CN107061382B - Positive flow imports and exports independent composite control hydraulic system - Google Patents
Positive flow imports and exports independent composite control hydraulic system Download PDFInfo
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- CN107061382B CN107061382B CN201710228940.XA CN201710228940A CN107061382B CN 107061382 B CN107061382 B CN 107061382B CN 201710228940 A CN201710228940 A CN 201710228940A CN 107061382 B CN107061382 B CN 107061382B
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Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B9/00—Servomotors with follow-up action, e.g. obtained by feed-back control, i.e. in which the position of the actuated member conforms with that of the controlling member
- F15B9/02—Servomotors with follow-up action, e.g. obtained by feed-back control, i.e. in which the position of the actuated member conforms with that of the controlling member with servomotors of the reciprocatable or oscillatable type
- F15B9/08—Servomotors with follow-up action, e.g. obtained by feed-back control, i.e. in which the position of the actuated member conforms with that of the controlling member with servomotors of the reciprocatable or oscillatable type controlled by valves affecting the fluid feed or the fluid outlet of the servomotor
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B13/00—Details of servomotor systems ; Valves for servomotor systems
- F15B13/02—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors
- F15B13/06—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with two or more servomotors
Abstract
A kind of positive flow imports and exports independent composite control hydraulic system, the composite control hydraulic system is added there are four proportional throttle valve, two two-position two-way solenoid valves, by pumping the complex controll with terminal valve, adjust the pressure and flow of hydraulic motor and two chamber of hydraulic cylinder, hydraulic motor and hydraulic pump is made to start and realize quick, steady and efficient operation in braking process, while is avoided in traditional positive flow control hydraulic system because of a large amount of restriction losses caused by on-demand fuel feeding.
Description
Technical field
It is particularly a kind of only with importing and exporting for positive flow the present invention relates to a kind of hydraulic system of independent complex controll
The technical solution of the hydraulic system of vertical complex controll.
Background technology
Often there is the problem of high oil temperature to engineering machinery in hydraulic system in use, is shown according to factual survey,
The oil temperature of hydraulic system is to influence hydraulic system and the master of reliability of hydraulic component and complete machine working efficiency when engineering machinery works
Want one of factor.Therefore ensure that the thermal equilibrium temperature of construction machinery hydraulic system is in normal condition, be to ensure that engineering machinery can
By work and the key of raising hydraulic system efficiency.The common control loop of hydraulic construction machine has load sensitive system, positive stream
Amount control system and inverted flux control system etc..Positive flow variable pump is an external control variable pump, and stroking mechanism is by external control
Pressing pressure controls：Control pressure is higher, and discharge capacity is bigger.Its operation principle is：Signal acquisition on the main control valve of positive flow in
Pilot pressure valve, the discharge capacity of main pump are directly proportional to the signal pressure that pilot operated handle exports.Master controller is according to different elder generations
Pilot force signal judges the flow demand of actuator, and discharge of main pump is implemented to adjust according to pressure signal so that the stream of system
Amount supplies dynamically follow the flow demand of executive component, realizes the real-time matching of flow system flow, reaches energy-on-demand.
It is still controlled in traditional engineering machinery positive stream amount control system using multi-way valve as main control valve, only
One control freedom degree, oil inlet and outlet area relationship immobilize, and synchronization can only control a chamber of hydraulic actuator
Pressure or flow, poor controllability；Actuator inlet and outlet throttle simultaneously during work, and the pressure loss is big, particularly in Exceed load work
Under condition, this problem is even more serious, causes big energy consumption and system heat generation.
Publication No. CN102758464A discloses " a kind of control method of excavator positive-flow hydraulic system ", according to elder generation
The pressure for leading handle carries out positive flow control to two main pumps, and system controllability and measurability is poor, and valve port restriction loss is big, system heat generation problem
Seriously, especially under Exceed load operating mode, these problems are more prominent.
