US3782404A - Adjustable, metered, directional flow control arrangements - Google Patents

Adjustable, metered, directional flow control arrangements Download PDF

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Publication number
US3782404A
US3782404A US3782404DA US3782404A US 3782404 A US3782404 A US 3782404A US 3782404D A US3782404D A US 3782404DA US 3782404 A US3782404 A US 3782404A
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Prior art keywords
inlet
control valve
flow
valve
fluid
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English (en)
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R Hodgson
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Commercial Shearing Inc
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Commercial Shearing Inc
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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
    • 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
    • F15B13/0401—Valve members; Fluid interconnections therefor
    • F15B13/0402—Valve members; Fluid interconnections therefor for linearly sliding valves, e.g. spool valves
    • F15B13/0403—Valve members; Fluid interconnections therefor for linearly sliding valves, e.g. spool valves a secondary valve member sliding within the main spool, e.g. for regeneration flow
    • 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
    • F15B11/00—Servomotor systems without provision for follow-up action; Circuits therefor
    • F15B11/16—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors
    • F15B11/161—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors with sensing of servomotor demand or load
    • F15B11/162—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors with sensing of servomotor demand or load for giving priority to particular servomotors or users
    • 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
    • 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
    • F15B13/022—Flow-dividers; Priority valves
    • 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
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/20—Fluid pressure source, e.g. accumulator or variable axial piston pump
    • F15B2211/205—Systems with pumps
    • F15B2211/20576—Systems with pumps with multiple pumps
    • 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
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/30—Directional control
    • F15B2211/305—Directional control characterised by the type of valves
    • F15B2211/30505—Non-return valves, i.e. check valves
    • 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
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/30—Directional control
    • F15B2211/35—Directional control combined with flow control
    • F15B2211/351—Flow control by regulating means in feed line, i.e. meter-in control
    • 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
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/40—Flow control
    • F15B2211/405—Flow control characterised by the type of flow control means or valve
    • F15B2211/40515—Flow control characterised by the type of flow control means or valve with variable throttles or orifices
    • 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
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/40—Flow control
    • F15B2211/45—Control of bleed-off flow, e.g. control of bypass flow to the return line
    • 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
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/70—Output members, e.g. hydraulic motors or cylinders or control therefor
    • F15B2211/71—Multiple output members, e.g. multiple hydraulic motors or cylinders
    • F15B2211/7142—Multiple output members, e.g. multiple hydraulic motors or cylinders the output members being arranged in multiple groups
    • 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
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/70—Output members, e.g. hydraulic motors or cylinders or control therefor
    • F15B2211/75—Control of speed of the output member
    • 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
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/70—Output members, e.g. hydraulic motors or cylinders or control therefor
    • F15B2211/78—Control of multiple output members
    • F15B2211/781—Control of multiple output members one or more output members having priority
    • 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
    • Y10T137/2514—Self-proportioning flow systems
    • Y10T137/2521—Flow comparison or differential response
    • Y10T137/2524—Flow dividers [e.g., reversely acting controls]
    • 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
    • Y10T137/2617—Bypass or relief valve biased open

