CN102297131A - Port plate and hydraulic pump equipped with it - Google Patents
Port plate and hydraulic pump equipped with it Download PDFInfo
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- CN102297131A CN102297131A CN2011101904368A CN201110190436A CN102297131A CN 102297131 A CN102297131 A CN 102297131A CN 2011101904368 A CN2011101904368 A CN 2011101904368A CN 201110190436 A CN201110190436 A CN 201110190436A CN 102297131 A CN102297131 A CN 102297131A
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Abstract
Aiming to solve the problems of great noise and poor output flow uniformity in present hydraulic pumps, the invention relates to a hydraulic pump, especially a port plate for hydraulic pumps. The invention discloses a port plate which is provided with oil discharge windows, at two ends and along the center line of which composite vibration damping grooves butted and communicated with the oil discharge windows extend outward. The composite vibration damping grooves consist of upper parts and lower parts. The upper parts are invariable flow section cavities, while the lower parts are variable flow section cavities, the ends of which far from the oil discharge windows have the smallest flow area. Thereofre, the vibration damping grooves at the ends of the oil discharge windows are formed by overlying and parallel connection of invariable flow section vibration damping grooves and variable flow section vibration damping grooves, so that the maximum pressure gradient in a pre-pressurizing working chamber is reduced during flow distribution and the flow distribution impact is also reduced, thus, minimizing the peak value of instantaneous loss flow, reducing the pump flow pulsation and improving the uniformity of output flow.
Description
Technical field
The present invention relates to thrust plate, and with the oil hydraulic pump of this thrust plate.
Background technique
Double-acting vane pump is a kind of structural type of oil hydraulic pump, because of having little, the low noise advantages of output flow pulsation, has obtained to use widely.As seen, the pulsation of noise and output flow is that the output flow uniformity is to weigh the important indicator of high pressure vane pump performance.The main source of high pressure vane pump noise is a flow noise, and flow noise is to be impacted by the flow that flowing of fluid in the vane pump assignment process produced to produce, therefore, as long as the flow when reducing the vane pump flow just impacts effectively control flows bulk noise.Experiment was once done by the special Rand Corporation of Saunders, and when the maximum value of pressure gradient in the pre-loading active chamber increases when being twice, the noise of axial piston pump has improved 6dB.This shows, the size that the flow when the peaked size of pre-loading pressure gradient has determined the high pressure vane pump flow impacts, promptly the pre-loading pressure gradient is the measurement index that flow impacts.Compression shock in order to reduce to join oil, The initial segment place corresponding to the oil extraction transition curve on the thrust plate of high pressure vane pump is provided with pre-loading choke-out angle and vibration damping groove, in the pre-loading process, high pressure oil in the oil-discharging cavity pours in down a chimney back in the active chamber by the vibration damping groove, make with mechanical choke-out compression acting in conjunction that the pressure of fluid raises gradually in the active chamber, wherein, mechanical choke-out compression flow and the loss flow that flow is a pump that pours in down a chimney by the vibration damping groove.
At present, the vibration damping groove of thrust plate commonly used is the triangular groove of change overflow section or the rectangle groove of permanent overflow section, and wherein, overflow section is meant the cross-section area when the fluid flowing full is by the vibration damping groove in the assignment process.Shown in Figure 1 is the thrust plate that adopts on the vane pump of this company's pin-type load structure of atropic, and its matrix 11 is for there being certain thickness cirque body, and its ring-type is limited by concentric interior circle of one and cylindrical and forms, and the center is a manhole.Have two oil extraction windows 12 and two oil sucking windows 13 near the cylindrical place on cirque body, described oil extraction window 12 and oil sucking window 13 are isolated mutually and be symmetrical distribution, are connected with the inlet port and the oil drain out of pump respectively.On cirque body, offer high-pressure oil chamber 14 and low pressure grease chamber 15 respectively near interior circle and with described oil extraction window 12 and oil sucking window 13 corresponding positions, and be communicated with by oilhole 16,17 and oil extraction window 12, oil sucking window 13 respectively, have vibration damping groove 18 in the end of low pressure grease chamber 15, have the vibration damping groove 19 that is communicated with it in the end of oil extraction window 12, described vibration damping groove 19 is the triangular cone tank, wherein, the summit of described triangular pyramid is away from oil extraction window 12.
