CN107059983B - Minus flow imports and exports independent composite control hydraulic system - Google Patents
Minus flow imports and exports independent composite control hydraulic system Download PDFInfo
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- CN107059983B CN107059983B CN201710228952.2A CN201710228952A CN107059983B CN 107059983 B CN107059983 B CN 107059983B CN 201710228952 A CN201710228952 A CN 201710228952A CN 107059983 B CN107059983 B CN 107059983B
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- 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
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- 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
- E02F9/2264—Arrangements or adaptations of elements for hydraulic drives
- E02F9/2267—Valves or distributors
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- Engineering & Computer Science (AREA)
- Mining & Mineral Resources (AREA)
- Civil Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Structural Engineering (AREA)
- Fluid-Pressure Circuits (AREA)
- Operation Control Of Excavators (AREA)
Abstract
It is to add that there are four proportional throttle valve and two two-position two-way solenoid valves that a kind of minus flow, which imports and exports independent composite control hydraulic system, and while changing discharge of main pump by inverted flux control, add proportional throttle valve respectively in boom cylinder and two chamber of rotary fluid motor, when main pump passes through master control banked direction control valves to one chamber fuel feeding of boom cylinder or rotary fluid motor, the pressure or flow of one chamber of fuel feeding are controlled by master control banked direction control valves, boom cylinder or another chamber of rotary fluid motor are communicated with proportional throttle valve, and pass through the mobile control pressure or flow of spool, realize the independent control of oil inlet and outlet pressure or flow.The present invention reduces the restriction losses at valve port, reduce system heat generation, especially under overburden operating condition, not only significantly reduce restriction loss, and the speed of service of hydraulic actuator can be improved, and facilitate and realize flow regeneration, and effect is more significant.
Description
Technical field
The present invention relates to a kind of multiplex control system of hydraulic crawler excavator, specifically a kind of disengaging for hydraulic crawler excavator
The independent multiplex control system of mouth.
Background technique
With being on the rise for energy shortage and problem of environmental pollution, the energy consumption problem of research engineering machinery has important
Realistic meaning.Hydraulic crawler excavator realizes that reducing energy loss is always that industry effort chases after as most common hydraulic construction machine
The target asked.With the development of Energy Saving Technology by Hydraulic Pressure, the hydraulic system of excavator developed inverted flux control, positive flow control and
The multiple control modes such as Ioad-sensing control.Inverted flux control refers to that the discharge capacity of hydraulic pump subtracts as control pressure signal increases
Small, i.e., control pressure and discharge capacity are inversely proportional.Its working principle is that: a throttling is set on the drainback passage of position in multiple directional control valve
Hole, oil liquid generate pressure difference by throttle orifice, pressure before throttle orifice are led to hydraulic pump stroking mechanism to control the discharge capacity of hydraulic pump.
The open number of asking is that CN 104452866A discloses a kind of " hydraulic excavating with hydraulic negative flow control device
Machine ", the hydraulic crawler excavator use inverted flux control, and the discharge capacity of hydraulic pump reduces as control pressure signal increases, that is, controls
Pressure and discharge capacity are inversely proportional.But in traditional inverted flux control system, it is hydraulic as main control valve control to be all made of multi-way valve
Actuator running, oil inlet and outlet area ratio relationship immobilize, only one control freedom degree, synchronization can only control hydraulic
The pressure or flow of one chamber of actuator, poor controllability；Actuator is imported and exported while being throttled when work, and the pressure loss is larger, special
It is not under the operating condition of Exceed load, this problem is even more serious, causes biggish system heat generation, energy loss.
Summary of the invention
In view of the above shortcomings of the prior art, the present invention provides a kind of minus flow inlet and outlet independent composite control hydraulic system
System, efficiently solves the deficiency that poor controllability, valve port restriction loss are big in existing minus flow system.
To achieve the above object, the present invention adopts the following technical scheme that.
