CN106640798A - Electro-hydraulic control mechanism capable of adjusting pressure and unloading - Google Patents
Electro-hydraulic control mechanism capable of adjusting pressure and unloading Download PDFInfo
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- CN106640798A CN106640798A CN201611058685.0A CN201611058685A CN106640798A CN 106640798 A CN106640798 A CN 106640798A CN 201611058685 A CN201611058685 A CN 201611058685A CN 106640798 A CN106640798 A CN 106640798A
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- pressure
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- push rod
- oil
- hydraulic oil
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Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B11/00—Servomotor systems without provision for follow-up action; Circuits therefor
- F15B11/08—Servomotor systems without provision for follow-up action; Circuits therefor with only one servomotor
-
- 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
-
- 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
- F15B13/025—Pressure reducing valves
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- Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Fluid Mechanics (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Control Of Positive-Displacement Pumps (AREA)
Abstract
The invention discloses an electro-hydraulic control mechanism capable of adjusting pressure and unloading. The control mechanism comprises a first servo unit, a fixed pressure reducing valve, an unloading unit and a pair of electromagnets. The fixed pressure reducing valve generates a pressure difference, thus generating a pressure signal which is converted into a mechanical signal of the first servo unit to control the displacement of a trunk stroke variable displacement pump. According to the electro-hydraulic control mechanism capable of adjusting pressure and unloading, because of the arrangement of the fixed pressure reducing valve, the servo relationship between the system pressure and the trunk stroke variable displacement pump is established, and the trunk piston variable displacement can be adjusted based on the pressure of the piston system. Moreover, the unloading unit can make the whole hydraulic system operate safely, and the electromagnets can enhance the sensitivity and range of the pressure adjustment.
Description
Technical field
The present invention relates to field of electromechanical technology, more particularly to a kind of pressure-adjustable and the electrohydraulic controlling mechanism of off-load.
Background technology
In fluid power system and hydraulic control system (both might as well be referred to as hydraulic system), system pressure or work are pressed
The size of power is by multiple units or system co- controlling and determines, for example, generally, the discharge capacity of such as variable pump is not varied widely
When, the system pressure of hydraulic system is mainly limited by overflow valve, when system pressure exceedes the control pressure of overflow valve, overflow valve
The system pressure of setting is revert to by making pressure to fuel tank draining, and the fluctuation for passing through overflow valve control system pressure is that have
Limit, in other words, when the discharge capacity of variable pump is varied widely, such as the discharge capacity of variable pump becomes big, even if overflow valve is constantly let out
Oil will not also reduce system pressure to setting pressure, and so overflow valve damaging.Accordingly, it would be desirable to regulated variable pump
Discharge capacity.
Various regulations are occurred in that in prior art or claims to change mechanism and the method for variable pumpage, e.g., plunger variable pump
Discharge capacity can be changed by changing the gradient of swash plate, the gradient of swash plate is provided by the servo piston regulation of connecting rod, specifically,
Servo piston is arranged in servo piston chamber, and connecting rod stretches out from the one end in servo piston chamber and changes swash plate gradient by flexible,
The within the chamber that servo piston chamber has connecting rod is provided with spring, draws hydraulic oil all the way from the oil-out of plunger variable pump and is passed through not
In having the chamber of piston rod, the stroke of connecting rod is changed by the hydraulic fluid pressure size, so as to change the gradient of swash plate, entered
And change the discharge capacity of plunger variable pump.However, this method can only be simple the discharge capacity for changing variable pump, can only be used in
Know or discharge capacity needed for precognition system under, for the substantially discharge capacity of regulated variable pump before using variable pump, the method is simultaneously
Discharge capacity not according to system pressure real-time regulation variable pump so that the discharge capacity of variable pump meets operating pressure requirement, in other words this
The method of kind can only make the discharge capacity after regulation generally conform to system requirements, and precision is poor.
The method that another kind of pilot plunger variable pump is have also appeared in prior art, on the one hand, obtained by angular transducer
The gradient of the swash plate of variable pump is obtained, steepness signals are passed to electromagnetic controller, had in electromagnetic controller by the angular transducer
With the one-to-one electric signal of gradient；On the other hand, the hydraulic pressure oil two-way of system respectively enters two chambers split by piston
In, the connecting rod on the piston is by moving the gradient for changing swash plate with piston；When controller needs to change the row of variable pump
During amount, controller changes the pressure of two-way hydraulic oil, so as to change the displacement of piston, and then changes the discharge capacity of variable pump.So
And, the method simply makes the gradient of swash plate of variable pump be associated with the electric signal of controller, and the pressure of hydraulic system is
As the simple power for changing piston transverse shifting, and it is not associated with the discharge capacity of variable pump, so that this method
Can not be according to system pressure come the discharge capacity of regulated variable pump, so as to the discharge capacity after regulation can only be made to generally conform to system requirements, essence
Degree is poor.
The content of the invention
For above-mentioned technical problem present in prior art, The embodiment provides one kind is in real time according to being
The discharge capacity of the pressure signal regulated variable pump of system hydraulic oil feedback is so that system pressure meets the pressure-adjustable of predetermined pressure and off-load
Electrohydraulic controlling mechanism.
