US3800669A - Control valve arrangement for a hydraulic drive - Google Patents

Control valve arrangement for a hydraulic drive Download PDF

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Publication number
US3800669A
US3800669A US00275829A US3800669DA US3800669A US 3800669 A US3800669 A US 3800669A US 00275829 A US00275829 A US 00275829A US 3800669D A US3800669D A US 3800669DA US 3800669 A US3800669 A US 3800669A
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Prior art keywords
valve
consumer
control
source
motor
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US00275829A
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English (en)
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J Distler
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Bosch Rexroth AG
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GL Rexroth GmbH
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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
    • 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
    • F15B11/17—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors using two or more pumps
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B62—LAND VEHICLES FOR TRAVELLING OTHERWISE THAN ON RAILS
    • B62D—MOTOR VEHICLES; TRAILERS
    • B62D11/00—Steering non-deflectable wheels; Steering endless tracks or the like
    • B62D11/02—Steering non-deflectable wheels; Steering endless tracks or the like by differentially driving ground-engaging elements on opposite vehicle sides
    • B62D11/06—Steering non-deflectable wheels; Steering endless tracks or the like by differentially driving ground-engaging elements on opposite vehicle sides by means of a single main power source
    • B62D11/10—Steering non-deflectable wheels; Steering endless tracks or the like by differentially driving ground-engaging elements on opposite vehicle sides by means of a single main power source using gearings with differential power outputs on opposite sides, e.g. twin-differential or epicyclic gears
    • B62D11/14—Steering non-deflectable wheels; Steering endless tracks or the like by differentially driving ground-engaging elements on opposite vehicle sides by means of a single main power source using gearings with differential power outputs on opposite sides, e.g. twin-differential or epicyclic gears differential power outputs being effected by additional power supply to one side, e.g. power originating from secondary power source
    • B62D11/18—Steering non-deflectable wheels; Steering endless tracks or the like by differentially driving ground-engaging elements on opposite vehicle sides by means of a single main power source using gearings with differential power outputs on opposite sides, e.g. twin-differential or epicyclic gears differential power outputs being effected by additional power supply to one side, e.g. power originating from secondary power source the additional power supply being supplied hydraulically
    • B62D11/183—Control systems therefor
    • E—FIXED CONSTRUCTIONS
    • E02—HYDRAULIC ENGINEERING; FOUNDATIONS; SOIL SHIFTING
    • E02F—DREDGING; SOIL-SHIFTING
    • E02F9/00—Component parts of dredgers or soil-shifting machines, not restricted to one of the kinds covered by groups E02F3/00 - E02F7/00
    • E02F9/20—Drives; Control devices
    • E02F9/22—Hydraulic or pneumatic drives
    • E02F9/2221—Control of flow rate; Load sensing arrangements
    • E02F9/2239—Control of flow rate; Load sensing arrangements using two or more pumps with cross-assistance
    • E—FIXED CONSTRUCTIONS
    • E02—HYDRAULIC ENGINEERING; FOUNDATIONS; SOIL SHIFTING
    • E02F—DREDGING; SOIL-SHIFTING
    • E02F9/00—Component parts of dredgers or soil-shifting machines, not restricted to one of the kinds covered by groups E02F3/00 - E02F7/00
    • E02F9/20—Drives; Control devices
    • E02F9/22—Hydraulic or pneumatic drives
    • E02F9/2278—Hydraulic circuits
    • E02F9/2292—Systems with two or more 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
    • F15B2211/20—Fluid pressure source, e.g. accumulator or variable axial piston pump
    • F15B2211/205—Systems with pumps
    • F15B2211/2053—Type of pump
    • F15B2211/20538—Type of pump constant capacity
    • 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
    • F15B2211/3056—Assemblies of multiple valves
    • F15B2211/3059—Assemblies of multiple valves having multiple valves for multiple output members
    • F15B2211/30595—Assemblies of multiple valves having multiple valves for multiple output members with additional valves between the groups of valves for multiple output members
    • 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
    • F15B2211/31—Directional control characterised by the positions of the valve element
    • F15B2211/3105—Neutral or centre positions
    • F15B2211/3116—Neutral or centre positions the pump port being open in the centre position, e.g. so-called open centre
    • 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

