CN105275900B - Fluid machine - Google Patents
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- CN105275900B CN105275900B CN201510834477.4A CN201510834477A CN105275900B CN 105275900 B CN105275900 B CN 105275900B CN 201510834477 A CN201510834477 A CN 201510834477A CN 105275900 B CN105275900 B CN 105275900B
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Abstract
The invention relates to the technical field of engineering machines, in particular to a fluid machine. The fluid machine comprises a fluid machine body, a first drive device, a second drive device, a work condition switching device, a first work condition adjusting device and a second work condition adjusting device. The work condition switching device is used for controlling the fluid machine to be switched between a pump work condition and a motor work condition. The first work condition adjusting device is used for enabling the fluid machine to have a pump proportion displacement control function and a pump constant-pressure cut-off control function. The second work condition adjusting device is used for enabling the fluid machine to have a motor proportion displacement control function. The fluid machine can be used as a pump and also as a motor, and has an energy recovery function, multiple control manners such as pump proportion displacement control, pump constant-pressure cut-off control and motor proportion displacement control can be achieved, the structure is simple, and control precision is high.
Description
Technical field
The present invention relates to technical field of engineering machinery, more particularly to a kind of fluid machinery.
Background technology
In the prior art, many engineering machinery be faced with how the problem of energy saving.For example, autocrane and rubbish
The running on wheels class engineering machinery such as transport vehicle, product quantity is big, and oil consumption is high, and it is poor to discharge, and these result in its power saving urgently
Solve.
And it is a kind of effective of the above-mentioned power saving of solution to pass through to design appropriate device and energy recycle
Technological means.
Cam-type axial piston pump and cam-type axial piston motor are the fluid machineries commonly used in engineering machinery, due to it
Have the advantages that small volume, lightweight, power density are big, easily controllable, therefore be widely used in various hydraulic systems.
Fig. 1-2 shows the operation principle of cam-type axial piston pump.Fig. 3-5 shows cam-type axial piston motor
Operation principle.By Fig. 1-5 as can be seen that cam-type axial piston pump and cam-type axial piston motor include swash plate 1 ', post
Plug 2 ', cylinder body 3 ', oil distribution casing 4 ' and power transmission shaft 5 ', except that the two institute of swash plate 1 ' is inclined in opposite direction, for example, in figure
In 1, the swash plate 1 ' of cam-type axial piston pump deflects δ angles to the left, and so when power transmission shaft 5 ' rotates, inlet port b is from fuel tank
Oil suction, and from force feed mouth a discharge, and 3 in the figure in, the swash plate 1 ' of cam-type axial piston motor deflects β angles to the right, so
In the equidirectional rotation of power transmission shaft 5 ', mouth a oil-feeds are pressed oil, and discharge from oil return opening b.
Accordingly as can be seen that when power transmission shaft it is constant in a kind of rotation direction (left-handed or dextrorotation) and constant high pressure hydraulic fluid port when, if thinking
The switching of pump condition and motor operating conditions is realized, one end of swash plate can be made to be rocked to zero degree plane by the side of zero degree plane
Opposite side, zero degree plane herein refers to the intersection point of the axis by swash plate Yu power transmission shaft 5 ' and perpendicular to power transmission shaft 5 '
The plane of axis.
But in the prior art, most of cam-type axial piston pumps or motor only have corresponding simple function, i.e.,
Pump can only realize pumping function, and motor can only realize motor function, and cannot be converted between pump condition and motor operating conditions, it is impossible to real
Existing energy recovery function；Although or also occurring in that some can realize the liquid switched between pump condition and motor operating conditions
Pressure element, but the structure of existing these Hydraulic Elements is typically complex, it is relatively costly, and its control effect is not yet
Ideal, for example, cannot simultaneously realize pump proportional displacement control function, motor proportional displacement control function and pump constant pressure cutting-off controlling
Function, so as to cause existing this kind of product performance not good, using by larger limitation.Wherein, pump proportional displacement control function
It is the function of referring to the proportion adjustment discharge capacity in pump condition, motor proportional displacement control function is referred in motor operating conditions
The function of proportion adjustment discharge capacity, pump constant pressure cutting-off controlling function refers to that can reach setting danger in pump discharge pressure in pump condition
Discharge capacity automatically becomes zero function after dangerous pressure value.
The content of the invention
The present invention is intended to provide a kind of fluid machinery, it can switch between pump condition and motor operating conditions, and can be same
Shi Shixian pump proportional displacement controls function, motor proportional displacement control function and pump constant pressure cutting-off controlling function.
To achieve these goals, the invention provides a kind of fluid machinery, it includes：
Fluid machinery body, first driving means, the second drive device, operating mode switching device, the first Working condition regulator
With the second Working condition regulator；
Fluid machinery body includes the first working hole, the second working hole and swash plate, and first driving means are connected to swash plate
The hydraulic control end of first end and first driving means connects with the second working hole, the second drive device be connected to the second end of swash plate and
The hydraulic control end of the second drive device is connected with operating mode switching device；
Operating mode switching device can control the hydraulic control end of the second drive device by the first oil circuit and the second oil circuit
It is individual to be connected with the second working hole, when the hydraulic control end of the second drive device is connected by the first oil circuit with the second working hole, fluid
Machinery is in pump condition, and the first working hole oil-feed, the second working hole is fuel-displaced, when the hydraulic control end of the second drive device is by the second oil
When road connects with the second working hole, fluid machinery is in motor operating conditions, and the second working hole oil-feed, the first working hole is fuel-displaced；
First Working condition regulator is arranged on the first oil circuit, and the first Working condition regulator is used to make fluid machinery have pump
Proportional displacement control function and pump constant pressure cutting-off controlling function；
Second Working condition regulator is arranged on the second oil circuit, and the second Working condition regulator can make the fluid machinery have horse
Up to proportional displacement control function.
Alternatively, operating mode switching device includes the first reversal valve, and the first reversal valve includes the first hydraulic fluid port, the second hydraulic fluid port and the
Three hydraulic fluid ports, the first hydraulic fluid port of the first reversal valve is connected with the second Working condition regulator, the second hydraulic fluid port of the first reversal valve and first
Working condition regulator is connected, and the 3rd hydraulic fluid port of the first reversal valve is connected with the hydraulic control end of the second drive device；First reversal valve has
There are the first working position and the second working position, the first hydraulic fluid port cut-off of the first reversal valve when the first reversal valve is in the first working position
And first reversal valve the second hydraulic fluid port and the connection of the 3rd hydraulic fluid port so that the hydraulic control end of the second drive device is by the first oil circuit and the
Two working holes connect, when the first reversal valve be in the second working position when the first reversal valve the first hydraulic fluid port connected with the 3rd hydraulic fluid port and
The second hydraulic fluid port cut-off of the first reversal valve, so that the hydraulic control end of the second drive device is connected by the second oil circuit and the second working hole
It is logical.
