An electric hydraulic pump with an integrated flow control valve

Abstract

An electro-hydraulic pump with an integrated flow-dividing valve, comprising a motor, a hydraulic pump and a flow-dividing valve. The flow-dividing valve includes: a valve body having a first cavity, a second cavity and a first flow-dividing channel. The first flow-dividing channel is communicated with the first cavity through a first flow-dividing port and with the second cavity through a first liquid outlet; a first valve member disposed in the first cavity and having a first damping hole; the first valve member has a first state of blocking the first flow-dividing port and a second state of opening the first flow-dividing port; the first valve member can be changed from the first state to the second state under the action of a sufficiently large axial external force, and can be restored from the second state to the first state when the external force disappears or weakens. When the electro-hydraulic pump is applied to a shock absorber, when the movement speed of the piston exceeds the control range, by integrating the flow-dividing valve on the electro-hydraulic pump, it can not only protect the hydraulic pump and the motor from exceeding the controllable speed, but also enable the shock absorber to maintain the performance of a passive shock absorber.

Description

Technical Field

[0001] The present invention relates to the technical field of automotive shock absorption, specifically to an electric hydraulic pump, and more specifically, to an electric hydraulic pump integrated with a flow dividing valve. Background Art

[0002] Shock absorbers play an extremely important role in attenuating the vibrations of the vehicle body and chassis, improving both the comfort of passengers inside the vehicle and the grip of the wheels. Generally speaking, shock absorbers can enhance the stability and maneuverability of the vehicle.

[0003] In traditional passive shock absorbers, since stability and maneuverability are two quantities that compromise with each other within a certain range, they are generally tuned at the time of vehicle factory production to achieve a widely acceptable effect. However, in actual applications, due to changes in road conditions, the number of passengers in the vehicle, etc., it is very difficult to achieve good results in all cases with traditional passive shock absorbers.

[0004] To improve the dynamic performance, active shock absorbers have been proposed in the industry. Active shock absorbers control the force output by the active shock absorber by controlling the pressure difference on both sides of the piston, thereby controlling the stability and maneuverability of the vehicle. The control of the pressure difference on both sides of the piston can be achieved through the control of an electric hydraulic pump. Compared with traditional passive shock absorbers, active shock absorbers can provide a better dynamic range, can achieve better control of stability and maneuverability under various conditions, and can recover the energy generated by vibrations.

[0005] The current problem is that the power of the electric hydraulic pump is limited. When the piston moves too fast, causing the rotational speed of the electric hydraulic pump to exceed the control range, it will be difficult to achieve good control of the vehicle's stability and maneuverability. Summary of the Invention

[0006] The technical problem to be solved by the present invention is to provide an electric hydraulic pump integrated with a flow dividing valve. After the electric hydraulic pump is connected to a shock absorber, when the piston rod of the shock absorber moves violently, the rotational speed of the electric hydraulic pump can still be ensured not to be too high, and the rotational speed of the hydraulic motor pump is maintained within a controllable range.

[0007] To solve the above technical problem, the technical solution adopted by the invention is to provide an electric hydraulic pump integrated with a flow dividing valve, including a motor and a hydraulic pump connected to the motor. It is characterized in that the electric hydraulic pump further includes a flow dividing valve connected to the hydraulic pump, and the flow dividing valve includes:

[0008] The valve body has an axially penetrating first cavity, an axially penetrating second cavity, and a first shunt channel that communicates with the first cavity and the second cavity respectively. The first cavity and the second cavity are respectively connected to the hydraulic pump. The first shunt channel communicates with the first cavity through a first shunt port and communicates with the second cavity through a first liquid outlet port.

[0009] The first valve member is disposed in the first cavity and has an axially penetrating first damping hole. The first valve member has a first state of blocking the first shunt port and a second state of opening the first shunt port. The first valve member can be changed from the first state to the second state under the action of a sufficient large axial external force, and can be restored from the second state to the first state when the external force disappears or weakens.

[0010] In the electric hydraulic pump of the integrated shunt valve provided by the present invention, the first valve member includes a first valve core and a first elastic connecting member. The first valve core is axially movably inserted into the first cavity, and the first damping hole is axially penetrated in the first valve core. Two ends of the first elastic connecting member are respectively connected to the first valve core and the inner wall of the first cavity. The first valve core completely blocks the first shunt port when not affected by an external force or when the external force is weak, and the first elastic connecting member is used to apply an opposite acting force to the first valve core when the first valve core is subjected to an axial external force.

