CN1699761A - Hydraulic control apparatus - Google Patents

Hydraulic control apparatus Download PDF

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Publication number
CN1699761A
CN1699761A CN 200510072761 CN200510072761A CN1699761A CN 1699761 A CN1699761 A CN 1699761A CN 200510072761 CN200510072761 CN 200510072761 CN 200510072761 A CN200510072761 A CN 200510072761A CN 1699761 A CN1699761 A CN 1699761A
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CN
China
Prior art keywords
loop sets
changing valve
pump
mentioned
hydraulic
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Granted
Application number
CN 200510072761
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Chinese (zh)
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CN100516555C (en
Inventor
藤井笃
菅野刚
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Kayaba Industry Co Ltd
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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

Landscapes

  • 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)

Abstract

A driving loss of a pump is avoided to reduce a load of an engine driving the pump. At least a first circuit group and a second circuit group, each including switching valves 11 to 19 to switch supply of operating oil to actuators, an auxiliary switching valve 16 disposed in the first circuit group to switch supply of the operating oil to an auxiliary actuator, and at least two pumps supplying the operating oil to each of the first circuit group and the second circuit group are provided. A convergence flow passage 40 to converge the operating oil from the second circuit group to the first circuit group, a drain flow passage 43 branched from the convergence flow passage 40 to release the operating oil to a side of a reservoir, and a control valve 42 interposed in the branched portion are provided, wherein the control valve 42 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 first circuit group to the drain flow passage 43 when supply pressure of the first circuit group is higher than supply pressure of the second circuit group.

