CN105156391A - Composite variable pump and hydraulic control system using composite variable pump - Google Patents
Composite variable pump and hydraulic control system using composite variable pump Download PDFInfo
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Abstract
The invention discloses a variable pump with load sensitive throttle control and volume control functions and a hydraulic control system using the composite variable pump. The composite variable pump comprises a shell, a pump body, a variable control hydrocylinder and an electromagnetic proportioning valve, wherein the electromagnetic proportioning valve is connected with a displacement valve in parallel; a constant-pressure control valve is connected between an oil outlet of the pump body and the electromagnetic proportioning valve; a flow control valve is connected between the oil outlet of the pump body and the constant-pressure control valve; and a control side of the flow control valve is connected with a load feedback oil port X. The hydraulic control system using the composite variable pump comprises a controller, the composite variable pump, a plurality of hydraulic actuating elements and a plurality of load sensitive valves. The composite hydraulic pump can enable the system to work in the volume control mode or load sensitive throttle control mode; the actions of the actuating mechanisms do not interfere with each other; and thus, the system has the advantages of higher efficiency and more energy saving.
Description
Technical field
The present invention relates to technical field of hydraulic, specifically a kind of variable displacement pump merging load-sensitive throttling control and volumetric void fraction function, and a kind of hydraulic control system having used the utilization composite variable pump of this variable displacement pump.
Background technique
Along with the progress of equipment manufacturing technology, main frame is more and more higher to the requirement of hydraulic system in lightweight, energy utilization efficiency, multi-execution component composition operation etc.In current hydraulic system, variable displacement pump volume control system and load-sensitive throttle control system are widely used due to self advantage unique separately.
Typical variable displacement pump volume control system principle as shown in Figure 1.The oil suction from fuel tank 10 of electricity Electro-hydraulic Proportional Displacement pump 20, supply solenoid directional control valve 30.The control signal of the controlled device 50 of solenoid directional control valve 30 carries out switch motion.When oil hydraulic cylinder 40 does not need action, solenoid directional control valve 30 cuts out by controller I 50, simultaneously by the discharge capacity vanishing of electric Electro-hydraulic Proportional Displacement pump 20.When oil hydraulic cylinder 40 needs action, solenoid directional control valve 30 is opened by controller I 50, needs the discharge capacity of electric Electro-hydraulic Proportional Displacement pump 20 to be adjusted to suitable size by system simultaneously.The displacement variation of electricity Electro-hydraulic Proportional Displacement pump 20 just controls the velocity magnitude of oil hydraulic cylinder.Because whether and direction solenoid directional control valve 30 only plays controlled motion, do not have throttling action, so the pressure loss in volume control system from delivery side of pump to executive component is less, the energy utilization efficiency of system is higher.
But variable displacement pump volume control system exists a shortcoming, any instant, pump can only the executive component of a corresponding job, and in other words, for multiple executive component composite move, each executive component needs an independent pump to control.When there is multiple executive component, needing multiple oil hydraulic pump, adding Design and manufacture cost.
Typical load-sensitive throttle control system principle as shown in Figure 2.High pressure oil, from oil suction in fuel tank 100, is given load-sensitive valve I 300 and load-sensitive valve II 400 by load sensitive pump 200 respectively.Load-sensitive valve I 300 and load-sensitive valve II 400 hydraulic control cylinder I 600 and oil hydraulic cylinder II 700(executive component respectively).The effect of shuttle valve 500 is compared by the maximum load pressure signal of two oil hydraulic cylinders, and by larger signal transmission to load-sensitive 200 pump.Controller II 800 is for needing aperture and the direction of control load sensitive valve according to system.Load sensitive pump 200 is built-in with flow control valve.Flow control valve can regulate the pressure of pump only to exceed a steady state value set than load.Thus, relative general measure pump relief valve loop, load sensitive system can reduce energy dissipation.The load-sensitive valve used in load sensitive system, can control the aperture of fluid direction and valve port as the Proportional valve of routine according to the electrical signal of controller.Meanwhile, load-sensitive valve inside is integrated with for making the pressure-compensated valve that before and after corresponding valve port, pressure reduction is constant.This constant pressure reduction for ensure valve port through-current capacity only and valve port flow area be directly proportional, and the pressure reduction that the flow control valve that this pressure reduction is less than pump inside sets.Like this, load sensitive system has just possessed the action of each executive component not by the impact of respective different loads size.