[0011] In the electric hydraulic pump of the integrated shunt valve provided by the present invention, the first cavity includes a first upper section with a smaller inner diameter and a first lower section with a larger inner diameter. The inner walls of the first upper section and the first lower section are connected by a first circular ring surface. The upper and lower ends of the first elastic connecting member are respectively connected to the first circular ring surface and the upper surface of the first valve core.

[0012] In the electric hydraulic pump of the integrated shunt valve provided by the present invention, the upper end opening of the first upper section is a first interface for connecting to the hydraulic pump, and the lower end opening of the first lower section is a first oil port for communicating with the shock absorber piston.

[0013] In the electric hydraulic pump of the integrated shunt valve provided by the present invention, the first valve core is in the shape of a flat circular ring, the first damping hole is disposed in the center of the first valve core, and the thickness of the first valve core is greater than or equal to the inner diameter of the first shunt port. When not affected by an external force or when the external force is weak, the circumferential outer surface of the first valve core completely covers the first shunt port.

[0014] In the electro-hydraulic pump of the integrated flow dividing valve provided by the present invention, the valve body further includes a second flow dividing channel respectively communicating with the first cavity and the second cavity. The second flow dividing channel communicates with the second cavity through a second flow dividing port and communicates with the first cavity through a second liquid outlet. The flow dividing valve further includes:

[0015] A second valve member, disposed in the second cavity and having an axially penetrating second damping hole; the second valve member has a third state of blocking the second flow dividing port and a fourth state of opening the second flow dividing port; the second valve member can be changed from the third state to the fourth state under the action of a sufficiently large axial external force, and can be restored from the fourth state to the third state when the external force disappears or weakens.

[0016] In the electro-hydraulic pump of the integrated flow dividing valve provided by the present invention, the second valve member includes a second valve core and a second elastic connecting member; the second valve core is axially movably plugged in the second cavity, and the second damping hole is axially penetrated in the second valve core; two ends of the second elastic connecting member are respectively connected to the second valve core and the inner wall of the second cavity; when the second valve core is not affected by an external force or the external force is weak, the circumferential outer surface of the second valve core completely blocks the second flow dividing port, and the second elastic connecting member is used to apply an opposite acting force to the second valve core when the second valve core is subjected to a sufficiently large axial external force.

[0017] In the electro-hydraulic pump of the integrated flow dividing valve provided by the present invention, the second cavity includes a second upper section with a smaller inner diameter and a second lower section with a larger inner diameter. The inner wall of the second upper section is connected to the inner wall of the second lower section through a second circular ring surface. The upper and lower ends of the second elastic connecting member are respectively connected to the second circular ring surface and the upper surface of the second valve core.

[0018] In the electro-hydraulic pump of the integrated flow dividing valve provided by the present invention, the upper end opening of the second upper section is a second interface for connecting with the hydraulic pump, and the lower end opening of the second lower section is a second oil port for communicating with a shock absorber piston.

[0019] In the electro-hydraulic pump of the integrated flow dividing valve provided by the present invention, the second valve core is in a flat circular ring shape, the second damping hole is disposed at the center of the first valve core, and the thickness of the second valve core is greater than or equal to the inner diameter of the second flow dividing port; when not affected by an external force or the external force is weak, the circumferential outer surface of the second valve core completely covers the second flow dividing port.

[0020] The electric hydraulic pump implementing the integrated flow dividing valve of the present invention can at least achieve the following beneficial effects: The electric hydraulic pump includes a motor and a hydraulic pump connected to the motor. The key lies in that the electric hydraulic pump further includes a flow dividing valve connected to the hydraulic pump. The flow dividing valve includes: a valve body having an axially penetrating first cavity, an axially penetrating second cavity, and a first flow dividing channel respectively communicating with the first cavity and the second cavity. The first cavity and the second cavity are respectively connected to the hydraulic pump. The first flow dividing channel communicates with the first cavity through a first flow dividing port and communicates with the second cavity through a first liquid outlet; a first valve member disposed in the first cavity and having an axially penetrating first damping hole; the first valve member has a first state of blocking the first flow dividing port and a second state of opening the first flow dividing port; the first valve member can be changed from the first state to the second state under the action of a sufficiently large axial external force, and can be restored from the second state to the first state when the external force disappears or weakens. Thus, when the pressure on both sides of the piston exceeds the control range, by integrating the flow dividing valve on the electric hydraulic pump, both the hydraulic pump and the motor are protected, and the shock absorber also maintains the performance of a passive shock absorber.