To solve above-mentioned technical problem, the technical solution used in the present invention is：
A kind of pressure-adjustable and the electrohydraulic controlling mechanism of off-load, for adjusting hydraulic pressure by changing the discharge capacity of plunger variable pump
The pressure of system, including：
First servo unit, it includes being formed with the first housing of first chamber, is arranged in the first chamber, and will
The first chamber is divided into the first servo piston of the first left chamber and the first right chamber room；It is provided with the first left chamber room
For pushing against the first spring of first servo piston, on first servo piston the first push rod is provided with；
Second servo unit, it includes being formed with the second housing of second chamber, is arranged in the second chamber, and will
The second chamber be divided into the second servo piston of the second left chamber and the second right chamber room and with second servo piston
Second spring is respectively provided with the second push rod being fixedly connected, second left chamber and the second right chamber room, described second pushes away
Bar is used to drive the swash plate, and：When second push rod is moved to left, the gradient of the swash plate reduces, second push rod
When moving to right, the gradient increase of the swash plate；
Two control units, two described control units are arranged side by side and include being formed with the valve body of valve pocket and be arranged on institute
The valve element in valve pocket is stated, first push rod is located between the valve element and is connected with valve element described in two simultaneously, and system liquid
Force feed by one of described control unit to second left chamber fuel feeding, by another described control unit to described
Second right chamber room fuel feeding, so that：
When first push rod is moved to the left, first push rod drives valve element described in two simultaneously mobile so as to be passed through institute
The pressure for stating the hydraulic oil in the second right chamber room is more than the pressure of the hydraulic oil in the second left chamber room, when first push rod
When moving right, first push rod drives valve element described in two simultaneously mobile so that the hydraulic oil being passed through in the second right chamber room
Pressure less than the hydraulic oil in the second left chamber room pressure.
The pressure-adjustable and the electrohydraulic controlling mechanism of off-load also include
Fixed pressure reducing valve, system hydraulic oil is divided into two-way and each leads into first left chamber and the first right chamber room,
The fixed pressure reducing valve is arranged on and is passed through on the pipeline of first left chamber, so that the hydraulic oil in the first left chamber room
Pressure keeps constant, so that the pressure of the hydraulic oil in the pressure of the hydraulic oil in the first right chamber room and the first left chamber room
The difference of power increases with the increase of system pressure；
Off-load unit, it is used for when system pressure is beyond default peak, forces the swash plate of the plunger variable pump
Gradient is zeroed；
The relative electromagnet pair of homopolarity, it is arranged in the first left chamber room, and the electromagnet is to by changing thereon
Electric current is changing the electromagnetic push to first servo piston.
Preferably, two described control units are proportional reversing valve, the oil-out of proportional reversing valve described in two respectively with institute
The second left chamber and the second right chamber are stated, oil-in is connected with system hydraulic oil, and when valve element described in two is with described
When first push rod level is moved to the left, the oil-out pressure connected with second left chamber is less than and connects with the second right chamber room
Logical oil-out pressure；When valve element described in two moves right with the first push rod level, connect with second left chamber
Oil-out pressure more than oil-out pressure with the described second right chamber.
Preferably, the off-load unit is connected for oil-in with system pipeline, oil-out and the described second right chamber
Individual event valve, the check valve setting pressure more than hydraulic system rated pressure.
Compared with prior art, embodiments of the invention are provided pressure-adjustable and the electrohydraulic controlling mechanism of off-load it is beneficial
Effect is：The present invention is due to being provided with fixed pressure reducing valve so that system pressure establishes servo relation with plunger variable pump, so as to
Plunger variable is set to be adjusted according to column system pressure.Additionally, off-load unit can enable the safe work of whole hydraulic system
Make, and electromagnet can improve pressure controlled sensitivity or pressure regulation spectrum, two control units can control the second servo
Second push rod of unit, makes being quick on the draw for the second push rod..
Description of the drawings
Fig. 1 is the structural representation of the electrohydraulic controlling mechanism of the pressure-adjustable of the present invention and off-load.
Specific embodiment
To make those skilled in the art be better understood from technical scheme, below in conjunction with the accompanying drawings and specific embodiment party
Formula elaborates to the present invention.
Pressure-adjustable of the invention and the electrohydraulic controlling mechanism purpose of off-load, technical scheme and advantage for convenience of explanation,
Before introducing the pressure-adjustable of the present invention and the electrohydraulic controlling mechanism of off-load, which kind of side introduces first in prior art is by
Which kind of situation is formula changing the main Ying Yu of discharge capacity and this kind of mode of variable pump in.
Variable pump of the prior art, particularly plunger variable pump 50 generally change change by changing the gradient of swash plate 51
The discharge capacity of amount pump, before variable pump is accessed into hydraulic system as power source, needs the flow according to hydraulic system to hydraulic oil
Require, system pressure requirements and operating pressure require to be adjusted the discharge capacity of variable pump, that is to say, that to the oblique of variable pump
The gradient of disk 51 is adjusted, so that the discharge capacity of variable pump generally conforms to the requirement of hydraulic system, so that variable pump accesses system
After system, the pressure remained steady of hydraulic system.