Invention content
In view of the deficiency of the prior art, the present invention provides a kind of positive flow and imports and exports independent composite control hydraulic
The shortcomings that system controls poor controllability in hydraulic system to solve traditional positive flow, and valve port restriction loss is big, further reduces
Restriction loss reduces fever, improves the revolution stationarity of engineering machinery and the energy-efficient performance of totality.
To achieve the above object, the present invention adopts the following technical scheme that.
A kind of positive flow imports and exports independent composite control hydraulic system, including main pump control valve, variable piston, signal amplification
Device, power source, main pump, pioneer pump, safety valve, the Ith master control banked direction control valves, the IIth master control banked direction control valves, the IIIth master control banked direction control valves, swing arm
Hydraulic cylinder, rotary fluid motor, the Ith Rotatary brake valve, the IIth Rotatary brake valve, the Ith check valve, the IIth check valve, the Ith operation
Handle and the IIth operation handle and fuel tank；It is characterized in that：
Have additional the Ith proportional throttle valve, the IIth proportional throttle valve, the IIIth proportional throttle valve, the IVth proportional throttle valve, the Ith
Two-position two-way solenoid valve and the IIth two-position two-way solenoid valve；
The H mouths of Ith proportional throttle valve are communicated with the rod chamber of boom cylinder；
The I mouths of IIth proportional throttle valve are communicated with the rodless cavity of boom cylinder；
The actuator port G of IIIth proportional throttle valve is communicated with the oil inlet X of rotary fluid motor；
The Y mouths of the actuator port L connection rotary fluid motors of IVth proportional throttle valve；
Ith proportional throttle valve, the IIth proportional throttle valve, the IIIth proportional throttle valve and the IVth ratio
Oil outlet T1, oil outlet T2, oil outlet T3 and the oil outlet T4 of throttle valve are communicated with fuel tank；
The composite control hydraulic system is by pumping the complex controll with terminal valve, adjusting hydraulic motor and hydraulic cylinder two
The pressure and flow of chamber make hydraulic motor and hydraulic pump start and realize quick, steady and Effec-tive Function in braking process.
In the above-mentioned technical solutions, the Ith proportional throttle valve, the IIth proportional throttle valve, the IIIth proportional throttle valve and
IV proportional throttle valve is pilot proportional throttle valve or direct action type proportional throttle valve.
In the above-mentioned technical solutions, the Ith two-position two-way solenoid valve and the IIth two-position two-way solenoid valve are pilot-operated types two
Position two-way electromagnetic valve or direct-acting type two-position two-way electromagnetic valve.
There is above-mentioned technical proposal of the present invention clear advantage and advantageous effect to be：Positive flow is independent compound with inlet and outlet
Hydraulic system is controlled, positive flow control makes the flow in hydraulic pump increase with the increase of control pressure signal, that is, controls oil pressure
It is directly proportional to flow；Rotary fluid motor uses two bi-bit bi-pass electromagnetic proportion throttles, by it by inlet and outlet independent control
Mode is controlled；Compared with prior art, control valve oil inlet and oil return is throttled to be changed to import and export and be throttled respectively by the present invention simultaneously, is subtracted
Lack the restriction loss at valve port, reduced system heat generation, particularly in Exceed load operating mode, not only significantly reduce throttling damage
It loses, and the speed of service of hydraulic actuator can be improved, facilitate and realize flow regeneration, effect is more notable；Independent control actuator
Two cavity pressures or flow improve the controllability of work system, make system operation more steady；Import can be respectively adopted as needed
Throttle grverning, outlet throttle timing and the independent composite throttling speed governing of inlet and outlet；Traditional positive flow control can be retained as needed
Hydraulic system can also use positive flow to import and export independent composite control hydraulic system.
In order to more clearly illustrate the structure feature and effect of the present invention, come with specific embodiment below in conjunction with the accompanying drawings to this
Invention is described in detail.
