CN105736491B - Based on the constant pressure variable plunger pump from pressure-reducing constant pressure valve - Google Patents
Based on the constant pressure variable plunger pump from pressure-reducing constant pressure valve Download PDFInfo
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- CN105736491B CN105736491B CN201510260939.6A CN201510260939A CN105736491B CN 105736491 B CN105736491 B CN 105736491B CN 201510260939 A CN201510260939 A CN 201510260939A CN 105736491 B CN105736491 B CN 105736491B
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Abstract
The application is related to a kind of constant pressure variable plunger pump based on from pressure-reducing constant pressure valve, including hydraulic pump, decompression half-bridge, pressure sensor block and executing agency.Hydraulic pump includes swash plate, oil inlet and oil-out, the inclination angle positive correlation of the outlet pressure and swash plate of the oil-out of hydraulic pump；The oil-out of the input and hydraulic pump that depressurize half-bridge is connected, and is generated first pressure for the outlet pressure based on hydraulic pump oil-out and is exported to pressure sensor block, first pressure is less than the outlet pressure of hydraulic pump oil-out；One end of executing agency and the output end of pressure sensor block are connected, and the other end is connected with swash plate, and the pressure signal generation for being exported based on pressure sensor block changes the thrust at the inclination angle of swash plate.The change displacement hydraulic pumping system of the present invention can reduce the whole volume for becoming displacement hydraulic pumping system with the volume of pressure sensor block is reduced.
Description
Technical field
The application is related to a kind of pump source system, particularly a kind of constant pressure variable plunger pump based on from pressure-reducing constant pressure valve.
Background technology
Become displacement hydraulic pumping system to be widely used in Hydraulic Field.It is shown in Figure 1, it is a kind of existing change discharge capacity liquid
The structure chart of press pump.In the change displacement hydraulic pump, the output pressure for becoming displacement hydraulic pump is gathered by pressure valve 2, works as pressure
When the output pressure of valve 2 is more than the elastic force of spring, thrust is formed, so as to promote the swashplate angle for becoming displacement hydraulic pump to reduce, is entered
And reduce the output pressure for becoming displacement hydraulic pump.
However, because the output pressure for becoming displacement hydraulic pump is larger, in order to obtain matching elastic force, the volume of spring
It is larger, and then make it that the whole size for becoming displacement hydraulic pumping system is larger.
The content of the invention
The brief overview on the present invention is given below, to provide the basic reason on certain aspects of the invention
Solution.It should be appreciated that this general introduction is not the exhaustive general introduction on the present invention.It is not intended to determine the key of the present invention
Or pith, nor is it intended to limit the scope of the present invention.Its purpose only provides some concepts in simplified form, with
This is used as the preamble in greater detail discussed later.
A primary object of the present invention is a kind of new change displacement hydraulic pumping system of offer, and it can be according to real needs
Adjust output pressure, and small volume.
According to an aspect of the present invention, it is a kind of to become displacement hydraulic pumping system, including hydraulic pump, decompression half-bridge, pressure sensing
Module and executing agency；
Wherein：
Hydraulic pump includes swash plate, oil inlet and oil-out, the outlet pressure of the oil-out of hydraulic pump and the inclination angle of swash plate
Positive correlation；
The oil-out of the input and hydraulic pump that depressurize half-bridge is connected, for the outlet pressure life based on hydraulic pump oil-out
Into first pressure and export to pressure sensor block, first pressure is less than the outlet pressure of hydraulic pump oil-out；
One end of executing agency and the output end of pressure sensor block are connected, and the other end is connected with swash plate, for based on pressure
The pressure signal generation of power sensing module output changes the thrust at the inclination angle of swash plate.
The change displacement hydraulic pumping system of the present invention, is reduced by depressurizing half-bridge and is input to the pressure of pressure sensor block,
So as to reduce the volume of pressure sensor block, and then reduce the whole volume for becoming displacement hydraulic pumping system.
