CN106369000A - Unloading electrohydraulic control mechanism - Google Patents
Unloading electrohydraulic control mechanism Download PDFInfo
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- CN106369000A CN106369000A CN201611036763.7A CN201611036763A CN106369000A CN 106369000 A CN106369000 A CN 106369000A CN 201611036763 A CN201611036763 A CN 201611036763A CN 106369000 A CN106369000 A CN 106369000A
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- 230000007246 mechanism Effects 0.000 title claims abstract description 29
- 239000010720 hydraulic oil Substances 0.000 claims description 83
- 239000000446 fuel Substances 0.000 claims description 7
- 239000007788 liquid Substances 0.000 claims 2
- 238000006073 displacement reaction Methods 0.000 abstract description 6
- 230000035945 sensitivity Effects 0.000 abstract description 2
- 230000001276 controlling effect Effects 0.000 description 22
- 230000008859 change Effects 0.000 description 19
- 238000000034 method Methods 0.000 description 16
- 230000001105 regulatory effect Effects 0.000 description 10
- 239000012530 fluid Substances 0.000 description 7
- 239000003921 oil Substances 0.000 description 6
- 230000008569 process Effects 0.000 description 4
- 230000032683 aging Effects 0.000 description 1
- 230000009286 beneficial effect Effects 0.000 description 1
- 230000008901 benefit Effects 0.000 description 1
- 230000000694 effects 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
- 230000009467 reduction Effects 0.000 description 1
- 230000004044 response Effects 0.000 description 1
- 230000000630 rising effect Effects 0.000 description 1
- 230000008054 signal transmission Effects 0.000 description 1
- 230000001550 time effect 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
- F15B13/00—Details of servomotor systems ; Valves for servomotor systems
- F15B13/02—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors
- F15B13/06—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with two or more servomotors
Abstract
The invention discloses an unloading electrohydraulic control mechanism. The unloading electrohydraulic control mechanism comprises a first servo unit, a second servo unit, a fixed pressure reducing valve, an unloading unit, a two-position three-way reversing valve and the like; the fixed pressure reducing valve generates the pressure difference so as to generate pressure signals, the pressure signals are converted into mechanical signals of the first servo unit, and therefore the displacement of a piston variable pump is controlled; due to the arrangement of the fixed pressure reducing valve, a servo relation is built between the pressure of a system and the piston variable pump, and therefore the piston variable pump can carry out adjustment according to the column system pressure; according to the two-position three-way reversing valve, the piston variable pump can be switched between two displacement adjusting manners. In addition, the unloading unit enables the whole hydraulic system to safely work, and an electromagnet can improve the pressure adjusting sensitivity or the pressure adjusting range.
Description
Technical field
The present invention relates to field of electromechanical technology, more particularly, to a kind of electrohydraulic controlling mechanism of relief.
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
By multiple units or system co- controlling and decision, for example, generally, large change in the discharge capacity of such as variable pump to the size of power there is not
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
It revert to the system pressure of setting by making pressure to fuel tank draining, and be to have by the fluctuation of overflow valve control system pressure
Limit, in other words, when the discharge capacity of variable pump occurs large change, such as the discharge capacity of variable pump becomes big, even if overflow valve is constantly let out
Oil also will not reduce system pressure to setting pressure, and such overflow valve will soon damage.Accordingly, it would be desirable to regulated variable pump
Discharge capacity.
Multiple mechanism and methods adjusting or claiming to change variable pumpage, e.g., plunger variable pump are occurred in that in prior art
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 passes through flexible change swash plate gradient,
The within the chamber that servo piston chamber has connecting rod is provided with spring, draws a road hydraulic oil from the oil-out of plunger variable pump and is passed through not
Have in the chamber of piston rod, changing the stroke of connecting rod by this hydraulic fluid pressure size, thus changing the gradient of swash plate, entering
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 discharge capacity of substantially 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 and requires, 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 have also appeared another kind of pilot plunger variable pump in prior art, on the one hand, obtained by angular transducer
Obtain the gradient of the swash plate of variable pump, steepness signals are passed to electromagnetic controller, have in electromagnetic controller by this angular transducer
The one-to-one signal of telecommunication with 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 this piston passes through with the mobile gradient for changing swash plate of piston；When controller needs to change the row of variable pump
During amount, controller changes the pressure of two-way hydraulic oil, thus changing the displacement of piston, and then changes the discharge capacity of variable pump.So
And, the method simply makes the gradient of the 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 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, thus the discharge capacity after regulation can only be made to generally conform to system requirements, essence
Degree is poor.
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 electro-hydraulic of the relief of predetermined pressure
Controlling organization.
