Plunger pump motor displacement high-frequency response adjusting device

Abstract

The invention belongs to the technical field of plunger pump motors, and particularly relates to a plunger pump motor displacement high-frequency response adjusting device which comprises an axial plunger pump motor, a nozzle baffle valve, a first piston, a second piston, a third piston and a fourth piston. The first piston and the third piston are located on one side of a swash plate of the axial plunger pump motor. The second piston and the fourth piston are positioned on the other side of the swash plate of the axial plunger pump motor; the nozzle baffle valve comprises a first nozzle unit and a second nozzle unit; the hydraulic cylinder has the advantages that the nozzle baffle valve is used, control is accurate, response is rapid, the four pistons are used, response is rapid, stability is high, machining is convenient, and the pistons have the feedback effect and are convenient to maintain due to the fact that the springs are installed.

Description

Technical Field

[0001] The present application belongs to the technical field of plunger pump motors, and in particular relates to a high-frequency response adjustment device for the displacement of a plunger pump motor. Background Art

[0002] Plunger pumps are widely used in various hydraulic systems to provide stable hydraulic power. Due to their compact structure, high efficiency, and large flow rate, plunger pumps are widely used in engineering machinery, agricultural machinery, ships, aerospace, and other fields. The existing technology has the problems of slow response speed and poor stability. Summary of the invention

[0003] Based on the above problems, the present application provides a high-frequency response adjustment device for the displacement of a plunger pump motor, and its technical solution is as follows:

[0004] A high-frequency response adjustment device for displacement of a plunger pump motor comprises an axial piston pump motor, a nozzle flapper valve, a first piston, a second piston, a third piston, and a fourth piston; the first piston and the third piston are located on one side of the swash plate of the axial piston pump motor; the second piston and the fourth piston are located on the other side of the swash plate of the axial piston pump motor;

[0005] The nozzle flapper valve includes a first nozzle unit and a second nozzle unit, and a fourth oil path section P2 and a third oil path section P1 are provided on the cross section of the nozzle flapper valve. The oil path at the position of the third oil path section P1 is ultimately connected to the first piston and the second piston through an oil path; the oil path at the position of the fourth oil path section P2 is ultimately connected to the third piston and the fourth piston through an oil path.

[0006] Preferably, the nozzle baffle valve includes a first nozzle fixing unit, a first nozzle unit, and a baffle; the first nozzle unit is provided with a first radial oil outlet Q1, the second nozzle unit is provided with a second radial oil outlet Q2, the first oil passage R from the second oil inlet X1 to the first nozzle unit and the second nozzle unit needs to ensure that the distances flowing into the first nozzle unit and the second nozzle unit are equal, and the baffle is located between the first nozzle unit and the second nozzle unit; the hydraulic oil flows into the first nozzle unit and the second nozzle unit from the second oil inlet X1 and is divided into two parts; the hydraulic oil flowing into the first nozzle unit flows out from the first radial oil outlet Q1, and the hydraulic oil flowing into the second nozzle unit flows out from the second radial oil outlet Q2. Due to the restriction of the baffle on the nozzle flow rate and the influence of the damping hole of the nozzle baffle valve on the pressure drop, the oil at one end becomes high-pressure oil and the other end becomes low-pressure oil. The specific situation is determined by the deflection of the baffle, and then the hydraulic oil flows into the axial piston pump motor respectively.

[0007] Preferably, the first piston, the second piston, the third piston and the fourth piston have the same structure, including a piston chamber, a spring and a piston rod, and a first spring mounting base and a second spring mounting base are respectively provided at both ends of the spring, the first spring mounting base is fixed on the cylinder body of the axial piston pump motor, and the second spring mounting base is installed on the front end of the piston rod and moves with the piston.

[0008] Preferably, the axial piston pump motor includes a front end housing, a shaft, an intermediate housing, and a rear end housing; a first rolling bearing, a distribution plate, a cylinder body, a return plate, a swash plate, and a second rolling bearing are sequentially arranged on the shaft; a first sealing ring is arranged above the first rolling bearing, a sliding shoe is arranged on the return plate, a plunger is arranged in the sliding shoe, and a second sealing ring is arranged below the second rolling bearing; a first oil inlet X2 and a first oil outlet X3 are opened on the rear end housing.

