CN104806588B - Dual-pump flow-converging hydraulic control system - Google Patents
Dual-pump flow-converging hydraulic control system Download PDFInfo
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- CN104806588B CN104806588B CN201510152107.2A CN201510152107A CN104806588B CN 104806588 B CN104806588 B CN 104806588B CN 201510152107 A CN201510152107 A CN 201510152107A CN 104806588 B CN104806588 B CN 104806588B
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- 238000006073 displacement reaction Methods 0.000 claims abstract description 16
- 239000003921 oil Substances 0.000 claims description 65
- 239000010720 hydraulic oil Substances 0.000 claims description 22
- 230000009471 action Effects 0.000 claims description 11
- 239000007788 liquid Substances 0.000 claims description 11
- 239000000446 fuel Substances 0.000 claims description 7
- 238000001514 detection method Methods 0.000 claims description 2
- 230000035939 shock Effects 0.000 abstract description 6
- 239000012530 fluid Substances 0.000 description 30
- 238000005516 engineering process Methods 0.000 description 13
- 239000002828 fuel tank Substances 0.000 description 11
- 230000009467 reduction Effects 0.000 description 6
- 238000004519 manufacturing process Methods 0.000 description 4
- 238000000034 method Methods 0.000 description 4
- 230000008901 benefit Effects 0.000 description 3
- 230000033001 locomotion Effects 0.000 description 3
- 239000000203 mixture Substances 0.000 description 3
- 230000008569 process Effects 0.000 description 3
- 238000005086 pumping Methods 0.000 description 3
- 235000006508 Nelumbo nucifera Nutrition 0.000 description 2
- 240000002853 Nelumbo nucifera Species 0.000 description 2
- 235000006510 Nelumbo pentapetala Nutrition 0.000 description 2
- 238000010276 construction Methods 0.000 description 2
- 238000011161 development Methods 0.000 description 2
- 230000018109 developmental process Effects 0.000 description 2
- 238000010586 diagram Methods 0.000 description 2
- 230000000694 effects Effects 0.000 description 2
- 238000005265 energy consumption Methods 0.000 description 2
- 230000001133 acceleration Effects 0.000 description 1
- 230000032683 aging Effects 0.000 description 1
- 230000003321 amplification Effects 0.000 description 1
- 238000013459 approach Methods 0.000 description 1
- 230000008859 change Effects 0.000 description 1
- 239000002131 composite material Substances 0.000 description 1
- 239000000356 contaminant Substances 0.000 description 1
- 230000007812 deficiency Effects 0.000 description 1
- 230000005611 electricity Effects 0.000 description 1
- 230000003628 erosive effect Effects 0.000 description 1
- 230000004907 flux Effects 0.000 description 1
- 238000012423 maintenance Methods 0.000 description 1
- 238000007726 management method Methods 0.000 description 1
- 238000003199 nucleic acid amplification method Methods 0.000 description 1
- 238000011160 research Methods 0.000 description 1
- 230000035945 sensitivity Effects 0.000 description 1
- 230000035882 stress Effects 0.000 description 1
- 230000007704 transition Effects 0.000 description 1
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
- F15B11/00—Servomotor systems without provision for follow-up action; Circuits therefor
- F15B11/16—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors
- F15B11/17—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors using two or more pumps
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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
-
- 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
- F15B13/16—Special measures for feedback, e.g. by a follow-up device
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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)
Abstract
The present invention relates to hydraulic control system, big shortcoming is impacted to solve existing dual-pump combining hydraulic system, the present invention provides a kind of Dual-pump flow-converging hydraulic control system, it includes hydraulic system of working, second hydraulic pump, electrichydraulic control off-load valve group, work system is connected valve group interflow oil-out by the road, valve group collaborates have check valve between oil inlet and valve group interflow oil-out, the oil inlet end of external control overflow valve and internal control end are connected with the oil inlet end of check valve, the oil-out of external control overflow valve is connected with valve group off-load oil-out, solenoid directional control valve, external control end and the valve group off-load oil-out of external control overflow valve are connected to after pilot operated directional control valve concatenation, pilot operated directional control valve hydraulic control end is connected through shuttle valve with pilot valve, control device includes controller and displacement detector, the automatically controlled end of solenoid directional control valve is connected with controller.The present invention can reduce hydraulic shock of the hydraulic actuator in its stroke terminal.
Description
Technical field
The present invention relates to a kind of engineering machinery hydraulic control system, more particularly to a kind of double pump of two pressure oil-source fuel feeding
Collaborate hydraulic control system.
