A plunger pump distribution end cover and plunger pump

Abstract

The application discloses a plunger pump flow distribution end cover and a plunger pump. The flow distribution end cover comprises an oil suction flow channel and an oil discharge flow channel. The oil suction flow channel and / or the oil discharge flow channel is provided with a plurality of sound attenuation grooves in the fluid flow direction. The sound attenuation groove comprises a flow guide part and a torsion part. The flow guide part is used for guiding the fluid in the flow channel to the torsion part. The torsion part is used for twisting the flow direction of the fluid, so that the fluid flowing out of the sound attenuation groove collides with the fluid in the flow channel. The application twists the flow direction of the fluid through the sound attenuation groove, so that the fluid flowing out of the sound attenuation groove collides with the fluid in the flow channel. Energy is consumed in the fluid collision process, so that the intensity of flow pulsation and pressure impact is reduced, thereby significantly reducing flow noise. The application not only has a simple structure and is easy to implement, but also helps to reduce production cost and reduce the weight of the plunger pump flow distribution end cover.

Description

Technical Field

[0001] This invention relates to a plunger pump distribution end cover and a plunger pump, belonging to the field of plunger pump technology. Background Technology

[0002] The noise of a plunger pump is divided into structural noise and fluid noise, which are closely related and mutually influential. Structural noise primarily arises from the pressure surges caused by the switching between high and low pressure during the oil suction and discharge processes. These pressure surges drive vibrations in the pump components, which is the vibration source of the structural noise. Fluid noise mainly stems from the limited number of plungers (usually 7 or 9) in the pump's structure. During operation, significant flow pulsations occur, accompanied by pressure surges at the same period frequency, which is also the vibration source of the fluid noise. Both structural and fluid noise are transmitted through the internal components to the pump housing and end caps, ultimately radiating into the surrounding environment as noise pollution.

[0003] To address the vibration and noise reduction issues of plunger pumps, existing technologies primarily focus on two aspects: blocking vibration transmission paths and reducing the amplitude of vibration sources. Blocking vibration transmission paths involves increasing the attenuation rate of the vibration source, mainly through structural optimization of the pump housing, thereby reducing the noise amplitude transmitted to the environment. For example, this involves adding silencing seats and holes to the rear pump housing. However, this approach does not eliminate noise at its source and increases the weight of the housing, thus reducing the power density of the plunger pump. Reducing the amplitude of vibration sources involves lowering the amplitude of flow pulsation and pressure shock at the source. Existing plunger pump solutions mainly focus on structural optimization of the suction and discharge transition zone of the distribution mechanism to reduce pressure shock and thus reduce structural noise. For example, this involves adding triangular grooves and throttling orifices to the suction and discharge transition zone of the distribution plate. However, this approach is difficult to design and match, struggles to dynamically reduce pressure shock in real time, has limited noise reduction effects, and is structurally complex and costly to manufacture. Another example is adding a pre-compression cavity to the end cap, but this also has a complex structure, numerous components, and limited noise reduction.

[0004] At the hydraulic system level, when the main unit uses a piston pump, most existing technologies will arrange a vibration-absorbing blind pipe or accumulator at the piston pump outlet to reduce the vibration and noise of the main unit's hydraulic system. However, this solution requires multiple comparative tests to obtain the optimal blind pipe length, which increases the cost of the main unit's hydraulic system.

[0005] The information disclosed in this background section is intended only to enhance the understanding of the overall background of the invention and should not be construed as an admission or in any way implying that the information constitutes prior art known to those skilled in the art. Summary of the Invention

[0006] The purpose of this invention is to overcome the shortcomings of the prior art and provide a plunger pump distribution end cover and plunger pump, which can significantly reduce the intensity of flow pulsation and pressure shock of the plunger pump, thereby reducing the vibration and noise of the plunger pump. It has the advantages of simple structure, light weight and low cost.