A kind of independent composite control hydraulic system of minus flow inlet and outlet, includes main pump control valve, variable piston, power
Source, main pump, pioneer pump, major loop 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, minus flow
Control loop safety valve, the resistance of flow detection liquid, the Ith operation handle, the IIth operation handle, the Ith swing arm control pilot valve, the IIth move
Arm controls pilot valve, the Ith revolution control pilot valve and the IIth revolution control pilot valve；It is characterized by:
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；
Ith proportional throttle valve actuator port H of the Ith proportional throttle valve and the rod chamber of boom cylinder pass through hydraulic
Pipeline connection, the Ith proportional throttle valve oil outlet be connected to fuel tank；
IIth proportional throttle valve actuator port I of the IIth proportional throttle valve and the rodless cavity of boom cylinder pass through liquid
The oil outlet of pipeline connection, the IIth proportional throttle valve is pressed to be connected to fuel tank；
The IIIth proportional throttle valve actuator port G and rotary fluid motor of IIIth proportional throttle valve
Rotary fluid motor the first hydraulic fluid port X pass through fluid pressure line connection, the IIIth proportional throttle valve oil outlet and fuel tank
Connection；
IVth proportional throttle valve actuator port L of the IVth proportional throttle valve and the hydraulic horse of revolution of rotary fluid motor
It is connected to up to the second hydraulic fluid port Y by the oil outlet of fluid pressure line connection, the IVth proportional throttle valve with fuel tank；
The Ith two-position two-way solenoid valve oil inlet V and the Ith master control banked direction control valves oil outlet Q of Ith two-position two-way solenoid valve
It is connected to by the oil outlet of fluid pressure line connection, the Ith two-position two-way solenoid valve with fuel tank；
IIth two-position two-way solenoid valve oil inlet W of the IIth two-position two-way solenoid valve and the IIth master control banked direction control valves work
Hydraulic fluid port R is connected to by fluid pressure line, the IIth two-position two-way solenoid valve oil outlet is connected to fuel tank.
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 closed in pilot proportional throttle valve, direct action type proportional throttle valve, electric closed loop proportional throttle valve and machinery
One of formula proportional throttle valve；Ith two-position two-way solenoid valve and the IIth two-position two-way solenoid valve are pilot-operated type two two
Three-way electromagnetic valve or direct-acting type two-position two-way electromagnetic valve.
A kind of above-mentioned minus flow imports and exports independent composite control hydraulic system, makes main pump by inverted flux control in systems
Displacement variation while, proportional throttle valve is added respectively in boom cylinder and two chamber of rotary fluid motor, when main pump passes through
When master control banked direction control valves are to one chamber fuel feeding of boom cylinder or rotary fluid motor, the pressure or flow of one chamber of fuel feeding are by master control multichannel
The proportional throttle valve of valve control, boom cylinder or the other chamber connection of rotary fluid motor controls pressure by the movement of spool
Power or flow realize the independent control of oil inlet and outlet pressure or flow.
Compared with prior art, the independent composite control hydraulic system of the above-mentioned provided a kind of minus flow inlet and outlet of the present invention
System has the advantage that and has the active effect that this system throttles control valve oil inlet and oil return simultaneously and be changed to oil inlet and outlet and throttle respectively,
Reduce the restriction loss at valve port, reduce system heat generation, especially in Exceed load operating condition, not only significantly reduces throttling damage
It loses, and the speed of service of hydraulic actuator can be improved, facilitate and realize flow regeneration, effect is more significant；This system independent control
Two cavity pressure of hydraulic actuator or flow, improve the controllability of work system, keep system operation more steady；This system is according to need
Inlet throttle speed regulation, outlet throttle timing and inlet and outlet composite throttling speed regulation is respectively adopted；This system uses minus flow control
Hydraulic system processed can also import and export independent composite control hydraulic system using minus flow.
In order to more clearly illustrate structure feature and effect of the invention, pass through specific embodiment pair with reference to the accompanying drawing
Technical solution of the present invention is further illustrated.
Detailed description of the invention
Fig. 1 is this topic structural schematic diagram of excavator in the embodiment of the present invention.
Fig. 2 is the structure principle chart of the specific embodiment of the invention.