For solving above-mentioned technical problem, the technical solution used in the present invention is:
A kind of electrohydraulic controlling mechanism of relief, adjusts hydraulic system for the discharge capacity by changing plunger variable pump
Pressure, comprising:
First servo unit, it includes being formed with the first housing of first chamber, is arranged in described first chamber, and will
Described first chamber is divided into the first left chamber and the first servo piston of the first right chamber room；Described first left chamber interior is provided with
For pushing against the first spring of described first servo piston；
Second servo unit, it includes being formed with the second housing of second chamber, is arranged in described second chamber, and will
Described second chamber is divided into the second left chamber and the second servo piston of the second right chamber room, described second left chamber and described
Two right chamber interiors are respectively provided with second spring；Wherein:
Described first servo piston and described second servo piston are connected with the first push rod jointly；
3rd servo unit, it includes being formed with the 3rd housing of the 3rd chamber, is arranged on described 3rd within the chamber, and will
Described 3rd chamber be divided into the 3rd left chamber and the 3rd right chamber room the 3rd servo piston and with described 3rd servo piston
The second push rod being fixedly connected, described 3rd left chamber and described 3rd right chamber interior are respectively provided with the 3rd spring, and described second pushes away
Bar is used for driving described swash plate, and: when described second push rod moves to left, the gradient of described swash plate reduces, described second push rod
When moving to right, the gradient of described swash plate increases；
First control unit, it includes being formed with the first valve body of the first valve pocket and is arranged in described first valve body
First valve element, described first control unit is used for for system hydraulic oil each leading into described second left chamber and the second right chamber room simultaneously
Control the pressure of the hydraulic oil of described second left chamber and the second right chamber interior by described first valve element of movement；
Two second control units, the second control unit described in two is arranged side by side and all includes being formed with the second of the second valve pocket
Valve body and be arranged on the second valve element in described second valve pocket, described first push rod be located at described in two between second valve element and with
When be connected with the second valve element described in two, and system hydraulic oil to pass through one of described second control unit left to the described 3rd
Chamber fuel feeding, by the second control unit another described to described 3rd right chamber room fuel feeding, so that:
When described first push rod is moved to the left, described first push rod drives the second valve element described in two to move so that leading to simultaneously
The pressure entering the indoor hydraulic oil of described 3rd right chamber is more than the pressure of the indoor hydraulic oil of described 3rd left chamber, when described first
When push rod moves right, described first push rod drives the second valve element described in two to move so that being passed through described 3rd right chamber interior simultaneously
The pressure of hydraulic oil be less than the pressure of the indoor hydraulic oil of described 3rd left chamber；
Two position three way directional control valve, it has makes system hydraulic oil be connected with described first servo unit and simultaneously with described
Primary importance that two servo units disconnect and make system hydraulic oil disconnect with described first servo unit and simultaneously with described the
The second position that two servo units connect；
The electrohydraulic controlling mechanism of described relief also includes
Fixed pressure reducing valve, system hydraulic oil is divided into two-way and each leads into described first left chamber and described first right chamber room,
Described fixed pressure reducing valve is arranged on the pipeline being passed through described first left chamber, so that the indoor hydraulic oil of described first left chamber
Pressure keeps constant, so that the pressure of the indoor pressure of hydraulic oil of the described first right chamber hydraulic oil indoor with described first left chamber
The increase of the pressure with system hydraulic oil for the difference of power and increase；
Controller, the steepness signals that it is used for according to angle sensor feedback in described plunger variable pump control described first
Control unit, so that when controller obtains steepness signals and is more than predetermined slant, described controller controls described first control unit
The first valve element mobile so that the pressure of the indoor hydraulic oil of described second left chamber is less than the indoor hydraulic oil of described second right chamber
Pressure；So that when controller obtains steepness signals and is less than predetermined slant, described controller controls the first of the first control unit
Valve element is mobile so that the pressure of the indoor hydraulic oil of described second left chamber is more than the pressure of the indoor hydraulic oil of described second right chamber；
Off-load unit, it is used for, when system pressure exceeds default peak, forcing the swash plate of described plunger variable pump
Gradient is zeroed.
Preferably, described in two, the second control unit is proportional reversing valve, and the oil-out of proportional reversing valve described in two is respectively
With described 3rd left chamber and described 3rd right chamber, oil-in is connected with system hydraulic oil, and works as the second valve described in two
When core is moved to the left with described first push rod level, the oil-out pressure being connected with described 3rd left chamber is less than and the described 3rd
The oil-out pressure of right chamber；When the second valve element described in two moves right with described first push rod level, with described
The oil-out pressure of three left chamber connection is more than the oil-out pressure with described 3rd right chamber.
Preferably, described off-load unit is connected with system pipeline for oil-in, oil-out and described 3rd right chamber
Individual event valve, described check valve set pressure be more than hydraulic system rated pressure.
Compared with prior art, the beneficial effect of the electrohydraulic controlling mechanism of the relief that embodiments of the invention are provided
It is: the present invention is due to being provided with fixed pressure reducing valve so that system pressure and plunger variable pump establish servo relation, so that post
Plug variable can be adjusted according to column system pressure.The present invention is also provided with two position three way directional control valve so that plunger variable pump
Can switch in two kinds of discharge capacity regulative modes.Additionally, off-load unit can enable whole hydraulic system trouble free service.
