CN106523457B - Electrohydraulic controlling mechanism - Google Patents
Electrohydraulic controlling mechanism Download PDFInfo
- Publication number
- CN106523457B CN106523457B CN201611035936.3A CN201611035936A CN106523457B CN 106523457 B CN106523457 B CN 106523457B CN 201611035936 A CN201611035936 A CN 201611035936A CN 106523457 B CN106523457 B CN 106523457B
- Authority
- CN
- China
- Prior art keywords
- pressure
- chamber
- hydraulic oil
- variable pump
- servo piston
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Active
Links
- 230000007246 mechanism Effects 0.000 title claims abstract description 27
- 239000010720 hydraulic oil Substances 0.000 claims description 57
- 230000008859 change Effects 0.000 claims description 28
- 239000003921 oil Substances 0.000 claims description 18
- 230000003993 interaction Effects 0.000 claims description 4
- 239000000446 fuel Substances 0.000 claims description 3
- XEEYBQQBJWHFJM-UHFFFAOYSA-N Iron Chemical compound [Fe] XEEYBQQBJWHFJM-UHFFFAOYSA-N 0.000 claims 2
- 229910052742 iron Inorganic materials 0.000 claims 1
- 230000001276 controlling effect Effects 0.000 description 22
- 238000000034 method Methods 0.000 description 17
- 230000001105 regulatory effect Effects 0.000 description 11
- 230000000875 corresponding effect Effects 0.000 description 9
- 230000007423 decrease Effects 0.000 description 7
- 239000012530 fluid Substances 0.000 description 6
- 238000006073 displacement reaction Methods 0.000 description 5
- 239000007788 liquid Substances 0.000 description 4
- 230000008569 process Effects 0.000 description 4
- 230000004048 modification Effects 0.000 description 2
- 238000012986 modification Methods 0.000 description 2
- 230000009471 action Effects 0.000 description 1
- 230000032683 aging Effects 0.000 description 1
- 230000009286 beneficial effect Effects 0.000 description 1
- 230000033228 biological regulation Effects 0.000 description 1
- 230000002596 correlated effect Effects 0.000 description 1
- 230000006837 decompression Effects 0.000 description 1
- 238000010586 diagram Methods 0.000 description 1
- 230000005611 electricity Effects 0.000 description 1
- 239000002828 fuel tank Substances 0.000 description 1
- 230000000977 initiatory effect Effects 0.000 description 1
- 230000009467 reduction Effects 0.000 description 1
- 230000000630 rising effect Effects 0.000 description 1
- 230000011218 segmentation Effects 0.000 description 1
- 230000035945 sensitivity 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
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B1/00—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders
- F04B1/12—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis
- F04B1/26—Control
- F04B1/28—Control of machines or pumps with stationary cylinders
- F04B1/29—Control of machines or pumps with stationary cylinders by varying the relative positions of a swash plate and a cylinder block
- F04B1/295—Control of machines or pumps with stationary cylinders by varying the relative positions of a swash plate and a cylinder block by changing the inclination of the swash plate
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B1/00—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders
- F04B1/12—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis
- F04B1/26—Control
- F04B1/30—Control of machines or pumps with rotary cylinder blocks
- F04B1/32—Control of machines or pumps with rotary cylinder blocks by varying the relative positions of a swash plate and a cylinder block
- F04B1/324—Control of machines or pumps with rotary cylinder blocks by varying the relative positions of a swash plate and a cylinder block by changing the inclination of the swash plate
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B11/00—Servomotor systems without provision for follow-up action; Circuits therefor
- F15B11/16—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors
-
- 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
- F15B13/16—Special measures for feedback, e.g. by a follow-up device
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B2211/00—Circuits for servomotor systems
- F15B2211/20—Fluid pressure source, e.g. accumulator or variable axial piston pump
- F15B2211/205—Systems with pumps
- F15B2211/2053—Type of pump
- F15B2211/20546—Type of pump variable capacity
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Fluid Mechanics (AREA)
- Control Of Positive-Displacement Pumps (AREA)
Abstract
The invention discloses a kind of electrohydraulic controlling mechanisms, it include: the first servo unit and fixed pressure reducing valve, which to generate pressure difference, to generate pressure signal, the pressure signal 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.
