CN106640575B - Electrohydraulic controlling mechanism - Google Patents
Electrohydraulic controlling mechanism Download PDFInfo
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- CN106640575B CN106640575B CN201611033993.8A CN201611033993A CN106640575B CN 106640575 B CN106640575 B CN 106640575B CN 201611033993 A CN201611033993 A CN 201611033993A CN 106640575 B CN106640575 B CN 106640575B
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- chamber
- pressure
- hydraulic oil
- servo
- variable pump
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Classifications
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- 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
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- 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
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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Control Of Positive-Displacement Pumps (AREA)
- Reciprocating Pumps (AREA)
Abstract
The invention discloses a kind of electrohydraulic controlling mechanisms, including：First servo unit and the second servo unit, fixed pressure reducing valve and two position three way directional control valve etc., the fixed pressure reducing valve to generate pressure difference, to generate pressure signal, which is converted to the mechanical signal of the first servo unit, to control the discharge capacity of plunger variable pump.The present invention is due to being provided with fixed pressure reducing valve, so that system pressure and plunger variable pump establish servo relationship, so that plunger variable be enable to be adjusted according to column system pressure.Two position three way directional control valve of the invention enables plunger variable pump to switch in two kinds of discharge capacity regulative modes.
Description
Technical field
The present invention relates to electrohydraulic control technology field more particularly to a kind of electrohydraulic controlling mechanisms.
Background technique
In fluid power system and hydraulic control system (the two might as well be referred to as hydraulic system), system pressure or work pressure
The size of power is by multiple units or system co- controlling and determines, for example, in general, the discharge capacity such as variable pump does not vary widely
When, the system pressure of hydraulic system is mainly limited by overflow valve, when system pressure is more than the control pressure of overflow valve, overflow valve
So that pressure is revert to the system pressure of setting and to fuel tank draining, and is to have by the fluctuation of overflow valve control system pressure
Limit, in other words, when the discharge capacity of variable pump varies widely, if the discharge capacity of variable pump becomes larger, even if overflow valve is constantly let out
System pressure will not be reduced to setting pressure by oil, and so overflow valve will soon damage.Therefore, it is necessary to regulated variable pumps
Discharge capacity.
Occur the mechanism and method of a variety of adjustings or change variable pumpage, e.g., plunger variable pump in the prior art
Discharge capacity can be changed by changing the gradient of swash plate, the gradient of swash plate is adjusted by being provided with the servo piston of connecting rod, specifically,
Servo piston is arranged in servo piston chamber, and connecting rod stretches out from one end of servo piston chamber and pass through flexible change swash plate gradient,
Servo piston chamber is drawn hydraulic oil all the way from the oil outlet of plunger variable pump and is passed through not with spring is provided in the chamber of connecting rod
Have in the chamber of piston rod, the stroke that connecting rod is changed by the hydraulic fluid pressure size, thus change the gradient of swash plate, into
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
Known or precognition system needed under discharge capacity, for the substantially discharge capacity of regulated variable pump before using variable pump, this method is simultaneously
Not according to the discharge capacity of system pressure real-time regulated variable pump so that the discharge capacity of variable pump meets operating pressure requirement, in other words this
Kind method can only make the discharge capacity after adjusting generally conform to system requirements, and precision is poor.
The method of another pilot plunger variable pump is had also appeared in the prior art, on the one hand, is obtained by angular transducer
The gradient of the swash plate of variable pump is obtained, which passes to electromagnetic controller for steepness signals, have in electromagnetic controller
With the one-to-one electric signal of gradient；On the other hand, the hydraulic oil two-way of system respectively enters two chambers divided by piston
In, the connecting rod on the piston passes through with the mobile gradient for changing swash plate of piston；When controller needs to change the row of variable pump
When amount, controller changes the pressure of two-way hydraulic oil, to change the displacement of piston, and then changes the discharge capacity of variable pump.So
And this method only keeps the gradient of the swash plate of variable pump 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 associated there is no the discharge capacity with variable pump, to make this method
The discharge capacity that cannot be pumped according to system pressure come regulated variable, so that the discharge capacity after adjusting can only be made to generally conform to system requirements, essence
It spends poor.
Summary of the invention
For the above-mentioned technical problems in the prior art, the embodiment provides a kind of in real time according to being
The discharge capacity of the pressure signal regulated variable pump for hydraulic oil feedback of uniting is so that system pressure meets the electrohydraulic controlling mechanism of predetermined pressure.