[0007] To achieve the above objectives, the present invention is implemented using the following technical solution:

[0008] In a first aspect, the present invention provides a plunger pump distribution end cover, including an oil suction channel and an oil discharge channel, wherein the oil suction channel and / or the oil discharge channel are provided with a plurality of noise-absorbing grooves distributed along the fluid flow direction;

[0009] The noise-reducing groove includes a flow guide and a torsion section;

[0010] The flow guide is used to guide the fluid in the flow channel to the twisting part;

[0011] The torsion section is used to reverse the flow direction of the fluid so that the fluid flowing out of the silencing groove and the fluid in the flow channel collide.

[0012] In conjunction with the first aspect, furthermore, the silencing grooves on the same circumferential distribution line of the oil suction channel and / or the oil discharge channel form a closed ring structure.

[0013] In conjunction with the first aspect, furthermore, the silencing grooves on the same circumferential distribution line of the oil suction channel and / or the oil discharge channel are discontinuously distributed, and the silencing grooves on adjacent circumferential distribution lines are staggered.

[0014] In conjunction with the first aspect, further, the flow guide includes an arc transition section and a conical section, the conical section gradually moving away from the center of the flow channel along the fluid flow direction; the torsion section includes a raised arc section; the arc transition section, the conical section, and the raised arc section are connected sequentially, and the conical section is tangent to the arc transition section and the raised arc section respectively; the arc transition section is connected to and tangent to the inner wall of the flow channel.

[0015] In conjunction with the first aspect, further, the outline of the arc transition section is a circular arc with a radius of 3 to 5 mm;

[0016] The outline of the conical section is a straight line, and the angle between the straight line and the fluid flow direction is 15° to 45°.

[0017] The outline of the raised arc segment is a semi-circular arc with a radius of 3 to 10 mm and a distance of 2 to 6 mm from the center of the semi-circular arc to the inner wall of the flow channel.

[0018] In conjunction with the first aspect, the raised arc segment is further connected to the inner wall of the flow channel by a transition round chamfer.

[0019] In conjunction with the first aspect, furthermore, the radius of the transition circle chamfer is 0.2 to 0.5 mm.

[0020] In conjunction with the first aspect, furthermore, except for the silencing groove, the cross-sectional areas of the oil suction channel and the oil discharge channel are the same everywhere.

[0021] In conjunction with the first aspect, further, along the fluid flow direction, the flow distance of the fluid from the oil discharge inlet to the first silencer groove in the oil discharge channel, and the distance the fluid flows through adjacent silencer grooves, satisfy the following relationship:

[0022]

[0023] Where: k is a positive integer, V0 is the displacement of the plunger pump, Z is the number of plungers in the plunger pump, and S1 is the cross-sectional area of ​​the oil discharge channel excluding the silencer groove.

[0024] Along the fluid flow direction, the fluid flow distance from the oil inlet to the first silencer groove in the oil suction channel, and the distance between adjacent silencer grooves, satisfy the following relationship:

[0025]

[0026] Where: p is a positive integer, Q2 is the oil suction flow rate of the plunger pump, f2 is the pulsation frequency of the oil suction flow rate of the plunger pump, and S2 is the cross-sectional area of ​​the oil suction channel excluding the silencing groove.

[0027] In a second aspect, the present invention provides a plunger pump, including the plunger pump distribution end cap as described in any of the preceding claims.

[0028] Compared with the prior art, the beneficial effects achieved by the present invention are as follows:

[0029] The oil suction channel and / or the oil discharge channel are provided with several silencing grooves along the fluid flow direction. The silencing grooves include a torsion section to torsion the fluid flow direction so that the fluid flowing out of the silencing grooves and the fluid in the channel collide. Energy is consumed during the fluid collision process, which reduces the intensity of flow pulsation and pressure shock. When the fluid passes through multiple silencing grooves in sequence, the intensity of flow pulsation and pressure shock will be reduced step by step, and the corresponding flow noise will also be reduced. The silencing grooves are not only simple in structure and easy to implement, which helps to reduce production costs, but also reduce the weight of the plunger pump distribution end cover. Attached Figure Description

