CN106593969A - Electric hydraulic control mechanism - Google Patents
Electric hydraulic control mechanism Download PDFInfo
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- CN106593969A CN106593969A CN201611033967.5A CN201611033967A CN106593969A CN 106593969 A CN106593969 A CN 106593969A CN 201611033967 A CN201611033967 A CN 201611033967A CN 106593969 A CN106593969 A CN 106593969A
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- pressure
- chamber
- push rod
- hydraulic oil
- variable pump
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- 230000007246 mechanism Effects 0.000 title claims abstract description 28
- 239000010720 hydraulic oil Substances 0.000 claims description 46
- 239000000446 fuel Substances 0.000 claims description 6
- 238000006073 displacement reaction Methods 0.000 abstract description 4
- 230000008859 change Effects 0.000 description 24
- 230000001276 controlling effect Effects 0.000 description 22
- 238000000034 method Methods 0.000 description 16
- 230000001105 regulatory effect Effects 0.000 description 9
- 239000012530 fluid Substances 0.000 description 7
- 239000003921 oil Substances 0.000 description 5
- 230000008569 process Effects 0.000 description 4
- 239000007788 liquid Substances 0.000 description 2
- 230000004048 modification Effects 0.000 description 2
- 238000012986 modification Methods 0.000 description 2
- 230000032683 aging Effects 0.000 description 1
- 230000009286 beneficial effect Effects 0.000 description 1
- 230000008901 benefit Effects 0.000 description 1
- 230000005611 electricity Effects 0.000 description 1
- 239000002828 fuel tank Substances 0.000 description 1
- 230000006870 function Effects 0.000 description 1
- 230000000977 initiatory effect Effects 0.000 description 1
- 230000005055 memory storage Effects 0.000 description 1
- 230000008520 organization Effects 0.000 description 1
- 230000000630 rising effect Effects 0.000 description 1
- 230000008054 signal transmission Effects 0.000 description 1
Classifications
-
- 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
- F15B11/02—Systems essentially incorporating special features for controlling the speed or actuating force of an output member
- F15B11/028—Systems essentially incorporating special features for controlling the speed or actuating force of an output member for controlling the actuating force
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B1/00—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders
- F04B1/12—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis
- F04B1/26—Control
- F04B1/28—Control of machines or pumps with stationary cylinders
- F04B1/29—Control of machines or pumps with stationary cylinders by varying the relative positions of a swash plate and a cylinder block
- F04B1/295—Control of machines or pumps with stationary cylinders by varying the relative positions of a swash plate and a cylinder block by changing the inclination of the swash plate
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B1/00—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders
- F04B1/12—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis
- F04B1/26—Control
- F04B1/30—Control of machines or pumps with rotary cylinder blocks
- F04B1/32—Control of machines or pumps with rotary cylinder blocks by varying the relative positions of a swash plate and a cylinder block
- F04B1/324—Control of machines or pumps with rotary cylinder blocks by varying the relative positions of a swash plate and a cylinder block by changing the inclination of the swash plate
-
- 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
- F15B21/001—Servomotor systems with fluidic control
-
- 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
-
- 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
- F15B2211/255—Flow control functions
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Fluid Mechanics (AREA)
- Chemical & Material Sciences (AREA)
- Analytical Chemistry (AREA)
- Control Of Positive-Displacement Pumps (AREA)
Abstract
The invention discloses an electric hydraulic control mechanism. The electric hydraulic control mechanism comprises a first servo unit and a constant-value reducing valve. By means of the constant-value reducing valve, a pressure difference is generated, and therefore a pressure signal is generated, the pressure signal is converted into a mechanical signal of the first servo unit, and the displacement of a plunger variable pump is controlled. Due to the fact that the electric hydraulic control mechanism is provided with the constant-value reducing valve, a servo relation is established between the system pressure and the plunger variable pump, and the plunger variate can be adjusted according to the system pressure.
Description
Technical field
The present invention relates to field of electromechanical technology, more particularly to a kind of electrohydraulic controlling mechanism.
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 signal of telecommunication 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 signal of telecommunication 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 electrohydraulic controlling mechanism of predetermined pressure.