In order to solve the above technical problems, the technical solution adopted by the present invention is that：
A kind of electrohydraulic controlling mechanism, for adjusting the pressure of hydraulic system, packet by the discharge capacity for changing plunger variable pump
It includes：
First servo unit comprising be formed with the first shell of first chamber, be 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；It is provided in first left chamber
For pushing against the first spring of first servo piston, wherein
The movement of first servo piston and the gradient of the swash plate of the plunger variable pump are configured to following interaction relation：
When the first servo piston level is moved to the left, first servo piston makes the plunger variable pump
The gradient of swash plate reduces；When first servo piston moves horizontally to the right, first servo piston makes the plunger
The gradient of the swash plate of variable pump increases；
The electrohydraulic controlling mechanism further includes
Fixed pressure reducing valve, system hydraulic oil are divided into two-way and each lead into first left chamber and first right chamber,
The fixed pressure reducing valve is arranged on the pipeline for being passed through first left chamber, so that the indoor hydraulic oil of the first left chamber
Pressure is kept constant, so that the pressure of the pressure of the indoor hydraulic oil of the first right chamber and the indoor hydraulic oil of the first left chamber
The difference of power increases with the increase of the pressure of system hydraulic oil；
Second servo unit comprising be formed with the second shell of second chamber, be arranged in the second chamber, and will
The second chamber is divided into the second servo piston of the second left chamber and the second right chamber, second left chamber and described
Second spring, second servo piston and the first servo piston synchronizing moving are respectively provided in two right chambers；
Two position three way directional control valve, having connect system hydraulic oil with first servo unit and simultaneously with described the
First position that two servo units disconnect and disconnect system hydraulic oil and first servo unit and simultaneously with described the
The second position of two servo units connection；
First control unit comprising be formed with the first valve body of the first valve chamber and to be set to first valve intracorporal
First spool, the first control unit are used to system hydraulic oil each leading into second left chamber and the second right chamber simultaneously
The pressure of second left chamber and the indoor hydraulic oil of the second right chamber is controlled by movement first spool；
Controller is used for the steepness signals control described first according to angle sensor feedback in the plunger variable pump
Control unit, with when controller obtains steepness signals and is greater than predetermined slant, the controller controls the first control unit
The first spool it is mobile so that the pressure of the indoor hydraulic oil of the second left chamber is less than the indoor hydraulic oil of the second right chamber
Pressure；With when controller obtains steepness signals and is less than predetermined slant, the controller controls the first of first control unit
Spool is mobile so that the pressure of the indoor hydraulic oil of the second left chamber is greater than the pressure of the indoor hydraulic oil of the second right chamber.
It preferably, further include third servo unit and the second control unit, first servo piston and described second are watched
It takes piston and is connected with the first push rod jointly；
The third servo unit comprising it is formed with the third shell of third chamber, is arranged in the third chamber,
And by the third chamber be divided into third left chamber and third right chamber third servo piston and with the third servo
The second push rod that piston is fixedly connected, the third left chamber are provided with third spring, and second push rod is described for driving
Swash plate, and：When second push rod moves to left, the gradient of the swash plate reduces, when second push rod moves to right, the swash plate
Gradient increase；
Second control unit includes being formed with the second valve body of the second valve chamber and being arranged in second valve chamber
The second spool, second spool is driven by first push rod, and system hydraulic oil passes through second control unit
To the third right chamber fuel feeding, so that：
When first push rod is moved to the left, first push rod drives the second spool movement so that the third
The pressure of the indoor hydraulic oil of right chamber increases；When first push rod moves right, first push rod drives described second
Spool movement is so that the pressure of the indoor hydraulic oil of third right chamber reduces.
Preferably, which is characterized in that second control unit is proportional reversing valve, the oil outlet of the proportional reversing valve
It is connected to the third right chamber, oil inlet is connected to system hydraulic oil, and when second spool is moved to the left, oil outlet
Hydraulic oil pressure increase so that the pressure of the indoor hydraulic oil of third right chamber increases；When second spool moves right
When dynamic, the pressure of the hydraulic oil of oil outlet reduces so that the pressure of the indoor hydraulic oil of third right chamber reduces.
