Damping system, suspension system and vehicle

Abstract

A damping system, a suspension system and a vehicle. The damping system is configured to adjust a flow damping or a damping coefficient between a first device and a second device.

Description

Damping system, suspension system and vehicle

[0001] This application claims priority to Chinese patent application No. 202411982578.1, filed on December 27, 2024; Chinese patent application No. 202411997894.6, filed on December 31, 2024; Chinese patent application No. 202411875672.7, filed on December 18, 2024; and Chinese patent application No. 202423155028.0, filed on December 18, 2024, the entire contents of which are incorporated herein by reference. Technical Field

[0002] This disclosure relates to the field of vehicle technology, and more particularly to a damping system, a suspension system, and a vehicle. Background Technology

[0003] The vehicle is equipped with a damping system, which is used to regulate the vehicle's dynamics and reduce vibrations and bumps during driving. Summary of the Invention

[0004] In a first aspect, a damping system is provided, the damping system being configured to adjust the flow damping or damping coefficient between a first device and a second device.

[0005] Secondly, a damping system is provided, the damping system comprising a one-way valve seat, or a one-way valve, or a valve assembly.

[0006] Thirdly, a suspension system is provided, the suspension system including the aforementioned damping system, or a gear pump, the suspension system being configured to transmit forces and torques to support the vehicle body.

[0007] Fourthly, a vehicle is provided, the vehicle including the aforementioned damping system or suspension system. Attached Figure Description

[0008] Figure 1 is a schematic diagram of a vehicle according to some embodiments;

[0009] Figure 2 is a cross-sectional view of the valve body device in the vehicle shown in Figure 1;

[0010] Figure 3 is a structural diagram of the base in the valve body device shown in Figure 2;

[0011] Figure 4 is a top view of the base shown in Figure 3;

[0012] Figure 5 is a cross-sectional view along line AA in Figure 4;

[0013] Figure 6 is a bottom view of the base shown in Figure 3;

[0014] Figure 7 is a left view of the base shown in Figure 3;

[0015] Figure 8 is a right view of the base shown in Figure 3;

[0016] Figure 9 is a cross-sectional view of a portion of the valve body assembly in the valve body device shown in Figure 2.

[0017] Figure 10 is a cross-sectional view of the first damping valve section in a state where the oil flows from the first connection to the second connection as shown in Figure 2.

[0018] Figure 11 is a cross-sectional view of the first damping valve section in another state, as shown in Figure 2, where the oil flows from the first connection to the second connection.

[0019] Figure 12 is a cross-sectional view of the first damping valve section in another state as shown in Figure 2, where the oil flows from the first connection to the second connection.

[0020] Figure 13 is a cross-sectional view of the second damping valve section in a state where the oil flows from the second connection to the first connection as shown in Figure 2.

[0021] Figure 14 is a cross-sectional view of the second damping valve section in Figure 2, where the oil flows from the second connection to the first connection in another state.

[0022] Figure 15 is a cross-sectional view of the second damping valve section in Figure 2, showing the oil flowing from the second connection to the first connection in another state.

[0023] Figure 16 is a structural diagram of a one-way valve seat according to some embodiments;

[0024] Figure 17 is a cross-sectional view of a valve assembly according to some embodiments;

[0025] Figure 18 is a cross-sectional view of a damping controller according to some embodiments;

[0026] Figure 19 is a schematic diagram of the first channel in a damping controller according to some embodiments;

[0027] Figure 20 is a schematic diagram of the second channel in a damping controller according to some embodiments;

[0028] Figure 21 is a cross-sectional view of a valve device in a first state according to some embodiments;

[0029] Figure 22 is a cross-sectional view of the valve device shown in Figure 21 in the second state;

[0030] Figure 23 is a perspective view of the pilot valve plug of the valve device shown in Figure 21;

[0031] Figure 24 is a cross-sectional view of the pilot valve plug of the valve device shown in Figure 21;

[0032] Figure 25 is a cross-sectional view of the valve device in a first state according to some embodiments;

[0033] Figure 26 is a cross-sectional view of the valve device shown in Figure 25 in the second state;

[0034] Figure 27 is a perspective view of the pilot valve plug of the valve device shown in Figure 25;

[0035] Figure 28 is a cross-sectional view of the pilot valve plug of the valve device shown in Figure 25;

[0036] Figure 29 is a perspective view of a first elastic member according to some embodiments;

[0037] Figure 30 is a cross-sectional view of a first valve assembly according to some embodiments;

[0038] Figure 31 is a cross-sectional view of a damping controller according to some embodiments;

[0039] Figure 32 is a schematic diagram of the flow path in the damping controller when the first and second valve devices are not energized and the piston rod of the damper returns to its original state, according to some embodiments.