In fact, hydraulic system is not be operated in multiple actuator when working always simultaneously.Many times, hydraulic system Jin Youyige actuator is in work.When only there is actuator's motion in system, to influence each other the problem of speed with regard to there is not multiple executive component.But now pressure-compensated valve still works, the pressure reduction before and after selector valve is kept to be a steady state value.At this moment, the flow control valve that load sensitive pump 200 is built-in also makes the pressure of pump discharge and load keep a steady state value.In this case, pressure-compensated valve and the built-in flow control valve of pump just constitute dual compensation, and in other words, pressure-compensated valve becomes the element of unnecessary waste energy.
The oil hydraulic pump that load-sensitive throttling control and volumetric void fraction advantage are merged in design is a problem being worth research.
Summary of the invention
In order to overcome above-mentioned the deficiencies in the prior art, the invention provides the hydraulic control system of a kind of composite variable pump and utilization composite variable pump.
The present invention is achieved through the following technical solutions: a kind of composite variable pump, comprises housing, the electromagnetic proportional valve of two-position three way being positioned at the pump body of housing, the Variable Control oil cylinder be connected with pump body and being connected with Variable Control oil cylinder; Described housing is provided with the B hydraulic fluid port connecting pump body oil outlet, connects the S hydraulic fluid port of pump body filler opening, connects the load feedback hydraulic fluid port X of external feedback oil circuit; Described electromagnetic proportional valve hydraulic fluid port P is connected to pump body oil outlet, and electromagnetic proportional valve hydraulic fluid port A is connected to Variable Control oil cylinder oil pocket;
The displacement valves of bi-bit bi-pass is connected with between described electromagnetic proportional valve hydraulic fluid port P and electromagnetic proportional valve hydraulic fluid port A;
The constant-pressure control valve of bi-bit bi-pass is connected with between described pump body oil outlet B and electromagnetic proportional valve hydraulic fluid port T;
The flow control valve of bi-bit bi-pass is connected with between described pump body oil outlet B and constant-pressure control valve; Described flow control valve one controls side and connects load feedback hydraulic fluid port X.
It is further: described pump body is provided with swash plate; Described swash plate one end is connected to the tailpiece of the piston rod of Variable Control oil cylinder; Described Variable Control oil cylinder is provided with feedback rod, and the other end of feedback rod is connected with the valve pocket of described electromagnetic proportional valve; Variable Control cylinder piston rod overlaps the Returnning spring having control piston bar to retract.
Described housing has and leaks hydraulic fluid port L.
Use a hydraulic control system for the utilization composite variable pump of described composite variable pump, comprise controller, composite variable pump, multiple hydraulic actuator and multiple load-sensitive valve; Electromagnetic proportional valve and displacement valves in described controller control connection composite variable pump, and load-sensitive valve; Described load-sensitive valve number is identical with hydraulic actuator number, and load-sensitive valve to be connected in hydraulic actuator and composite variable pump between hydraulic fluid port B; Described multiple load-sensitive valve oil outlet pressure is by being connected to load feedback hydraulic fluid port X in composite variable pump after multiple shuttle valve; In described composite variable pump, hydraulic fluid port S and hydraulic fluid port L is connected to fuel tank.
The principle of the invention is: when only having a hydraulic actuator job in hydraulic system, open to maximum open by the load-sensitive valve in hydraulic system, composite variable pump is in rate variable mode of operation, and namely system is volumetric void fraction pattern.The flow of control system is carried out by controlling pump delivery, and then the operating rate of hydraulic control executive component.When there being multiple hydraulic actuator to work in hydraulic system simultaneously, composite variable pump is in load-sensitive mode of operation, and namely system is load-sensitive throttling control mode.No matter several hydraulic actuator is in work, when the working pressure of composite variable pump exceedes certain pressure, discharge capacity reduces by composite variable pump under the effect of constant-pressure control valve, avoids spill losses.Meanwhile, above-mentioned all switchings are carried out automatically.
