CN105156391B - A kind of composite variable pump and the hydraulic control system with composite variable pump - Google Patents
A kind of composite variable pump and the hydraulic control system with composite variable pump Download PDFInfo
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- CN105156391B CN105156391B CN201510592502.2A CN201510592502A CN105156391B CN 105156391 B CN105156391 B CN 105156391B CN 201510592502 A CN201510592502 A CN 201510592502A CN 105156391 B CN105156391 B CN 105156391B
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Abstract
The present invention announces a kind of variable pump and a kind of hydraulic control system with composite variable pump for merging load-sensitive throttling control and volumetric void fraction function.Composite variable pump includes housing, pump body, Variable Control oil cylinder and electromagnetic proportional valve；Electromagnetic proportional valve is parallel with displacement valves；Constant-pressure control valve is connected between pump body oil-out and electromagnetic proportional valve；Flow control valve is connected between pump body oil-out and constant-pressure control valve；Flow control valve one controls side connection load feedback hydraulic fluid port X.A kind of hydraulic control system with composite variable pump, including controller, composite variable pump, multiple hydraulic actuators and multiple load-sensitive valves.Multiple hydraulic pump can be such that system is operated under volumetric void fraction pattern or load-sensitive throttling control model, and the action between multiple executing agencies is not interfere with each other, and system effectiveness is higher, is more saved.
Description
Technical field
The present invention relates to technical field of hydraulic, is specifically a kind of fusion load-sensitive throttling control and volumetric void fraction work(
The variable pump of energy, and a kind of hydraulic control system with composite variable pump for having used this variable pump.
Background technology
With the progress of equipment manufacturing technology, main frame is to hydraulic system in lightweight, energy utilization efficiency, more execution
The requirement more and more higher of element composition operation etc..In current hydraulic system, variable pump volume control system and load
Sensitive throttle control system is widely used due to the advantages of itself is each unique.
Typical variable pump volume control system principle is as shown in Figure 1.The electric oil suction from fuel tank 10 of Electro-hydraulic Proportional Displacement pump 20, supply
To solenoid directional control valve 30.The control signal of the controlled device 50 of solenoid directional control valve 30 carries out switch motion.Hydraulic cylinder 40 need not move
When making, controller I 50 closes solenoid directional control valve 30, while by the discharge capacity vanishing of electric Electro-hydraulic Proportional Displacement pump 20.Hydraulic cylinder 40 needs
When acting, controller I 50 opens solenoid directional control valve 30, while needs to adjust the discharge capacity of electric Electro-hydraulic Proportional Displacement pump 20 by system
To suitable size.The displacement variation of electric Electro-hydraulic Proportional Displacement pump 20 just controls the velocity magnitude of hydraulic cylinder.Because solenoid directional control valve 30
Control is only played whether to move and direction, without throttling action, so, export to executive component from pump in volume control system
The pressure loss it is smaller, the energy utilization efficiency of system is higher.
But variable pump volume control system has a shortcoming, any instant, a pump can only correspond to work
Executive component, in other words, for multiple executive component composite moves, each executive component is required for a single pump to carry out
Control.When multiple executive components be present, it is necessary to which multiple hydraulic pumps, add and be designed and manufactured as this.
Typical load-sensitive throttle control system principle is as shown in Figure 2.The oil suction out of fuel tank 100 of load sensitive pump 200,
Hydraulic oil is given to load-sensitive valve I 300 and load-sensitive valve II 400 respectively.Load-sensitive valve I 300 and load-sensitive valve II
400 control hydraulic cylinder I 600 and hydraulic cylinder II 700 respectively（Executive component）.The effect of shuttle valve 500 be by two hydraulic cylinders most
Heavy load pressure signal is compared, and a larger signal is passed into the pump of load-sensitive 200.Controller II 800 is used for
Needed to control aperture and the direction of load-sensitive valve according to system.Load sensitive pump 200 is built-in with flow control valve.Flow controls
The pressure that valve can adjust pump is only higher by a steady state value set than load.Thus, relatively conventional constant displacement pump overflow valve returns
For road, load sensitive system can reduce energy dissipation.The load-sensitive valve used in load sensitive system, can be as routine
The same aperture that fluid direction and valve port are controlled according to the electric signal of controller of proportioning valve.Meanwhile collect inside load-sensitive valve
The constant pressure-compensated valve of pressure difference before and after into valve port corresponding to being used to making.This constant pressure difference is used for the through-current capacity for ensureing valve port
Only and valve port flow area is directly proportional, and this pressure difference is less than the pressure difference of the flow control valve setting inside pump.So, load quick
The action that sensing system just possesses each executive component is not influenceed by respective different loads size.