Description

Hydraulic control device
Technical field
The present invention relates to be used for construction plant of hydraulic actuated excavator etc. and hydraulic control device with a plurality of oil hydraulic circuit groups.
Background technique
As this hydraulic control device, the disclosed device of JP2002-276607A communique is arranged, as shown in Figure 2.
Hydraulic control device has first～the 3rd pump P1～P3, and, on these first～the 3rd pump P1～P3, be connected with the 50a～50c of first～tertiary circuit system respectively.
For the first circuit system 50a,, be connected with first of standard-sized sheet reversing～the 3rd changing valve 11～13 being connected on the first supply stream 1 of the first pump P1.When these first～the 3rd changing valves 11～13 are in illustrated neutral position,, the first pump P1 and the cylinder stream 10 that is connected in not shown cylinder one side are connected by the first neutral stream 2.
When switching first changing valve 11 from the neutral position, the hydraulic oil (working oil) of self-pumping P1 directly supplies to the hydraulic transmission 71 that is connected with this changing valve 11 in the future.In addition, when switching any one of second, third changing valve 12,13, similarly hydraulic oil is supplied in the hydraulic transmission 72,73 that is connected with changing valve 12,13 by the first parallel stream 3.The maximum throughput of the first pump P1 is to set according to the maximum necessary flow that is connected to three hydraulic transmissions 71～73 of first～the 3rd changing valve 11～13.
For the second circuit system 50b,, be connected with the 4th of standard-sized sheet reversing～the 6th changing valve 14～16 being connected on the second supply stream 4 of the second pump P2.When these the 4th～the 6th changing valves 14～16 are in illustrated neutral position,, the second pump P2 and cylinder stream 10 are connected by the second neutral stream 5.When switching the 4th changing valve 14, in the future in the hydraulic transmission 74 that hydraulic oil directly supplies to this changing valve 14 is connected of self-pumping P2.In addition, when switching any one of the 5th, the 6th changing valve 15,16, similarly hydraulic oil is supplied to the hydraulic transmission 75,70 that is connected with changing valve 15,16 by the second parallel stream 6.
Above-mentioned the 6th changing valve 16 is standby changing valve, and this standby changing valve 16 is at the construction plant (Construction traffic) of the hydraulic transmission 70 of adopting Zhou Teshu and pre-prepd.That is,, do not use standby changing valve 16 only having under two situations by the hydraulic transmission of second circuit system 50b control; And have special hydraulic transmission 70 and having under the situation of three hydraulic transmissions that are connected with the second circuit system 50b, special hydraulic transmission 70 is connected with standby changing valve 16.And, control by 16 pairs of special hydraulic transmissions 70 of this standby changing valve.And, owing to be not the standing special hydraulic transmission 70 that has, so the maximum throughput of the second pump P2 is to set according to the maximum necessary flow that is connected to two hydraulic transmissions 74,75 of the 4th, the 5th changing valve 14,15.
For the 50c of tertiary circuit system,, be connected with the 7th of standard-sized sheet reversing～the 9th changing valve 17～19 being connected on the 3rd supply stream 7 of the 3rd pump P3.When these the 7th～the 9th changing valves 17～19 are in illustrated neutral position,, the 3rd pump P3 and its downstream side are connected by the 3rd neutral stream 8.When switching the 7th changing valve 17, the hydraulic oil of self-pumping P3 directly supplies to the hydraulic transmission 77 that is connected with this changing valve 17 in the future.In addition, when switching any one of the 8th, the 9th changing valve 18,19, similarly hydraulic oil is supplied in the hydraulic transmission 78,79 that is connected with changing valve 18,19 by the 3rd parallel stream 9.The maximum throughput of the 3rd pump P3 is to set according to the maximum necessary flow that is connected to three hydraulic transmissions 77～79 of the 7th～the 9th changing valve 17～19.
In addition, in order will and to supply among the second circuit system 50b from the hydraulic oil of the 50c of tertiary circuit system interflow as required, the downstream side of the 3rd neutral stream 8 is connected on the second neutral stream 5 of the second circuit system 50b.And, in the way of the stream that the above-mentioned the 3rd neutral stream 8 is connected to the second neutral stream 5, be provided with the interflow changing valve 20 of hydraulic pilot formula.
This interflow changing valve 20 is switched by the operator, and when being in the close position, the 3rd neutral stream 8 is connected with cylinder stream 10 and disconnects mutually with the second neutral stream 5, and then the discharge oil of the 3rd pump P3 can't supply among the second circuit system 50b.Therewith relatively, when interflow changing valve 20 switched to illustrated enable possition, the 3rd neutral stream 8 and the second neutral stream 5 were connected, and then the discharge oil of the 3rd pump P3 is fed among the second circuit system 50b.
It is not enough for the flow that supplies to the special hydraulic transmission 70 that is connected with standby changing valve 16 is produced that such interflow changing valve 20 is set.
Hydraulic oil from the second pump P2 does not supply in the standby changing valve 16, the maximum throughput of this second pump P2 is to set according to the maximum necessary flow that is connected to the hydraulic transmission 74,75 of the 4th, the 5th changing valve 14,15, when making hydraulic transmission 70 actions that are connected to standby changing valve 16, usually produce the problem of supply flow deficiency.Therefore, in the case, make the discharge oil of the 3rd pump P3 and from the discharge oil interflow of the second pump P2 by interflow changing valve 20, thereby can remedy this supply flow deficiency.
But, supply to the second circuit system 50b and make under the situation of the special hydraulic transmission that is connected with standby changing valve 16 70 actions at discharge oil the 3rd pump P3, when the pressure of the load pressure height of remaining hydraulic transmission 74,75 of the special hydraulic transmission 70 or the second circuit system 50b, the second circuit system 50b is high, the pressure that is attached thereto the supply stream 7 of the 3rd pump P3 that connects also raises, when surpassing the setting pressure of dropping valve 23, dropping valve 23 is opened.
