Valve plate group and tandem type axial plunger pump

Abstract

The present application provides a valve plate set (100) configured for a tandem axial plunger pump and comprising: a first valve plate (101) adapted to a front pump of the tandem plunger pump; and a second valve plate (102) adapted to a rear pump of the tandem plunger pump; the rear pump is arranged face to face relative to the front pump; wherein the first valve plate (101) is provided with a first oil absorption area (1011), the first oil absorption area (1011) is formed into an arc-shaped through hole, a gradually-changed concave part is formed at the tail part of the first oil absorption area (1011), the second valve plate (102) is provided with a second oil absorption area (1021), and the second oil absorption area (1021) is formed into an arc-shaped through hole and is not provided with a gradually-changed concave part.

Description

Technical Field

[0001] The present application relates to a valve plate assembly, which is used for a series axial piston pump. In addition, the present application also relates to a series axial piston pump. Background Art

[0002] When the axial piston pump is working, the high-pressure fluid is sucked into the plunger on one side of the valve plate, and then the fluid is pushed out of the plunger on the other side of the valve plate, thereby transmitting hydraulic pressure. In the case of long-term use of such an axial piston pump, the side of the valve plate where the fluid is sucked will form a cavity due to the cavitation effect, which will destroy the integrity of the valve plate and reduce its service life. This is undesirable.

[0003] In addition, in some cases, for example, in the case of a tandem piston pump, one side is more difficult to suck hydraulic oil than the other side due to the positioning of the hydraulic oil tank and the layout of the oil pipeline. This situation will further aggravate the cavitation effect and cause a more serious problem of cavitation damage to the valve plate.

[0004] In view of but not limited to the above-mentioned various problems, it is desirable to provide a new type of distribution plate to at least alleviate or even solve the above-mentioned problems. Utility Model Content

[0005] The present application aims to provide a valve plate, which is advantageous in at least one aspect over the prior art.

[0006] To this end, the present application provides, in one aspect, a distribution plate group, which is configured for a tandem axial piston pump and is characterized in that it includes: a first distribution plate, which is adapted to the front pump of the tandem piston pump; and a second distribution plate, which is adapted to the rear pump of the tandem piston pump; the rear pump is arranged face to face with respect to the front pump; wherein the first distribution plate has a first oil suction area, the first oil suction area is formed as an arc-shaped through hole and has a gradual recess formed at its tail, and the second distribution plate has a second oil suction area, the second oil suction area is formed as an arc-shaped through hole and does not have a gradual recess.

[0007] In a possible implementation, the tandem axial piston pump is configured so that the first port plate can more easily obtain the suction of hydraulic fluid than the second port plate.

[0008] In a possible embodiment, the tandem axial piston pump has a front pump and a rear pump, wherein an oil tank for the tandem axial piston pump delivers hydraulic oil to the front pump and the rear pump via a common oil delivery pipeline, and wherein the first distribution plate is adapted to the front pump and the second distribution plate is adapted to the rear pump.

[0009] In a feasible implementation manner, a first oil unloading hole and a first oil unloading channel connecting the first oil unloading hole to the outside of the first distribution plate are provided in the first oil sealing area where the first oil pushing area transitions to the first oil suction area.

[0010] In a possible implementation, the first oil discharge hole is connected to the outside of the first distribution plate via a first oil discharge channel.

[0011] In a possible implementation manner, the first oil unloading hole is connected to the outside of the first distribution plate via a plurality of first oil unloading channels.

[0012] In a feasible embodiment, the second distribution disk also has a second oil pushing area, wherein a second oil unloading hole and a second oil unloading channel connecting the second oil unloading hole to the outside of the second distribution disk are opened in the second oil sealing area where the second oil pushing area transitions to the second oil suction area.

[0013] In a feasible implementation, a groove is provided in the second oil unloading passage adjacent to the second distribution plate and the cylinder body of the tandem axial piston pump to reduce the corrosion of the cylinder body due to the cavitation effect.

[0014] In a feasible embodiment, the second oil unloading hole includes two second oil unloading holes, wherein one second oil unloading hole is connected to the outside of the second distribution disk via a second oil unloading channel, and wherein the other second oil unloading hole is connected to the outside of the second distribution disk via two second oil unloading channels.