Brief description of the drawings
Below with reference to the accompanying drawings illustrate embodiments of the invention, can be more readily understood that the present invention more than and its
Its objects, features and advantages.Part in accompanying drawing is intended merely to show the principle of the present invention.In the accompanying drawings, identical or similar
Technical characteristic or part will be represented using same or similar reference.
Fig. 1 is a kind of structure chart of embodiment of existing change displacement hydraulic pumping system；
Fig. 2 is a kind of structure chart of embodiment of the change displacement hydraulic pumping system of the present invention；
Fig. 3 be Fig. 2 in pressure sensor block a kind of embodiment structure chart；
Fig. 4 be Fig. 2 in executing agency a kind of embodiment structure chart.
Embodiment
Illustrate embodiments of the invention with reference to the accompanying drawings.Retouched in a kind of accompanying drawing or embodiment of the present invention
The element and feature that the element and feature stated can be shown in one or more other accompanying drawings or embodiment are combined.Should
Work as attention, for purposes of clarity, eliminated in accompanying drawing and explanation known to unrelated to the invention, those of ordinary skill in the art
Part and processing expression and description.
It is shown in Figure 2, it is a kind of structure chart of embodiment of the change displacement hydraulic pumping system of the present invention.
In the present embodiment, become displacement hydraulic pumping system include hydraulic pump 60, decompression half-bridge 1, pressure sensor block 2 with
And executing agency 3.
Wherein, hydraulic pump 60 include swash plate, oil inlet and oil-out, the outlet pressure Ps of the oil-out of hydraulic pump 60 with tiltedly
The inclination angle positive correlation of disk..The inclination angle of swash plate is the angle of swash plate and perpendicular.
For example, in some cases, after the load for being connected to the outlet pressure Ps ends of hydraulic pump 60 reaches setting value, if thinking
The outlet pressure Ps for adjusting hydraulic pump 60 reduces, and can correspond to the inclination angle for adjusting swash plate, reduce it, and then just can make outlet
Pressure Ps reduces.
The oil-out of the input and hydraulic pump that depressurize half-bridge 1 is connected, for the outlet pressure based on hydraulic pump oil-out
Ps generates first pressure Ps ' and exported to pressure sensor block 2.First pressure Ps ' is less than the outlet pressure of hydraulic pump oil-out
Ps。
One end of executing agency 40 is connected with the output end of pressure sensor block 2, and the other end is connected with swash plate, for based on
The pressure signal generation that pressure sensor block 2 is exported changes the thrust at the inclination angle of swash plate.
It is shown in Figure 3, it is a kind of structure chart of embodiment of pressure sensor block in Fig. 2.Preferably
In, pressure sensor block 2 can be pressure valve.
It is described below in conjunction with Fig. 2, Fig. 3.
Pressure valve can include valve body 20, the first asymmetry piston 10 and the first spring 30.
First asymmetry piston 10 can include the first post portion 11 stretched out outside valve body and vertical connected with the first post portion 11
And the first piston part in valve body.First piston part is provided with circumferential slot, and the first piston part is divided into the first cock body 12 and by circumferential slot
Two cock bodys 13.The inwall formation gap of first cock body 12, the second cock body 13 and valve body 20 coordinates.
Valve body 20 is divided into the rod chamber 24 for including the first post portion 11 by the first asymmetry piston 10, positioned at the first cock body
12 and the second intermediate cavity 25 between cock body 13, and rodless cavity 26.
First entrance 21, the entrance 23 of second entrance 22 and the 3rd are provided with valve body 20.First entrance 21 has been connected to bar
Chamber 24, the 3rd entrance 23 is connected to rodless cavity 26.
First entrance 21 and the 3rd entrance 23 are connected with depressurizing the output end of half-bridge 1, second entrance 22 also with hydraulic pump
Oil-out is connected.
The elastic force direction of first spring 30 is overlapped with the axis of the first asymmetry piston 10, for adjusting the first asymmetric work
The initial pretightning force of plug 10.