[0030] Figure 1 This is a schematic diagram of the structure of a plunger pump distribution end cover provided in Embodiment 1 of the present invention;

[0031] Figure 2 yes Figure 1A three-dimensional structural diagram of the central oil drain channel;

[0032] Figure 3 yes Figure 2 A three-dimensional structural diagram of the middle drain channel from another perspective;

[0033] Figure 4 yes Figure 1 A three-dimensional structural diagram of the central oil suction channel;

[0034] Figure 5 yes Figure 4 A three-dimensional structural diagram of the central oil suction channel from another perspective;

[0035] Figure 6 yes Figure 1 A three-dimensional structural schematic diagram of a sound-absorbing groove;

[0036] Figure 7 yes Figure 6 A three-dimensional structural diagram of the central silencing groove from another perspective;

[0037] Figure 8 yes Figure 6 Cross-sectional view of the sound-absorbing groove;

[0038] Figure 9 yes Figure 6 The diagram shows the fluid flow in the silencing groove.

[0039] Figure 10 Is adopted Figure 1 The diagram shows the flow pulsation and pressure shock curves of the plunger pump obtained from the plunger pump distribution end cap test.

[0040] Figure 11 This is a three-dimensional structural schematic diagram of the sound-absorbing groove provided in Embodiment 2 of the present invention;

[0041] Figure 12 yes Figure 11 A schematic diagram of the structure after unfolding along a certain longitudinal distribution line of the flow channel.

[0042] In the diagram: 1. Distribution end cap; 1-1. Oil drain channel; 1-1b. Oil drain inlet; 1-1c. Oil drain outlet; an. Oil drain silencer groove; dj. Oil suction silencer groove; 1-2. Oil suction channel; 1-2b. Oil suction inlet; 1-2c. Oil suction outlet; A02. Arc transition section; A01. Conical section; A03. Raised arc section; l1. Circumferential distribution line; l2. Longitudinal distribution line. Detailed Implementation

[0043] The present invention will be further described below with reference to the accompanying drawings. The following embodiments are only used to more clearly illustrate the technical solution of the present invention, and should not be used to limit the scope of protection of the present invention.

[0044] Example 1:

[0045] like Figure 1 As shown, this is a plunger pump distribution end cover provided in an embodiment of the present invention. The distribution end cover 1 has an oil discharge channel 1-1 and an oil suction channel 1-2. Both the oil discharge channel 1-1 and the oil suction channel 1-2 are hollow structures and can be integrally cast by casting. The oil discharge channel 1-1 and the oil suction channel 1-2 are distributed on both sides of the distribution end cover 1. The oil discharge channel 1-1 is provided with an oil discharge inlet 1-1b, an oil discharge outlet 1-1c, and several oil discharge silencer grooves an; the oil suction channel 1-2 is provided with an oil suction inlet 1-2b, an oil suction outlet 1-2c, and several oil suction silencer grooves dj.

[0046] In this embodiment of the invention, the oil discharge silencing groove AN and the oil suction silencing groove DD have the same structure, both including a flow guide and a torsion section. The flow guide is used to guide the fluid in the flow channel to the torsion section; the torsion section is used to torsion the flow direction of the fluid so that the fluid flowing out of the silencing groove and the fluid in the flow channel collide. For details, please refer to... Figure 9 Energy is consumed during fluid counterflow, which reduces the intensity of flow pulsation and pressure shock. As the fluid passes through multiple silencers in sequence, the intensity of flow pulsation and pressure shock will be reduced step by step, and the corresponding flow noise will also be reduced.

[0047] In one embodiment of the present invention, both the oil drain inlet 1-1b and the oil suction outlet 1-2b are oblong in shape and are distributed on the same plane of the distribution end cover 1. It should be noted that the oil drain outlet 1-1c and the oil suction inlet 1-2c can also be elliptical, circular, or other shapes, and do not necessarily have to be located on the same plane of the distribution end cover 1. The shape and distribution position of the oil drain outlet 1-1c and the oil suction inlet 1-2c can be selected according to actual needs.

