CN104806588A - Two-pump confluence hydraulic control system - Google Patents
Two-pump confluence hydraulic control system Download PDFInfo
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- CN104806588A CN104806588A CN201510152107.2A CN201510152107A CN104806588A CN 104806588 A CN104806588 A CN 104806588A CN 201510152107 A CN201510152107 A CN 201510152107A CN 104806588 A CN104806588 A CN 104806588A
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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
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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
- F15B13/16—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 invention relates to a hydraulic control system and discloses a two-pump confluence hydraulic control system to overcome the defect of large two-pump confluence hydraulic system impact. The system comprises a working hydraulic system, a second hydraulic pump and an electro-hydraulic control unloading valve group. A valve group confluence oil outlet is communicated with a valve group confluence oil inlet through a pipe working system, and a check valve is arranged between the valve group confluence oil inlet and the valve group confluence oil outlet. The oil inlet end of an external control spill valve is communicated with the oil inlet end of the check valve, and an oil outlet of the external control spill valve is communicated with a valve group unloading oil outlet. A solenoid directional valve and a hydraulic operated directional valve are connected in series and are then connected with an external control end of the external control spill valve and the valve group unloading oil outlet. The hydraulic control end of the hydraulic operated directional valve is connected with a pilot valve through a shuttle valve. The control unit comprises a controller and a displacement detection unit, and the electric control end of the solenoid directional valve is connected with a controller. By means of the system, the hydraulic impact of a hydraulic actuator at the stroke terminal can be reduced.
Description
Technical field
The present invention relates to a kind of engineering machinery hydraulic control system, particularly relate to a kind of Dual-pump flow-converging hydraulic control system of two pressure oil-source fuel feeding.
Background technique
The pressure oil-source of the multiple fuel feeding of many engineering machinery, such as there are at least two pressure oil-sources in loader, and one of them steering hydraulic system is used for turning to, another one be hydraulic system of working for equipment as the fuel feeding such as boom cylinder, rotary ink tank.Loader is as the main force of engineering machinery, due to its low price, use simple operation, the advantages such as mobile transition is quick, are widely used in the middle of many construction project, but it exists the shortcomings such as too high oil consumption, excessive discharge amount and fluid easily leak.Along with energy-saving and cost-reducing requirement, saving energy and reduce the cost also gradually by people's extensive concern of loader hydraulic system.The energy consumption of loader hydraulic system is mainly reflected in the volumetric loss of oil hydraulic pump, motor and oil cylinder, the various pressure losses of valve element and pipeline parts, mechanical friction loss of each class component etc.These losses finally can be present in the middle of hydraulic system with the form of heat, the oil temperature of hydraulic system is raised, and higher oil temperature directly can have influence on the performance of hydraulic system component, cause Sealing and sebific duct aging, spool is stuck because of expansion, the oil viscosity that causes due to temperature rise reduces and reveals increases, fluid vaporization formed cavitate, volumetric efficiency reduction etc.Loader operationally, load variations is larger, and most loader hydraulic system is all fixed dilivery hydraulic system in the market, therefore just can there are many spill lossess, off-load loss and restriction loss etc. unavoidably in loader in working cycle process, the temperature rise of loading machine quantitative hydraulic system more than 90% is substantially all because these losses cause, therefore how to reduce the unnecessary loss of hydraulic system, the power saving of research fixed dilivery hydraulic system has great importance.
The hydraulic system of existing loader is generally made up of hydraulic system of working, steering hydraulic system and hydraulic braking system etc., hydraulic system of working is often made up of elements such as working pump, distributing valve, pilot valve, boom cylinder, rotary ink tanks, steering hydraulic system is often made up of elements such as steering pump, pressure-gradient control valve, commutator (flux amplification valve), steering cylinders, and hydraulic braking system is often made up of elements such as brake pump, liquid-filling valve, brake valve, accumulators.At present, most on market loaders still adopts fixed dilivery hydraulic system; Also have quantitatively and variable delivery hydraulic system situation about being combined with each other; Entire variable hydraulic system is almost have employed in high-end loader.Fixed dilivery hydraulic system is compared to variable delivery hydraulic system, it is high that it has degree of normality, good reliability, resistance tocrocking is strong, cost performance advantages of higher, and fixed dilivery hydraulic system can meet the normal operation requirement of loader completely, but fixed dilivery hydraulic system also deposits deficiency in many aspects, bad, the shortcoming such as hydraulic shock is large of controllability as serious in energy loss, composite move operation, system can not be carried out.
