CN105443963A - Blade variable pump - Google Patents
Blade variable pump Download PDFInfo
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- CN105443963A CN105443963A CN201510869763.4A CN201510869763A CN105443963A CN 105443963 A CN105443963 A CN 105443963A CN 201510869763 A CN201510869763 A CN 201510869763A CN 105443963 A CN105443963 A CN 105443963A
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- stator
- control chamber
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- variable displacement
- displacement pump
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Abstract
The invention provides a blade variable pump which comprises a pump body, a pump cover, a stator, a rotor and blades arranged on the rotor. A first control cavity body and a second control cavity body which are opposite to each other are formed in the inner wall of a cavity body. The two ends of the stator are provided with a first force bearing boss connected with the first control cavity body in a matched manner and a second force bearing boss connected with the second control cavity body in a matched manner. The area of a force bearing face of the second force bearing boss is smaller than that of the force bearing face of the first force bearing boss. The first control cavity body is communicated with a main oil way. The second control cavity body is connected with an oil pressure control element. At least one elastic element for providing elastic force for the stator through the first force bearing boss or the second force bearing boss is arranged. The stator can slide under the pressure control effect of the first control cavity body or the second control cavity in the linear direction of the first force bearing boss and the second force bearing boss, and the output displacement is fed back and adjusted, so that the output displacement is stable.
Description
Technical field
The application relates to a kind of oil hydraulic pump, is specifically related to a kind of blade variable displacement pump.
Background technique
At present, with the oil pump of matching with automobile engine from traditional metering pump to variable displacement pump transition.Tradition fixed displacement oil pump is by driven by engine, its displacement size installation warrants engine operating condition and determining, the fuel delivery of this vane pump raises with engine speed and linearly increases, and the actual lubrication needs far away higher than motor after high speed, causes the waste of energy consumption.Blade variable displacement pump then can regulate pump delivery according to the pressure of outlet end voluntarily, achieve by complete machine lubrication needs fuel feeding, avoid superfluous due to fuel feeding and energy consumption that is that cause is wasted, reach energy-conservation object, decrease the pressure that pump bears simultaneously, thus extend the working life of pump.
Along with the development of auto parts and components technology, there is various forms of blade variable displacement pump oil pump in automobile industry.Wherein, two grade blade variable displacement pumps can automatically switch according to the difference of engine operating condition and become discharge capacity working pressure, make it pump pressure and motor actual demand pressure is more close, can reach than the better energy-saving effect of a grade blade variable displacement pump.
Two grade blade variable displacement pump many employings swing type adjustment ring structures in current industry, the motion of the blade variable displacement pump of this structure adjustment ring is in the course of the work for swinging, the change that adjustment ring is produced by oil pump chamber pressure is nonlinear, that is, in different operating mode lower blade variable displacement pump cavity, fluid pressure state is in continuous change procedure, and then adjustment ring is among fluctuation under the impact of fluid pressure.Therefore, the blade variable displacement pump of this type is not easy to analysis and designation, and meanwhile, pump displacement controls inaccuracy, can not reach energy-saving effect to greatest extent.
One is provided to be convenient to analytical calculation, and the accurate variable displacement pump of displacement control, raising becomes displacement oil pump control accuracy and energy-saving effect becomes those skilled in the art's technical issues that need to address.
Summary of the invention
The application provides a kind of blade variable displacement pump, not high to solve prior art Leaf variable displacement pump control accuracy, the technical problem that energy-saving effect is poor.
