EP1598561B1 - Hydraulisches Steuergerät - Google Patents

Hydraulisches Steuergerät Download PDF

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Publication number
EP1598561B1
EP1598561B1 EP20050010782 EP05010782A EP1598561B1 EP 1598561 B1 EP1598561 B1 EP 1598561B1 EP 20050010782 EP20050010782 EP 20050010782 EP 05010782 A EP05010782 A EP 05010782A EP 1598561 B1 EP1598561 B1 EP 1598561B1
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EP
European Patent Office
Prior art keywords
circuit group
flow passage
switching valve
pump
actuator
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired - Lifetime
Application number
EP20050010782
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English (en)
French (fr)
Other versions
EP1598561A3 (de
EP1598561A2 (de
Inventor
Atsushi c/o Kayaba Industry Co. Ltd. Fujii
Takeshi c/o Kayaba Industry Co. Ltd. Kanno
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.)
KYB Corp
Original Assignee
Kayaba Industry Co Ltd
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Kayaba Industry Co Ltd filed Critical Kayaba Industry Co Ltd
Publication of EP1598561A2 publication Critical patent/EP1598561A2/de
Publication of EP1598561A3 publication Critical patent/EP1598561A3/de
Application granted granted Critical
Publication of EP1598561B1 publication Critical patent/EP1598561B1/de
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
    • 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
    • F15B11/167—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors with sensing of servomotor demand or load using pilot pressure to sense the demand
    • 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
    • E02F9/2282—Systems using center bypass type changeover valves
    • 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
    • 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
    • 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
    • F15B2211/30—Directional control
    • F15B2211/31—Directional control characterised by the positions of the valve element
    • F15B2211/3122—Special positions other than the pump port being connected to working ports or the working ports being connected to the return line
    • F15B2211/3127—Floating position connecting the working ports and 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
    • F15B2211/30—Directional control
    • F15B2211/32—Directional control characterised by the type of actuation
    • F15B2211/329—Directional control characterised by the type of actuation actuated by fluid pressure
    • 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
    • F15B2211/353—Flow control by regulating means in return line, i.e. meter-out 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
    • F15B2211/70—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
    • F15B2211/78—Control of multiple output members
    • F15B2211/781—Control of multiple output members one or more output members having priority