Brief description
Fig. 1 is the structural representation of the electrohydraulic controlling mechanism of relief of the present invention.
In figure:
10- first servo unit；11- first left chamber；12- the first right chamber room；13- first servo piston；14- first bullet
Spring；15- first push rod；20- second servo unit；21- second left chamber；22- the second right chamber room；23- second servo piston；
24- second spring；30- the 3rd servo unit；31- the 3rd left chamber；32- the 3rd right chamber room；33- the 3rd servo piston；34-
Three springs；35- second push rod；40- first control unit；41- first valve element；50- second control unit；51- second valve element；
60- fixed pressure reducing valve；70- plunger variable pump；71- swash plate；80- two position three way directional control valve；90- off-load unit.
Specific embodiment
For making 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.
The electrohydraulic controlling mechanism purpose of the relief of the present invention, technical scheme and advantage for convenience of explanation, is introducing this
Before the electrohydraulic controlling mechanism of relief of invention, introducing first in prior art is which kind of mode to change variable by
The discharge capacity of pump and the main Ying Yu of this kind of mode are in which kind of situation.
Variable pump of the prior art, particularly plunger variable pump 70 generally change change by the gradient changing swash plate 71
The discharge capacity of amount pump, before variable pump is accessed hydraulic system as power source, needs according to hydraulic system the flow to hydraulic oil
Require, system pressure requirements and operating pressure require the discharge capacity of variable pump is adjusted that is to say, that oblique to 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, 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 do not have the flow of same hydraulic system, system pressure with
And the completely corresponding relation of operating pressure, for example, when the discharge capacity of variable pump is xv/s, system pressure does not have and this discharge capacity
A uniquely corresponding determination pressure, system pressure now in interior change in a big way or may claim fluctuation, and this fluctuation
The scope that may allow beyond system pressure, e.g., rated pressure beyond system (under this rated pressure, each unit of system
Device ability normal work).Make the discharge capacity of variable pump and the flow of hydraulic system, system pressure and operating pressure incomplete
A corresponding critically important reason is: in system, each Hydraulic Elements draining, oil leak, and Hydraulic Elements produce not to hydraulic oil
The change of evitable resistance and Hydraulic Elements aging etc..
And in prior art, the regulation of hydraulic system is all built upon with the discharge capacity of variable pump and system parameters is one by one
The situation of corresponding relation is carried out, and for example, is intended to for system pressure to be adjusted to a certain pressure value, only need to be by the swash plate 71 of variable pump
Pitch adjustment is to a certain discharge capacity with the unique corresponding variable pump of this pressure value.That is, only needing individually by swash plate 71
It is adjusted to a certain predetermined slant.
For example, the gradient of swash plate 71 is provided by the servo piston regulation of connecting rod, and specifically, servo piston is arranged on to be watched
Take in plunger shaft, connecting rod stretches out from the one end in servo piston chamber and passes through flexible change swash plate 71 gradient, and servo piston chamber has
The within the chamber of connecting rod is provided with spring, and drawing a road hydraulic oil and be passed through from the oil-out of plunger variable pump 70 does not have the chamber of piston rod
In room, changing the stroke of connecting rod by this hydraulic fluid pressure size, thus changing the gradient of swash plate 71, and then changing plunger
The discharge capacity of variable pump 70.
Again for example, on the one hand, obtain the gradient of the swash plate 71 of variable pump by angular transducer, this angular transducer will tiltedly
Degree signal transmission, to electromagnetic controller, has the one-to-one signal of telecommunication with gradient in electromagnetic controller；On the other hand, system
Hydraulic pressure oil two-way respectively enters in two chambers split by piston, and the connecting rod on this piston passes through to be used for changing with piston movement
The gradient of swash plate 71；When controller needs the discharge capacity changing variable pump, controller changes the pressure of two-way hydraulic oil, thus changing
Become the displacement of piston, and then change the discharge capacity of variable pump.
The situation that the discharge capacity that above two method is all built upon variable pump is one-to-one relationship with system parameters is entered
Row, however, from the foregoing, the discharge capacity of variable pump and system parameters do not constitute completely corresponding pass because of many factors
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
Under discharge capacity needed for system, the discharge capacity of substantially 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 merely piston transverse shifting
Power, and be not associated with the discharge capacity of variable pump.Whole regulation process is relied on controller completely and is fed back to controller
The gradient of swash plate 71 carry out, not according to hydraulic system pressure real-time regulation, isolate with hydraulic system phase.
One of above-mentioned control method the drawbacks of bigger is: due to variable pump life-time service, a certain gradient of its swash plate 71
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 71 and is adjusted to a certain gradient and makes the instruction that variable pump is adjusted to corresponding discharge capacity, on variable pump
Although swash plate 71 be adjusted to predetermined slant, discharge capacity is not up to pre- fixed displacement.