Definitions

  • ABSTRACT A directional control valve having a pair of standard work positions and a pair of extreme work positions and having a pressure compensating piston arranged between an input and a parallel input line controlling the flow to said control valve, said compensating valve acting as a check valve when the control valve is in its extreme positions and a flow dividing and control valve between the pressure compensating valve and an overflow outlet for delivering excess fluid to a separate load circuit.
  • This invention relates to adjustable, metered, directional flow control arrangements and particularly to a flow control arrangement for delivering pressure fluid to a steering circuit and a working circuit for vehicles of the loading and excavating type.
  • Directional control valves for controlling hydraulic fluid flow to and from a fluid actuated operator are old and well known. Such valves are commonly used to deliver fluid to a piston and cylinder or other form of fluid motor and are quite satisfactory for such purposes where the valve is fully actuated to an open or a closed position. Valves of this type are not, however, adapted to provide a controlled metered flow to or from a fluid motor to operate the actuator at reduced or varied speeds. In general, the conventional control valve will produce a comparatively large change in flow rate for a very small change in position.
  • the present invention provides an adjustable metered directional flow control arrangement which solves both the problems of the Herd et al. and the Allen patents as well as providing a safety system which will divert all fluid to the steering in the event of a failure or malfunction.
  • the arrangement of this invention provides precisely controlled fluid flow to the primary actuator regardless of the amount of excess flow going to a secondary load circuit. This arrangement is accordingly ideally suited to sue in a combination steering and load circuit for vehicles of the loading and excavating type.
  • I provide a directional flow control arrangement for selectively operating first fluid operated motors at a controlled speed and supplying overflow to a separate second fluid motor load circuit
  • a pair of spacedfirst and second directional control valve means each having first and second motor ports for connection to the opposite sides of one of said fluid operated motors and operable to provide a restricted inlet flow passage therethrough for passing input pressure fluid to one of said motor ports the first of said valves being connected to said first motor means and having a parallel high pressure passage, the second to said second motor means and return flow passage for passing return fluid from the other of said motor ports, a pair of flow control valves connected to the inlet of each said directional control valve one having an inlet connected to a source of pressure fluid for said fluid motor through the inlet of said first directional valves, a controlled flow outlet port connected to the inlet of said other flow control valve, an excess flow outlet port connected to said parallel passages, valve means between said inlet port and both said outlet ports to control the fluid flow from said inlet to each of said outlet ports, means for operating
  • the first directional control valve is provided with an extreme position at each end of its spool movement connecting the inlet of the directional control valve in one such position with the parallel path and a first motor port and in the other of said positions connecting the inlet of the directional control valve with the parallel passage and the second motor port, bypassing the flow control valves.
  • FIG. 1 is a sectional view of a preferred embodiment of a valve arrangement according to my invention
  • FIG. 2 is a schematic view of a steering and implement circuit according to my invention.
  • FIG. 1 have illustrated a preferred embodiment of valve structure according to my invention as embodied in a combination steering and implement circuit such as is used on earth moving machines.
  • FIG. l have illustrated a directional control valve housing 10 having an axial bore 11 carrying a valve member 12.
  • the housing is provided with spaced exhaust chamber 13 and 14 adjacent each end and intersecting bore 11, a pair of work chambers 15 and 16, one adjacent each exhaust chamber and each adapted to be connected to the opposite sides of a fluid motor.
  • valve member 12 is hollow at each end to provide a pair of spaced apart internal chambers 21 and 22 extending axially of the valve member and each connected by a separate axial passage 23 and 24 and a separate radial passage 25 and 26 to spaced annular grooves 27 and 28 around the valve member 12 adjacent its mid point.
  • Each of chambers 21 and 22 is provided with two sets of radial passages 2la and 21b and 22a and 22b extending radially to the periphery of the valve member.
  • the radial passages 21a and 21b are spaced apart axially in chamber 21 as are also passages 22a and 22b in chamber 22.
  • Passages 21a and 220 are separated from passages 21b and 22b respectively by check valves 21c and 22:: movable in chambers 21 and 22 respectively and operated by springs 21d and 22d.
  • lnlet chamber 19 is connected to a pump 29 for providing a source of high pressure fluid.
  • lnlet chamber 20 is connected to inlet 30 of flow control valve 31 which is in turn connected to inlet 40 of flow control valve 41.
  • lnlet 30 communicates with bore 32 of valve 31 which is provided with valve member 33 biased to close the bore 32 between the passage 37.
  • the inlet 30 communicates at all times with outlet 34 through annular chamber 31a.
  • the bias is provided by a spring 35 and by a fluid pressure line 36.
  • lnlet 40 communicates with bore 42 of valve 41 which is provided with valve member 43 biased to close outlet 44 and prevent communication of outlet 44 with inlet 40.
  • the bias is provided by spring 45 and fluid pressure line 46.
  • Fluid pressure lines 36 and 46 connect to a common annular manifold 47 in bore 11 of the directional control valve 10.
  • Outlet 44 is connected to implement directional control valve 50 through its inlet where it joins the input line 51 from a second pump 52 providing an independent source of high pressure fluid.
  • FIGS. 1 and 2 The operation of the structure of FIGS. 1 and 2 as applied to a combination steering and implement control arrangement is as follows assuming a pump pressure available in excess of 60 psi. When there is no flow of pressure fluid in the system and the directional control valve for steering control is in the neutral position, everything will be essentially as shown in the FIG. 1. The upper of the two flow control pistons will be to the right, and the lower will be to the left, both of which are spring biased. When the pump is started up and the spool 12 remains in neutral, the flow will be around the spool 12 and around the first 33 of the two flow control spools through annular chamber 31a to the annular groove 43a or reduced diameter area of the second spool at which time it is blocked monentarily.
  • the second spool 43 will then shift towards the right at approximately 60 psi because of the flow of fluid in line 43b and begin to bypass oil on to the rest of the circuit through outlet 44, which in this case is primarily the lifting circuit for the implement as represented by valve 50.
  • the spring .end of that flow regulating spool is vented to the reservoir through the line 46 of the spool as previously discussed. Any requirement of the implement circuit then can be accommodated by the flow through this valve on to the implement circuit, either by its singular supply from this pump or in conjunction with any other pump 52 which may be in this total circuit.