[0048] like Figure 2 , Figure 3 The diagram shows a schematic of the oil discharge channel in an embodiment of the present invention. The arrows in the diagram indicate the direction of high-pressure fluid flow. The oil discharge channel 1-1 provides a high-pressure fluid outlet channel for the plunger pump. The high-pressure fluid enters from the oil discharge inlet 1-1b, flows through the oil discharge channel 1-1 and the oil discharge silencer groove an, and through several sequentially arranged oil discharge silencer grooves an, the flow pulsation and pressure impact of the high-pressure fluid are gradually reduced. Finally, it flows out from the oil discharge outlet 1-1c and enters the main hydraulic system. As shown in the attached diagram, in this embodiment of the present invention, each oil discharge silencer groove an is arranged sequentially at intervals along the longitudinal distribution line of the oil discharge channel 1-1, and the oil discharge silencer grooves an extend along the circumferential distribution line of the oil discharge channel 1-1 to form a closed ring structure.

[0049] like Figure 4 , Figure 5The diagram shows a schematic of the oil suction channel in an embodiment of the present invention. The arrows in the diagram indicate the direction of low-pressure fluid flow. The oil suction channel 1-2 provides a low-pressure fluid source for the plunger pump. The low-pressure fluid enters from the oil suction inlet 1-2b, flows through the oil suction channel 1-2 and the oil suction silencer grooves dj, and after passing through several sequentially arranged oil suction silencer grooves dj, the flow pulsation and pressure impact of the low-pressure fluid are gradually reduced, and it flows out from the oil suction outlet 1-2c into the oil suction plunger cavity of the plunger pump. As can be seen from the attached diagram, in this embodiment of the present invention, the arrangement and structure of the oil suction silencer grooves dj are the same as those of the oil discharge silencer groove an. Each oil suction silencer groove dj is arranged sequentially and at intervals along the longitudinal direction of the oil suction channel 1-2, and the oil suction silencer grooves dj extend circumferentially along the oil suction channel 1-2 to form a closed ring structure.

[0050] It should be noted that in the figure, a-1, a-2, a-3, a-4, ..., an and d-1, d-2, d-3, d-4, ..., dj are only used to indicate the serial number of the silencing groove. The silencing groove closest to the inlet is numbered 1, and the grooves are numbered sequentially from 1 along the direction of fluid flow.

[0051] For ease of description, the oil drain muffler an and the oil suction muffler dj will be collectively referred to as mufflers below. In the embodiments of the present invention, the oil drain muffler an and the oil suction muffler dj have the same structure and shape. Figures 6-8 The specific structure of the noise reduction groove is shown:

[0052] The flow guide section includes an arc-shaped transition section A02 and a conical section A01. The starting end of the arc-shaped transition section A02 connects to the flow channel and is tangent to the inner wall of the flow channel. The ending end of the arc-shaped transition section A02 connects to the conical section A01 and is tangent to the conical section A01. The conical section A01 gradually moves away from the center of the flow channel along the fluid flow direction, meaning the flow guide section as a whole presents a trumpet-shaped structure. The torsion section includes a raised arc section A03. The starting end of the raised arc section A03 connects to the ending end of the conical section A01 and is tangent to the ending end of the conical section A01. The ending end of the raised arc section A03 connects to the inner wall of the flow channel.

[0053] The sequential and tangential arrangement of the arc transition section A02, the conical section A01, and the raised arc section A03 ensures smoother fluid flow through the silencing groove. Furthermore, the raised arc section A03 can be seamlessly integrated with the interior of the flow channel via a rounded transition corner.