Alternatively, the first reversal valve is solenoid directional control valve, and the Electromagnetic Control end of the first reversal valve is used to control first to commutate
Valve switches between the first working position and the second working position.
Alternatively, the first Working condition regulator includes proportion magnetic valve, and proportion magnetic valve includes the first hydraulic fluid port, the second hydraulic fluid port
With the first control end, the first hydraulic fluid port of proportion magnetic valve connects with the second working hole, the second hydraulic fluid port of proportion magnetic valve and first
The second hydraulic fluid port connection of reversal valve, proportion magnetic valve has the first working position, when proportion magnetic valve is in the first working position when ratio
First hydraulic fluid port of example magnetic valve is connected with the second hydraulic fluid port, and the first control end of proportion magnetic valve being capable of proportion adjustment proportion magnetic valve
Valve port size in the first working position, so that fluid machinery has pump proportional displacement control function.
Alternatively, the first Working condition regulator also includes pressure shut-off valve, and the second hydraulic fluid port of proportion magnetic valve passes through pressure
Stop valve is connected with the second hydraulic fluid port of the first reversal valve, and pressure shut-off valve is used to reach setting danger in the pressure of the second working hole
Control makes swash plate be rocked to zero angle by the first oil circuit into the hydraulic fluid pressure in the hydraulic control end of the second drive device during pressure
Degree position, so that fluid machinery has pump constant pressure cutting-off controlling function.
Alternatively, pressure shut-off valve includes the first hydraulic fluid port, the second hydraulic fluid port, the 3rd hydraulic fluid port and control end, pressure shut-off valve
First hydraulic fluid port is connected with the second working hole, and the second hydraulic fluid port of pressure shut-off valve is connected with the second hydraulic fluid port of proportion magnetic valve, pressure
3rd hydraulic fluid port of stop valve is connected with the second hydraulic fluid port of the first reversal valve；Pressure shut-off valve has the first working position and the second work
Position, when pressure shut-off valve is in the first working position, the first hydraulic fluid port of pressure shut-off valve ends and the second of pressure shut-off valve is oily
Mouth is connected with the 3rd hydraulic fluid port, when pressure shut-off valve is in the second working position, first hydraulic fluid port and the 3rd hydraulic fluid port of pressure shut-off valve
The second hydraulic fluid port cut-off of connection and pressure shut-off valve；The control end of pressure shut-off valve is connected so that when the second work with the second working hole
The control end of pressure shut-off valve being capable of control pressure cut-out Vavle switching when the pressure for making mouth reaches the setting pressure of pressure shut-off valve
To the second working position.
Alternatively, the first Working condition regulator also includes swash plate angular displacement feedback mechanism, swash plate angular displacement feedback mechanism energy
Enough angular displacements by swash plate in pump condition feed back to second control end relative with its first control end of proportion magnetic valve.
Alternatively, the second control end of proportion magnetic valve is provided with the first feedback spring, and swash plate angular displacement feedback mechanism can
Angular displacement of the swash plate in pump condition is converted to the deflection of the first feedback spring.
Alternatively, the second Working condition regulator can also be such that the hydraulic control end of the second drive device is connected with fuel tank, so that stream
Body machinery has pump maximum pump discharge control function.
Alternatively, the second Working condition regulator includes the second reversal valve, and the second reversal valve includes the first hydraulic fluid port, the second hydraulic fluid port
With the first control end, the first hydraulic fluid port of the second reversal valve connects with the second working hole, the second hydraulic fluid port of the second reversal valve and first
The first hydraulic fluid port connection of reversal valve, the second reversal valve has the first working position, when the second reversal valve is in the first working position the
First hydraulic fluid port of two reversal valves and the second hydraulic fluid port are connected, and the first control end of the second reversal valve being capable of the reversal valve of proportion adjustment second
Valve port size during in the first working position, so that fluid machinery has motor proportional displacement control function.
Alternatively, the second reversal valve also includes the 3rd hydraulic fluid port, and the 3rd hydraulic fluid port of the second reversal valve is connected with fuel tank, when second
When reversal valve is in the first working position, the 3rd hydraulic fluid port cut-off of the second reversal valve；Second reversal valve also has the second working position, when
The first hydraulic fluid port cut-off of the second reversal valve and the second hydraulic fluid port of the second reversal valve and the when second reversal valve is in the second working position
Three hydraulic fluid ports are connected；First control end of the second reversal valve can control the second reversal valve to switch to the second working position, so that fluid
Machinery has pump maximum pump discharge control function.
Alternatively, the angular displacement that swash plate angular displacement feedback mechanism can also be by swash plate in motor operating conditions feeds back to second and changes
To second control end relative with its first control end of valve.
Alternatively, the second control end of the second reversal valve is provided with the second feedback spring, and swash plate angular displacement feedback mechanism can
Angular displacement of the swash plate in motor operating conditions is converted to the deflection of the second feedback spring.
Alternatively, fluid machinery also includes the first stopping means, and the first stopping means is used to cut off second in pump condition
Active force of the feedback spring to swash plate angular displacement feedback mechanism；And/or, fluid machinery also includes the second stopping means, the second limit
Position device is used to cut off active force of first feedback spring to swash plate angular displacement feedback mechanism in motor operating conditions.
Alternatively, first driving means include the first plunger case, and the plunger of the first plunger case is connected with the first end of swash plate,
The hydraulic control end of first driving means is arranged on the rodless cavity of the first plunger case so that the rodless cavity of the first plunger case and the second work
Mouth connection, and it is provided with back-moving spring in the rodless cavity of the first plunger case；And/or, the second drive device includes the second plunger case, the
The plunger of two plunger cases is connected with the second end of swash plate, and the hydraulic control end of the second drive device is arranged on the rodless cavity of the second plunger case
So that the rodless cavity of the second plunger case is connected with operating mode switching device.
Fluid machinery provided by the present invention, can either use as pump, can be used as motor again, be returned with energy
Function is received, and makes fluid machinery that there is pump proportional displacement control function and pump constant pressure by setting the first Working condition regulator
Cutting-off controlling function, makes the fluid machinery have motor proportional displacement control function by setting the second Working condition regulator.
Additionally, according to further embodiment of the present invention, the second Working condition regulator of the invention can also make the fluid machinery have pump most
Huge discharge control function.Fluid mechanics of the invention are simple, and control accuracy is higher.
By being described in detail to exemplary embodiment of the invention referring to the drawings, further feature of the invention and
Its advantage will be made apparent from.
Brief description of the drawings
In order to illustrate more clearly about the embodiment of the present invention or technical scheme of the prior art, below will be to embodiment or existing
The accompanying drawing to be used needed for having technology description is briefly described, it should be apparent that, drawings in the following description are only this
Some embodiments of invention, for those of ordinary skill in the art, without having to pay creative labor, may be used also
Other accompanying drawings are obtained with according to these accompanying drawings.