[0040] Figure 33 is a schematic diagram of the flow path in the damping controller when the first and second valve devices are not energized and the piston rod of the damper is compressed, according to some embodiments.

[0041] Figure 34 is a schematic diagram of the flow path in the damping controller when the first valve device and the second valve device are energized and the piston rod of the damper returns to its original position according to some embodiments.

[0042] Figure 35 is a schematic diagram of another flow path in the damping controller when the first valve device and the second valve device are energized and the piston rod of the damper returns to its original position according to some embodiments.

[0043] Figure 36 is a schematic diagram of the flow path within the damping controller when the first and second valve devices are energized and the piston rod of the damper is compressed, according to some embodiments.

[0044] Figure 37 is a schematic diagram of another flow path in the damping controller when the first valve device and the second valve device are energized and the piston rod of the damper is compressed, according to some embodiments.

[0045] Figure 38 is a block diagram of a suspension damping control system according to some embodiments;

[0046] Figure 39 is a block diagram of a vehicle according to some embodiments;

[0047] Figure 40 is an exploded view of a gear pump according to some embodiments;

[0048] Figure 41 is a schematic diagram of the bushing of a gear pump according to some embodiments;

[0049] Figure 42 is a schematic diagram of the bushing of a gear pump according to some embodiments from another angle;

[0050] Figure 43 is a bottom view of the bushing of a gear pump according to some embodiments;

[0051] Figure 44 is an assembly diagram of the second gear and the second gear shaft of a gear pump according to some embodiments;

[0052] Figure 45 is an assembly bottom view of the second gear and the second gear shaft of a gear pump according to some embodiments;

[0053] Figure 46 is an assembly bottom view of the first and second gears of a gear pump according to some embodiments;

[0054] Figure 47 is an assembly top view of the first and second gears of a gear pump according to some embodiments;

[0055] Figure 48 is an internal schematic diagram of a gear pump according to some embodiments;

[0056] Figure 49 is a cross-sectional view of a gear pump according to some embodiments;

[0057] Figure 50 is an assembly diagram of the shaft sleeve and the second pump body of a gear pump according to some embodiments;

[0058] Figure 51 is a cross-sectional view of the second pump body of a gear pump according to some embodiments.