Compared with prior art, the beneficial effect of electrohydraulic controlling mechanism provided by the embodiment of the present invention is：The present invention
Due to being provided with fixed pressure reducing valve, so that system pressure and plunger variable pump establish servo relationship, to enable plunger variable
It is enough to be adjusted according to column system pressure.The present invention is also provided with two position three way directional control valve, enables plunger variable pump two
Switch in kind discharge capacity regulative mode.
Detailed description of the invention
Fig. 1 is the structure schematic diagram of electrohydraulic controlling mechanism of the invention.
In figure：
The first servo unit of 10-；The first left chamber of 11-；The first right chamber of 12-；The first servo piston of 13-；The first bullet of 14-
Spring；The first push rod of 15-；The second servo unit of 20-；The second left chamber of 21-；The second right chamber of 22-；The second servo piston of 23-；
24- second spring；30- third servo unit；31- third left chamber；32- third right chamber；33- third servo piston；34-
Three springs；The second push rod of 35-；40- first control unit；The first spool of 41-；The second control unit of 50-；The second spool of 51-；
60- fixed pressure reducing valve；70- plunger variable pump；71- swash plate；80- two position three way directional control valve.
Specific embodiment
Technical solution in order to enable those skilled in the art to better understand the present invention, with reference to the accompanying drawing and specific embodiment party
Formula elaborates to the present invention.
Electrohydraulic controlling mechanism objects, technical solutions and advantages of the invention for convenience of explanation are introducing electricity of the invention
Before liquid control mechanism, introducing first in the prior art is the discharge capacity and this kind which kind of mode to change variable pump by
The main Ying Yu of mode is in which kind of situation.
Variable pump in the prior art, especially plunger variable pump 70 are usually become by changing the gradient of swash plate 71 to change
The discharge capacity for measuring pump needs the flow according to hydraulic system to hydraulic oil before variable pump is accessed hydraulic system as power source
It is required that, system pressure requirements and operating pressure require that the discharge capacity of variable pump is adjusted, that is to say, that the oblique of variable pump
The gradient of disk 71 is adjusted, so that the discharge capacity of variable pump generally conforms to the requirement of hydraulic system, to make variable pump access system
After system, the pressure remained steady of hydraulic system.
Under normal conditions, flow, system pressure and the operating pressure of the discharge capacity and hydraulic system of variable pump are to be positively correlated
, that is to say, that in same hydraulic system, the discharge capacity of variable pump is bigger, flow, system pressure and the work of hydraulic system
Pressure is also bigger, otherwise smaller.After the discharge capacity of variable pump determines, flow, system pressure and the work pressure of hydraulic system
Power can be determined substantially in a certain range.However, the discharge capacity of variable pump and do not have with the flow of hydraulic system, system pressure with
And the completely corresponding relationship of operating pressure, for example, system pressure does not have and the discharge capacity simultaneously when the discharge capacity of variable pump is Xv/s
Unique corresponding one determines pressure, and system pressure at this time may change or fluctuate in a big way, and this fluctuation
The range that may allow beyond system pressure, e.g., rated pressure beyond system (under the rated pressure, each member of system
Device could work normally).So that the discharge capacity and the flow of hydraulic system of variable pump, system pressure and operating pressure are incomplete
Corresponding one it is critically important the reason is that：Each Hydraulic Elements draining, oil leak and Hydraulic Elements generate not hydraulic oil in system
Variation and the aging of Hydraulic Elements of evitable resistance etc..
And discharge capacity and the system parameters of variable pump are all built upon for one by one to the adjusting of hydraulic system in the prior art
What the case where corresponding relationship, carried out, for example, be intended to adjust system pressure to a certain pressure value, it only need to be by the swash plate 71 of variable pump
Pitch adjustment to a certain discharge capacity of the unique corresponding variable pump of the pressure value.That is, only needing swash plate 71 individually
Adjust a certain predetermined slant.
For example, the gradient of swash plate 71 is adjusted by being provided with the servo piston of connecting rod, specifically, servo piston setting is being watched
It takes in plunger shaft, connecting rod stretches out from one end of servo piston chamber and passes through flexible change 71 gradient of swash plate, and servo piston chamber has
It is provided with spring in the chamber of connecting rod, draws the chamber that hydraulic oil all the way is passed through not piston rod from the oil outlet of plunger variable pump 70
In room, the stroke for changing connecting rod by the hydraulic fluid pressure size to change the gradient of swash plate 71, and then changes plunger
The discharge capacity of variable pump 70.