Pump P1～P3 is controlled it as the driving horsepower that does not for example make pump P3 and is surpassed certain value by not shown engine-driving, and makes the relation of pump discharge head and flow keep certain.
If pumping pressure is elevated to the degree that the dropping valve 23 of the 3rd pump P3 is opened, then pump delivery reduces significantly, and the pump that also can take place to be produced by step-down drives loss.
Particularly in construction plant, because by the method for the desired operation of each hydraulic transmission etc., the action of hydraulic transmission is slack-off, the problem that the circuit pressure rising that is attached thereto is arranged more, therefore, the part that has the driving loss of above-mentioned the 3rd pump P3 can be used in the problem that the fuel cost of the motor of driven pump raises.
Summary of the invention
The present invention is a purpose to address the above problem.
Hydraulic control device of the present invention has: first, second two loop sets at least have the changing valve of the supply of changeable working oil to hydraulic transmission respectively; Standby changing valve is disposed at above-mentioned first loop sets, is used to switch the supply to the working oil of standby hydraulic transmission; At least two pumps are used for supplying with working oil to above-mentioned first, second loop sets respectively; The interflow stream makes from the working oil of second loop sets and collaborates in above-mentioned first loop sets; Drain passageway makes working oil discharge from fuel tank one side from above-mentioned interflow stream branch; Switchover control valve, be arranged at above-mentioned branching portion, carry out switch motion corresponding to the pressure reduction of first loop sets and second loop sets, when the supply pressure of first loop sets was higher than the supply pressure of second loop sets, the working oil of first loop sets flowed to drain passageway.
According to the present invention, can avoid the driving loss of the pump of the loop sets that makes the working oil interflow, can guarantee the required action of the hydraulic transmission of standby changing valve, can alleviate the burden that pump drives the motor of usefulness simultaneously, can improve fuel cost.
Description of drawings
Fig. 1 is the circuit diagram of hydraulic control device of the hydraulic actuated excavator of embodiments of the invention.
Fig. 2 is the circuit diagram of existing hydraulic control device.
Embodiment
Embodiments of the invention are described with reference to the accompanying drawings.
Fig. 1 represents the circuit diagram of the hydraulic control device of hydraulic actuated excavator.In Fig. 1, be the identical symbol of parts employing of same structure with above-mentioned Fig. 2.
Hydraulic control device of the present invention has first～the 3rd pump P1～P3, and these first～the 3rd pump P1～P3 are connected with the 60A～60C of first～tertiary circuit system respectively.
But, for with first, the 60A of tertiary circuit system, 60B and the 60C of tertiary circuit system at working oil interflow is distinguished, in claims, with first, second circuit system 60A, 60B as first loop sets, and with the 60C of tertiary circuit system as second loop sets.
For the first circuit system 60A (first loop sets),, be connected with first of standard-sized sheet reversing～the 3rd changing valve 11～13 being connected on the first supply stream 1 of the first pump P1.When these first～the 3rd changing valves 11～13 are in illustrated neutral position,, the first pump P1 and cylinder stream 10 are connected by the first neutral stream 2.
When switching above-mentioned first changing valve 11, the hydraulic oil of self-pumping P1 directly supplies in the hydraulic transmission that is connected with this changing valve (for example vehicle driving use left side drive motor) 31 in the future.In addition, when switching any one of second, third changing valve 12,13, by the first parallel stream 3, similarly hydraulic oil is supplied in the hydraulic transmission 32,33 that is connected with this changing valve 12,13, that is the shear leg that, is connected with second changing valve 12 drives with oil hydraulic cylinder 32 and the scraper bowl that is connected with the 3rd changing valve 13 and drives with in the oil hydraulic cylinder 33.
The maximum throughput of the first pump P1 is to set according to the maximum necessary flow that is connected to three hydraulic transmissions 31～33 of first～the 3rd changing valve 11～13.Among the figure, the 21st, when first circuit pressure (being the head pressure of pump P1) of supplying with stream 1 rises to predetermined value unlatching and dropping valve of release pressure when above, Pa1, Pb1, Pa2, Pb2, Pa3, Pb3 are the guiding loop, and the supply by guide pressure makes above-mentioned changing valve 11～13 carry out switch motion.In addition, DR is the discharging loop.
For the second circuit system 60B (first loop sets),, be connected with the 4th of standard-sized sheet reversing～the 6th changing valve 14～16 being connected on the second supply stream 4 of the second pump P2.
When these the 4th～the 6th changing valves 14～16 are in illustrated neutral position,, the second pump P2 and cylinder stream 10 are connected by the second neutral stream 5.When switching the 4th changing valve 14, the hydraulic oil of self-pumping P2 directly supplies in the hydraulic transmission (the right side drive motor that vehicle driving is used) 34 that is connected with this changing valve 14 in the future.In addition, when switching any one of the 5th, the 6th changing valve 15,16,, hydraulic oil is supplied in the hydraulic transmission 35,36 that is connected with this changing valve 15,16 by the second parallel stream 6, that is, arm drives with in oil hydraulic cylinder 35 and the special hydraulic transmission 30.
In the case, the 6th changing valve 16 has the function as standby changing valve, is used to control the driving of special hydraulic transmission 30.As special hydraulic transmission 30, for example disintegrator (breaker), excavation pawl etc. are arranged.
The maximum throughput of the second pump P2 is to set according to the maximum necessary flow that is connected to two hydraulic transmissions 34,35 of the 4th, the 5th changing valve 14,15.Among the figure, the 22nd, when the pressure of supplying with stream 4, be the dropping valve that the head pressure of pump P2 rises to predetermined value release pressure when above, Pa4, Pb4, Pa5, Pb5～Pa6, Pb6 are the guiding loop, are accompanied by the supply of guide pressure and make above-mentioned changing valve 14～16 carry out switch motion.
