CN107489663B - A kind of variable pump and the hydraulic control system with variable pump - Google Patents
A kind of variable pump and the hydraulic control system with variable pump Download PDFInfo
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- CN107489663B CN107489663B CN201710888902.7A CN201710888902A CN107489663B CN 107489663 B CN107489663 B CN 107489663B CN 201710888902 A CN201710888902 A CN 201710888902A CN 107489663 B CN107489663 B CN 107489663B
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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
- F15B7/00—Systems in which the movement produced is definitely related to the output of a volumetric pump; Telemotors
-
- 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
- F15B11/161—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors with sensing of servomotor demand or load
- F15B11/165—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors with sensing of servomotor demand or load for adjusting the pump output or bypass in response to demand
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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
- F15B21/00—Common features of fluid actuator systems; Fluid-pressure actuator systems or details thereof, not covered by any other group of this subclass
- F15B21/02—Servomotor systems with programme control derived from a store or timing device; Control devices therefor
-
- 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
- F15B21/00—Common features of fluid actuator systems; Fluid-pressure actuator systems or details thereof, not covered by any other group of this subclass
- F15B21/14—Energy-recuperation means
-
- 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
- F15B2211/00—Circuits for servomotor systems
- F15B2211/20—Fluid pressure source, e.g. accumulator or variable axial piston pump
- F15B2211/205—Systems with pumps
- F15B2211/2053—Type of pump
- F15B2211/20546—Type of pump variable capacity
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- Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Fluid Mechanics (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Analytical Chemistry (AREA)
- Fluid-Pressure Circuits (AREA)
- Control Of Positive-Displacement Pumps (AREA)
Abstract
A kind of variable pump and the hydraulic control system with variable pump, variable pump are equipped with spring with pumping in the variable oil cylinder that swash plate is connect in ontology, the piston rod of variable oil cylinder and the valve pocket of electromagnetic proportional valve connect；The P mouth of electromagnetic proportional valve, the P mouth of flow control valve, the outlet of pump ontology are connected with variable cylinder rod chamber；The left control mouth of flow control valve is connected to its P mouthfuls；Pump case be equipped with, into and feedback port；The A mouth of electromagnetic proportional valve is connected to the P mouth of switching valve；The A mouth of flow control valve is connected to the T mouth of switching valve；The A mouth of switching valve is connected to the rodless cavity of variable oil cylinder, and switching valve is by the B oral fluid control of electromagnetic proportional valve or automatically controlled.System, including the execution unit that variable pump and at least two are made of executive component and load-sensitive valve, controller connects electromagnetic proportional valve and load-sensitive valve.The variable pump can solve aging of electrical element acceleration problem, can prolong the service life, which can automatically switch on volume and Ioad-sensing control mode.
Description
Technical field
The present invention relates to variable pump and technical field of hydraulic, and in particular to a kind of variable pump and the liquid with variable pump
Pressure control system.
Background technique
It is compound in lightweight, energy utilization efficiency, multi-execution component to hydraulic system with the development of equipment manufacturing technology
The requirement of operation etc. is higher and higher.In existing hydraulic system, variable pump volume control system and load-sensitive throttling
Control system is widely used due to respective advantage.
In typical variable pump volume control system, electric Electro-hydraulic Proportional Displacement pump supplies hydraulic oil in fuel tank by solenoid directional control valve
To hydraulic cylinder.Wherein solenoid directional control valve is carried out switch motion by the control of controller.When hydraulic cylinder does not need movement, controller will
Solenoid directional control valve is closed, while the discharge capacity that electric Electro-hydraulic Proportional Displacement pumps being become zero.When hydraulic cylinder needs to act, controller changes electromagnetism
It is opened to valve, while needing to adjust the discharge capacity that electric Electro-hydraulic Proportional Displacement pumps to suitable size by system.The discharge capacity of electric Electro-hydraulic Proportional Displacement pump
Variation just controls the velocity magnitude of hydraulic cylinder.Because solenoid directional control valve only plays whether control moves and direction, without throttling
Effect, so, the pressure loss for exporting to executive component in volume control system from pump is smaller, the energy utilization efficiency of system
It is higher.But there is a disadvantages for variable pump volume control system, at any one time, a hydraulic pump can only correspond to one
The executive component of work, in other words, for multiple executive component composite moves, each executive component requires one individually
Hydraulic pump is controlled.In this way, needing to configure multiple hydraulic pumps when there is multiple executive components in systems, design is increased
And manufacturing cost.
In typical load-sensitive throttle control system, load sensitive pump gives hydraulic oil in fuel tank to multiple loads respectively
Sensitive valve.Each load-sensitive valve individually controls a hydraulic cylinder.By shuttle valve come to maximum load pressure between multiple hydraulic cylinders
Force signal is compared, and a biggish signal is fed back to load sensitive pump.Controller according to system for needing to control
The aperture of load-sensitive valve and direction.Each load sensitive pump is built-in with flow control valve, the adjustable load of flow control valve
The pressure of sensitive pump is only higher by the steady state value set than load.As a result, for relatively conventional constant displacement pump overflow valve circuit,
Load sensitive system can reduce energy dissipation.Load-sensitive valve used in load sensitive system, can be as conventional ratio
The same aperture that oil liquid direction and valve port are controlled according to the electric signal of controller of valve.Meanwhile load-sensitive valve has been internally integrated use
The constant pressure-compensated valve of pressure difference before and after making corresponding valve port.This constant pressure difference is used to guarantee the through-current capacity and valve of valve port
Mouth flow area is directly proportional, and this pressure difference is less than the pressure difference of the setting of the flow control valve inside load sensitive pump.In this way, load
The movement that sensory system just has each executive component is not influenced by respective different loads size.
