CN107061382A - 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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- CN107061382A CN107061382A CN201710228940.XA CN201710228940A CN107061382A CN 107061382 A CN107061382 A CN 107061382A CN 201710228940 A CN201710228940 A CN 201710228940A CN 107061382 A CN107061382 A CN 107061382A
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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
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- Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Fluid Mechanics (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Fluid-Pressure Circuits (AREA)
- Operation Control Of Excavators (AREA)
Abstract
A kind of positive flow imports and exports independent composite control hydraulic system, the composite control hydraulic system has additional four proportional throttle valves, two two-position two-way solenoid valves, pass through pump and the complex controll of terminal valve, adjust the pressure and flow of hydraulic motor and the chamber of hydraulic cylinder two, hydraulic motor and hydraulic pump is set to realize quick, steady and efficient operation in startup and braking procedure, while avoiding in traditional positive flow control hydraulic system because a large amount of restriction losses that fuel feeding is caused on demand.
Description
Technical field
It is particularly a kind of for the only of positive flow and import and export the present invention relates to a kind of hydraulic system of independent complex controll
The technical scheme of the hydraulic system of vertical complex controll.
Background technology
Engineering machinery shows according to factual survey the problem of hydraulic system often high oil temperature occurs in use,
The oil temperature of hydraulic system is to influence the master of hydraulic system and reliability of hydraulic component and complete machine operating 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 conventional 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 is controlled：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 signal pressure that the discharge capacity of main pump is exported to pilot operated handle is directly proportional.Master controller is according to different elder generations
Pilot force signal judges the traffic demand of actuator, and implements regulation to discharge of main pump according to pressure signal so that the stream of system
Amount supply can dynamically follow the traffic demand of executive component, realize the real-time matching of flow system flow, reach energy-on-demand.
Still it is controlled in traditional engineering machinery positive flow control system using banked direction control valves as main control valve, only
One control freedom degree, oil inlet and outlet area relationship immobilizes, and synchronization can only control a chamber of hydraulic actuator
Pressure or flow, poor controllability；Actuator is imported and exported during work throttles simultaneously, 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 protruded.
The content of the invention
The deficiency existed for above-mentioned prior art, the present invention provides a kind of positive flow and imports and exports independent composite control hydraulic
System, to solve poor controllability in traditional positive flow control hydraulic system, the big shortcoming of valve port restriction loss further reduces
Restriction loss, reduction heating improves the revolution stationarity of engineering machinery and the energy-efficient performance of totality.
To achieve the above object, the present invention is adopted the following technical scheme that.
A kind of positive flow imports and exports independent composite control hydraulic system, including the amplification of main pump control valve, variable piston, signal
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 2
Two-way electromagnetic 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 actuator port L of IVth proportional throttle valve connects the Y mouths of rotary fluid motor；
Ith proportional throttle valve, the IIth proportional throttle valve, the IIIth proportional throttle valve and the IVth ratio throttle
Oil-out T1, oil-out T2, oil-out T3 and the oil-out T4 of valve are communicated with fuel tank；
The composite control hydraulic system is the complex controll by pump and terminal valve, regulation hydraulic motor and the chamber of hydraulic cylinder two
Pressure and flow, make hydraulic motor and hydraulic pump be realized in startup and braking procedure.
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 choke valve, or direct action type proportional choke 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 self-action two-position two-way solenoid valve.
There is above-mentioned technical proposal of the present invention clear advantage and beneficial effect to be：Positive flow is independent compound with importing and exporting
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 is using two bi-bit bi-pass electromagnetic proportion throttles, by it by import and export 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 throttled respectively by the present invention simultaneously, is subtracted
The restriction loss at valve port is lacked, has reduced system heat generation, particularly in Exceed load operating mode, not only significantly reduced throttling and damage
Lose, and the speed of service of hydraulic actuator can be improved, conveniently realize that flow regenerates, 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 import and export independent composite throttling speed governing；Traditional positive flow control can be retained as needed
Hydraulic system, it would however also be possible to employ positive flow imports and exports independent composite control hydraulic system.
In order to more clearly illustrate the architectural feature and effect of the present invention, come below in conjunction with the accompanying drawings with specific embodiment to this
Invention is described in detail.
Brief 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, get off；31st, get 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
Banked direction control valves oil inlet；T：Oil-out；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-out；R：IIth master control banked direction control valves actuator port；V：Ith bi-bit bi-pass
Magnetic 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
Banked direction control valves remote control orifice；K3、K4：IIth master control banked direction control valves remote control orifice.
