CN107059983A - 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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- CN107059983A CN107059983A CN201710228952.2A CN201710228952A CN107059983A CN 107059983 A CN107059983 A CN 107059983A CN 201710228952 A CN201710228952 A CN 201710228952A CN 107059983 A CN107059983 A CN 107059983A
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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
-
- 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
Abstract
It is to have additional four proportional throttle valves 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 the chamber of rotary fluid motor two, when main pump by master control banked direction control valves to one chamber fuel feeding of boom cylinder or rotary fluid motor when, the pressure or flow of the chamber of fuel feeding one are by master control banked direction control valves control, boom cylinder or another chamber of rotary fluid motor are communicated with proportional throttle valve, and the mobile control pressure or flow for passing through valve element, realize the independent control of oil inlet and outlet pressure or flow.The present invention reduces the restriction loss at valve port, system heat generation is reduced, particularly under overburden operating mode, restriction loss is not only significantly reduced, and the speed of service of hydraulic actuator can be improved, conveniently realizes that flow regenerates, effect is more notable.
Description
Technical field
The present invention relates to a kind of multiplex control system of hydraulic crawler excavator, specifically a kind of turnover for hydraulic crawler excavator
The independent multiplex control system of mouth.
Background technology
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 it is always that industry makes great efforts to chase after to reduce energy loss as the most frequently used 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 is inversely proportional.Its operation principle is：One throttling is set on multiple directional control valve middle position drainback passage
Hole, fluid produces pressure difference by throttle orifice, and pressure before throttle orifice is led to hydraulic pump stroking mechanism to control the discharge capacity of hydraulic pump.
It is open number to disclose a kind of " hydraulic excavating with hydraulic negative flow control device for CN 104452866A
Machine ", the hydraulic crawler excavator uses inverted flux control, and the discharge capacity of hydraulic pump reduces as control pressure signal increases, that is, controlled
Pressure and discharge capacity are inversely proportional.But, in traditional inverted flux control system, hydraulic pressure is controlled as main control valve using banked direction control valves
Actuator is operated, and oil inlet and outlet area immobilizes than relation, and only one of which control freedom degree, synchronization can only control hydraulic pressure
The pressure or flow of one chamber of actuator, poor controllability；Actuator is imported and exported during work throttles simultaneously, and the pressure loss is larger, special
It is not that this problem is even more serious under the operating mode of Exceed load, causes larger system heat generation, energy loss.
The content of the invention
For above-mentioned the deficiencies in the prior art, the present invention provides a kind of minus flow and imports and exports independent composite control hydraulic system
System, efficiently solves the big deficiency of poor controllability, valve port restriction loss in existing minus flow system.
To achieve the above object, the present invention is adopted the following technical scheme that.
A kind of minus flow imports and exports independent composite control hydraulic system, 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 control pilot valve, the Ith revolution control pilot valve and the IIth revolution control pilot valve；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；
Ith proportional throttle valve actuator port H of the Ith proportional throttle valve and the rod chamber of boom cylinder pass through fluid pressure line
Connection, the oil-out of the Ith proportional throttle valve are connected with fuel tank；
IIth proportional throttle valve actuator port I of the IIth proportional throttle valve and the rodless cavity of boom cylinder pass through hydraulic tube
Road connection, the oil-out of the IIth proportional throttle valve are connected with fuel tank；
The IIIth proportional throttle valve actuator port G and rotary fluid motor of IIIth proportional throttle valve
The first hydraulic fluid port of rotary fluid motor X connected by fluid pressure line, the oil-out of the IIIth proportional throttle valve is connected with fuel tank；
IVth proportional throttle valve actuator port L of the IVth proportional throttle valve and the rotary fluid motor of rotary fluid motor
Two hydraulic fluid port Y are connected by fluid pressure line, the oil-out of the IVth proportional throttle valve is connected with fuel tank；
The Ith two-position two-way solenoid valve oil inlet V and the Ith master control banked direction control valves oil-out Q of Ith two-position two-way solenoid valve pass through
Fluid pressure line connection, the oil-out of the Ith two-position two-way solenoid valve are connected with fuel tank；
The IIth two-position two-way solenoid valve oil inlet W and the IIth master control banked direction control valves actuator port of IIth two-position two-way solenoid valve
R is connected by fluid pressure line, the IIth two-position two-way solenoid valve oil-out is connected with 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 choke valve, direct action type proportional choke valve, electric closed loop proportional throttle valve and machinery
One kind in formula proportional throttle valve；Ith two-position two-way solenoid valve and the IIth two-position two-way solenoid valve are pilot-operated types 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 set up respectively in boom cylinder and the chamber of rotary fluid motor two, 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 the chamber of fuel feeding one are by master control multichannel
Valve is controlled, and the proportional throttle valve of boom cylinder or the other chamber connection of rotary fluid motor controls pressure by the movement of valve element
Power or flow, realize the independent control of oil inlet and outlet pressure or flow.