[0015] In a possible implementation manner, the gradually changing recessed portion is formed as a double-bag structure, so as to prevent a sudden pressure change caused by hydraulic oil.

[0016] In addition, the present application provides a tandem axial piston pump in another aspect, characterized in that it includes: a distribution plate group for the tandem axial piston pump as described above; and a cylinder body including a front pump and a rear pump, the distribution plate group being adapted to the cylinder body, wherein the front pump and the rear pump share the same oil pipeline.

[0017] As can be seen from the above, the valve plate disclosed in the present application can improve the smoothness of hydraulic oil entering the plunger, reduce the impact of cavitation effect and the generation of cavitation holes. In this way, the service life of the valve plate can be increased, which is more economical. BRIEF DESCRIPTION OF THE DRAWINGS

[0018] Figure 1 A tandem axial piston pump according to one embodiment of the present application is shown.

[0019] Figure 2 A port plate according to one embodiment of the present application is shown.

[0020] Figure 3A port plate according to another embodiment of the present application is shown.

[0021] Figure 4-Figure 9 Several exemplary embodiments of hole enlargement are shown. DETAILED DESCRIPTION

[0022] Some feasible implementations of the present application are described below with reference to the accompanying drawings. It should be noted that the drawings are not drawn to scale. Some details may be enlarged for clear display, and some unnecessary details are omitted.

[0023] like Figure 1 As shown, a tandem axial piston pump 500 according to an embodiment of the present application is shown. The tandem axial piston pump 500 has a front pump 501 and a rear pump 502. The oil tank 600 for the tandem axial piston pump 500 delivers hydraulic oil to the front pump 501 and the rear pump 502 through a common oil pipeline 700, that is, the hydraulic oil used by the front pump 501 and the rear pump 502 comes from the same oil pipeline 700 and shares the oil suction port 701. It can be understood that "front" and "rear" are relative. As used herein, the side farther from the oil tank 600 is called "front", and the side closer to the oil tank 600 is called "rear".

[0024] like Figure 2 As shown in FIG. 1 , a distribution plate group 100 according to an embodiment of the present application is shown. The distribution plate group 100 can be used as follows: Figure 1 The tandem axial piston pump 500 is shown. This distribution plate group 100 includes a first distribution plate (also called the front distribution plate) 101 and a second distribution plate (also called the rear distribution plate) 102 which is symmetrically arranged relative to the first distribution plate. The first distribution plate 101 and the second distribution plate 102 are respectively adapted to two pumps of a tandem piston pump which are connected in series with each other. The first distribution plate 101 can be adapted to the front pump of the tandem piston pump. The second distribution plate 102 can be adapted to the rear pump of the tandem piston pump, wherein the rear pump is arranged face to face with respect to the front pump. The first distribution plate 101 is more likely to obtain the suction of the hydraulic fluid than the second distribution plate 102, that is, the first distribution plate 101 obtains a larger flow rate of the hydraulic fluid per unit time than the second distribution plate 102. For example, because the extension line of the oil delivery pipe at the connection with the axial piston pump is toward the first distribution plate 101 and away from the second distribution plate 102, the high-pressure fluid in the oil delivery pipe is more conveniently sucked into the first distribution plate 101 than the second distribution plate 102 due to inertia.

[0025] The first distributor plate 101 has a first oil suction area 1011 and a first oil pushing area 1012. The first oil suction area 1011 is configured to accommodate (communicate with) an arc-shaped through hole of each plunger (not shown) that is sucking oil. The tail of the first oil suction area 1011 (where the plunger exits the oil suction area) is formed with a gradual concave portion 1013 (for example, formed into a double-bladder structure), and the gradual concave portion 1013 is connected to the arc-shaped through hole. In this way, the sudden pressure change caused by the hydraulic oil can be prevented or at least alleviated, thereby alleviating the corrosion of the distributor plate, especially the arc-shaped through hole.