[0054] See Figure 9 To more clearly demonstrate the flow effect of the fluid in the flow channel, Figure 9 The structure of the silencing groove is magnified, showing a schematic diagram of fluid flow within the flow channel. The arrows in the diagram indicate the direction of fluid flow. As can be seen from the attached diagram:

[0055] When pulsating fluid flows through a silencing groove, the fluid close to the inner wall of the flow channel flows along the structural contours of the groove's arc transition section A02, conical section A01, and convex arc section A03. The flow direction is forcibly twisted, creating a lateral or relative collision with the pulsating fluid subsequently entering the silencing groove. During this collision, fluid energy is slightly consumed, reducing the intensity of flow pulsation and pressure shock, thus lowering the flow noise amplitude. When multiple silencing grooves are installed, the intensity of flow pulsation and pressure shock will be gradually reduced until it almost disappears, significantly reducing the fluid noise of the plunger pump.

[0056] As an optional embodiment of the present invention, the outline of the arc transition section A02 is an arc with a radius R1 of 3 to 5 mm; the outline of the conical section A01 is a straight line with an angle β of 15 to 45° between the straight line and the fluid flow direction; the outline of the raised arc section A03 is a semi-circular arc with a radius r of 3 to 10 mm, the distance h from the center of the semi-circular arc of the raised arc section A03 to the flow channel boundary is 2 to 6 mm, and the radius R2 of the transition fillet is 0.2 to 0.5 mm.

[0057] It should be understood that the attached drawings only show some optional shapes of the muffler groove. In the actual manufacturing process, the shape of the muffler groove can be the same as the closed ring shape formed by the outer edge of the cross section where the muffler groove is located on the oil drain channel 1-1 and the oil suction channel 1-2. It can be a circular ring, an elliptical ring or any other possible closed ring.

[0058] To ensure stable fluid flow rate, the cross-sectional area of ​​the oil discharge channel 1-1 is the same everywhere except for the oil discharge silencer groove, which is S1; the cross-sectional area of ​​the oil suction channel 1-2 is the same everywhere except for the oil suction silencer groove, which is S2.

[0059] To ensure that the reduction time and location are the same within the pulsation period T when the pulsating fluid flows through each silencer groove, and ultimately to ensure that the intensity of flow pulsation and pressure shock is smoothly reduced, the distance of the fluid flowing through adjacent silencer grooves (see attached diagram) is... Figure 2 L in m-n , attached Figure 4 L in i-j ), the flow distance of the fluid from the oil inlet to the first silencer groove (attached) Figure 2 L in 1b-1 , attached Figure 4 L in 2b-1 The following mathematical relationship must be satisfied with the technical parameters of the plunger pump.

[0060] For the oil drain channel:

[0061] The flow rate Q1 of the high-pressure fluid is

[0062] Q1=V0·ω (1-1)

[0063] The flow velocity v1 of the high-pressure fluid is

[0064] v1 = Q1 / S1 (1-2)

[0065] The pulsation frequency f1 of the high-pressure fluid is

[0066] f1 = 2π / 60·Z·ω (1-3)

[0067] The pulsation period T1 of the high-pressure fluid is

[0068] T1 = 1 / f1 (1-4)

[0069] The theoretical minimum spacing L of the oil drain muffler groove min1 for

[0070] L min1 =v1·T1 (1-5)

[0071] In equations (1-1), (1-2), (1-3), (1-4), and (1-5), V0 represents the displacement of the plunger pump; ω represents the rotational speed of the plunger pump; S1 represents the cross-sectional area of ​​the oil discharge channel 1-1 excluding the oil discharge muffler groove; and Z represents the number of plungers in the plunger pump, which is usually 7 or 9.

[0072] According to equations (1-1), (1-2), (1-3), (1-4), and (1-5), the distance between adjacent oil discharge silencers is L. m-n for

[0073]

[0074] In equation (1-6), k is a positive integer, k = 1, 2, 3...

