CN213298190U - High-bearing low-leakage anti-wear valve plate for axial plunger pump and axial plunger pump - Google Patents
High-bearing low-leakage anti-wear valve plate for axial plunger pump and axial plunger pump Download PDFInfo
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- CN213298190U CN213298190U CN202021580387.XU CN202021580387U CN213298190U CN 213298190 U CN213298190 U CN 213298190U CN 202021580387 U CN202021580387 U CN 202021580387U CN 213298190 U CN213298190 U CN 213298190U
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- plunger pump
- flow distribution
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Abstract
The utility model discloses a high-bearing low-leakage wear-resistant valve plate for axial plunger pump, the valve plate can cooperate with the cylinder body, wherein include with the cylinder body complex of axial plunger pump joins in marriage a class terminal surface, join in marriage and have top dead center and bottom dead center on the class terminal surface, the top dead center with the both sides of line form oil absorption low-pressure zone and oil discharge high-pressure zone respectively between the bottom dead center, near top dead center position and/or near bottom dead center position is equipped with radial oil groove and pit, oil absorption low-pressure zone and/or oil discharge high-pressure zone is equipped with circumference oil groove. Through right the valve plate sets up radial oil groove and pit and circumference oil groove, can promote the vice oil film of valve and become membrane and lubricating ability, makes to establish good oil film between valve plate and the cylinder body, forms the dynamic pressure lubrication, has good leakproofness, and it is inhomogeneous effectively to solve the valve plate oil film, and the problem of easy eccentric wear can improve the life and the mechanical efficiency of valve plate.
Description
Technical Field
The utility model belongs to the technical field of the plunger pump, concretely relates to a thrust plate that wear-resistants is leaked to height bearing for axial plunger pump hangs down.
Background
The axial plunger pump is widely applied to the fields of engineering machinery, ocean engineering, aerospace and the like, the service life of the axial plunger pump mainly depends on the service lives of three pairs of key friction pairs, wherein the cylinder body/valve plate friction pair is one of the three pairs of key friction pairs of the aviation axial plunger pump. Under the working condition of alternating load, the overturning phenomenon of the cylinder body easily causes the direct contact of the cylinder body and the valve plate, the eccentric wear of the valve plate is caused, the friction wear is generated, the internal leakage is increased, the volume efficiency of the axial plunger pump is reduced, and the phenomenon of 'plate burning' is even generated in severe cases.
Under the working condition of high speed and heavy load, the oil film failure of the cylinder body/valve plate friction pair is easy to occur, and the oil film failure can cause the bearing capacity of the valve pair to be seriously reduced, thereby influencing the service life of the valve pair. In the traditional method, an unloading groove is usually arranged to reduce the overturning moment of a cylinder body, so that the bearing performance of a flow distribution pair is improved, and the unloading groove is easy to cause the problem of abrasive dust pollution and blockage.
SUMMERY OF THE UTILITY MODEL
The utility model aims to solve the main problem that a high-bearing low-leakage wear-resistant valve plate for an axial plunger pump is provided, the problem of the vice easy eccentric wear of valve is effectively solved, and the vice life of valve is improved.
In order to solve the technical problem, the utility model provides a thrust plate that wear-resistants is hanged down leaked to high bearing for axial plunger pump, include: the flow distribution end face is matched with a cylinder body of the axial plunger pump;
the flow distribution end face is provided with an upper dead center and a lower dead center, one side of a connecting line between the upper dead center and the lower dead center forms an oil absorption low-pressure area, the other side of the connecting line between the upper dead center and the lower dead center forms an oil discharge high-pressure area, radial oil grooves and/or pits are arranged near the upper dead center position and/or near the lower dead center position, and circumferential oil grooves are arranged in the oil absorption low-pressure area and/or the oil discharge high-pressure area.
In a preferred embodiment, the projection of the radial oil groove in the flow distribution end surface is a straight line.
In a preferred embodiment, the cross-sectional profile of the radial oil groove in the direction normal to the flow distribution end face is rectangular or semicircular.
In a preferred embodiment, the radial oil grooves are more than two rows; and more than two rows of radial oil grooves are uniformly or symmetrically arranged along the flow distribution end surface of the flow distribution disc according to an equal circumferential angle.
In a preferred embodiment, the projection of the recess in the distribution end face is circular, elliptical or polygonal.
In a preferred embodiment, the number of the pits is more than two along the radial direction or the circumferential direction of the flow distribution end surface of the flow distribution disc; and more than two pits are uniformly or symmetrically arranged along the flow distribution end surface at an equal circumferential angle, or more than two pits are uniformly or symmetrically arranged along the radial direction of the flow distribution end surface of the flow distribution disc at equal intervals.
In a preferred embodiment, a projection of the circumferential oil groove in the flow distribution end surface is a circular arc.