Background technology
There are at least two pressure oil-sources in the pressure oil-source of the multiple fuel feeding of many engineering machinery, such as loading machine, wherein
One steering hydraulic system is used to turn to, and another is that hydraulic system of working is used for equipment such as boom cylinder, rotating bucket
The fuel feeding such as oil cylinder.Loading machine is as the main force of engineering machinery, and because its is cheap, using simple operation, mobile transition is fast
Fast the advantages of, it is widely used among many engineering projects, but there is too high oil consumption, excessive discharge capacity and oil in it
The shortcomings of liquid is easily leaked.With energy-saving requirement, loader hydraulic system it is energy-saving also gradually extensive by people
Concern.The energy consumption of loader hydraulic system is mainly reflected in the volumetric loss of hydraulic pump, motor and oil cylinder, valve element and pipeline
The various pressure losses of element, mechanical friction loss of each class component etc..These losses eventually exist in the form of heat
Among hydraulic system so that the oil temperature rise of hydraulic system, and higher oil temperature can directly influence hydraulic system parts
Performance, cause the aging of seal and sebific duct, valve element it is stuck because of expansion, due to temperature rise caused by oil viscosity reduction and let out
Dew increase, fluid vaporize to form cavitation erosion, volumetric efficiency reduction etc..Operationally, load is changed greatly loading machine, and at present
The most of loader hydraulic system of in the market is all fixed dilivery hydraulic system, therefore loading machine is just difficult in working cycle process
Exempt from can have many spill losses, off-load loss and restriction losses etc., the temperature rise of loading machine quantitative hydraulic system more than 90%
It is due to that these losses are caused to be substantially all, therefore how to reduce the unnecessary loss of hydraulic system, research quantitative hydraulic system
The power saving of system has great importance.
The hydraulic system of existing loading machine is general by hydraulic system of working, steering hydraulic system and hydraulic braking system etc.
Composition, hydraulic system of working is often made up of elements such as working barrel, distributing valve, pilot valve, boom cylinder, rotary ink tanks, turns to liquid
Pressure system is often made up of elements such as steering pump, pressure-gradient control valve, steering gear (flux amplification valve), steering cylinders, hydraulic braking system often by
The elements such as brake pump, replenishing valve, brake valve, accumulator are constituted.At present, the most loading machine of in the market still uses quantitative hydraulic
System；Also there is the situation that quantitative and variable delivery hydraulic system is combined with each other；Full change is almost employed in high-end loading machine
Measure hydraulic system.For fixed dilivery hydraulic system is compared to variable delivery hydraulic system, it has maturity high, good reliability, antipollution
Property it is strong, the advantages of cost performance is high, and fixed dilivery hydraulic system is fully able to meet the normal operation requirement of loading machine, but quantitative
Hydraulic system is there is also perhaps many deficiencies, and such as energy loss is serious, can not carry out composite move operation, the controllability of system
It is bad, the shortcomings of hydraulic shock is big.
One of the characteristics of variable delivery hydraulic system is can to carry out stepless speed regulation, so that unnecessary energy loss is reduced,
But the cost of variable system is high, manufacture difficulty is big, and system is relative complex, contaminant sensitivity of the variable system element to fluid
Height, for middle and low-end market, quantitative system is easier to allow user to receive than variable system.The use of converging system can be with
Realize and multistep speed regulation is carried out to system, if the quantity of pump is enough, the function of multiple pump will become closer to variable system
System.Loading machine in operation, different operating modes, different work object to the movement needs of executive component all difference, therefore it
Different rate requests are accomplished by, for the system of single oil pump feed, converging system can bring the discharge capacity of more pumps
Combination, realizes more rate requests, while the energy-saving effect of converging system is more notable.
Electrohydraulic control technology uses highly developed in industrial hydraulic, and various production lines, lathe of factory etc. have extensively
General application.Electrohydraulic control technology can substantially be divided into：The control of electromagnetic switch type, electrical-liquid control and electro-hydraulic servo control.
Electromagnetic switch type electrohydraulic control technology is the electrohydraulic control technology grown up earliest, and it with controlling manually, control of surging, motor-driven
The one kind that belong among many hydraulic controls such as control, switching mode control only has a function on or off, without ratio or
The function of servo, but its is simple in construction, good reliability, is the electrohydraulic control technology being widely used earliest.Electric-hydraulic proportion control
The implication of system refers to the output quantity of hydraulic system, such as pressure, flow, displacement, speed, rotating speed, acceleration, power, torque, can be with
Control signal such as electric current, voltage etc. are proportional is controlled for input, and the most crucial part of electro-hydraulic proportional control technology is ratio
Electromagnet, it is the converting member of electromechanical, its function be the current signal converting to force that exports Proportional Amplifer or
Displacement, electrohydraulic proportion technology is relative complex, manufacturing cost is of a relatively high, but has industrially also obtained many applications, in work
Journey mechanical field, such as serial later most loading machines of card spy H also use electro-hydraulic proportional control technology, and main valve is displaced through
The electro-hydraulic proportional reducing valves of left and right ends is controlled.The development of electro-hydraulic servo control starts from World War II weaponry,
There are good rapidity, dynamic accuracy and power-weight ratio etc., the end of the year 1940, electrohydraulic servo-controlling system to control system requirement
Appeared in first on aircraft, by the development of more than 20 years, various electrohydraulic servo valves were come out one after another, electro-hydraulic servo technology increasingly into
Ripe, the cleannes of electrohydraulic servo valve fluid medium have very harsh requirement, and manufacturing cost and maintenance cost costly, are
Energy consumption of uniting is also than larger, and electro-hydraulic servo technology is obtained extensively unlike electromagnetic hydraulic pressure control technology and electro-hydraulic proportional control technology
Application, in construction machinery hydraulic system, servo techniques is commonly used on the displacement control to variable pump.
In existing dual-pump combining hydraulic system, due to the interflow of many pumps, hydraulic system has big flow, high pressure
Feature, when hydraulic actuation element such as hydraulic jack runs to the terminal of its stroke, can cause huge impact.
The content of the invention
A kind of energy is provided it is an object of the invention to impact big shortcoming for existing dual-pump combining hydraulic system automatically
Close many pump combining hydraulic systems that Dual-pump flow-converging function reduces hydraulic shock.