Definitions

  • the present invention relates to a hydraulic control apparatus according to the preamble of claim 1.
  • the hydraulic control apparatus is provided with a plurality of hydraulic circuit groups and is for use of a construction machine such as a hydraulic shovel.
  • the hydraulic control apparatus is provided with a first to a third pump P1 to P3.
  • the first to the third pump P1 to P3 each are connected to a first circuit system to a third circuit system 50a to 50c.
  • a first to a third switching valve 11 to 13 of open center type are connected to a first supply flow passage 1 connected to the first pump P1.
  • the first pump P1 is communicated via a first neutral passage 2 with a tank flow passage 10 connected to a side of a tank (not shown).
  • a fourth to a sixth switching valve 14 to 16 of open center type are connected to a second supply flow passage 4 connected to the second pump P2.
  • the fourth to the sixth switching valve 14 to 16 are in a neutral position as shown in FIG. 2, the second pump P2 is communicated via a second neutral flow passage 5 with the tank flow passage 10.
  • the sixth switching valve 16 is an auxiliary switching valve, which is beforehand prepared for a construction machine (construction vehicle) using the special actuator 70. Namely in a case where only two actuators are controlled in the second circuit system 50b, the auxiliary switching valve 16 are not used and on the other hand, in a case where the special actuator 70 is added to the two actuators to provide three actuators in total connected to the second circuit system 50b, the special actuator 70 is connected to the auxiliary switching valve 16. And the special actuator 70 is adapted to be controlled by the auxiliary switching valve 16. Since the special actuator 70 is not regularly provided, the maximum discharge amount of the second pump P2 is set based upon the maximum amount demanded by the two actuators 74 and 75, which are connected respectively to the fourth and fifth switching valves 14 and 15.
  • a seventh to a ninth switching valve 17 to 19 of open center type are connected to a third supply flow passage 7 connected to the third pump P3.
  • the seventh to the ninth switching valve 17 to 19 are in a neutral position as shown in FIG. 2, the third pump P3 is communicated via a third neutral flow passage 8 with the downstream side.
  • the downstream side of the third neutral flow passage 8 is connected to the second neutral flow passage 5 of the second circuit system 50b in order to converge and supply the hydraulic oil from the third circuit system 50c to the second circuit system 50b as needed.
  • a hydraulic pilot type of convergence switching valve 20 is provided midway along a flow passage connecting the third neutral flow passage 8 to the second neutral flow passage 5.
  • the convergence switching valve 20 is switched by an operator.
  • the convergence switching valve 20 When the convergence switching valve 20 is in a closed position, the third neutral flow passage 8 is communicated with the tank flow passage 10 and disconnected to the second neutral flow passage 5, so that the discharge oil from the third pump P3 is not supplied to the second circuit system 50b.
  • the convergence switching valve 20 when the convergence switching valve 20 is switched to an opened position in FIG. 2, the third neutral flow passage 8 is communicated with the second neutral flow passage 5 to supply the hydraulic oil from the third pump P3 to the second circuit system 50b.
  • Provision of such convergence switching valve 20 prevents a flow amount of hydraulic oil supplied to the special actuator 70 connected to the auxiliary switching valve 16 from being insufficient.
  • the hydraulic oil discharged from the second pump P2 is supplied to the auxiliary switching valve 16 and the maximum discharge amount of the second pump P2 is set based upon the maximum amount demanded from the actuators 74 and 75 connected respectively to the fourth and fifth switching valves 14 and 15. Accordingly, when the actuator 70 connected to the auxiliary switching valve 16 is activated, the special actuator 16 is possibly in short supply of the hydraulic oil. Therefore, in such case, the convergence switching valve 20 converges the discharge oil from the third pump P3 into the discharge oil from the second pump P2, thus compensating for the short supply of the hydraulic oil.
  • JP 03 260 401 A refers to a hydraulic driving unit for a civil engineering and construction machine.
  • the document discloses a first circuit group supplied by a first pump and a second circuit group supplied by a second pump. Moreover, the document shows a connecting pipeline and a control valve.