Such thrust plate, simple in structure, to a certain extent reduced pump vibration, reduced noise, but in the flow transient process, the maximum value of pressure gradient is bigger in the pre-loading active chamber, can not control flow effectively impacts, cause flow noise big, and then the noise when causing hydraulic pump works is big; In addition, also bigger from the instantaneous flow that oil-discharging cavity is incorporated into fluid the pre-loading active chamber by the vibration damping groove, promptly the instantaneous loss flow of oil hydraulic pump is bigger, causes the output flow pulsation of pump to increase, and then reduces the output flow uniformity.
Summary of the invention
For oil hydraulic pump noise in the solution prior art is big, the problem of output flow lack of homogeneity.The inventor carries out deep discovering to existing oil hydraulic pump with the working principle and the structure of thrust plate: the vibration damping groove structure difference at oil extraction window place on the thrust plate, in assignment process, pour in down a chimney back the change curve difference of the instantaneous flow of fluid the active chamber from oil-discharging cavity, and then cause the change curve of the change curve of pressure gradient in the pre-loading active chamber and output flow also different; The pre-loading gradient that overflow section is respectively the vibration damping groove correspondence of permanent overflow section and change overflow section superposes, and the variation of resulting curve is milder.
On the basis of further investigation, the inventor proposes a kind of thrust plate, has the oil extraction window on this thrust plate, and the center line at the two ends of described oil extraction window along the oil extraction window is outward extended with the combined vibration-damping groove that is docked and connected with the oil extraction window; Described combined vibration-damping groove is made of upper and lower two-part; Described top is divided into permanent overflow section die cavity body; Described bottom is divided into and becomes overflow section die cavity body, and long-pending minimum away from the overflow section of an end of oil extraction window
Like this, the vibration damping groove of oil extraction window end adopts permanent overflow section type vibration damping groove and becomes overflow section type vibration damping groove stack form in parallel, has reduced in the assignment process maximum value of pressure gradient in the pre-loading active chamber, has reduced the flow impact; Make mechanical choke-out compression flow and the overlaying flow peak value minimum of pouring in down a chimney flow by the vibration damping groove, the peak value minimum of promptly instantaneous loss flow has reduced the flow pulsation of pump, has improved the uniformity of output flow.
Preferably, the top of described combined vibration-damping groove is divided into any one in multi-edge column-shaped cavity, half-cylindrical cavity or the semiellipse cylindricality cavity, and the bottom is divided into any one in polygonal pyramid shape cavity, half cone-shaped cavity or the semiellipse cone-shaped cavity.
Preferably, described polygon prism is any one in quadrangular, pentagonal prism, six prisms or seven prisms, and described polygonal pyramid is any one in triangular pyramid, rectangular pyramid, pentagonal pyramid, hexagonal pyramid or seven pyramids.
Such thrust plate processing technology is comparatively simple, and is that the thrust plate of triangular taper or cuboid shape is compared with vibration damping groove structure, can reduce further that flow in the assignment process impacts and the output flow of pump is pulsed.
The present invention also proposes a kind of oil hydraulic pump that above-mentioned thrust plate is housed.
Preferably, described oil hydraulic pump is a double-acting vane pump.
Description of drawings
Fig. 1 is the structural representation of the used thrust plate of vane pump of this company's pin-type load structure of atropic;
Fig. 2 is the structural representation of thrust plate of the present invention;
Fig. 3 is the A-A partial enlarged drawing (magnification ratio is 5: 1) of Fig. 2;
Fig. 4 is the B-B view of Fig. 3;
Fig. 5 is the A-A partial enlarged drawing (magnification ratio is 5: 1) of the another kind of structural type of Fig. 2;
Fig. 6 is the B-B view of Fig. 5;
Fig. 7 is a double-acting vane pump flow principle schematic of the present invention;
Fig. 8 is the plotted curve of vibration damping groove structural type to the influence of pre-loading variation in pressure;
Fig. 9 is the plotted curve of vibration damping groove structural type to the influence of pre-loading pressure gradient;
Figure 10 is the plotted curve of vibration damping groove structural type to the influence of pump instantaneous flow.
