CN105612359B - Fluid pressure drive device - Google Patents
Fluid pressure drive device Download PDFInfo
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- CN105612359B CN105612359B CN201480057066.2A CN201480057066A CN105612359B CN 105612359 B CN105612359 B CN 105612359B CN 201480057066 A CN201480057066 A CN 201480057066A CN 105612359 B CN105612359 B CN 105612359B
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- valve
- fluid
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Classifications
-
- 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
- E02F9/2296—Systems with a variable displacement pump
-
- 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
- E02F9/226—Safety arrangements, e.g. hydraulic driven fans, preventing cavitation, leakage, overheating
-
- 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
- E02F9/2285—Pilot-operated systems
-
- 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
- F15B20/00—Safety arrangements for fluid actuator systems; Applications of safety devices in fluid actuator systems; Emergency measures for fluid actuator systems
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B2211/00—Circuits for servomotor systems
- F15B2211/40—Flow control
- F15B2211/415—Flow control characterised by the connections of the flow control means in the circuit
- F15B2211/41563—Flow control characterised by the connections of the flow control means in the circuit being connected to a pressure source and a 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
- F15B2211/40—Flow control
- F15B2211/42—Flow control characterised by the type of actuation
- F15B2211/428—Flow 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
- F15B2211/40—Flow control
- F15B2211/45—Control of bleed-off flow, e.g. control of bypass flow to the return line
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B2211/00—Circuits for servomotor systems
- F15B2211/60—Circuit components or control therefor
- F15B2211/63—Electronic controllers
- F15B2211/6303—Electronic controllers using input signals
- F15B2211/6306—Electronic controllers using input signals representing a pressure
- F15B2211/6309—Electronic controllers using input signals representing a pressure the pressure being a pressure source supply 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
- F15B2211/60—Circuit components or control therefor
- F15B2211/63—Electronic controllers
- F15B2211/6303—Electronic controllers using input signals
- F15B2211/6306—Electronic controllers using input signals representing a pressure
- F15B2211/6313—Electronic controllers using input signals representing a pressure the pressure being a load 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
- F15B2211/60—Circuit components or control therefor
- F15B2211/665—Methods of control using electronic components
-
- 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
- F15B2211/60—Circuit components or control therefor
- F15B2211/665—Methods of control using electronic components
- F15B2211/6654—Flow rate 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
- F15B2211/80—Other types of control related to particular problems or conditions
- F15B2211/875—Control measures for coping with failures
- F15B2211/8752—Emergency operation mode, e.g. fail-safe operation mode
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mining & Mineral Resources (AREA)
- Civil Engineering (AREA)
- Structural Engineering (AREA)
- Fluid-Pressure Circuits (AREA)
- Chemical & Material Sciences (AREA)
- Analytical Chemistry (AREA)
- Physics & Mathematics (AREA)
- Fluid Mechanics (AREA)
- Mechanical Engineering (AREA)
- Operation Control Of Excavators (AREA)
Abstract
Fluid pressure drive device（1）By hydraulic pump（11）The working oil of discharge is supplied to actuator（7、9、10）So as to drive actuator（7、9、10）.Fluid pressure drive device（1）Have：Operation valve（13、14）, flow control mechanism（12）, proportional control solenoid valve（27）, automatic anti-fault mechanism（25）, and drain valve（15）.When the pressure differential of output pressure Prcv and control pressure Psol is in predetermined setting control range（52）When interior, automatic anti-fault mechanism（25）Control pressure Psol is exported as pilot pressure Ppil, pressure differential is not setting control range（52）When interior, output pressure Prcv is exported as pilot pressure.Drain valve（15）Aperture area is adjusted according to pilot pressure Ppil, the working oil that flow is matched with aperture area is from hydraulic pump（11）It is expelled to fuel tank.
Description
Technical field
The present invention relates to the pressure fluid that hydraulic pump spues is supplied to actuator so as to driving actuator（actuator）'s
Fluid pressure drive device.
Background technology
The building machineries such as hydraulic excavator possess multiple oil pressure actuators, manipulate swing arm by driving oil pressure actuator
（boom）, dipper（arm）, scraper bowl, the various inscapes such as whirligig and mobile devices, various so as to execute
Work.Building machinery is to drive these oil pressure actuators to possess the drive device for hydraulic that for example patent document 1 is recorded.
Drive device for hydraulic described in patent document 1 has oil pressure pump, by the pressure oil supply that oil pressure pump spues
To actuator, actuator is driven with this.In drive device for hydraulic, direction switch valve is accordingly configured with each actuator, side
The flowing of the pressure oil flowed into into the actuator corresponding to switching Vavle switching, and adjust its flow.Also, drive device for hydraulic tool
Standby drain valve (bleed off valve), the pressure oil that oil pressure pump is spued by drain valve is to fuel tank discharge so as to adjusting each execution
The flow flowed in device.Additionally, in drive device for hydraulic, operation device is accordingly configured with each actuator, operation device
To control device output function signal.Control device according to the operation signal that is sent by operation device, control direction switching valve and
The aperture area of drain valve, so as to the pressure oil matched with operation signal to the actuator direction of the supply and flow.
Prior art literature：
Patent document 1：Japanese Unexamined Patent Publication 7-63203 publication.
Content of the invention
Problems to be solved by the invention：
The drain valve of the drive device for hydraulic described in patent document 1 is made up of so-called solenoid electric valve, by signal
Line is electrically connected with control device.Drive signal is delivered letters to drain valve from control device by the holding wire, and drain valve is according to this
Drive signal adjusts its aperture area.Therefore, once because holding wire occur electric fault（Short-circuit and breaking etc.）, then uncontrollable
The discharge rate of the pressure oil that discharges to fuel tank (tank) from oil pressure pump, drain valve loss of function.Thus, discharge reduce off-flavor often to raise
Or there are vibrations when working in actuator（Shock）.
Therefore it is an object of the invention to provide the fluid pressure drive device that drain valve function is lost can be suppressed.
The means of solve problem：
The fluid pressure drive device of the present invention is to supply to actuator the pressure fluid that hydraulic pump spues so as to driving described holding
The fluid pressure drive device of row device, possesses：It is provided with action bars, and operates the action bars then to export and matches pressure with the operational ton
Output pressure operation valve；Aperture is adjusted according to the output pressure, will be matched with the load of the aperture and the actuator
The pressure fluid of flow supply from the hydraulic pump to the flow control mechanism of the actuator；Output is controlled as and input
Drive signal match pressure control pressure solenoid electric valve；The pressure differential of the output pressure and the control pressure is pre-
Then the control pressure is exported as the pilot pressure in fixed setting control range, the pressure differential departs from the setting
The automatic anti-fault that the output pressure is then exported by control range as pilot pressure（fail-safe）Mechanism；With according to institute
State automatic anti-fault mechanism output pilot pressure adjust aperture area, the pressure fluid that flow is matched with the aperture area from
The hydraulic pump is expelled to the drain valve of fuel tank.