The application provides a kind of blade variable displacement pump, comprising: the pump housing, pump cover, stator, rotor and be arranged at described epitrochanterian blade;
The described pump housing and described pump cover enclose form accommodating stator, rotor, blade cavity and provide the pipeline structure in path for working medium, this pipeline structure comprises and is positioned at described cavity both sides and the oil suction chamber do not communicated and go out oil pocket;
At least comprise between described stator and described rotor a profile close working zone, described working zone respectively with described oil suction chamber with described go out oil pocket be communicated with;
Described rotor is provided with the live axle with external driver device secure fit, or described external driver device comprises live axle, described rotor is provided with the attachment hole with this live axle secure fit; Described external driver device is rotated in the medial axis of described this rotor of stator internal winding by rotor described in described drive shaft;
Described cavity inner wall is provided with the first relative control chamber and the second control chamber, described stator two ends are respectively arranged with the first load boss be connected with described first control chamber and the second load boss be connected with described second control chamber, and the load-carrying surface area of described second load boss is less than the load-carrying surface area of the first load boss; Described first control chamber is communicated with main oil gallery; Described second control chamber is connected with oil pressure cntrol element; Further, one is at least provided with by described first load boss or described second load boss for described stator provides the elastic element of elastic force; Described stator can under the Stress control of described first control chamber or the second control chamber, and slide in the rectilinear direction of the described first load boss arranged and the second load boss, feedback regulation exports discharge capacity.
Preferably, described second control chamber can be communicated with main oil gallery by described oil pressure cntrol element, or is communicated with fuel tank.
Preferably, described oil pressure cntrol element is two-bit triplet solenoid valve.
Preferably, described elastic element is arranged on the second load boss side.
Preferably, described elastic element is pressure spring.
Preferably, comprising: support ring, be arranged on described rotor, and the dead in line of the axis of described support ring and described stator.
Preferably, comprising: safety unloading valve, be arranged on oil discharge passage.
Compared with prior art, the blade variable displacement pump that the application provides, described first control chamber and the second control chamber connection control oil pressure separately; Wherein, the first control chamber is communicated with main oil gallery, and the second control chamber, by connected oil pressure cntrol element, can work under the control oil pressure of different pressures.Also be provided with elastic element in the second control chamber side and elastic force is provided, under the main oil gallery pressure that stator can be provided at the first control chamber, slide in the straight direction according to oil pressure change, feedback regulation is carried out to discharge capacity; And, as required, the control oil pressure of the second control chamber can be controlled by oil pressure cntrol element, thus realize adjusting the change level of discharge capacity, in other words, the first control chamber that the fluid pressure that stator is subject to by the blade variable displacement pump that the application provides is arranged by its both sides and the second control chamber and cancel out each other, to reduce in cavity oil pressure to the impact of stator.
The blade variable pump delivery adjustment process provided due to this application is realized by the stator of straight line motion, and the linearity making it regulate is excellent, and displacement control is accurate, can obtain better energy-saving effect; The analytical calculation of this blade variable displacement pump is also more simple and easy.
Accompanying drawing explanation
Fig. 1 is the example structure schematic diagram of a kind of blade variable displacement pump that the application provides;
Fig. 2 is a kind of blade variable displacement pump that the application provides working state structure schematic diagram when being in low pressure grade variable;
Fig. 3 is a kind of blade variable displacement pump that the application provides working state structure schematic diagram when being in high pressure grade variable.
Figure number illustrates:
The pump housing 10, stator 11, rotor 12, blade 13, cavity 14, oil suction chamber 15, oil inlet end 151, goes out oil pocket 16, oil outlet end 161, live axle 17, the first control chamber 18, first load boss 181, second control chamber 19, second load boss 191, main oil gallery 20, fuel tank 21, elastic element 22, two-bit triplet solenoid valve 23, support ring 24, safety unloading valve 25, oil filter 26, machine oil cooler 27.
Embodiment
Set forth a lot of detail in the following description so that fully understand the application.But the application can be much different from alternate manner described here to implement, those skilled in the art can when doing similar popularization without prejudice to when the application's intension, and therefore the application is by the restriction of following public concrete enforcement.
Please refer to shown in Fig. 1, Fig. 1 is the example structure schematic diagram of a kind of blade variable displacement pump that the application provides.Wherein, the vane pump that the application provides comprises: the pump housing, pump cover (not shown), stator, rotor and be arranged at described epitrochanterian blade; The described pump housing and described pump cover enclose form accommodating stator, rotor, blade cavity and provide the pipeline structure in path for working medium, this pipeline structure comprises and is positioned at described cavity both sides and the oil suction chamber do not communicated and go out oil pocket, described oil suction chamber has oil inlet end, described in go out oil pocket there is oil outlet end; At least comprise between described stator and described rotor a profile close working zone, described working zone respectively with described oil suction chamber with described go out oil pocket be communicated with; Described rotor is provided with the live axle with external driver device secure fit, or described external driver device comprises live axle, described rotor is provided with the attachment hole (not shown) with this live axle secure fit; Described external driver device is rotated in the medial axis of described this rotor of stator internal winding by rotor described in described drive shaft.