[0059] Reference numerals: 1A, vehicle; 11A, body; 12A, wheel; 100, base; 110, first connecting part; 120, second connecting part; 130, third connecting part; 140, fourth connecting part; 200, valve body assembly; 210, damping valve assembly; 211. First damping valve section; 2111, first base; A1, first opening; 2112, first switch assembly; B1, first one-way component; B2, first channel; B3, first movable component; B31, first part; B32, second part; 212, second damping valve section; 2121, second base; C1, second opening; 2122, second switch assembly; D1, second one-way component; D2, second channel; D3, second movable component; D31, third part; D32, fourth part; 220, first one-way valve section; 221, first connecting seat; 222, first valve body; 230, second one-way valve section; 231, second connecting seat; 232, second valve body; 1B, Check valve seat; 2B, Sealing surface; 21B, Body; 22B, Sealing part; 23B, Connecting part; 24B, Groove; 3B, First check valve passage; 4B, Check valve through hole; 5B, First check valve plate; 6B, Check valve body; 7B, Second check valve plate; 8B, Second check valve passage; 9, Elastic element; 10, Valve assembly; 11B, Control assembly; 12B, First valve; 13B, Push rod; 14B, Housing; 15B, First connecting cavity; 16, Second connecting cavity; 17, Third connecting cavity; 18, Vibration damper; 19, Central control cylinder; 20, Stiffness conversion valve; 25B, Check valve; 26, First channel; 27, Second channel; 28, First sub-channel; 29, Second sub-channel; 30, First valve body; 31, First valve seat; 32, Guide sleeve; 33, Damping controller;34. Pilot valve assembly 10C, first valve assembly 10a, second valve assembly 10b, first valve component 1C, first valve body 11C, pilot channel 111C, Axial channel 1111, radial channel 1112, first valve hole 112C, first valve seat 12C, receiving cavity 13C, second elastic element 14C, first sealing ring 15C, pilot valve plug 2C, valve plug body 21, push rod guide surface 211C, elastic element guide surface 212C, elastic element abutment surface 213, sealing surface 2B14, valve plug skirt 22C, push rod groove 23C, first elastic element 3C, push rod 4C, base valve seat 5C, base valve hole 51, first chamber 52, valve shell 6C, medium outlet 61, valve channel 62, protruding structure 63, pressure relief chamber 64, second valve assembly 7C, second valve body 71, second valve seat 711, first channel 7111, second valve body 712, second channel 7121 The components include: third channel 7122, second chamber 713, first valve plate 72, second valve plate 73, third elastic element 74, drive assembly 8C, coil 81, magnetic core 82, fourth elastic element 83, fifth elastic element 84, inner shell 851, outer shell 852, first guide sleeve 861, second guide sleeve 862, locking sleeve 87, iron core cover 88, magnetic isolation ring 89; damping controller 100C, first cavity 101, second cavity 102, third cavity 103, fourth cavity 104, fifth cavity 105, central control cylinder interface 106, stiffness conversion valve interface 107, shock absorber interface 108, accumulator interface 109, controller body 110C; suspension damping control system 1000; vehicle 10000; 100. Gear pump; 1. Pump body; 11. First pump body; 111. First mounting groove; 112. Groove; 12. Second pump body; 121. Second mounting groove; 1211. Fifth fillet; 1213. First side wall; 1214. Second side wall; 122. Third mounting groove; 13. Mounting space; 14. First cavity; 15. Second cavity; 2. Gear set; 21. First gear; 22. Second gear; 23. First gear shaft; 24. Second gear shaft; 25. Bushing; 251. First bushing portion; 252. Second bushing portion; 253. First unloading groove; 2531. First fillet; 254. Second unloading groove; 2541. Second fillet; 255. Third fillet; 256. Fourth fillet; 3. Retaining ring; 4. First sealing ring; 5. Second sealing ring; 6. Filter element; 7. Positioning post; 8. Fastener. Detailed Implementation

[0060] The technical solutions of the embodiments of this disclosure will be clearly and completely described below with reference to the accompanying drawings. Obviously, the described embodiments are only some embodiments of this disclosure, and not all embodiments. Based on the embodiments of this disclosure, all other embodiments obtained by those of ordinary skill in the art without creative effort are within the scope of protection of this disclosure.

[0061] The terms "first" and "second" are used for descriptive purposes only and should not be construed as indicating or implying relative importance or implicitly specifying the number of technical features indicated. Thus, a feature defined as "first" or "second" may explicitly or implicitly include one or more of that feature. In the description of this disclosure, unless otherwise stated, "a plurality of" means two or more.

[0062] In the description of this disclosure, it should be noted that, unless otherwise expressly specified and limited, the terms "installation," "connection," "linking," and "communication" should be interpreted broadly. For example, they can refer to a fixed connection, a detachable connection, or an integral connection. They can refer to a direct connection or an indirect connection through an intermediate medium, or a connection within two components. Those skilled in the art can understand the specific meaning of the above terms in this disclosure according to the specific circumstances.

[0063] In embodiments of this disclosure, the terms "comprising," "including," or any other variations thereof are intended to cover a non-exclusive inclusion, such that a process, article, or apparatus that comprises a list of elements includes not only those elements but also other elements not expressly listed, or elements inherent to such a process, article, or apparatus. Without further limitation, an element defined by the phrase "comprising one..." does not exclude the presence of other identical elements in the process, article, or apparatus that includes that element.

[0064] In this disclosure, the terms "exemplary" or "for example" are used to indicate that something is an example, illustration, or illustration. Any embodiment or design described as "exemplary" or "for example" in this disclosure should not be construed as being more preferred or advantageous than other embodiments or designs. Rather, the use of terms such as "exemplary" or "for example" is intended to present the relevant concepts in a specific manner.