The technical proposal of the invention is realized in this way：A kind of Dual-pump flow-converging hydraulic control system, including the first liquid are provided
Press pump, distributing valve, hydraulic actuator, pilot valve, the second hydraulic pump, hydraulic oil container, the first hydraulic pump connect with distributing valve by the road
Connect, distributing valve is connected with hydraulic actuator by the road, the allocated valve of the first hydraulic pump is to hydraulic actuator fuel feeding, and pilot valve is through a left side
Pipeline and right pipeline are connected the commutation action of control distributing valve with distributing valve, and the control system also includes electrichydraulic control off-load in addition
Valve group, electrichydraulic control off-load valve group include external control overflow valve, solenoid directional control valve, control device, pilot operated directional control valve, valve group collaborate into
Hydraulic fluid port, valve group interflow oil-out, valve group off-load oil-out, the second hydraulic pump are connected with valve group interflow oil inlet by the road, valve group
Oil-out is connected with the interflow oil inlet of distributing valve by the road, valve group off-load oil-out is connected with hydraulic oil container by the road at interflow,
Collaborate to have between oil inlet and valve group interflow oil-out the check valve for collaborating oil-out one-way conduction to valve group, external control in valve group
The oil inlet end of overflow valve and internal control end are connected with the oil inlet end of check valve, oil-out and the valve group off-load oil-out of external control overflow valve
It is connected to after connection, solenoid directional control valve, pilot operated directional control valve concatenation between the external control end of external control overflow valve and valve group off-load oil-out,
Left pipeline of the hydraulic control end of pilot operated directional control valve through shuttle valve and pilot valve and the connection of right pipeline, control device include controller and with control
Device processed is connected to detect the displacement detector of hydraulic actuator travel position, and automatically controlled end and the controller of solenoid directional control valve connect
Connect.In the present invention, the pressure oil of the pumping of the second hydraulic pump is delivered to valve group interflow oil inlet, when pilot valve has action
When, the oil supply pressure of pilot valve acts on the hydraulic control end of pilot operated directional control valve, pilot operated directional control valve is opened conducting, and now controller leads to
The travel position that displacement detector detects hydraulic actuator is crossed, if the stroke of hydraulic actuator is not in ad-hoc location, now
Controller do not send control signal make solenoid directional control valve be in it is normally closed block state, now the external control end of external control overflow valve not with
Outside is communicated, and external control overflow valve is also at cut-off state, and the hydraulic oil of the second hydraulic pump pumping collaborates oil inlet, list by valve group
The hydraulic oil interflow for flowing to distributing valve and the first hydraulic pump to valve, valve group interflow oil-out is supplied to hydraulic actuator, realizes double
Pump collaborates to hydraulic actuator fuel feeding；When the travel position that controller detects hydraulic actuator by displacement detector is in
Ad-hoc location it is for example fast close to its stroke end when, now controller, which sends control signal, makes solenoid directional control valve commutation conducting, outside
The hydraulic oil at the external control end of control overflow valve is by solenoid directional control valve, the pilot operated directional control valve of conducting unlatching from valve group off-load oil-out
Flow into the pressure reduction at hydraulic oil container loop, the external control end of external control overflow valve, effect of the external control overflow valve in its internal control end oil pressure
Lower commutation and turn on, the hydraulic oil for collaborating oil inlet inflow from valve group through external control overflow valve flows to hydraulic pressure from valve group off-load oil-out
Fuel tank, realizes the off-load of the second hydraulic pump hydraulic oil.The second hydraulic pump is pumped in the end-of-travel position of hydraulic actuator
Hydraulic oil carries out off-load, not only saves the energy, while no matter load on hydraulic actuator is much, as long as the stroke position of actuator
Put and reach setting position, with regard to off-load can be carried out, so as to reduce hydraulic actuator caused hydraulic shock in stroke terminal.
Further, in Dual-pump flow-converging hydraulic control system, electrichydraulic control off-load valve group also includes pressure regulator valve, and pressure regulator valve connects
It is connected between the external control end of external control overflow valve and valve group off-load oil-out, the hydraulic control end of pressure regulator valve and the oil outlet end of check valve connect
It is logical.In this scheme, when the load of hydraulic actuator is not up to setting, pressure regulator valve cut-off, the external control end of external control overflow valve is not
With turned on outside, external control overflow valve be in cut-off state, now the second hydraulic pump pumping hydraulic oil pass through by valve group collaborate into
Hydraulic fluid port, check valve, valve group interflow oil-out flow to distributing valve and the hydraulic oil interflow of the first hydraulic pump is supplied to hydraulic actuator,
Realize Dual-pump flow-converging to hydraulic actuator fuel feeding；When the load of hydraulic actuator reaches the set pressure of pressure regulator valve, pressure regulator valve
The pressure at hydraulic control end promote pressure regulator valve commutation, oil inlet and the oil-out conducting of pressure regulator valve, so that external control overflow valve
The valve group off-load oil-out conducting of external control end and valve group, the pressure reduction at the external control end of external control overflow valve, external control overflow valve is at it
Commutate and turn in the presence of the oil pressure of internal control end, the hydraulic oil for collaborating oil inlet inflow from valve group is unloaded through external control overflow valve from valve group
Lotus oil-out flows to hydraulic oil container, realizes the off-load of the second hydraulic pump hydraulic oil, no matter what hydraulic actuator is in for now off-load
The travel position at place, as long as its load reaches just carries out off-load during certain value to the interflow hydraulic oil of the second hydraulic pump.