In figure: 1, main pump control valve；2, variable piston；3, power source；4, main pump；5, pioneer pump；6, major loop safety valve；
7, the Ith master control banked direction control valves；8, the IIth master control banked direction control valves；9, the Ith proportional throttle valve；10, the IIth proportional throttle valve；11, the IIIth ratio
Example throttle valve；12, the IVth proportional throttle valve；13, boom cylinder；14, the IIth operation handle；15, rotary fluid motor；16,
Ith Rotatary brake valve；17, the IIth Rotatary brake valve；18, the Ith check valve；19, the IIth check valve；20, inverted flux control circuit
Safety valve；21, flow detection liquid hinders；22, the Ith operation handle；23, the Ith swing arm controls pilot valve；24, the control of the IIth swing arm is first
Pilot valve；25, the Ith revolution control pilot valve；26, the IIth revolution control pilot valve；27, the IIIth master control banked direction control valves；28, the Ith 2
Two-way electromagnetic valve；29, the IIth two-position two-way solenoid valve；30, scraper bowl；31, dipper；32, bucket hydraulic cylinder；33, dipper hydraulic cylinder；
34, swing arm；35, it gets on the bus；36, it gets off.
P: the III master control banked direction control valves oil inlet；P1: the I the first oil inlet of master control banked direction control valves；P2: the I master control banked direction control valves second
Oil inlet；P3: the II the first oil inlet of master control banked direction control valves；P4: the II the second oil inlet of master control banked direction control valves；T: fuel tank；A: the I is main
Control the first actuator port of multi-way valve；B: the I the second actuator port of master control banked direction control valves；C: the I master control banked direction control valves third actuator port；
D: the II the first actuator port of master control banked direction control valves；E: the II the second actuator port of master control banked direction control valves；F: the II master control banked direction control valves
Three actuator ports；H: the I proportional throttle valve actuator port；I: the II proportional throttle valve actuator port；G: the III proportional throttle valve
Actuator port；L: the IV proportional throttle valve actuator port；X: the first hydraulic fluid port of rotary fluid motor；Y: the second oil of rotary fluid motor
Mouthful；N: the III the first actuator port of master control banked direction control valves；O: the III the second actuator port of master control banked direction control valves；M: main pump control valve work
Hydraulic fluid port；Q: the I master control banked direction control valves oil outlet；R: the II master control banked direction control valves actuator port；V: the I two-position two-way solenoid valve oil inlet
Mouthful；W: the II two-position two-way solenoid valve oil inlet；K: main pump control valve remote control orifice；K1: the I master control banked direction control valves first are long-range
Control mouth；K2: the I the second remote control orifice of master control banked direction control valves；K3: the II the first remote control orifice of master control banked direction control valves；K4: the II
The second remote control orifice of master control banked direction control valves.
Specific embodiment
A specific embodiment of the invention is further illustrated with reference to the accompanying drawing, but embodiments of the present invention
It is without being limited thereto.
Attached drawing 2 shows the specific structure of the preferred embodiments of the invention, includes main pump control valve 1, variable piston
2, power source 3, main pump 4, pioneer pump 5, major loop safety valve 6, the Ith master control banked direction control valves 7, the IIth master control banked direction control valves 8, the Ith ratio
Throttle valve 9, the IIth proportional throttle valve 10, the IIIth proportional throttle valve 11, the IVth proportional throttle valve 12, boom cylinder the 13, the IIth
Operation handle 14, rotary fluid motor 15, the Ith Rotatary brake valve 16, the IIth Rotatary brake valve 17, the Ith check valve the 18, the IIth are single
To valve 19, inverted flux control circuit safety valve 20, flow detection liquid hinder the 21, the Ith operation handle 22, the Ith swing arm controls pilot valve
23, the IIth swing arm control pilot valve the 24, the Ith revolution control pilot valve the 25, the IIth revolution control pilot valve 26, the IIIth master control multichannel
Valve 27, the Ith two-position two-way solenoid valve 28, the IIth two-position two-way solenoid valve 29.