In a preferred embodiment, a cross-sectional profile of the circumferential oil groove in a normal direction of the flow distribution end surface is rectangular or semicircular.
In a preferred embodiment, the circumferential oil grooves are distributed in more than two rows along the radial direction of the flow distribution end surface of the flow distribution disc; and more than two rows of circumferential oil grooves are arranged at equal intervals or symmetrically along the radial direction of the flow distribution end surface of the flow distribution disc.
The utility model also provides an axial plunger pump, include as above the valve plate, the valve terminal surface with the cylinder body cooperation forms the valve pair.
Compared with the prior art, the technical scheme of the utility model possess following beneficial effect:
1. the utility model provides a high-bearing low leakage valve plate that wear-resistants for axial plunger pump, through the easy wear area sets up the utility model provides a valve plate, at axial plunger pump during operation, fluid can flow in radial oil groove with the pit with the circumference oil groove makes establish its good oil film between valve plate and the cylinder body, form dynamic pressure lubrication. Because the areas where the pits and the circumferential oil grooves are arranged are easily worn, the oil film lubricating capability of the easily worn areas can be effectively improved by forming dynamic pressure lubrication in the areas, and the problems that the oil film of the thrust plate is uneven and is easily eccentric are solved, so that the service life of the axial plunger pump can be prolonged, and the mechanical efficiency of the axial plunger pump can be improved.
2. The utility model provides a high-bearing low-leakage wear-resistant valve plate for axial plunger pump, the valve plate can promote the vice oil film of valve and become membrane and lubricating property, has the capacity of holding bits simultaneously, and the vice bearing capacity of valve is strong, and withstand voltage wear-resisting characteristic is good, and long service life has important meaning to the reliability and the life-span that improve axial plunger pump.
Drawings
Fig. 1 is a schematic structural view of a flow distribution pair of an axial plunger pump according to an embodiment of the present invention;
fig. 2 is a schematic structural view of a port plate according to an embodiment of the present invention;
fig. 3 is a schematic structural view of a port plate according to an embodiment of the present invention;
fig. 4 is a schematic structural view of a port plate according to an embodiment of the present invention;
fig. 5 is a schematic structural view of a port plate according to an embodiment of the present invention;
fig. 6 is a partial view of a port face of a port plate according to an embodiment of the present invention;
fig. 7 is a partial view of a port face of a port plate according to an embodiment of the present invention;
fig. 8 is a partial view of a port face of a port plate according to an embodiment of the present invention;
fig. 9 is a partial view of a port face of a port plate according to an embodiment of the present invention;
the reference symbols in the drawings denote the following:
1-a valve plate; 10-flow distribution end face; 101-top dead center; 102-bottom dead center; 103-oil discharge high pressure area; 104-oil absorption low pressure zone; 11-low voltage zone kidney slot; 12-high voltage zone kidney slot; 13-a radial oil groove; 14-pits; 15-circumferential oil grooves; 2-cylinder body; 20-a plunger cavity; 21-spindle hole.
Detailed Description
The technical solution of the present invention will be further explained with reference to the accompanying drawings and embodiments.
As shown in fig. 1, the cylinder body 2 is provided with a plunger cavity 20 and a spindle hole 21 extending along the axial direction thereof, and the plunger cavity 20 is driven to rotate along the circumferential direction on the flow distribution end surface 10 of the flow distribution plate 1 by driving the cylinder body 2 to rotate along the spindle hole 21, so as to continuously screw into the oil discharge high pressure region 103 and the oil suction low pressure region 104 to alternately perform the oil suction and discharge processes.
As shown in fig. 2-5, the high-load-bearing low-leakage anti-wear port plate for an axial plunger pump according to the present invention comprises a port end surface 10, wherein the port end surface 10 has a top dead center 101 and a bottom dead center 102, and two sides of a connecting line between the top dead center 101 and the bottom dead center 102 form an oil discharge high pressure region 103 and an oil suction low pressure region 104, respectively.
As shown in fig. 2-5, the radial oil groove 13 is provided near the top dead center 101 and/or near the bottom dead center 102, i.e., in some examples, the radial oil groove 13 is provided only near the top dead center 101; in some examples, the oil groove 13 is provided only near the bottom dead center 102; in some examples, radial oil grooves 13 are provided near both top dead center 101 and bottom dead center 102.
As shown in fig. 2-5, the dimples 14 are provided near the top dead center 101 and/or near the bottom dead center 102, i.e., in some examples, the dimples 14 are provided only near the top dead center 101; in some examples, only the vicinity of the bottom dead center 102 is provided with the pit 14; in some examples, dimples 14 are provided near both the top dead center 101 and the bottom dead center 102.