Embodiment
As shown in Figure 2, thrust plate matrix 21 is for there being certain thickness cirque body, and its ring-type is limited by concentric interior circle of one and cylindrical and forms, and its center is a manhole.Have two oil extraction windows 22 and two oil sucking windows 23 near the cylindrical place on matrix 21, described oil extraction window 22 be that waist through hole and described oil sucking window 23 completely cut off mutually and be symmetrical distribution, and is communicated with the inlet port and the oil drain out of pump respectively.Offer the logical oil groove 24 of annular near inner circle on matrix 21, and be connected by the oil-discharging cavity of damping hole 25 and pump, described damping hole 25 is positioned on the logical oil groove 24 and is corresponding with the position of described oil extraction window 22.Center line at the two ends of described oil extraction window 22 along oil extraction window 22 is outward extended with the combined vibration-damping groove 26 that is communicated with oil extraction window 22.As shown in Figure 3 and Figure 4, described combined vibration-damping groove 26 is made of upper and lower two-part, be that top is divided into the cuboid shape cavity, the bottom is divided into triangular pyramid shape cavity, wherein, the summit of described triangular pyramid is away from oil extraction window 22, the bottom surface of this summit correspondence described oil extraction window 22 that is docked and connected, and the cross section that is parallel to this bottom surface or interface of described combined vibration-damping groove 26 is an overflow section.
Combined vibration-damping groove among Fig. 2 also can adopt structural type as illustrated in Figures 5 and 6, wherein, described combined vibration-damping groove is made of upper and lower two-part, be that top is divided into the cuboid shape cavity, the bottom is divided into the semiellipse cone-shaped cavity, wherein, the summit of described semiellipse awl is away from the oil extraction window, its bottom surface described oil extraction window that is docked and connected.
In addition, described combined vibration-damping groove also can adopt following structural type, be that the top of described combined vibration-damping groove is divided into any one cavity in multi-edge column-shaped cavity, half-cylindrical cavity or the semiellipse cylindricality cavity, the bottom is divided into any one cavity in polygonal pyramid shape cavity, half cone-shaped cavity or the semiellipse cone-shaped cavity.Wherein, described polygon prism can be quadrangular, pentagonal prism, six prisms or seven prisms etc.; Described semicolumn is meant that the bottom surface is semicircular cylinder; Described semiellipse post is meant that the bottom surface is half elliptic cylinder; Described polygonal pyramid is triangular pyramid, rectangular pyramid, pentagonal pyramid, hexagonal pyramid or seven pyramids etc.; Described half-conical is meant that the bottom surface is semicircular centrum; Described semiellipse awl is meant that the bottom surface is half elliptic centrum.Top such as described combined vibration-damping groove is that overflow section is trapezoidal four prism type cavity, and the bottom is the half cone-shaped cavity; The top of described combined vibration-damping groove is half-cylindrical cavity, and the bottom is the triangular cone-shaped cavity, and wherein, intersect in the joint of the two circular arc on the semicircle bottom edge of half-cylindrical cavity and the bottom surface of triangular cone-shaped cavity; The top of described combined vibration-damping groove is semiellipse cylindricality cavity, and the bottom is a rectangular pyramid shape cavity, and wherein, intersect in the joint of the two bottom surface of circular arc on the half elliptic bottom edge of semiellipse cylindricality cavity and rectangular pyramid shape cavity; The top of described combined vibration-damping groove is pentagonal prism shape cavity, and the bottom is a hexagonal pyramid shape cavity, and wherein, the pentagonal prism cavity bi-side of both sides up and down is parallel to each other, and is connected with hexagonal pyramid shape cavity by the side that is positioned at the below.
During concrete enforcement, the structure of described combined vibration-damping groove comprises that also the top that those skilled in the art can expect is divided into permanent overflow section die cavity body, the bottom is divided into change overflow section die cavity body, and described combined vibration-damping groove is away from long-pending other the minimum combining forms of the overflow section of an end of oil extraction window.