In addition, in case of need, can, by the effect of displacement valves, composite variable pump delivery be made to become minimum injection rate with the fastest speed.
Compared with prior art, the invention has the beneficial effects as follows: for the hydraulic system of multi-execution component, when the action of Jin Youyige actuator, multiple hydraulic pump can make system works in volumetric void fraction pattern, and system effectiveness can be made higher, more energy-conservation.When there being multiple actuator to work simultaneously, multiple hydraulic pump makes hydraulic system become load-sensitive throttling control mode, ensures that the action between multiple actuator does not interfere with each other.Meanwhile, in case of need, or when the working pressure of multiple hydraulic pump exceedes certain value, the discharge capacity of multiple hydraulic pump can be become minimum, ensure the safety of system.
Accompanying drawing explanation
Fig. 1 is the typical variable displacement pump volume control system hydraulic schematic diagram described in background technique;
Fig. 2 is the typical load-sensitive throttle control system hydraulic schematic diagram described in background technique;
Fig. 3 is a kind of composite variable pump hydraulic schematic diagram of the present invention;
Fig. 4 is that the present invention uses the fundamental diagram of the hydraulic control system of composite variable pump when only having a hydraulic actuator job; In figure, workless hydraulic actuator omits;
Fig. 5 is the detailed schematic diagram of electromagnetic proportional valve when equilibrium position in the present invention;
Fig. 6 is that the present invention uses the fundamental diagram of the hydraulic control system of composite variable pump when multiple hydraulic actuator works simultaneously; Two hydraulic actuators are only drawn as signal in figure;
Fig. 7 is the fundamental diagram that the present invention enters Isobarically Control when increasing discharge capacity under volumetric void fraction pattern;
Fig. 8 is the fundamental diagram that the present invention enters Isobarically Control when being stabilized in a certain discharge capacity under volumetric void fraction pattern;
Fig. 9 is the fundamental diagram that the present invention enters Isobarically Control when reducing discharge capacity under volumetric void fraction pattern;
Figure 10 is the fundamental diagram that the present invention enters Isobarically Control under load-sensitive throttling control mode;
The fundamental diagram of Figure 11 when to be the present invention use displacement valves control pump discharge capacity to become minimum when needing arbitrarily.
In Fig. 3 to Figure 11: 1, pump body; 2, swash plate; 3, Returnning spring; 4, Variable Control oil cylinder; 5, feedback rod; 6, electromagnetic proportional valve; 7, constant-pressure control valve; 8, flow control valve; 9, displacement valves; 101, housing; 11, load-sensitive valve II; 12, shuttle valve; 13, hydraulic actuator II; 14, hydraulic actuator I; 15, controller; 16, load-sensitive valve I.
Embodiment
Be below a specific embodiment of the present invention, existing the invention will be further described by reference to the accompanying drawings.
As shown in Figure 3, a kind of composite variable pump, comprises pump body 1, Variable Control oil cylinder 4, electromagnetic proportional valve 6, displacement valves 9, constant-pressure control valve 7 and flow control valve 8; The electromagnetic proportional valve 6 hydraulic fluid port P of two-position three way is connected to pump body 1 oil outlet, and electromagnetic proportional valve 6 hydraulic fluid port A is connected to Variable Control oil cylinder 4 oil pocket; The displacement valves 9 hydraulic fluid port P of bi-bit bi-pass is connected to pump body 1 oil outlet, and displacement valves 9 hydraulic fluid port A is connected to Variable Control oil cylinder 4 oil pocket; The constant-pressure control valve 7 hydraulic fluid port P of bi-bit bi-pass is connected to pump body 1 oil outlet, and constant-pressure control valve 7 hydraulic fluid port A is connected to electromagnetic proportional valve 6 hydraulic fluid port T, and the left control side of constant-pressure control valve 7 is connected to pump body 1 oil outlet; The flow control valve 8 hydraulic fluid port P of bi-bit bi-pass and left control side are to pump body 1 oil outlet, and flow control valve 8 hydraulic fluid port A is connected to constant-pressure control valve 7 hydraulic fluid port T, and the right control side of flow control valve 8 is connected to load feedback hydraulic fluid port X.Pump body 1 is provided with swash plate 2, swash plate 2 one end is connected to the tailpiece of the piston rod of Variable Control oil cylinder 4, and Variable Control oil cylinder 4 side-to-side movement promotes swash plate 2 and swings; Variable Control oil cylinder 4 is provided with feedback rod 5, and the other end of feedback rod 5 is connected with the valve pocket of electromagnetic proportional valve 6, and the valve pocket this achieving electromagnetic proportional valve 6 is consistent with the motion of Variable Control oil cylinder 4; The Returnning spring 3 that Variable Control oil cylinder 4 upper cover of piston rod has control piston bar to retract.Above-mentioned parts are all arranged on housing 101, and housing 101 is provided with the B hydraulic fluid port connecting pump body 1 oil outlet, connect the S hydraulic fluid port of pump body 1 filler opening, connect the load feedback hydraulic fluid port X of external feedback oil circuit and leak hydraulic fluid port L.