Description
Technical field
The present invention relates to field of electromechanical technology 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 first servo piston is moved to the left, first servo piston makes the swash plate of the plunger variable pump
Gradient reduce；When first servo piston moves right, first servo piston makes the plunger variable pump
The gradient of swash plate increases；Wherein:
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.
Preferably, further include the second servo unit and control unit, be provided with the first push rod on first servo piston；
Second servo unit includes the second shell for being formed with second chamber, is arranged in the second chamber, and
The second chamber is divided into the second servo piston of the second left chamber and the second right chamber and is arranged and is watched described second
The second push rod on piston is taken, second spring is provided in second left chamber, second push rod is connect with the swash plate,
And:
When second push rod is moved to the left, second push rod drives the gradient of the swash plate to reduce, and described second
Push rod to the right when, second push rod drives the gradient of the swash plate to increase；
Described control unit includes the spool for being formed with the valve body of valve chamber and being arranged in the valve chamber, the spool by
The first push rod driving, and system hydraulic oil passes through described control unit to the second right chamber fuel feeding, so that:
When first push rod is moved to the left, first push rod drives the spool movement so that second right chamber
The pressure of indoor hydraulic oil increases；When first push rod moves right, first push rod drives the spool mobile
So that the pressure of the indoor hydraulic oil of the second right chamber reduces.
Preferably, described control unit is proportional reversing valve, the oil outlet of the proportional reversing valve and second right chamber
Room connection, oil inlet are connected to system hydraulic oil, and when the spool is moved to the left, and the pressure of the hydraulic oil of oil outlet increases
So that the pressure of the indoor hydraulic oil of the second right chamber increases；When the spool moves right, the hydraulic oil of oil outlet
Pressure reduces so that the pressure of the indoor hydraulic oil of the second right chamber reduces.
Preferably, the electrohydraulic controlling mechanism further include:
The opposite electromagnet pair of homopolarity is arranged in second left chamber, and the electromagnet is to by changing thereon
Electric current is to change the electromagnetic push to second servo piston.
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.
Detailed description of the invention
Fig. 1 is the structural schematic diagram of electrohydraulic controlling mechanism of the invention.
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 50 are usually become by changing the gradient of swash plate 51 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 51 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: in system each Hydraulic Elements draining, oil leak and Hydraulic Elements to hydraulic oil generate not
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 51 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 51 individually
Adjust a certain predetermined slant.
For example, the gradient of swash plate 51 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 51 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 50
In room, the stroke for changing connecting rod by the hydraulic fluid pressure size to change the gradient of swash plate 51, and then changes plunger
The discharge capacity of variable pump 50.
For another example on the one hand, the gradient of the swash plate 51 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 51；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 51 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 51
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 51 makes variable pump adjusting to corresponding discharge capacity to a certain gradient, on variable pump
Although swash plate 51 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 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
50 discharge capacity adjusts the pressure of hydraulic system, which specifically includes: the first servo unit 10 and definite value decompression
Valve 40.
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 15 of the first servo piston 13, wherein
The gradient of the swash plate 51 of the movement and plunger variable pump 50 of first servo piston 13 is configured to following interaction relation:
When the first servo piston 13 is moved to the left, the first servo piston 13 makes the oblique of the swash plate 51 of plunger variable pump 50
Degree reduces；When the first servo piston 13 moves right, the first servo piston 13 makes the oblique of the swash plate 51 of plunger variable pump 50
Degree increases；Wherein:
System hydraulic oil is divided into two-way and each leads into the first left chamber 11 and the first right chamber 12, and fixed pressure reducing valve 40 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 constant, so that first
The difference of the pressure of hydraulic oil in the pressure of hydraulic oil in right chamber 12 and the first left chamber 11 with system hydraulic oil pressure
The increase of power and increase.