One of feature of variable delivery hydraulic system to carry out stepless speed regulation, thus reduce unnecessary energy loss, but the cost of variable system is high, manufacture difficulty is large, system relative complex, the contaminant sensitivity of variable system element to fluid is high, and for middle and low-end market, quantitative system more easily allows user accept than variable system.The use of converging system can realize carrying out multistep speed regulation to system, if the quantity of pump is abundant, the function of multiple pump will more and more close to variable system.Loader is when operation, different operating mode, different work object are to the movement needs of executive component difference all to some extent, therefore it just needs different rate requests, relative to the system of single oil pump feed, converging system can bring more pump delivery to combine, realize more rate request, the energy-saving effect of converging system is more remarkable simultaneously.
Electrohydraulic control technology uses very ripe in industrial hydraulic, and the various production lines, lathe etc. of factory have a wide range of applications.Electrohydraulic control technology roughly can be divided into: the control of magnetic switch type, electrical-liquid control and electro-hydraulic servo control.Magnetic switch type electrohydraulic control technology is the electrohydraulic control technology grown up the earliest, it and Non-follow control, surge control, maneuver autopilot etc. belongs to one in the middle of many hydraulic controls, switching mode controls the function only having out or close, not there is the function of ratio or servo, but its structure is simple, good reliability is the electrohydraulic control technology be widely used the earliest.The implication of electrical-liquid control refers to the output quantity of hydraulic system, as pressure, flow, displacement, speed, rotating speed, acceleration, power, moment etc., can with input control signal as electric current, proportional being controlled such as voltage, the most crucial parts of electro-hydraulic proportional control technology are proportion electro-magnets, it is the converting member of electromechanical, its function is the current signal converting to force or displacement that Proportional Amplifer are exported, electrohydraulic proportion technology relative complex, manufacture cost is relatively high, but industrially have also been obtained many application, in engineering machinery field, the later most loaders of H series as special in card also use electro-hydraulic proportional control technology, the electro-hydraulic proportional reducing valve being displaced through two ends, left and right of main valve controls.The development of electro-hydraulic servo control starts from World War II weaponry, good rapidity is required to control system, dynamic precision and power-weight ratio etc., the end of the year 1940, electrohydraulic servo-controlling system has appeared on aircraft first, through the development of more than 20 years, various electrohydraulic control is come out one after another, electro-hydraulic servo technology reaches its maturity, the turbidity test of electrohydraulic control fluid medium have very harsh requirement, manufacture cost and maintenance cost are costly, system energy consumption is also larger, electro-hydraulic servo technology is widely used unlike electromagnetic hydraulic pressure control technique and electro-hydraulic proportional control technology, in construction machinery hydraulic system, servo techniques is generally used on the displacement control to variable displacement pump.
In existing dual-pump combining hydraulic system, due to the interflow of many pumps, hydraulic system has the feature of large discharge, high pressure, when hydraulic actuating element to run to the terminal of its stroke as hydraulic jack, can cause huge impact.
Summary of the invention
The object of the invention is to impact large shortcoming for existing dual-pump combining hydraulic system and a kind of many pumps combining hydraulic system automatically closing Dual-pump flow-converging function reduction hydraulic shock is provided.
Technological scheme of the present invention is achieved in that provides a kind of Dual-pump flow-converging hydraulic control system, comprise the first oil hydraulic pump, distributing valve, hydraulic actuator, pilot valve, second oil hydraulic pump, hydraulic oil container, first oil hydraulic pump is connected with distributing valve by the road, distributing valve is connected with hydraulic actuator by the road, first oil hydraulic pump through distributing valve to hydraulic actuator fuel feeding, pilot valve is through the commutation action of left pipeline and right pipeline and distributing valve connection control distributing valve, this control system also comprises electrichydraulic control unloading valve group in addition, electrichydraulic control unloading valve group comprises external control relief valve, solenoid directional control valve, control gear, pilot operated directional control valve, valve mix flow filler opening, valve mix flow oil outlet, valve group off-load oil outlet, second oil hydraulic pump is communicated with valve mix flow filler opening by the road, valve mix flow oil outlet is communicated with the interflow filler opening of distributing valve by the road, off-load oil outlet be communicated with hydraulic oil container by the road, there is the one-way valve to valve group oil outlet one-way conduction between valve mix flow filler opening and valve mix flow oil outlet, the oil inlet end of external control relief valve is communicated with the oil inlet end of one-way valve with internal control end, the oil outlet of external control relief valve is communicated with valve group off-load oil outlet, solenoid directional control valve, external control end and the valve group off-load oil outlet of external control relief valve is connected