The degree of regulation of the method carrying out regulating system pressure above by the discharge capacity of regulated variable pump not or does not reach tune
The reason section is 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 relief of the present invention is to set up the discharge capacity with variable pump for the pressure of hydraulic system
Relation, that is, set up and so that the discharge capacity regulation of variable pump is carried out according to system pressure, and can affect after the discharge capacity regulation of variable pump again
The servo relation of system pressure.
As shown in figure 1, embodiment of the invention discloses that a kind of electrohydraulic controlling mechanism of relief, for by changing post
The pressure to adjust hydraulic system for the discharge capacity of plug variable pump 70, the electrohydraulic controlling mechanism of this relief specifically includes: the first servo
Unit 10, the second servo unit 20, the 3rd servo unit 30, the first control unit 40, the second control unit 50, two-position three way change
To valve 80, controller, off-load unit 90 and fixed pressure reducing valve 60.
First servo unit 10, it includes being formed with the first housing of first chamber, is arranged in described first chamber, and
Described first chamber is divided into the first servo piston 13 of the first left chamber 11 and the first right chamber room 12；Described first left chamber
It is provided with the first spring 14 for pushing against described first servo piston 13 in 11；
Second servo unit 20, it includes being formed with the second housing of second chamber, is arranged in described second chamber, and
Described second chamber is divided into the second servo piston 23 of the second left chamber 21 and the second right chamber room 22, described second left chamber
21 and described second right chamber room 22 in be respectively provided with second spring 24；Wherein:
Described first servo piston 13 and described second servo piston 23 are connected with the first push rod 15 jointly；
3rd servo unit 30, it includes being formed with the 3rd housing of the 3rd chamber, is arranged on described 3rd within the chamber, and
Described 3rd chamber is divided into the 3rd servo piston 33 of the 3rd left chamber 31 and the 3rd right chamber room 32 and with the described 3rd
The second push rod 35 that servo piston 33 is fixedly connected, is respectively provided with the 3rd in described 3rd left chamber 31 and described 3rd right chamber room 32
Spring 34, described second push rod 35 is used for driving described swash plate 71, and: when described second push rod 35 moves to left, described swash plate
71 gradient reduces, and when described second push rod 35 moves to right, the gradient of described swash plate 71 increases；
First control unit 40, it includes being formed with the first valve body of the first valve pocket and is arranged in described first valve body
The first valve element 41, described first control unit 40 is used for for system hydraulic oil each leading into described second left chamber 21 and second
Right chamber room 22 simultaneously controls the hydraulic oil in described second left chamber 21 and the second right chamber room 22 by mobile described first valve element 41
Pressure；
Two second control units 50, the second control unit 50 described in two is arranged side by side and all includes being formed with the second valve pocket
Second valve body and be arranged on the second valve element 51 in described second valve pocket, described first push rod 15 is located at the second valve element described in two
It is connected between 51 and simultaneously with the second valve element 51 described in two, and system hydraulic oil passes through one of described second control unit
50 to described 3rd left chamber 31 fuel feeding, by the second control unit 50 another described to described 3rd right chamber room 32 fuel feeding,
So that:
When described first push rod 15 is moved to the left, described first push rod 15 drives the second valve element 51 described in two to move simultaneously
So that the pressure of the hydraulic oil being passed through in described 3rd right chamber room 32 is more than the pressure of the hydraulic oil in described 3rd left chamber 31
Now, the second push rod 35 is moved to the left so that the gradient of the swash plate 71 of plunger variable pump 70 reduces, so that plunger variable pump 70
Discharge capacity reduce, when described first push rod 15 moves right, described first push rod 15 drives the second valve element 51 described in two simultaneously
Move so that the pressure of the hydraulic oil being passed through in described 3rd right chamber room 32 is less than the hydraulic oil in described 3rd left chamber 31
Pressure, now, the second push rod 35 moves right so that the gradient of the swash plate 71 of plunger variable pump 70 increases, so that plunger becomes
The discharge capacity of amount pump 70 increases；
Two position three way directional control valve 80, its have so that system hydraulic oil is connected with described first servo unit 10 and simultaneously with institute
State the primary importance of the second servo unit 20 disconnection and so that system hydraulic oil and described first servo unit 10 is disconnected and simultaneously
The second position being connected with described second servo unit 20；
The electrohydraulic controlling mechanism of described relief also includes
Fixed pressure reducing valve 60, system hydraulic oil is divided into two-way and each leads into described first left chamber 11 and described first right chamber
Room 12, described fixed pressure reducing valve 60 is arranged on the pipeline being passed through described first left chamber 11, so that described first left chamber 11
The pressure of interior hydraulic oil keeps constant, so that the pressure of hydraulic oil in described first right chamber room 12 and described first left chamber
The increase of the pressure with system hydraulic oil for the difference of the pressure of the hydraulic oil in 11 and increase；
Controller, the steepness signals that it is used for according to angle sensor feedback in described plunger variable pump 70 control described the
One control unit 40, so that when controller obtains steepness signals and is more than predetermined slant, described controller controls described first control
First valve element 41 of unit 40 is mobile so that the pressure of hydraulic oil in described second left chamber 21 is less than described second right chamber room
The pressure of the hydraulic oil in 22；So that when controller obtains steepness signals and is less than predetermined slant, described controller controls the first control
First valve element 41 of unit 40 processed is mobile so that the pressure of hydraulic oil in described second left chamber 21 is more than described second right chamber
The pressure of the hydraulic oil in room 22；
Off-load unit 90, it is used for, when system pressure exceeds default peak, forcing the oblique of described plunger variable pump 70
The gradient zero of disk 71.