Under normal circumstances, the flow of the discharge capacity of variable pump and hydraulic system, system pressure and operating pressure are positive correlation
, that is to say, that in same hydraulic system, the discharge capacity of variable pump is bigger, the flow of hydraulic system, system pressure and work
Pressure is also bigger, otherwise less.After the discharge capacity of variable pump determines, the flow of hydraulic system, system pressure and work pressure
Power can substantially determine within the specific limits.However, the discharge capacity of variable pump have with the flow of hydraulic system, system pressure with
And operating pressure corresponding relation completely, for example, when the discharge capacity of variable pump is Xv/s, system pressure does not have and the discharge capacity
Unique corresponding one determines pressure, and system pressure now may fluctuate in interior change or title in a big way, and this fluctuation
May exceed system pressure allow scope, e.g., beyond system rated pressure (under the rated pressure, each unit of system
Device ability normal work).So that the discharge capacity of variable pump is incomplete with the flow of hydraulic system, system pressure and operating pressure
A corresponding critically important reason is：Each Hydraulic Elements draining, oil leak, and Hydraulic Elements are produced not to hydraulic oil in system
The change of evitable resistance and Hydraulic Elements it is aging etc..
And it is one by one to be all built upon the discharge capacity of variable pump and system parameters in prior art to the regulation of hydraulic system
What the situation of corresponding relation was carried out, for example, it is intended to for system pressure to be adjusted to a certain pressure value, only need to be by the swash plate 51 of variable pump
Pitch adjustment is to a certain discharge capacity with the unique corresponding variable pump of the pressure value.That is, only needing swash plate 51 individually
It is adjusted to a certain predetermined slant.
For example, the gradient of swash plate 51 is provided by the servo piston regulation of connecting rod, and specifically, servo piston is arranged on to be watched
In taking plunger shaft, connecting rod stretches out from the one end in servo piston chamber and changes the gradient of swash plate 51 by flexible, and servo piston chamber has
The within the chamber of connecting rod is provided with spring, draws hydraulic oil all the way from the oil-out of plunger variable pump 50 and is passed through the chamber without piston rod
In room, the stroke of connecting rod is changed by the hydraulic fluid pressure size, so as to change the gradient of swash plate 51, and then change plunger
The discharge capacity of variable pump 50.
Again for example, on the one hand, the gradient of the swash plate 51 of variable pump is obtained by angular transducer, the angular transducer will be oblique
To electromagnetic controller, electromagnetic controller is interior to be had and gradient one-to-one electric signal degree signal transmission；On the other hand, system
Hydraulic pressure oil two-way is respectively enterd in two chambers split by piston, and the connecting rod on the piston with piston by moving for changing
The gradient of swash plate 51；When controller needs to change the discharge capacity of variable pump, controller changes the pressure of two-way hydraulic oil, so as to change
Become the displacement of piston, and then change the discharge capacity of variable pump.
Above two method is built upon situation of the discharge capacity of variable pump with system parameters for one-to-one relationship and enters
It is capable, however, from the foregoing, the discharge capacity of variable pump is completely corresponding because many factors are not constituted with system parameters closes
System, so that the discharge capacity for changing variable pump that this method can only be simple, can only be used in and know or predicting system
Needed for system under discharge capacity, the substantially discharge capacity of regulated variable pump before using variable pump.
In above-mentioned method of adjustment in the prior art, system hydraulic oil is intended only as changing piston transverse shifting merely
Power, and be not associated with the discharge capacity of variable pump.Whole regulation process is relied on completely controller and feeds back to controller
The gradient of swash plate 51 carry out, not according to hydraulic system pressure real-time regulation, mutually isolate with hydraulic system.
One of above-mentioned control method is the drawbacks of bigger：Due to variable pump Long-Time Service, a certain gradient of its swash plate 51
Corresponding discharge capacity can change, so that the numerical value of controller memory storage produces deviation with the discharge capacity of variable pump, so that：
When controller sends a swash plate 51 to be adjusted to a certain gradient and make variable pump be adjusted to the instruction of corresponding discharge capacity, on variable pump
Although swash plate 51 be adjusted to predetermined slant, discharge capacity is not up to pre- fixed displacement.
The degree of regulation for carrying out the method for regulating system pressure above by the discharge capacity of regulated variable pump not enough or does not reach tune
Saving the reason for being expected is：The discharge capacity of variable pump is not adjusted according to system pressure, and simply simple regulated variable
The discharge capacity of pump.The pressure-adjustable of the present invention and the electrohydraulic controlling mechanism purpose of off-load are to set up the pressure and variable pump of hydraulic system
The relation of discharge capacity, that is, setting up makes the discharge capacity regulation of variable pump be carried out according to system pressure, and energy again after the discharge capacity of variable pump is adjusted
Enough affect the servo relation of system pressure.