to after pilot operated directional control valve serial connection, the hydraulic control end of pilot operated directional control valve is connected through the left pipeline of shuttle valve and pilot valve and right pipeline, control gear comprises controller and is connected the displacement detector for detecting hydraulic actuator travel position with controller, the automatically controlled end of solenoid directional control valve is connected with controller.In the present invention, the pressure oil of the pumping of the second oil hydraulic pump is delivered to valve mix flow filler opening, when pilot valve has action, 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 made to open conducting, this Time Controller detects the travel position of hydraulic actuator by displacement detector, if the stroke of hydraulic actuator is not in special position, this Time Controller does not send control signal and solenoid directional control valve is in normally closed block state, now the external control end of external control relief valve does not communicate with outside, external control relief valve is also in cut-off state, the hydraulic oil of the second oil hydraulic pump pumping is by valve mix flow filler opening, one-way valve, the hydraulic oil that valve mix flow oil outlet flows to distributing valve and the first oil hydraulic pump collaborates to supply to hydraulic actuator, realize Dual-pump flow-converging to hydraulic actuator fuel feeding, when controller by displacement detector detect the travel position of hydraulic actuator be in special position such as fast close to its stroke end time, this Time Controller sends control signal and makes solenoid directional control valve commutation conducting, the solenoid directional control valve that the hydraulic oil of the external control end of external control relief valve is opened by conducting, pilot operated directional control valve and flow to hydraulic oil container loop from valve group off-load oil outlet, the pressure of the external control end of external control relief valve reduces, external control relief valve commutates and conducting under controlling the effect of end oil pressure within it, the hydraulic oil flowed into from valve mix flow filler opening flows to hydraulic oil container through external control relief valve from valve group off-load oil outlet, realize the off-load of the second oil hydraulic pump hydraulic oil.Off-load is carried out at the hydraulic oil of end-of-travel position to the second oil hydraulic pump pumping of hydraulic actuator, not only energy saving, load simultaneously no matter on hydraulic actuator is much, as long as the travel position of final controlling element reaches desired location, just can carry out off-load, thus the hydraulic shock that reduction hydraulic actuator causes when stroke terminal.
Further, in Dual-pump flow-converging hydraulic control system, electrichydraulic control unloading valve group also comprises pressure regulator valve, and pressure regulator valve is connected between the external control end of external control relief valve and valve mix flow oil outlet, and the hydraulic control end of pressure regulator valve is communicated with the oil outlet end of one-way valve.In this scheme, when the load of hydraulic actuator does not reach setting, pressure regulator valve ends, the external control end of external control relief valve not with turned on outside, external control relief valve is in cut-off state, the hydraulic oil of now the second oil hydraulic pump pumping hydraulic oil through being flowed to distributing valve and the first oil hydraulic pump by valve mix flow filler opening, one-way valve, valve mix flow oil outlet collaborates to supply to hydraulic actuator, realizes Dual-pump flow-converging to hydraulic actuator fuel feeding, when the load of hydraulic actuator reaches the set pressure of pressure regulator valve, the pressure of the hydraulic control end of pressure regulator valve promotes pressure regulator valve commutation, the filler opening of pressure regulator valve and oil outlet conducting, thus make the external control end of external control relief valve and the valve group off-load oil outlet conducting of valve group, the pressure of the external control end of external control relief valve reduces, external control relief valve commutates and conducting under controlling the effect of end oil pressure within it, the hydraulic oil flowed into from valve mix flow filler opening flows to hydraulic oil container through external control relief valve from valve group off-load oil outlet, realize the off-load of the second oil hydraulic pump hydraulic oil, now off-load no matter hydraulic actuator is in the travel position of where, as long as just carry out off-load to the interflow hydraulic oil of the second oil hydraulic pump when its load reaches certain value.
In above-mentioned Dual-pump flow-converging hydraulic control system, the steering cylinder comprising turning control cell and be connected with turning control cell, the second hydraulic jack is connected with turning control cell, and the interflow oil outlet of turning control cell is connected with valve mix flow filler opening by the road.In this scheme, second oil hydraulic pump is as the oil hydraulic pump turned to, when turning to demand, the hydraulic oil of the second oil hydraulic pump pumping preferentially feeds to steering cylinder by turning control cell, when nothing turns to demand, the hydraulic oil that second oil hydraulic pump more send is carried, for collaborating with the first oil hydraulic pump to electrichydraulic control unloading valve group by the interflow oil outlet of turning control cell.
In above-mentioned Dual-pump flow-converging hydraulic control system, hydraulic actuator is hydraulic jack.Whether displacement detector, for detecting the travel position of the piston rod of hydraulic jack, mainly detects piston rod close to complete extended position or close to complete advanced position.