According to the present invention, whether predetermined setting control range can be located at according to the pressure differential of output pressure and control pressure
Interior, switch for adjusting the pilot pressure of the aperture area of drain valve.By means of this, by suitably setting control model
Enclose, can break down etc. in solenoid electric valve and during uncontrollable control pressure, the output pressure according to operation valve makes drain valve
Work.Therefore, can suppress to cause the situation that drain valve cannot work orderly because of solenoid electric valve failure etc..
Can also be that the automatic anti-fault mechanism has in foregoing invention：The output pressure and the control pressure
Acted in the form of mutually resisting, and change the low-pressure side valve element of position according to the power of effect（spool）；With will be with the output
The applying power that pressure mutually resists imposes on the low-pressure side force application component of the low-pressure side valve element, and the low-pressure side valve element is according to its position choosing
Select and the output pressure or the control pressure are exported as the pilot pressure, the output pressure changes the low-pressure side
The position of valve element and act on the low-pressure side valve element so that the output pressure is selected as the pilot pressure；The control
Pressing pressure changes the position of the low-pressure side valve element and acts on the low-pressure side valve element, so that the control pressure is selected as
The pilot pressure.
According to said structure, low-pressure side valve element is according to output pressure and the pressure differential of control pressure（Specifically export
Pressure deducts the value of control pressure）Change its position, control pressure is very high and pressure differential less than the value matched with applying power when,
Control pressure is exported by low-pressure side valve element as pilot pressure.On the other hand, control pressure is too low and pressure differential more than and applying
During the value that power matches, output pressure is exported by low-pressure side valve element as pilot pressure.Thus, can according to pressure differential whether exceed with
Value that applying power matches and be selected as the oil pressure of pilot pressure output, setting control range can be changed by changing applying power.
Can also be as the control in foregoing invention after the decompression of pressure fluid that pioneer pump is spued by the solenoid electric valve
Pressing pressure is exported, and the automatic anti-fault mechanism has：The output pressure and the control pressure are in the form of mutually resisting
Effect, and change the high-pressure side valve element of position according to the power of effect；Institute is imposed on by the applying power mutually resisted with the control pressure
The high-pressure side force application component of high-pressure side valve element is stated, the high-pressure side valve element is selected the output pressure or described according to its position
Control pressure is exported as the pilot pressure, and the control pressure is more than the output pressure and the control pressure and described
When the pressure differential of output pressure departs from the setting control range, then the output pressure is preferentially defeated as the pilot pressure
Go out.
According to said structure, control pressure is too high and the pressure differential of control pressure and output pressure departs from setting control range
When, output pressure is preferentially exported as pilot pressure.Therefore, can break down etc. in solenoid electric valve and control pressure is excessive
When, the output pressure according to operation valve makes drain valve work.Therefore, can suppress to cause drain valve to lose because of solenoid electric valve failure etc.
Lose the situation of function.
Can also be that the solenoid electric valve is connected with the operation valve in foregoing invention, the operation valve is exported
Export as the control pressure after output pressure decompression.
According to said structure, it is no longer necessary to for the pump for making control pressure export from solenoid electric valve, component count can be reduced
Amount.
Can also be in foregoing invention, possess and the drive signal is exported to the solenoid electric valve according to working condition
Control device, mode of operation of the working condition comprising the action bars, the rotating speed of the engine of the driving hydraulic pump, institute
At least one state in the temperature for stating pressure fluid and the load for acting on the actuator.
According to said structure, the high-efficiency operation matched with working condition is can achieve.
Can also, in foregoing invention, possess：The multiple described operation respectively correspondingly arranged with multiple actuators
Valve；With the output pressure selection mechanism that highest output pressure is selected in the output pressure exported from the plurality of operation valve, work as behaviour
Execution when making the operation valve and exporting output pressure, corresponding to from the flow control mechanism to the operation valve for being operated
The pressure fluid that device supply flow rate is matched with the output pressure, when the pressure differential departs from the setting control range, described
Selected for output pressure selection mechanism output pressure is exported by automatic anti-fault mechanism as pilot pressure.
According to said structure, can adjust the discharge of the pressure fluid that fuel tank is expelled to from hydraulic pump according to maximum output pressure
Amount, the bigger discharge rate of the output pressure are less.Thereby, when operating multiple action bars, can be by the operational ton with these action bars
The flow that middle maximum operational ton matches is supplied to actuator side.
According to the present invention, the situation that can prevent drain valve from cannot work orderly.
Invention effect：
After being described with reference to, by the detailed description of following preferred embodiments, so as to the upper of the clear and definite present invention
State purpose, other purposes, feature and advantage.
Description of the drawings
Fig. 1 is the side view of the hydraulic excavator of the fluid pressure drive device for illustrating the embodiment for possessing the present invention；
Fig. 2 is the loop diagram of the hydraulic circuit of the fluid pressure drive device for illustrating first embodiment；
Fig. 3 is the pass between the throw of lever amount of the operation valve for illustrating fluid pressure drive device and the control pressure of solenoid electric valve
The chart of system；
Fig. 4 is the loop diagram of the hydraulic circuit of the fluid pressure drive device for illustrating the second embodiment.
Specific embodiment
Hereinafter, real according to the fluid pressure drive device 1 and second of the first embodiment of the present invention with reference to above-mentioned description of the drawings
The fluid pressure drive device 1A for applying form and the hydraulic excavator 2 for possessing them.Separately, the direction below used in explanation is general
Thought is to use for convenience of description, and structure direction of invention etc. is defined in the direction not.Also, the oil pressure of following explanation drives
Dynamic device 1,1A is only a kind of embodiment of the present invention.Therefore, the invention is not restricted to embodiment, in the master without departing from invention
Can increase in the range of purport, delete, change.
＜ first embodiments ＞
［ hydraulic excavator ］
As shown in figure 1, the hydraulic excavator 2 of an example as building machinery, by being installed on the accessory of slightly end
Such as scraper bowl 3 executes the various work such as excavation or carrying.Hydraulic excavator 2 has crawler（crawler）
Deng mobile devices 4, rotary body 5 is rotatably placed on mobile devices 4.Rotary body 5 is formed as can be by rotating motor
（Not shown）The structure of rotation driving, is formed with driver seat 5a for the driver to ride on rotary body 5.
Also, be provided with rotary body 5 can be in the swing arm 6 of above-below direction shake.Swing arm 6 from rotary body 5 obliquely upward and to
Front extension, setting up between swing arm 6 and rotary body 5 has swing arm cylinder 7.Stretched by making swing arm cylinder 7, swing arm 6 is made with this
Shake upward or downwards relative to rotary body 5.Also, be provided with the slightly end of swing arm 6 can be in the bucket of fore-and-aft direction shake
Bar 8.The slightly end of 8 slave arm 6 of dipper extends oliquely downward and forward, and setting up between swing arm 6 and dipper 8 has dipper cylinder 9.