  • the pumps P1 to P3 are driven by an engine (not shown) and, for example the pump P3 is controlled to maintain a constant relation between a pump discharge pressure and a pump flow amount so that horse power of the pump P3 does not go beyond a constant value.
  • the present invention has an object of solving the foregoing problems.
  • a hydraulic control apparatus in the present invention is provided with at least a first circuit group and a second circuit group, each including a switching valve to switch supply of operating oil to an actuator, an auxiliary switching valve disposed in the first circuit group to switch supply of operating oil to an auxiliary actuator, at least two pumps supplying the operating oil respectively to the first circuit group and the second circuit group, a convergence flow passage to converge the hydraulic oil from the second circuit group to the first circuit group, a drain flow passage branched from the convergence flow passage to relieve the operating oil to a side of a reservoir, and a control valve interposed in the branched portion of the drain flow passage, wherein the control valve is operated to be switched in accordance with a difference in pressures between the first circuit group and the second circuit group, and introduces the operating oil of the second circuit group to the drain flow passage when supply pressure of the first circuit group is higher than supply pressure of the second circuit group.
  • FIG. 1 shows a circuit view of a hydraulic control apparatus in a hydraulic shovel.
  • components substantially identical to those in FIG. 2 are referred to as identical numerals.
  • a hydraulic control apparatus of the present invention is provided with a first to a third pump P1 to P3, which are connected respectively to a first to a third circuit system 60A to 60C.
  • the first circuit system 60A and the second circuit system 60B are defined as a first circuit group and the third circuit system 60C is defined as a second circuit group.
  • a first switching valve to a third switching valve 11 to 13 of open center type are connected to a first supply flow passage 1 connected to the first pump P1.
  • the first to the third switching valve 11 to 13 are in a neutral position as shown in FIG. 1, the first pump P1 is communicated via a first neutral flow passage 2 with a tank flow passage 10.
  • hydraulic oil (the operating oil) from the first pump P1 is supplied directly to an actuator (for example, left hand driving motor for vehicle traveling) 31 connected to the switching valve 11.
  • hydraulic oil is similarly supplied via a first parallel flow passage 3 to an actuator 32 and an actuator 33 each connected to the switching valves 12 and 13, namely a cylinder 32 for boom driving connected to the second switching valve 12 and a cylinder 33 for bucket driving connected to the third switching valve 13.
  • the maximum discharge amount of the first pump P1 is set based upon the maximum amount demanded by three actuators 31 to 33 connected respectively to the first switching valve to the third switching valve 11 to 13.
  • a relief valve 21 opens when a circuit pressure (discharge pressure in the pump P1) in the first supply passage 1 rises up to more than a predetermined value to release the pressure, and each of pilot circuits Pa1, Pb1, Pa2, Pb2, Pa3, pb3 supplies a pilot pressure to switch the switching valves 11 to 13.
  • a DR indicates a drain circuit.
  • a fourth to a sixth switching valve 14 to 16 of open center type are connected to a second supply flow passage 4 connected to the second pump P2.
  • the second pump P2 When the fourth to the sixth switching valve 14 to 16 are in a neutral position as shown in FIG. 1, the second pump P2 is communicated via a second neutral flow passage 5 with the tank flow passage 10. And when the fourth switching valve 14 is switched from the neutral position, the hydraulic oil (the operating oil) from the second pump P2 is supplied directly to an actuator (right hand driving motor for vehicle traveling) 34 connected to the fourth switching valve 14. And when either one of the fifth switching valve 15 and the sixth switching valve 16 is switched from the neutral position, the hydraulic oil is similarly supplied via a second parallel flow passage 6 to an actuator 35 and an actuator 36, namely a cylinder 35 for arm driving and a special actuator 30 each connected to the switching valves 15 and 16.
  • an actuator 35 and an actuator 36 namely a cylinder 35 for arm driving and a special actuator 30 each connected to the switching valves 15 and 16.
  • the sixth switching valve 16 serves as an auxiliary switching valve to control drive of the special actuator 30, which includes, for example, a breaker, a drilling nail or the like.