  • the upper of the two flow regulating spools 33 is spring biased towards the right and also is vented to the reservoir by line 36 when the directional control valve spool 12 in this steering valve is in neutral; therefore, it will act as a check in certain cases. If we assume that the upper of the two flow regulating spools 33 has a 40 pound spring 35, it would be normal then for this spool 33 to shift to the left and close off any passage from the main open-center path 19, 20 to the parallel path 17, 18, 60 from which power can be directed to either work port 15 or 16 because of the fact that the spring end is vented to the reservoir which is at less than 40 or 60 psi.
  • the passages within the spool 12 will be aligned so that the parallel chamber 15 immediately adjacent to this upper flow regulating valve 31 will be connected through to port 15 except for the spring loaded check valve 210 within the spool.
  • the passage 23 within the spool 12 is also connected to the back of both of the flow regulating valves 31 and 41, both the upper and the lower, so that they then become pressure compensated. In effect, they are pressure compensated in an opposite manner from each other.
  • the lower valve 41 is pressure compensated to regulate the exhausting or excess oil.
  • the upper outlet 37, to the left, will actually be shut off and will not start to open up until communication between the parallel path 17, 60, 18 the center of the spool 12, the connecting or vent path and the back of the spool 33 is completed at which time the circuit is complete and both ends of the spool are connected together via the previously mentioned route.
  • the spring 35 will then push the spool to the right opening a path around the spool from the main open-center supply route from the pump to the parallel supply path 60 in the valve itself.
  • there will be a pressure drop from this main supply path to the parallel path and there will be a second pressure drop from the parallel path 60 into the spool, both of which will affect the total amount of flow being permitted to pass in that direction and ultimately to port 15.
  • a pressure drop from the parallel passage 60 into the center of the spool will be established. This will be matched by the pressure drop established across the spool and the edge of the housing metering the oil from the opencenter passage to the parallel path 60 in opposition to the spring 35. However, since there is assumed an established 60 psi pressure differential available, the spool will shift beyond that point and attempt to put more oil to the parallel passage. Now, the 40 psi drop will definitely be between the spool 33 OD and the spool 33 ID at the parallel passage 60 opening.
  • the spool 33 will continue to shift to the left until a 20 psi drop is established from the open-center passage to the reduced diameter area of the spool 33, thereby establishing a total of 60 psi pressure drop from the opencenter passage to the center of the directional spool 12. This will be balanced by the spring 35 and the differential pressure across the respective ends of the flow regulating spool 33. Any tendency of the external pressure to vary the amount of oil directed towards port will be automatically adjusted to compensate for this by the shifting of the flow regulating spool 33. In short, the spool 33 meters flow in to the parallel path 60. It can be seen that the only oil taken from the (open-center) inlet chambers 19 and path in the steering device will be that oil which is required and regulated by the steering directional control valve spool 12 and its associated compensator valve 31.
  • the operation will be the same whether this be higher than the operating pressure of the implement circuit or higher than the open-center pressure when there is no demand on the implement circuit.
  • the second or lower pressure compensated spool 41 is also connected to the respective side of the spool that is expecting power for the port, and it will load at whatever pressure is required by he steering circuit.
  • An additional feature which is available in the structure of this invention is the fact that the spool 12 can be shifted over and beyond that normally required for metered control. When this is done in either direction from neutral position, the full diameter of the spool which up to this point has been separating the opencenter path from the parallel path is now shifted off to the right so that it blocks the open-center path 19, 20 completely at that point and opens the direct passage from the inlet 19 to the parallel path 17, 60. At this time all of the oil from the pump will be directed to the parallel path 17, 60 and subsequently to port 15 via the spool 12 and check valve 21c. The lower 41 of the two flow regulating valves is no longer a factor in the circuit.
  • the upper 31 of the two valves will now assume a position as a check valve and block the escape of any oil from the parallel path 17, 60 to the open center 20 and thereby preventing the oil from subsequently be coming a loss to the circuit.
  • the spool 12 is moved to the extreme left position, there is a passage opened up between the open center 19 or pump inlet and the parallel path 17, 60 at the same time that the full diameter of the spool at land 12a blocks the opencenter path 20.
  • the implement valve 50 may be of the more common open-center type or it may be pressure compensated since this method of control does not affect performance of the steering valve.
  • the steering valve 10 will take whatever oil is necessary at its pressure regardless of what is going on at the balance of the circuit. In addition, the steering circuit takes only that oil which it needs unless an emergency occurs at which time all of the oil from pump is made available.
  • a directional flow control arrangement for selectively operating a first fluid motor in two directions at a controlled speed and supplying overflow to a separate second fluid motor load circuit
  • a directional control valve means (10, 11, 12) having an inlet means (19) and an outlet means (44) a parallel high pressure passage and first (15) and second (16) motor ports for connection to the opposite sides of said first fluid operated motor
  • said directional control valve including a movable valve member (12) having annular grooves and axial bores cooperating to provide a restricted inlet flow passage therethrough for passing input pressure fluid to one of said motor ports (15, 16) and return flow passage (21, 21a-c; 22, 22a-e) for passing return fluid from the other of said motor ports, to an adjacent exhaust chamber (13, 14) a pair of flow controls valves (31, 41) connected to the inlet (19) of said directional control valve (10) one having an inlet (30) connected to a source of pressure fluid for said first fluid motor through the inlet (19) for said directional control valve, an outlet port (34) cont
  • valve member of the directional control valve is movable in a bore therein, said valve member being hollow at each end to form chambers therein adapted selectively to communicate through the valve member walls with the inlet port, work ports, an outlet port and the pressure sensing port of the pressure compensating valve.
  • a control valve as claimed in claim 1 wherein the directional flow control valve means has an extreme position at each end which directly connects the inlet and parallel passage with one of the motor ports.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Fluid-Pressure Circuits (AREA)
  • Servomotors (AREA)
  • Multiple-Way Valves (AREA)
  • Power Steering Mechanism (AREA)
US3782404D 1972-06-14 1972-06-14 Adjustable, metered, directional flow control arrangements Expired - Lifetime US3782404A (en)

