High-pressure distribution disc three-joint groove anti-cavitation structure

Abstract

The present application relates to the technical field of flow distribution disc, and particularly relates to a high-pressure flow distribution disc three-section flow groove anti-cavitation structure, which comprises a flow distribution disc, the flow distribution disc comprises two centrally-symmetrically arranged large waist-shaped grooves, small waist-shaped grooves are symmetrically arranged on the two sides of the large waist-shaped grooves, the small waist-shaped grooves are arranged through the flow distribution disc, three-section flow grooves and a second single-section flow groove are respectively arranged at the two ends of the large waist-shaped grooves, and the two three-section flow grooves are centrally symmetrically arranged; the three-section flow groove comprises three triangular grooves which are completely identical in structure, the three triangular grooves are arranged at equal intervals, and one end of a same circular-arc groove is communicated with the end portions of the three triangular grooves, and the other end of the circular-arc groove is communicated with the large waist-shaped groove. The present application can increase the flow area, reduce the jet velocity, weaken the influence of wall shear force, thereby inhibit vortex production, further inhibit cavitation phenomenon of the flow distribution disc of the axial plunger pump under high-pressure working condition, reduce flow pressure pulsation and cavitation, and improve the efficiency and service life of the axial plunger pump.

Description

A three-channel anti-cavitation structure for a high-pressure distribution plate Technical Field

[0001] This invention relates to the field of distribution plate technology, and in particular to a three-channel anti-cavitation structure for a high-pressure distribution plate. Background Technology

[0002] Axial piston pumps achieve oil suction and discharge by periodically changing the volume of the piston chamber. They mainly consist of a cylinder block, distributor plate, piston, slipper, and swashplate. The swashplate has an inclined angle, and the piston engages with the swashplate via the slipper. The drive shaft rotates the cylinder block, which in turn rotates the piston. Due to the action of the swashplate, the piston reciprocates within the piston chamber during rotation, changing its volume and achieving oil suction and discharge. To coordinate the suction and discharge with the reciprocating motion of the piston, a distributor plate is installed on the end face of the cylinder block. To avoid pressure shocks in the suction and discharge transition region, a throttling groove is often installed for pre-pressurization or pre-unloading. When the piston chamber transitions from the suction zone to the discharge zone, the high-pressure oil in the discharge zone flows into the piston chamber and then through the piston chamber to the throttling groove in the suction zone. Because the flow area of ​​the throttling groove is small, the fluid velocity increases dramatically, leading to a local pressure drop and thus cavitation. Existing distribution plates have a single-slot structure with a small flow area, making them prone to generating high-speed jets. Simultaneously, under the influence of wall shear forces, vortices are easily formed. High-speed jets and vortices cause local pressures in the hydraulic oil to fall below the saturated vapor pressure, resulting in cavitation. When cavitation bubbles collapse, they cause pressure and flow pulsations and cavitation, affecting pump efficiency and lifespan. Therefore, a three-slot anti-cavitation structure for high-pressure distribution plates is urgently needed to address this issue. Summary of the Invention

[0003] The purpose of this invention is to provide a three-channel anti-cavitation structure for a high-pressure distribution plate to solve the above-mentioned problems, thereby suppressing cavitation in the distribution plate of an axial piston pump under high-pressure conditions, reducing flow and pressure pulsation and cavitation, and improving the efficiency and lifespan of the axial piston pump.

[0004] To achieve the above objectives, the present invention provides the following solution:

[0005] A high-pressure distribution plate with a three-slot anti-cavitation structure includes a distribution plate, the distribution plate including two large waist-shaped slots arranged symmetrically at the center, small waist-shaped slots symmetrically opened on both sides of the large waist-shaped slots, the small waist-shaped slots penetrating the distribution plate, and the two ends of the large waist-shaped slots respectively connected to a three-slot and a second single-slot, the two three-slots being arranged symmetrically at the center;

[0006] The three throttling channels include three triangular channels with identical structures, which are arranged at equal intervals. The ends of the three triangular channels are connected to one end of the same arc groove, and the other end of the arc groove is connected to the large waist-shaped channel.

[0007] Preferably, the interval between two adjacent triangular grooves is 3mm.

[0008] Preferably, the length of the triangular groove is 12mm and the width of the triangular groove is 2.5mm.

[0009] Preferably, the radius of the arc groove is 7mm and the depth of the arc groove is 1.2mm.

[0010] Preferably, the triangular groove has a straight section at one end near the arc groove, and a closed section at the other end away from the arc groove, with the straight section and the closed section transitioning smoothly.