In above-mentioned Dual-pump flow-converging hydraulic control system, including turning control cell and be connected with turning control cell turn
To oil cylinder, steering cylinder is connected with turning control cell, the interflow oil-out of turning control cell collaborate by the road with valve group into
Hydraulic fluid port is connected.In this scheme, the second hydraulic pump is as the hydraulic pump of steering, and when there is steering demand, the second hydraulic pump is pumped
Hydraulic oil steering cylinder is preferentially fed to by turning control cell, without turn to demand when, the hydraulic pressure that the second hydraulic pump is more sent
Oil is conveyed by the interflow oil-out of turning control cell to electrichydraulic control off-load valve group, for collaborating with the first hydraulic pump.
In above-mentioned Dual-pump flow-converging hydraulic control system, hydraulic actuator is hydraulic jack.Displacement detector is used to examine
The travel position of the piston rod of hydraulic jack is surveyed, mainly detects piston rod whether close to fully extended position or close to returning completely
Condense and put.
In above-mentioned Dual-pump flow-converging hydraulic control system, hydraulic actuator is two groups of hydraulic jacks, such as loading machine it is dynamic
Arm oil cylinder and rotary ink tank, distributing valve are duplex and connected with corresponding two groups of hydraulic jacks that pilot valve is that duplex is each corresponded to
It is connected with distributing valve, i.e., a pilot valve therein is connected to the hydraulic control two ends of one of distributing valve by its left and right pipeline,
For the control of boom cylinder, a pilot valve passes through the hydraulic control two ends of its left and right pipeline and another distributing valve in addition, uses
In the control of rotary ink tank, solenoid directional control valve and pilot operated directional control valve are respectively two, one of solenoid directional control valve and a hydraulic control
Reversal valve is connected, and another solenoid directional control valve is connected with another pilot operated directional control valve, solenoid directional control valve and liquid after series connection
Solenoid directional control valve and pilot operated directional control valve that control reversal valve is connected with another set are connected in parallel on external control end and the valve group of external control overflow valve
Between off-load oil-out, the hydraulic control ends of two pilot operated directional control valves each via shuttle valve correspondence connect a pilot valve left pipeline and
Right pipeline, the automatically controlled end of two solenoid directional control valves is connected with controller.Two solenoid directional control valves and two hydraulic controls are changed in the program
It can be substituted to valve by the O-shaped function solenoid directional control valve of a 3-position 4-way and the O-shaped function pilot operated directional control valve of a 3-position 4-way,
The O-shaped function solenoid directional control valve of 3-position 4-way and the O-shaped function pilot operated directional control valve of 3-position 4-way are still connected；Solenoid directional control valve two ends
Automatically controlled end is connected with controller, and the two ends hydraulic control end of pilot operated directional control valve is each via shuttle valve and the left pipeline of corresponding pilot valve and the right side
Pipeline is connected.In such scheme, displacement detector is two groups and corresponds to the travel position for detecting two groups of hydraulic jacks respectively.
The present invention has the advantage that compared with prior art：Stroke position of the invention by detecting hydraulic actuator
Put, off-load is carried out to the hydraulic oil of the second hydraulic pump when hydraulic actuator runs to setting position, reduction reduces hydraulic pressure and performed
Device produces huge hydraulic shock in its stroke terminal.
Brief description of the drawings
Fig. 1 is that the present invention is applied to loader dual-pump combining hydraulic control system principle schematic；
Fig. 2 is that the present invention shows applied to the composition of electrichydraulic control off-load valve group in loader dual-pump combining hydraulic control system
It is intended to；
Fig. 3 is another composition schematic diagram of electrichydraulic control off-load valve group of the present invention.
Parts title and sequence number in figure：
1. steering cylinder, 2. turning control cells, 3. fuel tanks, 4. second hydraulic pumps, 5. electrichydraulic control off-load valve groups, 5-1.
First solenoid directional control valve, the solenoid directional control valves of 5-2. second, 5-3. external controls overflow valve, 5-4. pressure regulator valves, the liquid controlled reversings of 5-5. second
Valve, the pilot operated directional control valves of 5-6. first, 5-7. check valves, 6. first hydraulic pump pumps, 7. distributing valves, 8. boom cylinders, 9. rotating buckets oil
Cylinder, 10. pilot valves, 11. first shuttle valves, 12. second shuttle valves, the O-shaped function solenoid directional control valve of 13. 3-position 4-ways, 14. 3 four
Lead to O-shaped function pilot operated directional control valve.
Embodiment
Illustrate specific embodiment below in conjunction with the accompanying drawings.
The present embodiment is the application on Dual-pump flow-converging hydraulic control system loading machine, and as shown in Figure 1, the hydraulic system includes
As in the first hydraulic pump 6 of working barrel, distributing valve 7, boom cylinder 8, rotary ink tank 9, pilot valve 10, distributing valve 7 have two
Connection commutation main valve, boom cylinder 8 and rotary ink tank 9 are corresponded to respectively to be connected with therein one commutation main valve, pilot valves 10
With two, two pilot valves in pilot valves 10 pass through respective left pipeline and right pipeline and corresponding commutation main valve respectively
Connection, the commutation action of control commutation main valve, so as to realize commutation main valve to boom cylinder 8, the expanding-contracting action of rotary ink tank 9.