Compared with prior art, a kind of above-mentioned the provided minus flow of the present invention imports and exports independent composite control hydraulic system
System, has the advantage that and is with good effect：The throttling simultaneously of control valve oil inlet and oil return is changed to oil inlet and outlet and throttled respectively by the system,
The restriction loss at valve port is reduced, system heat generation is reduced, particularly in Exceed load operating mode, throttling is not only significantly reduced and damages
Lose, and the speed of service of hydraulic actuator can be improved, conveniently realize that flow regenerates, effect is more notable；The system independent control
The cavity pressure of hydraulic actuator two or flow, improve the controllability of work system, make system operation more steady；The system is according to need
Inlet throttle speed governing, outlet throttle timing is respectively adopted and composite throttling speed governing is imported and exported；The system uses minus flow control
Hydraulic system processed, it would however also be possible to employ minus flow imports and exports independent composite control hydraulic system.
In order to more clearly illustrate the architectural feature and effect of the present invention, pass through embodiment pair below in conjunction with the accompanying drawings
Technical scheme is further illustrated.
Brief description of the drawings
Fig. 1 is this topic structural representation 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：1st, main pump control valve；2nd, variable piston；3rd, power source；4th, main pump；5th, pioneer pump；6th, major loop safety valve；
7th, the Ith master control banked direction control valves；8th, the IIth master control banked direction control valves；9th, the Ith proportional throttle valve；10th, the IIth proportional throttle valve；11st, the IIIth ratio
Example choke valve；12nd, the IVth proportional throttle valve；13rd, boom cylinder；14th, the IIth operation handle；15th, rotary fluid motor；16、
Ith Rotatary brake valve；17th, the IIth Rotatary brake valve；18th, the Ith check valve；19th, the IIth check valve；20th, inverted flux control loop
Safety valve；21st, flow detection liquid hinders；22nd, the Ith operation handle；23rd, the Ith swing arm control pilot valve；24th, the control of the IIth swing arm is first
Pilot valve；25th, the Ith revolution control pilot valve；26th, the IIth revolution control pilot valve；27th, the IIIth master control banked direction control valves；28th, the Ith 2
Two-way electromagnetic valve；29th, the IIth two-position two-way solenoid valve；30th, scraper bowl；31st, dipper；32nd, bucket hydraulic cylinder；33rd, dipper hydraulic cylinder；
34th, swing arm；35th, get on the bus；36th, get off.
P：IIIth master control banked direction control valves oil-feed；P1：Ith the first oil inlet of master control banked direction control valves；P2：Ith master control banked direction control valves second
Oil inlet；P3：IIth the first oil inlet of master control banked direction control valves；P4：IIth the second oil inlet of master control banked direction control valves；T：Fuel tank；A：Ith master
Control the actuator port of banked direction control valves first；B：Ith the second actuator port of master control banked direction control valves；C：The actuator port of Ith master control banked direction control valves the 3rd；
D：IIth the first actuator port of master control banked direction control valves；E：IIth the second actuator port of master control banked direction control valves；F：IIth master control banked direction control valves
Three actuator ports；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：The hydraulic fluid port of rotary fluid motor first；Y：The oil of rotary fluid motor second
Mouthful；N：IIIth the first actuator port of master control banked direction control valves；O：IIIth the second actuator port of master control banked direction control valves；M：Main pump control valve works
Hydraulic fluid port；Q：Ith master control banked direction control valves oil-out；R：IIth master control banked direction control valves actuator port；V：Ith two-position two-way solenoid valve oil-feed
Mouthful；W：IIth two-position two-way solenoid valve oil inlet；K：Main pump control valve remote control orifice；K1：Ith master control banked direction control valves first are long-range
Control mouth；K2：Ith the second remote control orifice of master control banked direction control valves；K3：IIth the first remote control orifice of master control banked direction control valves；K4：IIth
The remote control orifice of master control banked direction control valves second.