In above-mentioned Dual-pump flow-converging hydraulic control system, hydraulic actuator is two groups of hydraulic jacks, the boom cylinder of such as loader and rotary ink tank, distributing valve is duplex and connects with corresponding two groups of hydraulic jacks, to be that duplex is corresponding be separately connected with distributing valve pilot valve, namely a pilot valve is wherein connected to the hydraulic control two ends of one of them distributing valve by its left and right pipeline, for the control of boom cylinder, an other pilot valve passes through the hydraulic control two ends of its left and right pipeline and another one distributing valve, for the control of rotary ink tank, solenoid directional control valve and pilot operated directional control valve are respectively two, one of them solenoid directional control valve is connected with a pilot operated directional control valve, another one solenoid directional control valve is connected with another one pilot operated directional control valve, solenoid directional control valve after series connection and pilot operated directional control valve are connected in parallel between the external control end of external control relief valve and valve group off-load oil outlet with other one group of solenoid directional control valve of connecting and pilot operated directional control valve, the hydraulic control end of two pilot operated directional control valves connects the left pipeline of a pilot valve and right pipeline each via shuttle valve correspondence, the automatically controlled end of two solenoid directional control valves is connected with controller.In the program two solenoid directional control valves and two pilot operated directional control valves can by a 3-position 4-way O type function solenoid directional control valve and a 3-position 4-way O type function pilot operated directional control valve substitute, 3-position 4-way O type function solenoid directional control valve and 3-position 4-way O type function pilot operated directional control valve are still connected; The automatically controlled end at solenoid valve selector valve two ends is connected with controller, and the two ends hydraulic control end of pilot operated directional control valve connects each via the left pipeline of shuttle valve and corresponding pilot valve and right pipeline.In such scheme, displacement detector is two groups of corresponding travel position detecting two groups of hydraulic jacks respectively.
The beneficial effect that the present invention compared with prior art has: the present invention is by detecting the travel position of hydraulic actuator, when hydraulic actuator runs to desired location, off-load is carried out to the hydraulic oil of the second oil hydraulic pump, reduce reduction hydraulic actuator and produce huge hydraulic shock at its stroke terminal.
Accompanying drawing explanation
Fig. 1 is that the present invention is applied to loader dual-pump combining hydraulic control system principle schematic;
Fig. 2 is the composition schematic diagram that the present invention is applied to electrichydraulic control unloading valve group in loader dual-pump combining hydraulic control system;
Fig. 3 is the another kind composition schematic diagram of electrichydraulic control unloading valve group of the present invention.
Component title and sequence number in figure:
1. steering cylinder, 2. turning control cell, 3. fuel tank, 4. the second oil hydraulic pump, 5. electrichydraulic control unloading valve group, 5-1. first solenoid directional control valve, 5-2. second solenoid directional control valve, 5-3. external control relief valve, 5-4. pressure regulator valve, 5-5. second pilot operated directional control valve, 5-6. first pilot operated directional control valve, 5-7. one-way valve, 6. the first oil hydraulic pump pump, 7. distributing valve, 8. boom cylinder, 9. rotary ink tank, 10. pilot valves, 11. first shuttle valves, 12. second shuttle valves, 13. 3-position 4-way O type function solenoid directional control valves, 14. 3-position 4-way O type function pilot operated directional control valves.
Embodiment
Below in conjunction with accompanying drawing, specific embodiments is described.
The present embodiment is the application on Dual-pump flow-converging hydraulic control system loader, as shown in Figure 1, this hydraulic system comprises the first oil hydraulic pump 6 as working pump, distributing valve 7, boom cylinder 8, rotary ink tank 9, pilot valve 10, there are in distributing valve 7 two commutation main valves, boom cylinder 8 and the rotary ink tank 9 respectively corresponding and wherein main valve that commutates are connected, pilot valves 10 also has two, two pilot valves in pilot valves 10 are connected with corresponding commutation main valve with right pipeline respectively by respective left pipeline, control the commutation action of commutation main valve, thus realize commutation main valve to boom cylinder 8, the expanding-contracting action of rotary ink tank 9.In this hydraulic system, also comprise the second oil hydraulic pump 4, turning control cell 2, the steering cylinder 1 as steering pump, second oil hydraulic pump 4 is all connected with turning control cell 2 by pipeline with steering cylinder 1, controls the flexible of steering cylinder 1 and realize course changing control by turning control cell 2.Turning control cell 2 has an interflow oil outlet 2b, distributing valve group 7 has interflow filler opening 7b, electrichydraulic control unloading valve group 5 has valve mix flow filler opening 5a, valve mix flow oil outlet 5b, valve group off-load oil outlet 5c, wherein collaborate fuel-displaced 2b to be communicated with valve mix flow filler opening 5a by pipeline, interflow filler opening 7b is communicated with valve mix flow oil outlet 5b by pipeline, and valve group off-load oil outlet 5c is communicated with fuel tank 3 by pipeline.