The vibration attenuation mechanism of thrust plate combined vibration-damping groove among the present invention: with the double-acting vane pump thrust plate is example, its flow principle as shown in Figure 7, constitute a active chamber 72 by adjacent two blades 71, when single active chamber 72 rotates to the choke-out district with rotor 73 with independent oil extraction function
In, and when connecting with oil-discharging cavity by combined vibration-damping groove 75, the oil-discharging cavity high pressure oil is introduced active chamber 72 through the combined vibration-damping groove 75 of oil extraction window 74 ends, concur with the mechanical choke-out compression process of active chamber 72 and to make active chamber 72 inner fluid pre-loadings, and then and oil-discharging cavity connect, impact, reduce noise thereby reduce flow.
In assignment process:
The active chamber volume changes dV and is made of two-part, and the first is by the Volume Changes that retraction produced of blade at blade groove:
In the formula: B is the width of blade, and R is the radius of stator inner curve large radius arc, ρ
2Be the utmost point footpath of stator curve,
Be the corner of rotor, s is a vane thickness.
It two is to draw the Volume Changes that produced of oil by the vibration damping groove from oil-discharging cavity to the pre-loading active chamber:
In the formula: C
qBe flow coefficient, A
0Be vibration damping groove area of passage, ρ
1Be fluid density, p is the pressure of fluid in single active chamber.
So the active chamber volume is changed in the pre-loading process: dV=dV
1+ dV
2
That is:
Calculate for convenience, the fluid initial volume that the fluid volume seals when entering pre-loading choke-out district in the active chamber is similar to replacement:
In the formula: z is the number of blade, r
pBe the rotor exradius.
And in the choke-out cavity volume, the pass of variation in pressure Δ P and Volume Changes Δ V is: Δ P=-K Δ V/V
In the formula: V is the volume of fluid in single active chamber, and K is the volumetric modulus of elasticity of fluid.
After its differential equation arrangement:
And then, can draw the pressure gradient of fluid in the pre-loading active chamber
And the pass between Volume Changes dV is:
In the formula: p
sBe the oil extraction pressure of pump, ω is the rotating speed of rotor.
By above-mentioned pressure gradient
With the relation of Volume Changes dV as can be known, when vane pump adopts the thrust plate of vibration damping groove of different structure form, the pressure trend difference of the fluid in its pre-loading active chamber.As adopt the change overflow section type vibration damping groove of triangular taper, the permanent overflow section type vibration damping groove of cuboid shape and the permanent overflow section die cavity body that top is divided into cuboid shape, when the bottom was divided into the combined vibration-damping groove of change overflow section die cavity body of triangular pyramid shape, the pre-loading pressure history as shown in Figure 8.Wherein, curve 81 is for becoming the pre-loading pressure history of overflow section type vibration damping groove; Curve 82 is the pre-loading pressure history of permanent overflow section type vibration damping groove; Curve 83 is the pre-loading pressure history of combined vibration-damping groove.
As shown in Figure 8, from the pre-loading angle range, when adopting the combined vibration-damping groove, the pre-loading curve approximation in the blade working chamber is a straight line, and the process of boosting is the most steady; Become overflow section vibration damping groove when corner is big, pressure rises fast; Deng the beginning section of overflow section vibration damping groove at corner, pressure rises very fast, and variation in pressure is mild gradually subsequently.
The loss flow that draws oil by the vibration damping groove is:
How much instantaneous floies of pump are:
q
v，sh＝B(R
2-r
2)ω-2Bs∑v
In the formula: v is the radial velocity that is in oil suction district blade.
How much instantaneous flow q of pump
V, shWith the instantaneous flow q that draws oil in the pre-loading process by the vibration damping groove
V, sThe instantaneous flow q that superposes and to get pump
vFor:
This shows, drawing the flow loss that oil produces by the vibration damping groove in the pre-loading process is the main cause of double-acting vane pump instantaneous flow pulsation, the vibration damping groove of employing different structure form can make the waveform difference by the loss flow of vibration damping groove in the pre-loading process, and finally has influence on the instantaneous flow pulsation of pump.
Embodiment: with a kind of double-acting vane pump is example
The specification of selected double-acting vane pump: the radius of stator inner curve large radius arc is 21.2mm, the radius of stator inner curve small-radius arc is 18.6mm, rotating speed is 2200r/min, flow coefficient is 0.7, the volumetric modulus of elasticity of fluid is 1300MPa, and the density of fluid is 870Kg/m3, and the oil extraction pressure of pump is 14MPa, vane thickness is 1.2mm, and the width of blade is 17.8mm.
