B2 (en) 2010-12-17 2015-09-01 National Oilwell Varco, L.P. Pulsation dampening system for a reciprocating pump
US20170268681A1 (en) * 2016-03-15 2017-09-21 Hamilton Sundstrand Corporation Directional Control Valve

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4779419A (en) * 1985-11-12 1988-10-25 Caterpillar Inc. Adjustable flow limiting pressure compensated flow control
CN107762999B (zh) * 2017-11-23 2019-05-24 李群 三通压力补偿阀及压力补偿系统

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2610859A (en) * 1949-07-09 1952-09-16 Modern Products Inc Quick-exhausting valve
US3034527A (en) * 1959-11-17 1962-05-15 William E Hennells Safety check and exhaust valve
US3595265A (en) * 1969-04-14 1971-07-27 Caterpillar Tractor Co Self-cleaning orifice check valve
US3718159A (en) * 1971-01-20 1973-02-27 Hydraulic Industries Control valve

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2610859A (en) * 1949-07-09 1952-09-16 Modern Products Inc Quick-exhausting valve
US3034527A (en) * 1959-11-17 1962-05-15 William E Hennells Safety check and exhaust valve
US3595265A (en) * 1969-04-14 1971-07-27 Caterpillar Tractor Co Self-cleaning orifice check valve
US3718159A (en) * 1971-01-20 1973-02-27 Hydraulic Industries Control valve

Cited By (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
USD297256S (en) 1985-09-04 1988-08-16 Victaulic Company Of America Alarm test valve body
US6439257B1 (en) * 1998-07-01 2002-08-27 Hydac Fluidtechnik Gmbh Pressure control valve with hydrodynamic damping
US20050211296A1 (en) * 2004-03-24 2005-09-29 Norikazu Ide Flow control valve
US7243672B2 (en) * 2004-03-24 2007-07-17 Kayaba Industry Co., Ltd. Flow control valve
US9121397B2 (en) 2010-12-17 2015-09-01 National Oilwell Varco, L.P. Pulsation dampening system for a reciprocating pump
CN104235098A (zh) * 2013-12-23 2014-12-24 江苏恒立液压有限公司 液压阀装置
CN104235098B (zh) * 2013-12-23 2016-08-17 江苏恒立液压科技有限公司 液压阀装置
US20170268681A1 (en) * 2016-03-15 2017-09-21 Hamilton Sundstrand Corporation Directional Control Valve
US10197169B2 (en) * 2016-03-15 2019-02-05 Hamilton Sundstrand Corporation Directional control valve

Also Published As

Publication number Publication date
IT1032705B (it) 1979-06-20
PL96325B1 (pl) 1977-12-31
CA1019222A (en) 1977-10-18
FR2268212A1 (enrdf_load_stackoverflow) 1975-11-14
DE2517135A1 (de) 1975-10-30
JPS5533481B2 (enrdf_load_stackoverflow) 1980-09-01
FR2268212B1 (enrdf_load_stackoverflow) 1977-04-15
GB1493991A (en) 1977-12-07
JPS50144135A (enrdf_load_stackoverflow) 1975-11-19

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