Stretched by making dipper cylinder 9, dipper 8 is shaken rearward or forwards relative to swing arm 6 with this.Additionally, dipper 8 is slightly
Being provided with end can be in the scraper bowl 3 of fore-and-aft direction shake.Scraper bowl cylinder 10 is provided between scraper bowl 3 and dipper 8, by making
Scraper bowl is flexible with cylinder 10, scraper bowl 3 is shaken in fore-and-aft direction with this.
Swing arm cylinder 7, dipper cylinder 9, scraper bowl cylinder 10 and rotating motor are the actuator of fluid pressure type,
By to their supply pressure liquid（It is working oil in this embodiment）And drive.Hydraulic excavator 2 possesses to comprising rotation use
Each actuator 7,9,10 of motor supplies the fluid pressure drive device 1 of working oil, and by the fluid pressure drive device 1 to each actuator
7th, 9,10 supply working oil.Hereinafter, referring to the drawings the structure of 2 explanation fluid pressure drive devices 1.
［ fluid pressure drive device ］
Fluid pressure drive device 1 possesses hydraulic pump 11, flow control mechanism 12, multiple operation valves 13 and 14 and drain valve 15.
Hydraulic pump 11 is linked with engine E, discharge pressure liquid when engine E rotates（Working oil or water, are work in this embodiment
Oil）.Hydraulic pump 11 is the hydraulic pump of so-called variable capacity type, with swash plate 11a.Swash plate 11a is musted according to driving actuator
The flow for needing changes inclination angle, the working oil that hydraulic pump 11 matches from the angle of discharge opening discharge flow and swash plate 11a.Separately, tiltedly
The inclination angle of plate 11a is for example controlled by negative control or positive control mode.Discharge opening is connected with primary path 16, the primary path 16 and stream
Amount controlling organization 12 is connected.11 discharge working oil of hydraulic pump is directed into flow control mechanism 12 via primary path 16.
Flow control mechanism 12 and swing arm cylinder 7, dipper cylinder 9, scraper bowl cylinder 10 and rotating motor etc.
Actuator connects, and is formed as to supply the working oil from hydraulic pump 11 to each actuator 7,9,10 comprising rotating motor
Structure.Separately, in Fig. 2, for purposes of illustration only, swing arm cylinder 7 and dipper cylinder 9 is illustrate only, and scraper bowl vapour not shown
Cylinder 10 and rotating motor.Further describe flow control mechanism 12 structure, then flow control mechanism 12 have with per
The direction switch valve that individual actuator 7,9,10 is accordingly arranged（Not shown）.Direction switch valve respectively with corresponding actuator
7th, 9,10 two interfaces（In the case of swing arm cylinder 7 and dipper cylinder 9 for cylinder rostral interface 7a, 9a and
Interface 7b, 9b of bar side）Connection, the flow direction of changeable working oil is so as to the interface of the supply destination of switch operating oil.
Also, direction switch valve adjusts the aperture of the opening, the flow that the load with the aperture and actuation means 7,9,10 matches is made
Working oil flow into corresponding actuator 7,9,10.Be connected with the flow control mechanism 12 for so constituting multiple operation valves 13,
14.
Operation valve 13,14 and each direction switch valve（That is, each actuator 7,9,10）Driver's seat is accordingly arranged at
Chair 5a.Separately, below, for purposes of illustration only, operation valve of the swing arm corresponding to cylinder 7 and dipper cylinder 9 is described by Fig. 2 only
13rd, 14, and omit the relevant indicators and explanation of scraper bowl cylinder 10 and the operation valve of rotating motor.Operation valve 13,14 is distinguished
There is action bars 13a, 14a, action bars 13a, 14a can be executed to first direction and second direction on the basis of neutral position and be toppled over
Operation.Also, operation valve 13,14 is connected with the first pioneer pump 20 respectively.First pioneer pump 20 is the liquid of so-called fixed capacity type
Press pump, spue quantitative guide oil.The guide oil that first pioneer pump 20 spues is directed respectively into operation valve 13,14, operation valve 13,
The guide oil being imported into decompression is and operational ton by 14（I.e., flip angle）After the pressure for matching, towards with action bars 13a, 14a
The corresponding direction output of toppling direction.
It is described in more detail, then the operation valve 13 of swing arm is connected with two elder generations guiding path 17a, 17b, the operation valve of dipper
14 are respectively connected with two elder generations guiding path 18a, 18b.To first direction（Such as front）When operating its action bars 13a, swing arm is used
Operation valve 13 there is the elder generation of output pressure P1 that the flip angle with action bars 13a matches to the first guiding path 17a output of a side
Oil Guide.On the other hand, to second direction（Such as rear）During operation action bars 13a, the operation valve 13 of swing arm is to the opposing party's
The guide oil of the output pressure P2 that there is the flip angle with action bars 13a to match for first guiding path 17b outputs.Exported to guide respectively
The guide oil of path 17a, 17b is input to flow control mechanism 12, and in flow control mechanism 12, swing arm is with corresponding to cylinder 7
Direction switch valve worked according to the toppling direction of action bars 13a and flip angle.That is, by the swing arm 7 interior work that flows of cylinder
The direction of oil switches to direction corresponding with the toppling direction, and by the aperture regulation of the opening of direction switch valve is and topples over
The aperture that angle matches.Thereby, working oil can be supplied from hydraulic pump 11 to swing arm cylinder 7 via flow control mechanism 12.
Similarly, to first direction（Such as front）During operation action bars 14a, the elder generation of the operation valve 14 of dipper to a side
Guiding path 18a outputs have the guide oil of the output pressure P3 matched with its amount of toppling over, to second direction（Such as rear）Operation
During action bars 14a, the operation valve 14 of dipper has the output matched with its amount of toppling over to the first guiding path 18b outputs of the opposing party
The guide oil of pressure P4.Exported to the guide oil of first guiding path 18a, 18b respectively and be input to flow control mechanism 12, flow control
In mechanism processed 12, dipper is worked according to the toppling direction of action bars 14a and flip angle with the direction switch valve corresponding to cylinder 9.
That is, the direction of the working oil of flowing in dipper cylinder 9 is switched to direction corresponding with the toppling direction, and by the side
It is the aperture matched with flip angle to the aperture regulation of the opening of switching valve.Thereby, can be via flow control mechanism 12 from hydraulic pressure
Pump 11 supplies working oil to dipper with cylinder 9.