In the hydraulic system, in addition to it is used as the second hydraulic pump 4, turning control cell 2, the steering cylinder 1 of steering pump, the second liquid
Press pump 4 and steering cylinder 1 are all connected by pipeline with turning control cell 2, and steering cylinder 1 is controlled by turning control cell 2
It is flexible and realize course changing control.Turning control cell 2 has an interflow oil-out 2b, and distribution valve group 7 has interflow oil-feed
Mouth 7b, electrichydraulic control off-load valve group 5 has valve group interflow oil inlet 5a, valve group interflow oil-out 5b, valve group off-load oil-out 5c,
Wherein collaborate fuel-displaced 2b to connect by pipeline and valve group interflow oil inlet 5a, interflow oil inlet 7b collaborates by pipeline with valve group
Hydraulic fluid port 5b is connected, and valve group off-load oil-out 5c is connected by pipeline with fuel tank 3.
As shown in Fig. 2 electrichydraulic control off-load valve group 5 include external control overflow valve 5-3, pressure regulator valve 5-4, check valve 5-7, two
Solenoid directional control valve, two pilot operated directional control valves, wherein the first solenoid directional control valve 5-1 oil-out 51b and the first pilot operated directional control valve 5-6
Oil inlet 56a connect to form series connection, the second solenoid directional control valve 5-2 oil-out 52b and the second pilot operated directional control valve 5-5 oil-feed
Mouthful 55a connects to form series connection, and check valve 5-7 is connected to valve group interflow oil inlet 5a and valve group is collaborated between oil-out 5b and to valve
Combination outflow hydraulic fluid port 5b directions one-way conduction, external control overflow valve 5-3 oil inlet end 53a and internal control end 53A and entering for check valve 5-7
Oily end connection, external control overflow valve 5-3 oil outlet end 53b is connected with valve group off-load oil-out 5c, external control overflow valve 5-3 external control end
53B is connected with the first solenoid directional control valve 5-1 oil inlet 51a, the second solenoid directional control valve 5-2 oil inlet 52a simultaneously, the first liquid
The oil-out 55b for controlling reversal valve 5-6 oil-out 56b and the second pilot operated directional control valve 5-5 connects with valve group off-load oil-out 5c simultaneously
It is logical；Pressure regulator valve 5-4 oil inlet 54a is also connected with external control overflow valve 5-3 external control end 53B, pressure regulator valve 5-4 oil-out 54b
Also connected with valve group off-load oil-out 5c, the oil outlet end of pressure regulator valve 5-4 hydraulic control end 54A then with check valve 5-7 is connected, pressure regulator valve
5-4 is normally close valve, when the pressure at the 54A of its hydraulic control end is more than its presetting pressure, pressure regulator valve 5-4 valve element commutation, its
Oil inlet end 54a to oil outlet end 54b is turned on.
As shown in figure 1, the first pilot operated directional control valve 5-6 hydraulic control end 56A in the first shuttle valve 11 and pilot valves 10 by moving
The left pipeline of arm connection pilot valve and right management connection, the left pipeline of swing arm connection pilot valve and the distributing valve of right pipeline connection are controls
The swing arm connection distributing valve of brake arm oil cylinder 8；Second pilot operated directional control valve 5-5 hydraulic control end 55A passes through the second shuttle valve 12 and pilot valve
The left pipeline of another rotating bucket connection pilot valve in group 10 and the connection of right pipeline, the rotating bucket join the left pipeline and right pipe of pilot valve
The distributing valve of road connection is the rotating bucket connection distributing valve for controlling rotary ink tank 9；First pilot operated directional control valve 5-6 and the second pilot operated directional control valve
5-5 is normally closed reversal valve, when having operational motion on pilot valve, the first pilot operated directional control valve 5- of connection corresponding with pilot valve
6 or second pilot operated directional control valve 5-5 commutation turn it on.First solenoid directional control valve 5-1 and the second solenoid directional control valve 5-2 automatically controlled end
Connected respectively at the different output ends of controller, signal input part and detection boom cylinder 8, the work of-rotary ink tank 9 of controller
The displacement detector connection of position is filled in, the first solenoid directional control valve 5-1 and the second solenoid directional control valve 5-2 are also normally closed solenoid valve,
When displacement detector detects boom cylinder 8, the piston rod of-rotary ink tank 9 stretches out or retracted to predeterminated position and such as approaches
During end-of-travel position, controller corresponding solenoid directional control valve into the first solenoid directional control valve 5-1 and the second solenoid directional control valve 5-2
Output control electric potential signal, makes corresponding solenoid directional control valve be commutated and be turned it on.
The action realization principle of loader dual-pump combining hydraulic system is as follows in the present embodiment：
When steering has demand, the second hydraulic pump 4 draws hydraulic oil entering by turning control cell from fuel tank 3
Hydraulic fluid port 2a simultaneously enters steering cylinder 1 by its hydraulic fluid port 2c or hydraulic fluid port 2d, realizes the go to action of machine.The unnecessary oil of steering
The interflow oil-out 2b of the diverted control unit of liquid collaborates oil inlet 5a and valve group interflow to the valve group of electrichydraulic control off-load valve group 5
The interflow oil inlet 7b that oil-out 5b enters distribution valve group 7 collaborates among hydraulic system of working.