As shown in Figure 2, electrichydraulic control unloading valve group 5 comprises external control relief valve 5-3, pressure regulator valve 5-4, one-way valve 5-7, two solenoid directional control valves, two pilot operated directional control valves, wherein the oil outlet 51b of the first solenoid directional control valve 5-1 is communicated with to be formed with the filler opening 56a of the first pilot operated directional control valve 5-6 and connects, the oil outlet 52b of the second solenoid directional control valve 5-2 is communicated with to be formed with the filler opening 55a of the second pilot operated directional control valve 5-5 and connects, one-way valve 5-7 to be connected between valve mix flow filler opening 5a and valve mix flow oil outlet 5b and to valve mix flow oil outlet 5b direction one-way conduction, the oil inlet end 53a of external control relief valve 5-3 is communicated with the oil inlet end of one-way valve 5-7 with internal control end 53A, the oil outlet end 53b of external control relief valve 5-3 is communicated with valve group off-load oil outlet 5c, the external control end 53B of external control relief valve 5-3 simultaneously with the filler opening 51a of the first solenoid directional control valve 5-1, the filler opening 52a of the second solenoid directional control valve 5-2 is communicated with, the oil outlet 56b of the first pilot operated directional control valve 5-6 is communicated with valve group off-load oil outlet 5c with the oil outlet 55b of the second pilot operated directional control valve 5-5 simultaneously, the filler opening 54a of pressure regulator valve 5-4 is also communicated with the external control end 53B of external control relief valve 5-3, the oil outlet 54b of pressure regulator valve 5-4 is also communicated with valve group off-load oil outlet 5c, the hydraulic control end 54A of pressure regulator valve 5-4 is then communicated with the oil outlet end of one-way valve 5-7, pressure regulator valve 5-4 is normally close valve, when the pressure at its hydraulic control end 54A place is greater than its presetting pressure, the spool commutation of pressure regulator valve 5-4, its oil inlet end 54a to oil outlet end 54b conducting.
As shown in Figure 1, the hydraulic control end 56A of the first pilot operated directional control valve 5-6 join the left pipeline of pilot valve by the first shuttle valve 11 and swing arm in pilot valves 10 and right management is connected, and the distributing valve that the left pipeline that this swing arm joins pilot valve is connected with right pipeline is that the swing arm of control boom cylinder 8 joins distributing valve; The hydraulic control end 55A of the second pilot operated directional control valve 5-5 join the left pipeline of pilot valve by the second shuttle valve 12 and the another one rotating bucket in pilot valves 10 and right pipeline is connected, and the distributing valve that the left pipeline that this rotating bucket joins pilot valve is connected with right pipeline is that the rotating bucket of control rotary ink tank 9 joins distributing valve; First pilot operated directional control valve 5-6 and the second pilot operated directional control valve 5-5 is normally closed selector valve, and when pilot valve having act of operation, the first pilot operated directional control valve 5-6 that connect corresponding to pilot valve or the second pilot operated directional control valve 5-5 commutates and make its conducting.The automatically controlled end of the first solenoid directional control valve 5-1 and the second solenoid directional control valve 5-2 is connected respectively at the different output terminals of controller, signal input part and the detection boom cylinder 8 of controller, the displacement detector of the piston position of-rotary ink tank 9 connects, first solenoid directional control valve 5-1 and the second solenoid directional control valve 5-2 is also normally closed solenoid valve, when displacement detector detects boom cylinder 8, when the piston rod of-rotary ink tank 9 stretches out or retracts to predeterminated position such as close to end-of-travel position, the solenoid directional control valve that controller is corresponding in the first solenoid directional control valve 5-1 and the second solenoid directional control valve 5-2 exports controlling potential signal, corresponding solenoid directional control valve is made to carry out commutating and making its conducting.
In the present embodiment, to realize principle as follows in the action of loader dual-pump combining hydraulic system:
When steering system has demand, the second oil hydraulic pump 4 draws hydraulic oil by the filler opening 2a of turning control cell and enters steering cylinder 1 by its hydraulic fluid port 2c or hydraulic fluid port 2d from fuel tank 3, realizes the go to action of machine.The interflow filler opening 7b that the unnecessary fluid of steering system enters distributing valve group 7 through the interflow oil outlet 2b to the valve mix flow filler opening 5a of electrichydraulic control unloading valve group 5 of turning control cell and valve mix flow oil outlet 5b collaborates in the middle of hydraulic system of working.
The hydraulic pressure oil content two-way of electrichydraulic control unloading valve group 5, the one-way valve 5-7 of a road through its inside arrives valve mix flow oil outlet 5b and enters hydraulic system of working, one tunnel arrives the filler opening 53a of external control relief valve 5-3 and acts on its internal control end 53A, the external control end 53B of external control relief valve 5-3 is connected with the oil inlet end 54a of pressure regulator valve 5-4, when produce from hydraulic system of working pressure make every effort to overcome the pressure adjusting spring taking pressure regulator valve 5-4 pressure regulator valve 5-4 is commutated make oil inlet end 54a and the oil outlet end 54b conducting of pressure regulator valve 5-4 time, the fluid of the external control end 53B of external control relief valve 5-3 arrives valve group off-load oil outlet 5c through the oil inlet end 54a of pressure regulator valve 5-4 and oil outlet end 54b, valve group off-load oil outlet 5c mouth communicates with fuel tank 3, the fluid off-load of the external control end 53B of external control relief valve 5-3, now one-way valve 5-7 closes, the filler opening 53a of external control relief valve 5-3 and oil outlet 53b conducting, the fluid flowed out from turning control cell 2 is through the filler opening 53a of external control relief valve 5-3 and oil outlet 53b, valve group off-load oil outlet 5c flows back to fuel tank 3, realize the fluid Low-pressure load discharge of the second oil hydraulic pump.In this unloading process, have nothing to do with the travel position of the hydraulic actuator such as boom cylinder 8, rotary ink tank 9, only relevant with the load on these hydraulic actuators.