[0075] According to equations (1-1), (1-2), (1-3), (1-4), and (1-5), the flow distance L of the fluid from the oil discharge inlet 1-1b to the first oil discharge silencer a-1 is... 1b-1 for

[0076]

[0077] In equation (1-7), x is a positive integer; x = 1, 2, 3, ..., x and k can take the same value or different values.

[0078] For oil suction channels:

[0079] The flow velocity v2 of the low-pressure fluid is

[0080] v2=Q2 / S2 (1-8)

[0081] The pulsation period T2 of the low-pressure fluid is

[0082] T2 = 1 / f2 (1-9)

[0083] The theoretical minimum spacing L of the oil absorption and noise reduction groove min2 for

[0084] L min2 =v2·T2 (1-10)

[0085] In equations (1-8), (1-9), and (1-10), Q2 represents the oil suction flow rate of the plunger pump; S2 represents the cross-sectional area of ​​the remaining part of the oil suction channel 1-2 except for the oil suction silencer groove; and f2 represents the pulsation frequency of the oil suction flow rate of the plunger pump, such as the flow pulsation frequency of the oil suction port booster centrifugal pump.

[0086] According to equations (1-8), (1-9), and (1-10), the distance L between adjacent oil suction and silencing grooves is... i-j for

[0087]

[0088] In equation (1-11), p is a positive integer, p = 1, 2, 3, ...

[0089] According to equations (1-8), (1-9), and (1-10), the flow distance L of the fluid from the oil suction inlet 1-2b to the first oil suction silencer d-1 is... 2b-1 for

[0090]

[0091] In equation (1-12), y is a positive integer, y = 1, 2, 3, ...

[0092] As attached Figure 10 As shown, it is using Figure 1 The diagram shows the flow pulsation and pressure impact curves of the plunger pump obtained from the plunger pump distribution end cover test. The simulation conditions are: a 9-plunger plunger pump with a displacement of 280cc / r, 46# anti-wear hydraulic oil, pump speed of 1900rpm, flow rate of 532L / min, normal pressure of 350bar, and suction channels 1-2: except for the suction silencer groove, the cross-sectional area S2 of the rest is 2000mm. 2 Oil drain channel 1-1: Except for the oil drain silencer groove, the cross-sectional area S1 of the rest is 804mm². 2 ; Silencing groove: The radius of the arc of the arc transition section A02 is 5mm; the angle β between the contour of the conical section A01 and the fluid flow direction is 40°; the radius of the arc of the raised arc section A03 is 3mm, the distance h from the center of the arc to the flow channel boundary is 2mm, and the radius R2 of the transition fillet is 0.5mm. According to Figure 10It can be seen that after the pulsating fluid in the suction channel 1-2 or the discharge channel 1-1 passes through the first silencer groove, the intensity of the flow pulsation and pressure shock is reduced for the first time. After passing through the second silencer groove, the intensity is reduced again... and so on. After passing through several silencer grooves, the flow pulsation and pressure shock almost disappear after the fluid reaches the oil outlet, and finally the fluid noise of the plunger pump is significantly reduced.

[0093] Example 2:

[0094] Reference Figure 11 , 12 This illustration shows a noise reduction groove provided by an embodiment of the present invention. The difference from Embodiment 1 is that, in this embodiment of the present invention, the noise reduction grooves on the same circumferential distribution line of the flow channel are discontinuously distributed, and the noise reduction grooves on adjacent circumferential distribution lines are staggered.

[0095] See Figure 12 The silencing grooves are distributed along the direction of fluid flow to form longitudinal distribution lines and distributed circumferentially along the flow channel to form circumferential distribution lines. The number of longitudinal and circumferential distribution lines is not less than 3. The silencing grooves are distributed at the intersection of the odd-numbered longitudinal distribution lines and the odd-numbered circumferential distribution lines, and at the intersection of the even-numbered longitudinal distribution lines and the even-numbered circumferential distribution lines.

[0096] The silencing groove provided in this embodiment of the invention can also reduce the fluid noise of the plunger pump.