Embodiment
The embodiment to the present invention is further illustrated below in conjunction with the accompanying drawings, but embodiments of the present invention
Not limited to this.
Accompanying drawing 2 shows the concrete structure of the preferred embodiments of the invention, includes main pump control valve 1, variable piston
2nd, 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
Choke 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
The 21, the Ith operation handle 22, the Ith swing arm control pilot valve are hindered to valve 19, inverted flux control loop safety valve 20, flow detection liquid
23rd, the IIth swing arm control pilot valve the 24, the Ith revolution control revolution control of pilot valve the 25, the IIth 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 control are more
Ith master control banked direction control valves the first actuator port A of road valve 7 is connected with the rod chamber of boom cylinder 13 by fluid pressure line, the Ith ratio
The oil-out of example choke valve 9 is connected with fuel tank, the IIth proportional throttle valve actuator port I of the IIth proportional throttle valve 10, the Ith master control
The actuator port C of the Ith master control banked direction control valves the 3rd of banked direction control valves 7 is connected with the rodless cavity of boom cylinder 13 by fluid pressure line, the
The oil-out of II proportional throttle valve 10 is connected with fuel tank, the IIIth proportional throttle valve actuator port G of the IIIth proportional throttle valve 11,
The IIth the first actuator port of master control banked direction control valves D, the oil inlet of the Ith Rotatary brake valve 16, the Ith check valve of II master control banked direction control valves 8
18 oil-out is connected with the first hydraulic fluid port of rotary fluid motor X of rotary fluid motor 15 by fluid pressure line, the IIIth ratio section
The oil-out of stream valve 11 is connected with fuel tank, and the IVth proportional throttle valve actuator port L of the IVth proportional throttle valve 12, the IIth master control are more
The actuator port F of the IIth master control banked direction control valves the 3rd of road valve 8, the oil inlet of the IIth Rotatary brake valve 17, the IIth check valve 19 go out
Hydraulic fluid port is connected with the second hydraulic fluid port of rotary fluid motor Y of rotary fluid motor 15 by fluid pressure line, the IVth proportional throttle valve 12
Oil-out be connected with fuel tank, the Ith two-position two-way solenoid valve oil inlet V and the Ith master control multichannel of the Ith two-position two-way solenoid valve 28
Ith master control banked direction control valves oil-out Q of valve 7 is connected by fluid pressure line, and the oil-out and fuel tank of the Ith two-position two-way solenoid valve 28 connect
It is logical, 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 of the IIth master control banked direction control valves 8
Banked direction control valves actuator port R is connected by fluid pressure line, and the oil-out of the IIth two-position two-way solenoid valve 29 is connected with fuel tank；
The Ith the first oil inlet P of master control banked direction control valves 1, the Ith master control banked direction control valves of the Ith master control banked direction control valves 7 of Ith master control banked direction control valves 7
Two oil inlet Ps 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 of the IIIth master control banked direction control valves 27 the
Master control banked direction control valves oil inlet P is connected with the oil-out of main pump 4 by fluid pressure line, the Ith master control multichannel of the Ith master control banked direction control valves 7
IIth the first oil inlet P of master control banked direction control valves 3 of valve the second actuator port B and the IIth master control banked direction control valves 8 is connected, the Ith master control multichannel
Ith master control banked direction control valves the first remote control orifice K1 of valve 7 and the Ith swing arm control pilot valve 23 oil-out connection, the Ith master control are more
Ith master control banked direction control valves the second remote control orifice K2 of road valve 7 and the IIth swing arm control pilot valve 24 oil-out connection；IIth master