In fact, hydraulic system is not to always work under the operating condition that multiple executing agencies work at the same time.Many times,
Only have an executing agency in hydraulic system working.When only one executing agency moves in system, just there is no multiple
Executive component influence each other speed the problem of.However, the pressure-compensated valve in load-sensitive valve still works at this time, to keep
Pressure difference before and after reversal valve is a steady state value.At this moment, the flow control valve built in load sensitive pump also make pump discharge pressure and
Load keeps a steady state value.In this case, built in the pressure-compensated valve and load sensitive pump built in load-sensitive valve
Flow control valve just constitutes dual compensation, and which results in serious restriction losses, and in other words, pressure-compensated valve is at extra
Waste the element of energy.
The waste of energy when in order to solve the problems, such as that only one executing agency acts in load-sensitive throttle control system, it is existing
There is the variable pump for having developed a kind of fusion load-sensitive throttling control and volumetric void fraction function in technology again, is working as hydraulic system
In the work of only one hydraulic actuator when, the load-sensitive valve in hydraulic system is opened to maximum open, at composite variable pump
In rate variable operating mode, i.e. system is volumetric void fraction mode.By the discharge capacity of control pump come the flow of control system, in turn
Control the operating rate of hydraulic actuator.When there is multiple hydraulic actuators to work at the same time in hydraulic system, composite variable
Pump is in load-sensitive operating mode, i.e. system is load-sensitive throttling control model.No matter several hydraulic actuators are in work
Make, when the operating pressure of composite variable pump is more than certain pressure, composite variable pump subtracts discharge capacity under the action of constant-pressure control valve
It is small, avoid restriction loss.But it has the following problems, when pump work is in Ioad-sensing control mode, needs electric proportional valve
Maximum current is inputted, the normal output of output is just can guarantee, otherwise can not achieve volumetric void fraction mode, and electric elements are long-term
In maximum current state, the aging that will cause electrical component accelerates, and then the service life of solenoid valve can be made seriously to reduce for work.In this way
It is easy to cause the unstable working condition of pump.
Summary of the invention
In view of the above existing problems in the prior art, the present invention provides a kind of variable pump, which can be volume control
Hydraulic system processed is energized, and can be energized for Ioad-sensing control hydraulic system, can be hydraulic in Ioad-sensing control
Solve the problems, such as restriction loss caused by the flow control valve built in it in system, and it is for Ioad-sensing control hydraulic system
Aging of electrical element acceleration problem caused by avoiding when energy supply because of long-time to solenoid-operated proportional long-time power supply station can extend pump
Service life.
To achieve the goals above, the present invention provides a kind of variable pump, including shell, be located at the intracorporal pump ontology of shell,
Variable Control oil cylinder, electromagnetic proportional valve and flow control valve；It is arranged outside piston rod in the rod chamber of Variable Control oil cylinder multiple
Position spring, the piston rod end of Variable Control oil cylinder are connect with an end for pumping intrinsic swash plate, Variable Control oil cylinder
Piston rod end also passes through feedback rod and is connected with the valve pocket of the electromagnetic proportional valve；The P mouth of electromagnetic proportional valve and flow control
Connecting node between the P mouth of valve passes through piping connection to the oil outlet for pumping ontology；The left position control mouth of flow control valve passes through
Piping connection is to its P mouthfuls；
The shell is equipped with the B mouth of the oil outlet by piping connection to pump ontology, by piping connection to pump ontology
The S mouth of oil inlet, the X mouth by the spring cavity of piping connection to flow control valve；
It further include switching valve, the connecting node between electromagnetic proportional valve and flow control valve also passes through pipeline and Variable Control
The rod chamber of oil cylinder connects；The A mouth of electromagnetic proportional valve and the B mouthfuls of P mouths for passing through piping connection to switching valve respectively are controlled with left position
Mouthful；The T mouth that the A mouth of flow control valve passes through piping connection to switching valve；The A mouth of switching valve passes through piping connection to Variable Control
The rodless cavity of oil cylinder.
It further, further include being serially connected in flow control valve to protect the safety of system in order to achieve the purpose that overpressure protection
A mouth and switching valve T mouth between constant-pressure control valve, the P mouth and its left position control mouth of constant-pressure control valve are and solenoid-operated proportional
Connecting node connection between valve and flow control valve.