Definitions

  • First and second control units having first and second control valves, are provided for connecting first and second pumps with a plurality of hydraulic first and second consumer motors, respectively.
  • the units also include first and second switching valves which can be operated to supply pressure fluid from the respective first or second pumps to the second and first consumer motors, respectively, so that each consumer motor can be also operated with pressure fluid from both pumps.
  • CONTROL VALVE ARRANGEMENT FOR A HYDRAULIC DRIVE BACKGROUND OF THE INVENTION pumps are supplied through two control units totwo groups of hydraulic consumer motor which operate different parts of the machine. In the prior art, both pumps can be connected with a specific hydraulic motor. Due to this fact, the efficiency and power of a dredging machine can be substantially increased, and moreover the two pumps or other sources of pressure fluid, are economically used.
  • connection of one pressure source to a consumer motor which is already supplied with pressure fluid from another pressure fluid source is carried out in the prior art by connecting conduits for connecting the outlet of one control valve With the inlet of the followingcontrol valve which isassociated with the respective consumer motor.
  • the control valves must be large, since they have to control the double amount of pressure fluid. The cost of such an arrangement is high, and storage of different types of valves and additional tools are required.
  • At least one control unit of two control units which are connected with different pressure sources has an additional switching valve which can supply pressure fluid from one source to a consumer motor supplied with pressure fluid from another source by meansofa control valve. Due to the direct connection of the pressure source of the respective other control unit to the respective consumer motor, the control valve associated with the respective consumer motor, need not be enlarged, so that the control' valves and switching valves in each control unit may have the same size.
  • the additional-switching valve is the last valve in the respective control unit in downstream direction of the pressure fluid, and is connected in series with the preceeding control valve of the respective control unit.
  • the respective switching valve can only connect the associated pressure source with a consumer motor which is normally supplied by the other source, if the upstream control valves permit such a pressure fluid supply.
  • an upstream control valve of the same control unit is operated to supply pressure fluid, the flow of pressure fluid to the additional switching valve, which is arranged downstream of the respective control valves, is interrupted.
  • valve means which have a normal position of rest and two control positions, and whose valve body has six ports.
  • the control valves, but not the additional switching valves, of each control unit, are connected in parallel with each other between the respective pressure source and a low pressure discharge region such as a container with atmospheric pressure.
  • the additional switching valve has two control positions respectively connected with different consumer motors associated with the respective other control unit.
  • the respective additional shifting valve is associated with two hydraulic motors which are, in turn, supplied with pressure fluid from two control valves of the respective other control unit.
  • control units A particularly simple and advantageous construction of the control units is obtained if either chambers which communicate with the pressure source, and are located adjacent other annular chambers connected with consumer conduits, are connected by a channel which is located in another plane than a channel which is located between the chambers which can be connected with the pressure source. This results in the possibility to arrange the valve slide of the switching valve either in series or in parallel with the respective upstream slides of the control valves.
  • FIG. 1 is a diagrammatic view illustrating the hydraulic circuit of a control valve arrangement according to the invention which is particularly suited for a scoop dredging machine;
  • FIG. 2 is a longitudinal sectional view illustrating a control unit used in the embodiment of FIG. 1; and I FIG. 3 is a fragmentary sectional view illustrating a modification of the control unit shown in FIG. 2.
  • a first pump or other source of pressure fluid P supplies pressure fluid through a control unit I to hydraulic consumer motors F L and AT.
  • a second pump or'source of pressure fluid P suppli% pressure fluid through a second control unit II to hydraulic consumer motors F,-, SCH, and S.
  • Control unit I includes control valves 1, 2 and 3 and a switching valve 4, and control unit II includes control valves 5, 6, 7 and a switching valve 8.
  • the hydraulic motors are used for operating a scoop dredging ma chine.
  • Control valve 1 controls the left drive motor F
  • control valve 2 controls the scoop drive motor L
  • control valve 3 controls the boom drive motor AT.
  • the operating conduits A and B of the switching valve 4 are directly connected with the beam drive motor S, which is primarily controlled by the control valve 7 of the control unit II.
  • the control valve 5 of control unit II controls the right drive motor Fr
  • the control valve 6 controls the tilting drive motor SCH
  • control valve 7 controls the beam drive motor S independently of the positions of the control valves 5 and 6.
  • the additional switching valve 8 of control unit II is connected by its operating conduit A directly with a cylinder chamber 9 of the hydraulic consumer motor L, and operating conduit B is directly connected with the cylinder chamber 10 of the hydraulic consumer motor AT.
  • Each of the control valves has three positions a, b, c, for connecting three pairs of ports with different connections. All valves are shown in the normal position b in which connection between pump P, and pump P,, with the respective hydraulic motors is interrupted while the pumps P, and P,, are respectively connected with an open container T or other low pressure discharge area.