The IIth master control banked direction control valves the second actuator port E for controlling banked direction control valves 8 is connected with the oil inlet that flow detection liquid hinders 21, and the IIth master control is more
The oil-out connection of the revolution control pilot valves 25 of IIth master control banked direction control valves the first remote control orifice K3 of road valve 8 and the Ith, the IIth master
Control the oil-out connection of the revolution control pilot valves 26 of the IIth master control banked direction control valves the second remote control orifice K4 and the IIth of banked direction control valves 8；
The oil-out of IIIth master control banked direction control valves 27 is connected with fuel tank, the IIIth the first working oil of master control banked direction control valves of the IIIth master control banked direction control valves 27
Mouth N and the IIIth the second actuator port of master control banked direction control valves O of the IIIth master control banked direction control valves 27 are connected with the two ends of other actuators respectively
It is logical；
The oil inlet of flow detection liquid resistance 21, the oil inlet of inverted flux control loop safety valve 20, the main pump control of main pump control valve 1
Valve remote control orifice K processed 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 detection
Oil-out, the oil-out of inverted flux control loop safety valve 20 of liquid resistance 21 are connected with fuel tank；The oil-feed of major loop safety valve 6
Mouth, the small chamber of variable piston 2, the oil inlet of main pump control valve 1 are connected with the oil-out of pioneer pump 5, major loop safety valve 6
Oil-out, the oil-out of main pump control valve 1 are connected with fuel tank, the main pump control valve actuator port M and variable of main pump control valve 1
The big chamber of piston 2 is connected；The oil inlet of Ith swing arm control pilot valve 23, the oil inlet of the IIth swing arm control pilot valve 24, the
The oil inlet of I revolution control pilot valve 25, the oil inlet of the IIth revolution control pilot valve 26 are connected with the oil-out of main pump 4,
Remote control orifice, the remote control orifice of the IIth swing arm control pilot valve 24 and the Ith operation handle of Ith swing arm control pilot valve 23
22 are connected, the remote control orifice of the Ith revolution control pilot valve 25, the remote control orifice and the IIth of the IIth revolution control pilot valve 26
Operation handle 14 is connected；The oil-out of Ith Rotatary brake valve 16, the oil-out of the IIth Rotatary brake valve 17, the Ith check valve 18
Oil inlet, the oil inlet of the IIth check valve 19 are connected with fuel tank.
Excavator in specific embodiment is 20t excavators, and the discharge capacity of main pump 4 is 100ml/r, the Ith master control banked direction control valves, the
The Center-Open multiple directional control valve that II master control banked direction control valves gating footpath is 25, the Ith proportional throttle valve, the IIth proportional throttle valve, the IIIth
The direct action type proportional choke valve that proportional throttle valve, the IVth proportional throttle valve gating footpath are 20, the Ith two-position two-way solenoid valve, the IIth
The self-action magnetic valve that two-position two-way solenoid valve gating footpath is 20.
Referring to the drawings shown in 2, the structure working principle that the present embodiment is described in detail is as follows：
（1）An inverted flux control loop safety valve is provided with the back oil road of the IIth master control banked direction control valves 8 in hydraulic system
20 and flow detection liquid resistance 21 and constitute inverted flux control detection unit, fluid 21 can produce pressure difference by the resistance of flow detection liquid,
The inlet pressure that flow detection liquid hinders 21 is led to the main pump control valve 1 of hydraulic pump stroking mechanism as inverted flux control pressure
Control port K, so as 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 lower, becomes
Amount piston 2 is moved to the left, and the swashplate angle of main pump 4 diminishes, and the output flow of main pump 4 reduces.