A kind of variable pump, including shell are located at the intracorporal pump ontology of shell, Variable Control oil cylinder, electromagnetic proportional valve and flow
Control valve；Reset spring, the tailpiece of the piston rod of Variable Control oil cylinder are arranged outside piston rod in the rod chamber of Variable Control oil cylinder
Portion is connect with an end for pumping intrinsic swash plate, and the piston rod end of Variable Control oil cylinder also passes through feedback rod and the electricity
The valve pocket of magnetic proportioning valve is connected；Connecting node between the P mouth of electromagnetic proportional valve and the P mouth of flow control valve is connected by pipeline
It is connected to the oil outlet of pump ontology；The left position control mouth of flow control valve is by piping connection to its P mouthfuls；
The shell is equipped with the B mouth of the oil outlet by piping connection to pump ontology, by piping connection to pump ontology
The S mouth of oil inlet, the X mouth by the spring cavity of piping connection to flow control valve；
It further include switching valve, the connecting node between electromagnetic proportional valve and flow control valve also passes through pipeline and Variable Control
The rod chamber of oil cylinder connects；The P mouth that the A mouth of electromagnetic proportional valve passes through piping connection to switching valve；The A mouth of flow control valve passes through
Piping connection to switching valve T mouth；The rodless cavity that the A mouth of switching valve passes through piping connection to Variable Control oil cylinder；Switching valve is
Solenoid directional control valve.
It further, further include being serially connected in flow control valve to protect the safety of system in order to achieve the purpose that overpressure protection
A mouth and switching valve T mouth between constant-pressure control valve, the P mouth and its left position control mouth of constant-pressure control valve are and solenoid-operated proportional
Connecting node connection between valve and flow control valve.
In the technical scheme, which, can be automatic when being assemblied in the hydraulic system with multiple executive components
Ground automatically switches on volumetric void fraction mode and Ioad-sensing control mode according to executive component to be single or multiple.So as to
So that hydraulic system is more efficient, it is more energy saving.When in the hydraulic system that it is applied to multiple executive components, it can guarantee
Movement between multiple executing agencies is not interfere with each other.Meanwhile under Ioad-sensing control mode, do not need to electromagnetic proportional valve into
Row power supply can effectively extend electromagnetism to not only be avoided that the problem of electrical component aging because of caused by long-term power supply accelerates
The service life of proportioning valve, and then the service life of variable pump can be extended, and can also realize under Ioad-sensing control mode
Energy-efficient purpose.
The present invention also provides a kind of hydraulic control system with variable pump, which can only have one in hydraulic system
It is had higher efficiency when executive component, can effectively save energy consumption, moreover it is possible in Ioad-sensing control mode, guarantee multiple execution
Element is not interfere with each other mutually, meanwhile, it is not necessary to be carried out to electromagnetic proportional valve maximum for a long time under Ioad-sensing control mode
The supply of electric current, so as to there is the service life for extending electromagnetic proportional valve.
To achieve the goals above, the present invention also provides a kind of hydraulic control systems with variable pump, including variable
Pump, controller and at least two load execution units, the load execution unit is by hydraulic actuator and hydraulic actuator
The load-sensitive valve of connection and for controlling load-sensitive valve events control handle composition, the controller respectively with electromagnetism ratio
Example valve, control handle are connected with load-sensitive valve；
The B mouth of variable pump is connect by pipeline with the oil inlet for loading the load-sensitive valve in execution unit, two loads
The oil outlet of load-sensitive valve in execution unit is exported more afterwards by shuttle valve to the X mouth of variable pump, and the S mouth of variable pump passes through
Piping connection is to fuel tank.
The shell of the variable pump is equipped with the L mouth of leakage.
In the technical scheme, variable pump can be made to automatically switch on volume when only one executive component of system works
Under control model, load-sensitive valve is opened to maximum open, the discharge capacity of pump can be controlled by electromagnetic proportional valve, to control
The flow of system avoids the restriction loss problem in flow control valve adjustment process, the reaction of executive component can be made sensitiveer,
Energy utilization efficiency in the course of work is higher.When there are multiple executive components to work at the same time in system, variable pump can be made automatic
Ioad-sensing control mode is switched on, carries out the automatic tune of pumpage to perceive the signal of load feedback by flow control valve
Section, can guarantee that the movement between multiple executing agencies is not interfere with each other.Whole process does not need electromagnetic proportional valve energization, can not only keep away
Exempt from the problem of electromagnetic proportional valve causes aging to accelerate because of long-time energization, moreover it is possible to achieve the purpose that save electric energy.Meanwhile this is
System work carries out automatically in volumetric void fraction mode and Ioad-sensing control mode.Holding to which no matter the hydraulic system works
Product control model, or work can make the more efficient of system under Ioad-sensing control mode, more energy efficient.
Detailed description of the invention
Fig. 1 is the hydraulic schematic diagram for being not provided with the variable pump of constant-pressure control valve in the present invention in embodiment 1；
Fig. 2 is the hydraulic schematic diagram of the variable pump in the present invention in embodiment 1 equipped with constant-pressure control valve；
Fig. 3 is the hydraulic schematic diagram for being not provided with the variable pump of constant-pressure control valve in the present invention in embodiment 2；
Fig. 4 is the hydraulic schematic diagram of the variable pump in the present invention in embodiment 2 equipped with constant-pressure control valve；
Fig. 5 is the hydraulic schematic diagram of the hydraulic control system with variable pump in the present invention；
Fig. 6 is that the hydraulic control system with variable pump in the present invention works under volumetric void fraction mode in balance position
Hydraulic schematic diagram when setting；
Fig. 7 is becoming larger in the present invention with hydraulic control system work discharge capacity under volumetric void fraction mode of variable pump
Hydraulic schematic diagram；
Fig. 8 is becoming smaller in the present invention with hydraulic control system work discharge capacity under volumetric void fraction mode of variable pump
Hydraulic schematic diagram；
Fig. 9 is that the hydraulic control system with variable pump in the present invention works under Ioad-sensing control mode in flat
Hydraulic schematic diagram when weighing apparatus position；
Figure 10 is hydraulic control system work discharge capacity under Ioad-sensing control mode with variable pump in the present invention
The hydraulic schematic diagram to become larger；
Figure 11 is hydraulic control system work discharge capacity under Ioad-sensing control mode with variable pump in the present invention
The hydraulic schematic diagram to become smaller.