Description of the drawings
Fig. 1 shows the surface structure schematic diagram of excavator in the embodiment of the present invention.
Fig. 2 is the principle schematic diagram of the present invention.
In figure：1st, main pump control valve；2nd, variable piston；3rd, signal amplifier；4th, power source；5th, main pump；6th, pioneer pump；
7th, safety valve；8th, the Ith master control banked direction control valves；9th, the IIth master control banked direction control valves；10th, the Ith proportional throttle valve；11st, the IIth proportional throttle valve；
12nd, the IIIth proportional throttle valve；13rd, the IVth proportional throttle valve；14th, boom cylinder；15th, rotary fluid motor；16th, the Ith revolution
Brake valve；17th, the IIth Rotatary brake valve；18th, the Ith check valve；19th, the IIth check valve；20th, fuel tank；21st, the Ith operation handle；
22nd, the IIth operation handle；23rd, the Ith swing arm control pilot valve；24th, the IIth swing arm control pilot valve；25th, the Ith revolution control guide
Valve；26th, the IIth revolution control pilot valve；27th, the IIIth master control banked direction control valves；28th, the Ith two-position two-way solenoid valve；29th, the IIth 2 two
Three-way electromagnetic valve；30th, it gets off；31st, it gets on the bus；32nd, swing arm；33rd, dipper hydraulic cylinder；34th, bucket hydraulic cylinder；35th, dipper；6th, scraper bowl.
P：IIIth master control banked direction control valves oil inlet；P1、P2：Ith master control banked direction control valves oil inlet oil inlet；P3、P4：IIth master control
Multi-way valve oil inlet；T：Oil outlet；A、B、C：Ith master control banked direction control valves actuator port；D、E、F：IIth master control banked direction control valves working oil
Mouthful；H：Ith proportional throttle valve actuator port；I：IIth proportional throttle valve actuator port；G：IIIth proportional throttle valve actuator port；
L：IVth proportional throttle valve actuator port；X、Y：Rotary fluid motor hydraulic fluid port；N、O：IIIth master control banked direction control valves actuator port；M：It is main
Pump control valve actuator port；Q：Ith master control banked direction control valves oil outlet；R：IIth master control banked direction control valves actuator port；V：Ith bi-bit bi-pass
Solenoid valve oil inlet；W：IIth two-position two-way solenoid valve oil inlet；K：Main pump control valve remote control orifice；K1、K2：Ith master control
Multi-way valve remote control orifice；K3、K4：IIth master control banked direction control valves remote control orifice.
Specific embodiment
Implement the technical solution that a kind of positive flow imports and exports independent composite control hydraulic system, with reference to shown in attached drawing 2, show
It shows the concrete structure that the specific embodiment of the invention is 20t excavators, is put including main pump control valve 1, variable piston 2, signal
Big device 3, power source 4, main pump 5, pioneer pump 6, safety valve 7, the Ith master control banked direction control valves 8, the IIth master control banked direction control valves 9, the Ith Direct Action Type
Proportional throttle valve 10, the IIth direct action type proportional throttle valve 11, the IIIth direct action type proportional throttle valve 12, the throttling of the IVth direct action type proportional
Valve 13, boom cylinder 14, rotary fluid motor 15, the Ith Rotatary brake valve 16, the IIth Rotatary brake valve 17, the Ith check valve
18th, the IIth check valve 19, fuel tank 20, the Ith operation handle 21, the IIth operation handle 22, the Ith swing arm control pilot valve the 23, the IIth
Swing arm control pilot valve 24, the Ith revolution control pilot valve 25, the IIth revolution control pilot valve 26, the IIIth master control banked direction control valves 27, the
I self-action two-position two-way solenoid valve 28, the IIth self-action two-position two-way solenoid valve 29.Wherein：
The power source 4, pioneer pump 6 and main pump 5 are coaxially connected, and the Ith proportional throttle valve actuator port H and the Ith master control are more
Road valve actuator port A is all connected with the rod chamber of boom cylinder 14, the IIth proportional throttle valve actuator port I and the Ith master control multichannel
Valve actuator port C is all connected with the rodless cavity of boom cylinder 14, the IIIth proportional throttle valve actuator port G, the IIth master control banked direction control valves