So, when two position three way directional control valve 80 is in primary importance, even if system hydraulic oil and the first servo unit 10
When connecting and disconnecting with the second servo unit 20 simultaneously, and system pressure increases (because of some reasons, including plunger variable pump 70
Discharge capacity increases, the hydraulic fluid port of control element diminishes) when, the pressure of the hydraulic oil in the first right chamber room 12 increases, and the first left chamber
The pressure of the hydraulic oil in room 11 is because constant by fixed pressure reducing valve 60 control pressure, so that the first servo piston 13 is to moving to left
Dynamic, the movement of the first servo piston 13 makes the gradient of the swash plate 71 of plunger variable pump 70 reduce；Thus 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 makes the gradient of the swash plate 71 of plunger variable pump 70 increase；When system pressure reduces (because some former
Cause, the hydraulic fluid port including the discharge capacity reduction of plunger variable pump 70, control element becomes big etc.) when, the hydraulic oil in the first right chamber room 12
Pressure reduce, and the pressure of the hydraulic oil in the first left chamber 11 is because constant by fixed pressure reducing valve 60 control pressure so that
Obtain the first servo piston 13 to move right, the movement of the first servo piston 13 makes the gradient of the swash plate 71 of plunger variable pump 70 increase
Greatly, thus the discharge capacity of plunger variable pump 70 increases, the discharge capacity of plunger variable pump 70 increases the system pressure that post-compensation declines.
The electrohydraulic controlling mechanism of the relief of the present invention establishes the pass between system pressure and plunger variable pump 70 discharge capacity
System is so that system pressure is only adjusted by the change of the discharge capacity of plunger variable pump 70, thus eliminating regulation impact system
The process of other Hydraulic Elements of pressure, so that the process of regulation is simple and accurate.This process being capable of simple accurate adjustment system
The reason pressure, is: although the factor of impact system pressure is a lot, system pressure all can be by changing plunger variable pump 70
Discharge capacity be changed and adjust.
Between system pressure that the electrohydraulic controlling mechanism of the relief of the present invention is set up and plunger variable pump 70 discharge capacity
Relation be servo relation that is to say, that system pressure can produce pressure signal in real time, this pressure signal directly or is converted into
Mechanical signal passes to plunger variable pump 70 so that plunger variable pump 70 discharge capacity changes, and plunger variable pump 70 discharge capacity changes energy
Enough Real Time Effect system pressures, so that system pressure reaches a numerical value that is constant and meeting system requirements.
The electrohydraulic controlling mechanism of the relief of the present invention changes the discharge capacity of plunger variable pump 70 according to system pressure, thus
The system pressure after regulation is made to more conform to pre-provisioning request.
The electrohydraulic controlling mechanism of the relief of the present invention can according to the discharge capacity of system pressure pilot plunger variable pump 70, and
Set up it is critical only that of system pressure and the servo relation of plunger variable pump 70: on the system pipeline leading to the first left chamber 11
Setting fixed pressure reducing valve 60, this fixed pressure reducing valve 60 make the hydraulic oil in the first left chamber 11 pressure be less than system pressure and
The definite value changing for not changing with system pressure, and the pressure of the hydraulic oil in the first right chamber room 12 is equal to system pressure, from
And make the pressure differential of the pressure initiation of hydraulic oil in the pressure of hydraulic oil and the first left chamber 11 in the first right chamber room 12,
In predetermined pressure difference, (this predetermined pressure difference refers to: the system pressure required for hydraulic system, i.e. rated pressure, with the first left chamber
The difference of the pressure of the hydraulic oil in room 11) under, this predetermined pressure difference is offset by the first spring 14, now, the first servo is lived
Plug 13 remains stationary as, and when system pressure is above or below rated pressure, now, the first servo piston 13 is in the work of pressure differential
With under be moved so that swash plate 71 occurred by the movement of the first servo piston 13 gradient change, thus changing post
The discharge capacity of plug variable pump 70, and the change of this discharge capacity can make up just or the change of bucking-out system pressure, for example, works as system
When pressure increases, the first servo piston 13 makes plunger variable pump 70 discharge capacity reduce, and when system pressure reduces, the first servo is lived
Plug 13 makes plunger variable pump 70 discharge capacity increase.