[0026] A first oil unloading hole 1015 and a first oil unloading channel 1016 connecting the first oil unloading hole 1015 to the outside of the first distribution plate 101 are provided in the first oil sealing area 1014 where the first oil pushing area 1012 transitions to the first oil suction area 1011. In this way, a small portion of the high-pressure fluid can be discharged, thereby reducing a certain pressure before entering the first oil suction area 1011, thereby alleviating the corrosion caused by the cavitation effect. According to actual conditions, the number of the first oil unloading holes 1015 can be any suitable number. For example, as shown in the figure, two first oil unloading holes 1015 are shown. The two oil unloading holes 1015 are positioned along the trace of the rotation of the plunger. The two first oil unloading holes 1015 are arranged in the first oil sealing area 1014 where the first oil pushing area 1012 transitions to the first oil suction area 1011. The first oil unloading hole 1015 can be arranged to be closer to the first oil suction area 1011 relative to the first oil pushing area 1012. A first oil discharge hole 1015 can be connected to the outside of the first distribution plate via a first oil discharge channel 1016. A first oil discharge hole 1015 can also be connected to the outside of the first distribution plate via multiple (for example, Figure 2 The two first oil unloading channels 1016 (shown) are connected to the outside of the first distribution plate.

[0027] The second distributor 102 has a second oil suction area 1021 and a second oil pushing area 1022. The second oil suction area 1021 is configured as an arc-shaped through hole capable of accommodating (communicating) each plunger (not shown) that is sucking oil. Unlike the first distributor 101, the tail of the second oil suction area 1021 (where the plunger exits the corresponding oil suction area) does not have a gradual concave portion, but is formed as a part of the arc-shaped through hole. Through this configuration, it is more convenient to suck the high-pressure liquid in the oil pipeline from the second oil suction area 1021 into the plunger, thereby reducing the generation of cavitation effect and damage to the second distributor 102.

[0028] A second oil sealing area 1024 which transitions from the second oil pushing area 1022 to the second oil suction area 1021 is provided with a second oil unloading hole 1025 and a second oil unloading channel 1026 which connects the second oil unloading hole 1025 to the outside of the second distribution plate 102 .

[0029] The second oil unloading channel 1026 may have a reaming hole (also referred to as an edge notch) 1028 at the edge away from the second oil unloading hole 1025 and close to the second distribution plate 102. In this way, when the high-pressure fluid from the second oil unloading hole 1025 passes through the second oil unloading channel 1026, the pressure can be reduced when flowing through the reaming hole, thereby reducing the impact of cavitation on the second oil unloading channel 1026 and / or the cylinder body close to the second oil unloading channel 1026. According to actual needs, the reaming hole 1028 can be formed into a variety of shapes such as a hemispherical shape, a trumpet shape, a cone shape, etc. In this way, not only can the cavitation impact on the second oil suction area 1021 be reduced, but also the cavitation impact on the second oil unloading channel 1026 and nearby cylinder bodies and other components can be further reduced.

[0030] For example, each second oil discharge hole 1025 has a corresponding expansion hole 1028. For another example, the expansion holes 1028 of each second oil discharge hole 1025 are connected to each other. Such expansion holes 1028 can be configured to be suitable for various variations according to specific circumstances. Figure 4-Figure 9 As shown, several exemplary embodiments of the expansion hole 1028 are shown. Specifically, Figure 4 and Figure 5 An embodiment in which the first distributor plate 101 has a circular arc-shaped expansion hole 1028 is shown; Figure 6 and Figure 7 An embodiment in which the first distributor plate 101 has two arc-shaped expansion holes 1028 is shown; Figure 8 and Fig. 9 An embodiment is shown in which the first distribution plate 101 has one flat-cut reaming hole 1028. It can be understood that the reaming hole 1028 of the second distribution plate 102 corresponding to the first distribution plate 101 has a corresponding structure. It can be understood that in some cases, the first distribution plate 101 can also have the same or similar structure corresponding to the reaming hole 1028.