Wherein: the power source 3, main pump 4 and pioneer pump 5 are coaxially arranged；The actuator port H of Ith proportional throttle valve 9, the Ith master
Ith master control banked direction control valves the first actuator port A of control multi-way valve 7 is connected to the rod chamber of boom cylinder 13 by fluid pressure line,
The oil outlet of Ith proportional throttle valve 9 is connected to fuel tank, the IIth proportional throttle valve actuator port I of the IIth proportional throttle valve 10,
Ith master control banked direction control valves third actuator port C of I master control banked direction control valves 7 and the rodless cavity of boom cylinder 13 are connected by fluid pressure line
Logical, the oil outlet of the IIth proportional throttle valve 10 is connected to fuel tank, the IIIth proportional throttle valve working oil of the IIIth proportional throttle valve 11
Mouth G, the IIth the first actuator port of master control banked direction control valves D of the IIth master control banked direction control valves 8, the oil inlet of the Ith Rotatary brake valve 16, the Ith
The oil outlet of check valve 18 is connected to the first hydraulic fluid port of rotary fluid motor X of rotary fluid motor 15 by fluid pressure line, and the IIIth
The oil outlet of proportional throttle valve 11 is connected to fuel tank, the IVth proportional throttle valve actuator port L of the IVth proportional throttle valve 12, the IIth
The IIth master control banked direction control valves third actuator port F, the oil inlet of the IIth Rotatary brake valve 17, the IIth check valve of master control banked direction control valves 8
19 oil outlet is connected to the second hydraulic fluid port of rotary fluid motor Y of rotary fluid motor 15 by fluid pressure line, the IVth ratio section
The oil outlet of stream valve 12 is connected with fuel tank, and the Ith two-position two-way solenoid valve oil inlet V of the Ith two-position two-way solenoid valve 28 and the Ith is main
Control multi-way valve 7 the Ith master control banked direction control valves oil outlet Q by fluid pressure line be connected to, the oil outlet of the Ith two-position two-way solenoid valve 28 with
The of fuel tank connection, the IIth two-position two-way solenoid valve oil inlet W of the IIth two-position two-way solenoid valve 29 and the IIth master control banked direction control valves 8
II master control banked direction control valves actuator port R is connected to by fluid pressure line, and the oil outlet of the IIth two-position two-way solenoid valve 29 is connected to fuel tank；
The Ith master control banked direction control valves the first oil inlet P 1, the Ith master control multichannel of the Ith master control banked direction control valves 7 of Ith master control banked direction control valves 7
Valve the second oil inlet P 2, the IIth master control banked direction control valves the second oil inlet P 4 of the IIth master control banked direction control valves 8, the IIIth master control banked direction control valves 27
IIIth master control banked direction control valves oil inlet P is connected to the oil outlet of main pump 4 by fluid pressure line, the Ith master control of the Ith master control banked direction control valves 7
The connection of IIth the first oil inlet P of master control banked direction control valves 3 of multi-way valve the second actuator port B and the IIth master control banked direction control valves 8, the Ith master control
The oil outlet connection of Ith master control banked direction control valves the first remote control orifice K1 of multi-way valve 7 and the Ith swing arm control pilot valve 23, the Ith is main
Control the oil outlet connection of the Ith master control banked direction control valves the second remote control orifice K2 and the IIth swing arm control pilot valve 24 of multi-way valve 7；The
IIth master control banked direction control valves the second actuator port E of II master control banked direction control valves 8 is connected to the oil inlet of flow detection liquid resistance 21, and the IIth is main
The oil outlet connection of the revolution control pilot valve 25 of the IIth master control banked direction control valves the first remote control orifice K3 and the Ith of multi-way valve 8 is controlled, the
The oil outlet of the revolution control pilot valve 26 of IIth master control banked direction control valves the second remote control orifice K4 of II master control banked direction control valves 8 and the IIth connects
It is logical；The oil outlet of IIIth master control banked direction control valves 27 is connected to fuel tank, the IIIth the first work of master control banked direction control valves of the IIIth master control banked direction control valves 27
Make the IIIth the second actuator port of master control banked direction control valves O of hydraulic fluid port N and the IIIth master control banked direction control valves 27 respectively with the both ends of other actuators
It is connected；
The master of the oil inlet of flow detection liquid resistance 21, the oil inlet of inverted flux control circuit safety valve 20, main pump control valve 1
Pump control valve remote control orifice K and the IIth the second actuator port of master control banked direction control valves E of the IIth master control banked direction control valves 8 are connected, flow
The oil outlet of detection liquid resistance 21, the oil outlet of inverted flux control circuit safety valve 20 are connected with fuel tank；Major loop safety valve 6
Oil inlet, the small chamber of variable piston 2, main pump control valve 1 oil inlet be connected with the oil outlet of pioneer pump 5, major loop safety
The oil outlet of valve 6, the oil outlet of main pump control valve 1 are connected with fuel tank, the main pump control valve actuator port M of main pump control valve 1
It is connected with the big chamber of variable piston 2；Ith swing arm control pilot valve 23 oil inlet, the IIth swing arm control pilot valve 24 into
Hydraulic fluid port, the oil inlet of the Ith revolution control pilot valve 25, the IIth revolution control the oil inlet of pilot valve 26 and the oil outlet of main pump 4
It is connected, the Ith swing arm controls the remote control orifice and the Ith of the remote control orifice of pilot valve 23, the IIth swing arm control pilot valve 24
Operation handle 22 is connected, the long-range control of the remote control orifice of the Ith revolution control pilot valve 25, the IIth revolution control pilot valve 26
Mouth is connected with the IIth operation handle 14；The oil outlet of Ith Rotatary brake valve 16, the oil outlet of the IIth Rotatary brake valve 17, the Ith list
It is connected to the oil inlet of the oil inlet of valve 18, the IIth check valve 19 with fuel tank.