  • the operating conduits A and B of switching valve 4 are connected with the cylinder chambers S and S of the hydraulic motor S so that pressure fluid from the first pum p P, is supplied to the hydraulic motor S which is primarily driven by pressure fluid from the second pump P,,.
  • the switching valve 8 connects in the two control positions a and c, to the operating conduits A and B which supply pressure fluid from the pump P to a cylinder chamber 10 or 9 of the hydraulic motors AT, L which have a piston and piston rod 12 and 11.
  • hydraulic motors AT and L are primarily controlled by control valves 3 and 2 respectively which direct pressure fluid from pump P, to said motors.
  • control valve 3 When control valve 3 is shifted from the position b to the operative position a, and when the switching valve 8 is shifted from the position b to the control position a, the cylinder chamber 10 of the hydraullic consumer motor AT also receives pressure fluid from both pumps P, and P,, so that the piston rod 12 is moved at an increased speed.
  • consumer motors L, AT, and S can be either operated by pressure fluid from one pump only, or by pressure fluid from both pumps, depending on the position of the switching valves 4 and 8.
  • the pressure ports p of control valves 1, 2, 3 of control unit I are connected by a conduit 15 and branch conduits 15a, 15b directly with the pressure conduit 16 of the pump P,.
  • the pressure ports p of control valves 5, 6, 7 are connected in the same manner by a conduit 19 and branch conduits 19a, 19b with the pressure conduit 20 of the pump P,,.
  • the pressure ports p of the switching valves 4 and 8 are connected by conduits 17 and 21, respectively with connecting conduits l8 and 22, respectively which communicate with the pumps P, and P,, respectively. Consequently, the switching valves 4 and 8 can only be connected with the pumps P, and P,, when the control valves 1, 2, 3, and 5, 6, 7, respectively are in their normal positions of rest b.
  • Conduits 25 and 26 connect other ports of the control valves 1, 2, 3 and 6, 6 7 with the discharge conduits 27.
  • the control valves 1, 2, 3 are connected in parallel to pump P, and the control valves 5, 6, 7 are also connected in parallel with the pump P,,.
  • the control valves and the switching valve of each control unit I and II are connected in series so that the switching valves 4 or 8 are connected with the pump P, or pump P,, only when the control valves are in the normal position b. Switching valves 4 or 8 are separated from the pumps P, and P,,, respectively when one of the control valves 1, 2, 3 or 5, 6, 7 are shifted out of the normal position of rest.
  • the shifting of the switching valve 4 for supplying pressure fluid from pump P, to the consumer motor S in addition to the pressure fluid of pump P, takes place a small time period after the associated control valve 7 has been operated to drive consumer motor S with the fluid from pump P,,.
  • the switching valve 8 is operated after operation of the control valve 3, or of the control valve 2 to supply fluid from pump P,, additionally to consumer motors L and AT, respectively. Due to this arrangement, the time adjustment of the consumer motors is not disturbed by the adding of the flow of pressure fluid by the pump of the respective other control unit.
  • each control unit I or II has a cylindrical cast housing which is penetrated by four transverse bores 31, 32, 33 and 34.
  • the bores 32, 33 and 34 receive the valve slides 35, 36, 37 which establish together with ports in the cylindrical bores, the control valves 1, 2, 3, or 5, 6, 7, respectively described with reference to FIG. 1.
  • the valve slide 38 received by the cylinder bore 31 constitutes the switching valve 4 or 8, respectively.
  • the pressure fluid inlet P is provided at one end, and the discharge outlet T is leading to the discharge container T is provided at the other end of the housing 30.
  • the inlet P which is connected with one of thepumps P, and P opens into a cavity 40 which communicates with two longitudinal channels 41 and 42 which connect annular chambers 43, 44, 45 and 46, 47, 48, respectively. Consequently, these chambers are filled with the pressure fluid.
  • Other annular chambers 50, 51, 52 and 53, 54, 55 surrounding valve slides 37, 36, 35 are connected with operating conduits, not shown in FIG. 2 which'are connected with the consumer motors.
  • Two channels 56 and 57, communicating with dischargeoutlet T connect annular chambers 58, 59, 60, 61 and 62, 63, 64, 65, respectively.
  • the annular chambers to 77 are connected b channels 78 to 81, and portions of the valve bores. Consequently, the pressure inlet P is connected with the pressure outlet T and circulation in the control unit can take place'without pressure.
  • the valve slide 38 of theswitching valve 4 or 8 is surrounded by two annular chambers 87 and Y88 which respectively communicate with the operating conduits A and B which are connected with the respective consumer motors. Adjacent the annular chambers 86 and 87 other annular chambers 88 and 89 surround valve slide 38. Chambers 88 i and 89 are connected by a channel 90 which is located in another plane than the channel 81 which connects the chambers and 77. Channels 81 and are connected by a bore 91, so that in chambers 88, 89 the same pressure prevails as in channel 81, which is connected with the annular chamber 75.
  • valve slide 38 of a switching valve 4 or 8 When the valve slide 38 of a switching valve 4 or 8 is shifted in the direction of the arrow 93, the annular recesses of valve slide 38 connect the chamber 58 with chamber-86, and chamber-87 with chamber 89. At the same time, , the communication between chambers 76 and 77'is interrupted, so that the free flow from the high pressure chamber 40 to-the discharge outlet T is interrupted, whereby in channel 81 and chambers 88 and 8 9 the pressure is increased to the pressure of the respective pump.
  • the operating conduit communicating with chamber 87 is connected with thepump and due to the connection of the chamber 86 with the chamber 58 through the recess 94 of the valve slide 38, the operating conduit communieating with chamber 86 is connected with the discharge outlet T. l
  • connection between the annular chambers .75 and 74 is interrupted, so that channel 81 is separated from the pressure inlet P.
  • the connection between channel 81 and the pressure source is also interrupted if the valve slides 36 or 37 of the respective control valves are shifted to one of the end positions thereof.