In this enforcement, described cavity inner wall is respectively arranged with the first relative control chamber and the second control chamber, described stator two ends are respectively arranged with the first load boss be connected with described first control chamber and the second load boss be connected with described second control chamber, and the load-carrying surface area of described second load boss is less than the load-carrying surface area of the first load boss.Described first control chamber is communicated with main oil gallery; Described second control chamber is connected with oil pressure cntrol element, and adjusts the oil pressure in the second control chamber by oil pressure cntrol element; And, be at least provided with one by described first load boss or described second load boss for described stator provides the elastic element of elastic force.
Corresponding elastic force can be there is in described elastic element according to the size of pressure, under the main oil gallery pressure that can provide at the first control chamber, according to the oil pressure of oil pressure cntrol element adjustment, the rectilinear direction that the stator made is formed at both sides load boss is slided, feedback regulation is formed to discharge capacity, thus improve the precision of blade variable displacement pump displacement control, obtain better energy-saving effect.
In this enforcement, described elastic element can be arranged on the second load boss side, is namely arranged in described second control chamber, thus provides elastic force for described stator.
In this enforcement, can there is corresponding elastic strain according to the size of pressure in described elastic element, therefore, pressure spring can be adopted to realize corresponding function, certainly, elastic element can be met when being under pressure, elastically-deformable any element occurs.
Based on same principle, do not get rid of following technological scheme: elastic element is set in described first load boss side, and this elastic element is draught spring.
Pressure in described first control chamber and the second control chamber, realize adjusting by the oil pressure cntrol element be connected with described second control chamber, in this enforcement, pressure in described second control chamber can pass through oil pressure cntrol element, make described second control chamber be communicated with main oil gallery or be communicated with fuel tank, realize Stress control.Described oil pressure cntrol element can adopt two-bit triplet solenoid valve.
Be understandable that, above-mentioned second control chamber is all crossed oil pressure cntrol element and can is communicated with main oil gallery or be communicated with fuel tank respectively, thus realizes the adjustment of two-stage variable, can also arrange the adjustment realizing one-level or multi-stage variable by oil pressure cntrol element.
In the present embodiment, described two-bit triplet solenoid valve can pass through the break-make that ECU (electronic control unit) controls it.
Stator in the blade variable displacement pump provided for enabling the application is better firmly connected with blade, described rotor is provided with support ring, the axis of described support ring overlaps with the axis of described stator, and the outer wall of described support ring is connected with the blade near side, axle center.
For preventing outlet passage inner engine oil overpressure from causing the infringement to blade variable displacement pump, this enforcement is also provided with safety unloading valve on oil discharge passage, when engine oil pressure is too high, opens this safety unloading valve, release pressure.
Above the blade variable pump structure that the application provides is illustrated, is introduced, specifically with reference to following content below in conjunction with the work process of said structure to the frontal lobe sheet variable displacement pump that the application provides:
In this enforcement, be described with two-stage variable: the first is other variable working procedure of low pressure stage, the second is other variable working procedure of high pressure stage; Low pressure and high pressure is distinguished by setting ECU break-make condition.
Be understandable that, the blade variable displacement pump that the application provides is not limited to two-stage and regulates, and can set oil pressure cntrol element as required and realize multi-level variable adjustment.
For ensureing the normal work of blade variable displacement pump and improving working life, in this enforcement, main oil gallery is provided with oil filter and/or machine oil cooler, described oil filter can filter mechanical admixture, colloid etc. in machine oil.The heat radiation that described machine oil cooler can accelerate machine oil makes it keep lower temperature.
Please refer to shown in Fig. 2, Fig. 2 is a kind of blade variable displacement pump that the application provides working state structure schematic diagram when being in low pressure grade variable.