Pump body 1 from hydraulic fluid port S oil suction, and can be discharged by fuel-displaced B mouth, completes mechanical energy to pressure transformation of energy simultaneously.Hydraulic fluid port S is connected with hydraulic oil container, and its effect is that fluid can be sucked in the pump housing by this hydraulic fluid port by oil hydraulic pump.Swash plate 2 can rotate to an angle around own axes.The size of swash plate 2 angle and the size one_to_one corresponding of pump delivery.Returnning spring 3 can when air pump inoperative, and in Variable Control oil cylinder 4, piston is parked in low order end, i.e. the maximum position of corresponding pump delivery.
As shown in Figure 6, a kind of hydraulic control system using the utilization composite variable pump of composite variable pump, comprises controller 15, composite variable pump, multiple hydraulic actuator and multiple load-sensitive valve; Electromagnetic proportional valve 6 and displacement valves 9 in controller 15 control connection composite variable pump, and load-sensitive valve; Load-sensitive valve number is identical with hydraulic actuator number, and load-sensitive valve to be connected in hydraulic actuator and composite variable pump between hydraulic fluid port B; Multiple load-sensitive valve oil outlet pressure is by being connected to load feedback hydraulic fluid port X in composite variable pump after multiple shuttle valve 12; In composite variable pump, hydraulic fluid port S and hydraulic fluid port L is connected to fuel tank.
One, suppose that induced pressure does not reach the setting pressure of constant-pressure control valve 7, namely constant-pressure control valve 7 is in the work of position shown in Fig. 4.
When only an actuator works, controller sends signal to corresponding load-sensitive valve.As shown in Figure 4, other executive component not having action and associated loop are eliminated in figure.Controller 15 gives load-sensitive valve 16 with maximum controlling current, this valve valve port standard-sized sheet.Now, the pressure-compensated valve also standard-sized sheet that load-sensitive valve 16 is built-in, therefore whole load-sensitive valve only plays direction controlling effect, the expanding-contracting action of hydraulic control cylinder 14, without throttling action, the pressure loss is very little.Because the front and back pressure loss of load-sensitive valve 16 is little, thus the pressure of pump discharge and load feedback pressure very close, therefore the flow control valve 8 of pump works in right position all the time under the effect of right side spring, i.e. A to the T mouth standard-sized sheet of this valve, P to A mouth is closed completely.The action speed of oil hydraulic cylinder 14 is only determined by the flow of load-sensitive valve 16, namely the output flow of pump, i.e. pump delivery size.The electric current that pump delivery size exports to electromagnetic proportional valve 6 by controller 15 determines.System stability work time, electromagnetic proportional valve 6 stable operation under equilibrium position, as shown in Figure 5.Pump delivery size is directly proportional to the control electric current of electromagnetic proportional valve 6.Concrete multivariable process is as follows:
1) discharge capacity becomes large change procedure.Electromagnetic proportional valve 6 obtains certain current signal, and electromagnet promotes spool and moves right, and P mouth and the A mouth of valve are closed gradually, and A mouth and T mouth are opened gradually.Part fluid in cavity on the right side of Variable Control oil cylinder 4 is flowed out by A to the T mouth of electromagnetic proportional valve 6, and through constant-pressure control valve 7, flow control valve 8, the housing 10 of inflow pump, finally, through L mouth oil sump tank.Variable Control oil cylinder 4 moves right under the effect of left side Returnning spring 3, and pump delivery becomes large gradually.Meanwhile, feedback rod 5 also moves right under the drive of Variable Control oil cylinder 4, thus the valve pocket dragging electromagnetic proportional valve 6 moves right, therefore, A to the T mouth of electromagnetic proportional valve 6 turns down gradually, until Variable Control oil cylinder 4 is stabilized in a fixed position, electromagnetic proportional valve 6 reaches new equilibrium position.Now, pump delivery also just stabilizes.The process that Here it is pump delivery increases along with control signal and increases.