In fact, hydraulic system is not in the case of always working at multiple executing agencies while working.Many times,
Hydraulic system only has an executing agency and worked.When only existing executing agency's motion in system, just it is not present multiple
Executive component influence each other speed the problem of.However, now pressure-compensated valve still works, the pressure difference before and after reversal valve is kept
For a steady state value.At this moment, the flow control valve built in load sensitive pump 200 also makes the pressure of pump discharge and load keep a perseverance
Definite value.In this case, pressure-compensated valve and the flow control valve built in pump just constitute dual compensation, in other words, pressure
Element of the recuperation valve into unnecessary waste energy.
The hydraulic pump of design fusion load-sensitive throttling control and volumetric void fraction advantage is a problem for being worth research.
The content of the invention
In order to overcome the above-mentioned deficiencies of the prior art, the present invention provides a kind of composite variable pump and with composite variable pump
Hydraulic control system.
The present invention is achieved through the following technical solutions：A kind of composite variable pump, including housing, the pump sheet in housing
The electromagnetic proportional valve of body, the Variable Control oil cylinder being connected with pump body and the two-position three way being connected with Variable Control oil cylinder；It is described
Housing is provided with the B hydraulic fluid ports of connection pump body oil-out, connects the S hydraulic fluid ports of pump body oil inlet, connection external feedback oil circuit
Load feedback hydraulic fluid port X；The electromagnetic proportional valve hydraulic fluid port P is connected to pump body oil-out, and electromagnetic proportional valve hydraulic fluid port A is connected to variable
Control cylinder oil pocket；
The displacement valves of bi-bit bi-pass are connected 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 between described pump body oil-out B and electromagnetic proportional valve hydraulic fluid port T；
The flow control valve of bi-bit bi-pass is connected between described pump body oil-out B and constant-pressure control valve；Described
Flow control valve one controls side connection load feedback hydraulic fluid port X.
It is further：Swash plate is installed on the pump body；Described swash plate one end is connected to the work of Variable Control oil cylinder
Stopper rod end；The Variable Control oil cylinder is provided with feedback rod, the valve pocket phase of the other end of feedback rod and described electromagnetic proportional valve
Connection；The back-moving spring for controlling piston rod to retract is cased with Variable Control cylinder piston rod.
Leakage hydraulic fluid port L is provided with the housing.
A kind of hydraulic control system with composite variable pump with the composite variable pump, including it is controller, compound
Variable pump, multiple hydraulic actuators and multiple load-sensitive valves；Electromagnetism ratio in the controller control connection composite variable pump
Example valve and displacement valves, and load-sensitive valve；Described load-sensitive valve number is identical with hydraulic actuator number, and load is quick
Sense valve is connected in hydraulic actuator and composite variable pump between hydraulic fluid port B；The multiple load-sensitive valve oil-out pressure is led to
Load feedback hydraulic fluid port X in composite variable pump is connected to after crossing multiple shuttle valves；Hydraulic fluid port S and hydraulic fluid port in described composite variable pump
L is connected to fuel tank.
The principle of the invention is：, will be negative in hydraulic system when there was only a hydraulic actuator job in hydraulic system
Carry sensitive valve to open to maximum open, composite variable pump is in rate variable mode of operation, i.e. system is volumetric void fraction pattern.Pass through
The discharge capacity of controlling pump carrys out the flow of control system, and then controls the operating rate of hydraulic actuator.It is more when having in hydraulic system
Individual hydraulic actuator works simultaneously when, composite variable pump is in load-sensitive mode of operation, i.e. system throttles for load-sensitive
Control model.No matter several hydraulic actuators are working, when the operating pressure of composite variable pump exceedes certain pressure, compound change
Amount pump reduces discharge capacity in the presence of constant-pressure control valve, avoids spill losses.Meanwhile above-mentioned all switchings are to carry out automatically
's.