[0021] 2. The flow dividing valve is directly integrated in the electric hydraulic pump, which can ensure that the movable range (the piston rod stroke) of the piston rod of the shock absorber is not occupied, maintaining the existing shock absorber stroke, so that the piston rod can still maintain the original stroke. BRIEF DESCRIPTION OF THE DRAWINGS

[0022] In order to more clearly illustrate the technical solutions in the embodiments of the invention or the prior art, the following will briefly introduce the drawings required for the description of the embodiments or the prior art. Obviously, the drawings in the following description are only the embodiments of the invention. For those of ordinary skill in the art, without creative efforts, other drawings can also be obtained based on the provided drawings:

[0023] Figure 1 A three-dimensional schematic diagram of the electric hydraulic pump provided in this embodiment;

[0024] Figure 2 A three-dimensional schematic diagram of the valve body provided in this embodiment;

[0025] Figure 3 A top view schematic diagram of the valve body provided in this embodiment;

[0026] Figure 4 For Figure 3 A cross-sectional view taken along line A-A of the valve body in

[0027] Figure 5 For Figure 3 A cross-sectional view taken along line B-B of the valve body in

[0028] Figure 6 Top view schematic diagram of the flow dividing valve provided in this embodiment;

[0029] Figure 7 Bottom view schematic diagram of the flow dividing valve provided in this embodiment;

[0030] Figure 8 is Figure 6 Cross-sectional view taken along line A-A of the valve body in ;

[0031] Figure 9 is Figure 6 Cross-sectional view taken along line B-B of the valve body in ;

[0032] Figure 10 Connection diagram (I) of the electro-hydraulic pump provided in this embodiment;

[0033] Figure 11 Reference diagram (I) of the operating state of the electro-hydraulic pump provided in this embodiment;

[0034] Figure 12 Reference diagram (II) of the operating state of the electro-hydraulic pump provided in this embodiment;

[0035] Figure 13 Reference diagram (III) of the operating state of the electro-hydraulic pump provided in this embodiment;

[0036] Figure 14 Connection diagram (I) of the electro-hydraulic pump provided in this embodiment;

[0037] Figure 15 is the rotational speed comparison diagram of the electro-hydraulic pump with and without the flow dividing valve.

[0038] Explanation of the reference numerals in the specific embodiments:

[0039]

[0040] Specific embodiments

[0041] To facilitate the understanding of the invention, the invention will be described more comprehensively below with reference to the relevant drawings. The typical embodiments of the invention are given in the drawings. However, the invention can be implemented in many different forms and is not limited to the embodiments described herein. On the contrary, these embodiments are provided to make the disclosure of the invention more thorough and comprehensive.

[0042] Unless otherwise defined, all technical and scientific terms used herein have the same meaning as commonly understood by one of ordinary skill in the technical field to which this invention belongs. The terms used in the description of the invention herein are for the purpose of describing specific embodiments only and are not intended to limit the invention.

[0043] This embodiment provides an electro-hydraulic pump with an integrated flow-dividing valve. Refer to Figure 1 , Figure 1 which is a three-dimensional schematic diagram of the electro-hydraulic pump provided in this embodiment. As Figure 1 shown, the electro-hydraulic pump includes a motor 3, a hydraulic pump 2, and a flow-dividing valve 1. The hydraulic pump 2 is connected to the bottom of the motor 3, and the flow-dividing valve 1 is connected to the bottom of the hydraulic pump 2. The flow-dividing valve 1 includes a valve body 11, a first valve member 12, and a second valve member 13.