Excavator in specific embodiment is 20t excavator, and the discharge capacity of main pump 4 is 100ml/r, the Ith master control banked direction control valves, the
II master control banked direction control valves gate the Center-Open multiple directional control valve that diameter is 25, the Ith proportional throttle valve, the IIth proportional throttle valve, the IIIth
The direct action type proportional throttle valve that proportional throttle valve, the IVth proportional throttle valve gating diameter are 20, the Ith two-position two-way solenoid valve, the IIth
Two-position two-way solenoid valve gates the self-action solenoid valve that diameter is 20.
Referring to shown in attached drawing 2, the structure working principle that the present embodiment is described in detail is as follows:
(1) an inverted flux control circuit peace is provided on the back oil road of the IIth master control banked direction control valves 8 in hydraulic system
Full valve 20 and flow detection liquid hinder 21 and form inverted flux control detection unit, and oil liquid can generate pressure by flow detection liquid resistance 21
Difference controls the main pump that the inlet pressure of flow detection liquid resistance 21 leads to hydraulic pump stroking mechanism as inverted flux control pressure
The control port K of valve 1, to control the discharge capacity of main pump 4.Inverted flux control pressure is bigger, and the pressure of the big chamber of variable piston 2 is got over
Low, variable piston 2 is moved to the left, and the swashplate angle of main pump 4 becomes smaller, and the output flow of main pump 4 reduces.
(2) when the Ith operation handle 22 controls pilot valve 23 by the Ith swing arm of control and the IIth swing arm controls pilot valve 24 and makes
The Ith master control banked direction control valves 7 and the IIth operation handle 14 pass through the Ith revolution control pilot valve 25 of control and the IIth revolution control in circuit
When pilot valve 26 processed makes that the IIth master control banked direction control valves 8 are in middle position in circuit, the hydraulic fluid port P1-B and the IIth of the Ith master control banked direction control valves 7
The hydraulic fluid port P3-E relief circuit of master control banked direction control valves 8 is connected, and whole flows of main pump 4 return to fuel tank by flow detection liquid resistance 21,
Reach maximum value by the flow of flow detection liquid resistance 21, so that inverted flux control pressure is maximum value, inverted flux control
The maximum value of pressure is determined by the inverted flux control circuit safety valve 20 in parallel with the resistance 21 of flow detection liquid, so that the row of main pump 4
Amount is automatically reduced to minimum, substantially reduces empty stream loss.