In this way, when system pressure increases (for some reason, discharge capacity including plunger variable pump 50 increase, control element
Hydraulic fluid port becomes smaller) when, the pressure of the hydraulic oil in the first right chamber 12 increases, and the pressure of the hydraulic oil in the first left chamber 11
It is constant because being controlled pressure by fixed pressure reducing valve 40, so that the first servo piston 13 is moved to the left, the first servo piston 13
Movement is so that the gradient of the swash plate 51 of plunger variable pump 50 reduces；To which the discharge capacity of plunger variable pump 50 reduces, plunger variable pump
50 discharge capacity offsets the system pressure of rising after reducing.When the first servo piston 13 moves right, the first servo piston 13 makes
The gradient for obtaining the swash plate 51 of plunger variable pump 50 increases；When system pressure reduces (for some reason, including plunger variable pump 50
Discharge capacity reduces, the hydraulic fluid port of control element becomes larger) when, the pressure of the hydraulic oil in the first right chamber 12 reduces, and the first left chamber
The pressure of hydraulic oil in room 11 is because constant by the control of fixed pressure reducing valve 40 pressure, so that the first servo piston 13 moves right
Dynamic, the movement of the first servo piston 13 is so that the gradient of the swash plate 51 of plunger variable pump 50 increases, thus plunger variable pump 50
Discharge capacity increases, and the discharge capacity of plunger variable pump 50 increases the system pressure of post-compensation decline.
Electrohydraulic controlling mechanism of the invention establishes the relationship between 50 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 50 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
Be: although there are many factor for influencing system pressure, system pressure can be carried out by changing the discharge capacity of plunger variable pump 50
Change and adjusts.
Relationship between 50 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 50 is passed to so that 50 discharge capacity of plunger variable pump changes, and the change of 50 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 50 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 50, and establishes system
The key of pressure and the servo relationship of plunger variable pump 50 is: definite value is arranged on the system pipeline for leading to the first left chamber 11
Pressure reducing valve 40, the fixed pressure reducing valve 40 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: system pressure required for hydraulic system, i.e. rated pressure, in the first left chamber 11
The difference of the pressure of hydraulic oil) under, which is offset by the first spring 15, 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 51, to change plunger variable pump
50 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 50 discharge capacity of plunger variable pump, and when the system pressure decreases, the first servo piston 13 makes
50 discharge capacity of plunger variable pump increases.
The fixed pressure reducing valve 40 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 50.
The fixed pressure reducing valve 40 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 15 is certain, when fixed pressure reducing valve 40 sets predetermined value, system pressure is also determined that
, reason is: when fixed pressure reducing valve 40 sets predetermined value as A, 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 15 answered, otherwise
One servo piston 13 can move.That is, system pressure can generate one after 40 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 40 setting value
Pressure value.Therefore, the fixed pressure reducing valve 40 of electrohydraulic controlling mechanism of the invention is also equipped with the function of regulating system rated pressure.
Electrohydraulic controlling mechanism of the invention due to being provided with fixed pressure reducing valve 40, so as to accurate according to system pressure and
By the discharge capacity of adjustment plunger variable pump 50 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.
To realize the above-mentioned interaction relation of the gradient of the movement of the first servo piston 13 and the swash plate 51 of plunger variable pump 50:
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 51 of plunger variable pump 50
It is small；When the first servo piston 13 moves right, the first servo piston 13 increases the gradient of the swash plate 51 of plunger variable pump 50
Greatly；
Electrohydraulic controlling mechanism of the invention further includes the second servo unit 20 and control unit 30, on the first servo piston 13
It is provided with the first push rod 14；
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 left chamber 21 and is arranged in the second servo piston 23
On the second push rod 24, be provided with second spring 25 in the second left chamber 21, the second push rod 24 is connect with swash plate 51, and:
When the second push rod 24 is moved to the left, the second push rod 24 drives the gradient of swash plate 51 to reduce, and the second push rod 24 is to the right
When, the second push rod 24 drives the gradient of swash plate 51 to increase；
Control unit 30 includes the spool 31 for being formed with the valve body of valve chamber and being arranged in valve chamber, and spool 31 is pushed away by first
Bar 14 drives, and system hydraulic oil passes through control unit 30 to 21 fuel feeding of the second left chamber, so that:
When the first push rod 14 is moved to the left, the first push rod 14 moves the liquid so that in the second left chamber 21 with movable valve plug 31
The pressure of pressure oil increases；When the first push rod 14 moves right, the first push rod 14 is mobile so that the second left chamber with movable valve plug 31
The pressure of hydraulic oil in 21 reduces.