In figure: 1, pumping ontology；2, swash plate；3, reset spring；4, Variable Control oil cylinder；5, feedback rod；6, electromagnetic proportional valve；
7, switching valve；8, flow control valve；9, shell；10, constant-pressure control valve；11, hydraulic actuator, 12, load-sensitive valve, 13,
Shuttle valve, 14, controller, 15, variable pump, 16, control handle.
Specific embodiment
Below with reference to embodiment, the invention will be further described.
Embodiment 1:
As shown in Figure 1 and Figure 2, the program provides a kind of variable pump and a kind of hydraulic control system with variable pump.
A kind of variable pump: pump ontology 1, Variable Control oil cylinder 4,6 and of electromagnetic proportional valve including shell 9, in shell 9
Flow control valve 8；Reset spring 3 is arranged outside piston rod in the rod chamber of Variable Control oil cylinder 4, Variable Control oil cylinder 4
Piston rod end is connect with an end of the swash plate 2 in pump ontology 1, and the piston rod end of Variable Control oil cylinder 4 also passes through instead
Feedback bar 5 is connected with the valve pocket of the electromagnetic proportional valve 6；Electromagnetic proportional valve 6 work at left position, P mouthful with B mouthful connect, A mouthfuls and
T mouthfuls of connections, at right position, P mouthfuls are preferably 3-position 4-way electricity with A mouthfuls of connections, T mouthfuls and B mouthfuls connections, electromagnetic proportional valve 6 for work
Magnetic reversal valve, connecting node between the P mouth of electromagnetic proportional valve 6 and the P mouth of flow control valve 8 is by piping connection to pumping ontology
1 oil outlet；The left position control mouth of flow control valve 8 is by piping connection to its P mouthfuls；The shell 9, which is equipped with, passes through pipeline
Be connected to pump ontology 1 oil outlet B mouth, by piping connection to pump 1 oil inlet of ontology S mouth, pass through piping connection to flow
The X mouth of the spring cavity of control valve 8；It further include switching valve 7, the connecting node between electromagnetic proportional valve 6 and flow control valve 8 is also
It is connect by pipeline with the rod chamber of Variable Control oil cylinder 4；The A mouth of electromagnetic proportional valve 6 and B mouthful pass through piping connection to cutting respectively
Change the P mouth and left position control mouth of valve 7；The T mouth that the A mouth of flow control valve 8 passes through piping connection to switching valve 7；The A of switching valve 7
The rodless cavity that mouth passes through piping connection to Variable Control oil cylinder 4.
It further include the constant-pressure control valve 10 between the A mouth for being serially connected in flow control valve 8 and the T mouth of switching valve 7, specific:
The T mouth of constant-pressure control valve 10 is connect with the A of flow control valve 8 mouth, and the A mouth of constant-pressure control valve 10 is connect with the T of switching valve 7 mouth,
Connecting node of the P mouth and its left position control mouth of constant-pressure control valve 10 between electromagnetic proportional valve 6 and flow control valve 8 connects
It connects.
As shown in figure 5, a kind of hydraulic control system with variable pump: including variable pump 15, controller 14 and at least two
A load execution unit, the load-sensitive that the load execution unit is connected by hydraulic actuator with to your hydraulic actuator
Valve group is at the controller 14 also controls connection electromagnetic proportional valve 6 and load-sensitive valve 12；The B mouth of variable pump 15 passes through pipeline
It is connect with the oil inlet of the load-sensitive valve 12 in load execution unit, the load execution unit in two load execution units
Oil outlet is exported more afterwards by shuttle valve 13 to the X mouth of variable pump 15, and the S mouth of variable pump 15 passes through piping connection to fuel tank.Institute
The shell 9 for stating variable pump 15 is equipped with the L mouth for passing through piping connection between fuel tank of leakage.In variable pump 15 in Fig. 5
Portion's structure is that the structure of the variable pump in the present embodiment is for convenience's sake omitted the internal structure of variable pump 15.
Embodiment 2:
As shown in Figure 3, Figure 4, the program provides a kind of variable pump and a kind of hydraulic control system with variable pump.
A kind of variable pump: different from embodiment 1 is only that, the work of electromagnetic proportional valve 6 is at left position in the present embodiment, T
Mouth and A mouthfuls of connections, at right position, P mouthfuls are connected with A mouthfuls for work, the preferably 3-position-3-way solenoid directional control valve of electromagnetic proportional valve 6,
Electromagnetic proportional valve 6 is only connect by its A mouthfuls with switching valve 7；Switching valve 7 is solenoid directional control valve.