[0009] Preferably, when the baffle of the nozzle baffle valve is in the middle position, the hydraulic oil enters from the second oil inlet X1 of the nozzle baffle valve, and then enters the seventh oil circuit S1 and the eighth oil circuit S2 respectively through the first oil circuit R; the hydraulic oil enters the first nozzle fixing unit and the second nozzle fixing unit respectively through the seventh oil circuit S1 and the eighth oil circuit S2; the hydraulic oil flows from the first nozzle fixing unit into the first nozzle unit, and flows from the second nozzle fixing unit into the second nozzle unit; part of the hydraulic oil flows out from the first radial oil outlet Q1 on the first nozzle unit and from the second radial oil outlet Q2 on the second nozzle unit, and this part flows into the third oil circuit section P1 and the fourth oil circuit section P2 respectively; the other part of the hydraulic oil is sprayed out through the nozzle port and finally flows back to the oil tank. Since the baffle 22 is in the middle position, the distance experienced by the hydraulic oil on both sides is equal, so the pressure loss is equal, and the flow rate of the hydraulic oil flowing out of the nozzle at both ends is the same, so the pressure drop at both ends is equal, so the flow rate of the hydraulic oil flowing into the third oil circuit section P1 and the fourth oil circuit section P2 is equal, and the pressure is equal;

[0010] The hydraulic oil flows out from the third oil circuit section P1 and the fourth oil circuit section P2, wherein the hydraulic oil flowing out from the third oil circuit section P1 flows into the first piston and the second piston respectively through the oil circuit; the hydraulic oil flowing out from the fourth oil circuit section P2 flows into the third piston and the fourth piston respectively through the oil circuit; at this time, the distance that the hydraulic oil flows into the four pistons should be similar, because the pressure of the hydraulic oil flowing into the four piston chambers is equal, and the swash plate does not deflect at this time.

[0011] Preferably, when the baffle is deflected counterclockwise, the cross-sectional area of ​​the oil outlet of the nozzle changes, thereby increasing the oil outlet area of ​​the first nozzle unit and reducing the oil outlet area of ​​the second nozzle unit. Therefore, the oil outlet of the first nozzle unit increases, while the oil outlet of the second nozzle unit decreases, and then the pressure drop of the first nozzle unit is greater than that of the second nozzle unit, so that the pressure of the hydraulic oil flowing out of the second nozzle unit is higher than the pressure of the hydraulic oil flowing out of the first nozzle unit. At this time, the low-pressure oil finally enters the first piston and the second piston, and the high-pressure oil finally enters the third piston and the fourth piston, and the third piston and the fourth piston push the swash plate to rotate;

[0012] The front end mounting seat of the spring on the third piston and the fourth piston moves forward, and the spring is in a stretched and elongated state; the front end mounting seat of the spring on the first piston and the second piston moves backward, and the spring is in a compressed and shortened state. The deformation of the spring generates a feedback force, causing the piston to experience resistance in the opposite direction of rotation. When the propulsion force of the piston is equal to the feedback resistance, the swash plate stops rotating.

[0013] Preferably, when the baffle is deflected clockwise, the cross-sectional area of ​​the oil outlet of the nozzle changes, the oil outlet area of ​​the first nozzle unit decreases, and the oil outlet area of ​​the second nozzle unit increases, so the oil outlet of the first nozzle unit decreases, while the oil outlet of the second nozzle unit increases, so the pressure drop of the second nozzle unit is greater than that of the first nozzle unit, and finally the pressure of the hydraulic oil flowing out of the first nozzle unit is higher than the pressure of the hydraulic oil flowing out of the second nozzle unit. At this time, the high-pressure oil finally enters the first piston and the second piston, and the low-pressure oil finally enters the third piston and the fourth piston, and the first piston and the second piston push the swash plate to rotate;

[0014] The front end mounting seats of the springs on the first and second pistons move forward, and the springs are in a stretched and elongated state. The front end mounting seats of the springs on the third and fourth pistons move backward, and the springs are in a compressed and shortened state. The deformation of the springs generates a feedback force, causing the pistons to experience resistance in the opposite direction of rotation. When the propulsion force of the pistons is equal to the resistance, the swash plate stops rotating.