The oil outlet of actuator port D, the oil inlet of the Ith Rotatary brake valve 16 and the Ith check valve 18 are all connected with rotary fluid motor oil
Mouthful X, the IVth proportional throttle valve actuator port L, the IIth master control banked direction control valves actuator port F, the IIth Rotatary brake valve 17 oil inlet
And the IIth check valve 19 oil outlet connection rotary fluid motor hydraulic fluid port Y, the Ith two-position two-way solenoid valve oil inlet V connections the Ith
Master control banked direction control valves oil outlet Q, the IIth master control banked direction control valves actuator port R of the IIth two-position two-way solenoid valve oil inlet W connections, the Ith ratio
Example throttle valve, the IIth proportional throttle valve, the IIIth proportional throttle valve and the IVth proportional throttle valve oil outlet T1, T2, T3 and T4, the Ith
Two-position two-way solenoid valve and the IIth two-position two-way solenoid valve oil outlet T5 and T6, the Ith Rotatary brake valve and the IIth Rotatary brake valve
Oil outlet and the Ith check valve, the IIth check valve oil inlet connect fuel tank 20；Ith master control banked direction control valves oil inlet P 1 and oil inlet
Mouth P2, the IIth master control banked direction control valves oil inlet P4And the IIIth master control banked direction control valves oil inlet P connect the oil outlet of main pump 5, the Ith master
It controls multi-way valve actuator port B and connects the IIth master control banked direction control valves oil inlet P 3, the Ith master control banked direction control valves remote control orifice K1 connections the Ith
Swing arm controls the oil outlet of pilot valve 23, and the Ith master control banked direction control valves remote control orifice K2 connects the IIth swing arm control pilot valve 24
Oil outlet；The oil outlet of the Ith revolution control pilot valve 25 of IIth master control banked direction control valves remote control orifice K3 connections, the IIth master control multichannel
The oil outlet of the IIth revolution control pilot valve 26 of valve remote control orifice K4 connections；IIIth master control banked direction control valves oil outlet T and fuel tank 20
It is connected, the IIIth master control banked direction control valves actuator port O and actuator port N are respectively communicated with other actuator both ends；Variable piston it is small
The oil inlet of chamber and main pump control valve 1 connects the oil outlet of pioneer pump 6, and the oil outlet T of main pump control valve 1 connects fuel tank 20,
The big chamber of main pump control valve actuator port M connection variables piston 2；Variable piston 2 is connected with signal amplifier 3；Ith swing arm controls
The oil inlet of pilot valve 23, the IIth swing arm control revolution control revolution control pilot valve 26 of pilot valve the 25, the IIth of pilot valve 24 and the Ith
Mouth connects the oil outlet of main pump 5, and the Ith swing arm control pilot valve 23, the remote control orifice of the IIth swing arm control pilot valve 24 are equal
The Ith operation handle 21 is connected, the remote control orifice of the Ith revolution control revolution control pilot valve 26 of pilot valve the 25, the IIth connects
IIth operation handle 22.
With reference to shown in attached drawing 2, the work structuring principle that the present embodiment is described in detail is as follows：
（1）The pilot pressure signal of Ith operation handle 21 output controls pilot valve 23, the IIth swing arm control by the Ith swing arm
Pilot valve 24 processed is transmitted to passes through the Ith revolution with the Ith master control banked direction control valves 8, the pilot pressure signal of the IIth operation handle 22 output
The control revolution control pilot valve 17 of pilot valve the 16, the IIth is transmitted to main pump control valve remote control hydraulic fluid port K and the IIth master control simultaneously
Multi-way valve 9, while the pilot pressure signal of the Ith operation handle 21, the IIth operation handle 22 output is transmitted by signal amplifier 3
To main pump control valve 1, pilot control pressure is bigger, and the pressure of the big chamber of servo variable displacement piston 2 is bigger, servo variable displacement piston 2 to
It moves right, the swashplate angle of variable pump 5 is bigger, and the output flow of variable pump 5 is bigger.