The hydraulic pressure oil two-way of electrichydraulic control off-load valve group 5, reaches valve group interflow by its internal check valve 5-7 all the way
Oil-out 5b enters hydraulic system of working；External control overflow valve 5-3 oil inlet 53a is reached all the way and acts on its internal control end 53A；
External control overflow valve 5-3 external control end 53B and pressure regulator valve 5-4 oil inlet end 54a are connected, and are produced when from hydraulic system of working pressure
Power overcome pressure regulator valve 5-4 pressure spring so that pressure regulator valve 5-4 commutation make pressure regulator valve 5-4 oil inlet end 54a and oil outlet end 54b
During conducting, external control overflow valve 5-3 external control end 53B oil inlet end 54a and oil outlet end 54b of the fluid through pressure regulator valve 5-4 reach valve
Group off-load oil-out 5c, 5c mouthfuls of valve group off-load oil-out is communicated with fuel tank 3, and external control overflow valve 5-3 external control end 53B fluid is unloaded
Lotus, now check valve 5-7 closings, external control overflow valve 5-3 oil inlet 53a and oil-out 53b conducting, from turning control cell 2
The fluid of middle outflow flows back to fuel tank by external control overflow valve 5-3 oil inlet 53a and oil-out 53b, valve group off-load oil-out 5c
3, realize the fluid Low-pressure load discharge of the second hydraulic pump.In this unloading process, performed with the hydraulic pressure such as boom cylinder 8, rotary ink tank 9
The travel position of device is unrelated, only relevant with the load on these hydraulic actuators.
During the swing arm connection pilot valve of operated pilot valve group 10, pilot pressure oil controls distributing valve through its left pipeline and right pipeline
The action of swing arm connection commutation main valve plug in group 7；As long as swing arm connection pilot valve has pressure, this pilot pressure can pass through the first shuttle valve 11
The first pilot operated directional control valve 5-6 hydraulic control end 56A is reached so that the first pilot operated directional control valve 5-6 commutation conductings；If now boom cylinder
Piston rod stretch ad-hoc location for example close to the position of its stroke end, displacement detector is detected after the state, control
Device sends automatically controlled signal to the first solenoid directional control valve 5-1 automatically controlled end 2YA turns on its commutation, external control overflow valve 5-3 external control
53B fluid is held to reach valve group off-load oil-out 5c and the phase of fuel tank 3 through the first solenoid directional control valve 5-1, the first pilot operated directional control valve 5-6
Lead to, external control overflow valve 5-3 external control end 53B fluid off-load, now closed check valve, external control overflow valve 5-3 conductings, from steering
The hydraulic oil that control unit comes flows back to fuel tank through external control overflow valve 5-3, realizes the second hydraulic pump fluid Low-pressure load discharge.Similarly,
During the rotating bucket connection of operated pilot valve group 10, the Stress control of pilot pressure oil the action that distribution valve group 7 rotating bucket joins valve element；As long as
Rotating bucket connection pilot valve has pressure, and this pilot pressure can reach the second pilot operated directional control valve 5-5 hydraulic control end 55A by the second shuttle valve 12
So that pilot operated directional control valve 5-5 commutates；If now the piston rod of rotary ink tank stretches ad-hoc location for example close to its stroke end
Position, displacement detector is detected after the state, and controller sends automatically controlled to the second solenoid directional control valve 5-2 automatically controlled end 1YA
Signal makes its commutation conducting, and external control overflow valve 5-3 external control end 53B fluid is changed through the second solenoid directional control valve 5-2, the second hydraulic control
Valve group off-load oil-out 5c is reached to valve 5-5 to communicate with fuel tank 3, external control overflow valve 5-3 external control end 53B fluid off-load, this
When check valve 5-7 close, external control overflow valve 5-3 conductings, the hydraulic oil come from turning control cell flows through external control overflow valve 5-3
Oil return box, realizes the second hydraulic pump fluid Low-pressure load discharge.In this unloading process, the fluid of the second hydraulic pump whether off-load and liquid
Press the load of actuator unrelated, only related to the travel position of hydraulic actuator, this measure can be whole in its stroke in hydraulic actuator
End position nearby carries out off-load, hydraulic shock of the reduction hydraulic actuator in its stroke terminal to the second hydraulic pump fluid.
In the hydraulic system, when the load of rotary ink tank 9 or boom cylinder 8 is less than pressure regulator valve 5-4 set pressure,
The piston rod of boom cylinder 8 and rotary ink tank is not on specific travel position, and external control overflow valve 5-3 blocks shape in closing
State, the second hydraulic pump fluid come from turning control cell stream is realized and the first hydraulic pump 6 through check valve 5-7 flow direction distribution valve groups
Fluid interflow.
In hydraulic system shown in Fig. 1 Fig. 2, the first solenoid directional control valve 5-1 and first in electrichydraulic control off-load valve group 5
Pilot operated directional control valve 5-6 connects, as swing arm linkage control valve group；Second solenoid directional control valve 5-2 and the second pilot operated directional control valve 5-5 strings
Connection, as rotating bucket linkage control valve group；Swing arm linkage control valve group, rotating bucket linkage control valve group and pressure regulator valve 5-4 are connected in parallel on external control overflow
Between valve 5-3 external control end 53B and valve group off-load oil-out 5c, it is possible to achieve individually control the second hydraulic pump fluid off-load and
It does not interfere with each other, can forms the control mode of combination yet.