[0015] Compared with the prior art, the present invention has the following beneficial effects:

[0016] The use of nozzle flapper valve makes the control precise and the response quick. The use of four pistons has fast response, high reliability and convenient processing. The installation of springs makes the pistons have feedback effect and is easy to maintain. BRIEF DESCRIPTION OF THE DRAWINGS

[0017] Figure 1 is the main view;

[0018] Figure 2 For three-dimensional Figure 1 ;

[0019] Figure 3 For three-dimensional Figure 2 ;

[0020] Figure 4 It is a top view;

[0021] Figure 5 for Figure 1 A cross-sectional view of the AA position of the axial piston pump motor;

[0022] Figure 6 This is the appearance diagram of the nozzle flapper valve;

[0023] Figure 7 for Figure 6 Sectional view of the FF position of the middle nozzle flapper valve;

[0024] Figure 8 This is the appearance of the piston;

[0025] Fig. 9 It is the cross-sectional view of the piston at the EE position;

[0026] Fig.10 It is the cross-sectional view of the nozzle flapper valve GG position;

[0027] Fig.11 This is the cross-sectional view of the FF position of the axial piston pump motor;

[0028] Fig.12 This is the cross-sectional view of the BB position of the axial piston pump motor;

[0029] Fig.13 It is a simplified diagram of the swash plate piston device;

[0030] Fig.14 This is a simplified diagram of the device when the swash plate is balanced;

[0031] Fig.15 This is the case where the baffle is deflected counterclockwise;

[0032] Fig.16 This is a simplified diagram of the device when the swash plate deflects clockwise;

[0033] Fig.17 This is the case where the baffle is deflected clockwise;

[0034] Fig.18 This is a simplified diagram of the device when the swash plate deflects counterclockwise;

[0035] Fig.19 This is the hydraulic principle diagram of this scheme.

[0036] In the figure: 1-axial piston pump motor, 2-nozzle flapper valve, 3-front end housing, 4-shaft, 5-intermediate housing, 6-rear end housing, 7-first rolling bearing, 8-first sealing ring, 9-distributor, 10-cylinder body, 11-piston, 12-return plate, 13-slipper, 14-slant plate, 15-slant plate groove, 16-first piston, 17-third piston, 18-fourth piston, 19-second piston, 20-second nozzle fixing unit, 25-first nozzle unit, 22-flapper, 23-torque motor, 24-armature, 21-second nozzle unit, 26-first nozzle fixing unit. 27-second rolling bearing, 28-second sealing ring, piston chamber 29, first spring mounting base 30, integrated piston rod 31, second spring mounting base 32, spring 33, piston ball end fixing 34. DETAILED DESCRIPTION

[0037] In order to make the purpose of the present invention: the scheme and advantages of a plunger pump motor displacement high-frequency response adjustment device more clearly explained, the present invention is further described in detail below in combination with specific implementation methods and with reference to the accompanying drawings.

[0038] Figure 1 As shown, a high-frequency response adjustment device for displacement of a piston pump motor comprises an axial piston pump motor 1, a nozzle flapper valve 2, a first piston 16, a second piston 19, a third piston 17, and a fourth piston 18; the first piston 16 and the third piston 17 are located on one side of a swash plate 14 of the axial piston pump motor 1; the second piston 19 and the fourth piston 18 are located on the other side of the swash plate 14 of the axial piston pump motor 1;

[0039] The nozzle flapper valve 2 includes a first nozzle unit 25 and a second nozzle unit 21. The oil circuit at the third oil circuit section P1 position is connected to the first piston 16 and the second piston 19 through the oil circuit; the oil circuit at the fourth oil circuit section P2 position is connected to the third piston 17 and the fourth piston 18 through the oil circuit.