[0031] According to actual conditions, the number of the second oil unloading holes 1025 can be any suitable number. Figure 3 As shown, a second oil discharge hole 1025 is shown; correspondingly, a first oil discharge hole 1015 is also shown. Figure 2As shown, two second oil unloading holes 1025 are shown. The two second oil unloading holes 1025 are positioned along the trajectory of the plunger rotation. The two second oil unloading holes 1025 are arranged in the second oil sealing area 1024 between the second oil pushing area 1022 and the second oil suction area 1021. The second oil unloading hole 1025 can be arranged closer to the second oil suction area 1021 relative to the second oil pushing area 1022. A second oil unloading hole 1025 can be connected to the outside of the second distribution plate via a second oil unloading channel 1026. A second oil unloading hole 1025 can also be connected to the outside of the second distribution plate 102 via two second oil unloading channels 1026. The number of the expansion holes as described above can correspond to the number of the second oil unloading channels 1026. For example, when there are multiple second oil unloading channels 1026, a expansion hole can be arranged on the outside of each second oil unloading channel 1026 close to the second distribution plate 102. According to actual needs, the shapes of each expansion hole can be configured to be the same or different. Additionally or alternatively, the plurality of expansion holes of the plurality of second oil discharge channels 1026 may be interconnected, for example, by flat-cutting the edge of the second distribution plate 102 with the second oil discharge channels 1026 during the manufacturing process. In this way, the influence of cavitation can be further reduced.

[0032] Additionally or alternatively, a groove may be provided at the cylinder body adjacent to the second oil unloading passage 1026 of the second distributor plate 102 to reduce the adverse effects (corrosion) of cavitation on the cylinder body.

[0033] The diameter of the first unloading hole 1015 and / or the second unloading hole 1025 can be configured to correspond to the working conditions of the tandem axial piston pump. Compared with the general axial piston pump, the tandem axial piston pump has a larger displacement, which may aggravate the adverse effects of cavitation. The diameter (size) of the first unloading hole 1015 and / or the second unloading hole 1025 can at least be enlarged.

[0034] The first oil unloading channel 1016 and / or the second oil unloading channel 1026 can be respectively arranged inside the first distribution disk 101 and / or the second distribution disk 102 (closed channel), or can also be respectively arranged as a through hole design (open channel) with at least a portion of it located on the outside of the corresponding distribution disk (the side facing away from the cylinder body).

[0035] The extension line of the first oil unloading channel 1016 and / or the second oil unloading channel 1026 from the inlet to the outlet can be configured to be respectively away from the first oil suction area 1011 and / or the second oil suction area 1021. For example, the extension line of the first oil unloading channel 1016 from the inlet to the outlet can be configured to be greater than or equal to 1 mm from (the nearest point of) the first oil suction area 1011, and / or the extension line of the second oil unloading channel 1026 from the inlet to the outlet can be configured to be greater than or equal to 1 mm from (the nearest point of) the second oil suction area 1021. In this way, the corrosion of the corresponding oil suction area by the bubbles in the fluid discharged from the first oil unloading channel 1016 and / or the second oil unloading channel 1026 can be reduced.

[0036] Additionally, the head of the first oil suction area 1011 and / or the second oil suction area 1021 (through which the plunger enters the corresponding oil suction area) may be provided with a first extension groove and / or a second extension groove in a direction respectively toward the first oil discharge hole 1015 and / or the second oil discharge hole 1025. In this way, the slope of the pressure drop can be further smoothed and the influence of cavitation can be reduced.

[0037] The present application also relates to a tandem axial piston pump 500. The tandem piston pump comprises the valve plate assembly 100 as described above. The specific contents of the valve plate assembly 100 are described above. The tandem axial piston pump may also comprise a cylinder body having a front pump 501 and a rear pump 502, and the valve plate assembly 100 is adapted to the cylinder body.

[0038] The present application also relates to an axial piston pump. The axial piston pump may include the first valve plate 101 or the second valve plate 102 as described above. The axial piston pump may also include a cylinder body, the first valve plate 101 is adapted to the cylinder body or the second valve plate 102 is adapted to the cylinder body.

[0039] As used herein, the term “comprising” is open ended and includes one or more stated features, elements, components, or functions, but does not preclude the presence or addition of one or more other features, elements, components, functions, or combinations thereof.