Other, in case of need, the discharge capacity of composite variable pump by the effect of displacement valves, can be made with most fast
Speed becomes minimum injection rate.
Compared with prior art, the beneficial effects of the invention are as follows：For the hydraulic system of multi-execution component, at only one
When executing agency acts, multiple hydraulic pump can make system be operated in volumetric void fraction pattern, system effectiveness can be made higher, more
Energy-conservation.When having multiple executing agencies while working, multiple hydraulic pump makes hydraulic system become load-sensitive throttling control model,
Ensure that the action between multiple executing agencies is not interfere with each other.Meanwhile in case of need, or the work pressure of multiple hydraulic pump
When power exceedes certain value, the discharge capacity of multiple hydraulic pump can be become to minimum, ensure the safety of system.
Brief description of the drawings
Fig. 1 is the typical variable pump volume control system hydraulic schematic diagram described in background technology；
Fig. 2 is the typical load-sensitive throttle control system hydraulic schematic diagram described in background technology；
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 hydraulic control system of composite variable pump in an only hydraulic actuator job
Fundamental diagram；Workless hydraulic actuator omits in figure；
Fig. 5 is detailed schematic diagram of the electromagnetic proportional valve at equilbrium position in the present invention；
Fig. 6 is that the present invention uses the hydraulic control system of composite variable pump when multiple hydraulic actuators work simultaneously
Fundamental diagram；Two hydraulic actuators are only drawn in figure as signal；
Fig. 7 is fundamental diagram of the present invention under volumetric void fraction pattern during increase discharge capacity into Isobarically Control；
Fig. 8 stablizes in a certain discharge capacity into the fundamental diagram of Isobarically Control for the present invention under volumetric void fraction pattern；
Fig. 9 is fundamental diagram of the present invention under volumetric void fraction pattern during reduction discharge capacity into Isobarically Control；
Figure 10 is the fundamental diagram that the present invention enters Isobarically Control in the case where load-sensitive throttles control model；
Figure 11 is that work of the present invention when controlling pumpage to become minimum using displacement valves in the case of any need is former
Reason figure.
Fig. 3 is into Figure 11：1st, pump body；2nd, swash plate；3rd, back-moving spring；4th, Variable Control oil cylinder；5th, feedback rod；6th, electromagnetism
Proportioning valve；7th, constant-pressure control valve；8th, flow control valve；9th, displacement valves；101st, housing；11st, load-sensitive valve II；12nd, shuttle valve；
13rd, hydraulic actuator II；14th, hydraulic actuator I；15th, controller；16th, load-sensitive valve I.
Embodiment
It is the specific embodiment of the present invention below, in conjunction with accompanying drawing, the invention will be further described.