As shown in figure 1, embodiment of the invention discloses that a kind of pressure-adjustable and the electrohydraulic controlling mechanism of off-load, for passing through
Change electrohydraulic controlling mechanism of the discharge capacity of plunger variable pump 50 to adjust the pressure of hydraulic system, the pressure-adjustable and off-load specifically to wrap
Include：First servo unit 10, the second servo unit 20, two control units 30 and fixed pressure reducing valve 40.
First servo unit 10 includes being formed with the first housing of first chamber, is arranged in first chamber, and by first
Chamber is divided into the first servo piston 13 of the first left chamber 11 and the first right chamber room 12；Be provided with first left chamber 11 for
The first spring 15 of the first servo piston 13 is pushed against, the first push rod 14 is provided with the first servo piston 13；
Second servo unit 20 includes being formed with the second housing of second chamber, is arranged in second chamber, and by second
Chamber is divided into the second servo piston 23 of the second left chamber 21 and the second right chamber room 22 and fixes with the second servo piston 23
Second spring 25 is respectively provided with second push rod 24 of connection, the second left chamber 21 and the second right chamber room 22, the second push rod 24 is used for
Swash plate 51 is driven, and：When the second push rod 24 is moved to left, the gradient of swash plate 51 reduces, when the second push rod 24 is moved to right, swash plate 51
Gradient increases；
Two control units 30 are arranged side by side and include the valve body for being formed with valve pocket and the valve element 31 being arranged in valve pocket,
First push rod 14 is located between valve element 31 and is connected with two valve elements 31 simultaneously, and system hydraulic oil is single by one of control
First 30 to second left chamber 21 fuel feeding, by another control unit 30 to the fuel feeding of the second right chamber room 22, so that：
When the first push rod 14 is moved to the left, the first push rod 14 drives two valve elements 31 simultaneously mobile so as to be passed through the second right chamber
More than the pressure of the hydraulic oil in the second left chamber 21, now, the second push rod 24 is moved to the left the pressure of the hydraulic oil in room 22,
So that the gradient of the swash plate 51 of plunger variable pump 50 reduces, so that the discharge capacity of plunger variable pump 50 reduces；When the first push rod 14
When moving right, the first push rod 14 drives two valve elements 31 simultaneously mobile so that the pressure of the hydraulic oil being passed through in the second right chamber room 22
Less than the pressure of the hydraulic oil in the second left chamber 21, now, the second push rod 24 moves right so that plunger variable pump 50 it is oblique
The gradient increase of disk 51, so that the discharge capacity increase of plunger variable pump 50.
Pressure-adjustable and the electrohydraulic controlling mechanism of off-load also include
Fixed pressure reducing valve 40, system hydraulic oil is divided into two-way and each leads into the first left chamber 11 and the first right chamber room 12, fixed
Value pressure-reducing valve 40 is arranged on and is passed through on the pipeline of the first left chamber 11, so that the pressure of the hydraulic oil in the first left chamber 11 keeps
It is constant, so that the difference of the pressure of the hydraulic oil in the pressure of the hydraulic oil in the first right chamber room 12 and the first left chamber 11 is with being
System pressure increase and increase.
Off-load unit, it is used for when system pressure is beyond default peak, forces the swash plate 51 of plunger variable pump 50
Gradient is zeroed；
To 16, it is arranged in the first left chamber 11 the relative electromagnet of homopolarity, and electromagnet is to 16 by changing electricity thereon
Flow to change the electromagnetic push to the first servo piston 13.
Thus, when system pressure increase is (because of some reasons, including the discharge capacity increase of plunger variable pump 50, control element
Hydraulic fluid port diminishes) when, the pressure increase of the hydraulic oil in the first right chamber room 12, and the pressure of the hydraulic oil in the first left chamber 11
Because receiving the control pressure of fixed pressure reducing valve 40 constant, so that the first servo piston 13 is moved to the left, the first servo piston 13
Movement causes the gradient of the swash plate 51 of plunger variable pump 50 to reduce；So as to the discharge capacity of plunger variable pump 50 reduces, plunger variable pump
50 discharge capacity offsets the system pressure of rising after reducing.When the first servo piston 13 moves right, the first servo piston 13 makes
Obtain the gradient increase of the swash plate 51 of plunger variable pump 50；Reduce when system pressure (because of some reasons, including plunger variable pump 50
Discharge capacity reduces, the hydraulic fluid port of control element becomes big etc.) when, the pressure of the hydraulic oil in the first right chamber room 12 reduces, and the first left chamber
The pressure of the hydraulic oil in room 11 because by the control pressure of fixed pressure reducing valve 40 it is constant so that the first servo piston 13 moves right
Dynamic, the movement of the first servo piston 13 causes the gradient of the swash plate 51 of plunger variable pump 50 to increase, so as to plunger variable pump 50
Discharge capacity increases, and the discharge capacity of plunger variable pump 50 increases the system pressure that post-compensation declines.