  • the maximum discharge amount of the second pump P2 is set based upon the maximum amount demanded by the two actuators 34 and 35 connected respectively to the fourth and fifth switching valves 14 and 15.
  • a relief valve 22 opens when a circuit pressure, namely a discharge pressure in the pump P2 in the second supply flow passage 4 rises up to more than a predetermined value to release the pressure and each of pilot circuits Pa4, Pb4, Pa5, Pb5, Pa6, pb6 supplies a pilot pressure to switch the switching valves 14 to 16.
  • a seventh to a ninth switching valve 17 to 19 of open center type are connected to a third supply flow passage 7 connected to the third pump P3.
  • the seventh to the ninth switching valve 17 to 19 are in a neutral position as shown in FIG. 1, the third pump P3 is communicated via a third neutral flow passage 8 with a downstream passage 40.
  • the hydraulic oil from the third pump P3 is supplied directly to an actuator (driving motor for vehicle chassis turning) 37 connected to the switching valve 17.
  • the hydraulic oil is similarly supplied via a third parallel flow passage 9 to an actuator 38 and an actuator 39, namely a cylinder 38 for blade driving connected to the eighth switching valve 18 and a cylinder 39 for swing driving connected the ninth switching valve 19.
  • the maximum discharge amount of the third pump P3 is set based upon the maximum amount demanded by the three actuators 37 to 39 connected respectively to the seventh to the ninth switching valve 17 to 19.
  • a relief valve 23 opens when a circuit pressure in the third supply flow passage 7, namely a discharge pressure of the pump P3 rises up to more than a predetermined value to release the pressure and each of pilot circuits Pa7, Pb7, Pa8, Pb8,Pa9, pb9 supplies a pilot pressure to switch the switching valves 17 to 19.
  • downstream passage 40 of the third neutral flow passage 8 is connected to a convergence flow passage 41 of the second circuit system 60B in order to converge and supply the hydraulic oil from the third circuit system 60C to the second circuit system 60B as needed.
  • the convergence flow passage 41 is connected to the second neutral flow passage 5 upstream of the auxiliary switching valve 16 and the second parallel flow passage 6.
  • a drain flow passage 43 is provided to be branched from the downstream passage 40 of the third circuit system 60C and a switching control valve 42 is provided in a branch portion between the convergence flow passage 41 and the drain flow passage 43 for passage switching.
  • the switching control valve 42 connects the downstream passage 40 of the third circuit system 60C to the drain flow passage 43 when the discharge pressure in the second pump P2 of the second circuit system 60B is by a predetermined pressure higher than the discharge pressure in the third pump P3 of the third circuit system 60C and on the other hand, when by a predetermined pressure lower than that, connects the downstream passage 40 of the third circuit system 60C to the convergence flow passage 41.
  • the switching control valve 42 is adapted to serve as a pilot pressure switching valve to which a pilot passage 45 for introducing the discharge pressure from the third pump P3 as a pilot pressure and a pilot passage 46 for introducing the discharge pressure from the second pump P2 as a pilot pressure are connected, and is operated to be switched due to receiving these pilot pressures.
  • the discharge pressure in the third pump P3 rises up, the discharge pressure does not reach a predetermined pressure of the relief valve 23, so that the relief valve 23 does not open.
  • a driving loss of the third pump p3 caused by the relief of the discharge pressure in the third pump P3 by the relief valve 23 can be avoided to reduce a load of the engine for driving the pump, thus improving a fuel economy.
  • the hydraulic pressure in the third pump P3 can be appropriately supplied by the operating oil converged into the actuator 30 connected to the auxiliary switching valve 16, thereby securing a desired operation of the actuator 30.
  • the first to the third circuit system 60A to 60C are provided, but the present invention may be provided with at least two circuit systems 60B and 60C.
  • the hydraulic oil may be supplied from the one circuit system 60C to the other circuit system 60B provided with the auxiliary switching valve 16.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Mining & Mineral Resources (AREA)
  • Civil Engineering (AREA)
  • Structural Engineering (AREA)
  • Mechanical Engineering (AREA)
  • Fluid-Pressure Circuits (AREA)
  • Operation Control Of Excavators (AREA)