The fixed pressure reducing valve 60 of the electrohydraulic controlling mechanism of the relief of the present invention is the decisive element producing pressure differential, and
Make system pressure and plunger variable pump 70 produce condition the exactly first servo piston 13 two ends under the decision of servo relation to create
Pressure differential.
The fixed pressure reducing valve 60 of the electrohydraulic controlling mechanism of the relief of the present invention also determines the rated pressure of system, also
It is to say, on the premise of the coefficient of elasticity of the first spring 14 is certain, when fixed pressure reducing valve 60 sets predetermined value, system pressure
Determine that, reason is: when fixed pressure reducing valve 60 sets predetermined value as a, now, system pressure should be equal to and predetermined value
For the thrust fb sum of the corresponding hydraulic fluid pressure of a (pressure of the hydraulic oil in the first left chamber 11) fa and the first spring 14,
Otherwise the first servo piston 13 can be moved.That is, after fixed pressure reducing valve 60 setting value determines, system pressure can produce
A raw pressure value corresponding with setting value, conversely, can make system pressure meet by adjusting fixed pressure reducing valve 60 setting value
Required pressure value.Therefore, the fixed pressure reducing valve 60 of the electrohydraulic controlling mechanism of the relief of the present invention is also equipped with regulating system volume
The function of constant-pressure.
The electrohydraulic controlling mechanism of the relief of the present invention is due to being provided with fixed pressure reducing valve 60 such that it is able to according to system pressure
The discharge capacity accurately and by adjustment plunger variable pump 70 repeatedly for the power, so that system pressure being adjusted to fast and accurately
The rated pressure requiring, thus alleviating overflow valve to maintain the constant pressure of system pressure, improves the shelf life of overflow valve.
As above-mentioned, when two position three way directional control valve 80 is in primary importance, that is, system hydraulic oil and the first servo unit 10 be even
Connect and disconnect with the second servo unit 20 simultaneously, now make gradient and the system pressure of swash plate 71 using the first servo unit 10
Set up above-mentioned servo relation, so that whole mechanism can adjust the row of real-time regulation plunger variable pump 70 according to system pressure
Amount, this regulative mode, due to needing repeatedly to adjust, is used in hydraulic system processing, is used for running in hydraulic system
When, the fluctuation of regulating system pressure.
And working as before hydraulic system is run it is also desirable to tentatively be adjusted to the discharge capacity of the pump of plunger variable, so that hydraulic pressure
After system operation, it is excessive, thus being conducive to, after hydraulic system is run, watching by first that system pressure does not deviate by predetermined pressure
Take unit 10 and fixed pressure reducing valve 60 carries out accurate adjustment to hydraulic system.
For this reason, another key point of the present invention is, it is also provided with two position three way directional control valve 80, the second servo unit
20th, controller and the first control unit 40, this two position three way directional control valve 80 enables hydraulic system to watch with second by commutation
Take unit 20 to connect, when that is, two position three way directional control valve 80 is in the second position, thus facilitating controller and the first control unit 40
Control the second servo unit 20, control the discharge capacity of plunger variable pump 70 by the second servo unit 20.And pass through controller, first
The mode of control unit 40 and the second control unit 50 control plunger variable pump 70 is hereinbefore described prior art
In control plunger variable pump 70 mode, that is, pass through controller and send instruction, oblique by the instruction of controller control swash plate 71
Degree, and then control the discharge capacity of plunger variable pump 70, and the now power extremely as generation mechanical signal for the system pressure, and be not involved in
The regulation compared.The mode of the discharge capacity of pilot plunger variable pump 70 of the prior art becomes to plunger for before system operation
The regulation of amount pump 70 has this significance, and this regulative mode tentatively can be adjusted to plunger variable pump 70, so that system
After operation, hydraulic system can fluctuate within the specific limits, thus convenient utilize fixed pressure reducing valve 60 and the first servo unit
10 pairs of plunger variable pumps 70 carry out accurate adjustment again.
The present invention passes through to switch two position three-way valve so that can carry out initial adjustment to plunger variable pump 70 before system operation,
After system operation, accurate adjustment can be carried out to plunger variable pump 70, so that system operation is steady.