As shown in fig. 2-5, the oil drain high pressure region 103 and/or the oil suction low pressure region 104 are provided with circumferential oil grooves 15, i.e., in some examples, the circumferential oil grooves 15 are provided only on the oil drain high pressure region 103; in some examples, the circumferential oil groove 15 is provided only on the oil suction low-pressure region 104; in some examples, the oil drain high pressure region 103 and the oil suction low pressure region 104 are each provided with a circumferential oil groove 15.
According to the utility model discloses a high burden low leakage valve plate 1 that wear-resistants for axial plunger pump, through setting up radial oil groove 13, pit 14 and circumference oil groove 15, can strengthen the dynamic pressure effect of the vice clearance oil film of joining in marriage a class, thereby strengthen the bearing capacity of oil film, at radial oil groove 13, pit 14 and circumference oil groove 15 department form the wedge appearance of converging, thereby radial oil groove 13, pit 14 and circumference oil groove 15 department produce additional fluid dynamic pressure, thereby radial oil groove 13, pit 14 and circumference oil groove 15 provide additional bearing capacity for the vice sliding surface of joining in marriage a class.
According to the utility model discloses a high burden low leakage valve plate 1 that wear-resistants for axial plunger pump, through setting up radial oil groove 13, pit 14 and circumference oil groove 15, can strengthen lubricating oil film formation ability, all can store hydraulic oil in radial oil groove 13, pit 14 and the circumference oil groove 15 to can provide the secondary oil source to valve plate 1's valve terminal surface 10, improve valve plate 1's valve terminal surface 10 and form the ability of fluid lubrication membrane.
In the case of abrasive dust or impurities in the hydraulic oil, the radial oil grooves 13, the dimples 14 and the circumferential oil grooves 15 provided on the port end surface 10 of the port plate 1 can accommodate the abrasive dust and impurities, thereby reducing surface wear of the port plate 1.
As shown in fig. 6 to 9, the surface shape of the recess 14 along the port surface 10 may be selected according to needs or processing convenience, and may be, for example, a polygon, a circle or an ellipse, so that the processing difficulty of the port plate 1 may be reduced while ensuring additional hydrodynamic effect and wear resistance of the port surface 10 of the port plate 1. For example, in the example shown in fig. 5, the surface shape profile of the recess 14 along the flow distribution end surface 10 is circular; in the example shown in fig. 6, the contour of the surface shape of the recess 14 along the flow distribution end surface 10 is an isosceles triangle; in the example shown in fig. 7, the surface shape profile of the dimples 14 along the flow distribution end surface 10 is square; in the example shown in fig. 8, the surface shape profile of the dimples 14 along the flow distribution end surface 10 is an ellipse. Of course, the present invention is not limited thereto, and the surface shape profile of the concave pit 14 along the flow distribution end surface 10 may be an irregular polygon or the like.
In the example shown in fig. 2, radial oil grooves 13 and dimples 14 are provided near both the top dead center 101 and the bottom dead center 102, and the plurality of radial oil grooves 13 are arranged in order in the direction of both sides of the line connecting the top dead center 101 and the bottom dead center 102 of the flow distribution end surface 10. The plurality of dimples 14 are divided into a plurality of groups which are sequentially arranged in the circumferential direction along both sides of a line connecting the top dead center 101 and the bottom dead center 102 of the flow distribution end surface 10, and each group includes a plurality of dimples 14 which are sequentially arranged in the radial direction of the flow distribution end surface 10.
In the example shown in fig. 3, the dimples 14 are provided near both the top dead center 101 and the bottom dead center 102, and the plurality of dimples 14 are divided into a plurality of groups arranged in order in the circumferential direction along both sides of a line connecting the top dead center 101 and the bottom dead center 102 of the flow distribution end surface 10, each group including the plurality of dimples 14 arranged in order in the radial direction of the flow distribution end surface 10.
In the example shown in fig. 4, the radial oil grooves 13 are provided near both the top dead center 101 and the bottom dead center 102, and the plurality of radial oil grooves 13 are arranged in order in the direction of both sides of the line connecting the top dead center 101 and the bottom dead center 102 of the flow distribution end surface 10.
In the example shown in fig. 3, the oil suction/low pressure region 104 is provided with radial circumferential oil grooves 15, and the plurality of circumferential oil grooves 15 are divided into a plurality of groups arranged in sequence in the circumferential direction of the flow distribution end surface 10, each group including a plurality of circumferential oil grooves arranged in sequence in the radial direction of the flow distribution end surface 10.
In the example shown in fig. 4, the oil discharge high pressure region 103 is provided with radial circumferential oil grooves 15, and the plurality of circumferential oil grooves 15 are divided into a plurality of groups arranged in order in the circumferential direction of the flow distribution end surface 10, each group including a plurality of circumferential oil grooves arranged in order in the radial direction of the flow distribution end surface 10.