When the change overflow section type vibration damping groove, the permanent overflow section type vibration damping groove of cuboid shape and the permanent overflow section die cavity body that top is divided into the cuboid type that adopt the triangular taper, when the bottom is divided into the combined vibration-damping groove of change overflow section die cavity body of triangular pyramid shape, in assignment process, the pressure gradient of fluid changes as shown in Figure 9 in the pre-loading active chamber, and the instantaneous flow of pump changes as shown in figure 10.Among Fig. 9, curve 91 is for becoming the pre-loading pressure gradient change curve of overflow section type vibration damping groove; Curve 92 is the pre-loading pressure gradient change curve of permanent overflow section type vibration damping groove; Curve 93 is the pre-loading pressure gradient change curve of combined vibration-damping groove.Among Figure 10, curve 101 is for becoming the instantaneous flow change curve of overflow section type vibration damping groove; Curve 102 is the instantaneous flow change curve of permanent overflow section type vibration damping groove; Curve 103 is the instantaneous flow change curve of combined vibration-damping groove.
By Fig. 9 and Figure 10 as seen, adopt the combined vibration-damping groove and adopt change overflow section type vibration damping groove separately or etc. overflow section type vibration damping groove compare, in assignment process, the pulsation of the maximum value of pressure gradient and the instantaneous flow of pump all reduced more than one times, significantly reduced the uniformity that flow impacts and improved POF.
By above-mentioned vibration attenuation mechanism and specific embodiment as can be known, be divided into permanent overflow section die cavity body by top, the bottom is divided into and becomes combined vibration-damping groove that overflow section type groove is combined into and be applied to arbitrarily on the thrust plate, all can reduce the size that flow impacts by the maximum value that reduces the pre-loading pressure gradient, and then effective control flows bulk noise, reduce the noise of oil hydraulic pump; The peak value of the instantaneous loss flow by reducing the vibration damping groove reduces the instantaneous flow pulsation of oil hydraulic pump, and then improves the uniformity of output flow.
Claims (7)
1. a thrust plate has the oil extraction window on this thrust plate, it is characterized in that, the center line at the two ends of described oil extraction window along the oil extraction window is outward extended with the combined vibration-damping groove that is docked and connected with the oil extraction window; Described combined vibration-damping groove is made of upper and lower two-part; Described top is divided into permanent overflow section die cavity body; Described bottom is divided into and becomes overflow section die cavity body, and long-pending minimum away from the overflow section of an end of oil extraction window.
2. thrust plate according to claim 1 is characterized in that, the top of described combined vibration-damping groove is divided into any one in multi-edge column-shaped cavity, half-cylindrical cavity or the semiellipse cylindricality cavity.
3. thrust plate according to claim 1 is characterized in that, the bottom of described combined vibration-damping groove is divided into any one in polygonal pyramid shape cavity, half cone-shaped cavity or the semiellipse cone-shaped cavity.
4. thrust plate according to claim 2 is characterized in that, described polygon prism is any one in quadrangular, pentagonal prism, six prisms or seven prisms.
5. thrust plate according to claim 3 is characterized in that, described polygonal pyramid is any one in triangular pyramid, rectangular pyramid, pentagonal pyramid, hexagonal pyramid or seven pyramids.
6. an oil hydraulic pump is characterized in that, comprises any described thrust plate in the claim 1 to 5.