（2）When the second operation handle 22 by control the Ith swing arm control pilot valve 23, Ι Ι swing arms control pilot valve 24,
Ι revolution controls pilot valve 25, Ι Ι revolution control pilot valves 26 make Ι master control banked direction control valves 8 and Ι Ι main valves 9 in circuit locate
When middle position, hydraulic fluid port P1-A, C-T or P1-C of Ι master control banked direction control valves 8, the hydraulic fluid port P1-D of A-C and Ι Ι master control banked direction control valves 9,
F-T or P1-F, D-T are turned off, and the hydraulic fluid port P-E off-loads of hydraulic fluid port P-B and Ι the Ι master control banked direction control valves of Ι master control banked direction control valves 8 are returned
Road is connected, and whole flows of main pump 5 flow back into fuel tank 20, so that positive flow control pressure is minimum value so that main pump 5
Discharge capacity is automatically reduced to minimum, substantially reduces empty stream loss.
（3）When the second operation handle 22 by control the Ith swing arm control pilot valve 23, Ι Ι swing arms control pilot valve 24,
Ι revolution controls pilot valve 25, Ι Ι revolution control pilot valves 26 make circuit Ι master control banked direction control valves 8 or Ι Ι master control multichannels
When valve 9 is between left position and middle position, the output flow part of main pump 5 passes through the hydraulic fluid port P1-A of Ι master control banked direction control valves 8 or
The hydraulic fluid port P1-D of Ι Ι master control banked direction control valves 9 enters the rodless cavity of corresponding Ι working cylinders 14.1 and Ι Ι working cylinders 14.2 or returns
The hydraulic fluid port H-T or the IVth electromagnetic proportion throttle 13 of one chamber of rotating hydraulic motor 15, at this time Ι electromagnetic proportion throttles 10
Hydraulic fluid port L-T connect, the hydraulic fluid port G-T of the hydraulic fluid port I-T or Ι Ι Ι electromagnetic proportion throttles 12 of Ι Ι electromagnetic proportion throttles 11
It closes, therefore the hydraulic oil of another chamber of the rod chamber or rotary motor 15 of Ι working cylinders 14.1 and Ι Ι working cylinders 14.2
Fuel tank is flow back by the hydraulic fluid port H-T of Ι electromagnetic proportion throttles 10 or the hydraulic fluid port L-T of the 4th electromagnetic proportion throttle 13
20, it can be controlled by controlling the size of 10 or the 4th 13 valve opening mouths of electromagnetic proportion throttle of Ι electromagnetic proportion throttles
Ι working cylinders 14.1 and the flow or pressure of 14.2 rod chamber of Ι Ι working cylinders or another chamber of rotary fluid motor are made, makes it
Steadily operated with the operating speed of needs, so as to reduce the restriction loss that valve port goes out, the discharge capacity of main pump 5 increases to be made with meeting
The needs of industry speed；When Ι master control banked direction control valves 8 or Ι Ι master control banked direction control valves 9 are located at limit on the left position, the output stream of main pump 5
Amount all passes through the hydraulic fluid port P of Ι master control banked direction control valves 81The hydraulic fluid port P of-A or Ι Ι master control banked direction control valves 91- D enters corresponding Ι works
Make the rodless cavity of cylinder 14.1 and Ι Ι working cylinders 14.2 or a chamber of rotary motor 15, the discharge capacity of main pump 5 increase to it is maximum with
Meet the needs of operating speed
（4）When the second operation handle 22 by control the Ith swing arm control pilot valve 23, Ι Ι swing arms control pilot valve 24,
Ι revolution controls pilot valve 25, Ι Ι revolution control pilot valves 26 make circuit Ι main valves 8 or Ι Ι main valves 9 be located at right position and