[0044] Refer to Figure 2 and Figure 3 , Figure 2 which is a three-dimensional schematic diagram of the valve body 11 provided in this embodiment, Figure 3 and Figure 2 which is a top view schematic diagram of the valve body 11 provided in this embodiment. As Figure 3 shown, the valve body 11 has an axially penetrating first cavity 111 and an axially penetrating second cavity 112. Refer to Figure 4 , Figure 4 which is a cross-sectional schematic diagram taken along line A-A of the valve body 11 in Figure 3 . As Figure 4 shown, the valve body 11 further includes a first flow-dividing channel 113 that communicates with the first cavity 111 and the second cavity 112 respectively. The first flow-dividing channel 113 communicates with the first cavity 111 through a first flow-dividing port 1131. At the same time, the first flow-dividing channel 113 communicates with the second cavity 112 through a first liquid outlet 1132. Refer to Figure 5 , Figure 5 which is a cross-sectional schematic diagram taken along line B-B of the valve body 11 in Figure 3 . As Figure 5 shown, the valve body 11 further includes a second flow-dividing channel 114 that communicates with the first cavity 111 and the second cavity 112 respectively. The second flow-dividing channel 114 communicates with the second cavity 112 through a second flow-dividing port 1141. At the same time, the second flow-dividing channel 114 communicates with the first cavity 111 through a second liquid outlet 1142.

[0045] The first valve member 12 is disposed within the first cavity 111 and has a first damping hole 1211 that axially penetrates therethrough. The first valve member 12 has a first state in which the first diversion port 1131 is blocked and a second state in which the first diversion port 1131 is opened; the first valve member 12 can be changed from the first state to the second state under the action of a sufficiently large axial external force, and can be restored from the second state to the first state when the external force disappears or weakens. Refer to Figure 6 and Figure 7 , Figure 6 is a top view schematic diagram of the diversion valve 1 provided in this embodiment, Figure 7 is a bottom view schematic diagram of the diversion valve 1 provided in this embodiment. As shown in Figure 6 and Figure 7 shown, the first valve member 12 is disposed within the first cavity 111. Refer to Figure 8 , Figure 8 is Figure 6 a cross-sectional schematic diagram taken along line A-A of the valve body 11 in Figure 7 shown. The first valve member 12 includes a first valve core 121 and a first elastic connecting member 122; the first valve core 121 is axially movably inserted into the first cavity 111, and the first damping hole 1211 is axially disposed through the first valve core 121; both ends of the first elastic connecting member 122 are respectively connected to the first valve core 121 and the inner wall of the first cavity 111; the first valve core 121 completely blocks the first diversion port 1131 when not subject to external force or when the external force is weak, and the first elastic connecting member 122 is configured to apply an opposite acting force to the first valve core 121 when the first valve core 121 is subject to an axial external force. The first cavity 111 includes a first upper section 1111 with a smaller inner diameter and a first lower section 1112 with a larger inner diameter. The inner walls of the first upper section 1111 and the first lower section 1112 are connected by a first circular ring surface 1113. The upper and lower ends of the first elastic connecting member 122 are respectively connected to the first circular ring surface 1113 and the upper surface of the first valve core 121. The upper end opening of the first upper section 1111 is a first interface 1114 connected to the first hydraulic port 21 of the hydraulic pump 2 (see Figures 11 - 13 ), and the lower end opening of the first lower section 1112 is a first oil port 1115 for communicating with the shock absorber piston. In this embodiment, the first elastic connecting member 122 is a straight spring. The first valve core 121 is in the shape of a flat circular ring, and the first damping hole 1211 is disposed at the center of the first valve core 121 (see Figure 6 and Figure 7), the thickness of the first spool 121 is greater than or equal to the inner diameter of the first diversion port 1131. When there is no external force or the external force is weak, the radial outer surface of the first spool 121 completely covers the first diversion port 1131. It is worth mentioning that, in order to ensure that the first spool 121 can accurately and stably stay in the initial position, that is, the position where the first diversion port 1131 can be completely blocked, when there is no external force or the external force is weak, a first limiting part 123 for supporting the bottom surface of the first spool 121 can also be installed in the first cavity 111. See Figure 8 , the first limiting part 123 includes a first cylindrical part 1231 and a first ring part 1232 connected to the first cylindrical part 1231. In Figure 8 , it can be seen that the inner diameters of the first cylindrical part 1231 and the first ring part 1232 are both greater than the inner diameter of the first damping hole 1211, so as not to block the oil passage. The first cylindrical part 1231 is inserted into the first cavity 111 from the first oil port 1115 of the first cavity 111 and abuts against the bottom surface of the first spool 121, thereby forming a limit on the first spool 121. The first ring part 1232 is fixedly connected to the bottom surface of the valve body 11. It should be understood that when there is no external force or the external force is weak, the first spool 121 can be supported and limited by the first limiting part 123, so that the first valve member 12 can be maintained in the first state. At this time, the radial outer surface of the first spool 121 completely covers the first diversion port 1131. When there is a large enough external axial force pressing the first spool 121 upward, the first elastic connecting piece 122 will undergo elastic deformation under the pressure transmitted by the first spool 121, that is, it will be compressed. The first spool 121 will then move upward axially in the first cavity 111. During the upward movement of the first spool 121, the first diversion port 1131 will gradually open. When the first spool 121 moves upward under the action of a large enough axial external force until it completely protrudes above the first diversion port 1131, the first diversion port 1131 is completely open. At this time, the first valve member 12 turns into the second state. When the external force acting on the first spool 121 disappears or weakens, the first spool 121 moves downward under the elastic force of the first elastic connecting piece 122 and returns to its original position. At this time, the first spool 121 completely covers the first diversion port 1131 again, that is, the first valve member 12 returns to the first state.