  • valve slide 38 An effective control of the valve slide 38 is assured only in the illustrated position of the valve slides 35, 36, 37, since only in this position, the channel 81 which communicates with the annular chamber 77, is connected with the pressure inlet P.
  • the annular chambers 43, 44, 45 and 46, .47, 48 of the control valve slides 34, 36, 37 are directly connected by the housing channels 100, 101, 102, 103 and are connected by channels 41, 42 in any position of the control valve slides with the pressure inlet P, and are connected in parallel, so that an effective shifting of one of these control valve slides, independently of the position of another control valve slide, can be carried out. If more than one valve slide is operated, the pressure fluid supplied through the inlet P is divided between the respective consumer motors.
  • connecting channel 90 is not directly connected with the housing channel 81, but by means of a transverse bore 91, the housing chambers 88 and 89 of the shifting valve slide 38 can be also directly connected with the pressure inlet, so that they are connected in parallel to the pressure source, together with the respective chambers of the other control valve slides. It is only necessary to devise a connecting bore 104 between the annular chambers 45 or 48 and the channel 90, instead of connecting channel 81 with the channel 90.
  • connection between channel 81 and the connecting channel 90 is not obtained directly by a connecting bore, but indirectly by widened cylinder portion 98 forming an annular space 99 between valve slide 38 and portion 98.
  • the annular space 99 connects housing chamber 77, which is connected with channel 81, with the annular chamber 88 which is connected by the connecting channel 90 with annular chamber 89.
  • Control valve arrangement for a hydraulic drive comprising at least one hydraulic first consumer motor, at least one hydraulic second consumer motor; a first control unit including a first source of pressure fluid, and at least one first control valve for controlling the flow of fluid from said first source to said first consumer motor; a second control unit including a second source of pressure fluid, at least one second control valve for controlling the flow of fluid from said second source to said second consumer motor, a pressure conduit connected with said second source, and a switching valve located in said pressure conduit downstream of and connected in series with said second control valve, said switching valve being also connected with said first consumer motor and being movable between a normal position, and at least one control position for connecting said second source with said first consumer motor whereby said first consumer motor can be operated by pressure fluid from said first source alone or by pressure fluid from said first and said second sources; and another switching valve in said first control unit and connected with said second consumer motor of said second control unit, and movable between a normal position, and a control position for connecting said first source with said second consumer motor whereby said second consumer motor can be operated
  • Control valve arrangement as claimed in claim 1 wherein said first and second control valves are connected in parallel between the first and second source, respectively, and a low pressure discharge region.
  • Control valve arrangement as claimed in claim 1 and comprising means for operating said switching valve of said second control unit to move to said control position at a time different from the time at which said first control valve is operated.
  • Control valve arrangement as claimed in claim 1 comprising twofirst consumer motors; wherein said firstcontrol unit includes two first control valves for controlling the flows from said first source to.said first consumer motors, respectively, each first control valve being movable between an inoperative position and at least one operative position; and wherein said switching valve has two control positions respectively directly connected with said two first consumer motors.
  • At least said second control unit includes a substantially cylindrical valve body formed with an inlet for pressure fluid at one end, and with an outlet to a low pressure region at the other end, with consumer conduits connected with said second consumer motor, with diametrical valve cylinder bores, and with duct means connecting said inlet, said outlet, said consumer conduits and said bores, each valve of said control valves and switching valve including a valve slide located in one of said diametrical valve cylinder bores and having piston portions, said valve body having annular chambers cooperating with said piston. portions connected with said duct means and surrounding said valve slides for establishing different connections of said duct means between said inlet and outlet, and said consumer conduits when said valve slides are displaced.
  • Control valve arrangement for a hydraulic drive comprising at least one hydraulic first consumer motor and at least one hydraulic second consumer motor; a first control unit including a first source of pressure fluid and at least one first control valve for controlling said flow of fluid from said first source to said first consumer motor; and a second control unit including a second source of pressure fluid, at least one second control valve for controlling the flow of fluid from said second source to said second consumer motor, and a switching valve connected with said first consumer motor and movable between a normal position, and at least one control position for connecting said second source with said first consumer motor whereby said first consumer motor can be operated by pressure fluid from said first source alone, or by pressure fluid from said first and said second sources; at least said second control unit including a substantially cylindrical valve body formed with an inlet for pressure fluid at one end, and with an outlet to a low pressure region at the other end, with consumer conduits connected with said second consumer motor, with diametrical valve cylinder bores, and with duct means connecting said inlet, said outlet, said conduits and said bores, each valve of said control