2) change procedure that diminishes of discharge capacity.When the electric current that controller 15 exports to electromagnetic proportional valve 6 reduces, the power of electromagnet reduces, and spool is to left movement under the effect of right side spring, and P mouth and the A mouth of valve are opened gradually, and A mouth and T mouth are closed gradually.The high-voltage oil liquid of pump discharge is by the cavity on the right side of electromagnetic proportional valve 6 entering variable control oil cylinder 4.Variable Control oil cylinder 4 compression reseting spring 3 is moved to the left, and pump delivery reduces gradually.Meanwhile, feedback rod 5 is also moved to the left under the drive of Variable Control oil cylinder 4, thus the valve pocket of dragging electromagnetic proportional valve 6 is to left movement, therefore, P to the A mouth of electromagnetic proportional valve 6 turns down gradually, until Variable Control oil cylinder 4 is stabilized in a fixed position, electromagnetic proportional valve 6 reaches new equilibrium position.Now, pump delivery also just stabilizes.The process that Here it is pump delivery reduces along with control signal and reduces.
Known by above analysis, now system is a volume control system.Like this, just higher energy utilization efficiency can be obtained.Meanwhile, this working principle is all effective for any one executive component in system.
When there being multiple executive component (only depicting two oil hydraulic cylinders in figure as signal) work in hydraulic system, controller 15 exports maximum controlling current to electromagnetic proportional valve 6, the power of electromagnet is made to be greater than spring force on the right side of valve, when ensureing that in Variable Control oil cylinder 4, piston at an arbitrary position, spool stable operation is in left position, as shown in Figure 6.The pressure signal of load by shuttle valve 12 relatively and draw maximum pressure signal, and by the X mouth feedback effect on the housing 9 of pump on the right side of flow control valve 8.During system stability work, the highest load pressure on the right side of the pressure versus flow control valve 8 of pump discharge and spring force balance each other, and flow control valve 8 stable operation is under a certain position, and pump delivery size is directly proportional to the total open area of the load-sensitive valve in system.Now system is that load-sensitive throttling controls, and concrete multivariable process is as follows:
A, discharge capacity become large change procedure.When the control signal of load-sensitive valve one or more in system becomes large, its opening area increases.Now load does not change, therefore the active force on the right side of flow control valve 8 does not change.The opening area of valve increases and the flow of pump does not change, therefore its pressure loss diminishes, therefore the pressure of pump discharge reduces.To left movement under the effect that the spool of flow control valve 8 is made a concerted effort on right side, P mouth and the A mouth of valve are closed gradually, and A mouth and T mouth are opened gradually.Part fluid in cavity on the right side of Variable Control oil cylinder 4 is by A to the T mouth of electromagnetic proportional valve 6, and through A to the T mouth of constant-pressure control valve 7, then pass through A to the T mouth of flow control valve 8, the housing 10 of inflow pump, finally, through L mouth oil sump tank.Variable Control oil cylinder 4 moves right under the effect of left side Returnning spring 3, and pump delivery becomes large gradually.Meanwhile, the flow that pump exports increases, and increased by the flow of load-sensitive valve, the pressure loss of its valve port also increases, therefore the pressure of pump discharge raises gradually.The spool of flow control valve 8 is stressed to be balanced gradually, moves towards equilibrium position, and A to the T mouth of valve turns down gradually, until Variable Control oil cylinder 4 is stabilized in a fixed position, flow control valve 8 reaches new equilibrium position.Now, pump delivery also just stabilizes.The process that Here it is pump delivery increases along with control signal and increases.