For another example on the one hand, the gradient of the swash plate 71 of variable pump is obtained by angular transducer, which will be oblique
Degree signal passes to electromagnetic controller, has and the one-to-one electric signal of gradient in electromagnetic controller；On the other hand, system
Hydraulic oil two-way respectively enters in two chambers by piston segmentation, connecting rod on the piston by with piston it is mobile for changing
The gradient of swash plate 71；When controller needs to change the discharge capacity of variable pump, controller changes the pressure of two-way hydraulic oil, to change
Become the displacement of piston, and then changes the discharge capacity of variable pump.
Above two method be built upon variable pump discharge capacity and system parameters be one-to-one relationship the case where into
Capable, however, it can be seen from the above, the discharge capacity of variable pump is with system parameters because many factors do not constitute completely corresponding pass
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 uniting 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 there is no the discharge capacity with variable pump is associated.Entire adjustment process relies on controller completely and feeds back to controller
The gradient of swash plate 71 carry out, being adjusted in real time according to hydraulic system pressure, mutually isolated with hydraulic system.
One bigger drawback of above-mentioned adjusting method is：Since variable pump is used for a long time, a certain gradient of swash plate 71
Corresponding discharge capacity can change, so that the discharge capacity of the numerical value stored in controller and variable pump is made to generate deviation, so that：
When controller issues the instruction that the adjusting of swash plate 71 makes variable pump adjusting to corresponding discharge capacity to a certain gradient, on variable pump
Although swash plate 71 adjust and arrive 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 that regulated variable pumps is inadequate or tune is not achieved
The expected reason of section is：The discharge capacity of variable pump according to system pressure not being adjusted, and only simple regulated variable
The discharge capacity of pump.The purpose of electrohydraulic controlling mechanism of the invention is the relationship of the discharge capacity for the pressure and variable pump for establishing hydraulic system, i.e.,
After establishing adjusts the discharge capacity of variable pump carries out according to system pressure, and the discharge capacity of variable pump is adjusted and system pressure can be influenced
Servo relationship.
As shown in Figure 1, embodiment of the invention discloses a kind of electrohydraulic controlling mechanism, for by changing plunger variable pump
70 discharge capacity adjusts the pressure of hydraulic system, which specifically includes：First servo unit 10, the second servo list
Member 20, first control unit 40, two position three way directional control valve 80, controller and fixed pressure reducing valve 60.
First servo unit 10 includes the first shell for being formed with 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 12；It is provided with and is used in first left chamber 11
Push against the first spring 14 of the first servo piston 13, wherein
The gradient of the swash plate 71 of the movement and plunger variable pump 70 of first servo piston 13 is configured to following interaction relation：
When 13 level of the first servo piston is moved to the left, the first servo piston 13 makes the swash plate 71 of plunger variable pump 70
Gradient reduce；When the first servo piston 13 moves horizontally to the right, the first servo piston 13 makes the oblique of plunger variable pump 70
The gradient of disk 71 increases；
Fixed pressure reducing valve 60, system hydraulic oil are divided into two-way and each lead into the first left chamber 11 and the first right chamber 12, fixed
Value pressure reducing valve 60 is arranged on the pipeline for being passed through the first left chamber 11, so that the pressure of the hydraulic oil in the first left chamber 11 is kept
It is constant, so that the difference of the pressure of the hydraulic oil in the first right chamber 12 and the pressure of the hydraulic oil in the first left chamber 11 is with being
Unite hydraulic oil pressure increase and increase；
Second servo unit 20 includes the second shell for being formed with 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 22, the second left chamber 21 and the second right chamber
Second spring 24,13 synchronizing moving of the second servo piston 23 and the first servo piston are respectively provided in 22；
Two position three way directional control valve 80 have make system hydraulic oil connect with the first servo unit 10 and simultaneously with the second servo
Unit 20 disconnect first position and make system hydraulic oil and the first servo unit 10 disconnection and simultaneously with the second servo unit
The second position of 20 connections；
First control unit 40 includes being formed with the first valve body of the first valve chamber and being set to the first valve intracorporal first
Spool 41, first control unit 40 is for each leading into the second left chamber 21 and the second right chamber 22 for system hydraulic oil and passing through
The pressure of mobile first spool 41 control the second left chamber 21 and the hydraulic oil in the second right chamber 22；
Controller is used to control first control unit according to the steepness signals of angle sensor feedback in plunger variable pump 70
40, with when controller obtains steepness signals and is greater than predetermined slant, controller controls the first spool 41 of first control unit 40
It is mobile so that the hydraulic oil in the second left chamber 21 pressure less than the hydraulic oil in the second right chamber 22 pressure；When control
When device obtains steepness signals less than predetermined slant, the first spool 41 that controller controls first control unit 40 is mobile so that second
The pressure of hydraulic oil in left chamber 21 is greater than the pressure of the hydraulic oil in the second right chamber 22.