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mining & Mineral Resources (AREA)
  • Mechanical Engineering (AREA)
  • Fluid Mechanics (AREA)
  • Physics & Mathematics (AREA)
  • Civil Engineering (AREA)
  • Structural Engineering (AREA)
  • Automation & Control Theory (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Transportation (AREA)
  • Fluid-Pressure Circuits (AREA)
  • Multiple-Way Valves (AREA)
  • Operation Control Of Excavators (AREA)
US00275829A 1971-08-04 1972-07-27 Control valve arrangement for a hydraulic drive Expired - Lifetime US3800669A (en)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE2138986A DE2138986C3 (de) 1971-08-04 1971-08-04 Steuerventileinrichtung für mehrere hydraulische Antriebe

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US3926124A (en) * 1974-07-25 1975-12-16 Abex Corp Railroad car retarders
US3980000A (en) * 1973-08-24 1976-09-14 Mitsubishi Jukogyo Kabushiki Kaisha Control system for a hydraulic clamping device
US4073141A (en) * 1977-03-17 1978-02-14 Caterpillar Tractor Co. Fluid control system with priority flow
US4078681A (en) * 1976-08-24 1978-03-14 Caterpillar Tractor Co. Dual pump hydraulic control system with predetermined flow crossover provision
US4207740A (en) * 1979-06-12 1980-06-17 Akermans Verkstad Ab Valve blocks, in particular for hydraulic excavators
EP0028448A2 (de) * 1979-11-01 1981-05-13 Caterpillar Tractor Co. Steuerungssystem für hydraulische Motoren
US4342254A (en) * 1973-12-22 1982-08-03 O & K Orenstein & Koppel Aktiengesellschaft Circuit for hydrostatically operable devices
US4488365A (en) * 1982-12-06 1984-12-18 Jensen Corporation Hydraulic system for laundry flatwork ironer
US4534268A (en) * 1981-07-10 1985-08-13 Hitachi Construction Machinery Co., Ltd. Hydraulic fluid circuit of hydraulic shovel
US4875337A (en) * 1986-09-27 1989-10-24 Hitachi Construction Machinery Co., Ltd. Construction machine dual-dump hydraulic circuit with piloted arm-boom cylinder supply priority switching valves
US5946910A (en) * 1995-05-17 1999-09-07 Komatsu Ltd. Hydraulic circuit for hydraulically driven working vehicle
US6164069A (en) * 1997-06-23 2000-12-26 Hitachi Construction Machinery Co., Ltd. Hydraulic drive system for construction machine
US20030167762A1 (en) * 2002-03-07 2003-09-11 Leon's Mfg. Company Inc. Loader drive system
WO2005015030A1 (de) * 2003-08-08 2005-02-17 Cnh Baumaschinen Gmbh Hydraulisches steuersystem für baumaschinen, insbesondere für bagger
RU2506373C2 (ru) * 2009-07-28 2014-02-10 Виталий Иванович Колтыга Канал встречных потоков многопоточного гидропривода
US20150059331A1 (en) * 2012-06-15 2015-03-05 Sumitomo(S.H.I.) Construction Machinery Co., Ltd. Hydraulic circuit for construction machine and control device therefor
US20150059332A1 (en) * 2012-06-15 2015-03-05 Sumitomo(S.H.I.) Construction Machinery Co., Ltd. Hydraulic circuit for construction machine
US20150354167A1 (en) * 2012-12-26 2015-12-10 Kobelco Construction Machinery Co., Ltd. Hydraulic control device and construction machine with same