When between middle position, hydraulic fluid port P that the flow part of variable pump 5 passes through Ι master control banked direction control valves 81- C or Ι Ι master control banked direction control valves 9
Hydraulic fluid port P1- F enters corresponding Ι working cylinders 14.1 and the rod chamber of Ι Ι working cylinders 14.2 or a chamber of rotary motor 15,
The hydraulic fluid port L-T of the hydraulic fluid port H-T of Ι electromagnetic proportion throttles 10 or the 4th electromagnetic proportion throttle 13 is closed at this time, Ι Ι electricity
The hydraulic fluid port G-T of the hydraulic fluid port I-T or Ι Ι Ι electromagnetic proportion throttles 12 of magnetic proportional throttle valve 11 is connected, therefore Ι working cylinders
The hydraulic oil of the rodless cavity of 14.1 and Ι Ι working cylinders 14.2 or another chamber of rotary motor 15 passes through Ι Ι solenoid-operated proportional sections
The hydraulic fluid port G-T for flowing the hydraulic fluid port I-T or Ι Ι Ι electromagnetic proportion throttles 12 of valve 11 flow back into fuel tank, can be by controlling Ι Ι
The size of electromagnetic proportion throttle 11 or Ι Ι Ι 12 valve opening mouths of electromagnetic proportion throttle controls 14.1 He of Ι working cylinders
The flow or pressure of 15 another chamber of rodless cavity or rotary fluid motor of Ι Ι working cylinders 14.2 make their operations with needs
Speed steadily operates, and so as to reduce the restriction loss that valve port goes out, the discharge capacity of main pump 5 increases the needs to meet operating speed；
When circuit Ι master control banked direction control valves 8 or Ι Ι master control banked direction control valves 9 are located at limit on the right-right-hand limit position, whole flows of main pump 5 pass through Ι
The hydraulic fluid port P of master control banked direction control valves 81The hydraulic fluid port P of-C or Ι Ι master control banked direction control valves 91- F enters corresponding Ι working cylinders 14.1 and Ι
The rod chamber of Ι working cylinders 14.2 or a chamber of rotary fluid motor 15, the discharge capacity of variable pump 5 increase to maximum to meet operation
The needs of speed.
The design focal point of the present invention is：While making the displacement variation of variable pump by positive flow control, by work
Make cylinder and two chamber of rotary motor adds the electromagnetic proportion throttle of a 2/2-way respectively, when variable pump by main valve to working cylinder
Or during one chamber fuel feeding of rotary motor, the pressure or flow of one chamber of fuel feeding are controlled by main valve, working cylinder or the other chamber of rotary motor
The electromagnetic proportion throttle of connection controls the pressure of this chamber or flow by the movement of spool, thereby realizes oil inlet and outlet
The independent control of pressure or flow reduces the restriction loss at valve port, reduces the loss of power and system hair to the maximum extent
Heat, and improve the stationarity and controllability of working cylinder and rotary motor.
By pumping the complex controll with terminal valve, the pressure and flow of hydraulic motor and two chamber of hydraulic cylinder are adjusted, makes liquid
Pressure motor and hydraulic pump are starting and are realizing quick, steady and efficient operation, while avoid traditional positive stream in braking process
A large amount of restriction loss caused by fuel feeding on demand in amount control hydraulic system.
The above is only the preferable implementation of the present invention, is not intended to limit the scope of the present invention, therefore
Any subtle modifications, equivalent variations and modifications that every technique according to the invention substantially makees above example, still belong to
In the range of technical solution of the present invention.