First guiding path 17a, 17b, 18a, 18b of the operation valve 13,14 for so constituting and high pressure selection mechanism 19 connect.High
Highest output pressure is selected in output pressure P1～P4 that pressure selection mechanism 19 is exported from operation valve 13,14 and is exported.Specifically
Bright then high pressure selection mechanism 19 has three shuttle valves（shuttle valve）21st, 22,23, the first shuttle valve 21 and operation valve 13
Two first guiding path 17a, 17b connections, from the oil pressure of first guiding path 17a, 17b, downstream side is defeated for the oil pressure of selection higher side
Go out.Also, the second shuttle valve 22 is connected with two elder generations guiding path 18a, 18b of operation valve 14, from the oil pressure of first guiding path 18a, 18b
Select the oil pressure downstream side output of a higher side.Additionally, the 3rd shuttle valve 23 from respectively by the first shuttle valve 21 and the second shuttle valve
The oil pressure of higher side is selected in two oil pressure of 22 outputs.Also, the 3rd shuttle valve 23 is connected with automatic anti-fault mechanism 25 described later
Connect, the oil pressure of selection is exported to automatic anti-fault mechanism 25 as output pressure Prcv.Second pioneer pump 26 is selecting with high pressure
The form of 19 parallel connection of structure of selecting a good opportunity is connected with the automatic anti-fault mechanism 25 via proportional control solenoid valve 27.
Second pioneer pump 26 is the hydraulic pump of so-called fixed capacity type, and spue quantitative guide oil.Second pioneer pump 26
It is connected with proportional control solenoid valve 27, is connected with automatic anti-fault mechanism 25 by the proportional control solenoid valve 27.Solenoid-operated proportional
Control valve 27 is the proportional control solenoid valve of closed type, with the signal being input into（Current value）The aperture of mouth is increased in ratio.
Separately, proportional control solenoid valve 27 can also be the electromagnetism of the open type contrary with closed type characteristic against proportional control valve.Electromagnetism ratio
Example control valve 27 can input drive signal（Electric current）, the discharge pressure of the second pioneer pump 26 is reduced pressure into the pressure matched with drive signal
Export to automatic anti-fault mechanism 25 as control pressure Psol after power.The proportional control solenoid valve 27 for so constituting and control dress
Put 30 electrical connections.
Control device 30 and speed probe 31, oil temperature sensor 32, pilot pressure sensor PS1～PS4, cylinder pressure
Sensor LS1～LS4 electrical connections.Speed probe 31 detects that the rotating speed of engine E, oil temperature sensor 32 detect primary path 16
The temperature of the working oil of interior flowing.Also, pilot pressure sensor PS1～PS4 is respectively arranged at the first conducting of each operation valve 13,14
On road 17a, 17b, 18a, 18b, the output pressure P1～P4 from the output of each operation valve 13,14 is detected respectively.Also, oil pressure sensor
LS1～LS4 is respectively arranged on the path 33～36 of connection traffic controlling organization 12 and each actuator 7,9,10 respectively, is examined respectively
The oil pressure of the working oil flowed in each actuator 7,9,10 is surveyed from flow control mechanism 12.Each sensor 31,32, PS1～
PS4, LS1～LS4 exports testing result to control device 30.
Control device 30 is based on from various sensors 31,32, PS1～PS4, and the testing result of LS1～LS4 outputs judges liquid
Whether hydraulic driver 1 meets prespecified condition of work.Additionally, control device 30 by with meet the drive that condition of work matches
Dynamic signal（That is, with meet the electric current that condition of work matches）It is input into proportional control solenoid valve 27, so as to by control pressure Psol
It is controlled to and meets the pressure that condition of work matches.Thus controlled control pressure Psol with from high pressure selection mechanism 19
The output pressure Prcv of output is input into together to automatic anti-fault mechanism 25.
Automatic anti-fault mechanism 25 has two automatic anti-fault valves 41,42.Low-pressure side automatic anti-fault valve 41 has low
Pressure side valve core 41a and low-pressure side force application component 41b.Low-pressure side valve element 41a is with high pressure selection mechanism 19 and proportional control solenoid valve
27 are connected with two output channels 43,44 together, and output pressure Prcv and control pressure Psol are from the direction difference that mutually resists
Act on the two ends of low-pressure side valve element 41a.Also, low-pressure side valve element 41a by low-pressure side force application component 41b to output pressure
The direction force that Prcv phases resist.Effect has the low-pressure side valve element 41a of such power so that output pressure Prcv, control pressure
The form of the applying dynamic balance of Psol and low-pressure side force application component 41b changes position, and the position according to low-pressure side valve element 41a
High pressure selection mechanism 19 and 27 respective access point of proportional control solenoid valve are switched to either one in output channel 43,44.
Illustrate in greater detail, then output pressure Prcv so that high pressure selection mechanism 19 be connected with the first output channel 43 and to
The form of the output output pressure Prcv of the first output channel 43 acts on low-pressure side valve element 41a, and control pressure Psol is so that electromagnetism
Proportional control valve 27 is connected with the first output channel 43 and is acted on to the form of 43 pressure output control Psol of the first output channel
In low-pressure side valve element 41a.By means of this, control pressure Psol and critical（threshold）Pressure Pth1 makes a concerted effort more than output pressure
During power Prcv, low-pressure side valve element 41a makes proportional control solenoid valve 27 be connected with the first output channel 43, makes high pressure selection mechanism 19
It is connected with the second output channel 44.On the other hand, control pressure Psol and critical pressure Pth1 make a concerted effort be less than output pressure Prcv
When, low-pressure side valve element 41a makes high pressure selection mechanism 19 be connected with the first output channel 43, and separates 27 He of proportional control solenoid valve
Between second output channel 44.Herein, critical pressure Pth1 is the value determined according to the applying power of low-pressure side force application component 41b.
So, low-pressure side valve element 41a changes its position according to the pressure differential of output pressure Prcv and control pressure Psol, and via each defeated
Go out path 43,44 and output pressure Prcv and control pressure Psol are imported high-pressure side automatic anti-fault valve 42.
High-pressure side automatic anti-fault valve 42 is with high-pressure side valve element 42a and high-pressure side force application component 42b.High-pressure side valve element
42a is connected with first guiding path 45 together with two output channels 43,44, and output pressure Prcv and control pressure Psol are from mutually supporting
Anti- direction is respectively acting on the two ends of high-pressure side valve element 42a.Also, being provided with high-pressure side force application component on the valve element 42a of high-pressure side
42b, is exerted a force to the direction resisted with control pressure Psol phase by high-pressure side force application component 42b.High-pressure side valve element 42a is so that output
The form of the applying dynamic balance of pressure Prcv, control pressure Psol and high-pressure side force application component 42b changes position, and according to height
The access point of first guiding path 45 is switched to either one in two paths 43,44 by the position of pressure side valve core 42a.