[0046] The second valve member 13 is disposed within the second cavity 112 and has an axially penetrating second damping hole 1311; the second valve member 13 has a third state of blocking the second diversion port 1141 and a fourth state of opening the second diversion port 1141; the second valve member 13 can be changed from the third state to the fourth state under the action of a sufficiently large axial external force, and can be restored from the fourth state to the third state when the external force disappears or weakens. See Figure 6 and Figure 7 , Figure 6 is a top view schematic diagram of the flow dividing valve 1 provided in this embodiment, Figure 7 is a bottom view schematic diagram of the flow dividing valve 1 provided in this embodiment. As shown in Figure 6 and Figure 7 , the second valve member 13 is disposed within the second cavity 112. See Figure 9 , Figure 9 is Figure 6 a cross-sectional schematic diagram taken along line B-B of the valve body 11 in Figure 9 . As shown in Figures 11 - 13 , the second valve member 13 includes a second valve core 131 and a second elastic connecting member 132; the second valve core 131 is axially movably plugged within the second cavity 112, and the second damping hole 1311 is axially penetrated through the second valve core 131; two ends of the second elastic connecting member 132 are respectively connected to the second valve core 131 and the inner wall of the second cavity 112; when the second valve core 131 is not subject to external force or the external force is weak, the circumferential outer surface of the second valve core 131 completely blocks the second diversion port 1141, and the second elastic connecting member 132 is configured to apply an opposite acting force to the second valve core 131 when the second valve core 131 is subject to an axial external force. The second cavity 112 includes a second upper section 1121 with a smaller inner diameter and a second lower section 1122 with a larger inner diameter. The inner wall of the second upper section 1121 is connected to the inner wall of the second lower section 1122 through a second toroidal surface 1123. The upper and lower ends of the second elastic connecting member 132 are respectively connected to the second toroidal surface 1123 and the upper surface of the second valve core 131. The upper end opening of the second upper section 1121 is a second interface 1124 connected to the second hydraulic port 22 of the hydraulic pump 2 (see Figure 6 and Figure 7), the thickness of the second spool 131 is greater than or equal to the inner diameter of the second diversion port 1141; when no external force or a weak external force is applied, the outer circumferential surface of the second spool 131 completely covers the second diversion port 1141. It is worth mentioning that in order to ensure that the second spool 131 can accurately and stably maintain its initial position, that is, the position where the second diversion port 1141 can be completely blocked, when no external force or a weak external force is applied, a second limiting part 133 for supporting the bottom surface of the second spool 131 can also be installed in the second cavity 112. See Figure 8 , the second limiting part 133 includes a second cylindrical part 1331 and a second ring part 1332 connected to the second cylindrical part 1331. In Figure 8 it can be seen that the inner diameters of both the second cylindrical part 1331 and the second ring part 1332 are greater than the inner diameter of the second damping hole 1311 to avoid obstructing the oil path. The second cylindrical part 1331 is inserted into the second cavity 112 from the second oil port 1125 of the second cavity 112 and abuts against the bottom surface of the second spool 131, thereby forming a limit for the second spool 131. The second ring part 1332 is fixedly connected to the bottom surface of the valve body 11. It should be understood that when no external force or a weak external force is applied, the second spool 131 can be supported and limited by the second limiting part 133, so that the second valve member 13 can be maintained in the third state. At this time, the outer circumferential surface of the second spool 131 completely covers the second diversion port 1141. When there is a sufficiently large external axial force pressing the second spool 131 upward, the second elastic connecting member 132 will undergo elastic deformation under the pressure transmitted by the second spool 131, that is, it will be compressed. The second spool 131 will then move upward axially in the second cavity 112. During the upward movement of the second spool 131, the second diversion port 1141 will gradually open. When the second spool 131 moves upward to a position completely higher than the second diversion port 1141 under the action of a sufficiently large axial external force, the second diversion port 1141 is completely open. At this time, the second valve member 13 changes to the fourth state. When the external force acting on the second spool 131 disappears or weakens, the second spool 131 moves downward under the elastic force of the second elastic connecting member 132 and returns to its original position. At this time, the second spool 131 completely covers the second diversion port 1141 again, that is, the second valve member 13 returns to the third state.