[0040] The plunger pump motor 1 is mainly composed of a front end housing 3, a shaft 4, an intermediate housing 5, a rear end housing 6, a first rolling bearing 7, a first sealing ring 8, a distribution plate 9, a cylinder body 10, a plunger 11, a return plate 12, a sliding shoe 13, a swash plate 14, a swash plate groove 15, a first piston 16, a second piston 19, a third piston 17, a fourth piston 18, a piston ball end fixing 34, a second rolling bearing 27, and a second sealing ring 28. The rear end housing 6 is provided with a first oil inlet X2 and a first oil outlet X3, and the cross-sectional position FF has a ninth oil path cross-sectional area K.

[0041] The nozzle flapper valve 2 is mainly composed of a first nozzle fixing unit 26 , a first nozzle unit 25 , a flapper 22 , a torque motor 23 , an armature 24 , a second nozzle unit 21 , and a second nozzle fixing unit 20 .

[0042] The upper end surface of the nozzle flapper valve 2 is provided with a second oil inlet X1. Fig.10 The cross section GG has a first oil passage R, a seventh oil passage S1, and an eighth oil passage S2. The first nozzle unit 25 has a first radial oil outlet Q1. The second nozzle unit 21 has a second radial oil outlet Q2. Figure 7 The third oil passage section P1 is shown on the left end of the cross section FF, and the fourth oil passage section P2 is shown on the right end. Fig.12 The section BB has a second oil circuit W1 and a third oil circuit W2 that penetrate the nozzle flapper valve 2 and the axial piston pump motor 1. The left end of BB shown in the figure has a fifth oil circuit section V1, and the right end shown in the figure has a sixth oil circuit section V2. The first piston 16 has a third oil inlet Y, the second piston 19 has a fourth oil inlet Z, the third piston 17 has a fifth oil inlet T, and the fourth piston 18 has a sixth oil inlet U. The assembly and maintenance are convenient and the stability is high.

[0043] In the solution of the present invention, the valve body of the nozzle flapper valve is processed with a second oil inlet X1, and the symmetrical and equidistant first oil circuit R and the first nozzle unit 25 and the second nozzle unit 21 of the same structure and symmetrical arrangement can achieve theoretically equal pressure loss of hydraulic oil at both ends. The first nozzle fixing unit 26 and the second nozzle fixing unit 20 can fix the nozzle unit in the valve body. After the oil flows into the nozzle unit from the nozzle fixing unit, it is divided into two parts. The left end oil of one part flows out from the first radial oil outlet Q1, and the right end oil flows out from the second radial oil outlet Q2. Due to the effect of the baffle 22 on the oil outlet area and the influence of the damping hole on the pressure drop, one end of this part of hydraulic oil becomes high-pressure oil and the other end becomes low-pressure oil. The hydraulic oil flows out of the nozzle flapper valve 2 through the oil circuit and flows into the axial piston pump motor 1. High-pressure oil and low-pressure oil flow into the pump motor housing from the equidistant oil circuit. The piston cavity is provided with an oil inlet so that the hydraulic oil finally flows into the piston. The piston is mounted on the swash plate 14 through the piston ball end fixing 34, pushing the swash plate to reciprocate. The spring installed on the piston plays a feedback role in the rotation of the swash plate. The swash plate 14 is mounted on the swash plate groove 15 and rotates in the groove. Another part of the hydraulic oil sprayed by the nozzle flows through the sixth oil path J that runs through the pump motor and the valve, flows to the ninth oil path section K, and finally returns the oil.

[0044] Taking the first piston 16 as an example, the piston structure is described. The piston mainly includes a piston chamber 29, which is used to provide a closed space for the piston. The first spring mounting base 30 is fixed on the cylinder body 10. The spring 33 provides a feedback force in the opposite direction of the swash plate rotation. The second spring mounting base 32 moves with the spring 33, driving the spring 33 to stretch. The integrated piston rod 31, when hydraulic oil enters, gives hydraulic pressure to the piston rod 31, thereby driving the swash plate 14 to rotate.