(3) when the Ith operation handle 22 controls pilot valve 23 by the Ith swing arm of control and the IIth swing arm controls pilot valve 24 and makes
The Ith master control banked direction control valves 7 or the IIth operation handle 14 pass through the Ith revolution control pilot valve 25 of control and the IIth revolution control in circuit
When pilot valve 26 makes that the IIth master control banked direction control valves 8 are between left position and middle position in circuit, the output flow part of main pump 4 passes through the
The hydraulic fluid port P2-C of I master control banked direction control valves 7 enters the rodless cavity of boom cylinder 13 or the hydraulic fluid port P4-F by the IIth master control banked direction control valves 8
Into the Y hydraulic fluid port of rotary fluid motor 15.In the actuator port V or the IIth bi-bit bi-pass electromagnetism of the Ith two-position two-way solenoid valve 28
In the case where not connecting with fuel tank, the actuator port H of the Ith proportional throttle valve 9 is connected or the IIIth with fuel tank by the oil inlet W of valve 29
The actuator port G of proportional throttle valve 11 is connected and the actuator port I of the IIth proportional throttle valve 10 or the throttling of the IVth ratio with fuel tank
For the actuator port L of valve 12 without connecting with fuel tank, the hydraulic oil of the rod chamber of boom cylinder 13 passes through the Ith proportional throttle valve 9
The hydraulic oil of 15 first hydraulic fluid port X of actuator port H or rotary fluid motor flowed by the actuator port G of the IIIth proportional throttle valve 11
Fuel tank is returned to, the size by the Ith proportional throttle valve 9 of control or the IIIth 11 valve opening mouths of proportional throttle valve is hydraulic to control swing arm
The flow or pressure of the X hydraulic fluid port of 13 rod chamber of cylinder or rotary fluid motor 15, transport them steadily with the operating speed of needs
Make, to reduce the restriction loss that valve port goes out；In the actuator port V or the IIth bi-bit bi-pass of the Ith two-position two-way solenoid valve 28
In the case that the actuator port W of solenoid valve 29 is connected with fuel tank, the hydraulic oil of the rod chamber of boom cylinder 13 passes through the Ith 2
The hydraulic oil of the 15 first hydraulic fluid port X of actuator port V or rotary fluid motor of two-way electromagnetic valve 28 passes through the IIth bi-bit bi-pass electromagnetism
The actuator port W of valve 29 flow back into fuel tank, and only inverted flux control does not import and export independent control at this time.In above-mentioned two situations
Under, it is reduced by the flow of flow detection liquid resistance 21, the pressure that flow detection liquid hinders 21 oil inlets reduces, and the discharge capacity of main pump 4 increases
Needs greatly to meet operating speed；When the Ith master control banked direction control valves 7 or the IIth master control banked direction control valves 8 are located at limit on the left position, main pump 4
Output flow all pass through the hydraulic fluid port P2-C of the Ith master control banked direction control valves 7 and enter the rodless cavity of swing arm hydraulic motor 13 or by the
The hydraulic fluid port P4-F of II master control banked direction control valves 8 enters the Y hydraulic fluid port of rotary fluid motor 15, hinders 21 by flow detection liquid without flow,
The discharge capacity of main pump 4 increases to the maximum needs to meet operating speed.
(4) when the Ith operation handle 22 controls pilot valve 23 by the Ith swing arm of control and the IIth swing arm controls pilot valve 24 and makes
The Ith master control banked direction control valves 7 or the IIth operation handle 14 pass through the Ith revolution control pilot valve 25 of control and the IIth revolution control in circuit
When pilot valve 26 is in the IIth master control banked direction control valves 8 between right position and middle position, the output flow part of main pump 4 passes through the
The hydraulic fluid port P2-A of I master control banked direction control valves 7 enters the rod chamber of boom cylinder 13 or the hydraulic fluid port P4-D by the IIth master control banked direction control valves 8
Into the X hydraulic fluid port of rotary fluid motor 15.In the actuator port V or the IIth bi-bit bi-pass electromagnetism of the Ith two-position two-way solenoid valve 28
The actuator port W of valve 29 is that in the case where connecting with fuel tank, the actuator port I of the IIth proportional throttle valve 10 is connected or the IVth ratio
The actuator port L of example throttle valve 12 is connected and the actuator port H or the IIIth proportional throttle valve 11 of the Ith proportional throttle valve 9 with fuel tank
Actuator port G being connected with fuel tank, the hydraulic oil of the rodless cavity of boom cylinder 13 passes through the IIth proportional throttle valve 10
The hydraulic oil of 15 second hydraulic fluid port Y of actuator port I or rotary fluid motor is flowed back to by the actuator port L of the IVth proportional throttle valve 12