As shown in figure 5, a kind of hydraulic control system with variable pump: in addition to variable pump 15 internal structure change and
Switching valve 7 connects outside controller 14, and one of rest part and embodiment 1 use the technology of the hydraulic control system of variable pump
Scheme is identical.15 internal structure of variable pump in Fig. 5 is that the structure of the variable pump in the present embodiment will become for convenience's sake
The internal structure of amount pump 15 is omitted.
Illustrate the working principle of the invention based on embodiment 1 below:
When the setting pressure of constant-pressure control valve 10 is not achieved in system pressure, work of the constant-pressure control valve 10 in its right position spring
Right position is always worked under, A mouthfuls and T mouthfuls in an ON state, and P mouthfuls in an off state.
Controller 14 detects the action situation of the control handle 16 in each load execution unit, controls when operator operates
Handle 16 processed is come when controlling the movement of corresponding hydraulic actuator 11, the corresponding handle 16 that controls can issue a movement electric signal
To controller 14, controller 14 judges to have control handle 16 movement or be had according to the movement electric signal quantity received
Multiple control handles 16 act, and still should work in load-sensitive to differentiate that hydraulic system should work in volumetric void fraction mode
Control model.When only one control 16 sending of handle movement electric signal is to controller 14, the work of 14 control system of controller
In volumetric void fraction mode, when there is multiple 16 sending of control handle movement electric signals to controller 14,14 control system of controller
Work is in Ioad-sensing control mode.
One, when system work is at volumetric void fraction mode (electric proportional control mode).Only has executing agency's work
When, the displacement size of pump and the control electric current of electromagnetic proportional valve 6 are directly proportional.It is not acted as shown in fig. 6, other are omitted in figure
Executive component and associated loop.Controller 14 sends signal to corresponding load-sensitive valve.Controller 14 gives load-sensitive valve
12 with maximum controlling current, the valve valve port standard-sized sheet.At this point, pressure-compensated valve built in load-sensitive valve 12 also standard-sized sheet, therefore it is entire
Load-sensitive valve 12 only plays direction controlling, controls the expanding-contracting action of hydraulic actuator (hydraulic cylinder) 11, no throttling action,
Pressure loss very little.Because the front and back pressure loss of load-sensitive valve 12 is small, the pressure and load feedback pressure of pump discharge
Very close to, therefore, the flow control valve 8 of pump works in right position always under the action of the spring of right side, i.e. A to the T mouth standard-sized sheet of the valve,
P to A mouthfuls completely close.The movement speed of hydraulic actuator (hydraulic cylinder) 11 is only dependent upon the stream by load-sensitive valve 12
Amount, that is, the output flow pumped, that is, the displacement size pumped.The displacement size of pump is exported by controller 14 to electromagnetic proportional valve 6
Electric current determine.When system steady operation, 6 steady operation of electromagnetic proportional valve is under equilbrium position.Specific multivariable process is as follows:
1) change procedure that discharge capacity becomes larger, as shown in Figure 6 and Figure 7.Electromagnetic proportional valve 6 obtains current signal and becomes larger,
The power of electromagnet increases, and spool overcomes the elastic force of spring to be pushed to the right, and electromagnetic proportional valve 6 gradually works in left position, the P mouth of valve
It is progressively closed off with A mouthfuls, B mouthfuls are closed with T mouthfuls, and P mouthfuls are connected with B mouthfuls, and T mouthfuls are gradually connected to A mouthfuls, the P mouth oil inlet of electromagnetic proportional valve 6
The left position control mouth of switching valve 7 is supplied by B mouthfuls, the spool of switching valve 7 is gradually pushed to the right, and switching valve 7 gradually works
Left position, A mouthfuls are gradually turned on P mouthfuls, and T mouthfuls progressively close off with A mouthfuls.Part oil liquid in 4 rodless cavity of Variable Control oil cylinder passes through
A to the P mouth of switching valve 7 flows out, and using the A mouth of solenoid directional control valve 6 and T mouthfuls, flows into the shell 9 of pump, finally, returning through L mouthfuls
Fuel tank.Variable Control oil cylinder 4 moves right under the action of left side reset 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 that the valve pocket for dragging electromagnetic proportional valve 6 moves right,
Therefore the P mouth of electromagnetic proportional valve 6 is gradually turned down to B mouthfuls, until Variable Control oil cylinder 4 is stablized in a fixed position, solenoid-operated proportional
Valve 6 reaches new equilbrium position.At this point, the discharge capacity of pump also just stabilizes.Here it is the discharge capacity of pump with control signal reduce and
The process of increase.
2) change procedure that discharge capacity becomes smaller, as shown in Figure 6 and Figure 8.When the output of controller 14 is to the electric current of electromagnetic proportional valve 6
When reduction, the power of electromagnet reduces, and spool moves downward under the action of the spring of right side, the spool of electromagnetic proportional valve 6 gradually to
It moves to left, close to right position, the access between P mouthfuls and B mouthfuls is gradually turned down for work, and P mouthfuls are gradually connected to A mouthfuls, a left side for switching valve 7
Position control mouth still cannot let out load, and switching valve 7 still works in left position, and P mouthfuls are still connected to A mouthfuls.The high pressure oil of pump discharge
Liquid passes through the access between P mouthfuls to A mouthfuls in electromagnetic proportional valve 6, the P mouth again through switching valve 7 to the access entering variable between A mouthfuls
Control the cavity on 4 right side of oil cylinder.4 compression reseting spring 3 of Variable Control oil cylinder is moved to the left, and the discharge capacity of pump is gradually reduced.With this
Meanwhile feedback rod 5 is also moved to the left under the drive of Variable Control oil cylinder 4, so that the valve pocket for dragging electromagnetic proportional valve 6 is transported to the left
It is dynamic, therefore, the B mouth of electromagnetic proportional valve 6 is gradually turned on to P mouthfuls, until Variable Control oil cylinder 4 is stablized in a fixed position, electromagnetism
Proportioning valve 6 reaches new equilbrium position.At this point, the discharge capacity of pump also just stabilizes.Here it is the discharge capacity of pump as control signal increases
Reduced process greatly.