Illustrate in greater detail, then output pressure Prcv is so that the form that the first output channel 43 is connected with first guiding path 45 is made
For high-pressure side valve element 42a, control pressure Psol is so that the form that the second output channel 44 is connected with first guiding path 45 is acted on
High-pressure side valve element 42a.By means of this, output pressure Prcv and critical pressure Pth2 make a concerted effort more than control pressure Psol when, high pressure
Side valve core 42a makes the first output channel 43 be connected with first guiding path 45, is less than output pressure Prcv and critical pressure Pth2 with joint efforts
During control pressure Psol, high-pressure side valve element 42a connects the second output channel 44 and first guiding path 45.Herein, critical pressure Pth2
It is the value determined according to the applying power of high-pressure side force application component 42b.In this embodiment, low-pressure side force application component 41b with high
Pressure side force application component 42b has roughly the same coefficient of elasticity, and critical pressure Pth2 is roughly the same with critical pressure Pth1.Thus, high
Pressure side valve core 42a changes position according to the pressure differential of control pressure Psol and output pressure Prcv, and according to the position by guide
The access point of path 45 switches to either one in output channel 43,44.
The automatic anti-fault mechanism 25 for so constituting is exported respectively in high pressure selection mechanism 19 and proportional control solenoid valve 27
When output pressure Prcv and control pressure Psol, by output pressure Prcv and control pressure Psol with output pressure Prcv and control
The oil pressure that the pressure differential of pressing pressure Psol matches is exported to first guiding path 45 as discharge pilot pressure Ppil.
That is, as shown in figure 3, pressure differential Psol-Prcv of output pressure Prcv and control pressure Psol exists
Psol-Prcv ＜-Pth1 ...（1）
Fisrt fault（fail）When in scope 51, high pressure selection mechanism 19 passes through low-pressure side force application component 41b and first
Output channel 43 connects, and the first output channel 43 is connected with first guiding path 45 by high-pressure side valve element 42a.Thereby, output pressure
Prcv imports first guiding path 45, output pressure Prcv via low-pressure side automatic anti-fault valve 41 and high-pressure side automatic anti-fault valve 42
Export from automatic anti-fault mechanism 25 as discharge pilot pressure Ppil.
Pressure differential Psol-Prcv of output pressure Prcv and control pressure Psol exists
- Pth1 ＜ Psol-Prcv ＜ Pth2 ...（2）
Setting control range 52 in when, proportional control solenoid valve 27 by low-pressure side force application component 41b with first export
Path 43 connects, and the first output channel 43 is connected with first guiding path 45 by high-pressure side valve element 42a.Thereby, control pressure Psol
First guiding path 45, the conduct of control pressure Psol are imported via low-pressure side automatic anti-fault valve 41 and high-pressure side automatic anti-fault valve 42
Discharge pilot pressure Ppil is exported from automatic anti-fault mechanism 25.
Additionally, pressure differential Psol-Prcv of control pressure Psol and output pressure Prcv exists
Pth2 ＜ Psol-Prcv ...（3）
The second fault coverage 53 in when, high pressure selection mechanism 19 by low-pressure side force application component 41b with second output lead to
Road 44 connects, and the second output channel 44 is connected with first guiding path 45 by high-pressure side valve element 42a.Thereby, output pressure Prcv warps
First guiding path 45 is imported by low-pressure side automatic anti-fault valve 41 and high-pressure side automatic anti-fault valve 42.There is the automatic of such function
Fail-safe mechanism 25 is connected with drain valve 15, and the discharge pilot pressure Ppil being output is input to drain valve 15.
Drain valve 15 is connected with primary path 16, and primary path 16 is connected with fuel tank 24.Drain valve 15 will flow in primary path 16
Working oil discharge to fuel tank 24, so as to adjust from hydraulic pump 11 flow into flow control mechanism 12 working oil flow.Discharge
Valve 15 is the valve element valve of so-called open type, and the discharge pilot pressure Ppil from automatic anti-fault mechanism 25 acts on valve element
15a.Also, on drain valve 15 arrange elastic member 28, valve element 15a by elastic component 28 to discharge pilot pressure Ppil
The direction force for mutually resisting.The drain valve 15 for so constituting is so that the active force and elastic component of discharge pilot pressure Ppil generations
The form of the 28 applying dynamic balances for producing provides the aperture area of valve element 15a, is spued with pilot pressure Ppil and pump with discharge and is pressed
The working oil of the discharge rate for matching is expelled to fuel tank 24 from hydraulic pump 11 via drain valve 15.
［ work of fluid pressure drive device ］
The work of fluid pressure drive device 1 is below described.In fluid pressure drive device 1, in action bars 13a, 14a, any one is toppled over
When, outbound course output pressure P1～P4 corresponding with the toppling direction of action bars 13a, 14a for being dumped.For example, action bars
13a is forwards（First direction）When toppling over, the first output pressure P1 is exported to first guiding path 17a.First output pressure of output
P1 then selects first output pressure P1 by the first shuttle valve 21 and the 3rd shuttle valve 23, using first output pressure P1 as output
Pressure Prcv is exported from high pressure selection mechanism 19.
Also, detecting pressure by pilot pressure sensor PS1 after the first output pressure P1 of output, control device 30 is based on should
Testing result decision valve 13 operated, and judges whether that the condition of work for meeting regulation is matched with working condition to export
Control pressure Psol.For example, testing result of the control device 30 based on oil temperature sensor 32, judges whether oil temperature meets predetermined
Condition of work（Specially more than set point of temperature）.Another, or, based on the testing result of speed probe 31, judge to start
Whether the rotating speed of machine E meets predetermined condition of work（Specially below egulation rotating speed）, or, based on oil pressure sensor LS1～
The testing result of LS4, judges whether the load of actuator 7,9 meets predetermined condition of work（Specially below given load）.
Control device 30 according to the satisfaction of condition of work whether（I.e., according to working condition）Adjust to the flowing of proportional control solenoid valve 27
The size of electric current.For example, when meeting condition of work, control device 30 can be made than not meeting big current flowing during condition of work,
It is bigger than not meeting control pressure Psol during condition of work to make control pressure Psol when meeting condition of work.And, or,
Respective electric current mapping graph is preset in each actuator 7,9, according to the satisfaction of the condition of work of each actuator 7,9 with
No, the size of the electric current flowed in proportional control solenoid valve 27 is adjusted from control device 30.Like this, by making electric current from control
Device 30 flows into proportional control solenoid valve 27, with this from 27 pressure output control Psol of proportional control solenoid valve.
Automatic anti-fault mechanism 25 is based on the output for exporting from high pressure selection mechanism 19 and proportional control solenoid valve 27 respectively
The absolute value of pressure differential Psol-Prcv of pressure Prcv and control pressure Psol | Psol-Prcv|, from output pressure Prcv and
The oil pressure for being selected as discharge pilot pressure Ppil in control pressure Psol and exporting from automatic anti-fault mechanism 25.For example,
27 normal work of proportional control solenoid valve, and control device 30 according to condition of work by control pressure Psol control in Prcv-
When in the range of Pth1 ＜ Psol ＜ Prcv+Pth2, the absolute value of pressure differential Psol-Prcv | Psol-Prcv| is located at and sets
In control range 52.Consequently, it is possible to control pressure Psol as discharge with pilot pressure Ppil from automatic anti-fault mechanism 25
Output, drain valve 15 are adjusted to the aperture area matched with control pressure Psol.Discharge what pressure matched with the aperture area and pump
The working oil of discharge rate is expelled to fuel tank 24 from hydraulic pump 11 via drain valve 15.