In this way, when two position three way directional control valve 80 is in first position, even if system hydraulic oil and the first servo unit 10
When connecting and disconnecting simultaneously with the second servo unit 20, and system pressure increases (for some reason, including plunger variable pump 70
Discharge capacity increases, the hydraulic fluid port of control element becomes smaller) when, the pressure of the hydraulic oil in the first right chamber 12 increases, and the first left chamber
The pressure of hydraulic oil in room 11 is constant because being controlled pressure by fixed pressure reducing valve 60, so that the first servo piston 13 is to moving to left
Dynamic, the movement of the first servo piston 13 is so that the gradient of the swash plate 71 of plunger variable pump 70 reduces；To plunger variable pump 70
Discharge capacity reduces, and the discharge capacity of plunger variable pump 70 offsets the system pressure of rising after reducing.When the first servo piston 13 moves right
When, the first servo piston 13 increases the gradient of the swash plate 71 of plunger variable pump 70；When system pressure reduces (because of certain originals
Cause, discharge capacity including plunger variable pump 70 reduces, the hydraulic fluid port of control element becomes larger) when, the hydraulic oil in the first right chamber 12
Pressure reduce, and the pressure of the hydraulic oil in the first left chamber 11 because by fixed pressure reducing valve 60 control pressure it is constant, to make
It obtains the first servo piston 13 to move right, the movement of the first servo piston 13 is so that the gradient of the swash plate 71 of plunger variable pump 70 increases
Greatly, so that the discharge capacity of plunger variable pump 70 increases, the discharge capacity of plunger variable pump 70 increases the system pressure of post-compensation decline.
Electrohydraulic controlling mechanism of the invention establishes the relationship between 70 discharge capacity of system pressure and plunger variable pump, so that being
The change for the discharge capacity that system pressure only passes through plunger variable pump 70 is adjusted, to eliminate other for adjusting and influencing system pressure
The process of Hydraulic Elements, to keep adjustment process simply and accurate.The process can simply accurate regulating system pressure the reason of
It is：Although there are many factor for influencing system pressure, system pressure can be carried out by changing the discharge capacity of plunger variable pump 70
Change and adjusts.
Relationship between 70 discharge capacity of the system pressure that electrohydraulic controlling mechanism of the invention is established and plunger variable pump is to watch
Take relationship, that is to say, that system pressure can generate pressure signal in real time, and the pressure signal is direct or is converted into mechanical signal
Plunger variable pump 70 is passed to so that 70 discharge capacity of plunger variable pump changes, and the change of 70 discharge capacity of plunger variable pump being capable of real-time shadow
Acoustic system pressure, so that system pressure be made to reach a numerical value that is constant and meeting system requirements.
Electrohydraulic controlling mechanism of the invention changes the discharge capacity of plunger variable pump 70 according to system pressure, thus after making adjusting
System pressure be more in line with pre-provisioning request.
Electrohydraulic controlling mechanism of the invention can be according to the discharge capacity of system pressure pilot plunger variable pump 70, and establishes system
The key of pressure and the servo relationship of plunger variable pump 70 is：Definite value is set on the system pipeline for leading to the first left chamber 11
Pressure reducing valve 60, the fixed pressure reducing valve 60 make the pressure of the hydraulic oil in the first left chamber 11 be 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 12 is equal to system pressure, so that the
The pressure of hydraulic oil in one right chamber 12 and the pressure initiation of the hydraulic oil in the first left chamber 11 pressure difference, in pre- level pressure
Power is poor, and (predetermined pressure difference refers 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, which is offset by the first spring 14, at this point, the first servo piston 13 is kept
It is motionless, and when system pressure is above or below rated pressure, at this point, the first servo piston 13 occurs under the action of pressure difference
It is mobile, change so that by the movement of the first servo piston 13 gradient occurs for swash plate 71, to change plunger variable pump
70 discharge capacity, and the change of this discharge capacity can make up for it just or the change of bucking-out system pressure, for example, when system pressure increases
When, the first servo piston 13 reduces 70 discharge capacity of plunger variable pump, and when the system pressure decreases, the first servo piston 13 makes
70 discharge capacity of plunger variable pump increases.