[0047] The operating principle of the electric hydraulic pump is introduced below. Here, the first oil port 1115 of the flow dividing valve 1 is connected to the compression chamber of the shock absorber according to the connection method as Figure 10 shown.

[0048] SeeFigure 11 , Figure 11 is a reference diagram (I) of the operating state of the electro-hydraulic pump provided in this embodiment. When the shock absorber piston moves and causes the hydraulic oil to flow into the electro-hydraulic pump through the first oil port 1115 of the flow dividing valve 1, during the process of the hydraulic oil flowing through the first damping hole 1211, a pressure difference will be formed at both ends of the first damping hole 1211, thereby forming a pressure in the axial direction of the first valve core 121. When the pressure is less than or equal to the pre-tightening force of the first elastic connecting member 122, the first valve core 121 will not move, and all the hydraulic oil flowing in through the first oil port 1115 will flow into the hydraulic pump 2 through the first damping hole 1211 (as shown by the solid arrows in Figure 11 ), and at this time, the pump speed of the hydraulic motor 3 is proportional to the piston movement speed.

[0049] Refer to Figure 12 , Figure 12 is a reference diagram (II) of the operating state of the electro-hydraulic pump provided in this embodiment. When the movement of the shock absorber piston rod gradually intensifies, the pressure difference generated when the hydraulic oil flowing in through the first oil port 1115 flows through the first damping hole 1211 increases, so that when the pressure acting in the axial direction of the first valve core 121 is greater than the pre-tightening force of the first elastic connecting member 122, the first valve core 121 begins to move upward. At this time, the first flow dividing port 1131 gradually opens. The hydraulic oil flowing in through the first oil port 1115 is divided into two parts, where: one part flows through the first damping hole 1211 and then flows into the hydraulic pump 2 from the first interface 1114, then flows into the second cavity 112 from the second interface 1124, and flows out of the electro-hydraulic pump through the second oil port 1125 (as shown by the solid arrows in Figure 12 ); the other part flows into the first flow dividing channel 113 from the first flow dividing port 1131, and flows into the second cavity 112 from the first liquid outlet 1132 of the first flow dividing channel 113, and then flows out of the electro-hydraulic pump through the second oil port 1125 (as shown by the solid and dashed arrows in Figure 12 ). It should be understood that as the speed of the piston rod increases, the pressure difference generated when the hydraulic oil flowing in through the first oil port 1115 flows through the first damping hole 1211 further increases, the first valve core 121 moves further upward, and the opening degree of the first flow dividing port 1131 becomes larger and larger, thereby increasing the flow dividing ability of the first flow dividing channel 113, so that the pump speed of the hydraulic motor 3 can still remain constant when the movement of its piston rod gradually intensifies.

[0050] Refer to Figure 13 , Figure 13Reference diagram (III) of the operating state of the electro-hydraulic pump provided in this embodiment. When the oil fluid velocity continues to increase, the pressure difference of the oil fluid flowing through the first damping hole 1211 on the first spool valve 121 continues to increase. The first spool valve 121 moves upward to the limit position, causing the first diversion port 1131 to be fully opened, and the diversion capacity of the first diversion channel 113 reaches the maximum. Similarly, the oil fluid flowing in from the first oil port 1115 is divided into two parts, where: one part flows into the hydraulic pump 2 from the first interface 1114 after passing through the first damping hole 1211, then flows into the second cavity 112 from the second interface 1124, and flows out of the electro-hydraulic pump through the second oil port 1125 (as shown by the solid arrow in Figure 13 ); the other part flows into the first diversion channel 113 from the first diversion port 1131, and flows into the second cavity 112 from the first liquid outlet 1132 of the first diversion channel 113, and then flows out of the electro-hydraulic pump through the second oil port 1125 (as shown by the solid and dashed arrow in Figure 13 ).