[0011] Preferably, the straight section of the triangular groove has a length of 3.2 mm.

[0012] Preferably, both sides of the closed section of the triangular groove are arc-shaped structures, the radius of the arc-shaped structure of the triangular groove is 21.9 mm, and the side walls of the arc-shaped structure of the triangular groove intersect on the central axis of the triangular groove.

[0013] The present invention has the following technical effects: In use, the three triangular grooves arranged at equal intervals on the three throttling grooves increase the flow area and reduce the jet velocity. The triangular grooves located on the left and right sides of the arc groove also increase the flow velocity near the wall of the arc groove, weaken the influence of the wall shear force, thereby suppressing vortex production. The three triangular grooves and the arc groove cooperate with each other to suppress the cavitation phenomenon of the axial plunger pump distribution plate under high pressure conditions, reduce flow and pressure pulsation and cavitation, and improve the efficiency and life of the axial plunger pump. Attached Figure Description

[0014] To more clearly illustrate the technical solutions in the embodiments of the present invention or the prior art, the drawings used in the embodiments will be briefly described below. Obviously, the drawings described below are only some embodiments of the present invention. For those skilled in the art, other drawings can be obtained based on these drawings without creative effort.

[0015] Figure 1 is a schematic diagram of the structure of the present invention;

[0016] Figure 2 is a schematic diagram of the three-channel structure of the present invention;

[0017] Figure 3 is a schematic diagram of the distribution disk structure of a single throttling channel in the prior art of the present invention;

[0018] Figure 4 is a schematic diagram of a single throttling channel structure in the prior art of the present invention;

[0019] Figure 5 is a diagram showing the velocity streamline distribution of the three-section flow channel of the present invention;

[0020] Figure 6 is a cloud map of the steam volume fraction of the three-throttling channel of the present invention;

[0021] Figure 7 is a diagram showing the velocity streamline distribution of a single throttling channel according to the present invention;

[0022] Figure 8 is a cloud map of the steam volume fraction in a single throttling channel according to the present invention.

[0023] Among them, 1. Three-stage throttling channel; 2. High-low pressure transition zone; 3. Large waist-shaped channel; 4. Small waist-shaped channel; 5. Single throttling channel; 11. Triangular channel; 12. Circular arc channel; 51. Single throttling triangular channel; 52. Single throttling circular arc channel; 6. Second single throttling channel. Detailed Implementation

[0024] The technical solutions of the embodiments of the present invention will be clearly and completely described below with reference to the accompanying drawings. Obviously, the described embodiments are only some embodiments of the present invention, and not all embodiments. Based on the embodiments of the present invention, all other embodiments obtained by those skilled in the art without creative effort are within the scope of protection of the present invention.

[0025] To make the above-mentioned objects, features and advantages of the present invention more apparent and understandable, the present invention will be further described in detail below with reference to the accompanying drawings and specific embodiments.

[0026] Referring to Figures 1 to 8, the present invention provides a high-pressure distribution plate with a three-slot anti-cavitation structure, including a distribution plate, the distribution plate including two centrally symmetrically arranged large waist-shaped slots 3, small waist-shaped slots 4 symmetrically opened on both sides of the large waist-shaped slots 3, the small waist-shaped slots 4 are arranged through the distribution plate, and the two ends of the large waist-shaped slots 3 are respectively connected to a three-slot 1 and a second single-slot 6, the two three-slot 1 are centrally symmetrically arranged;

[0027] The three-channel trough 1 includes three identical triangular channels 11, which are arranged at equal intervals. The ends of the three triangular channels 11 are connected to one end of the same arc channel 12, and the other end of the arc channel 12 is connected to the large waist-shaped channel 3.

[0028] In use, the three triangular grooves 11 arranged at equal intervals on the three-throttling groove 1 increase the flow area and reduce the jet velocity. The triangular grooves 11 located on the left and right sides of the arc groove 12 also increase the flow velocity near the wall of the arc groove 12, weakening the influence of the wall shear force, thereby suppressing vortex generation. The three triangular grooves 11 and the arc groove 12 work together to suppress the cavitation phenomenon of the axial plunger pump distribution plate under high pressure conditions, reduce flow and pressure pulsation and cavitation, and improve the efficiency and life of the axial plunger pump.

[0029] The design was further optimized so that the interval between two adjacent triangular grooves 11 is 3mm.

[0030] The interval between two adjacent triangular grooves 11 is 3mm, denoted as h, which increases the flow area.

[0031] The design was further optimized so that the length of the triangular groove 11 is 12mm and the width of the triangular groove 11 is 2.5mm.