Embodiment
Implement the technical scheme that a kind of positive flow imports and exports independent composite control hydraulic system, referring to the drawings shown in 2, it shows
Show that the concrete structure that the specific embodiment of the invention is 20t excavators, including main pump control valve 1, variable piston 2, signal are put
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 choke valve 11, the IIIth direct action type proportional choke 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 are coaxially connected with main pump 5, the Ith proportional throttle valve actuator port H and the Ith master control banked direction control valves
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 banked direction control valves work
Make the rodless cavity that hydraulic fluid port C is all connected with boom cylinder 14, the IIIth proportional throttle valve actuator port G, the work of the IIth master control banked direction control valves
Hydraulic fluid port D, the oil inlet of the Ith Rotatary brake valve 16 and the Ith check valve 18 oil-out are all connected with rotary fluid motor hydraulic fluid port X,
IVth proportional throttle valve actuator port L, the IIth master control banked direction control valves actuator port F, the oil inlet of the IIth Rotatary brake valve 17 and
The oil-out connection rotary fluid motor hydraulic fluid port Y of IIth check valve 19, the master control of the Ith two-position two-way solenoid valve oil inlet V connections the Ith
Banked direction control valves oil-out Q, the master control banked direction control valves actuator port R of the IIth two-position two-way solenoid valve oil inlet W connections the IIth, the Ith ratio section
Flow valve, the IIth proportional throttle valve, the IIIth proportional throttle valve and the IVth proportional throttle valve oil-out T1, T2, T3 and T4, the Ith 2
Two-way electromagnetic valve and the IIth two-position two-way solenoid valve oil-out T5 and T6, the Ith Rotatary brake valve and the IIth Rotatary brake valve are fuel-displaced
Mouth 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 P 2,
IIth master control banked direction control valves oil inlet P4And the IIIth master control banked direction control valves oil inlet P connect the oil-out of main pump 5, the Ith master control is more
Road valve actuator port B connects the IIth master control banked direction control valves oil inlet P 3, and the Ith master control banked direction control valves remote control orifice K1 connects the Ith swing arm
The oil-out of pilot valve 23 is controlled, the Ith master control banked direction control valves remote control orifice K2 connects the fuel-displaced of the IIth swing arm control pilot valve 24
Mouthful；The oil-out of the revolution control pilot valve 25 of IIth master control banked direction control valves remote control orifice K3 connections the Ith, the IIth master control banked direction control valves are remote
The oil-out of the program control revolution control pilot valve 26 of donsole K4 connections the IIth；IIIth master control banked direction control valves oil-out T is connected with fuel tank 20
Logical, the IIIth master control banked direction control valves actuator port O and actuator port N are respectively communicated with other actuator two ends；The small chamber of variable piston with
And the oil inlet of main pump control valve 1 connects the oil-out of pioneer pump 6, the oil-out T connection fuel tanks 20 of main pump control valve 1, main pump
The big chamber of control valve actuator port M connection variables piston 2；Variable piston 2 is connected with signal amplifier 3；Ith swing arm controls guide
The oil inlet of valve 23, the IIth swing arm control pilot valve 24 and the Ith revolution control revolution control pilot valve 26 of pilot valve the 25, the IIth is equal
The oil-out of main pump 5 is connected, the Ith swing arm control pilot valve 23, the remote control orifice of the IIth swing arm control pilot valve 24 are connected
Ith operation handle 21, the remote control orifice of the Ith revolution control revolution control pilot valve 26 of pilot valve the 25, the IIth connects the IIth
Operation handle 22.
Referring to the drawings shown in 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 to control first by the Ith swing arm
Pilot valve 24 is sent to be controlled with the Ith master control banked direction control valves 8, the pilot pressure signal of the IIth operation handle 22 output by the Ith revolution
The revolution control pilot valve 17 of pilot valve the 16, the IIth is sent to main pump control valve remote control hydraulic fluid port K and the IIth master control multichannel simultaneously
Valve 9, while the pilot pressure signal of the Ith operation handle 21, the IIth operation handle 22 output is sent to master by signal amplifier 3
Pump control valve 1, pilot control pressure is bigger, and the pressure of the big chamber of servo variable displacement piston 2 is bigger, and servo variable displacement piston 2 moves right
Dynamic, 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, theWhen pressure-reducing valve makes that Ι master control banked direction control valves 8 and Ι Ι main valves 9 are in middle position in loop,
Hydraulic fluid port P1-A, C-T or P1-C of Ι master control banked direction control valves 8, A-C and Ι Ι master control banked direction control valves 9 hydraulic fluid port P1-D, F-T or
P1-F, D-T are turned off, and the hydraulic fluid port P-E relief circuits 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 connected,
Whole flows of main pump 5 flow back into fuel tank 20, and then cause positive flow control pressure to be minimum value so that the discharge capacity of main pump 5 is certainly
It is dynamic to be reduced to minimum, substantially reduce 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 loop Ι master control banked direction control valves 8 or Ι Ι master control multichannels
When valve 9 is located 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
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 returned
One chamber of rotating hydraulic motor 15, now the hydraulic fluid port H-T of Ι electromagnetic proportion throttles 10 orElectromagnetic proportion throttle 13
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