When the piston rod movement of boom cylinder 8 is to close to limit position, the fluid of the second hydraulic pump is in setting displacement
Locate off-load, if now unclamping swing arm connection pilot valve handle, the first pilot operated directional control valve 5-6 hydraulic control end 56A fluid can be by the
The oil-out that the swing arm of one shuttle valve 11 and pilot valves is linked to up to pilot valves is communicated with fuel tank, and the first pilot operated directional control valve 5-6 exists
Resetted in the presence of left end spring force, cut off external control overflow valve 5-3 external control end 53B to the passage of fuel tank 3, unloading function disappears
Lose, the fluid of the second hydraulic pump enters hydraulic system of working by check valve 5-7, be that next action of work system prepares foot
Enough fluid.When rotary ink tank moves to limit position, release handle, the action of electrichydraulic control off-load valve group 5 is similar with above-mentioned.
In the above-described embodiment, the first pilot operated directional control valve and the second pilot operated directional control valve can use an O-shaped machine of 3-position 4-way
Energy pilot operated directional control valve 14 is substituted, and the O-shaped function electricity of a 3-position 4-way can be used in the first solenoid directional control valve and the second solenoid directional control valve
Magnetic reversal valve 13 is replaced, as shown in figure 3, the O-shaped function pilot operated directional control valve of 3-position 4-way and the O-shaped function solenoid directional control valve of 3-position 4-way
It is connected to after series connection between external control overflow valve 5-3 and valve group off-load oil-out 5c, the O-shaped function solenoid directional control valve 13 of 3-position 4-way
The automatically controlled end in two ends is connected with controller, and the two ends hydraulic control end of the O-shaped function pilot operated directional control valve 14 of 3-position 4-way is each by corresponding
The left pipeline and right pipeline that shuttle valve joins pilot valve and swing arm connection pilot valve with rotating bucket are connected, and can equally be realized in above-mentioned Fig. 1 Fig. 2
The function of hydraulic system in schematic diagram.
Claims (6)
1. a kind of Dual-pump flow-converging hydraulic control system, including the first hydraulic pump, distributing valve, hydraulic actuator, pilot valve, the second liquid
Press pump, hydraulic oil container, first hydraulic pump are connected with distributing valve by the road, and the distributing valve connects with hydraulic actuator by the road
Connect, the allocated valve of the first hydraulic pump is to hydraulic actuator fuel feeding, and the pilot valve is through left pipeline and right pipeline and distributing valve
The commutation action of connection control distributing valve, it is characterised in that also including electrichydraulic control off-load valve group, the electrichydraulic control unloading valve
Group includes external control overflow valve (5-3), solenoid directional control valve (5-1), control device, pilot operated directional control valve (5-6), valve group interflow oil inlet
(5a), valve group interflow oil-out (5b), valve group off-load oil-out (5c), pressure regulator valve (5-4), second hydraulic pump by the road with
Valve group interflow oil inlet (5a) connection, valve group interflow oil-out (5b) is connected with the interflow oil inlet of distributing valve by the road, valve group
Off-load oil-out (5c) is connected with hydraulic oil container by the road, valve group interflow oil inlet (5a) with valve group interflow oil-out (5b) it
Between have to valve group collaborate oil-out (5b) one-way conduction check valve, the oil inlet end (53a) of the external control overflow valve (5-3) and
(53A) is connected with the oil inlet end of the check valve at internal control end, and the oil-out of the external control overflow valve (5-3) and valve group off-load are fuel-displaced
The external control overflow valve (5-3) is connected to after mouth (5c) connection, the solenoid directional control valve (5-1), pilot operated directional control valve (5-6) concatenation
External control end (53B) and valve group off-load oil-out (5c) between, the hydraulic control end (56A) of pilot operated directional control valve (5-6) is through shuttle valve and institute
Left pipeline and the connection of right pipeline of pilot valve are stated, the control device includes controller and is connected to detect hydraulic pressure with controller
The displacement detector of actuator travel position, the automatically controlled end of the solenoid directional control valve (5-1) is connected with controller,
The pressure regulator valve is connected between the external control end (53B) of the external control overflow valve (5-3) and valve group off-load oil-out (5c),
The hydraulic control end (54A) of the pressure regulator valve is connected with the oil outlet end of the check valve.
2. Dual-pump flow-converging hydraulic control system according to claim 1, it is characterised in that also including turning control cell and
The steering cylinder being connected with turning control cell, the steering cylinder is connected with the turning control cell, the course changing control
The interflow oil-out of unit is connected with valve group interflow oil inlet (5a) by the road.
3. Dual-pump flow-converging hydraulic control system according to claim 1, it is characterised in that the hydraulic actuator is hydraulic pressure
Oil cylinder.
4. Dual-pump flow-converging hydraulic control system according to claim 3, it is characterised in that the hydraulic actuator is two groups
Hydraulic jack, the distributing valve is duplex and connected with corresponding two groups of hydraulic jacks that the pilot valve is that duplex is each corresponded to
It is connected with described distributing valve, the solenoid directional control valve and pilot operated directional control valve are respectively two, one of solenoid directional control valve and one
Individual pilot operated directional control valve series connection, another solenoid directional control valve is connected with another pilot operated directional control valve, the electromagnetic switch after series connection
The solenoid directional control valve and pilot operated directional control valve that valve and pilot operated directional control valve are connected with another set are connected in parallel on the outer of the external control overflow valve
Control between end and valve group off-load oil-out, the hydraulic control end of described two pilot operated directional control valves is each via one elder generation of shuttle valve correspondence connection
The left pipeline and right pipeline of pilot valve, the automatically controlled end of described two solenoid directional control valves is connected with the controller.