（2）When the Ith operation handle 22 is by controlling the Ith swing arm to control the swing arm of pilot valve 23 and the IIth to control pilot valve 24 to make
The Ith master control banked direction control valves 7 and the IIth operation handle 14 are controlled by the revolution control revolution of pilot valve 25 and the IIth of control the Ith in loop
When pilot valve 26 processed makes that the IIth master control banked direction control valves 8 are in middle position in loop, 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 circuits of master control banked direction control valves 8 are connected, and whole flows of main pump 4 return to fuel tank by flow detection liquid resistance 21,
The flow for hindering 21 by flow detection liquid reaches maximum, and then causes inverted flux control pressure to be maximum, inverted flux control
The maximum of pressure is determined by hindering 21 inverted flux control loop safety valves 20 in parallel with 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 is by controlling the Ith swing arm to control the swing arm of pilot valve 23 and the IIth to control pilot valve 24 to make
The Ith master control banked direction control valves 7 or the IIth operation handle 14 are controlled by the revolution control revolution of pilot valve 25 and the IIth of control the Ith in loop
When pilot valve 26 makes in loop the IIth master control banked direction control valves 8 be between left position and middle position, 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 or the hydraulic fluid port P4-F by the IIth master control banked direction control valves 8 of boom cylinder 13
Into the Y hydraulic fluid ports 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 oil inlet W of valve 29 with fuel tank in the case of not connected, and the actuator port H of the Ith proportional throttle valve 9 is connected or the IIIth with fuel tank
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
The actuator port L of valve 12 with fuel tank without connecting, and the hydraulic oil of the rod chamber of boom cylinder 13 passes through the Ith proportional throttle valve 9
Actuator port H or the hydraulic fluid port X of rotary fluid motor 15 first hydraulic oil pass through the actuator port G of the IIIth proportional throttle valve 11 stream
Fuel tank is returned to, by controlling the size of the Ith proportional throttle valve 9 or the IIIth proportional throttle valve 11 valve opening mouthful to control swing arm hydraulic pressure
The flow or pressure of the X hydraulic fluid ports of the rod chamber of cylinder 13 or rotary fluid motor 15, make them steadily be transported with the operating speed of needs
Make, so as 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 magnetic valve 29 is connected with fuel tank, the hydraulic oil of the rod chamber of boom cylinder 13 passes through the Ith 2
The actuator port V or the hydraulic fluid port X of rotary fluid motor 15 first of two-way electromagnetic valve 28 hydraulic oil pass through the IIth bi-bit bi-pass electromagnetism
The actuator port W of valve 29 flow back into fuel tank, and now only inverted flux control does not import and export independent control.In above-mentioned two situations
Under, the flow for hindering 21 by flow detection liquid is reduced, and the pressure that flow detection liquid hinders 21 oil inlets reduces, and the discharge capacity of main pump 4 increases
The need for 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 the rodless cavity of swing arm hydraulic motor 13 is all entered or by the by the hydraulic fluid port P2-C of the Ith master control banked direction control valves 7
The hydraulic fluid port P4-F of II master control banked direction control valves 8 enters the Y hydraulic fluid ports of rotary fluid motor 15, without flow by flow detection liquid resistance 21,
The need for the discharge capacity of main pump 4 increases to maximum to meet operating speed.
（4）When the Ith operation handle 22 is by controlling the Ith swing arm to control the swing arm of pilot valve 23 and the IIth to control pilot valve 24 to make
The Ith master control banked direction control valves 7 or the IIth operation handle 14 are controlled by the revolution control revolution of pilot valve 25 and the IIth of control the Ith in loop
When pilot valve 26 makes in loop the IIth master control banked direction control valves 8 be 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 or the hydraulic fluid port P4-D by the IIth master control banked direction control valves 8 of boom cylinder 13
Into the X hydraulic fluid ports 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 with fuel tank without in the case of being connected, and the actuator port I of the IIth proportional throttle valve 10 is connected or the IVth ratio
The actuator port L of example choke 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 not connected with fuel tank, the hydraulic oil of the rodless cavity of boom cylinder 13 passes through the IIth proportional throttle valve 10
Actuator port I or the hydraulic fluid port Y of rotary fluid motor 15 second hydraulic oil are flowed back to by the actuator port L of the IVth proportional throttle valve 12
To fuel tank, by controlling the size of the IIth proportional throttle valve 10 or the IVth proportional throttle valve 12 valve opening mouthful to control swing arm hydraulic pressure
The flow or pressure of the Y hydraulic fluid ports of the rodless cavity of cylinder 13 or rotary fluid motor 15, make them steadily be transported with the operating speed of needs
Make, so as 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 magnetic valve 29 is connected with fuel tank, the hydraulic oil of the rodless cavity of boom cylinder 13 passes through the Ith 2
The actuator port V or the hydraulic fluid port Y of rotary fluid motor 15 second of two-way electromagnetic valve 28 hydraulic oil pass through the IIth bi-bit bi-pass electromagnetism
The actuator port W of valve 29 flow back into fuel tank, and now only inverted flux control does not import and export independent control.In above-mentioned two situations
Under, the flow for hindering 21 by flow detection liquid is reduced, and the pressure that flow detection liquid hinders 21 oil inlets reduces, and the discharge capacity of main pump 4 increases
The need for 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 the rod chamber of swing arm hydraulic motor 13 is all entered or by the by the hydraulic fluid port P2-A of the Ith master control banked direction control valves 7
The hydraulic fluid port P4-D of II master control banked direction control valves 8 enters the X hydraulic fluid ports of rotary fluid motor 15, without flow by flow detection liquid resistance 21,
The need for the discharge capacity of main pump 4 increases to maximum to meet operating speed.