[0065] In the description of this specification, specific features, structures, materials, or characteristics may be combined in any suitable manner in one or more embodiments or examples.

[0066] In related technologies, the damping control precision of the valve device in the damping system is low, which cannot guarantee the stability of the vehicle during movement.

[0067] To address the aforementioned problems, some embodiments of this disclosure provide a vehicle 1A, which can be a pure electric vehicle 1A, a hybrid electric vehicle 1A, a plug-in hybrid electric vehicle 1A, a range-extended electric vehicle 1A, a gasoline-powered vehicle, etc. Vehicle 1A can also be a sedan, truck, bus, lorry, trailer, etc.

[0068] Referring to Figure 1, vehicle 1A includes a body 11A and wheels 12A. The body 11A is used for passengers to ride in and for carrying goods. The wheels 12A are installed under the body 11A to support the body 11A and are able to roll on the road surface so that vehicle 1A can move.

[0069] A damping system is connected between the body 11A and the wheel 12A. The damping system includes a hydraulic shock absorber, a valve device, and an oil reservoir. The damping system is connected between the body 11A and the wheel 12A through the hydraulic shock absorber. The hydraulic shock absorber, valve device, and oil reservoir are filled with oil.

[0070] When wheel 12A moves upward, the piston of the hydraulic damper moves downward, driving oil from the hydraulic damper through the valve device into the oil reservoir. During the flow of the oil, the oil is damped by the valve device, which buffers the mechanical force of the wheel 12A moving upward. When wheel 12A moves downward, the piston of the hydraulic damper moves upward, driving oil from the oil reservoir through the valve device into the hydraulic damper. During the flow of the oil, the oil is damped by the valve device, which buffers the mechanical force of the wheel 12A moving downward.

[0071] However, in related technologies, the damping control precision of valve devices is low, which cannot guarantee the stability of vehicle 1A during movement.

[0072] To address the aforementioned problems, some embodiments of this disclosure also provide a valve device, which is described below.

[0073] Referring to Figures 2 to 9, some embodiments of this disclosure provide a valve device, including a base 100 and a valve body assembly 200. The base 100 includes a first connecting portion 110 and a second connecting portion 120. The first connecting portion 110 is adapted to connect a first module, and the second connecting portion 120 is adapted to connect a second module. The valve body assembly 200 is disposed on the base 100 and located between the first connecting portion 110 and the second connecting portion 120, and is capable of adjusting the damping coefficients of oil flowing from the first connecting portion 110 to the second connecting portion 120 and from the second connecting portion 120 to the first connecting portion 110, respectively.

[0074] When wheel 12A moves upward, the piston inside the hydraulic shock absorber moves downward. The oil inside the first module passes through the valve body assembly 200 from the first connecting part 110 to the second connecting part 120 and enters the second module. During the process of the oil moving from the first module through the first connecting part 110, the valve body assembly 200, and the second connecting part 120 to the second module, the piston movement of the first module is converted into the energy stored inside the oil. During the movement of the oil, the stored energy is converted into heat energy, etc., thereby absorbing the energy of the upward movement of wheel 12A.

[0075] When wheel 12A moves upward, the piston inside the first module moves upward, and the oil inside the second module flows from the second connecting part 120 through the valve body assembly 200 to the first connecting part 110 and enters the hydraulic damper. During the process of the oil flowing from the inside of the first module through the second connecting part 120, the valve body assembly 200, and the first connecting part 110 to the first module, the piston movement of the first module is converted into the energy stored inside the oil. During the movement of the oil, the energy stored inside is converted into heat energy, etc., thereby absorbing the energy of wheel 12A moving downward.

[0076] In some embodiments, the first module includes a hydraulic damper, which includes, but is not limited to, a monotube damper, a twin-tube damper, etc. The second module includes an oil reservoir.

[0077] This disclosure provides a valve device in some embodiments. By including a base 100 and a valve body assembly 200, the damping coefficient of oil flowing from the first connecting part 110 to the second connecting part 120 can be adjusted independently. This means the damping coefficient of oil flowing from the first module to the second module within the valve device can be adjusted independently, as can the damping coefficient of oil flowing from the second connecting part 120 to the first connecting part 110, and vice versa. This allows for independent control of the damping coefficients of oil in both directions, improving the control accuracy of the valve device's damping coefficient and enhancing the reliability of the valve device's vibration damping effect.