As shown in figure 3, a kind of composite variable pump, including pump body 1, Variable Control oil cylinder 4, electromagnetic proportional valve 6, displacement valves
9th, constant-pressure control valve 7 and flow control valve 8；The hydraulic fluid port P of electromagnetic proportional valve 6 of two-position three way is connected to the oil-out of pump body 1, electromagnetism
The hydraulic fluid port A of proportioning valve 6 is connected to the oil pocket of Variable Control oil cylinder 4；It is fuel-displaced that the hydraulic fluid port P of displacement valves 9 of bi-bit bi-pass is connected to pump body 1
Mouthful, the hydraulic fluid port A of displacement valves 9 is connected to the oil pocket of Variable Control oil cylinder 4；The hydraulic fluid port P of constant-pressure control valve 7 of bi-bit bi-pass is connected to pump body
1 oil-out, the hydraulic fluid port A of constant-pressure control valve 7 are connected to the hydraulic fluid port T of electromagnetic proportional valve 6, and the left control side of constant-pressure control valve 7 is connected to pump sheet
The oil-out of body 1；The hydraulic fluid port P of flow control valve 8 of bi-bit bi-pass and left control side are to the oil-out of pump body 1, the hydraulic fluid port of flow control valve 8
A is connected to the hydraulic fluid port T of constant-pressure control valve 7, and the right control side of flow control valve 8 is connected to load feedback hydraulic fluid port X.Installed on pump body 1
There is swash plate 2, the one end of swash plate 2 is connected to the tailpiece of the piston rod of Variable Control oil cylinder 4, and the side-to-side movement of Variable Control oil cylinder 4 promotes swash plate 2
Swing；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, this reality
The valve pocket for having showed electromagnetic proportional valve 6 is consistent with the motion of Variable Control oil cylinder 4；The upper cover of piston rod of Variable Control oil cylinder 4 has control
The back-moving spring 3 that piston rod is retracted.Above-mentioned part is arranged at housing 101, and housing 101 is provided with the oil-out of connection pump body 1
B hydraulic fluid ports, the S hydraulic fluid ports of the oil inlet of connection pump body 1, connect the load feedback hydraulic fluid port X and leakage hydraulic fluid port L of external feedback oil circuit.
Pump body 1 can discharge from hydraulic fluid port S oil suctions, and by fuel-displaced B mouths, while complete mechanical energy to pressure transformation of energy.
Hydraulic fluid port S is connected with hydraulic oil container, and its effect is that hydraulic pump can be by this hydraulic fluid port by fluid suction pump body.Swash plate 2 can be around
Own axes rotate to an angle.The size of the size of the angle of swash plate 2 and the discharge capacity of pump corresponds.Back-moving spring 3 can be
During air pump inoperative, piston is parked in the maximum position of low order end, the i.e. discharge capacity of respective pump in Variable Control oil cylinder 4.
As shown in fig. 6, a kind of hydraulic control system with composite variable pump with composite variable pump, including controller
15th, composite variable pump, multiple hydraulic actuators and multiple load-sensitive valves；Electricity in the control connection composite variable pump of controller 15
Magnetic proportioning valve 6 and displacement valves 9, and load-sensitive valve；Load-sensitive valve number is identical with hydraulic actuator number, and load is quick
Sense valve is connected in hydraulic actuator and composite variable pump between hydraulic fluid port B；Multiple load-sensitive valve oil-out pressure pass through more
Load feedback hydraulic fluid port X in composite variable pump is connected to after individual shuttle valve 12；Hydraulic fluid port S and hydraulic fluid port L are connected in composite variable pump
Fuel tank.
First, assume that load pressure is not reaching to the setting pressure of constant-pressure control valve 7, i.e. constant-pressure control valve 7 is in shown in Fig. 4
Position works.
When only one executing agency works, controller sends signal to corresponding load-sensitive valve.As shown in figure 4, figure
In eliminate other without action executive component and associated loop.Controller 15 is to load-sensitive valve 16 with maximum control electricity
Stream, the valve valve port standard-sized sheet.Now, the also standard-sized sheet of the pressure-compensated valve built in load-sensitive valve 16, therefore whole load-sensitive valve only rises
Direction controlling acts on, and controls the expanding-contracting action of hydraulic cylinder 14, no throttling action, pressure loss very little.Because load-sensitive valve 16
The front and rear pressure loss it is small, so the pressure of pump discharge and load feedback pressure very close to, therefore, the flow control valve 8 of pump is on the right side
Worked all the time in right position in the presence of lateral spring, i.e., A to the T mouth standard-sized sheets of the valve, P to A mouths completely close.The action of hydraulic cylinder 14
Speed is only dependent upon the flow by load-sensitive valve 16, that is, the displacement size of the output flow of pump, i.e. pump.The discharge capacity of pump
Size is exported by controller 15 and determined to the electric current of electromagnetic proportional valve 6.During system steady operation, the steady operation of electromagnetic proportional valve 6
Under equilbrium position, as shown in Figure 5.The displacement size of pump is directly proportional to the control electric current of electromagnetic proportional valve 6.Specific multivariable process
It is as follows：
1）Discharge capacity becomes big change procedure.Electromagnetic proportional valve 6 obtains certain current signal, and electromagnet promotes valve element to the right
Motion, P mouths and the A mouths of valve are progressively closed off, and A mouths are gradually opened with T mouths.Part oil in the cavity on the right side of Variable Control oil cylinder 4
Liquid is flowed out by A to the T mouths of electromagnetic proportional valve 6, by constant-pressure control valve 7, flow control valve 8, flows into the housing 10 of pump, most
Afterwards, through L mouth oil return boxes.Variable Control oil cylinder 4 moves right in the presence of left side back-moving spring 3, and the discharge capacity of pump becomes larger.