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 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 hydraulic pressure
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
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 swing arm control
Pilot valve processed, the Ith revolution control pilot valve and the IIth revolution control pilot valve；It is characterized in that：
Have additional the Ith proportional throttle valve（9）, the IIth proportional throttle valve（10）, the IIIth proportional throttle valve（11）, the IVth ratio throttling
Valve（12）, the Ith two-position two-way solenoid valve（28）And the IIth two-position two-way solenoid valve（29）；
Ith proportional throttle valve（9）The Ith proportional throttle valve actuator port H and boom cylinder（13）Rod chamber pass through
Fluid pressure line connection, the Ith proportional throttle valve（9）Oil-out connected with fuel tank；
IIth proportional throttle valve（10）The IIth proportional throttle valve actuator port I and boom cylinder（13）Rodless cavity lead to
Cross fluid pressure line connection, the IIth proportional throttle valve（10）Oil-out connected with fuel tank；
IIIth proportional throttle valve（11）The IIIth proportional throttle valve actuator port G and rotary fluid motor
（15）The first hydraulic fluid port of rotary fluid motor X connected by fluid pressure line, the IIIth proportional throttle valve（11）Oil-out with
Fuel tank is connected；
IVth proportional throttle valve（12）The IVth proportional throttle valve actuator port L and rotary fluid motor
（15）The second hydraulic fluid port of rotary fluid motor Y connected by fluid pressure line, the IVth proportional throttle valve（12）Oil-out with
Fuel tank is connected；
Ith two-position two-way solenoid valve（28）The Ith two-position two-way solenoid valve oil inlet V and the Ith master control banked direction control valves oil-out Q
Connected by fluid pressure line, the Ith two-position two-way solenoid valve（28）Oil-out connected with fuel tank；
IIth two-position two-way solenoid valve（29）The IIth two-position two-way solenoid valve oil inlet W and the IIth master control banked direction control valves work
Hydraulic fluid port R is connected by fluid pressure line, the IIth two-position two-way solenoid valve（29）Oil-out connected with fuel tank.
2. minus flow according to claim 1 imports and exports independent composite control hydraulic system, it is characterised in that：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）It is guide
One in formula proportional throttle valve, direct action type proportional choke valve, electric closed loop proportional throttle valve and the interior enclosed proportional throttle valve of machinery
Kind.
3. minus 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 |
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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 true CN107059983A (en) | 2017-08-18 |
| CN107059983B 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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| CN (1) | CN107059983B (en) |
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| CN107701532A (en) * | 2017-11-16 | 2018-02-16 | 恒天九五重工有限公司 | Minus flow banked direction control valves hydraulic control system and its control method |
| CN107882100A (en) * | 2017-10-11 | 2018-04-06 | 柳州柳工挖掘机有限公司 | excavator hydraulic control method and control system |
| CN108591148A (en) * | 2018-05-28 | 2018-09-28 | 河南工学院 | The accuracy control method of oilhydraulic engineering equipment |
| CN108661965A (en) * | 2018-05-28 | 2018-10-16 | 徐州燕大传动与控制技术有限公司 | A kind of 3 position-5 way load port independent control multi-way valve with Y type Median Functions |
| CN108716491A (en) * | 2018-05-28 | 2018-10-30 | 徐州燕大传动与控制技术有限公司 | A kind of 3 position-5 way load port independent control multi-way valve with O-shaped Median Function |
| CN108975188A (en) * | 2018-08-31 | 2018-12-11 | 武汉船用机械有限责任公司 | A kind of hydraulic system |
| CN110714941A (en) * | 2019-10-11 | 2020-01-21 | 燕山大学 | Pump valve composite cylinder control force control and valve control cylinder position control combined loading device and control method |
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| CN107059983B (en) | 2019-10-29 |
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