[0051] It should be understood that by connecting the second oil port 1125 of the diversion valve 1 to the compression chamber of the shock absorber in the connection manner shown in Figure 14 , the diversion valve 1 can also play a role in diverting the oil fluid through the second diversion channel 114 and the second valve member. The specific principle is similar to the above, and will not be elaborated here.

[0052] To further verify the beneficial effects of the electro-hydraulic pump provided in this embodiment, we conducted a comparative test on the electro-hydraulic pump provided in this embodiment with and without the diversion valve 1. Refer to Figure 15 , Figure 15 which is the comparison diagram of the rotational speed of the electro-hydraulic pump with and without the diversion valve 1. After the electro-hydraulic pump is connected to the shock absorber, when the piston rod is moving, the electro-hydraulic pump will rotate. When there is a diversion valve 1, when the electro-hydraulic pump reaches a certain rotational speed, the diversion valve 1 gradually comes into play to ensure that the rotational speed of the electro-hydraulic pump will not be too high.

[0053] The embodiments of the invention have been described above in conjunction with the accompanying drawings. However, the invention is not limited to the above specific embodiments. The above specific embodiments are merely illustrative and not restrictive. Under the inspiration of the invention, those of ordinary skill in the art can also make many forms without departing from the spirit of the invention and the scope protected by the claims. All of these fall within the protection scope of the invention.

Claims

1. An electro-hydraulic pump with an integrated flow-dividing valve, comprising a motor (3) and a hydraulic pump (2) connected to the motor (3), characterized in that, The electric hydraulic pump further includes a flow dividing valve (1) connected to the hydraulic pump (2), and the flow dividing valve (1) includes: A valve body (11) having an axially penetrating first cavity (111), an axially penetrating second cavity (112), and a first flow dividing channel (113) communicating with the first cavity (111) and the second cavity (112) respectively. The first cavity (111) and the second cavity (112) are respectively communicated with the hydraulic pump (2). The first flow dividing channel (113) is communicated with the first cavity (111) through a first flow dividing port (1131) and is communicated with the second cavity (112) through a first liquid outlet (1132); A first valve member (12) disposed in the first cavity (111) and having an axially penetrating first damping hole (1211); the first valve member (12) has a first state of blocking the first flow dividing port (1131) and a second state of opening the first flow dividing port (1131); the first valve member (12) can be changed from the first state to the second state under the action of a sufficiently large axial external force, and can be restored from the second state to the first state when the external force disappears or weakens; The first valve member (12) includes a first valve core (121) and a first elastic connecting member (122); the first elastic connecting member (122) is a straight spring; the first valve core (121) is axially movably inserted into the first cavity (111), and the first damping hole (1211) is axially penetrated in the first valve core (121); both ends of the first elastic connecting member (122) are respectively connected to the first valve core (121) and the inner wall of the first cavity (111); the first valve core (121) completely blocks the first flow dividing port (1131) when not subjected to external force or when the external force is weak, and the first elastic connecting member (122) is used to apply an opposite acting force to the first valve core (121) when the first valve core (121) is subjected to an axial external force; When the pressure acting in the axial direction of the first valve core (121) is less than or equal to the pre-tightening force of the first elastic connecting member (122), the first valve core (121) will not move, and all the oil fluid flows into the hydraulic pump (2) through the first damping hole (1211), and the pump speed of the hydraulic pump (2) is proportional to the piston movement speed; When the pressure acting in the axial direction of the first spool (121) is greater than the pre-tightening force of the first elastic connecting member (122), the first spool (121) starts to move upward, and the first diversion port (1131) gradually opens; the hydraulic oil is divided into two parts, where: one part flows into the hydraulic pump (2) after passing through the first damping hole (1211), then flows into the second cavity (112), and then flows out of the electro-hydraulic pump; the other part flows into the first diversion channel (113) from the first diversion port (1131), and flows into the second cavity (112) from the first liquid outlet (1132) of the first diversion channel (113), and then flows out of the electro-hydraulic pump; as the speed of the piston rod increases, the pressure difference generated when the inflowing hydraulic oil passes through the first damping hole (1211) further increases, the first spool (121) moves further upward, and the opening degree of the first diversion port (1131) becomes larger and larger, increasing the diversion ability of the first diversion channel (113), so that the pump speed of the hydraulic pump (2) can remain constant even when the movement of the piston rod gradually intensifies.