In the example shown in fig. 5, the radial oil grooves 13 and the dimples 14 are provided near both the top dead center 101 and the bottom dead center 102, and the plurality of radial oil grooves 13 are arranged in order in the direction of both sides of the line connecting the top dead center 101 and the bottom dead center 102 of the flow distribution end surface 10. The plurality of dimples 14 are divided into a plurality of groups which are sequentially arranged in the circumferential direction along both sides of a line connecting the top dead center 101 and the bottom dead center 102 of the flow distribution end surface 10, and each group includes a plurality of dimples 14 which are sequentially arranged in the radial direction of the flow distribution end surface 10. The oil discharge high-pressure area 103 and the oil absorption low-pressure area 104 are both provided with radial circumferential oil grooves 15, the plurality of circumferential oil grooves 15 are divided into a plurality of groups which are sequentially arranged along the circumferential direction of the flow distribution end surface 10, and each group comprises a plurality of circumferential oil grooves which are sequentially arranged along the radial direction of the flow distribution end surface 10.
The above description is only the preferred embodiment of the present invention; the scope of the present invention is not limited thereto. Any person skilled in the art should also be able to cover the technical scope of the present invention by replacing or changing the technical solution and the improvement concept of the present invention with equivalents and modifications within the technical scope of the present invention.
Claims (10)
1. A high-load-bearing low-leakage wear-resistant port plate for an axial plunger pump, comprising: the flow distribution end face is matched with a cylinder body of the axial plunger pump;
the flow distribution end face is provided with an upper dead center and a lower dead center, one side of a connecting line between the upper dead center and the lower dead center forms an oil absorption low-pressure area, the other side of the connecting line between the upper dead center and the lower dead center forms an oil discharge high-pressure area, radial oil grooves and/or pits are arranged near the upper dead center position and/or near the lower dead center position, and circumferential oil grooves are arranged in the oil absorption low-pressure area and/or the oil discharge high-pressure area.
2. A high load bearing, low leakage, anti-wear port plate for an axial plunger pump according to claim 1 wherein the projection of said radial oil groove into said port end face is a straight line.
3. A high load bearing, low leakage, wear resistant port plate for an axial plunger pump as described in claim 1 wherein said radial oil groove has a rectangular or semi-circular cross-sectional profile normal to said port end face.
4. A high load bearing, low leakage, wear resistant port plate for an axial piston pump as defined in claim 1 wherein said radial oil grooves are in more than two rows; and more than two rows of radial oil grooves are uniformly or symmetrically arranged along the flow distribution end surface of the flow distribution disc according to an equal circumferential angle.
5. A high load bearing, low leakage, wear resistant port plate for an axial piston pump as described in claim 1 wherein said dimples are circular, elliptical or polygonal in projection into said port face.
6. The high load-bearing low leakage wear-resistant port plate for an axial plunger pump according to claim 1, wherein said dimples are distributed in a radial or circumferential direction of a port end surface of said port plate in two or more numbers; and more than two pits are uniformly or symmetrically arranged along the flow distribution end surface at an equal circumferential angle, or more than two pits are uniformly or symmetrically arranged along the radial direction of the flow distribution end surface of the flow distribution disc at equal intervals.
7. A high load bearing, low leakage, wear resistant port plate for an axial piston pump as described in claim 1 wherein said circumferential oil groove projection into said port face is an arc of a circle.
8. A high load bearing, low leakage, wear resistant port plate for an axial plunger pump as described in claim 1 wherein said circumferential oil groove has a rectangular or semi-circular cross-sectional profile normal to said port end face.
9. The high load bearing, low leakage, wear resistant port plate for an axial plunger pump of claim 1, wherein said circumferential oil grooves are radially distributed in more than two rows along a port end face of said port plate; and more than two rows of circumferential oil grooves are arranged at equal intervals or symmetrically along the radial direction of the flow distribution end surface of the flow distribution disc.
10. Axial piston pump, characterized in that it comprises a port plate according to any one of claims 1-9, the port end face cooperating with the cylinder to form a port pair.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202021580387.XU CN213298190U (en) | 2020-08-03 | 2020-08-03 | High-bearing low-leakage anti-wear valve plate for axial plunger pump and axial plunger pump |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202021580387.XU CN213298190U (en) | 2020-08-03 | 2020-08-03 | High-bearing low-leakage anti-wear valve plate for axial plunger pump and axial plunger pump |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN213298190U true CN213298190U (en) | 2021-05-28 |
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| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN202021580387.XU Active CN213298190U (en) | 2020-08-03 | 2020-08-03 | High-bearing low-leakage anti-wear valve plate for axial plunger pump and axial plunger pump |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN213298190U (en) |
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2020
- 2020-08-03 CN CN202021580387.XU patent/CN213298190U/en active Active
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