When the swing arm of operated pilot valve group 10 joins pilot valve, pilot pressure oil controls the action of swing arm connection commutation main valve plug in distributing valve group 7 through its left pipeline and right pipeline, as long as swing arm connection pilot valve has pressure, the hydraulic control end 56A that this pilot pressure can arrive the first pilot operated directional control valve 5-6 through the first shuttle valve 11 makes the first pilot operated directional control valve 5-6 to commutate conducting, if now the piston rod of boom cylinder stretches special position such as close to the position of its stroke end, after displacement detector detects this state, controller sends automatically controlled signal to the automatically controlled end 2YA of the first solenoid directional control valve 5-1 and makes its conducting that commutates, the fluid of the external control end 53B of external control relief valve 5-3 is through the first solenoid directional control valve 5-1, first pilot operated directional control valve 5-6 arrives valve group off-load oil outlet 5c and communicates with fuel tank 3, the fluid off-load of the external control end 53B of external control relief valve 5-3, now closed check valve, external control relief valve 5-3 conducting, the hydraulic oil of coming from turning control cell flows back to fuel tank through external control relief valve 5-3, realize the second oil hydraulic pump fluid Low-pressure load discharge.In like manner, when the rotating bucket of operated pilot valve group 10 joins, the Stress control of pilot pressure oil the action of distributing valve group 7 rotating bucket connection spool, as long as rotating bucket connection pilot valve has pressure, the hydraulic control end 55A that this pilot pressure can arrive the second pilot operated directional control valve 5-5 through the second shuttle valve 12 makes pilot operated directional control valve 5-5 commutate, if now the piston rod of rotary ink tank stretches special position such as close to the position of its stroke end, after displacement detector detects this state, controller sends automatically controlled signal to the automatically controlled end 1YA of the second solenoid directional control valve 5-2 and makes its conducting that commutates, the fluid of the external control end 53B of external control relief valve 5-3 is through the second solenoid directional control valve 5-2, second pilot operated directional control valve 5-5 arrives valve group off-load oil outlet 5c and communicates with fuel tank 3, the fluid off-load of the external control end 53B of external control relief valve 5-3, now one-way valve 5-7 closes, external control relief valve 5-3 conducting, the hydraulic oil of coming from turning control cell flows back to fuel tank through external control relief valve 5-3, realize the second oil hydraulic pump fluid Low-pressure load discharge.In this unloading process, the load of the fluid of the second oil hydraulic pump whether off-load and hydraulic actuator has nothing to do, only relevant to the travel position of hydraulic actuator, this measure can carry out off-load to the second oil hydraulic pump fluid at hydraulic actuator near its end-of-travel position, reduces the hydraulic shock of hydraulic actuator at its stroke terminal.
In this hydraulic system, when the load of rotary ink tank 9 or boom cylinder 8 is less than the set pressure of pressure regulator valve 5-4, the piston rod of boom cylinder 8 and rotary ink tank is not in specific travel position, external control relief valve 5-3 is in closedown and blocks state, flows to distributing valve group realize collaborating with the fluid of the first oil hydraulic pump 6 from the second oil hydraulic pump fluid that turning control cell stream is next through one-way valve 5-7.
In the hydraulic system shown in Fig. 1 Fig. 2, in electrichydraulic control unloading valve group 5, the first solenoid directional control valve 5-1 and the first pilot operated directional control valve 5-6 connects, and becomes swing arm linkage control valve group; Second solenoid directional control valve 5-2 and the second pilot operated directional control valve 5-5 connects, and becomes 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 between the external control end 53B of external control relief valve 5-3 and valve group off-load oil outlet 5c, can realize controlling the fluid off-load of the second oil hydraulic pump and not interfereing with each other separately, also can form the control mode of combination.
When the piston rod movement of boom cylinder 8 is to during close to limit position, the fluid of the second oil hydraulic pump is in setting displacement place off-load, if now unclamp swing arm connection pilot valve handle, then the hydraulic control end 56A fluid of the first pilot operated directional control valve 5-6 can be linked to through the swing arm of the first shuttle valve 11 and pilot valves the oil outlet reaching pilot valves and communicates with fuel tank, first pilot operated directional control valve 5-6 resets under the effect of left end spring force, cut off the passage of external control end 53B to fuel tank 3 of external control relief valve 5-3, unloading function disappears, the fluid of the second oil hydraulic pump enters hydraulic system of working through one-way valve 5-7, for the next action of work system prepares enough fluid.When rotary ink tank moves to limit position, release handle, the action of electrichydraulic control unloading valve group 5 and above-mentioned similar.