In this way, the first push rod 14 is moved to the left when the hydraulic increase of system, the second push rod 24 is made by control unit 30
Also it is moved to the left, so that the gradient of swash plate 51 reduces, the discharge capacity of plunger variable pump 50 reduces；When the hydraulic reduction of system,
First push rod 14 moves right, and by control unit 30 second push rod 24 is also moved right, so that swash plate 51 is oblique
Degree increases, and the discharge capacity of plunger variable pump 50 increases.
In a preferred embodiment of the invention, control unit 30 is proportional reversing valve, the oil outlet of proportional reversing valve
It is connected to the second left chamber 21, oil inlet is connected to system hydraulic oil, and when spool 31 is moved to the left, the hydraulic oil of oil outlet
Pressure increase so that the pressure of hydraulic oil in the second left chamber 21 increases；When spool 31 moves right, the liquid of oil outlet
The pressure of pressure oil reduces so that the pressure of the hydraulic oil in the second left chamber 21 reduces.
In a preferred embodiment of the invention, electrohydraulic controlling mechanism further includes that the opposite electromagnet 26 of homopolarity is right, should
Electromagnet to be arranged in the second left chamber 21, electromagnet 26 to by change thereon electric current to change to the second servo piston 23
Electromagnetic push, which changes the pretightning force of second spring 25 by changing electromagnetic push to 26, so that second
The every Moving Unit of servo piston 23 be displaced required for hydraulic pressure increase and decrease amount change, in this way, if the magnet to 26 magnetic
When repulsion increases, the pretightning force of second spring 25 reduces, and then 23 Moving Unit of the second servo piston is made to be displaced required liquid
The increase and decrease amount of pressure pressure reduces, in other words every increase and decrease unit hydraulic pressure, and the mobile displacement of the second servo piston 23 is bigger, thus
So that the second servo piston 23 is more sensitive to hydraulic pressure variation, to directly enhance the discharge capacity of pilot plunger variable pump 50
Sensitivity；If the magnet reduces 26 magnetic repulsion, the pretightning force of second spring 25 increases, and then makes the second servo piston
The increase and decrease amount of hydraulic pressure required for 23 Moving Units are displaced increases, in other words every increase and decrease unit hydraulic pressure, the second servo
The mobile displacement of piston 23 is smaller, even if thus when changing the second servo piston 23 in larger pressure limit, the second servo
Piston 23 can also be in the discharge capacity for forming direct pilot plunger variable pump 50 in range, to increase the adjusting of system pressure
Range.
Above embodiments are only exemplary embodiment of the present invention, are not used in the limitation present invention, protection scope of the present invention
It is defined by the claims.Those skilled in the art can within the spirit and scope of the present invention make respectively the present invention
Kind modification or equivalent replacement, this modification or equivalent replacement also should be regarded as being within the scope of the present invention.
Claims (1)
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, comprising:
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 first servo piston is moved to the left, first servo piston makes the oblique of the swash plate of the plunger variable pump
Degree reduces；When first servo piston moves right, first servo piston makes the swash plate of the plunger variable pump
Gradient increase；Wherein:
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 and control unit are provided with the first push rod on first servo piston；
Second servo unit includes the second shell for being formed with second chamber, is arranged in the second chamber, and by institute
Stating second chamber is divided into the second servo piston of the second left chamber and the second right chamber and setting living in second servo
The second push rod beyond the Great Wall is provided with second spring in second left chamber, and second push rod is connect with the swash plate, and
And:
When second push rod is moved to the left, second push rod drives the gradient of the swash plate to reduce, second push rod