Fig. 1 shows the fundamental diagram of axial plunger pump.
Fig. 2 shows the A-A sectional views of Fig. 1.
Fig. 3 shows the fundamental diagram of axial piston motor.
Fig. 4 shows the B-B sectional views of Fig. 3.
Fig. 5 shows the C-C sectional views of Fig. 3.
Fig. 6 shows the hydraulic schematic diagram of the fluid machinery of one embodiment of the invention.
In figure：
1 ', swash plate；2 ', plunger；3 ', cylinder body；4 ', oil distribution casing；5 ', power transmission shaft；
1st, fluid machinery body；2nd, the first plunger case；3rd, the second plunger case；4th, swash plate angular displacement feedback mechanism；6th, first
Reversal valve；7th, pressure shut-off valve；8th, proportion magnetic valve；9th, the second reversal valve；10th, the first stopping means；11st, the second spacing dress
Put；801st, the first feedback spring；901st, the second feedback spring.
Specific embodiment
Below in conjunction with the accompanying drawing in the embodiment of the present invention, the technical scheme in the embodiment of the present invention is carried out clear, complete
Site preparation is described, it is clear that described embodiment is only a part of embodiment of the invention, rather than whole embodiments.Below
Description only actually at least one exemplary embodiment is illustrative, and never conduct is to the present invention and its application or makes
Any limitation.Based on the embodiment in the present invention, those of ordinary skill in the art are without development creative work premise
Lower obtained every other embodiment, belongs to the scope of protection of the invention.
May be not discussed in detail for technology, method and apparatus known to person of ordinary skill in the relevant, but suitable
In the case of, the technology, method and apparatus should be considered as authorizing a part for specification.
In the description of the invention, it is to be understood that the noun of locality such as " forward and backward, upper and lower, left and right ", " it is laterally, vertical,
The indicated orientation such as vertically, level " and " top, bottom " or position relationship are normally based on orientation shown in the drawings or position and close
System, is for only for ease of the description present invention and is described with simplified, and in the case where opposite explanation is not made, these nouns of locality are not indicated that
There must be specific orientation or with specific azimuth configuration and operation with the device or element for implying meaning, therefore can not manage
It is limiting the scope of the invention to solve；The noun of locality " inside and outside " refers to relative to inside and outside each part profile in itself.
In the description of the invention, it is to be understood that limit parts using the word such as " first ", " second ", only
It is for only for ease of and corresponding parts is distinguished, such as without Stated otherwise, above-mentioned word does not have particular meaning, therefore not
It is understood that to be limiting the scope of the invention.
Fig. 6 shows the hydraulic schematic diagram of one embodiment of the invention.Reference picture 6, fluid machinery provided by the present invention,
Including fluid machinery body 1, first driving means, the second drive device, operating mode switching device, the first Working condition regulator and
Two Working condition regulators, wherein：
Fluid machinery body 1 includes the first working hole S, the second working hole B and swash plate, and first driving means are connected to swash plate
First end and the hydraulic control end of first driving means connected with the second working hole B, the second drive device is connected to the second of swash plate
The hydraulic control end of end and the second drive device is connected with operating mode switching device.
Operating mode switching device can control the hydraulic control end of the second drive device by the first oil circuit and the second oil circuit
It is individual to be connected with the second working hole B, when the hydraulic control end of the second drive device is connected by the first oil circuit with the second working hole B, stream
Body machinery is in pump condition, and the first working hole S oil-feeds, the second working hole B is fuel-displaced, when the hydraulic control end of the second drive device is by the
When two oil circuits are connected with the second working hole B, fluid machinery is in motor operating conditions, and the second working hole B oil-feeds, the first working hole S goes out
Oil.
First Working condition regulator is arranged on the first oil circuit, and first Working condition regulator is used to have fluid machinery
Pump proportional displacement control function and pump constant pressure cutting-off controlling function.
Second Working condition regulator is arranged on the second oil circuit, and second Working condition regulator can have a fluid machinery
Motor proportional displacement control function.
Fluid machinery provided by the present invention, can either use as pump, can be used as motor again, be returned with energy
Function is received, and makes fluid machinery that there is pump proportional displacement control function and pump constant pressure by setting the first Working condition regulator
Cutting-off controlling function, makes fluid machinery have motor proportional displacement control function by setting the second Working condition regulator, so that
So that fluid machinery function of the invention is more various, actual demand is more disclosure satisfy that.
Additionally, the second Working condition regulator of the invention can also be such that the hydraulic control end of the second drive device is connected with fuel tank,
So cause that fluid machinery further has pump maximum pump discharge control function, so that fluid machinery of the invention being capable of conduct
Energy recovery pump is used.
The present invention is described further with reference to the embodiment shown in Fig. 6.
As shown in fig. 6, in this embodiment, fluid machinery includes fluid machinery body 1, as first driving means the
One plunger case 2, the second plunger case 3 as the second drive device, the first reversal valve 6 as operating mode switching device, including than
First Working condition regulator, second Working condition regulator including the second reversal valve 9 of example magnetic valve 8 and pressure shut-off valve 7.
In the embodiment, the hydraulic control end of first driving means is arranged on the rodless cavity of the first plunger case 2, the hydraulic control end of the second drive device
The rodless cavity of the second plunger case 3 is arranged on, the first oil circuit is to be provided with ratio electromagnetism between the second working hole B and the first reversal valve 6
The oil circuit of valve 8 and pressure shut-off valve 7, the second oil circuit is that the second reversal valve 9 is provided between the second working hole B and the first reversal valve 6
Oil circuit.
As shown in fig. 6, in this embodiment, fluid machinery body 1 uses the structure of cam-type axial piston pump, and it includes
First working hole S, the second working hole B and swash plate, so without being changed to basic components such as its housing, plunger, cylinder bodies, tie
Structure is simple, and cost is relatively low.
The plunger of the first plunger case 2 is connected, the first plunger case with the first end (being the lower end of swash plate in figure 6) of swash plate
2 rodless cavity is connected with the second working hole B, and is provided with back-moving spring in the rodless cavity of the first plunger case 2, and the back-moving spring is used
Apply to make swash plate be maintained at the active force of initial position in the first end to swash plate.
The plunger of the second plunger case 3 is connected, second plunger with second end (being the upper end of swash plate in figure 6) of swash plate
The rodless cavity of cylinder 3 is connected with the first reversal valve 6.In order to simplify structure and be easy to control, in this embodiment, the second plunger case 3
Diameter of plunger more than the first plunger case 2 diameter of plunger, so can more conveniently by control the second plunger case 3 without bar
The difference of the hydraulic fluid pressure in the rodless cavity of chamber and the first plunger case 2 changes come the pivot angle for controlling swash plate.