The pressure-adjustable of the present invention and the electrohydraulic controlling mechanism of off-load establish system pressure and the discharge capacity of plunger variable pump 50 it
Between relation so that system pressure is only adjusted by the change of the discharge capacity of plunger variable pump 50, so as to eliminate regulation shadow
The process of other Hydraulic Elements of acoustic system pressure, so that the process of regulation is simple and accurate.The process simply can be adjusted accurately
Section system pressure the reason for be：Although affecting the factor of system pressure a lot, system pressure can be become by changing plunger
The discharge capacity of amount pump 50 is changed and adjusts.
System pressure and the discharge capacity of plunger variable pump 50 that the pressure-adjustable of the present invention and the electrohydraulic controlling mechanism of off-load are set up
Between relation be servo relation, that is to say, that system pressure can in real time produce pressure signal, the pressure signal directly or
It is converted into mechanical signal and passes to plunger variable pump 50 so that the discharge capacity of plunger variable pump 50 changes, and the discharge capacity of plunger variable pump 50 changes
Become again can Real Time Effect system pressure so that system pressure reaches a numerical value that is constant and meeting system requirements.
The pressure-adjustable of the present invention and the electrohydraulic controlling mechanism of off-load change the row of plunger variable pump 50 according to system pressure
Amount, so that the system pressure after adjusting more conforms to pre-provisioning request.
The pressure-adjustable of the present invention and the electrohydraulic controlling mechanism of off-load can be according to system pressure pilot plunger variable pumps 50
Discharge capacity, and set up it is critical only that for system pressure and the servo relation of plunger variable pump 50：It is lead to the first left chamber 11
Fixed pressure reducing valve 40 is set on road under the overall leadership, and the fixed pressure reducing valve 40 is so that the pressure of the hydraulic oil in the first left chamber 11 is less than and is
System pressure and the definite value changed not change with system pressure, and the pressure of the hydraulic oil in the first right chamber room 12 is equal to system
Pressure, so that the pressure initiation of the hydraulic oil in the pressure of the hydraulic oil in the first right chamber room 12 and the first left chamber 11
Pressure differential, in predetermined pressure difference, (predetermined pressure difference is referred to：System pressure required for hydraulic system, i.e. rated pressure, with
The difference of the pressure of the hydraulic oil in one left chamber 11) under, the predetermined pressure difference, now, first are offset by the first spring 15
Servo piston 13 is remained stationary as, and when system pressure is above or below rated pressure, now, the first servo piston 13 is in pressure
It is moved in the presence of difference, so that there is gradient change by the movement of the first servo piston 13 in swash plate 51, so as to
Change the discharge capacity of plunger variable pump 50, and the change of this discharge capacity can make up just or the change of bucking-out system pressure, for example,
When system pressure increases, the first servo piston 13 causes the discharge capacity of plunger variable pump 50 to reduce, when system pressure reduces, first
Servo piston 13 causes the increase of the discharge capacity of plunger variable pump 50.
The fixed pressure reducing valve 40 of the pressure-adjustable of the present invention and the electrohydraulic controlling mechanism of off-load is the decisive of generation pressure differential
Element, and make system pressure that the condition exactly two ends of the first servo piston 13 under the decision of servo relation are produced with plunger variable pump 50
Generate pressure differential.
The fixed pressure reducing valve 40 of the pressure-adjustable of the present invention and the electrohydraulic controlling mechanism of off-load also determines the specified pressure of system
Power, that is to say, that on the premise of the coefficient of elasticity of the first spring 15 is certain, when fixed pressure reducing valve 40 sets predetermined value, be
System pressure also determines that reason is：When fixed pressure reducing valve 40 sets predetermined value as A, now, system pressure should be equal to
With the thrust that predetermined value is corresponding hydraulic fluid pressure (pressure of the hydraulic oil in the first left chamber 11) FA of A and the first spring 15
FB sums, otherwise the first servo piston 13 can be moved.That is, after the setting value of fixed pressure reducing valve 40 determines, system
Pressure can produce a pressure value corresponding with setting value, conversely, system can be made by adjusting the setting value of fixed pressure reducing valve 40
The satisfactory pressure value of pressure.Therefore, the fixed pressure reducing valve 40 of pressure-adjustable of the invention and the electrohydraulic controlling mechanism of off-load is gone back
Possesses the function of regulating system rated pressure.
The pressure-adjustable of the present invention and the electrohydraulic controlling mechanism of off-load are due to being provided with fixed pressure reducing valve 40 such that it is able to according to
System pressure is accurate and by the discharge capacity of adjustment plunger variable pump 50 repeatedly, so that system pressure regulation fast and accurately
To satisfactory rated pressure, the constant pressure of system pressure is maintained so as to alleviate overflow valve, improve the suitable of overflow valve
Use the life-span.