Thus, when control pressure Psol is located in the range of Prcv-Pth1 ＜ Psol ＜ Prcv+Pth2, control can be made
Control pressure Psol that device 30 is controlled according to working condition is exported as discharge pilot pressure Ppil.Thereby, can the row of making
The working oil that output is matched with control pressure Psol is expelled to fuel tank 24 from hydraulic pump 11 via drain valve 15, and energy will be with action bars
The working oil of the flow that the flip angle and condition of work of 13a matches imports flow control mechanism 12 from hydraulic pump 11.Flow is controlled
In mechanism 12, direction switch valve works according to the first output pressure P1 of operation valve 13, i.e., direction switch valve is according to action bars
The toppling direction of 13a and flip angle work.By means of this, the working oil matched with the flip angle of flow action bars 13a is from hydraulic pressure
Pump 11 is supplied to the expansion link of swing arm cylinder 7（rod）Side 7b, swing arm 6 with the speed that matches with the flip angle and with behaviour
Make the direction that the toppling direction of bar 13a matches（I.e., lower section）Topple over.
So in the fluid pressure drive device 1 of work, control pressure Psol can be adjusted in Prcv-Pth1 ＜ Psol ＜
In the range of Prcv+Pth2.Thereby, control device 30 changes the electricity to the flowing of proportional control solenoid valve 27 according to working condition
Stream so as to adjusting control pressure Psol, even if with the flip angle of this action bars 13a is identical also can be according to the work of fluid pressure drive device 1
Make the aperture area of state change drain valve 15.I.e., with according to working condition change to proportional control solenoid valve 27 flowing electricity
The form of stream is set, and can carry out the emission control of precision.For example, the high temperature border when oil temperature is more than set point of temperature
Under, the viscosity of working oil need to supply more pressure fluid to swing arm cylinder 7 when swing arm 6 starts to work, may produce
Impact.In fluid pressure drive device 1, oil temperature is more than set point of temperature and the opening surface for when meeting condition of work, increasing drain valve 15
Product is so as to increasing the discharge rate to fuel tank 24.Thereby, suppress the flow of the working oil of flowing in swing arm cylinder 7 so as to relax
State impact.Similarly, when the rotating speed of engine E increases so as to increase from the discharge-amount of hydraulic pump 11, increase drain valve 15
The aperture of opening so as to increase the discharge rate to fuel tank 24, with this suppress the flow of the working oil of flowing in swing arm cylinder 7 from
And relax the impact.
Thus, in fluid pressure drive device 1, control pressure Psol matched with the working condition is used as discharge pilot pressure
Ppil is exported, and the aperture area of drain valve 15 can be adjusted to the area that matched with control pressure Psol.Accordingly, it is capable to pass through to set
Condition of work relaxes and impacts and improve operability as previously described, can also reduce the aperture of the opening of drain valve 15 on the contrary and seek
Seek energy-saving.Also, proportional control solenoid valve 27 adopts proportional control solenoid valve, therefore, it is possible to the back pressure of accurately controlled output
Pa.Thereby, critically can adjust（tuning ）Operability.Additionally, drain valve 15 can be set for only by control device 30
The adjustment operation of related operability, therefore the adjustment operation of fluid pressure drive device 1 become easy, can shorten fluid pressure drive device
1 research and development time.
On the other hand, it is contemplated that can produce and occur because of the holding wire 46 for connecting proportional control solenoid valve 27 and control device 30
Electric fault（Short-circuit and breaking etc.）And cannot pressure output control Psol, or, because proportional control solenoid valve 27 valve body glue
Stagnant（stick）And proportional control solenoid valve 27 is maintained open or is closed.So, because proportional control solenoid valve 27 etc. breaks down
And during 30 uncontrollable control pressure Psol of control device, control pressure Psol may be in Psol ＜ Prcv-Pth1 or Prcv
In the range of+Pth2 ＜ Psol.Now, pressure differential Psol-Prcv is located at Fisrt fault scope 51 or the second fault coverage 53
Interior, the output pressure Prcv from high pressure selection mechanism 19 is defeated from automatic anti-fault mechanism 25 with pilot pressure Ppil as discharge
Go out.Thereby, drain valve 15 is adjusted to the aperture area matched with control pressure Psol, the work that discharge rate is matched with the aperture area
Make oil fuel tank 24 is expelled to from hydraulic pump 11 via drain valve 15.
Thus, because proportional control solenoid valve 27 etc. breaks down, the control pressure Psol exception matched with working condition
When increase or reduction, the output pressure Prcv that high pressure selection mechanism 19 is exported is as discharge with pilot pressure Ppil from anti-event automatically
Barrier mechanism 25 exports.Therefore, even if proportional control solenoid valve 27 etc. breaks down, also can be according to the flip angle of action bars 13a
And correspondingly make drain valve 15 work, prevent 15 function of drain valve from losing.
In fluid pressure drive device 1, the absolute value of pressure differential Psol-Prcv is in advance based on | Psol-Prcv| is selected as
Oil pressure of the discharge with pilot pressure Ppil outputs, judges the boundary value for selecting which kind of oil pressure, is low-pressure side force application component 41b and height
Applying power distinguished corresponding critical pressure Pth1, Pth2 of pressure side force application component 42b.Therefore, by changing low-pressure side force structure
Part 41b and high-pressure side force application component 42b, can change critical pressure Pth1, the Pth2 as the boundary value using this, by means of
This, can change the scope for setting control range 52.And, suitably set by adjusting critical pressure Pth1, Pth2
Control range 52, even if can be as described above, solenoid electric valve breaks down etc. and uncontrollable control pressure with this, also can basis
The output pressure of operation valve makes drain valve work, and caused by suppressing barrier etc. for some reason, 15 function of drain valve is lost.