For convenience, in following description, the end of swash plate in Fig. 6 second is swung to zero degree plane right side
Extreme position is defined as first angle position, and the end of swash plate second is defined as to the extreme position that zero degree plane left side swings
Second angle position, and the position that swash plate is in when in zero degree plane is defined as zero angle position, zero degree herein is put down
Face still refers to the intersection point of the drive shaft axis by swash plate Yu fluid machinery body 1 and the plane perpendicular with drive shaft axis.
In this embodiment, the second end of swash plate is initially in zero degree plane right side and positioned at first angle position, this
When in pump condition and in pump maximum pump discharge operating mode, the first working hole S oil-feeds, the second working hole B is fuel-displaced, in the second working hole
Control swash plate is rocked to zero angle position when the pressure of B reaches setting dangerous pressure, then can realize pump constant pressure cutting-off controlling work(
Energy；By control the second end of swash plate by zero degree plane right side be rocked to zero degree plane left side can then make fluid machinery by
Pump condition switches to motor operating conditions, now the second working hole B oil-feeds, and the first working hole S is fuel-displaced；And passing ratio regulation swash plate exists
Angular displacement on the left of zero degree plane right side and zero degree plane, then can realize pump proportional displacement control function and motor ratio
Displacement control function.
First reversal valve 6 can control the rodless cavity of the second plunger case 3 by the first oil circuit and the second oil circuit
Connected with the second working hole B, when the rodless cavity of the second plunger case 3 is connected by the first oil circuit with the second working hole B, fluid machine
Tool is in pump condition, and the first working hole S oil-feeds, the second working hole B is fuel-displaced；When the hydraulic control end of the second drive device is by the second oil
When road connects with the second working hole B, fluid machinery is in motor operating conditions, and the second working hole B oil-feeds, the first working hole S is fuel-displaced.
As shown in fig. 6, first reversal valve 6 includes the first hydraulic fluid port, the second hydraulic fluid port and the 3rd hydraulic fluid port, wherein, the first commutation
First hydraulic fluid port of valve 6 is connected with the second reversal valve 9, and the second hydraulic fluid port of the first reversal valve 6 is connected with the first Working condition regulator, the
3rd hydraulic fluid port of one reversal valve 6 is connected with the rodless cavity of the second plunger case 3；And, the first reversal valve 6 have the first working position and
Second working position, when the first reversal valve 6 is in the first working position (i.e. right position in Fig. 6), the first hydraulic fluid port of the first reversal valve 6
Cut-off and the second hydraulic fluid port and the 3rd the hydraulic fluid port connection of the first reversal valve 6, so that the rodless cavity of the second plunger case 3 can be by first
Oil circuit is connected with the second working hole B, and then fluid machinery is in pump condition；When the first reversal valve 6 is in the second working position (i.e.
Left position in Fig. 6) when, the first hydraulic fluid port of the first reversal valve 6 is connected with the 3rd hydraulic fluid port and the second hydraulic fluid port of the first reversal valve 6 cuts
Only, so that the rodless cavity of the second plunger case 3 can be connected by the second oil circuit with the second working hole B, and then make at fluid machinery
In motor operating conditions.
Realize that the control mode that the first reversal valve 6 switches between the first working position and the second working position has various, for example
Hydraulic control, an electronically or mechanically control, in the embodiment shown in fig. 6, using automatically controlled mode, i.e., in this embodiment, the first commutation
Valve 6 is solenoid directional control valve, and it has Electromagnetic Control end Y1, so can be controlled by adjusting the turn on angle of Electromagnetic Control end Y1
First reversal valve 6 switches between the first working position and the second working position, simple and convenient, it is easy to accomplish.
In this embodiment, proportion magnetic valve 8 is used for passing ratio regulation via the first oil circuit into the second plunger case 3
Hydraulic fluid pressure in rodless cavity carrys out angular displacement of the second end of proportion adjustment swash plate on the right side of zero degree plane, right so as to realize
The ratio control of discharge capacity of the fluid machinery in pump condition, even if also fluid machinery has pump proportional displacement control function.
As shown in fig. 6, proportion magnetic valve 8 includes the first hydraulic fluid port, the second hydraulic fluid port, the 3rd hydraulic fluid port and the first control end Y2, its
In, the first hydraulic fluid port of proportion magnetic valve 8 is connected with the second working hole B, and the second hydraulic fluid port of proportion magnetic valve 8 passes through pressure shut-off valve
7 are connected with the second hydraulic fluid port of the first reversal valve 6, and the 3rd hydraulic fluid port of proportion magnetic valve 8 is connected with fuel tank；Proportion magnetic valve 8 has
First working position and the second working position, when proportion magnetic valve 8 is in the first working position (i.e. left position in Fig. 6), ratio electromagnetism
First hydraulic fluid port of valve 8 is connected with the second hydraulic fluid port and the 3rd hydraulic fluid port ends；When proportion magnetic valve 8 is in the second working position (i.e. in Fig. 6
Right position) when, proportion magnetic valve 8 the first hydraulic fluid port cut-off and the second hydraulic fluid port connected with the 3rd hydraulic fluid port；The first of proportion magnetic valve 8
Control end Y2 is used to control proportion magnetic valve 8 to switch between the first working position and the second working position, and passing ratio regulation should
The turn on angle of the first control end Y2 can valve port size of the proportion adjustment proportion magnetic valve 8 in the first working position so that
The hydraulic fluid pressure that proportion adjustment enters in the rodless cavity of the second plunger case 3 via the first oil circuit, realizes the pump ratio of fluid machinery
Example displacement control function.
In order to realize more accurate pump proportional displacement control function, as shown in fig. 6, being also provided with swash plate in this embodiment
Angular displacement feedback mechanism 4, and second control end relative with its first control end Y2 in proportion magnetic valve 8 is provided with the first feedback
Spring 801, wherein, one end of swash plate angular displacement feedback mechanism 4 is connected with the plunger of the second plunger case 3, when the second end of swash plate
When being swung on the right side of zero degree plane, the other end of swash plate angular displacement feedback mechanism 4 can connect with first feedback spring 801
Connect such that it is able to which the angular displacement of swash plate is converted to the deflection of the first feedback spring 801, also will swash plate in pump condition
Angular displacement feeds back to the second control end of proportion magnetic valve 8, and then is engaged to be formed with the first control end Y2 of proportion magnetic valve 8
Closed-loop control to the hydraulic fluid pressure in the rodless cavity for entering the second plunger case 3 via the first oil circuit, further improves pump ratio
The control accuracy of example displacement control.Certainly, swash plate angular displacement feedback mechanism 4 can also for example may be used using other implementation methods
The sensor that can gather swash plate angular displacement signal etc. is thought, as long as the angular displacement that it can be by swash plate in pump condition feeds back to
Second control end of proportion magnetic valve 8 is forming closed-loop control.