Above-mentioned electromagnet changes the pretightning force of the first spring 15 to 16 by changing electromagnetic push, so that first
Servo piston 13 changes per the hydraulic pressure increase and decrease amount required for Moving Unit displacement, if thus, the electromagnet is to 16
When magnetic repulsion increases, the pretightning force of the first spring 15 reduces, and then makes required for the Moving Unit displacement of the first servo piston 13
The increase and decrease amount of hydraulic pressure reduces, and unit hydraulic pressure is often increased and decreased in other words, and the displacement of the movement of the first servo piston 13 is bigger, from
And cause the first servo piston 13 to change more sensitive to hydraulic pressure, so as to improve the row of pilot plunger variable pump 50 indirectly
The sensitivity of amount；If the magnetic repulsion of the magnet pair reduces, the pretightning force increase of the first spring 15, and then make the first servo piston
The increase and decrease amount increase of the hydraulic pressure required for 13 Moving Unit displacements, often increases and decreases in other words unit hydraulic pressure, the first servo
The displacement of the movement of piston 13 is less, even if so that when the first servo piston 13 changes in larger pressure limit, the first servo
Piston 13 can also in forming range the indirectly discharge capacity of pilot plunger variable pump 50, so as to increased the regulation of system pressure
Scope.
Above-mentioned off-load unit is acted on：When system pressure increases to the peak of preset pressure because of certain reason
(within the peak, the components and parts of hydraulic system will not be damaged, and can send out more than the components and parts of the peak hydraulic system
It is raw to damage), off-load unit causes the gradient of the swash plate 51 of plunger variable pump 50 to be zeroed, so that the discharge capacity of plunger variable pump 50 is
Vanishing is carved, so that system pressure is reduced to zero at once, so as to timely and effectively protect including including plunger variable pump 50
Hydraulic system components and parts.
Preferably, off-load unit is connected for oil-in with system pipeline, the individual event that oil-out is connected with the second right chamber room 22
Valve, the setting pressure of check valve 60 is more than the rated pressure of hydraulic system.Thus, when system pressure because certain reason increases to pre-
If during the peak of pressure, now, system pressure has exceeded the setting pressure of check valve 60, and individual event valve is turned at once, system liquid
Force feed is directly entered the second right chamber room 22, promotes the second servo piston 23 to move to left to the leftmost side at once, makes plunger variable pump 50
The gradient of swash plate 51 is zeroed at once, so that plunger variable pump 50 dallies and not fuel feeding.
The above-mentioned feature of the second servo unit 20 is：By two second springs 25 the second servo piston 23 is caused the
Centering when hydraulic fluid pressure is equal in two left chamber 21 and the second right chamber room 22, because two control units 30 control respectively second
The pressure of the pressure oil in the right chamber room 22 of left chamber 21 and second, and the movement of valve element 31 in two control units 30 is pushed away with first
The mobile synchronization of bar 14, i.e. when the first push rod 14 is moved to left, valve element 31 is also moved to left, when valve element 31 is moved to left, the second right chamber room 22
The pressure of interior hydraulic oil increases, and the pressure of the hydraulic oil in the second left chamber 21 is less, so that the second push rod 24 is left
Move, when the first push rod 14 is moved to right, valve element 31 is also moved to right, when valve element 31 is moved to right, the pressure of the hydraulic oil in the second right chamber room 22
Power reduces, and the pressure of the hydraulic oil in the second left chamber 21 increases, so that the second push rod 24 is moved to right.So that first
The action that push rod 14 passes through the second push rod of indirect control 24 of two control unit 30, and then control the discharge capacity of plunger variable pump 50.On
State by two control unit 30 control two chambers hydraulic oil pressure controlling the displacement of the second push rod 24, control more smart
Really, and the second push rod 24 is because of hydraulic oil rigidly pushing and pressing (the compressibility very little of hydraulic oil), so as to the mobile response of the second push rod 24
It is sensitiveer, that is to say, that the sensitivity servo-actuated with the first push rod 14 of the second push rod 24 is higher.
In a preferred embodiment of the invention, two control units 30 are proportional reversing valve, two proportional reversing valves
Oil-out is connected respectively with the second left chamber 21 and the second right chamber room 22, and oil-in is connected with system hydraulic oil, and when two valve elements
31 with the level of the first push rod 14 when being moved to the left, and the oil-out pressure connected with the second left chamber 21 is less than and the second right chamber room 22
The oil-out pressure of connection；When two valve elements 31 move right with the level of the first push rod 14, with going out that the second left chamber 21 connects
Hydraulic fluid port pressure is more than the oil-out pressure connected with the second right chamber room 22.
Above example is only the exemplary embodiment of the present invention, is not used in the restriction present invention, protection scope of the present invention
It is defined by the claims.Those skilled in the art can make respectively in the essence and protection domain of the present invention to the present invention
Modification or equivalent are planted, this modification or equivalent also should be regarded as being within the scope of the present invention.