Applications Claiming Priority (1)

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US26246072A 1972-06-14 1972-06-14

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JP (1) JPS5741609B2 (de)
DE (1) DE2328658C2 (de)
GB (1) GB1387543A (de)

Cited By (9)

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DE2513919A1 (de) * 1974-03-28 1975-10-09 Gen Signal Corp Druckkompensierte hydraulische antriebseinrichtung mit einer mehrzahl von arbeitsfunktionen
US3934742A (en) * 1973-12-26 1976-01-27 Hydraulic Industries, Inc. Valve mechanism for automatic control of a number of fluid motors
US4095617A (en) * 1976-05-06 1978-06-20 Commercial Shearing, Inc. Control valves
US4215720A (en) * 1978-10-02 1980-08-05 General Signal Corporation Fluid control valve system
EP0438606A1 (de) * 1989-08-16 1991-07-31 Hitachi Construction Machinery Co., Ltd. Ventilanordnung und hydraulische schaltungsanordnung
US6295811B1 (en) * 1998-03-11 2001-10-02 Poclain Hydraulics Industrie Valve device for a hydraulic motor adapted to drive a high inertia mass
WO2006049347A1 (en) * 2004-11-08 2006-05-11 Kabushiki Kaisha Toyota Jidoshokki Flow rate switching type flow divider
CN108644418A (zh) * 2018-05-18 2018-10-12 宁波真格液压科技有限公司 一种用于农机的液压控制装置
CN109630489A (zh) * 2018-11-06 2019-04-16 襄阳航宇机电液压应用技术有限公司 一种电液压力伺服阀