In this embodiment, pressure shut-off valve 7 is used to be controlled when the pressure of the second working hole B reaches setting dangerous pressure
Being reached into the hydraulic fluid pressure in the rodless cavity of the second plunger case 3 by the first oil circuit can drive swash plate to be rocked to zero degree
The pressure of position, so allows in pump condition once the pressure of the second working hole B reaches setting dangerous pressure, fluid machinery
Flow can just automatically become zero, so as to realize the pump constant pressure cutting-off controlling function of fluid machinery.
Specifically, as shown in fig. 6, pressure shut-off valve 7 includes the first hydraulic fluid port, the second hydraulic fluid port, the 3rd hydraulic fluid port and control end, its
In, the first hydraulic fluid port of pressure shut-off valve 7 is connected with the second working hole B, the second hydraulic fluid port and the proportion magnetic valve 8 of pressure shut-off valve 7
The connection of the second hydraulic fluid port, the 3rd hydraulic fluid port of pressure shut-off valve 7 connects with the second hydraulic fluid port of the first reversal valve 6；Pressure shut-off valve 7 has
There are the first working position and the second working position, when pressure shut-off valve 7 is in the first working position (i.e. right position in Fig. 6), pressure is cut
First hydraulic fluid port of disconnected valve 7 ends and the second hydraulic fluid port of pressure shut-off valve 7 is connected with the 3rd hydraulic fluid port, such second actuator port B energy
First work of first working position, the first working position of pressure shut-off valve 7 and the first reversal valve 6 of enough passing ratio magnetic valves 8
Make position to be connected with the rodless cavity of the second plunger case 3, the energization of the first control end Y2 of now passing ratio regulation proportion magnetic valve 8
Amount can be realized as pump proportional displacement control function；And work as pressure shut-off valve 7 and be in the second working position (i.e. left position in Fig. 6)
When, the first hydraulic fluid port of pressure shut-off valve 7 is connected with the 3rd hydraulic fluid port and the second hydraulic fluid port of pressure shut-off valve 7 ends, such second work
Making hydraulic fluid port B can be by the second working position of pressure shut-off valve 7 and first working position and the second plunger case of the first reversal valve 6
3 rodless cavity connection；The control end of pressure shut-off valve 7 is connected with the second working hole B, so when the pressure of the second working hole B reaches
To pressure shut-off valve 7 setting pressure when, the control end of pressure shut-off valve 7 then can control pressure stop valve 7 switch to second
Working position, and work as after pressure shut-off valve 7 switches to the second working position, the hydraulic oil pressure into the rodless cavity of the second plunger case 3
Power can promote swash plate to be rocked to zero angle position, so as to realize pump constant pressure cutting-off controlling function.
In this embodiment, the one side of the second reversal valve 9 can passing ratio regulation via the second oil circuit enter the second post
Hydraulic fluid pressure in the rodless cavity of plug cylinder 3 carrys out angular displacement of the second end of proportion adjustment swash plate on the left of zero degree plane, from
And realize the motor proportional displacement control function of fluid machinery；On the other hand, the second reversal valve 9 can also be by making the second plunger
The rodless cavity of cylinder 3 connects to realize the pump maximum pump discharge control function of fluid machinery by drain tap L with fuel tank.For the side of description
Just, both are referred to as pump motor operating mode by the operating mode that the second reversal valve 9 is adjusted, namely in pump motor operating mode, Ji Nengshi
The maximum pump discharge function of existing pump, can realize motor proportional displacement control function again.
Specifically, as shown in fig. 6, the second reversal valve 9 includes the first hydraulic fluid port, the second hydraulic fluid port, the 3rd hydraulic fluid port and the first control
End Y3, the first hydraulic fluid port of the second reversal valve 9 is connected with the second working hole B, second hydraulic fluid port and the first reversal valve of the second reversal valve 9
6 the first hydraulic fluid port connection, the 3rd hydraulic fluid port of the second reversal valve 9 is connected with fuel tank；First control end Y3 of the second reversal valve 9 can
The second reversal valve 9 is controlled to switch between the first working position and the second working position, when the second reversal valve 9 is in the first working position
When (i.e. left position in Fig. 6), the first hydraulic fluid port of the second reversal valve 9 and the connection of the second hydraulic fluid port and the 3rd hydraulic fluid port end, and are changed first
When switching to the second working position simultaneously to valve 6, the second working hole B can be by the first working position of the second reversal valve 9 and the
Second working position of one reversal valve 6 is connected with the rodless cavity of the second plunger case 3, and the second plunger case 3 is then able to drive swash plate
Second end is rocked to zero degree plane left side, so that fluid machinery switches to motor operating conditions；And when the second reversal valve 9 is in the
During two working positions (i.e. right position in Fig. 6), the first hydraulic fluid port of the second reversal valve 9 ends and the second hydraulic fluid port is connected with the 3rd hydraulic fluid port,
The rodless cavity of such second plunger case 3 can be by the second working position of the first reversal valve 6 and the second work of the second reversal valve 9
Make position to be connected with fuel tank, by the hydraulic oil earial drainage in the rodless cavity of the second plunger case 3 to fuel tank, so as to release the second plunger case 3
The active force of first angle position is left to the swash plate that makes that swash plate applies, swash plate is then in the presence of the first plunger case 2
First angle position, and then realize pump maximum pump discharge control function；Additionally, the first control end Y3 of the second reversal valve 9 can compare
Valve port size when the second reversal valve of example regulation 9 is in the first working position, namely first control end Y3 being capable of ratio tune
The hydraulic fluid pressure entered in the rodless cavity of the second plunger case 3 via the second oil circuit is saved, the second plunger case 3 is then able to ratio tune
Angular displacement of the second end of swash plate on the left of zero degree plane is saved, so that row of the proportion adjustment fluid machinery in motor operating conditions
Amount, realizes the motor proportional displacement control function of fluid machinery.
With pump proportional displacement control function similarly, the control in order to further improve motor proportional displacement control function is smart
Degree, in this embodiment, the angular displacement that swash plate angular displacement feedback control strategies 4 can also be by swash plate in motor operating conditions feeds back to
Second control end relative with its first control end Y3 of the second reversal valve 9.As shown in fig. 6, the second control of the second reversal valve 9
End is provided with the second feedback spring 901, when the second end of swash plate is rocked to zero degree plane left side, swash plate angular displacement feedback mechanism
4 can be connected with the second feedback spring 901, so as to be converted to the second feedback spring 901 by the angular displacement by swash plate now
Angular displacement of the deflection by swash plate in motor operating conditions feeds back to the second control end of the second reversal valve 9.Based on this, second changes
Coordinating to the first control end Y3 and the second feedback spring 901 of valve 9 can form to entering the second plunger case 3 via the second oil circuit
Rodless cavity in hydraulic fluid pressure closed-loop control so that the ratio control of discharge capacity to fluid machinery in motor operating conditions
It is more accurate.