The fixed pressure reducing valve 60 of electrohydraulic controlling mechanism of the invention is the decisive element for generating pressure difference, and makes system pressure
Condition is exactly that 13 both ends of the first servo piston produce pressure difference under the decision of power and the generation servo relationship of plunger variable pump 70.
The fixed pressure reducing valve 60 of electrohydraulic controlling mechanism of the invention also determines the rated pressure of system, that is to say, that
Under the premise of the coefficient of elasticity of first spring 14 is certain, when fixed pressure reducing valve 60 sets predetermined value, system pressure is also determined that
, reason is：When fixed pressure reducing valve 60 sets predetermined value as A, at this point, it is A pairs that system pressure, which should be equal to predetermined value,
Hydraulic fluid pressure (pressure of the hydraulic oil in the first left chamber 11) the sum of the FA and the thrust FB of the first spring 14 answered, otherwise
One servo piston 13 can move.That is, system pressure can generate one after 60 setting value of fixed pressure reducing valve determines
With setting value corresponding pressure value, conversely, system pressure can be kept satisfactory by adjusting fixed pressure reducing valve 60 setting value
Pressure value.Therefore, the fixed pressure reducing valve 60 of electrohydraulic controlling mechanism of the invention is also equipped with the function of regulating system rated pressure.
Electrohydraulic controlling mechanism of the invention due to being provided with fixed pressure reducing valve 60, so as to accurate according to system pressure and
By the discharge capacity of adjustment plunger variable pump 70 repeatedly, to make the volume for being adjusted to require of system pressure fast and accurately
Constant-pressure improves the shelf life of overflow valve to alleviate the pressure that overflow valve maintains system pressure constant.
As above-mentioned, when two position three way directional control valve 80 is in first position, i.e., system hydraulic oil and the first servo unit 10 connect
It connects and is disconnected simultaneously with the second servo unit 20, make the gradient and system pressure of swash plate 71 using the first servo unit 10 at this time
Above-mentioned servo relationship is established, so that entire mechanism be enable to adjust the row of real-time pilot plunger variable pump 70 according to system pressure
Amount, the regulative mode are chiefly used in hydraulic system processing due to needing to adjust repeatedly, are chiefly used in running in hydraulic system
When, the fluctuation of regulating system pressure.
And before hydraulic system operation, it is also desirable to tentatively be adjusted to the discharge capacity of the pump of plunger variable, to make hydraulic
After system operation, it is excessive that system pressure does not deviate by predetermined pressure, to be conducive to watch after hydraulic system is run by first
Unit 10 and fixed pressure reducing valve 60 is taken accurately to adjust hydraulic system.
For this purpose, another key point of the invention is, it is also provided with two position three way directional control valve 80, the second servo unit
20, controller and first control unit 40, the two position three way directional control valve 80 enable hydraulic system to watch with second by commutation
The connection of unit 20 is taken, i.e., when two position three way directional control valve 80 is in the second position, to facilitate controller and first control unit 40
The second servo unit 20 is controlled, the discharge capacity of plunger variable pump 70 is controlled by the second servo unit 20.And pass through controller, first
Control unit 40 and the mode of the second control unit 50 control plunger variable pump 70 are hereinbefore the described prior art
In control plunger variable pump 70 mode, i.e., instruction is sent by controller, swash plate 71 is controlled tiltedly by the instruction of controller
Degree, and then the discharge capacity of plunger variable pump 70 is controlled, and power of the system pressure extremely as generation mechanical signal at this time, and be not involved in
The adjusting being compared.The mode of the discharge capacity of pilot plunger variable pump 70 in the prior art is for becoming plunger before system operation
The adjusting of amount pump 70 has this significance, which can tentatively be adjusted plunger variable pump 70, to make system
After operation, hydraulic system can fluctuate in a certain range, utilize fixed pressure reducing valve 60 and the first servo unit to facilitate
10 pairs of plunger variable pumps 70 are accurately adjusted again.