When to the right, second push rod drives the gradient of the swash plate to increase；
Described control unit includes the spool for being formed with the valve body of valve chamber and being arranged in the valve chamber, and the spool is by described
The driving of first push rod, and system hydraulic oil passes through described control unit to the second right chamber fuel feeding, so that:
When first push rod is moved to the left, first push rod drives the spool movement so that in second right chamber
Hydraulic oil pressure increase；When first push rod moves right, first push rod drive the spool mobile so that
The pressure of the indoor hydraulic oil of second right chamber reduces；
Described control unit is proportional reversing valve, and the oil outlet of the proportional reversing valve is connected to second right chamber, oil inlet
It mouthful is connected to system hydraulic oil, and when the spool is moved to the left, the pressure increase of the hydraulic oil of oil outlet is so that described the
The pressure of the indoor hydraulic oil of two right chambers increases；When the spool moves right, the pressure of the hydraulic oil of oil outlet reduce with
Reduce the pressure of the indoor hydraulic oil of the second right chamber；
The opposite electromagnet pair of homopolarity is set in second left chamber, one of electromagnet of the electromagnet pair
Second servo piston is set to towards on one end of second left chamber, the another one electromagnetism of the electromagnet pair
Iron is set in the second shell and opposite with the electromagnet being set on second servo piston, in which:
The electromagnet to by change thereon electric current to change the electromagnetic push to second servo piston.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201611035936.3A CN106523457B (en) | 2016-11-22 | 2016-11-22 | Electrohydraulic controlling mechanism |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201611035936.3A CN106523457B (en) | 2016-11-22 | 2016-11-22 | Electrohydraulic controlling mechanism |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN106523457A CN106523457A (en) | 2017-03-22 |
| CN106523457B true CN106523457B (en) | 2019-05-10 |
Family
ID=58356037
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201611035936.3A Active CN106523457B (en) | 2016-11-22 | 2016-11-22 | Electrohydraulic controlling mechanism |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN106523457B (en) |
Families Citing this family (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN112097740A (en) * | 2020-09-15 | 2020-12-18 | 山东工业职业学院 | Walking type automatic leveling surveying instrument |
Citations (9)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US5809157A (en) * | 1996-04-09 | 1998-09-15 | Victor Lavrov | Electromagnetic linear drive |
| JP2002198218A (en) * | 2000-10-19 | 2002-07-12 | Genesis:Kk | Magnetic force actuator |
| CN102900643A (en) * | 2011-07-29 | 2013-01-30 | 波克兰液压工业设备公司 | Hydraulic control circuit |
| DE102012012141A1 (en) * | 2012-06-20 | 2013-12-24 | Robert Bosch Gmbh | Hydrostatic axial piston machine for use as e.g. hydro pump in hybrid drive for driving vehicle, has feeding back device comprising torsion and/or spiral springs, which are directly or indirectly clamped between swash plate and adjuster |
| CN103486101A (en) * | 2013-09-29 | 2014-01-01 | 徐州重型机械有限公司 | Controlling method and device for improving response speed of hydraulic oil pump |
| CN203383788U (en) * | 2013-04-27 | 2014-01-08 | 王文雯 | Flywheel energy-saving hydraulic pumping unit |
| CN205225909U (en) * | 2015-11-04 | 2016-05-11 | 潍柴动力股份有限公司 | All -hydraulic travel drive system |
| CN205446237U (en) * | 2016-02-17 | 2016-08-10 | 潍柴动力股份有限公司 | Hydraulic pump control ware |
| CN105960493A (en) * | 2014-02-07 | 2016-09-21 | 卡特彼勒环球矿业有限责任公司 | Hydraulic control system and method |
Family Cites Families (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US3444689A (en) * | 1967-02-02 | 1969-05-20 | Weatherhead Co | Differential pressure compensator control |
| JPH0849659A (en) * | 1994-08-05 | 1996-02-20 | Hitachi Constr Mach Co Ltd | Hydraulic pump flow controller |
| US6109030A (en) * | 1998-02-13 | 2000-08-29 | Sauer Inc. | Apparatus and method for ganging multiple open circuit pumps |
| DE20114466U1 (en) * | 2001-09-01 | 2002-01-03 | Eto Magnetic Kg | Electromagnetic actuator |
-
2016
- 2016-11-22 CN CN201611035936.3A patent/CN106523457B/en active Active