Claims (4)

  1. Hydraulische Steuervorrichtung, die umfasst:
    wenigstens eine erste Kreisgruppe (60A, 60B) und eine zweite Kreisgruppe (60C), die jeweils ein Umschaltventil (11-19) zum Umschalten einer Zufuhr von Betriebsöl zu einem Stellglied (31-39) enthalten;
    ein Zusatz-Umschaltventil (16), das in der ersten Kreisgruppe (60B) angeordnet ist, um Zufuhr des Betriebsöls zu einem Zusatz-Stellglied (30) umzuschalten;
    wenigstens zwei Pumpen (P1-P3), die das Betriebsöl der ersten Kreisgruppe (60A, 60B) bzw. der zweiten Kreisgruppe (60C) zuführen;
    einen Zusammenführ-Strömungsweg (40, 41), der das Betriebsöl von der zweiten Kreisgruppe (60C) zu der ersten Kreisgruppe (60B) zusammenführt;
    einen Ablass-Strömungsweg (43), der von dem Zusammenführ-Strömungsweg abzweigt, um das Betriebsöl zu einer Seite eines Tanks abzugeben; und
    ein Umschalt-Steuerventil (42), das in den abgezweigten Abschnitt des Ablass-Strömungsweges (43) eingesetzt ist,
    dadurch gekennzeichnet, dass:
    das Umschalt-Steuerventil (42) so betrieben wird, dass es entsprechend einer Differenz der Drücke zwischen der ersten Kreisgruppe (60B) und der zweiten Kreisgruppe (60C) umgeschaltet wird, und das Betriebsöl der zweiten Kreisgruppe (60C) in den Ablass-Strömungsweg (43) einleitet, wenn Zufuhrdruck der ersten Kreisgruppe (60B) höher ist als Zufuhrdruck der zweiten Kreisgruppe (60C).
  2. Hydraulische Steuervorrichtung nach Anspruch 1, wobei
    das Umschalt-Steuerventil (42) so eingerichtet ist, dass es das Betriebsöl in dem Zusammenführ-Strömungsweg in den Ablass-Strömungsweg (43) einleitet, wenn der Zufuhrdruck der ersten Kreisgruppe um einen vorgegebenen Wert höher ist als der Zufuhrdruck der zweiten Kreisgruppe (60C), und ansonsten das Betriebsöl von dem Zuführ-Strömungsweg in die erste Kreisgruppe einleitet.
  3. Hydraulische Steuervorrichtung nach Anspruch 2, wobei:
    das Umschalt-Steuerventil (42) so eingerichtet ist, dass es als Pilotdruck-Umschaltventil dient, das so betrieben wird, dass es durch den Zufuhrdruck der ersten Kreisgruppe und den Zufuhrdruck der zweiten Kreisgruppe als einem Pilotdruck umgeschaltet wird.
  4. Hydraulische Steuervorrichtung nach Anspruch 1, wobei:
    jedes der Umschaltventile (11-19) in der ersten Kreisgruppe (60A, 60B) und der zweiten Kreisgruppe (60C) ein Umschaltventil vom Typ mit offener Mitte enthält und eine Vielzahl der Umschaltventile in Reihe in der ersten Kreisgruppe und der zweiten Kreisgruppe angeordnet sind.
EP20050010782 2004-05-19 2005-05-18 Hydraulisches Steuergerät Expired - Lifetime EP1598561B1 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2004148967 2004-05-19
JP2004148967A JP4139352B2 (ja) 2004-05-19 2004-05-19 油圧制御装置

Publications (3)

Publication Number Publication Date
EP1598561A2 EP1598561A2 (de) 2005-11-23
EP1598561A3 EP1598561A3 (de) 2005-12-14
EP1598561B1 true EP1598561B1 (de) 2007-12-26

Family

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Family Applications (1)

Application Number Title Priority Date Filing Date
EP20050010782 Expired - Lifetime EP1598561B1 (de) 2004-05-19 2005-05-18 Hydraulisches Steuergerät

Country Status (4)

Country Link
EP (1) EP1598561B1 (de)
JP (1) JP4139352B2 (de)
CN (1) CN100516555C (de)
DE (1) DE602005003980T2 (de)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US9290912B2 (en) 2012-10-31 2016-03-22 Caterpillar Inc. Energy recovery system having integrated boom/swing circuits