In the above-described embodiment, first pilot operated directional control valve and the second pilot operated directional control valve can substitute with a 3-position 4-way O type function pilot operated directional control valve 14, first solenoid directional control valve and the second solenoid directional control valve can use a 3-position 4-way O type function solenoid directional control valve 13 to replace, as shown in Figure 3, 3-position 4-way O type function pilot operated directional control valve is connected to after connecting with 3-position 4-way O type function solenoid directional control valve between external control relief valve 5-3 and valve group off-load oil outlet 5c, the automatically controlled end in two ends of 3-position 4-way O type function solenoid directional control valve 13 is connected with controller, the two ends hydraulic control end of 3-position 4-way O type function pilot operated directional control valve 14 joins pilot valve and swing arm through corresponding shuttle valve and rotating bucket separately and joins the left pipeline of pilot valve and right pipeline is connected, the function of hydraulic system in schematic diagram in above-mentioned Fig. 1 Fig. 2 can be realized equally.
Claims (7)
1. a Dual-pump flow-converging hydraulic control system, comprise the first oil hydraulic pump, distributing valve, hydraulic actuator, pilot valve, second oil hydraulic pump, hydraulic oil container, described first oil hydraulic pump is connected with distributing valve by the road, described distributing valve is connected with hydraulic actuator by the road, described first oil hydraulic pump through distributing valve to hydraulic actuator fuel feeding, described pilot valve is through the commutation action of left pipeline and right pipeline and distributing valve connection control distributing valve, characterized by further comprising electrichydraulic control unloading valve group, described electrichydraulic control unloading valve group comprises external control relief valve (5-3), solenoid directional control valve (5-1), control gear, pilot operated directional control valve (5-6), valve mix flow filler opening (5a), valve mix flow oil outlet (5b), valve group off-load oil outlet (5c), described second oil hydraulic pump is communicated with valve mix flow filler opening (5a) by the road, valve mix flow oil outlet (5b) is communicated with the interflow filler opening of distributing valve by the road, off-load oil outlet (5c) be communicated with hydraulic oil container by the road, there is the one-way valve to valve group oil outlet (5b) one-way conduction between valve mix flow filler opening (5a) and valve mix flow oil outlet (5b), the oil inlet end (53a) of described external control relief valve (5-3) is communicated with the oil inlet end of described one-way valve with internal control end (53A), the oil outlet of described external control relief valve (5-3) is communicated with valve group off-load oil outlet (5c), described solenoid directional control valve (5-1), external control end (53B) and valve group off-load oil outlet (5c) of described external control relief valve (5-3) is connected to after pilot operated directional control valve (5-6) serial connection, the hydraulic control end (56A) of pilot operated directional control valve (5-6) is connected through the left pipeline of shuttle valve and described pilot valve and right pipeline, described control gear comprises controller and is connected the displacement detector for detecting hydraulic actuator travel position with controller, the automatically controlled end of described solenoid directional control valve (5-1) is connected with controller.
2. Dual-pump flow-converging hydraulic control system according to claim 1, it is characterized in that described electrichydraulic control unloading valve group also comprises pressure regulator valve (5-4), between the external control end (53B) that described pressure regulator valve is connected to described external control relief valve (5-3) and valve mix flow oil outlet (5b), the hydraulic control end (54A) of described pressure regulator valve is communicated with the oil outlet end of described one-way valve.
3. Dual-pump flow-converging hydraulic control system according to claim 1 and 2, the steering cylinder that characterized by further comprising turning control cell and be connected with turning control cell, described second hydraulic jack is connected with described turning control cell, and the interflow oil outlet of described turning control cell is connected with described valve mix flow filler opening (5a) by the road.
4. Dual-pump flow-converging hydraulic control system according to claim 1 and 2, is characterized in that described hydraulic actuator is hydraulic jack.
5. Dual-pump flow-converging hydraulic control system according to claim 4, it is characterized in that described hydraulic actuator is two groups of hydraulic jacks, described distributing valve is duplex and connects with corresponding two groups of hydraulic jacks, to be that duplex is corresponding be separately connected with described distributing valve described pilot valve, described solenoid directional control valve and pilot operated directional control valve are respectively two, one of them solenoid directional control valve is connected with a pilot operated directional control valve, another one solenoid directional control valve is connected with another one pilot operated directional control valve, solenoid directional control valve after series connection and pilot operated directional control valve are connected in parallel between the external control end of described external control relief valve and valve group off-load oil outlet with other one group of solenoid directional control valve of connecting and pilot operated directional control valve, the hydraulic control end of described two pilot operated directional control valves connects left pipeline and the oil pipe line of a pilot valve each via shuttle valve correspondence, the automatically controlled end of described two solenoid directional control valves is connected with described controller.