[0040] It is expressly intended that within the scope of the present application, the various aspects, embodiments, examples and alternatives listed in the preceding paragraphs, claims and / or in the following description and figures, and in particular the individual features thereof, may be used independently or in any combination. That is, all embodiments and / or features of any embodiment may be used in any manner and / or combination unless such features are incompatible. Applicants reserve the right to change any originally filed claims or to file any new claims accordingly, including amending any originally filed claim to be subordinate to and / or incorporate any features of any other claim, even though not originally claimed in this manner.

[0041] Although the present application is described herein with reference to specific embodiments, the scope of the present application is not limited to the details shown. Various modifications may be made to these details without departing from the basic principles of the present application.

Claims

1. A valve plate assembly (100) configured for use in a tandem axial piston pump and characterized in that include: A first valve plate (101), which is adapted to the front pump of the tandem piston pump; and A second port plate (102) adapted for a rear pump of a series piston pump; the rear pump is arranged face to face with respect to the front pump; The first distribution plate (101) has a first oil suction area (1011), which is formed as an arc-shaped through hole and has a gradual recess at its tail, and the second distribution plate (102) has a second oil suction area (1021), which is formed as an arc-shaped through hole and does not have a gradual recess.

2. The valve plate assembly (100) according to claim 1, characterized in that: The serial axial piston pump is configured so that the first valve plate (101) can more easily obtain the suction of hydraulic fluid than the second valve plate (102).

3. The valve plate assembly (100) according to claim 1, characterized in that: The tandem axial piston pump (500) comprises a front pump (501) and a rear pump (502), wherein an oil tank (600) for the tandem axial piston pump (500) delivers hydraulic oil to the front pump (501) and the rear pump (502) via a common oil delivery pipeline (700), and wherein the first valve plate (101) is adapted to the front pump (501), and the second valve plate (102) is adapted to the rear pump (502).

4. The distributor plate assembly (100) according to any one of claims 1 to 3, characterized in that: A first oil unloading hole (1015) and a first oil unloading channel (1016) connecting the first oil unloading hole (1015) to the outside of the first distribution plate (101) are provided in the first oil sealing area (1014) transitioning from the first oil pushing area (1012) to the first oil suction area (1011).

5. The valve plate assembly (100) according to claim 4, characterized in that: The first oil discharge hole is connected to the outside of the first distribution plate (101) via a first oil discharge channel (1016).

6. The valve plate assembly (100) according to claim 4, characterized in that: The first oil discharge hole is connected to the outside of the first distribution plate (101) via a plurality of first oil discharge channels (1016).

7. The distributor plate assembly (100) according to claim 4, characterized in that: The second distribution plate (102) also has a second oil pushing area (1022), wherein a second oil sealing area (1024) transitioning from the second oil pushing area (1022) to the second oil suction area (1021) is provided with a second oil unloading hole (1025) and a second oil unloading channel (1026) connecting the second oil unloading hole (1025) to the outside of the second distribution plate (102).

8. The distributor plate assembly (100) according to claim 7, characterized in that: A groove is provided on the cylinder body of the second oil unloading passage (1026) adjacent to the second distribution plate (102) and the tandem axial piston pump to reduce the corrosion of the cylinder body caused by the cavitation effect.

9. The distributor plate assembly (100) according to claim 7, characterized in that: The second oil unloading hole (1025) includes two second oil unloading holes (1025), wherein one second oil unloading hole (1025) is connected to the outside of the second distribution plate via a second oil unloading channel (1026), and wherein the other second oil unloading hole (1025) is connected to the outside of the second distribution plate (102) via two second oil unloading channels (1026).

10. The valve plate assembly (100) according to any one of claims 1 to 3, characterized in that: The gradually changing recess (1013) is formed into a double-bag structure, so as to prevent sudden pressure changes caused by hydraulic oil.

11. A series axial piston pump (500), characterized in that include: The distributor plate assembly (100) according to any one of claims 1 to 10; and A cylinder body comprising a front pump (501) and a rear pump (502), wherein the valve plate assembly (100) is adapted to the cylinder body, wherein the front pump (501) and the rear pump (502) share the same oil delivery pipeline.

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