Claims (3)
1. a kind of pressure-adjustable and the electrohydraulic controlling mechanism of off-load, for adjusting hydraulic pressure system by changing the discharge capacity of plunger variable pump
The pressure of system, it is characterised in that include：
First servo unit, it includes being formed with the first housing of first chamber, is arranged in the first chamber, and will be described
First chamber is divided into the first servo piston of the first left chamber and the first right chamber room；Be provided with the first left chamber room for
The first spring of first servo piston is pushed against, on first servo piston the first push rod is provided with；
Second servo unit, it includes being formed with the second housing of second chamber, is arranged in the second chamber, and will be described
Second chamber is divided into the second servo piston of the second left chamber and the second right chamber room and fixes with second servo piston
Second push rod of connection, is respectively provided with second spring in second left chamber and the second right chamber room, second push rod is used
In the driving swash plate, and：When second push rod is moved to left, the gradient of the swash plate reduces, and second push rod is moved to right
When, the gradient increase of the swash plate；
Two control units, two described control units are arranged side by side and include being formed with the valve body of valve pocket and be arranged on the valve
Valve element in chamber, first push rod is located between the valve element and is connected with valve element described in two simultaneously, and system hydraulic oil
By one of described control unit to second left chamber fuel feeding, by another described control unit to described second
Right chamber room fuel feeding, so that：
When first push rod is moved to the left, first push rod drives valve element described in two simultaneously mobile so as to be passed through described the
The pressure of the hydraulic oil in two right chamber rooms more than the hydraulic oil in the second left chamber room pressure, when first push rod to the right
When mobile, first push rod drives valve element described in two simultaneously mobile so that the pressure of the hydraulic oil being passed through in the second right chamber room
Pressure of the power less than the hydraulic oil in the second left chamber room；
The pressure-adjustable and the electrohydraulic controlling mechanism of off-load also include
Fixed pressure reducing valve, system hydraulic oil is divided into two-way and each leads into first left chamber and the first right chamber room, described
Fixed pressure reducing valve is arranged on and is passed through on the pipeline of first left chamber, so that the pressure of the hydraulic oil in the first left chamber room
Keep constant, so that the pressure of the hydraulic oil in the pressure of the hydraulic oil in the first right chamber room and the first left chamber room
Difference increases with the increase of system pressure；
Off-load unit, it is used for when system pressure is beyond default peak, forces the gradient of the swash plate of the plunger variable pump
Zero；
The relative electromagnet pair of homopolarity, it is arranged in the first left chamber room, and the electromagnet is to by changing electric current thereon
To change the electromagnetic push to first servo piston.
2. pressure-adjustable according to claim 1 and the electrohydraulic controlling mechanism of off-load, it is characterised in that two described control units
Proportional reversing valve is, the oil-out of proportional reversing valve described in two connects respectively with second left chamber and the second right chamber room
Logical, oil-in is connected with system hydraulic oil, and when valve element described in two is moved to the left with the first push rod level, with described the
The oil-out pressure of two left chamber connection is less than the oil-out pressure with the described second right chamber；When valve element described in two is with institute
When stating the first push rod level and moving right, the oil-out pressure connected with second left chamber is more than and the second right chamber room
The oil-out pressure of connection.
3. pressure-adjustable according to claim 2 and the electrohydraulic controlling mechanism of off-load, it is characterised in that the off-load unit is
Oil-in is connected with system pipeline, the individual event valve of oil-out and the described second right chamber, the setting pressure of the check valve
More than the rated pressure of hydraulic system.
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| Application Number | Priority Date | Filing Date | Title |
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| CN201611058685.0A CN106640798B (en) | 2016-11-22 | 2016-11-22 | The electrohydraulic controlling mechanism of pressure-adjustable and off-load |
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| CN201611058685.0A CN106640798B (en) | 2016-11-22 | 2016-11-22 | The electrohydraulic controlling mechanism of pressure-adjustable and off-load |
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| CN106640798B CN106640798B (en) | 2019-05-31 |
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| CN201611058685.0A Expired - Fee Related CN106640798B (en) | 2016-11-22 | 2016-11-22 | The electrohydraulic controlling mechanism of pressure-adjustable and off-load |