[0032] The length of the triangular groove 11 is represented by b, and the width of the triangular groove 11 is represented by a.

[0033] The design was further optimized so that the radius of the arc groove 12 is 7mm and the groove depth is 1.2mm.

[0034] The radius of the circular groove 12 is represented as R2.

[0035] In a further optimized design, the triangular groove 11 has a straight section at the end near the arc groove 12, and a closed section at the end away from the arc groove 12, with a smooth transition between the straight section and the closed section.

[0036] The design was further optimized so that the straight section length of the triangular groove 11 is 3.2mm.

[0037] Further optimization of the design: the two side walls of the closed section of the triangular groove 11 are both arc-shaped structures, the radius of the arc-shaped structure of the triangular groove 11 is 21.9mm, and the side walls of the arc-shaped structure of the triangular groove 11 intersect on the central axis of the triangular groove 11.

[0038] The radius of the arc-shaped structure of the triangular groove 11 is denoted as R1.

[0039] As shown in Figure 1, the distribution plate has an oil suction area on the left and an oil discharge area on the right. The oil suction area and the oil discharge area are the same size and structure and are centrally symmetrically distributed on the distribution plate.

[0040] Both the oil suction zone and the oil discharge zone include a large waist-shaped groove 3 and throttling grooves set at both ends of the large waist-shaped groove 3. The large waist-shaped groove 3 includes two through-type small waist-shaped grooves 4, which are evenly distributed within the large waist-shaped groove 3. The throttling grooves connected at both ends of the large waist-shaped groove 3 are a three-throttling groove 1 and a second single-throttling groove 6. The three-throttling groove 1 includes an arc groove 12 and three triangular grooves 11. The second single-throttling groove 6 includes another arc groove 12 and a trapezoidal groove connected to the arc groove 12.

[0041] The three-throttling groove 1 located in the oil suction zone and the second single-throttling groove 6 located in the oil discharge zone are arranged adjacent to each other. A high-low pressure transition zone 2 is formed between the three-throttling groove 1 located in the oil suction zone and the second single-throttling groove 6 located in the oil discharge zone. The angle between the tip of the triangular groove 11 in the middle of the three-throttling groove 1 located in the oil suction zone and the vertical center line is 2°, denoted as φ1. The angle between the short side of the trapezoidal groove located in the oil discharge zone and the vertical center line is 10°, denoted as φ2.

[0042] The inner radius of the large waist-shaped groove 3 is denoted as R3, which is 33mm, and the outer radius of the large waist-shaped groove 3 is denoted as R5, which is 43mm.

[0043] The radius of the distribution plate is represented as R6, which is 58mm.

[0044] The four small waist-shaped grooves are arranged in a circle, and the radius of the circle is represented as R4, which is 38mm.

[0045] Referring to Figures 3 and 4, the traditional single-throttling channel distribution plate structure is shown in Figure 3. It only includes a single throttling channel 5, which comprises a single-throttling triangular channel 51 and a single-throttling circular arc channel 52. Referring to Figures 7 and 8, the distribution plate with the single-throttling channel 5 was subjected to CFD simulation at a rotational speed of 2850 r / min and a load pressure of 60 MPa. Cavitation cloud maps of the single-throttling triangular channel 51 at three different locations in the high-low pressure transition region were obtained. As can be seen from the figures, at the single-throttling triangular channel 51, due to the small flow area, a high-speed jet is generated. Under the action of wall shear force, vortices are formed on both sides of the single-throttling circular arc channel 52 of the single-throttling triangular channel 51, as shown in Figure 7. The maximum jet velocities at the three locations are 188.93 m / s, 250.44 m / s, and 294.76 m / s, respectively. As a result, cavitation occurred in the high-speed jet region and the vortex region, as shown in Figure 8; the average steam volume fractions were 0.72%, 6.48%, and 19.26%, respectively.

[0046] To address the problem that high-speed jets and vortices easily occur in the single-throttling triangular groove 51, leading to cavitation, the present invention proposes a three-throttling groove anti-cavitation structure.

[0047] By setting up three throttling channels 1, two triangular channels 11 of the same size are added on the left and right sides of the circular arc channel 12, forming a structure of three triangular channels 11. The two triangular channels 11 are symmetrically distributed on both sides, and the three triangular channels 11 are identical. The distance between any two adjacent triangular channels 11 is 3 mm, denoted as h. On the one hand, this can increase the flow area, reduce the jet velocity, and reduce cavitation; on the other hand, the triangular channels 11 on the left and right sides can increase the flow velocity near the wall of the circular arc channel 12, weaken the influence of wall shear force, thereby suppressing vortex generation and reducing cavitation.