7. oil hydraulic pump according to claim 6 is characterized in that, described oil hydraulic pump is a double-acting vane pump.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN2011101904368A CN102297131A (en) | 2011-07-08 | 2011-07-08 | Port plate and hydraulic pump equipped with it |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN2011101904368A CN102297131A (en) | 2011-07-08 | 2011-07-08 | Port plate and hydraulic pump equipped with it |
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|---|---|
| CN102297131A true CN102297131A (en) | 2011-12-28 |
Family
ID=45357752
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN2011101904368A Pending CN102297131A (en) | 2011-07-08 | 2011-07-08 | Port plate and hydraulic pump equipped with it |
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|---|---|
| CN (1) | CN102297131A (en) |
Cited By (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN103727028A (en) * | 2013-12-18 | 2014-04-16 | 宁波市鄞州金本机械有限公司 | Double-acting impeller pump |
| CN104121189A (en) * | 2014-07-14 | 2014-10-29 | 阜新德尔汽车部件股份有限公司 | A difunctional stepless speed regulator oil pump |
| CN103511251B (en) * | 2012-06-04 | 2017-03-08 | 罗伯特博世汽车转向有限公司 | Positive displacement pump |
| CN107035686A (en) * | 2015-12-25 | 2017-08-11 | 株式会社昭和 | Vane pump apparatus |
| CN107387404A (en) * | 2017-09-09 | 2017-11-24 | 湖南机油泵股份有限公司 | A kind of high-efficiency blade pump |
| WO2019216173A1 (en) * | 2018-05-11 | 2019-11-14 | Ｋｙｂ株式会社 | Vane pump |
Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN2351596Y (en) * | 1998-09-30 | 1999-12-01 | 上海液压件厂 | Pin-type vane pump |
| CN1544813A (en) * | 2003-11-12 | 2004-11-10 | 浙江大学 | Bubble evolution proof plunger pump port plate |
| CN101694211A (en) * | 2009-10-16 | 2010-04-14 | 华中科技大学 | Port plate for plunger pump |
| CN101881270A (en) * | 2010-07-21 | 2010-11-10 | 无锡威孚精密机械制造有限责任公司 | Oil distribution disk with damping structure |
| US20110150684A1 (en) * | 2009-12-18 | 2011-06-23 | Hitachi Automotive Systems, Ltd. | Variable displacement vane pump |
-
2011
- 2011-07-08 CN CN2011101904368A patent/CN102297131A/en active Pending
Patent Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN2351596Y (en) * | 1998-09-30 | 1999-12-01 | 上海液压件厂 | Pin-type vane pump |
| CN1544813A (en) * | 2003-11-12 | 2004-11-10 | 浙江大学 | Bubble evolution proof plunger pump port plate |
| CN101694211A (en) * | 2009-10-16 | 2010-04-14 | 华中科技大学 | Port plate for plunger pump |
| US20110150684A1 (en) * | 2009-12-18 | 2011-06-23 | Hitachi Automotive Systems, Ltd. | Variable displacement vane pump |
| CN101881270A (en) * | 2010-07-21 | 2010-11-10 | 无锡威孚精密机械制造有限责任公司 | Oil distribution disk with damping structure |
Non-Patent Citations (1)
| Title |
|---|
| 李向辉等: "减振槽型式对转向叶片泵瞬时流量的影响", 《液压与气动》, no. 12, 31 December 2006 (2006-12-31), pages 74 - 76 * |
Cited By (10)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN103511251B (en) * | 2012-06-04 | 2017-03-08 | 罗伯特博世汽车转向有限公司 | Positive displacement pump |
| CN103727028A (en) * | 2013-12-18 | 2014-04-16 | 宁波市鄞州金本机械有限公司 | Double-acting impeller pump |
| CN103727028B (en) * | 2013-12-18 | 2016-04-13 | 宁波市鄞州金本机械有限公司 | A kind of double-action wing pump |
| CN104121189A (en) * | 2014-07-14 | 2014-10-29 | 阜新德尔汽车部件股份有限公司 | A difunctional stepless speed regulator oil pump |
| CN107035686A (en) * | 2015-12-25 | 2017-08-11 | 株式会社昭和 | Vane pump apparatus |
| US10655624B2 (en) | 2015-12-25 | 2020-05-19 | Showa Corporation | Vane pump device for controlling deviation of a force applied to the vanes |
| CN107035686B (en) * | 2015-12-25 | 2020-07-24 | 株式会社昭和 | Vane pump device |
| CN107387404A (en) * | 2017-09-09 | 2017-11-24 | 湖南机油泵股份有限公司 | A kind of high-efficiency blade pump |
| WO2019216173A1 (en) * | 2018-05-11 | 2019-11-14 | Ｋｙｂ株式会社 | Vane pump |
| JP2019196768A (en) * | 2018-05-11 | 2019-11-14 | Ｋｙｂ株式会社 | Vane pump |
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Application publication date: 20111228 |