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Cited By (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN107877877A (en) * | 2017-11-07 | 2018-04-06 | 佛山威明塑胶有限公司 | A kind of make-up machine for PVC artificial leather |
| CN108506261A (en) * | 2018-04-11 | 2018-09-07 | 王爱菊 | Pressure regulating method based on valve gear |
| CN109469594A (en) * | 2018-09-29 | 2019-03-15 | 北京航空航天大学 | Continuous voltage regulating electric-hydraulic proportion shaft orientation plunger variable pump for plane hydraulic system |
| CN110332112A (en) * | 2019-06-13 | 2019-10-15 | 江苏理工学院 | A kind of ratio differential pressure type variable vane pump |
Citations (13)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US3444689A (en) * | 1967-02-02 | 1969-05-20 | Weatherhead Co | Differential pressure compensator control |
| JPH0849659A (en) * | 1994-08-05 | 1996-02-20 | Hitachi Constr Mach Co Ltd | Hydraulic pump flow control device |
| US5809157A (en) * | 1996-04-09 | 1998-09-15 | Victor Lavrov | Electromagnetic linear drive |
| JP2002198218A (en) * | 2000-10-19 | 2002-07-12 | Genesis:Kk | Magnetic force actuator |
| CN1100208C (en) * | 1998-02-13 | 2003-01-29 | 沙厄-丹福丝股份有限公司 | Apparatus and method for ganging multiple open circuit pumps |
| US20040201441A1 (en) * | 2001-09-01 | 2004-10-14 | Ina-Schaeffler Kg | Electromagnetic regulating device |
| CN102900643A (en) * | 2011-07-29 | 2013-01-30 | 波克兰液压工业设备公司 | Hydraulic control circuit |
| DE102012012141A1 (en) * | 2012-06-20 | 2013-12-24 | Robert Bosch Gmbh | Hydrostatic axial piston machine for use as e.g. hydro pump in hybrid drive for driving vehicle, has feeding back device comprising torsion and/or spiral springs, which are directly or indirectly clamped between swash plate and adjuster |
| CN103486101A (en) * | 2013-09-29 | 2014-01-01 | 徐州重型机械有限公司 | Controlling method and device for improving response speed of hydraulic oil pump |
| CN203383788U (en) * | 2013-04-27 | 2014-01-08 | 王文雯 | Flywheel energy-saving hydraulic pumping unit |
| CN205225909U (en) * | 2015-11-04 | 2016-05-11 | 潍柴动力股份有限公司 | All -hydraulic travel drive system |
| CN205446237U (en) * | 2016-02-17 | 2016-08-10 | 潍柴动力股份有限公司 | Hydraulic pump control ware |
| CN105960493A (en) * | 2014-02-07 | 2016-09-21 | 卡特彼勒环球矿业有限责任公司 | Hydraulic control system and method |
-
2016
- 2016-11-22 CN CN201611058685.0A patent/CN106640798B/en not_active Expired - Fee Related
Patent Citations (13)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US3444689A (en) * | 1967-02-02 | 1969-05-20 | Weatherhead Co | Differential pressure compensator control |
| JPH0849659A (en) * | 1994-08-05 | 1996-02-20 | Hitachi Constr Mach Co Ltd | Hydraulic pump flow control device |
| US5809157A (en) * | 1996-04-09 | 1998-09-15 | Victor Lavrov | Electromagnetic linear drive |
| CN1100208C (en) * | 1998-02-13 | 2003-01-29 | 沙厄-丹福丝股份有限公司 | Apparatus and method for ganging multiple open circuit pumps |
| JP2002198218A (en) * | 2000-10-19 | 2002-07-12 | Genesis:Kk | Magnetic force actuator |
| US20040201441A1 (en) * | 2001-09-01 | 2004-10-14 | Ina-Schaeffler Kg | Electromagnetic regulating device |
| CN102900643A (en) * | 2011-07-29 | 2013-01-30 | 波克兰液压工业设备公司 | Hydraulic control circuit |
| DE102012012141A1 (en) * | 2012-06-20 | 2013-12-24 | Robert Bosch Gmbh | Hydrostatic axial piston machine for use as e.g. hydro pump in hybrid drive for driving vehicle, has feeding back device comprising torsion and/or spiral springs, which are directly or indirectly clamped between swash plate and adjuster |
| CN203383788U (en) * | 2013-04-27 | 2014-01-08 | 王文雯 | Flywheel energy-saving hydraulic pumping unit |
| CN103486101A (en) * | 2013-09-29 | 2014-01-01 | 徐州重型机械有限公司 | Controlling method and device for improving response speed of hydraulic oil pump |
| CN105960493A (en) * | 2014-02-07 | 2016-09-21 | 卡特彼勒环球矿业有限责任公司 | Hydraulic control system and method |
| CN205225909U (en) * | 2015-11-04 | 2016-05-11 | 潍柴动力股份有限公司 | All -hydraulic travel drive system |
| CN205446237U (en) * | 2016-02-17 | 2016-08-10 | 潍柴动力股份有限公司 | Hydraulic pump control ware |
Non-Patent Citations (1)
| Title |
|---|
| 吴晓明等: "《液压变量泵（马达）变量调节原理与应用》", 31 March 2012, 机械工业出版社 * |
Cited By (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN107877877A (en) * | 2017-11-07 | 2018-04-06 | 佛山威明塑胶有限公司 | A kind of make-up machine for PVC artificial leather |
| CN108506261A (en) * | 2018-04-11 | 2018-09-07 | 王爱菊 | Pressure regulating method based on valve gear |
| CN109469594A (en) * | 2018-09-29 | 2019-03-15 | 北京航空航天大学 | Continuous voltage regulating electric-hydraulic proportion shaft orientation plunger variable pump for plane hydraulic system |
| CN109469594B (en) * | 2018-09-29 | 2020-06-16 | 北京航空航天大学 | Continuous pressure regulating electro-hydraulic proportional axial plunger variable pump for aircraft hydraulic system |
| CN110332112A (en) * | 2019-06-13 | 2019-10-15 | 江苏理工学院 | A kind of ratio differential pressure type variable vane pump |
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Effective date of registration: 20190506 Address after: 211200 Shihuang Town Industrial Park, Lishui District, Nanjing City, Jiangsu Province Applicant after: Nanjing Huiqiang Machinery Equipment Co.,Ltd. Address before: 300000 Tianjin Hexi District Huanhu Zhonglu Binhu Building Negative Floor B150 Applicant before: TIANJIN HAIAN TECHNOLOGY CO.,LTD. |
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