The 60C of tertiary circuit system (second loop sets) being connected on the 3rd supply stream 7 of the 3rd pump P3, is connected with the 7th of standard-sized sheet reversing～the 9th changing valve 17～19.
When these the 7th～the 9th changing valves 17～19 are in illustrated neutral position,, the 3rd pump P3 and its downstream road 40 are connected by the 3rd neutral stream 8.When switching the 7th changing valve 17, the hydraulic oil of self-pumping P3 directly supplies in the hydraulic transmission (drive motor of chassis revolution usefulness) 37 that is connected with this changing valve 17 in the future.In addition, when switching any one of the 8th, the 9th changing valve 18,19, by the 3rd parallel stream 9, hydraulic oil is supplied in the hydraulic transmission 38,39 that is connected with this changing valve 18,19, that is the scraper plate that, is connected with the 8th changing valve 18 drives with oil hydraulic cylinder and turning to driving in the oil hydraulic cylinder 39 of being connected with the 9th changing valve 19.
The maximum throughput of the 3rd pump P3 is to set according to the maximum necessary flow that is connected to three hydraulic transmissions 37～39 of the 7th～the 9th changing valve 17～19.Among the figure, the 23rd, when the 3rd circuit pressure of supplying with stream 7, be that the head pressure of pump P3 rises to predetermined value unlatching and dropping valve of release pressure when above, Pa7, Pb7, Pa8, Pb8, Pa9, Pb9 are the guiding loop, and the supply by guide pressure makes above-mentioned changing valve 17～19 carry out switch motion.
In order will and to supply among the second circuit system 60B from the hydraulic oil of the 60C of tertiary circuit system interflow as required, the downstream road 40 of the 3rd neutral stream 8 is connected on the interflow stream 41 of the second circuit system 60B.This interflow stream 41 is connected on the upstream second neutral stream 5 and the second parallel stream 6 of standby changing valve 16.
In addition, be provided with the discharge stream 43 that comes out from downstream road 40 branches of the above-mentioned tertiary circuit 60C of system, on the branching portion of above-mentioned interflow stream 41 and discharge stream 43, be provided with the switchover control valve 42 that is used to carry out the stream switching.
For switchover control valve 42, when the head pressure of the second pump P2 of the second circuit system 60B exceeds setting pressure when above than the head pressure of the 3rd pump P3 of the 60C of tertiary circuit system, the downstream road 40 of the 60C of tertiary circuit system with discharge stream 43 and be connected; And therewith relatively, when the head pressure of the second pump P2 of the second circuit system 60B was compared in above-mentioned setting pressure with the head pressure of the 3rd pump P3 of the 60C of tertiary circuit system, the downstream road 40 of the 60C of tertiary circuit system was connected with interflow stream 41.
Switchover control valve 42 is as the guide pressure changing valve, be connected with path of navigation 45 that the head pressure from the 3rd pump P3 is led as guide pressure and the path of navigation 46 that will be led as guide pressure from the head pressure of the second pump P2 on changing valve 42, this changing valve is subjected to these guide pressures and carries out switch motion.
Owing to be said structure, when the head pressure of the 3rd pump P3 of the head pressure of the second pump P2 of the second circuit system 60B and the 60C of tertiary circuit system about equally the time, when switchover control valve 42 is switched to interflow stream 41 1 sides, in the second neutral stream 5 and the second parallel stream 6 of the second circuit system 60B, the hydraulic oil interflow of the hydraulic oil of the second pump P2 and the 3rd pump P3 also is supplied to.Under this state, if standby changing valve 16 is switched to any direction, the working oil of then having collaborated is fed in the hydraulic transmission 30 that is connected with standby changing valve 16, makes this hydraulic transmission 30 actions.
In the action of the hydraulic transmission 30 that is connected to standby changing valve 16, when the load pressure of remaining hydraulic transmission 34 of this hydraulic transmission 30 or the second circuit system 60B or 35 uprised, the head pressure of the second pump P2 of the second circuit system 60B rose.The head pressure of the 3rd pump P3 of the 60C of tertiary circuit system also raises, and exceed setting pressure when above than the head pressure of the 3rd pump P3 of the 60C of tertiary circuit system when the head pressure of the second pump P2 of the second circuit system 60B, switch transition control valve 42 makes the discharge oil of the 3rd pump P3 flow to cylinder stream 10 from discharging stream 43.
Therefore, even the head pressure of the 3rd pump P3 uprises, under the situation of the setting pressure of no show dropping valve 23, dropping valve 23 can not opened.Consequently, can avoid the driving loss of the 3rd pump P3 that produces through the step-down of dropping valve 23 by the hydraulic oil of the 3rd pump P3, therefore, can alleviate the burden of the motor of driven pump, can improve fuel cost.
Load pressure in remaining hydraulic transmission 34 of the hydraulic transmission 30 that is connected to standby changing valve 16 or the second circuit system 60B or 35 is low, the head pressure of the second pump P2 of the second circuit system 60B is low in the setting pressure time, on the basis of the hydraulic oil of the second pump P2, by switchover control valve 42, the hydraulic oil of the 3rd pump P3 is supplied in the hydraulic transmission 30 that is connected with standby changing valve 16.
Therefore, the hydraulic oil of the 3rd pump P3 suitably can be supplied in the hydraulic transmission 30 that is connected in standby changing valve 16 as working oil through the interflow, thereby guarantee the action that this hydraulic transmission 30 is required.
In the above-described embodiments, show example with first～the 3rd these three circuit system 60A～60C, as long as but the present invention has at least two circuit system 60B and 60C, in the case, as long as hydraulic oil is supplied to the circuit system 60B with standby changing valve 16 from a circuit system 60C.
The present invention is not limited to the foregoing description, comprises various distortion and improvement that those skilled in the art can implement.