The change procedure that B, discharge capacity diminish.When the control signal of load-sensitive valve one or more in system diminishes, its opening area reduces.Now load does not change, therefore the active force on the right side of flow control valve 8 does not change.The opening area of valve reduces and the flow of pump does not change, therefore its pressure loss increases, therefore the pressure of pump discharge raises.The spool of flow control valve 8 moves right under the effect of the outlet pressure of left pump, and P mouth and the A mouth of valve are opened gradually, and A mouth and T mouth are closed gradually.When the most extreme, P mouth and A mouth are opened without throttling completely, and A mouth and T mouth only retain a minimum gap and maintain system stability.The high-voltage oil liquid of pump discharge is flowed out by P to the A mouth of flow control valve, and through T to the A mouth of constant-pressure control valve 7, T to the A mouth of electromagnetic proportional valve 6, entering variable controls the cavity on the right side of oil cylinder 4.Variable Control oil cylinder 4 compression reseting spring 3 is also moved to the left, and pump delivery reduces gradually.Meanwhile, the flow that pump exports reduces, and reduced by the flow of load-sensitive valve, the pressure loss of its valve port also reduces, therefore the pressure of pump discharge reduces gradually.The spool of flow control valve 8 is stressed to be balanced gradually, moves towards equilibrium position, and P to the A mouth of valve turns down gradually, until Variable Control oil cylinder 4 is stabilized in a fixed position, flow control valve 8 reaches new equilibrium position.Now, pump delivery also just stabilizes.The process that Here it is pump delivery reduces along with control signal and reduces.
Known by above analysis, now system can make the output flow size of pump and the openings of sizes of load-sensitive valve adapt automatically, is a load sensitive system.Like this, the speed of each executive component just can be made only relevant with the opening of corresponding load-sensitive valve, and not by the impact of other executive component loads.
Two, under above-mentioned arbitrary load-sensitive or volumetric void fraction pattern, if delivery side of pump pressure exceedes the setting pressure of spring on the right side of constant-pressure control valve 7, P mouth and the A mouth of constant-pressure control valve are opened completely, and A mouth and T mouth are closed completely, pump delivery diminishes, and avoids spill losses.Be analyzed as follows:
1) under volumetric void fraction pattern: as shown in Fig. 7, Fig. 8, Fig. 9.Can find out, under volumetric void fraction pattern, regardless of the working state of electromagnetic proportional valve 6, the high-voltage oil liquid of all equivalent pump discharge controls the right side of oil cylinder 4 through electromagnetic proportional valve 6 entering variable.Variable Control oil cylinder 4 is to left movement, and pump delivery reduces.
2) under load-sensitive pattern: as shown in Figure 10.Under load-sensitive pattern, due to the position relationship of each control valve, when after constant-pressure control valve 7 action, regardless of the working state of flow control valve 8, the high-voltage oil liquid of pump discharge can control the right side of oil cylinder 4 by P to the A mouth entering variable of valve.Variable Control oil cylinder 4 is to left movement, and pump delivery reduces.
Three, when needing arbitrarily, such as equipment needs emergent stopping action, and controller 15 exports to the certain electric current of displacement valves 9, controls its commutation, as shown in figure 11.The P mouth of minimum injection rate valve 9 is communicated with A mouth, makes the high pressure oil entering variable of pump discharge control the right side of oil cylinder 4.Variable Control oil cylinder 4 is to left movement, and pump delivery reduces.