The present invention is by switching two position three way directional control valve 80, so that can carry out to plunger variable pump 70 before system operation
Initial adjustment can carry out accurate adjustment to plunger variable pump 70, so that system be made to run smoothly after system operation.
To realize the above-mentioned interaction relation of the gradient of the movement of the first servo piston 13 and the swash plate 71 of plunger variable pump 70：
I.e. when the first servo piston 13 is moved to the left, the first servo piston 13 subtracts the gradient of the swash plate 71 of plunger variable pump 70
It is small；When the first servo piston 13 moves right, the first servo piston 13 increases the gradient of the swash plate 71 of plunger variable pump 70
Greatly；
Electrohydraulic controlling mechanism of the invention further includes third servo unit 30 and two second control units 50, and the first servo is living
Plug 13 and the second servo piston 23 are connected with the first push rod 15 jointly；
Third servo unit 30 comprising be formed with the third shell of third chamber, be arranged in third chamber, and by the
Three chambers are divided into the third servo piston 33 of third left chamber 31 and third right chamber 32 and consolidate with third servo piston 33
Surely the second push rod 35 connected, third left chamber 31 are provided with third spring 34, and the second push rod 35 is used to drive swash plate 71, and
And：When the second push rod 35 moves to left, the gradient of swash plate 71 reduces, and when the second push rod 35 moves to right, the gradient of swash plate 71 increases；
Second control unit 50 includes second for being formed with the second valve body of the second valve chamber and being arranged in the second valve chamber
Spool 51, the second spool 51 are driven by the first push rod 15, and system hydraulic oil passes through the second control unit 50 to third right chamber
32 fuel feeding of room, so that：
When the first push rod 15 is moved to the left, the first push rod 15 drives the second spool 51 mobile so that in third right chamber 32
Hydraulic oil pressure increase；When the first push rod 15 moves right, the first push rod 15 drives the second spool 51 mobile so that the
The pressure of hydraulic oil in three right chambers 32 reduces.
In this way, the first push rod 15 is moved to the left when the hydraulic increase of system, the second push rod 35 is made by control unit
It is moved to the left, so that the gradient of swash plate 71 reduces, the discharge capacity of plunger variable pump 70 reduces；When the hydraulic reduction of system, the
One push rod 15 moves right, and by control unit the second push rod 35 is also moved right, so that the gradient of swash plate 71 increases
Greatly, the discharge capacity of plunger variable pump 70 increases.
Second control unit 50 is proportional reversing valve, and the oil outlet of proportional reversing valve is connected to third right chamber 32, oil inlet
Mouth is connected to system hydraulic oil, and when the second spool 51 is moved to the left, and the pressure of the hydraulic oil of oil outlet increases so that third
The pressure of hydraulic oil in right chamber 32 increases；When the second spool 51 moves right, the pressure of the hydraulic oil of oil outlet reduces
So that the pressure of the hydraulic oil in third right chamber 32 reduces.
Claims (3)
1. a kind of electrohydraulic controlling mechanism, special for adjusting the pressure of hydraulic system by the discharge capacity for changing plunger variable pump
Sign is, including：
First servo unit comprising be formed with the first shell of first chamber, be 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；It is provided with and is used in first left chamber
Push against the first spring of first servo piston, wherein
The movement of first servo piston and the gradient of the swash plate of the plunger variable pump are configured to following interaction relation：
When the first servo piston level is moved to the left, first servo piston makes the swash plate of the plunger variable pump
Gradient reduce；When first servo piston moves horizontally to the right, first servo piston makes the plunger variable
The gradient of the swash plate of pump increases；
The electrohydraulic controlling mechanism further includes
Fixed pressure reducing valve, system hydraulic oil is divided into two-way and each leads into first left chamber and first right chamber, described
Fixed pressure reducing valve is arranged on the pipeline for being passed through first left chamber, so that the pressure of the indoor hydraulic oil of the first left chamber
It keeps constant, so that the pressure of the indoor hydraulic oil of the first right chamber and the pressure of the indoor hydraulic oil of the first left chamber
Difference increases with the increase of the pressure of system hydraulic oil；
Second servo unit comprising be formed with the second shell of second chamber, be 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, second left chamber and second right side
Second spring, second servo piston and the first servo piston synchronizing moving are respectively provided in chamber；
Two position three way directional control valve, having makes system hydraulic oil connect with first servo unit and watch simultaneously with described second
It takes the first position of unit disconnection and system hydraulic oil is made to disconnect with first servo unit and watch simultaneously with described second
Take the second position of unit connection；
First control unit comprising be formed with the first valve body of the first valve chamber and be set to first valve intracorporal first
Spool, the first control unit is for each leading into second left chamber and the second right chamber for system hydraulic oil and passing through
Mobile first spool controls the pressure of second left chamber and the indoor hydraulic oil of the second right chamber；
Controller is used for steepness signals control first control according to angle sensor feedback in the plunger variable pump
Unit, with when controller obtains steepness signals and is greater than predetermined slant, the controller controls the of the first control unit
One spool is mobile so that the pressure of the indoor hydraulic oil of the second left chamber is less than the pressure of the indoor hydraulic oil of the second right chamber
Power；With when controller obtains steepness signals and is less than predetermined slant, the controller controls the first spool of first control unit
Movement is so that the pressure of the indoor hydraulic oil of the second left chamber is greater than the pressure of the indoor hydraulic oil of the second right chamber.