At the same time, feedback rod 5 also moves right under the drive of Variable Control oil cylinder 4, so as to drag the valve pocket of electromagnetic proportional valve 6 to
Right motion, therefore, A to the T mouths of electromagnetic proportional valve 6 gradually turn down, until Variable Control oil cylinder 4 is stable in a fixed position, electricity
Magnetic proportioning valve 6 reaches new equilbrium position.Now, the discharge capacity of pump also just stabilizes.Here it is the discharge capacity of pump with control signal
The process for increasing and increasing.
2）The change procedure that discharge capacity diminishes.When controller 15 exports the electric current reduction to electromagnetic proportional valve 6, electromagnet
Power reduces, and valve element is gradually opened in the presence of the spring of right side to left movement, P mouths and the A mouths of valve, and A mouths progressively close off with T mouths.
The cavity that the high-voltage oil liquid of pump discharge passes through the right side of 6 entering variable control cylinder of electromagnetic proportional valve 4.Variable Control oil cylinder 4 compresses
Back-moving spring 3 is moved to the left, and the discharge capacity of pump is gradually reduced.At the same time, feedback rod 5 is under the drive of Variable Control oil cylinder 4
It is moved to the left, so as to drag the valve pocket of electromagnetic proportional valve 6 to left movement, therefore, P to the A mouths of electromagnetic proportional valve 6 gradually turn down, directly
Reach new equilbrium position in a fixed position, electromagnetic proportional valve 6 to Variable Control oil cylinder 4 is stable.Now, the discharge capacity of pump
Just stabilize.Here it is the process that the discharge capacity of pump reduces as control signal reduces.
Analysis more than, now system is a volume control system.In this manner it is possible to obtain higher energy
Measure utilization ratio.Meanwhile this operation principle is all effective for any one executive component in system.
When there is multiple executive components in hydraulic system（Two hydraulic cylinders are only depicted in figure as signal）During work, control
Device 15 exports maximum controlling current to electromagnetic proportional valve 6, the power of electromagnet is ensured Variable Control more than the spring force on the right side of valve
In oil cylinder 4 piston at an arbitrary position when valve element steady operation in left position, as shown in Figure 6.The pressure signal of load passes through shuttle valve 12
Relatively and maximum pressure signal is drawn, and the X mouths feedback effect on the housing 9 for passing through pump is on the right side of flow control valve 8.System
During steady operation, the pressure of pump discharge balances each other with the highest load pressure and spring force on the right side of flow control valve 8, flow control
For the steady operation of valve 8 under a certain position, the displacement size of pump is directly proportional to the total open area of the load-sensitive valve in system.This
When system be load-sensitive throttling control, specific multivariable process is as follows：
A, discharge capacity becomes big change procedure.When the control signal of one or more load-sensitive valves in system becomes big, its
Aperture area increases.Now load and do not change, therefore the active force on the right side of flow control valve 8 does not change.Valve
Aperture area increases and the flow of pump does not change, therefore its pressure loss diminishes, therefore the pressure of pump discharge reduces.Flow control
The valve element of valve 8 processed is progressively closed off in the presence of making a concerted effort on right side to left movement, P mouths and the A mouths of valve, and A mouths are gradually opened with T mouths.