Close, 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 into 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, can be by controlling the size of 10 or the 4th electromagnetic proportion throttle of Ι electromagnetic proportion throttles, 13 valve opening mouthful to control
The flow or pressure of Ι working cylinders 14.1 and the rod chamber of Ι Ι working cylinders 14.2 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 meet work
The need for 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 81- A or Ι Ι master control banked direction control valves 9 hydraulic fluid port P1- D enters corresponding Ι works
Make the rodless cavity or a chamber of rotary motor 15 of cylinder 14.1 and Ι Ι working cylinders 14.2, the discharge capacity of main pump 5 increase to it is maximum with
The need for meeting operating speed
（4）When the second operation handle 22 is by controlling the Ith swing arm to control pilot valve 23, Ι Ι swing arms to control pilot valve 24, Ι to return
Turning control pilot valve 25, Ι Ι revolution control pilot valves 26 makes loop Ι main valves 8 or Ι Ι main valves 9 be located at right position and middle position
Between when, the 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 the rod chamber or a chamber of rotary motor 15 of corresponding Ι working cylinders 14.1 and Ι Ι working cylinders 14.2, now
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 are closed, Ι Ι electromagnetism ratios
The hydraulic fluid port G-T of the hydraulic fluid port I-T or Ι Ι Ι electromagnetic proportion throttles 12 of example choke valve 11 is connected, therefore the He of Ι working cylinders 14.1
The hydraulic oil of the rodless cavity of Ι Ι working cylinders 14.2 or another chamber of rotary motor 15 passes through Ι Ι electromagnetic proportion throttles 11
The hydraulic fluid port G-T of hydraulic fluid port I-T or Ι Ι Ι electromagnetic proportion throttles 12 flow back into fuel tank, can pass through and control Ι Ι electromagnetism ratios
The sizes of example choke valve 10 or Ι Ι Ι electromagnetic proportion throttles 11 valve opening mouthful controls Ι working cylinders 14.1 and Ι Ι works
Make the rodless cavity of cylinder 14.2 or the flow or pressure of another chamber of rotary fluid motor 15, make them flat with the operating speed of needs
Steady running, so that the restriction loss that valve port goes out is reduced, the need for the discharge capacity of main pump 5 increases to meet operating speed；Work as loop
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 right-right-hand limit position, whole flows of main pump 5 are more by Ι master controls
The hydraulic fluid port P of road valve 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 Ι Ι work
The rod chamber of cylinder 14.2 or a chamber of rotary fluid motor 15, the discharge capacity of variable pump 5 increase to maximum to meet operating speed
The need for.
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 the chamber of rotary motor two 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 the chamber of fuel feeding one are by main valve control, working cylinder or the other chamber of rotary motor
The electromagnetic proportion throttle of connection controls the pressure or flow of this chamber by the movement of valve element, is so achieved that oil inlet and outlet
The independent control of pressure or flow, reduces the restriction loss at valve port, and loss and the system hair of power are reduced to greatest extent
Heat, and improve the stationarity and controllability of working cylinder and rotary motor.
By pump and the complex controll of terminal valve, the pressure and flow of regulation hydraulic motor and the chamber of hydraulic cylinder two make liquid
Pressure motor and hydraulic pump realize quick, steady and efficient operation in startup and braking procedure, while avoiding traditional positive stream
The substantial amounts of restriction loss that fuel feeding is caused on demand in amount control hydraulic system.
It is described above, only it is 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 is substantially made to 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 the amplification of main pump control valve, variable piston, signal
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-out T1, oil-out T2, oil-out T3 and oil-out T4 be communicated with fuel tank（20）；
The composite control hydraulic system is the complex controll by pump and terminal valve, regulation hydraulic motor and the chamber of hydraulic cylinder two
Pressure and flow, make hydraulic motor and hydraulic pump be realized in startup and braking procedure.
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 choke 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 self-action 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 true CN107061382A (en) | 2017-08-18 |
| CN107061382B 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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Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN107701530A (en) * | 2017-08-24 | 2018-02-16 | 潍柴动力股份有限公司 | Hydraulic system and engineering machinery for engineering machinery |
| CN110486341A (en) * | 2018-05-14 | 2019-11-22 | 博世力士乐（北京）液压有限公司 | Hydraulic control system and mobile working equipment |
| CN110671376A (en) * | 2019-09-29 | 2020-01-10 | 中国矿业大学 | Engineering machinery load sensitive-inlet-outlet independent hydraulic system and control method thereof |
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| 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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| Publication number | Priority date | Publication date | Assignee | Title |
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| CN107701530A (en) * | 2017-08-24 | 2018-02-16 | 潍柴动力股份有限公司 | Hydraulic system and engineering machinery for engineering machinery |
| CN110486341A (en) * | 2018-05-14 | 2019-11-22 | 博世力士乐（北京）液压有限公司 | Hydraulic control system and mobile working equipment |
| CN110671376A (en) * | 2019-09-29 | 2020-01-10 | 中国矿业大学 | Engineering machinery load sensitive-inlet-outlet independent hydraulic system and control method thereof |
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Effective date of registration: 20190924 Address after: 250101 Jinan High-tech Zone and No. 171 Xuanlu, Shandong Province Patentee after: Taizhong Yuci Hydraulic Industry (Jinan) Co., Ltd. Address before: 030024 Yingze, Shanxi Province, Berlin District, West Street, No. 79, No. Patentee before: Taiyuan University of Technology |