In this embodiment, the first control end Y3 of the second reversal valve 9 is electric proportional control end, so can be according to second
The deflection of feedback spring 901 adjusts the turn on angle of the first control end Y3, and then realizes more accurate to motor operating conditions discharge capacity
Ratio control.
Additionally, the fluid machinery of the embodiment also includes the first stopping means 10 and the second stopping means 11, wherein, first
Stopping means 10 is used to cut off active force of second feedback spring 901 to swash plate angular displacement feedback mechanism 4 in pump condition, to keep away
Exempt from degree of regulation of in pump condition the second feedback spring 901 influence proportion magnetic valve 8 to discharge capacity, and the second stopping means 11 is then
For cutting off active force of first feedback spring 801 to swash plate angular displacement feedback mechanism 4 in motor operating conditions, to avoid in motor
Degree of regulation of the second reversal valve 9 of influence of first feedback spring 801 to discharge capacity during operating mode.It can be seen that, by setting the first spacing dress
Put 10 and second stopping means 11, the proportional displacement control function of pump condition and motor operating conditions is independent of one another such that it is able to avoid
Interfering therebetween, further improves degree of regulation, it is ensured that the functional reliability of fluid machinery of the present invention.
Based on the hydraulic circuit shown in Fig. 6, the operation principle of fluid machinery of the present invention is as follows：
(1) when fluid machinery is input into without rotating speed, without hydraulic oil input, the second plunger in the rodless cavity of the second plunger case 3
It is 0 that the plunger of cylinder 3 stretches out displacement, although also no pressure oil input in the rodless cavity of the first plunger case 2, due to the first plunger case 2
Back-moving spring is provided with rodless cavity, therefore, the plunger of the first plunger case 2 can stretch out in the presence of back-moving spring and be in swash plate
First angle position, now fluid machinery be in pump condition displacement.
(2) acquiescence operating mode is pump condition, under the operating mode, can realize that pump proportional displacement control function and pump constant pressure are cut
Disconnected control function.Implement process as follows：First control end Y1 dead electricity of the first reversal valve 6, the first reversal valve 6 is in first
Working position, and pressure shut-off valve 7 and proportion magnetic valve 8 are in the first working position, now give fluid machinery input speed, fuel tank
Interior oil enters fluid machinery body 1 from the first working hole S, and from the second working hole B outflows, and flowed out from the second working hole B
Hydraulic oil be divided into three tunnels, the first via is exported to executing agency, the second tunnel enter the first plunger case 2 rodless cavity, with the first post
Back-moving spring in the rodless cavity of plug cylinder 2 applies to make swash plate be maintained at the effect of first angle position to the first end of swash plate together
Power；3rd tunnel then the first working position of passing ratio magnetic valve 8, the first working position of pressure shut-off valve 7 and the first reversal valve 6
The first working position reach the rodless cavity of the second plunger case 3, active force is applied to the second end of swash plate, when the nothing of the second plunger case 3
After the difference of the hydraulic oil active force in hydraulic oil active force and the rodless cavity of the first plunger case 2 in rod cavity reaches certain value, second
Plunger case 3 can just promote swash plate to be swung from first angle position to zero angle position, the discharge capacity of pump is gradually reduced, in this process
In, the first stopping means 10 cuts off active force of second feedback spring 901 to swash plate angular displacement feedback mechanism 4, swash plate angular displacement
Swash plate is then only converted to the first feedback spring by feedback mechanism 4 in first angle position to the angular displacement between zero angle position
801 deflection, and the turn on angle of the first control end Y2 according to ratio feedback signal regulation proportion magnetic valve 8, it becomes possible to
More precisely valve port size of the proportion adjustment proportion magnetic valve 8 in the first working position such that it is able to more precisely compare
The hydraulic fluid pressure that example regulation enters in the rodless cavity of the second plunger case 3 via the first oil circuit, the second plunger case 3 is then able to ratio
Angular displacement of the second end of swash plate on the right side of zero degree plane is adjusted, makes to be exported to the first of executing agency by the second working hole B
The discharge capacity of road hydraulic oil changes in ratio, realizes the pump proportional displacement control function of fluid machinery；And when the pressure of the second working hole B
When power reaches dangerous setting pressure, pressure shut-off valve 7 switches to the second working position, from the 3rd road liquid of the second working hole B outflows
Force feed no longer passing ratio magnetic valve 8, but directly pass through second working position and the first reversal valve 8 of pressure shut-off valve 7
First working position reaches the rodless cavity of the second plunger case 3, and the second plunger case 3 then drives swash plate to be rocked to zero angle position, flows
Body machinery no longer output flow realizes pump constant pressure cutting-off controlling function to executing agency, prevents overload, improves the work of fluid machinery
Make security.
(3) pump motor operating mode, under the operating mode, can realize motor proportional displacement control function and pump maximum pump discharge control
Function processed.Implement process as follows：First control end Y1 of the first reversal valve 6 obtains electric, the first reversal valve 8 is switched to second
Working position, and the second reversal valve 9 the first control end Y3 dead electricity, make the second reversal valve 9 in the second working position, then the second plunger
Hydraulic oil in the rodless cavity of cylinder 3 by the second working position of the first reversal valve 6 and the second working position of the second reversal valve 9 with
Fuel tank is connected, and hydraulic oil earial drainage that will be in the rodless cavity of the second plunger case 3 to fuel tank, receive completely by the piston rod of the second plunger case 3
Return, swash plate is in first angle position all the time in the presence of the first plunger case 2 so that fluid machinery is in this case all the time
In pump maximum pump discharge working condition, so that fluid machinery has pump maximum pump discharge control function, can be used as energy recovery pump
Use；And when the first control end Y1 of the first reversal valve 6 obtains electric, the first reversal valve 8 and switches to the second working position, if second changes
To valve 9 the first control end Y3 also it is electric, the second reversal valve 9 of control switches to the first working position, then the second working hole B is by the
Second working position of the first working position of two reversal valves 9 and the first reversal valve 6 enters in the rodless cavity of the second plunger case 3, the
Two plunger case 3 drives the second end of swash plate to be rocked to zero degree plane left side, fluid machinery is switched to motor work by pump condition
Condition, now hydraulic oil enters fluid machinery body 1 from the second working hole B, and is flowed out from the first working hole S, in the process, the
Two stopping means 11 cuts off active force of first feedback spring 801 to swash plate angular displacement feedback mechanism 4, swash plate angular displacement feedback machine
Angular displacement of the structure 4 then only by the second end of swash plate on the left of zero degree plane is converted to the deflection of the second feedback spring 901,
And the turn on angle of the first control end Y3 of the second reversal valve 9 is adjusted according to the ratio feedback signal, it becomes possible to more precisely compare
Valve port size of example the second reversal valve 9 of regulation in the first working position such that it is able to which more precisely proportion adjustment is via the
The hydraulic fluid pressure that two oil circuits enter in the rodless cavity of the second plunger case 3, the second plunger case 3 is then able to the of proportion adjustment swash plate
Angular displacement of two ends on the left of zero degree plane, makes discharge capacity of the fluid machinery in motor operating conditions change in ratio, realizes fluid
The motor proportional displacement control function of machinery.