In one embodiment, decompression half-bridge 1 can include the first segment discharge orifice R1 and the second throttle orifice of serial connection
R2。
First segment discharge orifice R1 first end is connected with hydraulic pump oil-out, first segment discharge orifice R1 the second end and the second throttling
Hole R2 first end is connected to the entrance 23 of first entrance 21 and the 3rd of valve body 20.So, first entrance 21 and the 3rd enters
Pressure at mouth 22 is Ps '.
In one embodiment, the externally connected fuel tank 70 in the second throttle orifice R2 the second end.Now, the second throttle orifice
Pressure at the ends of R2 second can be considered zero.So, exist between the output pressure Ps ' and input pressure Ps of decompression half-bridge 1
Following relation：
Ps '=Ps × r2/ (r1+r2)
Wherein, r1 and r2 is respectively first segment discharge orifice R1 and the second throttle orifice R2 liquid resistance.
As a kind of preferred scheme, change displacement hydraulic pumping system of the invention can also include the 3rd throttle orifice R3.
In one embodiment, the output end of pressure valve can be connected to the input of executing agency 40 through the 3rd throttle orifice R3
End.So, input to the fluid flow of executing agency 40 can be caused more to stablize.
In one embodiment, executing agency 40 for example can be single-action hydraulic cylinder.
It is shown in Figure 4, it is a kind of structure chart of embodiment of single-action hydraulic cylinder.
In the present embodiment, single-action hydraulic cylinder can include the asymmetry piston of cylinder body 41 and second.Second is asymmetric
Piston includes vertically connected the second post portion 43 and the second piston part 42.
The inwall of second piston part 43 and cylinder body 41 cooperatively forms the first cavity 44, and the first cavity includes and is connected to the 3rd throttling
The opening 45 of hole output end；
The first end in the second post portion 43 is connected with the second piston part 42, and second end in the second post portion 43 is connected to swash plate.
As a kind of preferred scheme, single-action hydraulic cylinder can also include second spring 44.The first end of second spring 44
It is connected with a fixing point 46, second end at the second end of second spring 44 and the second post portion 43 is connected.
So, thrust and second spring of the liquid to the second asymmetry piston of the first cavity 44 are flowed into from opening 45
To the force action of the elastic force of the second asymmetry piston to swash plate so that the inclination angle of swash plate changes, and then causes hydraulic pump
Output flow changes.
2-4 is to the workflow for becoming displacement hydraulic pumping system of the invention below in conjunction with the accompanying drawings.
When hydraulic pump 60 is without output flow, Ps and Ps ' they are zero, now, and the first asymmetry piston 10 is in right position,
Under the thrust of first 30 pair of first asymmetry piston 10 of spring, the first asymmetry piston 10 is in low order end, and first without bar
The volume of chamber 26 is zero.
After hydraulic pump 60 is started working, Ps ' respectively enters the first of pressure valve through the entrance 23 of first entrance 21 and the 3rd
The rodless cavity 26 of rod chamber 24 and first, and the area that Ps ' acts on the first rod chamber 24 is S1, Ps ' acts on the first rodless cavity
26 area is S2.Due to S2＞ S1, then total hydraulic coupling F1=Ps ' (S2- S1), direction is to the left.
When valve element 20 is balanced, by the elastic force F of the first spring 300With hydraulic coupling F1Force action, now has：
F0=F1=Ps ' (S2-S1)
Therefore, in the F of setting0Under, when the outlet pressure Ps increases of hydraulic pump 60, the proportional increases of Ps ', so that hydraulic pressure
Power F1Increase.
If F1＜ F0, valve element 20 is in elastic force F0Effect is lower to be in initial position (i.e. right position), and the second of single-action hydraulic cylinder is non-
Symmetrical piston makes swashplate angle be in maximum position in the presence of second spring 50, and hydraulic pump discharge is maximum, oil in pressure valve
Liquid flows to fuel tank 70 through the throttle orifice R3 of outlet 27 and the 3rd.