To solve above-mentioned technical problem, the technical solution used in the present invention is：
A kind of electrohydraulic controlling mechanism, for by the pressure for changing the discharge capacity of plunger variable pump to adjust hydraulic system, bag
Include：
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 electrohydraulic controlling mechanism also includes
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.
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.
Compared with prior art, the beneficial effect of the electrohydraulic controlling mechanism that embodiments of the invention are provided is：The present invention
Due to being provided with fixed pressure reducing valve so that system pressure establishes servo relation with plunger variable pump, so that plunger variable energy
It is enough to be adjusted according to column system pressure.Additionally, two control units can control the second push rod of the second servo unit, second is made
Push rod is quick on the draw.
Description of the drawings
Fig. 1 is the structural representation of the electrohydraulic controlling mechanism of the present invention.
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.
For convenience of explanation electrohydraulic controlling mechanism purpose of the invention, technical scheme and advantage, are introducing electricity of the invention
Before liquid controlling organization, it is the discharge capacity and this kind which kind of mode to change variable pump by introduce first in prior art
The main Ying Yu of mode is in which kind of situation.
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 the gradient one-to-one signal of telecommunication 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 life-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 electrohydraulic controlling mechanism purpose of the present invention is to set up the relation of the pressure with the discharge capacity of variable pump of hydraulic system, i.e.,
Foundation adjusts the discharge capacity of variable pump to be carried out according to system pressure, and can affect system pressure again after the discharge capacity of variable pump is adjusted
Servo relation.
As shown in figure 1, embodiment of the invention discloses that a kind of electrohydraulic controlling mechanism, for by changing plunger variable pump
Adjusting the pressure of hydraulic system, the electrohydraulic controlling mechanism is specifically included 50 discharge capacity：First servo unit 10, the second servo list
First 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.
Electrohydraulic controlling mechanism also includes fixed pressure reducing valve 40, and system hydraulic oil is divided into two-way and each leads into the first left chamber 11
With the first right chamber room 12, fixed pressure reducing valve 40 is arranged on and is passed through on the pipeline of the first left chamber 11, so that in the first left chamber 11
Hydraulic oil pressure keep it is constant so that the hydraulic pressure in the pressure of the hydraulic oil in the first right chamber room 12 and the first left chamber 11
The difference of the pressure of oil increases with the increase of system pressure.
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 electrohydraulic controlling mechanism of the present invention establishes the relation between system pressure and the discharge capacity of plunger variable pump 50 so that be
System pressure is only adjusted by the change of the discharge capacity of plunger variable pump 50, and so as to eliminate other for affecting system pressure are adjusted
The process of Hydraulic Elements, so that the process of regulation is simple and accurate.The process can simply accurate adjustment system pressure the reason for
It is：Although affecting the factor of system pressure a lot, system pressure can be carried out by changing the discharge capacity of plunger variable pump 50
Change and adjust.
Relation between the system pressure set up of electrohydraulic controlling mechanism of the present invention and the discharge capacity of plunger variable pump 50 is to watch
Take relation, that is to say, that system pressure can in real time produce pressure signal, the pressure signal directly or is converted into mechanical signal
Plunger variable pump 50 is passed to so that the discharge capacity of plunger variable pump 50 changes, and the discharge capacity of plunger variable pump 50 change being capable of shadow in real time
Acoustic system pressure, so that system pressure reaches a numerical value that is constant and meeting system requirements.
The electrohydraulic controlling mechanism of the present invention changes the discharge capacity of plunger variable pump 50 according to system pressure, so that after adjusting
System pressure more conform to pre-provisioning request.