Patent Citations (9)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US5809157A (en) * | 1996-04-09 | 1998-09-15 | Victor Lavrov | Electromagnetic linear drive |
| JP2002198218A (en) * | 2000-10-19 | 2002-07-12 | Genesis:Kk | Magnetic force actuator |
| CN102900643A (en) * | 2011-07-29 | 2013-01-30 | 波克兰液压工业设备公司 | Hydraulic control circuit |
| DE102012012141A1 (en) * | 2012-06-20 | 2013-12-24 | Robert Bosch Gmbh | Hydrostatic axial piston machine for use as e.g. hydro pump in hybrid drive for driving vehicle, has feeding back device comprising torsion and/or spiral springs, which are directly or indirectly clamped between swash plate and adjuster |
| CN203383788U (en) * | 2013-04-27 | 2014-01-08 | 王文雯 | Flywheel energy-saving hydraulic pumping unit |
| CN103486101A (en) * | 2013-09-29 | 2014-01-01 | 徐州重型机械有限公司 | Controlling method and device for improving response speed of hydraulic oil pump |
| CN105960493A (en) * | 2014-02-07 | 2016-09-21 | 卡特彼勒环球矿业有限责任公司 | Hydraulic control system and method |
| CN205225909U (en) * | 2015-11-04 | 2016-05-11 | 潍柴动力股份有限公司 | All -hydraulic travel drive system |
| CN205446237U (en) * | 2016-02-17 | 2016-08-10 | 潍柴动力股份有限公司 | Hydraulic pump control ware |
Also Published As
| Publication number | Publication date |
|---|---|
| CN106523457A (en) | 2017-03-22 |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| CN106762926B (en) | The electrohydraulic controlling mechanism of pressure-adjustable and off-load | |
| CN104728196B (en) | The Electrical hydrostatic actuator of load-sensitive | |
| CN106640798B (en) | The electrohydraulic controlling mechanism of pressure-adjustable and off-load | |
| US20080145248A1 (en) | Liquid chemical supply system and liquid chemical supply control device | |
| CN106351813B (en) | The inclined disc type electric ratio axial plunger pump of compact and its control method | |
| CN109469594B (en) | Continuous pressure regulating electro-hydraulic proportional axial plunger variable pump for aircraft hydraulic system | |
| CN108431417A (en) | Hydraulic pump control | |
| CN105370958B (en) | A kind of Piezoelectric Ceramic diaphragm type servo valve | |
| CN104819176B (en) | The Electrical hydrostatic actuator of the load-sensitive based on switch valve and hydraulic control one-way valve | |
| CN106194680B (en) | The axial plunger pump installation and control method of a kind of high-precision electric proportional control | |
| CN108443257A (en) | A kind of servo variable mechanism of hydraulic pump motor | |
| CN106523457B (en) | Electrohydraulic controlling mechanism | |
| CN106950690A (en) | A kind of primary mirror of astronomical telescope hydraulic support device | |
| EP3513073A2 (en) | Displacement pump and control system | |
| CN104728193B (en) | The Electrical hydrostatic actuator of load-sensitive | |
| CN106593969B (en) | Electrohydraulic controlling mechanism | |
| CN107061394B (en) | The electrohydraulic controlling mechanism of adjustable pressure susceptibility | |
| CN108331743A (en) | Hydraulic plunger pumpage and alternating power control mechanism | |
| CN106640575B (en) | Electrohydraulic controlling mechanism | |
| CN106499683B (en) | Electrohydraulic controlling mechanism | |
| CN109441906B (en) | Electro-hydraulic proportional load sensitive pump and pump valve combined control servo system | |
| CN116336024A (en) | Electro-hydraulic reversing flow proportional control valve with load flow compensation | |
| CN106369000B (en) | The electrohydraulic controlling mechanism of relief | |
| CN111852810A (en) | Two-dimensional pressure servo variable pump | |
| CN217783888U (en) | Load Sensing Valves, Variable Displacement Hydraulic Pumps and Hydraulic Systems |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| C06 | Publication | ||
| PB01 | Publication | ||
| SE01 | Entry into force of request for substantive examination | ||
| SE01 | Entry into force of request for substantive examination | ||
| TA01 | Transfer of patent application right |
Effective date of registration: 20190221 Address after: 225000 Donghui Town, Fanchuan Town, Jiangdu District, Yangzhou City, Jiangsu Province Applicant after: Tian Jia smart equipment manufacturing Jiangsu Limited by Share Ltd Address before: 300000 Tianjin Hexi District Huanhu Zhonglu Binhu Building Negative Floor B150 Applicant before: Tianjin Haian science and Technology Co., Ltd. |
|
| TA01 | Transfer of patent application right | ||
| GR01 | Patent grant | ||
| GR01 | Patent grant |