If F1＞ F0, the first asymmetry piston 10 is in F1With F0Force action under be moved to the left, liquid is through pressure valve and
Three throttle orifice R3 enter the first cavity 44 of single-action hydraulic cylinder, promote the motion of the second asymmetry piston, and then promote swash plate to incline
Oblique angle reduces, and reduces the discharge capacity of hydraulic pump 60, so as to reduce the outlet pressure Ps of hydraulic pump 60.
Because the outlet pressure Ps of hydraulic pump 60 is input to the first rod chamber 24 of pressure valve 2 through depressurizing after half-bridge 1 is depressurized
With the first rodless cavity 26, hydraulic coupling F1Absolute value it is smaller, therefore, the elastic force F of the offer of the first spring 300Also it is smaller, Jin Erke
Reduce the volume of the first spring 30.
Further, since the first asymmetry piston 10 is only in F1＞ F0When to executing agency 40 produce output, therefore, can pass through
Adjust initial pretightning force (the i.e. elastic force F of spring of the first spring 300), to change the output threshold value of hydraulic pump 60.In other words,
Make Ps ' (S when output flow Ps is increased to2-S1) ＞ F0When, executing agency 40 produces the angle of inclination that thrust reduces swash plate, and then
Reduce the output flow and outlet pressure Ps of hydraulic pump 60, so, just realize the maximum outlet pressure to hydraulic pump 60
Control.
In the apparatus and method of the present invention, it is clear that each part or each step are after can decomposing, combine and/or decomposing
Reconfigure.These decompose and/or reconfigured the equivalents that should be regarded as the present invention.Meanwhile, above to present invention tool
In the description of body embodiment, the feature for describing and/or showing for a kind of embodiment can be existed in same or similar mode
Used in one or more other embodiments, it is combined with feature in other embodiment, or substitute other embodiment party
Feature in formula.
It should be emphasized that term "comprises/comprising" refers to the presence of feature, key element, step or component when being used herein, but simultaneously
It is not excluded for the presence or additional of one or more further features, key element, step or component.
Although the present invention and its advantage has been described in detail it should be appreciated that without departing from by appended claim
Various changes can be carried out in the case of the spirit and scope of the present invention limited, substitutes and converts.Moreover, the model of the application
Enclose the process described by specification of being not limited only to, equipment, means, the specific embodiment of method and steps.In the art is common
Technical staff be will readily appreciate that from the disclosure, and execution and corresponding reality described herein can be used according to the present invention
Apply the essentially identical function of example or obtain process essentially identical with it result, existing and that future is to be developed, equipment,
Means, method or step.Therefore, appended claim includes such process, equipment, hand in the range of being directed at them
Section, method or step.
Claims (6)
1. one kind becomes displacement hydraulic pumping system, it is characterised in that half-bridge, pressure sensor block and held including hydraulic pump, decompression
Row mechanism；
Wherein；
The hydraulic pump includes swash plate, oil inlet and oil-out, the outlet pressure of the oil-out of the hydraulic pump and the swash plate
Inclination angle positive correlation；
The input of the decompression half-bridge is connected with the oil-out of the hydraulic pump, for going out based on the hydraulic pump oil-out
Mouth pressing creation first pressure is simultaneously exported to the pressure sensor block, and the first pressure is less than the hydraulic pump oil-out
Outlet pressure；
One end of the executing agency is connected with the output end of the pressure sensor block, and the other end is connected with the swash plate, is used
Change the thrust at the inclination angle of the swash plate in the pressure signal generation exported based on the pressure sensor block；
The pressure sensor block is pressure valve；
The pressure valve includes valve body, the first asymmetry piston and the first spring；
The the first post portion and the first post portion that first asymmetry piston includes stretching out outside the valve body are vertically connected and position
In the first piston part in the valve body, first piston part is provided with circumferential slot, and first piston part is divided into by the circumferential slot
One cock body and the second cock body, the inwall gap of first cock body and second cock body and the valve body coordinate；
The valve body is divided into the rod chamber for including the first post portion by first asymmetry piston, positioned at described first
Intermediate cavity between cock body and second cock body, and rodless cavity；
First entrance, second entrance and the 3rd entrance are provided with the valve body, the first entrance is connected to the rod chamber,
3rd entrance is connected to the rodless cavity；
The first entrance is connected with the 3rd entrance with the output end of the decompression half-bridge, the second entrance and the liquid
The oil-out connection of press pump；
The elastic force direction of first spring is overlapped with the axis of first asymmetry piston, non-right for adjusting described first
Claim the initial pretightning force of piston.