The electrohydraulic controlling mechanism of the present invention according to the discharge capacity of system pressure pilot plunger variable pump 50, and can set up system
Pressure it is critical only that with the servo relation of plunger variable pump 50：Definite value is set on the system pipeline for leading to the first left chamber 11
Air relief valve 40, the fixed pressure reducing valve 40 causes the pressure of the hydraulic oil in the first left chamber 11 less than system pressure and for not with being
System pressure change and the definite value that changes, and the pressure of the hydraulic oil in the first right chamber room 12 is equal to system pressure, so that the
The pressure initiation of the hydraulic oil in the pressure of the hydraulic oil in one right chamber room 12 and the first left chamber 11 pressure differential, in pre- level pressure
Power is poor, and (predetermined pressure difference is referred to：In system pressure required for hydraulic system, i.e. rated pressure, with the first left chamber 11
The difference of the pressure of hydraulic oil) under, the predetermined pressure difference is offset by the first spring 15, now, the first servo piston 13 keeps
It is motionless, and when system pressure is above or below rated pressure, now, the first servo piston 13 occurs in the presence of pressure differential
It is mobile, so that there is gradient change by the movement of the first servo piston 13 in swash plate 51, so as to change plunger variable pump
50 discharge capacity, and the change of this discharge capacity can make up just or the change of bucking-out system pressure, for example, when system pressure increase
When, the first servo piston 13 causes the discharge capacity of plunger variable pump 50 to reduce, and when system pressure reduces, the first servo piston 13 is caused
The discharge capacity of plunger variable pump 50 increases.
The fixed pressure reducing valve 40 of the electrohydraulic controlling mechanism of the present invention is to produce the decisive element of pressure differential, and makes system pressure
Power generates pressure differential with the condition exactly two ends of the first servo piston 13 under the decision of the generation servo relation of plunger variable pump 50.
The fixed pressure reducing valve 40 of the electrohydraulic controlling mechanism of the present invention also determines the rated pressure of system, 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, system pressure is also determined that
, reason is：When fixed pressure reducing valve 40 sets predetermined value as A, now, it is A pair that system pressure should be equal to predetermined value
Hydraulic fluid pressure (pressure of the hydraulic oil in the first left chamber 11) FA for answering and the thrust FB sum of the first spring 15, otherwise
One servo piston 13 can be moved.That is, after the setting value of fixed pressure reducing valve 40 determines, system pressure can produce one
Pressure value corresponding with setting value, conversely, by adjusting the setting value of fixed pressure reducing valve 40 system pressure can be made satisfactory
Pressure value.Therefore, the fixed pressure reducing valve 40 of electrohydraulic controlling mechanism of the invention is also equipped with the function of regulating system rated pressure.
The electrohydraulic controlling mechanism of the present invention is due to being provided with fixed pressure reducing valve 40 such that it is able to according to system pressure it is accurate and
By the discharge capacity of adjustment plunger variable pump 50 repeatedly, so that the system pressure volume for being adjusted to require fast and accurately
Constant-pressure, so as to alleviate overflow valve the constant pressure of system pressure is maintained, and improves the shelf life of overflow valve.
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 (2)
1. a kind of electrohydraulic controlling mechanism, for by the pressure for changing the discharge capacity of plunger variable pump to adjust hydraulic system, it to be special
Levy and be, including：
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
The valve element of intracavity, 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 electrohydraulic controlling mechanism also includes
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.
2. electrohydraulic controlling mechanism according to claim 1, it is characterised in that two described control units are ratio commutation
Valve, the oil-out of proportional reversing valve described in two respectively with second left chamber and the second right chamber, oil-in with
System hydraulic oil is connected, and when valve element described in two is moved to the left with the first push rod level, is connected with second left chamber
Logical oil-out pressure is less than the oil-out pressure with the described second right chamber；When valve element described in two is with first push rod
When level moves right, the oil-out pressure connected with second left chamber is more than fuel-displaced with the described second right chamber
Mouth pressure.
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| CN201611033967.5A CN106593969B (en) | 2016-11-22 | 2016-11-22 | Electrohydraulic controlling mechanism |
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| CN201611033967.5A CN106593969B (en) | 2016-11-22 | 2016-11-22 | Electrohydraulic controlling mechanism |
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Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN110761964A (en) * | 2019-11-13 | 2020-02-07 | 北京凯德福液压技术有限公司 | Digital control proportional plunger variable pump and pump control system |
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| CN110761964B (en) * | 2019-11-13 | 2023-11-28 | 北京凯德福液压技术有限公司 | Digital control proportional plunger variable pump and pump control system |
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| Publication number | Publication date |
|---|---|
| CN106593969B (en) | 2019-01-08 |
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