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DE4243289C1 (de) * 1992-12-21 1994-02-17 Hemscheidt Maschf Hermann Steuergerät für ein hydraulisches Schreitausbaugestell
US6892535B2 (en) * 2002-06-14 2005-05-17 Volvo Construction Equipment Holding Sweden Ab Hydraulic circuit for boom cylinder combination having float function

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US2103530A (en) * 1935-09-05 1937-12-28 Maine Steel Inc System of equalizing the lifting speed of differently loaded hydraulic jacks
US3146593A (en) * 1960-04-18 1964-09-01 Parker Hannifin Corp Dual pump system and control valve assembly therefor
US3258926A (en) * 1963-08-01 1966-07-05 Caterpillar Tractor Co Hydraulic control circuit for selfloading scrapers
US3208221A (en) * 1963-09-30 1965-09-28 Drott Mfg Corp Hydraulic operating apparatus
US3360925A (en) * 1966-02-03 1968-01-02 Int Harvester Co Multiple speed hydraulic control system
US3350986A (en) * 1966-03-17 1967-11-07 Caterpillar Tractor Co Two-pump supply for hydraulic circuits having different flow requirements
US3543646A (en) * 1967-11-24 1970-12-01 Mitsubishi Heavy Ind Ltd Hydraulic system

Cited By (26)