Claims (3)
1. a kind of positive flow imports and exports independent composite control hydraulic system, including main pump control valve, variable piston, signal amplification
Device, power source, main pump, pioneer pump, safety valve, the Ith master control banked direction control valves, the IIth master control banked direction control valves, the IIIth master control banked direction control valves, swing arm
Hydraulic cylinder, rotary fluid motor, the Ith Rotatary brake valve, the IIth Rotatary brake valve, the Ith check valve, the IIth check valve, the Ith operation
Handle and the IIth operation handle and fuel tank；It is characterized in that：
Have additional the Ith proportional throttle valve（10）, the IIth proportional throttle valve（11）, the IIIth proportional throttle valve（12）, the IVth ratio section
Flow valve（13）, the Ith two-position two-way solenoid valve（28）And the IIth two-position two-way solenoid valve（29）；
Ith proportional throttle valve（10）H mouths be communicated with boom cylinder（14）Rod chamber；
IIth proportional throttle valve（11）I mouths be communicated with boom cylinder（14）Rodless cavity；
IIIth proportional throttle valve（12）Actuator port G be communicated with rotary fluid motor（15）Oil inlet X；
IVth proportional throttle valve（13）Actuator port L connection rotary fluid motor（15）Y mouths；
Ith proportional throttle valve（10）, the IIth proportional throttle valve（11）, the IIIth proportional throttle valve（12）With it is described
IVth proportional throttle valve（13）Oil outlet T1, oil outlet T2, oil outlet T3 and oil outlet T4 be communicated with fuel tank（20）；
The composite control hydraulic system is by pumping the complex controll with terminal valve, adjusting hydraulic motor and two chamber of hydraulic cylinder
Pressure and flow, make hydraulic motor and hydraulic pump start and braking process in realize quick, steady and Effec-tive Function.
2. positive flow according to claim 1 imports and exports independent composite control hydraulic system, it is characterised in that：Described Ith
Proportional throttle valve（10）, the IIth proportional throttle valve（11）, the IIIth proportional throttle valve（12）And the IVth proportional throttle valve（13）It is first
Conduction proportional throttle valve or direct action type proportional throttle valve.
3. positive flow according to claim 1 imports and exports independent composite control hydraulic system, it is characterised in that：Described Ith
Two-position two-way solenoid valve（28）With the IIth two-position two-way solenoid valve（29）It is pilot-operated type two-position two-way solenoid valve or Direct Action Type two
Position two-way electromagnetic valve.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201710228940.XA CN107061382B (en) | 2017-04-10 | 2017-04-10 | Positive flow imports and exports independent composite control hydraulic system |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201710228940.XA CN107061382B (en) | 2017-04-10 | 2017-04-10 | Positive flow imports and exports independent composite control hydraulic system |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN107061382A CN107061382A (en) | 2017-08-18 |
| CN107061382B true CN107061382B (en) | 2018-06-19 |
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| CN201710228940.XA Active CN107061382B (en) | 2017-04-10 | 2017-04-10 | Positive flow imports and exports independent composite control hydraulic system |
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Families Citing this family (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN107701530B (en) * | 2017-08-24 | 2020-03-10 | 潍柴动力股份有限公司 | Hydraulic system for engineering machinery and engineering machinery |
| CN110486341B (en) * | 2018-05-14 | 2023-03-21 | 博世力士乐（北京）液压有限公司 | Hydraulic control system and mobile working equipment |
| CN110671376B (en) * | 2019-09-29 | 2021-03-12 | 中国矿业大学 | Engineering machinery load sensitive-inlet-outlet independent hydraulic system and control method thereof |
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| CN103857926A (en) * | 2011-03-15 | 2014-06-11 | 胡斯可国际股份有限公司 | Multiple function hydraulic system with a variable displacement pump and a hydrostatic pump-motor |
| CN102758464A (en) * | 2012-07-09 | 2012-10-31 | 徐州徐工挖掘机械有限公司 | Method for controlling positive-flow hydraulic system of excavator |
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| CN107061382A (en) | 2017-08-18 |
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