Claims (4)

1. hydraulic control device is characterized in that having:
At least first, second two loop sets, these two loop sets have the changing valve of the supply of changeable working oil to hydraulic transmission respectively;
Standby changing valve is disposed at above-mentioned first loop sets, is used to switch the supply to the working oil of standby hydraulic transmission;
At least two pumps are used for supplying with working oil to above-mentioned first, second loop sets respectively;
The interflow stream makes from the working oil of second loop sets and collaborates in above-mentioned first loop sets;
Discharge stream, working oil is discharged from cylinder one side from above-mentioned interflow stream branch;
Switchover control valve, be clipped on above-mentioned branching portion, carry out switch motion corresponding to the pressure reduction of first loop sets and second loop sets, when the supply pressure of first loop sets was higher than the supply pressure of second loop sets, the working oil that makes first loop sets was to discharging flow path.
2. hydraulic control device as claimed in claim 1 is characterized in that, for above-mentioned switchover control valve, when the supply pressure of first loop sets exceeds predetermined value when above than the supply pressure of second loop sets, the working oil of above-mentioned interflow stream is to discharging flow path; In addition, with working oil from above-mentioned interflow stream first loop sets that leads.
3. hydraulic control device as claimed in claim 2 is characterized in that, above-mentioned switchover control valve is the guide pressure changing valve that the supply pressure of the supply pressure of above-mentioned first loop sets and second loop sets is carried out switch motion as guide pressure.
4. hydraulic control device as claimed in claim 1 is characterized in that, the changing valve of above-mentioned first, second loop sets is the changing valve of standard-sized sheet reversing, and each a plurality of changing valve is in series being provided with.
CNB2005100727619A 2004-05-19 2005-05-19 Hydraulic control apparatus Expired - Fee Related CN100516555C (en)

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JP4139352B2 (en) 2008-08-27
EP1598561A2 (en) 2005-11-23
CN100516555C (en) 2009-07-22
DE602005003980T2 (en) 2008-04-30
JP2005331011A (en) 2005-12-02
DE602005003980D1 (en) 2008-02-07
EP1598561A3 (en) 2005-12-14
EP1598561B1 (en) 2007-12-26

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