To sum up, body of the present invention based on common cam-type axial piston pump, by setting up reversal valve, ratio electromagnetism
Valve, swash plate angular displacement feedback mechanism etc., make fluid machinery not only while having pumping function and motor function, and by inside
The design of control logic, realizes the cut-out control of pump proportional displacement control function, motor proportional displacement control function and pump constant pressure
The Variable Control of various functions such as function processed, and do not interfere with each other each other, control accuracy is high, and simple structure, cost is relatively low.
The fluid machinery can apply to the Brake energy recovery hydraulic pressure system of road running class vehicle or construction machinery product
System or other potential energy (or inertia energy) energy-recuperation systems, effectively solve the power saving of these engineering machinery.
Exemplary embodiment of the invention is these are only, is not intended to limit the invention, it is all in spirit of the invention and former
Within then, any modification, equivalent substitution and improvements made etc. should be included within the scope of the present invention.
Claims (15)
1. a kind of fluid machinery, it is characterised in that including：
Fluid machinery body (1), first driving means, the second drive device, operating mode switching device, the first Working condition regulator and
Second Working condition regulator；
The fluid machinery body (1) includes the first working hole (S), the second working hole (B) and swash plate, the first driving means
It is connected to the first end of the swash plate and the hydraulic control end of the first driving means connects with second working hole (B), it is described
Second drive device is connected to the second end of the swash plate and the hydraulic control end of second drive device and switches dress with the operating mode
Put connection；
The operating mode switching device can control the hydraulic control end of second drive device by the first oil circuit and the second oil circuit
One connected with second working hole (B), when second drive device hydraulic control end pass through first oil circuit and institute
When stating the second working hole (B) connection, the fluid machinery is in pump condition, first working hole (S) oil-feed, second work
Make that mouth (B) is fuel-displaced, when the hydraulic control end of second drive device is connected by second oil circuit with second working hole (B)
When, the fluid machinery is in motor operating conditions, and second working hole (B) oil-feed, first working hole (S) is fuel-displaced；
First Working condition regulator is arranged on first oil circuit, and first Working condition regulator is used to make the stream
Body machinery has pump proportional displacement control function and pump constant pressure cutting-off controlling function, wherein, first Working condition regulator
Passing ratio regulation makes described via first oil circuit into the hydraulic fluid pressure at the hydraulic control end of second drive device
Fluid machinery has the pump proportional displacement control function, and first Working condition regulator is by second working hole
(B) control enters in the hydraulic control end of second drive device via first oil circuit when pressure reaches setting dangerous pressure
Hydraulic fluid pressure and the swash plate is rocked to zero angle position, realize the pump constant pressure cutting-off controlling function；
Second Working condition regulator is arranged on second oil circuit, and second Working condition regulator being capable of passing ratio
Regulation makes the fluid machinery via second oil circuit into the hydraulic fluid pressure at the hydraulic control end of second drive device
With motor proportional displacement control function.
2. fluid machinery according to claim 1, it is characterised in that the operating mode switching device includes the first reversal valve
(6), first reversal valve (6) includes the first hydraulic fluid port, the second hydraulic fluid port and the 3rd hydraulic fluid port, the first of first reversal valve (6)
Hydraulic fluid port is connected with second Working condition regulator, the second hydraulic fluid port and first regulating working conditions of first reversal valve (6)
Device is connected, and the 3rd hydraulic fluid port of first reversal valve (6) is connected with the hydraulic control end of second drive device；Described first changes
To valve (6) with the first working position and the second working position, first described in when first reversal valve (6) is in the first working position
The first hydraulic fluid port cut-off of reversal valve (6) and the second hydraulic fluid port and the 3rd the hydraulic fluid port connection of first reversal valve (6), so that described the
The hydraulic control end of two drive devices is connected by first oil circuit with second working hole (B), when first reversal valve (6)
The first hydraulic fluid port of the first reversal valve (6) is connected and first reversal valve (6) with the 3rd hydraulic fluid port described in during in the second working position
The second hydraulic fluid port cut-off so that the hydraulic control end of second drive device pass through second oil circuit and second working hole
(B) connect.
3. fluid machinery according to claim 2, it is characterised in that first reversal valve (6) is solenoid directional control valve, institute
Stating the Electromagnetic Control end (Y1) of the first reversal valve (6) is used to control first reversal valve (6) in the first working position and the second work
Make to switch between position.
4. fluid machinery according to claim 2, it is characterised in that first Working condition regulator includes ratio electromagnetism
Valve (8), the proportion magnetic valve (8) includes the first hydraulic fluid port, the second hydraulic fluid port and the first control end (Y2), the proportion magnetic valve
(8) the first hydraulic fluid port is connected with second working hole (B), and the second hydraulic fluid port of the proportion magnetic valve (8) is changed with described first
To valve (6) the second hydraulic fluid port connect, the proportion magnetic valve (8) with the first working position, when the proportion magnetic valve (8) is in
The first hydraulic fluid port of the proportion magnetic valve (8) is connected with the second hydraulic fluid port during the first working position, and the first of the proportion magnetic valve (8)
Control end (Y2) can valve port size of the proportion magnetic valve (8) in the first working position described in proportion adjustment so that described
Fluid machinery has pump proportional displacement control function.
5. fluid machinery according to claim 4, it is characterised in that first Working condition regulator is also cut including pressure
Disconnected valve (7), the second hydraulic fluid port of the proportion magnetic valve (8) passes through the pressure shut-off valve (7) and first reversal valve (6)
Second hydraulic fluid port is connected, and the pressure shut-off valve (7) is for when the pressure of second working hole (B) reaches setting dangerous pressure
Control swings the swash plate by first oil circuit into the hydraulic fluid pressure in the hydraulic control end of second drive device
To zero angle position, so that the fluid machinery has pump constant pressure cutting-off controlling function.