To fuel tank, the size by the IIth proportional throttle valve 10 of control or the IVth 12 valve opening mouths of proportional throttle valve is hydraulic to control swing arm
The flow or pressure of the Y hydraulic fluid port of 13 rodless cavity of cylinder or rotary fluid motor 15, transport them steadily with the operating speed of needs
Make, to reduce the restriction loss that valve port goes out；In the actuator port V or the IIth bi-bit bi-pass of the Ith two-position two-way solenoid valve 28
In the case that the actuator port W of solenoid valve 29 is connected with fuel tank, the hydraulic oil of the rodless cavity of boom cylinder 13 passes through the Ith 2
The hydraulic oil of the 15 second hydraulic fluid port Y of actuator port V or rotary fluid motor of two-way electromagnetic valve 28 passes through the IIth bi-bit bi-pass electromagnetism
The actuator port W of valve 29 flow back into fuel tank, and only inverted flux control does not import and export independent control at this time.In above-mentioned two situations
Under, it is reduced by the flow of flow detection liquid resistance 21, the pressure that flow detection liquid hinders 21 oil inlets reduces, and the discharge capacity of main pump 4 increases
Needs greatly to meet operating speed；When the Ith master control banked direction control valves 7 or the IIth master control banked direction control valves 8 are located at limit on the right-right-hand limit position, main pump 4
Output flow all pass through the hydraulic fluid port P2-A of the Ith master control banked direction control valves 7 and enter the rod chamber of swing arm hydraulic motor 13 or by the
The hydraulic fluid port P4-D of II master control banked direction control valves 8 enters the X hydraulic fluid port of rotary fluid motor 15, hinders 21 by flow detection liquid without flow,
The discharge capacity of main pump 4 increases to the maximum needs to meet operating speed.
The above is only preferable implementation of the invention, is not intended to limit the scope of the present invention, therefore
All technical spirit according to the present invention any subtle modifications, equivalent variations and modifications to the above embodiments, still belong to
In the range of technical solution of the present invention.
Claims (3)
1. a kind of minus flow imports and exports independent composite control hydraulic system, include main pump control valve, variable piston, power source,
Main pump, pioneer pump, major loop 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 are hydraulic
Cylinder, rotary fluid motor, the Ith Rotatary brake valve, the IIth Rotatary brake valve, the Ith check valve, the IIth check valve, inverted flux control
Circuit safety valve, the resistance of flow detection liquid, the Ith operation handle, the IIth operation handle, the Ith swing arm control pilot valve, the IIth swing arm control
Pilot valve, the Ith revolution control pilot valve and the IIth revolution control pilot valve processed；It is characterized by:
Have additional the Ith proportional throttle valve (9), the IIth proportional throttle valve (10), the IIIth proportional throttle valve (11), the throttling of the IVth ratio
Valve (12), the Ith two-position two-way solenoid valve (28) and the IIth two-position two-way solenoid valve (29)；
The rod chamber of the Ith proportional throttle valve actuator port H and boom cylinder (13) of Ith proportional throttle valve (9) pass through
Fluid pressure line is connected to, the oil outlet of the Ith proportional throttle valve (9) is connected to fuel tank；
IIth proportional throttle valve actuator port I of the IIth proportional throttle valve (10) and the rodless cavity of boom cylinder (13) are logical
Cross fluid pressure line connection, the oil outlet of the IIth proportional throttle valve (10) is connected to fuel tank；
The IIIth proportional throttle valve actuator port G and rotary fluid motor of IIIth proportional throttle valve (11)
(15) rotary fluid motor the first hydraulic fluid port X is connected to by fluid pressure line, the oil outlet of the IIIth proportional throttle valve (11) with
Fuel tank connection；
The IVth proportional throttle valve actuator port L and rotary fluid motor of IVth proportional throttle valve (12)
(15) rotary fluid motor the second hydraulic fluid port Y is connected to by fluid pressure line, the oil outlet of the IVth proportional throttle valve (12) with
Fuel tank connection；
The Ith two-position two-way solenoid valve oil inlet V and the Ith master control banked direction control valves oil outlet Q of Ith two-position two-way solenoid valve (28)
It is connected to by the oil outlet of fluid pressure line connection, the Ith two-position two-way solenoid valve (28) with fuel tank；
IIth two-position two-way solenoid valve oil inlet W of the IIth two-position two-way solenoid valve (29) and the IIth master control banked direction control valves work
Hydraulic fluid port R is connected to by fluid pressure line, the oil outlet of the IIth two-position two-way solenoid valve (29) is connected to fuel tank.