[0045] (1) Theoretically: When the baffle 22 is in the middle position, after the hydraulic oil enters from the second oil inlet X1 of the nozzle baffle valve, the hydraulic oil is divided into two parts through the first oil circuit R and enters the seventh oil circuit S1 and the eighth oil circuit S2. At the position of the flow section FF, the hydraulic oil enters the first nozzle fixing unit 26 and the second nozzle fixing unit 20 from the left and right sides respectively. The hydraulic oil flows from the first nozzle fixing unit 26 to the first nozzle unit 25, and flows from the second nozzle fixing unit 20 to the second nozzle unit 21. The left end of the first part of the hydraulic oil flows out from the first radial oil outlet Q1 on the first nozzle unit 25, and the right end flows out from the second radial oil outlet Q2 on the second nozzle unit 21, and flows into the third oil circuit section P1 and the fourth oil circuit section P2 respectively, and the other part of the hydraulic oil is sprayed out through the nozzle. Since the baffle 22 is located in the middle position, the distance traveled by the hydraulic oil on both sides is equal, so the pressure loss is equal, and the hydraulic oil flow rate flowing out of the nozzles at both ends is the same, so the pressure drop is the same, then the hydraulic oil flow rate flowing into the third oil circuit section P1 and the fourth oil circuit section P2 is equal, and the pressure is equal.

[0046] The hydraulic oil further flows out from the third oil passage section P1 and the fourth oil passage section P2 and enters the above Fig.12 Section BB section position. From the second oil passage W1 and the third oil passage W2, respectively, through the nozzle flapper valve 2, enter the fifth oil passage section V1 and the sixth oil passage section V2 of the axial piston pump motor 1, Fig.12 The oil at the left end enters the fifth oil passage section V1. Fig.12 The oil at the right end enters the sixth oil passage section V2. Fig.12 The oil at the left end enters the fifth oil passage section V1 and finally supplies oil to the first piston 16 and the second piston 19 . Fig.12 After the right end oil enters the sixth oil passage section V2, it finally supplies oil to the third piston 17 and the fourth piston 18. Since the pressure of the hydraulic oil flowing into the four piston chambers is equal, the swash plate does not deflect at this time. (In this process, it is necessary to ensure that the length of the path through which the hydraulic oil flows is approximately equal, so that the four pistons can be supplied with oil at the same time, and the pressure loss will not differ too much).

[0047] (2) Theoretically: When the baffle is deflected counterclockwise, the situation is as follows: Fig.15 shown.

[0048] The counterclockwise deflection of the baffle will affect the cross-sectional area of ​​the oil outlet of the nozzle, ultimately increasing the oil outlet of the left nozzle and reducing the oil outlet of the right nozzle, thereby increasing the pressure drop of the left nozzle unit and reducing the pressure drop of the right nozzle unit, making the pressure of the hydraulic oil flowing out of the left nozzle unit lower than the pressure of the hydraulic oil flowing out of the right nozzle unit.

[0049] Further, the hydraulic oil enters the above mentioned Fig.12Section BB section position. The oil flows from the second oil circuit W1 and the third oil circuit W2 through the nozzle flapper valve 2 into the fifth oil circuit section V1 and the sixth oil circuit section V2 of the axial piston pump motor 1. The oil at the left end of the nozzle flapper valve 2 flows into the fifth oil circuit section V1, and the oil at the right end flows into the sixth oil circuit section V2. Finally, it passes through the oil circuit arranged on the housing of the axial piston pump motor. Fig.12 The low-pressure oil at the left end flows into the first piston 16 and the second piston 19 through the oil circuit at the fifth oil circuit section V1, and the high-pressure oil at the right end flows into the third piston 17 and the fourth piston 18 through the oil circuit at the sixth oil circuit section V2.