Engine speed is 650-2500rpm, and engine temperature is higher than 50 DEG C, and blade variable displacement pump is in low pressure rank.The solenoid valve of blade variable displacement pump is in "on" position, and described second control chamber is communicated with described fuel tank, and the pressure in described second control chamber was zero (ignoring atmospheric pressure herein); Described first control chamber is communicated with described main oil gallery, and the pressure in described first control chamber equals the pressure in main oil gallery.
Work as constant engine speed NE, main oil gallery pressure is constant, and Stator forces state is: F
elastic force=P
main oil gallery× S
1(wherein F
elastic forcebe the pressure of the second control chamber internal pressure spring, S
1be the compression area of the first control chamber or the load area of the first load boss), stator is now in balance state of rest, and the eccentric distance between stator and rotor is constant, and blade variable pump delivery is stablized, constant flow.
When engine speed rises, main oil gallery pressure rises, and stator presents following stress in transition state: F
elastic force<P
main oil gallery× S
1, described stator, to a Slideslip of the second control chamber, makes the throw of eccentric between stator and rotor reduce, and produces to blade variable pump delivery, output flow, main oil gallery pressure the feedback reducing direction; Work as F
spring '=P
main oil gallery '× S
1time, the position residing for stator is the new equilibrium position of blade variable displacement pump, stator stop slide, thus make blade variable displacement pump enter discharge capacity stablize, output flow is constant, the new state of main oil gallery invariablenes pressure of liquid.Because stator occurs slide thus make the throw of eccentric between stator, rotor reduce, oil pump is often transferred out discharge capacity and is reduced, the flow making engine speed increase to cause increases trend and is significantly attenuated, and makes this blade pump delivery relatively stable before and after engine speed change.
When engine speed declines, main oil gallery pressure declines, and stator presents following stress in transition state: F
elastic force>P
main oil gallery× S
1, described stator, to a Slideslip of the first control chamber, makes the throw of eccentric between stator and rotor increase, and produces to blade variable pump delivery, output flow, main oil gallery pressure the feedback increasing direction; Work as F
spring '=P
main oil gallery '× S
1time, the position residing for stator is the new equilibrium position of blade variable displacement pump, stator stop slide, thus make blade variable displacement pump enter discharge capacity stablize, output flow is constant, the new state of main oil gallery invariablenes pressure of liquid.Because stator occurs slide thus make the throw of eccentric between stator, rotor increase, oil pump often transfers out discharge capacity to be increased, flow engine speed being declined cause reduces trend and is significantly attenuated, and makes this blade pump delivery relatively stable before and after engine speed change.
More than for blade variable displacement pump is in the explanation of low pressure grade variable work, can find out, blade variable displacement pump according to the change of engine speed, by improve stator slide direction, make the pressure in the first control chamber and the second control chamber reach balance, thus ensure the stable output of blade variable displacement pump.
Please refer to shown in Fig. 3, Fig. 3 is a kind of blade variable displacement pump that the application provides working state structure schematic diagram when being in high pressure grade variable.
Engine speed is for being greater than 3000rpm, and engine temperature is higher than 50 DEG C, and blade variable displacement pump is in high pressure rank.The solenoid valve of blade variable displacement pump is in off-position, and described second control chamber is communicated with described main oil gallery, that is, the pressure in the second control chamber equals main oil gallery pressure; Described first control chamber is communicated with described main oil gallery, that is, the pressure in described first control chamber equals the pressure in main oil gallery.In practical work process, can by detecting main oil gallery pressure or engine speed, determine whether that the pressure of described second control chamber is switched to by needs to be communicated with main oil gallery, if needed, then that passes through the described two-position three-way valve of control obtains electric or dead electricity realization.
Work as constant engine speed NE, main oil gallery pressure is constant, and stator presents following stress in transition state: F
elastic force=P
main oil gallery× (S
1-S
2) (wherein F
elastic forcebe the pressure of the second control chamber internal pressure spring, S
1be the compression area of the first control chamber or the load area of the first load boss, S
2be the compression area of the second control chamber or the load area of the second load boss), stator is now in balance state of rest, and the eccentric distance between stator and rotor is constant, and blade variable pump delivery is stablized, constant flow, main oil gallery invariablenes pressure of liquid.