6. Dual-pump flow-converging hydraulic control system according to claim 4, it is characterized in that described hydraulic actuator is two groups of hydraulic jacks, described distributing valve is duplex and connects with corresponding two groups of hydraulic jacks, to be that duplex is corresponding be separately connected with described distributing valve described pilot valve, and described solenoid valve selector valve is 3-position 4-way O type function solenoid directional control valve; Described pilot operated directional control valve is 3-position 4-way O type function pilot operated directional control valve; The automatically controlled end of described solenoid valve selector valve is connected with described controller, and the two ends hydraulic control end of described pilot operated directional control valve connects each via the left pipeline of shuttle valve and corresponding pilot valve and right pipeline.
7. the Dual-pump flow-converging hydraulic control system according to claim 5 or 6, is characterized in that described displacement detector is two groups of corresponding travel position detecting two groups of hydraulic jacks respectively.
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Cited By (10)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN105114687A (en) * | 2015-08-19 | 2015-12-02 | 江苏大学 | Hydraulic control system for controlling opening and closing of multiple hydraulic butterfly valves |
| CN105110192A (en) * | 2015-07-31 | 2015-12-02 | 徐州徐工液压件有限公司 | Confluence control device of hydraulic crane |
| CN105350598A (en) * | 2015-10-21 | 2016-02-24 | 徐工集团工程机械股份有限公司科技分公司 | Hydraulic control system for improving energy saving performance of loader and control method of hydraulic control system |
| CN105465088A (en) * | 2015-12-22 | 2016-04-06 | 徐州徐工液压件有限公司 | Automatic multi-way-valve non-confluent adaptation device |
| CN106351909A (en) * | 2016-08-30 | 2017-01-25 | 徐州重型机械有限公司 | Confluent switching system with multiple oil supply units |
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| CN112012969A (en) * | 2020-08-27 | 2020-12-01 | 广西柳工机械股份有限公司 | Hydraulic system and loader |
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Citations (8)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| 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 |
| CN101910646A (en) * | 2008-01-22 | 2010-12-08 | 大金工业株式会社 | Confluent control system |
| CN102229328A (en) * | 2011-05-05 | 2011-11-02 | 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 |
| US20140020370A1 (en) * | 2010-12-14 | 2014-01-23 | Torsten Berg | Closed loop drive circuit with open circuit pump assist for high speed travel |
| 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 |
| CN103883571A (en) * | 2013-12-18 | 2014-06-25 | 广西柳工机械股份有限公司 | Electrohydraulic control multi-pump quantitive confluence hydraulic system for loading machines |
-
2015
- 2015-04-01 CN CN201510152107.2A patent/CN104806588B/en active Active
Patent Citations (8)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| 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 |
| CN101910646A (en) * | 2008-01-22 | 2010-12-08 | 大金工业株式会社 | Confluent control system |
| US20140020370A1 (en) * | 2010-12-14 | 2014-01-23 | Torsten Berg | Closed loop drive circuit with open circuit pump assist for high speed travel |
| CN102229328A (en) * | 2011-05-05 | 2011-11-02 | 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 |
| CN103883571A (en) * | 2013-12-18 | 2014-06-25 | 广西柳工机械股份有限公司 | Electrohydraulic control multi-pump quantitive confluence hydraulic system for loading machines |
Cited By (15)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| 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 |
| CN105110192A (en) * | 2015-07-31 | 2015-12-02 | 徐州徐工液压件有限公司 | Confluence control device of hydraulic crane |
| CN105114687A (en) * | 2015-08-19 | 2015-12-02 | 江苏大学 | Hydraulic control system for controlling opening and closing of multiple hydraulic butterfly valves |
| CN105350598A (en) * | 2015-10-21 | 2016-02-24 | 徐工集团工程机械股份有限公司科技分公司 | Hydraulic control system for improving energy saving performance of loader and control method of 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 |
| CN105465088A (en) * | 2015-12-22 | 2016-04-06 | 徐州徐工液压件有限公司 | Automatic multi-way-valve non-confluent adaptation device |
| CN106351909A (en) * | 2016-08-30 | 2017-01-25 | 徐州重型机械有限公司 | Confluent switching system with multiple oil supply units |
| 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 |
| CN110486341A (en) * | 2018-05-14 | 2019-11-22 | 博世力士乐（北京）液压有限公司 | Hydraulic control system and mobile working equipment |
| 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 |
| CN112012969A (en) * | 2020-08-27 | 2020-12-01 | 广西柳工机械股份有限公司 | Hydraulic system and loader |
| CN114087249A (en) * | 2021-11-18 | 2022-02-25 | 国能神东煤炭集团有限责任公司 | Electro-hydraulic pressure control system and control method |
| 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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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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