[0050] At this time, the low-pressure oil enters the first piston 16 and the second piston 19, and the high-pressure oil enters the third piston 17 and the fourth piston 18 (in this process, it is necessary to ensure that the path length through which the hydraulic oil flows is equal, the four pistons can be supplied with oil at the same time, and the pressure loss difference will not be too large). The third piston 17 and the fourth piston 18 push the swash plate 14 to rotate, and the front end mounting seats of the springs on the third piston 17 and the fourth piston 18 move forward, and the springs are in a stretched and elongated state. The front end mounting seats of the springs on the first piston 16 and the second piston 19 move backward, and the springs are in a compressed and shortened state. The deformation of the spring generates a feedback force, causing the piston to be subjected to resistance in the opposite direction of rotation. When the propulsion force of the piston is equal to the feedback resistance, the swash plate stops rotating. The schematic diagram of the device when the swash plate described in this scheme deflects clockwise is as follows. Fig.16 shown.

[0051] (3) Theoretically: When the baffle is deflected clockwise, the situation is as follows: Fig.17 shown.

[0052] The clockwise deflection of the baffle will affect the cross-sectional area of ​​the nozzle oil outlet, ultimately increasing the oil outlet of the right nozzle and reducing the oil outlet of the left nozzle, ultimately making the hydraulic oil pressure flowing out of the right nozzle unit lower than the hydraulic oil pressure flowing out of the left nozzle unit.

[0053] Further, the hydraulic oil enters the above mentioned Fig.12 Section BB section position. From the second oil circuit W1 and the third oil circuit W2, the nozzle flapper valve 2 enters the fifth oil circuit section V1 and the sixth oil circuit section V2 of the axial piston pump motor 1. The oil at the left end of the nozzle flapper valve 2 flows into the fifth oil circuit section V1, and the oil at the right end enters the sixth oil circuit section V2. Finally, it passes through the oil circuit arranged on the housing of the axial piston pump motor. Fig.12 The high-pressure oil at the left end flows into the first piston 16 and the second piston 19 through the oil circuit at the fifth oil circuit section V1, and the low-pressure oil at the right end flows into the third piston 17 and the fourth piston 18 through the oil circuit at the sixth oil circuit section V2.

[0054] At this time, high-pressure oil enters the first piston 16 and the second piston 19, and low-pressure oil enters the third piston 17 and the fourth piston 18 (in this process, it is necessary to ensure that the path length through which the hydraulic oil flows is equal, the four pistons can be supplied with oil at the same time, and the pressure loss will not differ too much). The first piston 16 and the second piston 19 push the swash plate 14 to rotate (the rotation direction is opposite to the above-mentioned rotation direction). The front end mounting seat of the spring on the first piston 16 and the second piston 19 moves forward, and the spring is in a stretched and elongated state. The front end mounting seat of the spring entering the third piston 17 and the fourth piston 18 moves backward, and the spring is in a compressed and shortened state. The deformation of the spring generates a feedback force, causing the piston to be subjected to resistance in the opposite direction of rotation. When the propulsion force of the piston is equal to the feedback resistance, the swash plate stops rotating. The schematic diagram of the device when the swash plate described in this scheme deflects counterclockwise is as follows. Fig.18 shown.

[0055] The hydraulic principle diagram of this scheme is as follows Fig.19 shown.

[0056] The hydraulic control principle is as follows: the hydraulic oil flows from the second oil inlet X1 through the first throttle port a and the second throttle port b into the second nozzle unit 21 and the first nozzle unit 25 in the nozzle flapper valve 2. The outflowing hydraulic oil is divided into two parts. One part of the hydraulic oil enters the oil return line of the axial piston pump motor 1. The other part of the hydraulic oil is divided into two parts, Fig.19 The left end portion of the hydraulic oil eventually flows into the first piston 16 and the second piston 19. Fig.19 The hydraulic oil at the right end eventually flows into the third piston 17 and the fourth piston 18. Due to the influence of the baffle 22 on the oil outlet area and the damping hole on the pressure drop, the flow rate of the hydraulic oil at both ends of this part of the hydraulic oil will be different, causing the pressure drop at both ends to change, thereby generating a pressure difference. The piston injected with high-pressure oil pushes the swash plate 14 to rotate. The piston is equipped with a spring. The active motion piston spring is stretched, and the passive motion piston spring is compressed. The stretched spring and compressed spring generate resistance. When the piston pushing force is equal to the spring resistance, a balanced state is reached. Adjusting the deflection angle of the baffle adjusts the deflection angle and direction of the swash plate, thereby adjusting the flow of the axial piston pump motor 1.