Above-mentioned the 3rd servo unit 30 feature is: makes the 3rd servo piston 33 by two the 3rd springs 34
Centering when hydraulic fluid pressure is equal in three left chamber 31 and the 3rd right chamber room 32, because two the second control units 50 control respectively
The pressure of the pressure oil in the 3rd left chamber 31 and the 3rd right chamber room 32, and the second valve element 51 in two the second control units 50
The mobile mobile synchronization with the first push rod 15, i.e. when the first push rod 15 moves to left, the second valve element 51 also moves to left, when the second valve element
51 when moving to left, and the pressure of the hydraulic oil in the 3rd right chamber room 32 increases, and the pressure of the hydraulic oil in the 3rd left chamber 31 is less,
So that the second push rod 35 moves to left, when the first push rod 15 moves to right, the second valve element 51 also moves to right, when the second valve element 51 moves to right
When, the pressure of the hydraulic oil in the 3rd right chamber room 32 reduces, and the pressure of the hydraulic oil in the 3rd left chamber 31 increases, so that
Obtain the second push rod 35 to move to right.So that the first push rod 15 passes through the dynamic of two second control unit 50 indirect control the second push rod 35
Make, and then control the discharge capacity of plunger variable pump 70.Control the pressure of the hydraulic oil of two chambers above by two second control unit 50
Power, to control the displacement of the second push rod 35, controls more accurate, and the second push rod 35 is because of the hydraulic oil rigidly pushing and pressing (pressure of hydraulic oil
Contracting very little), thus the mobile response of the second push rod 35 sensitiveer that is to say, that the second push rod 35 is servo-actuated with the first push rod 15
Sensitivity higher.
Above-mentioned off-load unit 90 effect is: when system pressure increases to the peak of preset pressure because of certain reason
(within this peak, the components and parts of hydraulic system will not be damaged, and the components and parts exceeding this peak hydraulic system can be sent out
Raw damage), off-load unit 90 makes the gradient of the swash plate 71 of plunger variable pump 70 be zeroed, so that the discharge capacity of plunger variable pump 70
At once vanishing, so that system pressure is reduced to zero at once, thus timely and effectively protect exist including plunger variable pump 70
The components and parts of interior hydraulic system.
Preferably, off-load unit 90 is connected with system pipeline for oil-in, the list that oil-out is connected with the 3rd right chamber room 32
Item valve, the setting pressure of check valve is more than the rated pressure of hydraulic system.So, when system pressure is pre- because certain reason increases to
If during the peak of pressure, now, system pressure has exceeded the setting pressure of check valve, individual event valve turns at once, system hydraulic pressure
Oil is directly entered the 3rd right chamber room 32, at once promotes the 3rd servo piston 33 to move to left to the leftmost side, makes the oblique of plunger variable pump 70
The gradient of disk 71 is zeroed at once, so that plunger variable pump 70 dallies and not fuel feeding.
Described in two, the second control unit 50 is proportional reversing valve, the oil-out of proportional reversing valve described in two respectively with described
3rd left chamber 31 connects with described 3rd right chamber room 32, and oil-in is connected with system hydraulic oil, and when the second valve element described in two
51 when being moved to the left with described first push rod 15 level, the oil-out pressure connecting with described 3rd left chamber 31 be less than with described
The oil-out pressure of the 3rd right chamber room 32 connection；When the second valve element 51 described in two moves right with described first push rod 15 level
When, the oil-out pressure connecting with described 3rd left chamber 31 is more than the oil-out pressure connecting with described 3rd right chamber room 32.
Claims (3)
1. a kind of electrohydraulic controlling mechanism of relief, adjusts the pressure of hydraulic system for the discharge capacity by changing plunger variable pump
Power is it is characterised in that include:
First servo unit, it includes being formed with the first housing of first chamber, is arranged in described first chamber, and will be described
First chamber is divided into the first left chamber and the first servo piston of the first right chamber room；Described first left chamber interior be provided with for
Push against the first spring of described first servo piston；
Second servo unit, it includes being formed with the second housing of second chamber, is arranged in described second chamber, and will be described
Second chamber is divided into the second left chamber and the second servo piston of the second right chamber room, described second left chamber and described second right side
Within the chamber is respectively provided with second spring；Wherein:
Described first servo piston and described second servo piston are connected with the first push rod jointly；
3rd servo unit, it includes being formed with the 3rd housing of the 3rd chamber, is arranged on described 3rd within the chamber, and will be described
3rd chamber is divided into the 3rd servo piston of the 3rd left chamber and the 3rd right chamber room and is fixed with described 3rd servo piston
The second push rod connecting, described 3rd left chamber and described 3rd right chamber interior are respectively provided with the 3rd spring, and described second push rod is used
In the described swash plate of driving, and: when described second push rod moves to left, the gradient of described swash plate reduces, and described second push rod moves to right
When, the gradient of described swash plate increases；
First control unit, it includes being formed with the first valve body of the first valve pocket and is arranged in described first valve body first
Valve element, described first control unit is used for system hydraulic oil being each led into described second left chamber and the second right chamber room and passing through
Described first valve element of movement controls the pressure of the hydraulic oil of described second left chamber and the second right chamber interior；