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Publication number Priority date Publication date Assignee Title
JPS5148829A (ja) * 1974-10-23 1976-04-27 Kawasaki Heavy Ind Ltd Atsuryokuhoshotsukimaruchikontoroorubarubu
JPS5272074A (en) * 1975-12-06 1977-06-16 Kawasaki Heavy Ind Ltd Multicontrol valve available pressure compensation
JPS52114865A (en) * 1976-03-23 1977-09-27 Nippon Air Brake Co Flow divider for multiple type direction shifting valve
JPS61207007U (de) * 1985-06-18 1986-12-27
KR20160009617A (ko) 2013-05-07 2016-01-26 바이오 블라스트 파마 리미티드 트레할로스의 비경구 투여에 의한 단백질 응집 근병증 및 신경퇴행성 질환의 치료
CN104295553A (zh) * 2014-10-15 2015-01-21 恒天创丰重工有限公司 一种双退活塞液压阀组及双退活塞液压装置
CN104358728B (zh) * 2014-11-04 2016-05-04 浙江大学 将溢流功能集成于先导阀芯的二级负载控制阀
CN107387476B (zh) * 2017-09-08 2019-09-06 上海航天控制技术研究所 一种抗振型直动式球形溢流阀

Citations (9)

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US3179120A (en) * 1963-05-24 1965-04-20 Koehring Co Proportional flow divider
US3363516A (en) * 1966-01-03 1968-01-16 Webster Electric Co Inc Hydraulic system and valve assembly therefor
US3410295A (en) * 1966-02-21 1968-11-12 Gen Signal Corp Regulating valve for metering flow to two hydraulic circuits
US3411416A (en) * 1965-01-29 1968-11-19 Eton Yale & Towne Inc Adjustable, metered, directional flow control arrangement
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US3934742A (en) * 1973-12-26 1976-01-27 Hydraulic Industries, Inc. Valve mechanism for automatic control of a number of fluid motors
DE2513919A1 (de) * 1974-03-28 1975-10-09 Gen Signal Corp Druckkompensierte hydraulische antriebseinrichtung mit einer mehrzahl von arbeitsfunktionen
US4095617A (en) * 1976-05-06 1978-06-20 Commercial Shearing, Inc. Control valves
US4215720A (en) * 1978-10-02 1980-08-05 General Signal Corporation Fluid control valve system
EP0438606A1 (de) * 1989-08-16 1991-07-31 Hitachi Construction Machinery Co., Ltd. Ventilanordnung und hydraulische schaltungsanordnung
EP0438606A4 (en) * 1989-08-16 1993-07-28 Hitachi Construction Machinery Co., Ltd. Valve device and hydraulic circuit device
US6295811B1 (en) * 1998-03-11 2001-10-02 Poclain Hydraulics Industrie Valve device for a hydraulic motor adapted to drive a high inertia mass
WO2006049347A1 (en) * 2004-11-08 2006-05-11 Kabushiki Kaisha Toyota Jidoshokki Flow rate switching type flow divider
US20080271788A1 (en) * 2004-11-08 2008-11-06 Takeharu Matsuzaki Flow Rate Switching Type Flow Divider
CN108644418A (zh) * 2018-05-18 2018-10-12 宁波真格液压科技有限公司 一种用于农机的液压控制装置
CN108644418B (zh) * 2018-05-18 2019-12-24 江苏南京白马现代农业高新技术产业园有限公司 一种用于农机的液压控制装置
CN109630489A (zh) * 2018-11-06 2019-04-16 襄阳航宇机电液压应用技术有限公司 一种电液压力伺服阀
CN109630489B (zh) * 2018-11-06 2024-02-27 襄阳航宇机电液压应用技术有限公司 一种电液压力伺服阀

Also Published As

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DE2328658A1 (de) 1974-01-03
JPS5741609B2 (de) 1982-09-03
JPS4950521A (de) 1974-05-16
GB1387543A (en) 1975-03-19
DE2328658C2 (de) 1983-07-28

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