[0057] It will be easily understood by those skilled in the art that the above description is only a preferred embodiment of the present invention and is not intended to limit the present invention. Any modifications, equivalent substitutions and improvements made within the spirit and principles of the present invention should be included in the protection scope of the present invention.

Claims

1. A high-frequency response adjustment device for a plunger pump motor displacement, characterized in that: It includes an axial piston pump motor, a nozzle flapper valve, a first piston, a second piston, a third piston, and a fourth piston; the first piston and the third piston are located on one side of the swash plate of the axial piston pump motor; the second piston and the fourth piston are located on the other side of the swash plate of the axial piston pump motor; The nozzle flapper valve includes a first nozzle unit and a second nozzle unit, and a fourth oil path section P2 and a third oil path section P1 are provided on the cross section of the nozzle flapper valve. The oil path at the position of the third oil path section P1 is ultimately connected to the first piston and the second piston through an oil path; the oil path at the position of the fourth oil path section P2 is ultimately connected to the third piston and the fourth piston through an oil path.

2. The high-frequency response adjustment device for the displacement of a plunger pump motor according to claim 1, characterized in that: The nozzle flapper valve includes a first nozzle fixing unit, a first nozzle unit, and a baffle; the first nozzle unit is provided with a first radial oil outlet Q1, the second nozzle unit is provided with a second radial oil outlet Q2, the first oil passage R from the second oil inlet X1 to the first nozzle unit and the second nozzle unit needs to ensure that the distances flowing into the first nozzle unit and the second nozzle unit are equal, and the baffle is located between the first nozzle unit and the second nozzle unit; the hydraulic oil flows into the first nozzle unit and the second nozzle unit from the second oil inlet X1 and is divided into two parts; the hydraulic oil flowing into the first nozzle unit flows out from the first radial oil outlet Q1, and the hydraulic oil flowing into the second nozzle unit flows out from the second radial oil outlet Q2. Due to the restriction of the baffle on the nozzle flow rate and the influence of the damping hole of the nozzle flapper valve on the pressure drop, the oil at one end becomes high-pressure oil and the other end becomes low-pressure oil. The specific situation is determined by the deflection of the baffle, and then the hydraulic oil flows into the axial piston pump motor respectively.

3. The high-frequency response adjustment device for the displacement of a plunger pump motor according to claim 1, characterized in that: The first piston, the second piston, the third piston and the fourth piston have the same structure, including a piston chamber, a spring and a piston rod. A first spring mounting base and a second spring mounting base are respectively provided at both ends of the spring. The first spring mounting base is fixed on the cylinder body of the axial piston pump motor, and the second spring mounting base is installed on the front end of the piston rod and moves with the piston.

4. The high-frequency response adjustment device for the displacement of a plunger pump motor according to claim 1, characterized in that: The axial piston pump motor includes a front end housing, a shaft, an intermediate housing, and a rear end housing; a first rolling bearing, a distribution plate, a cylinder body, a return plate, a swash plate, and a second rolling bearing are sequentially arranged on the shaft; a first sealing ring is arranged above the first rolling bearing, a sliding shoe is arranged on the return plate, a plunger is arranged in the sliding shoe, and a second sealing ring is arranged below the second rolling bearing; a first oil inlet X2 and a first oil outlet X3 are opened on the rear end housing.