When engine speed rises, main oil gallery pressure rises, and stator presents following stress in transition state: F
elastic force<P
main oil gallery× (S
1-S
2), described stator, to a Slideslip of the second control chamber, makes the throw of eccentric between stator and rotor reduce, and produces to blade variable pump delivery, output flow, main oil gallery pressure the feedback reducing direction; Work as F
spring '=P
main oil gallery '× (S
1-S
2) time, the position residing for stator is the equilibrium position that blade variable displacement pump is new, stator stop slide, thus make blade variable displacement pump enter discharge capacity stablize, output flow is constant, the new state of main oil gallery invariablenes pressure of liquid.Because stator occurs slide thus make the throw of eccentric between stator, rotor reduce, oil pump is often transferred out discharge capacity and is reduced, the flow making engine speed increase to cause increases trend and is significantly attenuated, and makes this blade pump delivery relatively stable before and after engine speed change.
When engine speed declines, main oil gallery pressure declines, and Stator forces state is: F
elastic force>P
main oil gallery× (S
1-S
2), described stator, to a Slideslip of the first control chamber, makes the throw of eccentric between stator and rotor increase, and blade variable pump delivery, output flow, main oil gallery pressure produce the feedback increasing direction; Work as F
spring '=P
main oil gallery '× (S
1-S
2) time, the position residing for stator is the equilibrium position that blade variable displacement pump is new, stator stop slide, thus make blade variable displacement pump enter discharge capacity stablize, output flow is constant, the new state of main oil gallery invariablenes pressure of liquid.Because stator occurs slide thus make the throw of eccentric between stator, rotor increase, oil pump often transfers out discharge capacity to be increased, flow engine speed being declined cause reduces trend and is significantly attenuated, and makes this blade pump delivery relatively stable before and after engine speed change.
The working procedure of the blade variable displacement pump provided for the application above illustrates, it should be noted that, when stator reaches the limiting value of eccentric position, if main oil gallery pressure continues to raise, when reaching 5.5Bar, safety unloading valve then can trigger unlatching, release main oil gallery pressure.Described eccentric position limiting value is, and stator slides and is subject to cavity restriction when cannot slide, then be limit position, and certainly, limit position also can pass through to arrange limit parts in cavity or on stator outer wall, realize the triggering of safety unloading valve.
Although the application with preferred embodiment openly as above; but it is not for limiting the application; any those skilled in the art are not departing from the spirit and scope of the application; can make possible variation and amendment, the scope that therefore protection domain of the application should define with the application's claim is as the criterion.
Claims (7)
1. a blade variable displacement pump, comprises the pump housing, pump cover, stator, rotor and is arranged at described epitrochanterian blade;
The described pump housing and described pump cover enclose form accommodating stator, rotor, blade cavity and provide the pipeline structure in path for working medium, this pipeline structure comprises and is positioned at described cavity both sides and the oil suction chamber do not communicated and go out oil pocket;
At least comprise between described stator and described rotor a profile close working zone, described working zone respectively with described oil suction chamber with described go out oil pocket be communicated with;
Described rotor is provided with the live axle with external driver device secure fit, or described external driver device comprises live axle, described rotor is provided with the attachment hole with this live axle secure fit; Described external driver device is rotated in the medial axis of described this rotor of stator internal winding by rotor described in described drive shaft;
It is characterized in that: on described cavity inner wall, be provided with the first relative control chamber and the second control chamber, described stator two ends are respectively arranged with the first load boss be connected with described first control chamber and the second load boss be connected with described second control chamber, and the load-carrying surface area of described second load boss is less than the load-carrying surface area of the first load boss; Described first control chamber is communicated with main oil gallery; Described second control chamber is connected with oil pressure cntrol element; Further, one is at least provided with by described first load boss or described second load boss for described stator provides the elastic element of elastic force; Described stator can under the Stress control of described first control chamber or the second control chamber, and slide in the rectilinear direction of the described first load boss arranged and the second load boss, feedback regulation exports discharge capacity.