Part fluid in the cavity on the right side of Variable Control oil cylinder 4 is by A to the T mouths of electromagnetic proportional valve 6, by the A of constant-pressure control valve 7
To T mouths, then A to the T mouths by flow control valve 8, the housing 10 of pump is flowed into, finally, through L mouth oil return boxes.Variable Control oil cylinder 4
Moved right in the presence of left side back-moving spring 3, the discharge capacity of pump becomes larger.At the same time, the flow increase of pump output, leads to
The flow increase of overload sensitive valve, the pressure loss of its valve port also increases, therefore the pressure of pump discharge gradually rises.Flow controls
The valve element stress of valve 8 gradually balances, and is moved towards equilbrium position, A to the T mouths of valve gradually turn down, until Variable Control oil cylinder 4 is steady
A fixed position is scheduled on, flow control valve 8 reaches new equilbrium position.Now, the discharge capacity of pump also just stabilizes.Here it is pump
Discharge capacity with control signal increase and increase process.
B, the change procedure that discharge capacity diminishes.When the control signal of one or more load-sensitive valves in system becomes small, its
Aperture area reduces.Now load and do not change, therefore the active force on the right side of flow control valve 8 does not change.Valve
Aperture area reduces and the flow of pump does not change, therefore its pressure loss increases, therefore the pressure rise of pump discharge.Flow control
The valve element of valve 8 processed is moved right in the presence of the outlet pressure of left pump, and P mouths and the A mouths of valve are gradually opened, A mouths and T mouths by
Gradually close.In the case of most extreme, P mouths are opened with A mouths entirely without throttling, and A mouths only retain a minimum gap with T mouths and maintained
System is stable.The high-voltage oil liquid of pump discharge is flowed out by P to the A mouths of flow control valve, by T to the A mouths of constant-pressure control valve 7,
T to the A mouths of electromagnetic proportional valve 6, the cavity on the right side of entering variable control cylinder 4.The compression reseting spring 3 of Variable Control oil cylinder 4 is simultaneously
It is moved to the left, the discharge capacity of pump is gradually reduced.At the same time, the flow of pump output reduces, and is reduced by the flow of load-sensitive valve,
The pressure loss of its valve port also reduces, therefore the pressure of pump discharge gradually reduces.The valve element stress of flow control valve 8 gradually balances,
Moved towards equilbrium position, P to the A mouths of valve gradually turn down, until Variable Control oil cylinder 4 is stable in a fixed position, flow
Control valve 8 reaches new equilbrium position.Now, the discharge capacity of pump also just stabilizes.Here it is the discharge capacity of pump as control signal subtracts
Small and reduction process.
By more than analysis, now system can make the output flow size of pump and opening for load-sensitive valve automatically
Mouth size is adapted, and is a load sensitive system.In this manner it is possible to so that the speed of each executive component is only born with corresponding
It is relevant to carry the opening of sensitive valve, without being influenceed by the load of other executive components.
2nd, under above-mentioned arbitrary load-sensitive or volumetric void fraction pattern, if the outlet pressure of pump exceedes constant pressure control
The setting pressure of the right side spring of valve 7 processed, P mouths and the A mouths of constant-pressure control valve are opened completely, and A mouths completely close with T mouths, the row of pump
Amount diminishes, and avoids spill losses.It is analyzed as follows：
1）Under volumetric void fraction pattern：As shown in Fig. 7, Fig. 8, Fig. 9.As can be seen that under volumetric void fraction pattern, no matter electromagnetism
How is the working condition of proportioning valve 6, and the high-voltage oil liquid of all equivalent pump discharge passes through the entering variable control cylinder 4 of electromagnetic proportional valve 6
Right side.Variable Control oil cylinder 4 reduces to left movement, the discharge capacity of pump.
2）Under load-sensitive pattern：As shown in Figure 10.Under load-sensitive pattern, because the position of each control valve is closed
System, after constant-pressure control valve 7 acts, the working condition regardless of flow control valve 8, the high-voltage oil liquid of pump discharge can lead to
Cross the right side of P to the A mouth entering variables control cylinder 4 of valve.Variable Control oil cylinder 4 reduces to left movement, the discharge capacity of pump.