2. The electro-hydraulic pump of the integrated flow dividing valve according to claim 1, characterized in that, The first cavity (111) includes a first upper section (1111) with a smaller inner diameter and a first lower section (1112) with a larger inner diameter. The inner wall of the first upper section (1111) is connected to the inner wall of the first lower section (1112) through a first circular ring surface (1113). The upper and lower ends of the first elastic connecting member (122) are respectively connected to the first circular ring surface (1113) and the upper surface of the first spool (121).

3. The electric hydraulic pump of the integrated flow dividing valve according to claim 2, characterized in that, The upper end opening of the first upper section (1111) is a first interface (1114) connected to the hydraulic pump (2), and the lower end opening of the first lower section (1112) is a first oil port (1115) for communicating with the shock absorber piston.

4. The electro-hydraulic pump of the integrated flow dividing valve according to claim 1, wherein The first spool (121) is in the shape of a flat circular ring. The first damping hole (1211) is provided in the center of the first spool (121). The thickness of the first spool (121) is greater than or equal to the inner diameter of the first diversion port (1131); when there is no external force or the external force is weak, the outer circumferential surface of the first spool (121) completely covers the first diversion port (1131).

5. The electro-hydraulic pump of the integrated flow dividing valve according to any one of claims 1-4, characterized in that, The valve body (11) further includes a second diversion channel (114) respectively communicating with the first cavity (111) and the second cavity (112). The second diversion channel (114) communicates with the second cavity (112) through a second diversion port (1141) and communicates with the first cavity (111) through a second liquid outlet (1142); the diversion valve (1) further includes: A second valve member (13) is disposed within the second cavity (112) and has a second damping hole (1311) that axially penetrates therethrough; the second valve member (13) has a third state in which the second diversion port (1141) is blocked and a fourth state in which the second diversion port (1141) is opened; the second valve member (13) can be changed from the third state to the fourth state under the action of a sufficiently large axial external force, and can be restored from the fourth state to the third state when the external force disappears or weakens.

6. The electro-hydraulic pump of the integrated flow dividing valve according to claim 5, characterized in that, The second valve member (13) includes a second valve core (131) and a second elastic connecting member (132); the second valve core (131) is axially movably plugged within the second cavity (112), and the second damping hole (1311) is axially disposed through the second valve core (131); both ends of the second elastic connecting member (132) are respectively connected to the second valve core (131) and the inner wall of the second cavity (112); the outer circumferential surface of the second valve core (131) completely blocks the second diversion port (1141) when the second valve core (131) is not subject to external force or the external force is weak, and the second elastic connecting member (132) is used to apply an opposite acting force to the second valve core (131) when the second valve core (131) is subject to an axial external force.

7. The electro-hydraulic pump of the integrated flow splitting valve according to claim 6, characterized in that, The second cavity (112) includes a second upper section (1121) with a smaller inner diameter and a second lower section (1122) with a larger inner diameter. The inner walls of the second upper section (1121) and the second lower section (1122) are connected by a second annular surface (1123). The upper and lower ends of the second elastic connecting member (132) are respectively connected to the second annular surface (1123) and the upper surface of the second valve core (131).

8. The electric hydraulic pump of the integrated flow dividing valve according to claim 7, characterized in that, The upper end opening of the second upper section (1121) is a second interface (1124) connected to the hydraulic pump (2), and the lower end opening of the second lower section (1122) is a second oil port (1125) for communicating with the shock absorber piston.

9. The electro-hydraulic pump of the integrated flow dividing valve according to claim 6, characterized in that, The second valve core (131) is in the shape of a flat circular ring. The second damping hole (1311) is disposed at the center of the first valve core (121). The thickness of the second valve core (131) is greater than or equal to the inner diameter of the second diversion port (1141); when not subject to external force or the external force is weak, the outer circumferential surface of the second valve core (131) completely covers the second diversion port (1141).

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