Multiple action bars 13a, 14a, the situation that specially two action bars 13a, 14a topple over simultaneously are described below.Two
When action bars 13a, 14a topple over simultaneously, each operation valve 13,14 exports output pressure P1～P4 respectively.For example, action bars 13a to
Second direction（I.e., rear）Topple over and action bars 14a is to first direction（I.e., front）When toppling over, to first guiding path 17b outputs the
Two output pressure P2, export the 3rd output pressure P3 to first guiding path 18a.Second output pressure P2 and the 3rd output pressure P3 are defeated
When going out, the first shuttle valve 21 and the second shuttle valve 22 select the second output pressure P2 and the 3rd output pressure P3 respectively, and to the 3rd shuttle
Valve 23 exports the second output pressure P2 and the 3rd output pressure P3.3rd shuttle valve 23 selects the outputs of the second output pressure P2 and the 3rd
In pressure P3, any higher side, exports to automatic anti-fault mechanism 25 as output pressure Prcv.Automatic anti-fault machine
Absolute value of the structure 25 according to the pressure differential of the output pressure Prcv and control pressure Psol for so exporting, such as afore-mentioned are in the same manner
Using in output pressure Prcv and control pressure Psol, any one is exported as discharge with pilot pressure Ppil.Therefore, the pressure
Poor absolute value not set in control range 52 and output pressure Prcv exported with pilot pressure Ppil as discharge when, according to
Maximum output pressure in first output pressure P1～the 4th output pressure P4, adjusts the pressure for being expelled to fuel tank 24 from hydraulic pump 11
The discharge rate of power liquid.Therefore, the bigger discharge rate of maximum output pressure is less, can be to actuator 7,9 sides for giving operated two
The flow that maximum flip angle matches in the flip angle of individual action bars 13a, 14a.Thereby, can suppress because of underfed and cause
Actuator work relaxation.
Separately, when two action bars 13a, 14a topple over simultaneously, control device 30 is according to maximum output Stress control control pressure
Psol.Therefore, when the pressure differential of output pressure Prcv and control pressure Psol is located at and sets in control range 52, with output pressure
Prcv is identical when being chosen, and control pressure Psol can will be maximum with the flip angle of two action bars 13a, 14a being operated
The flow that flip angle matches is supplied to actuator 7,9 sides, can be suppressed because of underfed and the work of caused actuator relaxation.
The second embodiments ＞ of ＜
The structure of the fluid pressure drive device 1A of the second embodiment is similar with the fluid pressure drive device 1 of first embodiment,
The main pressure source in proportional control solenoid valve 27A be on the output pressure Prcv of high pressure selection mechanism 19 aspects and
Possess different from the fluid pressure drive device 1 of first embodiment on the automatic anti-fault mechanism 25A aspects.Hereinafter, further in detail
The fluid pressure drive device 1A of the second embodiment is described, but is only illustrated different from the fluid pressure drive device 1 of first embodiment
Point, in addition identical structure be marked with same-sign and omit the description.
In fluid pressure drive device 1A, as shown in figure 4, the once pressure side of proportional control solenoid valve 27A be connected the 3rd shuttle valve
23 and the path 47 of drain valve 15 connect, proportional control solenoid valve 27A is by the output pressure Prcv from high pressure selection mechanism 19
Pressure output control Psol after decompression.The output pressure that will be exported from high pressure selection mechanism 19 and proportional control solenoid valve 27A respectively
Power Prcv and control pressure Psol input automatic anti-fault mechanism 25A.Automatic anti-fault mechanism 25A has low-pressure side anti-event automatically
Barrier valve 41A, low-pressure side automatic anti-fault valve 41A have low-pressure side valve element 41a and low-pressure side force application component 41b.Work as output pressure
When pressure differential Psol-Prcv of Prcv and control pressure Psol is " Psol-Prcv ＜-Pth1 ", low-pressure side automatic anti-fault
Valve 41A connects high pressure selection mechanism 19 and first guiding path 45, and output pressure Prcv is defeated with pilot pressure Ppil as discharge
Go out.Also, when pressure differential Psol-Prcv of output pressure Prcv and control pressure Psol is "-Pth1 ＜ Psol-Prcv ",
Low-pressure side automatic anti-fault valve 41A makes proportional control solenoid valve 27 be connected with first guiding path 45, using control pressure Psol as row
Put and exported with pilot pressure Ppil.
In the fluid pressure drive device 1A for so constituting, proportional control solenoid valve 27A normal work, control device 30 is according to work
Make state and execute control, when making control pressure Psol be changed into " Prcv-Pth1 ＜ Psol ", control pressure Psol is used as discharge
Pilot pressure Ppil is exported.By means of this, the working oil that discharge rate is matched with control pressure Psol can be from hydraulic pump 11 via row
Put valve 15 and be expelled to fuel tank 24, the working oil of the flow matched with the flip angle and condition of work of action bars 13a can be from hydraulic pump
11 import flow control mechanism 12.On the other hand, proportional control solenoid valve 27A etc. breaks down, so as to be filled by control
When putting 30 control control pressures Psol and then being changed into " Psol ＜ Prcv-Pth1 ", output pressure Prcv is used as discharge elder generation's pilot
Power Ppil is exported.By means of this, the working oil that discharge rate is matched with output pressure Prcv can be from hydraulic pump 11 via drain valve 15
It is expelled to fuel tank 24.Therefore, even if proportional control solenoid valve 27A etc. breaks down, also can be according to the flip angle of action bars 13a
Correspondingly make drain valve 15 work, prevent the function of drain valve 15 from losing.
In fluid pressure drive device 1A, output pressure Prcv as pressure source, is not therefore being grasped by proportional control solenoid valve 27A
At the neutral position of action bars 13a, 14a for operating valve 13,14, even if proportional control solenoid valve 27A is delayed work, drain valve 15
Also it is not turn off.Therefore, there is automatic anti-fault in fluid pressure drive device 1A.Also, without the need for proportional control solenoid valve 27A
Pioneer pump（For example, the second pioneer pump 26 of the fluid pressure drive device 1 of first embodiment）, number of components can be reduced.
It is identical with the fluid pressure drive device 1 of first embodiment that the fluid pressure drive device 1A of the second embodiment plays other
Action effect.
［ other embodiments ］
In the fluid pressure drive device 1,1A of first and second embodiment, electricity of the proportional control solenoid valve 27 using closed type
Magnetic proportional control valve, but the electromagnetism using open type also may be used against proportional control valve.Also, the fluid pressure drive device of first embodiment
In 1, automatic anti-fault mechanism 25 possesses two automatic anti-fault valves 41,42, but need not also possess two.Also, executing
Device 7,9,10 is not limited to above-mentioned, can also be steering（steering）With cylinder or traveling drive motor.Also, hydraulic pump 11
Need not be the pump of variable capacity type, the pump of fixed capacity type also may be used.Additionally, the pressure fluid for being used is not limited to work
Oil, water or other liquid also may be used.
According to the above description, those skilled in the art understand the more improvement of the present invention and other embodiments.Therefore, on
The bright example that is only used as is stated for illustrating, and is the optimal modality for implementing the present invention is instructed as mesh to those skilled in the art
And offer.Without departing from the concept thereof of the present invention, other structures and/or function can be substantially changed to.
Symbol description：
1st, 1A fluid pressure drive devices；
7 swing arm cylinders；
9 dipper cylinders；
10 scraper bowl cylinders；
11 hydraulic pumps；
12 flow control mechanisms；
13rd, 14 operation valve；
13a, 14a action bars；
15 drain valves；
19 high pressure selection mechanisms
25 automatic anti-fault mechanisms；
26 second pioneer pumps
27th, 27A proportional control solenoid valves
30 control devices；
41a low-pressure side valve elements；
41b low-pressure side force application components；
42a high-pressure sides valve element；
42b high-pressure sides force application component.