6. fluid machinery according to claim 5, it is characterised in that the pressure shut-off valve (7) includes the first hydraulic fluid port,
Two hydraulic fluid ports, the 3rd hydraulic fluid port and control end, the first hydraulic fluid port of the pressure shut-off valve (7) are connected with second working hole (B), institute
The second hydraulic fluid port for stating pressure shut-off valve (7) is connected with the second hydraulic fluid port of the proportion magnetic valve (8), the pressure shut-off valve (7)
The 3rd hydraulic fluid port connected with the second hydraulic fluid port of first reversal valve (6)；The pressure shut-off valve (7) with the first working position and
Second working position, when the pressure shut-off valve (7) is in the first working position, the first hydraulic fluid port of the pressure shut-off valve (7) cuts
Only and the second hydraulic fluid port of the pressure shut-off valve (7) is connected with the 3rd hydraulic fluid port, when the pressure shut-off valve (7) is in the second work
During position, the first hydraulic fluid port of the pressure shut-off valve (7) is connected with the 3rd hydraulic fluid port and the second hydraulic fluid port of the pressure shut-off valve (7) cuts
Only；The control end of the pressure shut-off valve (7) is connected so that when second working hole (B) with second working hole (B)
Pressure when reaching the setting pressure of the pressure shut-off valve (7) control end of the pressure shut-off valve (7) pressure can be controlled
Power stop valve (7) switches to the second working position.
7. fluid machinery according to claim 4, it is characterised in that first Working condition regulator also includes swash plate angle
Displacement Feedback mechanism (4), the angular displacement that the swash plate angular displacement feedback mechanism (4) can be by the swash plate in the pump condition
Feed back to second control end relative with its first control end (Y2) of the proportion magnetic valve (8).
8. fluid machinery according to claim 7, it is characterised in that the second control end of the proportion magnetic valve (8) sets
There are the first feedback spring (801), the angle that the swash plate angular displacement feedback mechanism (4) can be by the swash plate in the pump condition
Displacement is converted to the deflection of first feedback spring (801).
9. fluid machinery according to claim 1, it is characterised in that second Working condition regulator can also make described
The hydraulic control end of the second drive device connects with fuel tank, so that the fluid machinery has pump maximum pump discharge control function.
10. according to any described fluid machineries of claim 2-9, it is characterised in that second Working condition regulator includes
Second reversal valve (9), second reversal valve (9) includes the first hydraulic fluid port, the second hydraulic fluid port and the first control end (Y3), described second
First hydraulic fluid port of reversal valve (9) is connected with second working hole (B), the second hydraulic fluid port of second reversal valve (9) with it is described
First reversal valve (6) the first hydraulic fluid port connection, second reversal valve (9) with the first working position, when second reversal valve
(9) the first hydraulic fluid port of the second reversal valve (9) described in when in the first working position and the second hydraulic fluid port are connected, second reversal valve
(9) the first control end (Y3) can be when the second reversal valve (9) be in the first working position described in proportion adjustment valve port it is big
It is small, so that the fluid machinery has motor proportional displacement control function.
11. fluid machineries according to claim 10, it is characterised in that second reversal valve (9) also includes the 3rd oil
Mouthful, the 3rd hydraulic fluid port of second reversal valve (9) is connected with fuel tank, when second reversal valve (9) is in the first working position,
The 3rd hydraulic fluid port cut-off of second reversal valve (9)；Second reversal valve (9) also has the second working position, when described second
The first hydraulic fluid port cut-off of the second reversal valve (9) described in when reversal valve (9) is in the second working position and second reversal valve (9)
Second hydraulic fluid port is connected with the 3rd hydraulic fluid port；First control end (Y3) of second reversal valve (9) can control second commutation
Valve (9) switches to the second working position, so that the fluid machinery has pump maximum pump discharge control function.
12. fluid machineries according to claim 11, it is characterised in that when claim 10 quotes claim 7 or 8
When, the angular displacement that the swash plate angular displacement feedback mechanism (4) can also be by the swash plate in the motor operating conditions feeds back to institute
State second control end relative with its first control end (Y3) of the second reversal valve (9).
13. fluid machineries according to claim 12, it is characterised in that the second control end of second reversal valve (9)
The second feedback spring (901) is provided with, the swash plate angular displacement feedback mechanism (4) can be by the swash plate in the motor operating conditions
Angular displacement be converted to the deflection of second feedback spring (901).
14. fluid machineries according to claim 13, it is characterised in that when claim 10 quotes claim 8, institute
Stating fluid machinery also includes the first stopping means (10), and first stopping means (10) is for cutting off institute in the pump condition
State active force of the second feedback spring (901) to the swash plate angular displacement feedback mechanism (4)；And/or, the fluid machinery is also wrapped
The second stopping means (11) is included, second stopping means (11) is for cutting off the first feedback bullet in the motor operating conditions
Active force of the spring (801) to the swash plate angular displacement feedback mechanism (4).
15. according to any described fluid machineries of claim 1-9, it is characterised in that the first driving means include first
Plunger case (2), the plunger of first plunger case (2) is connected with the first end of the swash plate, the liquid of the first driving means
Control end is arranged on the rodless cavity of first plunger case (2) so that the rodless cavity of first plunger case (2) and second work
Make mouth (B) connection, and back-moving spring is provided with the rodless cavity of first plunger case (2)；And/or, second drive device
Including the second plunger case (3), the plunger of second plunger case (3) is connected with the second end of the swash plate, and described second drives
The hydraulic control end of device is arranged on the rodless cavity of second plunger case (3) so that rodless cavity and the institute of second plunger case (3)
State the connection of operating mode switching device.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201510834477.4A CN105275900B (en) | 2015-11-26 | 2015-11-26 | Fluid machine |
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| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201510834477.4A CN105275900B (en) | 2015-11-26 | 2015-11-26 | Fluid machine |
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| CN105275900A CN105275900A (en) | 2016-01-27 |
| CN105275900B true CN105275900B (en) | 2017-05-24 |
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| CN106194680B (en) * | 2016-08-28 | 2018-02-06 | 中航力源液压股份有限公司 | The axial plunger pump installation and control method of a kind of high-precision electric proportional control |
| CN106762506B (en) * | 2016-12-15 | 2018-10-02 | 徐州重型机械有限公司 | A kind of control valve that can realize bidirectional variable and open hydraulic pump |
| CN108533545B (en) * | 2018-06-29 | 2020-03-10 | 潍柴动力股份有限公司 | Mechanical proportional controller of hydraulic variable pump and hydraulic variable pump |
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| US7076946B2 (en) * | 2004-08-16 | 2006-07-18 | Eaton Corporation | Hydraulic kicker control piston |
| US8429908B2 (en) * | 2009-12-17 | 2013-04-30 | Deere & Company | Hydraulic system |
| JP5323753B2 (en) * | 2010-03-26 | 2013-10-23 | カヤバ工業株式会社 | Construction machine control equipment |
| CN104847613B (en) * | 2015-04-13 | 2017-09-19 | 徐州重型机械有限公司 | A kind of inclined disc type axial hydraulic plunger pump or motor apparatus |
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Address after: 221001 Jiangsu city of Xuzhou Province Economic and Technological Development Zone of High Road No. 68 Patentee after: Xuzhou Heavy Machinery Co., Ltd. Address before: 221004 Xuzhou, Zhejiang Province, Jiangsu Road No. 165 Patentee before: Xuzhou Heavy Machinery Co., Ltd. |