[0048] Referring to Figures 4 and 5, under the same operating conditions as described above, CFD simulations were performed to obtain cavitation cloud maps of the three-channel 1 at three different locations in the high-low pressure transition region. In Figure 4, the maximum jet velocities at the three locations are 93.71 m / s, 196.15 m / s, and 263.68 m / s, respectively. In Figure 5, the average steam volume fractions are 0.14%, 1.63%, and 8.66%, respectively. From the figures, it can be seen that the jet velocity decreases significantly due to the increased flow area; and the addition of triangular channels 11 on both sides increases the fluid velocity near the wall of the circular channel 12, thereby suppressing vortex generation. Based on these two points, the cavitation region of the entire distribution plate is significantly reduced.

[0049] Compared to the single-throttling channel 5, the maximum jet velocity is reduced by 50.40%, 21.68%, and 10.54%, respectively, and the cavitation region volume is reduced by 80.56%, 74.85%, and 55.04%, respectively. Therefore, the structure of the three-throttling channel 1 greatly reduces the jet velocity, eliminates vortex flow, and suppresses cavitation.

[0050] With the design of this invention, the jet velocity is reduced by more than 10%, the cavitation area is reduced by more than 50%, the cavitation phenomenon of the distribution plate is significantly suppressed, and the pressure, flow pulsation and cavitation of the axial plunger pump can be reduced, thereby improving the pump efficiency and life.

[0051] In the description of this invention, it should be understood that the terms "longitudinal", "lateral", "up", "down", "front", "rear", "left", "right", "vertical", "horizontal", "top", "bottom", "inner", "outer", etc., indicate the orientation or positional relationship based on the orientation or positional relationship shown in the accompanying drawings, and are only for the convenience of describing this invention, and are not intended to indicate or imply that the device or element referred to must have a specific orientation, or be constructed and operated in a specific orientation, and therefore should not be construed as a limitation of this invention.

[0052] The embodiments described above are merely preferred embodiments of the present invention and are not intended to limit the scope of the present invention. Various modifications and improvements made by those skilled in the art to the technical solutions of the present invention without departing from the spirit of the present invention should fall within the protection scope defined by the claims of the present invention.

Claims

1. A three-slot anti-cavitation structure for a high-pressure distribution plate, characterized in that: The distribution plate includes two centrally symmetrically arranged large waist-shaped grooves (3), and small waist-shaped grooves (4) symmetrically opened on both sides of the large waist-shaped grooves (3). The small waist-shaped grooves (4) are arranged through the distribution plate. The two ends of the large waist-shaped grooves (3) are respectively connected to a three-throttling groove (1) and a second single-throttling groove (6). The two three-throttling grooves (1) are centrally symmetrically arranged. The three-throttling grooves (1) include three triangular grooves (11) with identical structures. The three triangular grooves (11) are arranged at equal intervals. The ends of the three triangular grooves (11) are connected to one end of the same arc groove (12). The other end of the arc groove (12) is connected to the large waist-shaped groove (3). The three-throttling groove (1) is connected to the circular arc groove (12) at one end, and a straight section is provided at the other end of the three-throttling groove (11) away from the circular arc groove (12). The straight section and the closed section are smoothly connected. The two side walls of the closed section of the three-throttling groove (11) are both circular arc structures. The side walls of the circular arc structures of the three-throttling groove (11) intersect on the central axis of the three-throttling groove (11). The three-throttling groove (1) located in the oil suction area is adjacent to the second single throttling groove (6) located in the oil discharge area. A high-low pressure transition area is formed between the three-throttling groove (1) located in the oil suction area and the second single throttling groove (6) located in the oil discharge area.

2. The high-pressure distribution plate three-channel anti-cavitation structure according to claim 1, characterized in that: The interval between two adjacent triangular grooves (11) is 3mm.

3. The high-pressure distribution plate three-channel anti-cavitation structure according to claim 1, characterized in that: The length of the triangular groove (11) is 12mm and the width of the triangular groove (11) is 2.5mm.

4. The high-pressure distribution plate three-channel anti-cavitation structure according to claim 1, characterized in that: The radius of the arc groove (12) is 7mm, and the depth of the arc groove (12) is 1.2mm.

5. The high-pressure distribution plate three-channel anti-cavitation structure according to claim 1, characterized in that: The straight section of the triangular groove (11) has a length of 3.2 mm.

6. The high-pressure distribution plate three-channel anti-cavitation structure according to claim 1, characterized in that: The radius of the arc-shaped structure of the triangular groove (11) is 21.9 mm.

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