Two, load-sensitive throttling control model: when there is the work of multiple executive components in hydraulic system, as shown in figure 9, figure
Two hydraulic cylinders are only depicted in 9 as signal, supply of the controller 14 to 6 turn-off current of electromagnetic proportional valve makes spring masterpiece
For the spool of electromagnetic proportional valve 6, guarantee 6 steady operation of electromagnetic proportional valve when piston is at an arbitrary position in Variable Control oil cylinder 4
In right position.To fuel tank, therefore the left position control mouth of switching valve 7 passes through the oil communication between the B mouth of electromagnetic proportional valve 6 and T mouthfuls
Switching valve 7 always works in right position on the right side of it under the action of spring, A mouthfuls are connected with T mouthfuls, P mouthfuls of shutdowns.It is born under the mode
The pressure signal of load relatively and obtains maximum pressure signal by shuttle valve 13, and is existed by the X mouth feedback effect on the shell 9 of pump
The right side of flow control valve 8.When system steady operation, the highest load pressure on 8 right side of pressure and flow control valve of pump discharge
It balances each other with spring force, 8 steady operation of flow control valve balances the load under middle position, in the displacement size and system of pump
The total open area of sensitive valve 12 is directly proportional.System is load-sensitive throttling control at this time, and specific multivariable process is as follows:
A, the change procedure that discharge capacity becomes larger, as shown in Figure 9 and Figure 10.When load-sensitive valves 12 one or more in system
When control signal becomes larger, opening area increases.It loads and does not change at this time, therefore the active force on 8 right side of flow control valve
No change has taken place.The opening area of valve increases and the flow of pump is there is no changing, therefore its pressure loss becomes smaller, therefore pump discharge
Pressure reduction.The spool of flow control valve 8 moves downward under the action of the resultant force of right side, and flow control valve 8 gradually works
The P mouth of right position, valve is progressively closed off with A mouthfuls, and A mouthfuls are gradually opened with T mouthfuls.In this way, the portion in the cavity on 4 right side of Variable Control oil cylinder
A to the T mouth for dividing oil liquid to pass through switching valve 7, then pass through A to the T mouth of flow control valve 8, the shell 9 of pump is flowed into, finally, through L mouthfuls
Oil return box.Variable Control oil cylinder 4 moves right under the action of left side reset spring 3, and the discharge capacity of pump becomes larger.It is same with this
When, the flow for pumping output increases, and is increased by the flow of load-sensitive valve, the pressure loss of valve port also increases, therefore pump discharge
Pressure gradually rise.The spool stress of flow control valve 8 gradually balances, and mobile towards equilbrium position, A to the T mouth of valve is gradually
It turns down, until Variable Control oil cylinder 4 is stablized a fixed position, flow control valve 8 reaches new equilbrium position.At this point, pump
Discharge capacity also just stabilize.Here it is the processes that the discharge capacity of pump increases with the increase of control signal.
B, the change procedure that discharge capacity becomes smaller, as shown in figures 9 and 11.When load-sensitive valves one or more in system
When control signal becomes smaller, opening area reduces.It loads and does not change at this time, therefore the active force on 8 right side of flow control valve
No change has taken place.The opening area of valve reduces and the flow of pump is there is no changing, therefore its pressure loss increases, therefore pump discharge
Pressure rise.The spool of flow control valve 8 moves right under the action of the outlet pressure of left pump, flow control valve 8 by
It gradually works in left position, the A mouth of valve is gradually opened with P mouthfuls, and T mouthfuls progressively close off with A mouthfuls.In the case where most extreme, P mouthfuls complete with A mouthfuls
It is opened completely without throttling, A mouthfuls only retain a very small gap with T mouthfuls and system is maintained to stablize.Meanwhile the high-voltage oil liquid of pump discharge is logical
P to the A mouth of overcurrent control valve 8 flows out, T to the A mouth by switching valve 7, and entering variable controls the cavity on 4 right side of oil cylinder.Become
Amount control 4 compression reseting spring 3 of oil cylinder is simultaneously moved to the left, and the discharge capacity of pump is gradually reduced.At the same time, the flow for pumping output subtracts
It is small, reduced by the flow of load-sensitive valve, the pressure loss of valve port also reduces, therefore the pressure of pump discharge gradually decreases.Stream
The spool stress of control valve 8 gradually balances, and mobile towards equilbrium position, P to the A mouth of valve gradually turns down, until Variable Control
Oil cylinder 4 is stablized a fixed position, and flow control valve 8 reaches new equilbrium position.At this point, the discharge capacity of pump also just stabilizes.