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US7481052B2 (en) 2006-04-17 2009-01-27 Clark Equipment Company Fluid circuit with multiple flows from a series valve
KR100906228B1 (ko) * 2007-03-30 2009-07-07 볼보 컨스트럭션 이키프먼트 홀딩 스웨덴 에이비 건설중장비용 유압회로
CN101929177A (zh) * 2008-07-02 2010-12-29 沃尔沃建造设备控股（瑞典）有限公司 用于挖掘机的液压控制系统
JP5188444B2 (ja) * 2009-04-23 2013-04-24 カヤバ工業株式会社 作業機の液圧駆動装置
JP6015157B2 (ja) 2011-07-01 2016-10-26 コベルコ建機株式会社 建設機械
US8944103B2 (en) 2011-08-31 2015-02-03 Caterpillar Inc. Meterless hydraulic system having displacement control valve
US8966892B2 (en) 2011-08-31 2015-03-03 Caterpillar Inc. Meterless hydraulic system having restricted primary makeup
US8863509B2 (en) 2011-08-31 2014-10-21 Caterpillar Inc. Meterless hydraulic system having load-holding bypass
US9057389B2 (en) 2011-09-30 2015-06-16 Caterpillar Inc. Meterless hydraulic system having multi-actuator circuit
US8966891B2 (en) 2011-09-30 2015-03-03 Caterpillar Inc. Meterless hydraulic system having pump protection
US9151018B2 (en) 2011-09-30 2015-10-06 Caterpillar Inc. Closed-loop hydraulic system having energy recovery
US9051714B2 (en) 2011-09-30 2015-06-09 Caterpillar Inc. Meterless hydraulic system having multi-actuator circuit
US8984873B2 (en) 2011-10-21 2015-03-24 Caterpillar Inc. Meterless hydraulic system having flow sharing and combining functionality
US8910474B2 (en) 2011-10-21 2014-12-16 Caterpillar Inc. Hydraulic system
US8978373B2 (en) 2011-10-21 2015-03-17 Caterpillar Inc. Meterless hydraulic system having flow sharing and combining functionality
US8973358B2 (en) 2011-10-21 2015-03-10 Caterpillar Inc. Closed-loop hydraulic system having force modulation
US9080310B2 (en) 2011-10-21 2015-07-14 Caterpillar Inc. Closed-loop hydraulic system having regeneration configuration
US8943819B2 (en) 2011-10-21 2015-02-03 Caterpillar Inc. Hydraulic system
US9068578B2 (en) 2011-10-21 2015-06-30 Caterpillar Inc. Hydraulic system having flow combining capabilities
US8978374B2 (en) 2011-10-21 2015-03-17 Caterpillar Inc. Meterless hydraulic system having flow sharing and combining functionality
US8893490B2 (en) 2011-10-21 2014-11-25 Caterpillar Inc. Hydraulic system
US8919114B2 (en) 2011-10-21 2014-12-30 Caterpillar Inc. Closed-loop hydraulic system having priority-based sharing
JP5901378B2 (ja) * 2012-03-23 2016-04-06 Ｋｙｂ株式会社 走行制御バルブ
US9279236B2 (en) 2012-06-04 2016-03-08 Caterpillar Inc. Electro-hydraulic system for recovering and reusing potential energy
JP6012021B2 (ja) * 2012-11-07 2016-10-25 Ｋｙｂ株式会社 パワーショベルの流体圧制御装置
JP6004900B2 (ja) 2012-11-07 2016-10-12 Ｋｙｂ株式会社 パワーショベルの流体圧制御装置
US9290911B2 (en) 2013-02-19 2016-03-22 Caterpillar Inc. Energy recovery system for hydraulic machine
JP6196499B2 (ja) * 2013-08-20 2017-09-13 ナブテスコ株式会社 建設機械の多連方向切換弁
JP6231949B2 (ja) * 2014-06-23 2017-11-15 株式会社日立建機ティエラ 建設機械の油圧駆動装置
JP6555709B2 (ja) * 2015-04-17 2019-08-07 キャタピラー エス エー アール エル 流体圧回路および作業機械
JP6898834B2 (ja) * 2017-11-15 2021-07-07 Ｋｙｂ−Ｙｓ株式会社 流体圧制御装置
CN111197603B (zh) * 2020-03-05 2021-11-30 三一汽车起重机械有限公司 分合流控制模块、双主泵供油系统、液压系统及工程机械

Family Cites Families (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH03260401A (ja) * 1990-03-09 1991-11-20 Hitachi Constr Mach Co Ltd 土木・建設機械の油圧駆動装置
JP4548959B2 (ja) * 2001-03-19 2010-09-22 カヤバ工業株式会社 油圧制御装置
JP4137431B2 (ja) * 2001-11-09 2008-08-20 ナブテスコ株式会社 油圧回路

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US9290912B2 (en) 2012-10-31 2016-03-22 Caterpillar Inc. Energy recovery system having integrated boom/swing circuits

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JP4139352B2 (ja) 2008-08-27
DE602005003980T2 (de) 2008-04-30
JP2005331011A (ja) 2005-12-02
CN1699761A (zh) 2005-11-23
CN100516555C (zh) 2009-07-22
DE602005003980D1 (de) 2008-02-07
EP1598561A3 (de) 2005-12-14
EP1598561A2 (de) 2005-11-23

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