Two second control units, the second control unit described in two is arranged side by side and all includes being formed with the second valve body of the second valve pocket
And be arranged on the second valve element in described second valve pocket, described first push rod be located at described in two between second valve element and simultaneously with
Described in two, the second valve element connects, and system hydraulic oil passes through one of described second control unit to described 3rd left chamber
Fuel feeding, by the second control unit another described to described 3rd right chamber room fuel feeding, so that:
When described first push rod is moved to the left, described first push rod drives the second valve element described in two to move so that being passed through institute simultaneously
The pressure stating the indoor hydraulic oil of the 3rd right chamber is more than the pressure of the indoor hydraulic oil of described 3rd left chamber, when described first push rod
When moving right, described first push rod drives the second valve element described in two to move so that being passed through the indoor liquid of described 3rd right chamber simultaneously
The pressure of force feed is less than the pressure of the indoor hydraulic oil of described 3rd left chamber；
Two position three way directional control valve, it has is made system hydraulic oil be connected with described first servo unit and watches with described second simultaneously
Take the primary importance of unit disconnection and so that system hydraulic oil is disconnected and watch with described second simultaneously with described first servo unit
Take the second position of unit connection；
The electrohydraulic controlling mechanism of described relief also includes
Fixed pressure reducing valve, system hydraulic oil is divided into two-way and each leads into described first left chamber and described first right chamber room, described
Fixed pressure reducing valve is arranged on the pipeline being passed through described first left chamber, so that the pressure of the indoor hydraulic oil of described first left chamber
Keep constant, so that the indoor pressure of hydraulic oil of the described first right chamber pressure of hydraulic oil indoor with described first left chamber
The increase of the pressure with system hydraulic oil for the difference and increase；
Controller, the steepness signals that it is used for according to angle sensor feedback in described plunger variable pump control described first control
Unit, with when controller obtains steepness signals and is more than predetermined slant, described controller controls the of described first control unit
One valve element is mobile so that the pressure of the indoor hydraulic oil of described second left chamber is less than the pressure of the indoor hydraulic oil of described second right chamber
Power；So that when controller obtains steepness signals and is less than predetermined slant, described controller controls the first valve element of the first control unit
Move so that the pressure of the indoor hydraulic oil of described second left chamber is more than the pressure of the indoor hydraulic oil of described second right chamber；
Off-load unit, it is used for, when system pressure exceeds default peak, forcing the gradient of the swash plate of described plunger variable pump
Zero.
2. the electrohydraulic controlling mechanism of relief according to claim 1 is it is characterised in that the second control unit described in two is equal
For proportional reversing valve, the oil-out of proportional reversing valve described in two is respectively with described 3rd left chamber and described 3rd right chamber room even
Logical, oil-in is connected with system hydraulic oil, and when the second valve element described in two is moved to the left with described first push rod level, with institute
The oil-out pressure stating the connection of the 3rd left chamber is less than the oil-out pressure with described 3rd right chamber；When described in two second
When valve element moves right with described first push rod level, the oil-out pressure that connected with described 3rd left chamber is more than and described the
The oil-out pressure of three right chamber.
3. the electrohydraulic controlling mechanism of relief according to claim 1 is it is characterised in that described off-load unit is oil-in
Connect with system pipeline, the individual event valve of oil-out and described 3rd right chamber, the setting pressure of described check valve is more than liquid
The rated pressure of pressure system.
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| CN201611036763.7A CN106369000B (en) | 2016-11-22 | 2016-11-22 | The electrohydraulic controlling mechanism of relief |
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|---|---|---|---|
| CN201611036763.7A CN106369000B (en) | 2016-11-22 | 2016-11-22 | The electrohydraulic controlling mechanism of relief |
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| CN106369000A true CN106369000A (en) | 2017-02-01 |
| CN106369000B CN106369000B (en) | 2018-02-06 |
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| CN201611036763.7A Active CN106369000B (en) | 2016-11-22 | 2016-11-22 | The electrohydraulic controlling mechanism of relief |
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| CN203891108U (en) * | 2014-04-15 | 2014-10-22 | 华侨大学 | Automatic idling system of electro-hydraulic mixing driving engineering machine |
| JP2015175491A (en) * | 2014-03-17 | 2015-10-05 | 日立建機株式会社 | Hydraulic pressure driving device for construction machine |
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|---|---|---|---|---|
| US4895182A (en) * | 1988-01-11 | 1990-01-23 | Hoerbiger Hydraulik Gmbh | Hydraulic control unit |
| CN2617566Y (en) * | 2002-12-27 | 2004-05-26 | 中国石化齐鲁股份有限公司 | Electrohydraulic ratio controlling rubber briquetting machine |
| CN1800654A (en) * | 2005-12-20 | 2006-07-12 | 武汉科技大学 | Asymmetric cylinder closed-loop speed system controlled by electro-hydraulic proportional pump |
| CN200974743Y (en) * | 2006-10-21 | 2007-11-14 | 江苏永丰机械有限责任公司 | Energy-saving tower machine hydraulic stepless change control system |
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| Publication number | Publication date |
|---|---|
| CN106369000B (en) | 2018-02-06 |
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