Here it is the discharge capacity of pump as control signal reduces and reduced process.
Under above-mentioned volumetric void fraction mode, due to there is no oil in whole process between switching valve 7 and flow control valve 8
Liquid stream is logical, is only the oil liquid circulation between switching valve 7 and electromagnetic proportional valve 6 to adjust the discharge capacity of pump, so for being connected on
Constant-pressure control valve 10 between switching valve 7 and flow control valve 8 can not carry out system under volumetric void fraction mode effective
Overpressure protection.
Since under Ioad-sensing control mode, the discharge capacity of pump is by the oil liquid between switching valve 7 and flow control valve 8
Circulation is to be adjusted, so constant-pressure control valve 10 being capable of effective protection Ioad-sensing control mode.Specifically, in load-sensitive
Under control model, when system overpressure, the oil liquid of pump discharge directly acts on the left position control mouth of constant-pressure control valve 10, and then pushes away
Move its spool to overcome the elastic force of spring and work in left position, at this moment, the P mouth of constant-pressure control valve 10 and A mouthfuls of connections, A mouthfuls disconnected with T mouthfuls
It opens, and under Ioad-sensing control mode, the work of switching valve 7 is connected right position, A mouthfuls with T mouthfuls, in this way, the high pressure of pump discharge
Oil by through constant-pressure control valve 10 P mouth and A mouthful, using the P mouth of switching valve and A mouthfuls of entering variables control oil cylinder 4 without bar
Chamber pushes the piston rod in Variable Control oil cylinder 4 to be moved to the left, and the discharge capacity of compression reseting spring 3, pump is gradually reduced.
For embodiment 2, under volumetric void fraction mode, switching valve 7 always it is electric, when discharge capacity becomes larger, electromagnetic proportional valve 6
Electricity becomes larger, and gradually works in left position, and P mouthfuls gradually turn off with A mouthfuls, and A mouthfuls are gradually turned on T mouthfuls, 7 work once electrified of valve
In left position, P mouthfuls are connected with A mouthfuls, and the part oil liquid in 4 rodless cavity of Variable Control oil cylinder is flowed out by A to the P mouth of switching valve 7,
Using the A mouth of solenoid directional control valve 6 and T mouthfuls, flow into the shell 9 of pump, finally, through L mouthfuls of oil return boxes.When discharge capacity becomes smaller, electromagnetism
Proportioning valve 6 electric must be gradually reduced, and gradually be worked in right position, T mouthfuls gradually turn off with A mouthfuls, and A mouthfuls are gradually turned on P mouthfuls, valve
In left position, P mouthfuls pass through between P mouthfuls to A mouthfuls in electromagnetic proportional valve 67 work once electrifieds with A mouthfuls of connections, the high-voltage oil liquid of pump discharge
Access, the P mouth again through switching valve 7 to 4 right side of access entering variable control oil cylinder between A mouthfuls cavity.In load-sensitive
Under control model, switching valve 7 powers off always, and A mouthfuls are connected always with T mouthfuls.6 whole process of solenoid-operated proportional proportioning valve must not be electric,
The principle that its discharge capacity becomes smaller and becomes larger is identical as embodiment 1.
Claims (6)
1. a kind of variable pump, including shell (9), pump ontology (1), the Variable Control oil cylinder (4), electromagnetism ratio being located in shell (9)
Example valve (6) and flow control valve (8)；Reset spring (3) are arranged outside piston rod in the rod chamber of Variable Control oil cylinder (4),
The piston rod end of Variable Control oil cylinder (4) is connect with an end of the swash plate (2) in pump ontology (1), Variable Control oil cylinder
(4) piston rod end also passes through feedback rod (5) and is connected with the valve pocket of the electromagnetic proportional valve (6)；Electromagnetic proportional valve (6)
Connecting node between P mouthfuls and the P mouth of flow control valve (8) passes through piping connection to the oil outlet for pumping ontology (1)；Flow control
The left position control mouth of valve (8) is by piping connection to its P mouthfuls；
The shell (9) be equipped with by piping connection to pump ontology (1) oil outlet B mouth, by piping connection to pump originally
The S mouth of body (1) oil inlet, by piping connection to flow control valve (8) spring cavity X mouth；
It is characterized by also including switching valve (7), and the connecting node between electromagnetic proportional valve (6) and flow control valve (8) is also logical
Pipeline is crossed to connect with the rod chamber of Variable Control oil cylinder (4)；The A mouth of electromagnetic proportional valve (6) passes through piping connection extremely respectively with B mouthfuls
The P mouth and left position control mouth of switching valve (7)；The T mouth that the A mouth of flow control valve (8) passes through piping connection to switching valve (7)；It cuts
The A mouth for changing valve (7) passes through the rodless cavity of piping connection to Variable Control oil cylinder (4)；
At left position, P mouthfuls are connected to B mouthfuls, and T mouthfuls are connected to A mouthfuls for the electromagnetic proportional valve (6) work, and work is close to right position
When, the access between P mouthfuls and B mouthfuls gradually becomes smaller, and P mouthfuls are gradually connected to A mouthfuls, and at right position, P mouthfuls are connected to A mouthfuls, T for work
Mouth is connected to B mouthfuls.