2. change displacement hydraulic pumping system according to claim 1, it is characterised in that：
The decompression half-bridge includes the first segment discharge orifice and the second throttle orifice of serial connection；
The first end of the first segment discharge orifice is connected with the hydraulic pump oil-out；
The first end of second end of the first segment discharge orifice and second throttle orifice be connected to the valve body first entrance and
3rd entrance；
The externally connected mailbox in the second end of second throttle orifice.
3. change displacement hydraulic pumping system according to claim 2, it is characterised in that also including the 3rd throttle orifice；
The output end of the pressure valve is connected to the input of the executing agency through the 3rd throttle orifice.
4. change displacement hydraulic pumping system according to claim 3, it is characterised in that：
The executing agency is single-action hydraulic cylinder.
5. change displacement hydraulic pumping system according to claim 4, it is characterised in that：
The single-action hydraulic cylinder includes cylinder body, the second asymmetry piston；
Second asymmetry piston includes vertically connected the second post portion and the second piston part；
The inwall of second piston part and the cylinder body cooperatively forms the first cavity, and first cavity is comprising being connected to described the
The opening of three throttle orifice output ends；
The first end in the second post portion and second piston part are connected, second end in the second post portion be connected to it is described tiltedly
Disk.
6. change displacement hydraulic pumping system according to claim 5, it is characterised in that：
The single-action hydraulic cylinder also includes second spring；
The first end of the second spring and a fixing point are connected, and the of the second end of the second spring and the second post portion
Two ends are connected.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201510260939.6A CN105736491B (en) | 2015-05-20 | 2015-05-20 | Based on the constant pressure variable plunger pump from pressure-reducing constant pressure valve |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201510260939.6A CN105736491B (en) | 2015-05-20 | 2015-05-20 | Based on the constant pressure variable plunger pump from pressure-reducing constant pressure valve |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN105736491A CN105736491A (en) | 2016-07-06 |
| CN105736491B true CN105736491B (en) | 2017-09-22 |
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| Application Number | Title | Priority Date | Filing Date |
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| CN201510260939.6A Active CN105736491B (en) | 2015-05-20 | 2015-05-20 | Based on the constant pressure variable plunger pump from pressure-reducing constant pressure valve |
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Families Citing this family (1)
| Publication number | Priority date | Publication date | Assignee | Title |
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| CN109798272B (en) * | 2019-01-11 | 2020-08-28 | 徐州工业职业技术学院 | Compound variable pump and compound hydraulic control system |
Family Cites Families (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US3864063A (en) * | 1973-09-11 | 1975-02-04 | Cessna Aircraft Co | Automatic torque limitation control |
| US6033188A (en) * | 1998-02-27 | 2000-03-07 | Sauer Inc. | Means and method for varying margin pressure as a function of pump displacement in a pump with load sensing control |
| DE10219850B3 (en) * | 2002-05-03 | 2004-02-05 | Brueninghaus Hydromatik Gmbh | Control device with limit control valve |
| DE102005011395A1 (en) * | 2005-03-11 | 2006-09-14 | Bosch Rexroth Ag | Hydraulic control arrangement |
| JP4365870B2 (en) * | 2007-03-30 | 2009-11-18 | 三菱重工業株式会社 | Fluid pressure actuator |
| CN102996391B (en) * | 2012-12-03 | 2016-03-02 | 中联重科股份有限公司 | Load sensitive pump, load-sensitive hydraulic system and concrete pumping equipment |
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