[0097] It should be noted that for the oil suction channel and the oil discharge channel, both can adopt the silencing groove structure shown in Example 1, or both can adopt the silencing groove structure shown in Example 2, or one channel can adopt the silencing groove structure shown in Example 1, and the other channel can adopt the silencing groove structure shown in Example 2.

[0098] Example 3:

[0099] This invention provides a plunger pump, which can employ a distribution end cap as shown in Embodiment 1 or Embodiment 2. Therefore, the plunger pump provided by this invention achieves the technical effects described in Embodiment 1 or Embodiment 2, which will not be elaborated further here.

[0100] The above description is only a preferred embodiment of the present invention. It should be noted that for those skilled in the art, several improvements and modifications can be made without departing from the technical principles of the present invention, and these improvements and modifications should also be considered within the scope of protection of the present invention.

Claims

1. A piston pump porting head comprising a suction flow passage and a discharge flow passage, characterized by, The oil suction channel and / or the oil discharge channel are provided with several noise reduction grooves along the fluid flow direction. The noise-reducing groove includes a flow guide and a torsion section; The flow guide is used to guide the fluid in the flow channel to the twisting part; The torsion section is used to reverse the flow direction of the fluid so that the fluid flowing out of the silencing groove and the fluid in the flow channel collide. The flow guide section includes an arc transition section and a conical section, the conical section gradually moving away from the center of the flow channel along the fluid flow direction; the torsion section includes a raised arc section; the arc transition section, the conical section, and the raised arc section are connected in sequence, and the conical section is tangent to the arc transition section and the raised arc section respectively; the arc transition section is connected to and tangent to the inner wall of the flow channel.

2. The plunger pump distribution end cover according to claim 1, characterized in that, The silencing grooves on the same circumferential distribution line of the oil suction channel and / or the oil discharge channel form a closed ring structure.

3. The gerotor pump port plate of claim 1, wherein, The silencing grooves on the same circumferential distribution line of the oil suction channel and / or the oil discharge channel are discontinuously distributed, and the silencing grooves on adjacent circumferential distribution lines are staggered.

4. The gerotor pump port plate of claim 1, wherein, The outline of the arc transition section is a circular arc with a radius of 3-5 mm. The outline of the conical section is a straight line, and the angle between the straight line and the fluid flow direction is 15° to 45°. The outline of the raised arc segment is a semi-circular arc with a radius of 3 to 10 mm and a distance of 2 to 6 mm from the center of the semi-circular arc to the inner wall of the flow channel.

5. The gerotor pump port plate of claim 1, wherein, The raised arc segment is connected to the inner wall of the flow channel by a transition round chamfer.

6. The gerotor pump port plate of claim 5, wherein, The radius of the transition chamfer is 0.2 to 0.5 mm.

7. The gerotor pump flow divider cover of claim 1, wherein, Except for the silencing groove, the cross-sectional area of ​​the oil suction channel and the oil discharge channel is the same everywhere.

8. The gerotor pump flow divider cover of claim 1, wherein, Along the fluid flow direction, the fluid flow distance from the oil inlet to the first silencer groove and the distance between adjacent silencers in the oil discharge channel satisfy the following relationship: ； Where: k is a positive integer, V0 is the displacement of the plunger pump, Z is the number of plungers in the plunger pump, and S1 is the cross-sectional area of ​​the oil discharge channel excluding the silencer groove. Along the fluid flow direction, the fluid flow distance from the oil inlet to the first silencer groove in the oil suction channel, and the distance between adjacent silencer grooves, satisfy the following relationship: ； Where: p is a positive integer, Q2 is the oil suction flow rate of the plunger pump, f2 is the pulsation frequency of the oil suction flow rate of the plunger pump, and S2 is the cross-sectional area of ​​the oil suction channel excluding the silencing groove.

9. A piston pump characterized in that Includes the plunger pump distribution end cap as described in any one of claims 1 to 8.

Images