2. a kind of variable pump according to claim 1, which is characterized in that further include the A mouth for being serially connected in flow control valve (8)
Constant-pressure control valve (10) between the T mouth of switching valve (7), the P mouth and its left position control mouth of constant-pressure control valve (10) with electricity
Connecting node connection between magnetic proportioning valve (6) and flow control valve (8).
3. a kind of variable pump, including shell (9), pump ontology (1), the Variable Control oil cylinder (4), electromagnetism ratio being located in shell (9)
Example valve (6) and flow control valve (8)；Reset spring (3) are arranged outside piston rod in the rod chamber of Variable Control oil cylinder (4),
The piston rod end of Variable Control oil cylinder (4) is connect with an end of the swash plate (2) in pump ontology (1), Variable Control oil cylinder
(4) piston rod end also passes through feedback rod (5) and is connected with the valve pocket of the electromagnetic proportional valve (6)；Electromagnetic proportional valve (6)
Connecting node between P mouthfuls and the P mouth of flow control valve (8) passes through piping connection to the oil outlet for pumping ontology (1)；Flow control
The left position control mouth of valve (8) is by piping connection to its P mouthfuls；
The shell (9) be equipped with by piping connection to pump ontology (1) oil outlet B mouth, by piping connection to pump originally
The S mouth of body (1) oil inlet, by piping connection to flow control valve (8) spring cavity X mouth；
It is characterized by also including switching valve (7), and the connecting node between electromagnetic proportional valve (6) and flow control valve (8) is also logical
Pipeline is crossed to connect with the rod chamber of Variable Control oil cylinder (4)；The A mouth of electromagnetic proportional valve (6) passes through piping connection to switching valve (7)
P mouth；The T mouth that the A mouth of flow control valve (8) passes through piping connection to switching valve (7)；The A mouth of switching valve (7) is connected by pipeline
It is connected to the rodless cavity of Variable Control oil cylinder (4)；Switching valve (7) is solenoid directional control valve.
4. a kind of variable pump according to claim 3, which is characterized in that further include the A mouth for being serially connected in flow control valve (8)
Constant-pressure control valve (10) between the T mouth of switching valve (7), the P mouth and its left position control mouth of constant-pressure control valve (10) with electricity
Connecting node connection between magnetic proportioning valve (6) and flow control valve (8).
5. a kind of hydraulic control system with variable pump, including variable pump (15), controller (14) and at least two loads are held
Row unit, the load execution unit is by hydraulic actuator (11), the load-sensitive valve connecting with hydraulic actuator (11)
(12) with for control load-sensitive valve (12) movement control handle (16) composition, the controller (14) respectively with electromagnetism ratio
Example valve (6), control handle (16) and load-sensitive valve (12) connection；
It is characterized in that, the variable pump (15) uses the described in any item variable pumps of Claims 1-4, the B of variable pump (15)
Mouth is connect by pipeline with the oil inlet for loading the load-sensitive valve (12) in execution unit, negative in two load execution units
The oil outlet for carrying sensitive valve (12) is exported more afterwards by shuttle valve (13) to the X mouth of variable pump (15), and the S mouth of variable pump (15) is logical
Piping connection is crossed to fuel tank.
6. a kind of hydraulic control system with variable pump according to claim 5, which is characterized in that the variable pump
(15) shell (9) is equipped with the L mouth of leakage.
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| CN108343649B (en) * | 2018-04-14 | 2024-02-06 | 华东交通大学 | Load port/displacement independent control system based on single-side outlet throttle control valve group |
| CN109538456B (en) * | 2018-09-18 | 2023-10-24 | 浙江大学 | Electro-hydraulic proportional valve control pump adopting proportional valve and miniature high-speed digital valve for combined control and control method |
| 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 |
| CN109882462B (en) * | 2019-01-11 | 2020-08-28 | 徐州工业职业技术学院 | Hydraulic control proportion and load sensitivity fusion variable pump and hydraulic control intelligent flow distribution system |
| CN113915190B (en) * | 2021-10-29 | 2022-07-05 | 上海三一重机股份有限公司 | Quantitative and fixed variable switchable hydraulic system, control method thereof and working machine |
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| Publication number | Priority date | Publication date | Assignee | Title |
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| DE10247665B4 (en) * | 2002-10-11 | 2006-05-11 | Brueninghaus Hydromatik Gmbh | Regulating device and valve block for a control device |
| US20060198736A1 (en) * | 2005-03-01 | 2006-09-07 | Caterpillar Inc. | Pump control system for variable displacement pump |
| DE102008054876A1 (en) * | 2008-12-18 | 2010-07-01 | Deere & Company, Moline | hydraulic system |
| CN203420858U (en) * | 2013-07-19 | 2014-02-05 | 佛山市科达液压机械有限公司 | Novel hydraulic pump constant-flow output and standby state control structure |
| 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 |
| CN204984843U (en) * | 2015-07-30 | 2016-01-20 | 徐州重型机械有限公司 | Plunger pump that possesses energy recuperation function |
| CN105156391B (en) * | 2015-09-17 | 2017-11-14 | 徐州工业职业技术学院 | A kind of composite variable pump and the hydraulic control system with composite variable pump |
| CN205478600U (en) * | 2016-01-13 | 2016-08-17 | 潍柴动力股份有限公司 | Constant voltage variable pump |
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