Claims (6)
1. a kind of fluid pressure drive device, is to supply to actuator the pressure fluid that hydraulic pump spues so as to driving the actuator
Fluid pressure drive device, possesses：
Be provided with action bars, and operate the action bars then export with operational ton match pressure output pressure operation valve；
According to the output pressure adjust aperture, by the pressure fluid of the flow matched with the load of the aperture and the actuator from
The hydraulic pump is supplied to the flow control mechanism of the actuator；
Output be controlled as with input drive signal match pressure control pressure solenoid electric valve；
The pressure differential of the output pressure and the control pressure is in predetermined setting control range then by the control pressure
Export as pilot pressure, the pressure differential departs from the setting control range then will be defeated as pilot pressure for the output pressure
The automatic anti-fault mechanism for going out；With
Pilot pressure according to automatic anti-fault mechanism output adjusts aperture area, and flow is matched with the aperture area
Pressure fluid be expelled to the drain valve of fuel tank from the hydraulic pump.
2. fluid pressure drive device according to claim 1, it is characterised in that
The automatic anti-fault mechanism has：
The output pressure and the control pressure are acted in the form of mutually resisting, and change the low of position according to the power of effect
Pressure side valve core；With
The low-pressure side force application component that the applying power mutually resisted with the output pressure is imposed on the low-pressure side valve element；
The low-pressure side valve element is selected the output pressure or the control pressure as the pilot pressure according to its position
Output；
The output pressure changes the position of the low-pressure side valve element and acts on the low-pressure side valve element, so that the output pressure
Power is selected as the pilot pressure；
The control pressure changes the position of the low-pressure side valve element and acts on the low-pressure side valve element, so that the control pressure
Power is selected as the pilot pressure.
3. fluid pressure drive device according to claim 1 and 2, it is characterised in that
Export as the control pressure after the pressure fluid decompression that pioneer pump is spued by the solenoid electric valve；
The automatic anti-fault mechanism has：The output pressure and the control pressure are acted in the form of mutually resisting, and
Power according to effect changes the high-pressure side valve element of position；With
The high-pressure side force application component that the applying power mutually resisted with the control pressure is imposed on the high-pressure side valve element；
The high-pressure side valve element is selected the output pressure or the control pressure as the pilot pressure according to its position
Output, the control pressure is more than the output pressure and described in the pressure differential disengaging of the control pressure and the output pressure
When setting control range, then the output pressure is preferentially exported as the pilot pressure.
4. fluid pressure drive device according to claim 1 and 2, it is characterised in that the solenoid electric valve and the operation
Valve connects, and exports as the control pressure after the output pressure decompression that the operation valve is exported.
5. fluid pressure drive device according to claim 1 and 2, it is characterised in that
Possess the control device that the drive signal is exported according to working condition to the solenoid electric valve；
Mode of operation of the working condition comprising the action bars, the rotating speed of the engine of the driving hydraulic pump, the pressure
The temperature of power liquid and at least one state in acting on the load of the actuator.
6. fluid pressure drive device according to claim 1 and 2, it is characterised in that possess：
The multiple described operation valve respectively correspondingly arranged with multiple actuators；With
The output pressure selection mechanism of highest output pressure is selected from the output pressure of multiple operation valve outputs；
When operating the operation valve and exporting output pressure, the flow control mechanism to the operation valve for being operated right
The pressure fluid that the actuator supply flow rate that answers is matched with the output pressure；
When the pressure differential departs from the setting control range, the output pressure is selected machine by the automatic anti-fault mechanism
The selected output pressure of structure is exported as pilot pressure.
Applications Claiming Priority (3)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2013-226720 | 2013-10-31 | ||
| JP2013226720A JP6228430B2 (en) | 2013-10-31 | 2013-10-31 | Hydraulic drive device |
| PCT/JP2014/005286 WO2015064044A1 (en) | 2013-10-31 | 2014-10-17 | Hydraulic drive unit |
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| Publication Number | Publication Date |
|---|---|
| CN105612359A CN105612359A (en) | 2016-05-25 |
| CN105612359B true CN105612359B (en) | 2017-03-15 |
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| Application Number | Title | Priority Date | Filing Date |
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| CN201480057066.2A Active CN105612359B (en) | 2013-10-31 | 2014-10-17 | Fluid pressure drive device |
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|---|---|
| JP (1) | JP6228430B2 (en) |
| CN (1) | CN105612359B (en) |
| WO (1) | WO2015064044A1 (en) |
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| JP6603568B2 (en) * | 2015-12-14 | 2019-11-06 | 川崎重工業株式会社 | Hydraulic drive system |
| WO2018224834A1 (en) | 2017-06-09 | 2018-12-13 | Liberty Vehicle Technologies Limited | Fluidic control system |
| GB2555884B (en) * | 2017-06-09 | 2018-10-24 | Liberty Vehicle Tech Limited | Fluidic control system |
| US11415154B2 (en) * | 2019-04-12 | 2022-08-16 | Husco International, Inc. | Hydraulic systems and methods for nested pressure regulating valves |
| JP7297617B2 (en) * | 2019-09-13 | 2023-06-26 | 日本ムーグ株式会社 | Electro-hydraulic actuator system, hydraulic circuit for electro-hydraulic actuator system, and steam turbine system including the same |
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| CN102704524A (en) * | 2012-04-19 | 2012-10-03 | 华南理工大学 | Rotary energy saving system of hydraulic excavator |
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| JPH11303809A (en) * | 1998-04-20 | 1999-11-02 | Komatsu Ltd | Pump control device for hydraulic drive machine |
| JP2001200802A (en) * | 2000-01-13 | 2001-07-27 | Teijin Seiki Co Ltd | Hydraulic drive unit |
| JP2004360898A (en) * | 2003-05-15 | 2004-12-24 | Kobelco Contstruction Machinery Ltd | Hydraulic control device for working machine |
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| EP1022395A1 (en) * | 1998-07-07 | 2000-07-26 | Kabushiki Kaisha Kobe Seiko Sho | Hydraulic control device of working machine |
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| CN100385081C (en) * | 2003-05-15 | 2008-04-30 | 神钢建设机械株式会社 | Hydraulic controller for working machine |
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| CN101457778A (en) * | 2007-12-10 | 2009-06-17 | 沃尔沃建造设备控股（瑞典）有限公司 | Hydraulic circuit having holding valve of external pilot pressure operation type |
| CN102704524A (en) * | 2012-04-19 | 2012-10-03 | 华南理工大学 | Rotary energy saving system of hydraulic excavator |
Also Published As
| Publication number | Publication date |
|---|---|
| WO2015064044A1 (en) | 2015-05-07 |
| CN105612359A (en) | 2016-05-25 |
| JP6228430B2 (en) | 2017-11-08 |
| JP2015086963A (en) | 2015-05-07 |
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