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US3980000A (en) * 1973-08-24 1976-09-14 Mitsubishi Jukogyo Kabushiki Kaisha Control system for a hydraulic clamping device
US4342254A (en) * 1973-12-22 1982-08-03 O & K Orenstein & Koppel Aktiengesellschaft Circuit for hydrostatically operable devices
US3926124A (en) * 1974-07-25 1975-12-16 Abex Corp Railroad car retarders
US4078681A (en) * 1976-08-24 1978-03-14 Caterpillar Tractor Co. Dual pump hydraulic control system with predetermined flow crossover provision
US4073141A (en) * 1977-03-17 1978-02-14 Caterpillar Tractor Co. Fluid control system with priority flow
US4207740A (en) * 1979-06-12 1980-06-17 Akermans Verkstad Ab Valve blocks, in particular for hydraulic excavators
EP0028448A2 (de) * 1979-11-01 1981-05-13 Caterpillar Tractor Co. Steuerungssystem für hydraulische Motoren
EP0028448A3 (de) * 1979-11-01 1982-03-31 Caterpillar Tractor Co. Steuerungssystem für hydraulische Motoren
US4534268A (en) * 1981-07-10 1985-08-13 Hitachi Construction Machinery Co., Ltd. Hydraulic fluid circuit of hydraulic shovel
US4488365A (en) * 1982-12-06 1984-12-18 Jensen Corporation Hydraulic system for laundry flatwork ironer
US4875337A (en) * 1986-09-27 1989-10-24 Hitachi Construction Machinery Co., Ltd. Construction machine dual-dump hydraulic circuit with piloted arm-boom cylinder supply priority switching valves
US5946910A (en) * 1995-05-17 1999-09-07 Komatsu Ltd. Hydraulic circuit for hydraulically driven working vehicle
US6164069A (en) * 1997-06-23 2000-12-26 Hitachi Construction Machinery Co., Ltd. Hydraulic drive system for construction machine
US20030167762A1 (en) * 2002-03-07 2003-09-11 Leon's Mfg. Company Inc. Loader drive system
US6651426B2 (en) * 2002-03-07 2003-11-25 Leon's Mfg. Company, Inc. Loader drive system
WO2005015030A1 (de) * 2003-08-08 2005-02-17 Cnh Baumaschinen Gmbh Hydraulisches steuersystem für baumaschinen, insbesondere für bagger
US20070056437A1 (en) * 2003-08-08 2007-03-15 Volker Bosebeck Hydraulic control system for construction vehicle, particularly excavators
US7475502B2 (en) 2003-08-08 2009-01-13 Cnh Baumaschinen Gmbh Hydraulic control system for construction vehicle, particularly excavators
RU2506373C2 (ru) * 2009-07-28 2014-02-10 Виталий Иванович Колтыга Канал встречных потоков многопоточного гидропривода
US20150059331A1 (en) * 2012-06-15 2015-03-05 Sumitomo(S.H.I.) Construction Machinery Co., Ltd. Hydraulic circuit for construction machine and control device therefor
US20150059332A1 (en) * 2012-06-15 2015-03-05 Sumitomo(S.H.I.) Construction Machinery Co., Ltd. Hydraulic circuit for construction machine
US9903097B2 (en) * 2012-06-15 2018-02-27 Sumitomo(S.H.I.) Construction Machinery Co., Ltd. Hydraulic circuit for construction machine
US9932994B2 (en) * 2012-06-15 2018-04-03 Sumitomo(S.H.I.) Construction Machinery Co., Ltd. Hydraulic circuit for construction machine and control device therefor
US10443213B2 (en) 2012-06-15 2019-10-15 Sumitomo(S.H.I.) Construction Machinery Co., Ltd. Hydraulic circuit for construction machine
US20150354167A1 (en) * 2012-12-26 2015-12-10 Kobelco Construction Machinery Co., Ltd. Hydraulic control device and construction machine with same
US10047494B2 (en) * 2012-12-26 2018-08-14 Kobelco Construction Machinery Co., Ltd. Hydraulic control device and construction machine with same

Also Published As

Publication number Publication date
DE2138986B2 (de) 1978-01-05
DE2138986C3 (de) 1978-09-07
DE2138986A1 (de) 1973-02-15

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