5. Dual-pump flow-converging hydraulic control system according to claim 3, it is characterised in that the hydraulic actuator is two groups
Hydraulic jack, the distributing valve is duplex and connected with corresponding two groups of hydraulic jacks that the pilot valve is that duplex is each corresponded to
It is connected with described distributing valve, the solenoid directional control valve is the O-shaped function solenoid directional control valve of 3-position 4-way；The pilot operated directional control valve
For the O-shaped function pilot operated directional control valve of 3-position 4-way；The automatically controlled end of the solenoid directional control valve is connected with the controller, and the hydraulic control is changed
Connected to the two ends hydraulic control end of valve each via shuttle valve with the left pipeline of corresponding pilot valve and right pipeline.
6. the Dual-pump flow-converging hydraulic control system according to claim 4 or 5, it is characterised in that described displacement detector
Correspond to the travel position of two groups of hydraulic jacks of detection respectively for two groups.
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| CN105110192B (en) * | 2015-07-31 | 2018-03-20 | 徐州徐工液压件有限公司 | A kind of hydraulic crane collaborates control device |
| CN105114687B (en) * | 2015-08-19 | 2017-12-05 | 江苏大学 | A kind of more hydraulic butterfly valves open and close control hydraulic control system |
| CN105350598B (en) * | 2015-10-21 | 2018-06-12 | 徐工集团工程机械股份有限公司科技分公司 | A kind of hydraulic control system and control method for improving loading machine energy saving |
| CN105465088B (en) * | 2015-12-22 | 2017-10-31 | 徐州徐工液压件有限公司 | A kind of banked direction control valves does not collaborate automatic adaptive device |
| CN106351909B (en) * | 2016-08-30 | 2018-08-21 | 徐州重型机械有限公司 | A kind of more oil supply unit interflow switching system |
| CN108568450A (en) * | 2017-03-12 | 2018-09-25 | 上海康恒环境股份有限公司 | A kind of automatic control system of self-propelled soil remediation equipment |
| CN107387506A (en) * | 2017-07-31 | 2017-11-24 | 江苏大学 | A kind of dual-workpiece abrasive Flow polishes machine hydraulic power system |
| CN110486341B (en) * | 2018-05-14 | 2023-03-21 | 博世力士乐（北京）液压有限公司 | Hydraulic control system and mobile working equipment |
| CN112012969B (en) * | 2020-08-27 | 2022-07-12 | 广西柳工机械股份有限公司 | Hydraulic system and loader |
| CN114087249B (en) * | 2021-11-18 | 2023-05-26 | 国能神东煤炭集团有限责任公司 | Electrohydraulic pressure control system and control method |
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| DE3433896A1 (en) * | 1983-09-14 | 1985-03-28 | Linde Ag, 6200 Wiesbaden | Hydraulic system for a steerable vehicle with battery-supplied electrical drive |
| JPH0291328A (en) * | 1988-09-28 | 1990-03-30 | Hitachi Constr Mach Co Ltd | Hydraulic circuit for self-running working machine |
| JP4548488B2 (en) * | 2008-01-22 | 2010-09-22 | ダイキン工業株式会社 | Merge control system |
| EP2466017A1 (en) * | 2010-12-14 | 2012-06-20 | Caterpillar, Inc. | Closed loop drive circuit with open circuit pump assist for high speed travel |
| CN102229328B (en) * | 2011-05-05 | 2013-05-08 | 四川大学 | Vehicle mechanical energy-saving hydraulic system with multi-pump confluence |
| JP2013079552A (en) * | 2011-10-05 | 2013-05-02 | Komatsu Ltd | Work vehicle |
| CN103882897A (en) * | 2012-12-20 | 2014-06-25 | 青岛鲁达工程机械制造有限公司 | Loader hydraulic system |
| CN103883571B (en) * | 2013-12-18 | 2016-05-25 | 广西柳工机械股份有限公司 | The many pumps of loading machine electrichydraulic control are the hydraulic system at interflow quantitatively |
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Effective date of registration: 20200629 Address after: No.588 Yancheng South Road, Wujin high tech Zone, Changzhou City, Jiangsu Province Patentee after: Liugong (Changzhou) Mining Machinery Co.,Ltd. Address before: 545007 the Guangxi Zhuang Autonomous Region Liuzhou City Liu Tai Road No. 1 Patentee before: GUANGXI LIUGONG MACHINERY Co.,Ltd. |
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Effective date of registration: 20240723 Address after: No. 588 Yancheng South Road, Wujin High tech Industrial Development Zone, Changzhou City, Jiangsu Province, China 213000 Patentee after: LIUGONG CHANGZHOU MACHINERY Co.,Ltd. Country or region after: China Address before: No. 588 Yancheng South Road, Wujin High tech Zone, Changzhou City, Jiangsu Province, China 213168 Patentee before: Liugong (Changzhou) Mining Machinery Co.,Ltd. Country or region before: China |