2. blade variable displacement pump according to claim 1, is characterized in that: described second control chamber can be communicated with main oil gallery by described oil pressure cntrol element, or is communicated with fuel tank.
3. blade variable displacement pump according to claim 2, is characterized in that: described oil pressure cntrol element is two-bit triplet solenoid valve.
4. blade variable displacement pump according to claim 1, is characterized in that, described elastic element is arranged on the second load boss side.
5. blade variable displacement pump according to claim 1, is characterized in that: described elastic element is pressure spring.
6. blade variable displacement pump according to claim 1, is characterized in that, comprising: support ring, is arranged on described rotor, and the dead in line of the axis of described support ring and described stator.
7. blade variable displacement pump according to claim 1, is characterized in that, comprising: safety unloading valve, be arranged on oil discharge passage.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201510869763.4A CN105443963A (en) | 2015-12-01 | 2015-12-01 | Blade variable pump |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201510869763.4A CN105443963A (en) | 2015-12-01 | 2015-12-01 | Blade variable pump |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN105443963A true CN105443963A (en) | 2016-03-30 |
Family
ID=55554472
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201510869763.4A Pending CN105443963A (en) | 2015-12-01 | 2015-12-01 | Blade variable pump |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN105443963A (en) |
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN110529720A (en) * | 2019-09-26 | 2019-12-03 | 淄博九洲润滑科技有限公司 | A kind of all-sealed lubrication relay pump |
| CN112682679A (en) * | 2021-01-25 | 2021-04-20 | 湖南机油泵股份有限公司 | Variable displacement oil pump capable of avoiding interference |
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| US4035105A (en) * | 1975-04-16 | 1977-07-12 | G. L. Rexroth Gmbh | Variable-output pump control arrangement |
| JPS59137673A (en) * | 1983-01-25 | 1984-08-07 | Saitama Kiki Kk | Flow-rate control valve |
| CN201723442U (en) * | 2010-07-21 | 2011-01-26 | 安徽工程大学 | Variable displacement energy-saving lubricating oil vane pump |
| DE102012217100A1 (en) * | 2012-09-24 | 2014-04-17 | Robert Bosch Gmbh | Pump assembly comprising a vane pump |
| CN104204528A (en) * | 2012-03-21 | 2014-12-10 | 萱场工业株式会社 | Variable-capacity vane pump |
| CN205191174U (en) * | 2015-12-01 | 2016-04-27 | 东风汽车泵业有限公司 | Blade variable pump |
-
2015
- 2015-12-01 CN CN201510869763.4A patent/CN105443963A/en active Pending
Patent Citations (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US4035105A (en) * | 1975-04-16 | 1977-07-12 | G. L. Rexroth Gmbh | Variable-output pump control arrangement |
| JPS59137673A (en) * | 1983-01-25 | 1984-08-07 | Saitama Kiki Kk | Flow-rate control valve |
| CN201723442U (en) * | 2010-07-21 | 2011-01-26 | 安徽工程大学 | Variable displacement energy-saving lubricating oil vane pump |
| CN104204528A (en) * | 2012-03-21 | 2014-12-10 | 萱场工业株式会社 | Variable-capacity vane pump |
| DE102012217100A1 (en) * | 2012-09-24 | 2014-04-17 | Robert Bosch Gmbh | Pump assembly comprising a vane pump |
| CN205191174U (en) * | 2015-12-01 | 2016-04-27 | 东风汽车泵业有限公司 | Blade variable pump |
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN110529720A (en) * | 2019-09-26 | 2019-12-03 | 淄博九洲润滑科技有限公司 | A kind of all-sealed lubrication relay pump |
| CN112682679A (en) * | 2021-01-25 | 2021-04-20 | 湖南机油泵股份有限公司 | Variable displacement oil pump capable of avoiding interference |
| CN112682679B (en) * | 2021-01-25 | 2022-03-11 | 湖南机油泵股份有限公司 | Variable displacement oil pump capable of avoiding interference |
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Application publication date: 20160330 |
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