5. The plunger pump motor displacement high-frequency response adjustment device according to claim 1, characterized in that: When the baffle of the nozzle baffle valve is in the middle position, the hydraulic oil enters from the second oil inlet X1 of the nozzle baffle valve, and then enters the seventh oil circuit S1 and the eighth oil circuit S2 respectively through the first oil circuit R; the hydraulic oil enters the first nozzle fixing unit and the second nozzle fixing unit respectively through the seventh oil circuit S1 and the eighth oil circuit S2; the hydraulic oil flows from the first nozzle fixing unit into the first nozzle unit, and flows from the second nozzle fixing unit into the second nozzle unit; part of the hydraulic oil flows out from the first radial oil outlet Q1 on the first nozzle unit and from the second radial oil outlet Q2 on the second nozzle unit, and this part flows into the third oil circuit section P1 and the fourth oil circuit section P2 respectively; the other part of the hydraulic oil is sprayed out through the nozzle port and finally flows back to the oil tank. Since the baffle 22 is in the middle position, the distance experienced by the hydraulic oil on both sides is equal, so the pressure loss is equal, and the flow rate of the hydraulic oil flowing out of the nozzle at both ends is the same, so the pressure drop at both ends is equal, so the flow rate of the hydraulic oil flowing into the third oil circuit section P1 and the fourth oil circuit section P2 is equal, and the pressure is equal; The hydraulic oil flows out from the third oil circuit section P1 and the fourth oil circuit section P2, wherein the hydraulic oil flowing out from the third oil circuit section P1 flows into the first piston and the second piston respectively through the oil circuit; the hydraulic oil flowing out from the fourth oil circuit section P2 flows into the third piston and the fourth piston respectively through the oil circuit; at this time, the distance that the hydraulic oil flows into the four pistons should be similar, because the pressure of the hydraulic oil flowing into the four piston chambers is equal, and the swash plate does not deflect at this time.

6. The plunger pump motor displacement high frequency response adjustment device according to claim 1, characterized in that: When the baffle is deflected counterclockwise, the cross-sectional area of ​​the oil outlet of the nozzle changes, thereby increasing the oil outlet area of ​​the first nozzle unit and reducing the oil outlet area of ​​the second nozzle unit. Therefore, the oil outlet of the first nozzle unit increases, while the oil outlet of the second nozzle unit decreases. In addition, the pressure drop of the first nozzle unit is greater than that of the second nozzle unit, so that the pressure of the hydraulic oil flowing out of the second nozzle unit is higher than that of the hydraulic oil flowing out of the first nozzle unit. At this time, the low-pressure oil finally enters the first piston and the second piston, and the high-pressure oil finally enters the third piston and the fourth piston. The third piston and the fourth piston push the swash plate to rotate; The front end mounting seats of the springs on the third piston and the fourth piston move forward, and the springs are in a stretched and elongated state; the front end mounting seats of the springs on the first piston and the second piston move backward, and the springs are in a compressed and shortened state; the deformation of the springs generates a feedback force, causing the pistons to be subjected to resistance in the opposite direction of rotation. When the propulsion force of the pistons is equal to the feedback resistance, the swash plate stops rotating.

7. The high-frequency response adjustment device for the displacement of a plunger pump motor according to claim 1, characterized in that: When the baffle is deflected clockwise, the cross-sectional area of ​​the nozzle oil outlet changes, the oil outlet area of ​​the first nozzle unit decreases, and the oil outlet area of ​​the second nozzle unit increases, so the oil outlet of the first nozzle unit decreases, while the oil outlet of the second nozzle unit increases, so the pressure drop of the second nozzle unit is greater than that of the first nozzle unit, and finally the hydraulic oil pressure flowing out of the first nozzle unit is higher than the hydraulic oil pressure flowing out of the second nozzle unit. At this time, the high-pressure oil finally enters the first piston and the second piston, and the low-pressure oil finally enters the third piston and the fourth piston, and the first piston and the second piston push the swash plate to rotate; The front end mounting seats of the springs on the first piston and the second piston move forward, and the springs are in a stretched state; The front end mounting seats of the springs on the third and fourth pistons move backwards, and the springs are in a compressed and shortened state; the deformation of the springs generates a feedback force, causing the pistons to experience resistance in the opposite direction of rotation. When the propulsion force of the pistons is equal to the resistance, the swash plate stops rotating.

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