2. minus flow according to claim 1 imports and exports independent composite control hydraulic system, it is characterised in that: the described Ith
Proportional throttle valve (9), the IIth proportional throttle valve (10), the IIIth proportional throttle valve (11) and the IVth proportional throttle valve (12) are guides
In formula proportional throttle valve, direct action type proportional throttle valve, electric closed loop proportional throttle valve and machinery in enclosed proportional throttle valve one
Kind.
3. minus flow according to claim 1 imports and exports independent composite control hydraulic system, it is characterised in that: the described Ith
Two-position two-way solenoid valve (28) and the IIth two-position two-way solenoid valve (29) are pilot-operated type two-position two-way solenoid valve or Direct Action Type two
Position two-way electromagnetic valve.
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| Application Number | Priority Date | Filing Date | Title |
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| CN201710228952.2A CN107059983B (en) | 2017-04-10 | 2017-04-10 | Minus flow imports and exports independent composite control hydraulic system |
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| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201710228952.2A CN107059983B (en) | 2017-04-10 | 2017-04-10 | Minus flow imports and exports independent composite control hydraulic system |
Publications (2)
| Publication Number | Publication Date |
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| CN107059983A CN107059983A (en) | 2017-08-18 |
| CN107059983B true CN107059983B (en) | 2019-10-29 |
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| CN201710228952.2A Active CN107059983B (en) | 2017-04-10 | 2017-04-10 | Minus flow imports and exports independent composite control hydraulic system |
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| Country | Link |
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| CN (1) | CN107059983B (en) |
Families Citing this family (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN107882100B (en) * | 2017-10-11 | 2020-07-21 | 柳州柳工挖掘机有限公司 | Excavator hydraulic control method and control system |
| CN107701532B (en) * | 2017-11-16 | 2023-11-28 | 恒天九五重工有限公司 | Negative flow multi-way valve hydraulic control system and control method thereof |
| CN108591148B (en) * | 2018-05-28 | 2020-08-25 | 河南工学院 | Accurate control method of hydraulic engineering equipment |
| CN108716491B (en) * | 2018-05-28 | 2022-02-11 | 徐州燕大传动与控制技术有限公司 | Three-position five-way load port independent control multi-way valve with O-shaped neutral position function |
| CN108661965B (en) * | 2018-05-28 | 2022-02-11 | 徐州燕大传动与控制技术有限公司 | Three-position five-way load port independent control multi-way valve with Y-shaped neutral position function |
| CN108975188B (en) * | 2018-08-31 | 2020-07-17 | 武汉船用机械有限责任公司 | Hydraulic system |
| CN110714941B (en) * | 2019-10-11 | 2020-09-25 | 燕山大学 | Pump valve composite cylinder control force control and valve control cylinder position control combined loading device and control method |
Family Cites Families (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN1800654A (en) * | 2005-12-20 | 2006-07-12 | 武汉科技大学 | Asymmetric cylinder closed-loop speed system controlled by electro-hydraulic proportional pump |
| CN100491748C (en) * | 2007-08-01 | 2009-05-27 | 太原理工大学 | Independent control electrohydraulic system of oil inlet and outlet matching with pump valve composite flux |
| JP2012255434A (en) * | 2011-05-13 | 2012-12-27 | Hitachi Constr Mach Co Ltd | Hydraulic control device of construction machine |
| DE102013214807A1 (en) * | 2013-07-30 | 2015-02-05 | Robert Bosch Gmbh | Hydrostatic drive, in particular hydrostatic fan drive |
| CN104452866A (en) * | 2013-09-13 | 2015-03-25 | 浦云飞 | Hydraulic excavator having hydraulic negative-flow control device |
| CN104294877B (en) * | 2014-09-17 | 2016-03-30 | 太原理工大学 | Hybrid power hydraulic excavator active-passive composite control system |
| CN105840598B (en) * | 2016-05-25 | 2017-08-25 | 华侨大学 | The drive system that a kind of engineering machinery turntable energy is recycled automatically |
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