2. electrohydraulic controlling mechanism according to claim 1, which is characterized in that further include third servo unit and the second control
Unit, first servo piston and second servo piston are connected with the first push rod jointly；
The third servo unit comprising be formed with the third shell of third chamber, be arranged in the third chamber, and will
The third chamber be divided into third left chamber and third right chamber third servo piston and with the third servo piston
The second push rod being fixedly connected, the third left chamber are provided with third spring, and second push rod is used to drive the swash plate,
And：When second push rod moves to left, the gradient of the swash plate reduces, when second push rod moves to right, the swash plate it is oblique
Degree increases；
Second control unit includes for being formed with the second valve body of the second valve chamber and being arranged in second valve chamber
Two spools, second spool are driven by first push rod, and system hydraulic oil by second control unit to institute
Third right chamber fuel feeding is stated, so that：
When first push rod is moved to the left, first push rod drives the second spool movement so that the third right chamber
The pressure of indoor hydraulic oil increases；When first push rod moves right, first push rod drives second spool
Movement is so that the pressure of the indoor hydraulic oil of third right chamber reduces.
3. electrohydraulic controlling mechanism according to claim 2, which is characterized in that it is characterized in that, second control unit
For proportional reversing valve, the oil outlet of the proportional reversing valve is connected to the third right chamber, and oil inlet and system hydraulic oil connect
It is logical, and when second spool is moved to the left, the pressure of the hydraulic oil of oil outlet increases so that the third right chamber is indoor
The pressure of hydraulic oil increases；When second spool moves right, the pressure of the hydraulic oil of oil outlet reduces so that described the
The pressure of the indoor hydraulic oil of three right chambers reduces.
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| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201611033993.8A CN106640575B (en) | 2016-11-22 | 2016-11-22 | Electrohydraulic controlling mechanism |
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| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201611033993.8A CN106640575B (en) | 2016-11-22 | 2016-11-22 | Electrohydraulic controlling mechanism |
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| CN106640575A CN106640575A (en) | 2017-05-10 |
| CN106640575B true CN106640575B (en) | 2018-11-16 |
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| CN201611033993.8A Active CN106640575B (en) | 2016-11-22 | 2016-11-22 | Electrohydraulic controlling mechanism |
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| Publication number | Priority date | Publication date | Assignee | Title |
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| CH717936A1 (en) * | 2020-10-06 | 2022-04-14 | Liebherr Machines Bulle Sa | Axial piston machine with control valve. |
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| US4895182A (en) * | 1988-01-11 | 1990-01-23 | Hoerbiger Hydraulik Gmbh | Hydraulic control unit |
| CN102900643A (en) * | 2011-07-29 | 2013-01-30 | 波克兰液压工业设备公司 | Hydraulic control circuit |
| 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 |
| 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 |
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2016
- 2016-11-22 CN CN201611033993.8A patent/CN106640575B/en active Active
Patent Citations (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US4895182A (en) * | 1988-01-11 | 1990-01-23 | Hoerbiger Hydraulik Gmbh | Hydraulic control unit |
| CN102900643A (en) * | 2011-07-29 | 2013-01-30 | 波克兰液压工业设备公司 | Hydraulic control circuit |
| 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 |
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| CN106640575A (en) | 2017-05-10 |
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