3rd, when any need, such as equipment needs emergent stopping to act, and controller 15 is exported to displacement valves 9 one
Fixed electric current, its commutation is controlled, as shown in figure 11.The P mouths of minimum injection rate valve 9 connect with A mouths, enter the hydraulic oil of pump discharge
The right side of Variable Control oil cylinder 4.Variable Control oil cylinder 4 reduces to left movement, the discharge capacity of pump.
Claims (3)
1. a kind of composite variable pump, including housing（101）, positioned at housing（101）Interior pump body（1）And pump body（1）Connection
Variable Control oil cylinder（4）With with Variable Control oil cylinder（4）The electromagnetic proportional valve of the two-position three way of connection（6）；The housing
（101）It is provided with connection pump body（1）The B hydraulic fluid ports of oil-out, connect pump body（1）The S hydraulic fluid ports of oil inlet, connect external feedback
The load feedback hydraulic fluid port X of oil circuit；The electromagnetic proportional valve（6）Hydraulic fluid port P is connected to pump body（1）Oil-out, electromagnetic proportional valve（6）
Hydraulic fluid port A is connected to Variable Control oil cylinder（4）Oil pocket；
It is characterized in that：
Described electromagnetic proportional valve（6）Hydraulic fluid port P and electromagnetic proportional valve（6）The displacement valves of bi-bit bi-pass are connected between hydraulic fluid port A
（9）；
Described pump body（1）Oil-out B and electromagnetic proportional valve（6）The constant-pressure control valve of bi-bit bi-pass is connected between hydraulic fluid port T
（7）；
Described pump body（1）Oil-out B and constant-pressure control valve（7）Between be connected with the flow control valve of bi-bit bi-pass（8）；Institute
The flow control valve stated（8）One control side connection load feedback hydraulic fluid port X；
The pump body（1）On swash plate is installed（2）；The swash plate（2）One end is connected to Variable Control oil cylinder（4）Piston rod
End；The Variable Control oil cylinder（4）It is provided with feedback rod（5）, feedback rod（5）The other end and described electromagnetic proportional valve（6）
Valve pocket be connected；Variable Control oil cylinder（4）Upper cover of piston rod has the back-moving spring that control piston rod is retracted（3）.
A kind of 2. composite variable pump according to claim 1, it is characterised in that：The housing（101）On be provided with Leakage Energy
Mouth L.
A kind of 3. hydraulic control system with composite variable pump described in claim 1, it is characterised in that：Including controller
（15）, composite variable pump, multiple hydraulic actuators and multiple load-sensitive valves；The controller（15）Control connects compound change
Measure electromagnetic proportional valve in pump（6）And displacement valves（9）, and load-sensitive valve；Described load-sensitive valve number performs with hydraulic pressure
Element number is identical, and load-sensitive valve is connected in hydraulic actuator and composite variable pump between hydraulic fluid port B；The multiple load
Sensitive valve oil-out pressure passes through multiple shuttle valves（12）After be connected to load feedback hydraulic fluid port X in composite variable pump；Described
Hydraulic fluid port S and hydraulic fluid port L are connected to fuel tank in composite variable pump.
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| Application Number | Priority Date | Filing Date | Title |
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| CN201510592502.2A CN105156391B (en) | 2015-09-17 | 2015-09-17 | A kind of composite variable pump and the hydraulic control system with composite variable pump |
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| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201510592502.2A CN105156391B (en) | 2015-09-17 | 2015-09-17 | A kind of composite variable pump and the hydraulic control system with composite variable pump |
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| CN105156391B true CN105156391B (en) | 2017-11-14 |
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| DE102013214861A1 (en) * | 2012-08-16 | 2014-05-22 | Robert Bosch Gmbh | Regulating device for static fluid hydrostatic pump, has power adjusting valve provided with three interfaces and valve slide block, and clapboard provided with throttling bolt, where pressure of pressure interface is reduced |
| CN204284032U (en) * | 2014-11-18 | 2015-04-22 | 徐州工业职业技术学院 | Single actuator automatic switchover rapid movement oil hydraulic circuit |
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