Claims (4)
1. a composite variable pump, comprises housing (101), the electromagnetic proportional valve (6) of two-position three way being positioned at the pump body (1) of housing (101), the Variable Control oil cylinder (4) be connected with pump body (1) and being connected with Variable Control oil cylinder (4); Described housing (101) is provided with the B hydraulic fluid port connecting pump body (1) oil outlet, connects the S hydraulic fluid port of pump body (1) filler opening, connects the load feedback hydraulic fluid port X of external feedback oil circuit; Described electromagnetic proportional valve (6) hydraulic fluid port P is connected to pump body (1) oil outlet, and electromagnetic proportional valve (6) hydraulic fluid port A is connected to Variable Control oil cylinder (4) oil pocket;
It is characterized in that:
The displacement valves (9) of bi-bit bi-pass is connected with between described electromagnetic proportional valve (6) hydraulic fluid port P and electromagnetic proportional valve (6) hydraulic fluid port A;
The constant-pressure control valve (7) of bi-bit bi-pass is connected with between described pump body (1) oil outlet B and electromagnetic proportional valve (6) hydraulic fluid port T;
The flow control valve (8) of bi-bit bi-pass is connected with between described pump body (1) oil outlet B and constant-pressure control valve (7); Described flow control valve (8) controls side and connects load feedback hydraulic fluid port X.
2. a kind of composite variable pump according to claim 1, is characterized in that: described pump body (1) is provided with swash plate (2); Described swash plate (2) one end is connected to the tailpiece of the piston rod of Variable Control oil cylinder (4); Described Variable Control oil cylinder (4) is provided with feedback rod (5), and the other end of feedback rod (5) is connected with the valve pocket of described electromagnetic proportional valve (6); The Returnning spring (3) that Variable Control oil cylinder (4) upper cover of piston rod has control piston bar to retract.
3. a kind of composite variable pump according to claim 1, is characterized in that: described housing (101) has and leaks hydraulic fluid port L.
4. use a hydraulic control system for the utilization composite variable pump of described composite variable pump, it is characterized in that: comprise controller (15), composite variable pump, multiple hydraulic actuator and multiple load-sensitive valve; Electromagnetic proportional valve (6) and displacement valves (9) in described controller (15) control connection composite variable pump, and load-sensitive valve; Described load-sensitive valve number is identical with hydraulic actuator number, and load-sensitive valve to be connected in hydraulic actuator and composite variable pump between hydraulic fluid port B; Described multiple load-sensitive valve oil outlet pressure is connected to load feedback hydraulic fluid port X in composite variable pump more afterwards by multiple shuttle valve (12); In described composite variable pump, hydraulic fluid port S and hydraulic fluid port L is connected to fuel tank.
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| CN107237785A (en) * | 2017-07-25 | 2017-10-10 | 江苏谷登工程机械装备有限公司 | A kind of pressure cut off control system of external enclosed pump |
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| CN108571481B (en) * | 2018-01-23 | 2020-03-13 | 北京航空航天大学 | Oil inlet and return independent regulation retarding control strategy of heavy vehicle electro-hydraulic traveling system |
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| CN108953258A (en) * | 2018-09-25 | 2018-12-07 | 中国重型机械研究院股份公司 | A kind of energy-efficient four cylinder of flexible pipe membrane pump back and forth drives pump control hydraulic system |
| CN108953258B (en) * | 2018-09-25 | 2024-02-02 | 中国重型机械研究院股份公司 | Efficient and energy-saving hose diaphragm pump four-cylinder reciprocating driving pump control hydraulic system |
| CN109798272A (en) * | 2019-01-11 | 2019-05-24 | 徐州工业职业技术学院 | A kind of composite variable pump and composite hydraulic control system |
| CN109882462A (en) * | 2019-01-11 | 2019-06-14 | 徐州工业职业技术学院 | Hydraulic control ratio merges variable pump and hydraulic control intelligent flow distribution system with load-sensitive |
| CN109798272B (en) * | 2019-01-11 | 2020-08-28 | 徐州工业职业技术学院 | Compound variable pump and compound hydraulic control system |
| CN114483684A (en) * | 2022-01-28 | 2022-05-13 | 北京京环装备设计研究院有限公司 | Hydraulic control system of garbage compression station, garbage compression station and hydraulic control method |
| CN114483684B (en) * | 2022-01-28 | 2024-06-07 | 北京京环装备设计研究院有限公司 | Hydraulic control system of garbage compression station, garbage compression station and hydraulic control method |
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