[0078] In some embodiments, the valve body assembly 200 includes a damping valve assembly 210, which is adapted to adjust the damping coefficient of oil flowing from the first connection portion 110 to the second connection portion 120, and to adjust the damping coefficient of oil flowing from the second connection portion 120 to the first connection portion 110.

[0079] The structure of the damping valve assembly 210 may also include a drive structure and two output terminals. The drive structure is connected to both output terminals, and different states of the two output terminals can be set through a single drive structure.

[0080] Some embodiments of this disclosure provide a valve device that, through the arrangement of a damping valve assembly 210, facilitates the adjustment of the damping coefficient in different directions.

[0081] In some embodiments, the damping valve assembly 210 includes a first damping valve portion 211 and a second damping valve portion 212. The first damping valve portion 211 is adapted to regulate the damping force of the oil flowing from the first connection portion 110 to the second connection portion 120, and the second damping valve portion 212 is adapted to regulate the damping coefficient of the oil flowing from the second connection portion 120 to the first connection portion 110.

[0082] This disclosure provides a valve device in some embodiments. By configuring a damping valve assembly 210 including a first damping valve section 211 and a second damping valve section 212, it is possible to adjust the damping coefficient of oil flowing from the first connecting part 110 to the second connecting part 120, and to adjust the damping coefficient of oil flowing from the second connecting part 120 to the first connecting part 110. Furthermore, the configuration of the first damping valve section 211 and the second damping valve section 212 facilitates the disassembly, assembly, and maintenance of the valve device.

[0083] In some embodiments, the first damping valve portion 211 includes a first base 2111 and a first switch assembly 2112. The first base 2111 is disposed on the base 100 and surrounds to form a first inner cavity, which communicates with the first connecting portion 110 and the second connecting portion 120. The first switch assembly 2112 is installed in the first inner cavity and is adapted to adjust the damping coefficient of the oil flowing in the first inner cavity.

[0084] This disclosure provides a valve device in some embodiments, which, through the arrangement of a first base 2111 and a first switch assembly 2112, can adjust the damping force of oil flowing in the first inner cavity through the first switch assembly 2112, and the structure is simple and compact.

[0085] In some embodiments, the first switch assembly 2112 includes a first channel B2, the two ends of which are connected to the first connecting portion 110 and the second connecting portion 120. The first switch assembly 2112 includes a first movable member B3, which has an open state and a closed state. In the open state, the first movable member B3 is separated from the first base 2111, and oil can flow through the gap between the first movable member B3 and the first base 2111 to flow from the first connecting portion 110 to the second connecting portion 120. The damping coefficient of the first switch assembly 2112 is N1. In the closed state, the first movable member B3 is in contact with the first base 2111, and the damping coefficient of the first switch assembly 2112 is N2. Oil can flow through the first channel B2 to flow from the first connecting portion 110 to the second connecting portion 120. N1 is less than N2.

[0086] Some embodiments of this disclosure provide a valve device that, through the above-described configuration, allows for setting the damping coefficient of the first switching assembly 2112, and the damping coefficient can be adjusted by the state of the first moving member B3, thereby enabling buffering of vehicle 1A under different conditions and improving the shock resistance of vehicle 1A.

[0087] In some embodiments, the first switch assembly 2112 includes a first channel B2, the two ends of which are connected to the first connecting portion 110 and the second connecting portion 120. The first switch assembly 2112 includes a first movable member B3, and the first base 2111 includes a first opening A1. The first movable member B3 includes an energized state and an de-energized state. In the de-energized state, the oil flowing out of the first connecting portion 110 reaches the first opening A1, and the damping force overcome by the oil is M1. The energized state includes a first state and a second state. In the first state, the oil flowing out of the first connecting portion 110 flows through the first channel B2, and the damping force overcome by the oil is M2. In the second state, the oil flowing out of the first connecting portion 110 reaches the first opening A1, and the damping force overcome by the oil is M3. M3 is greater than M2, and M2 is greater than M1.

[0088] Some embodiments of this disclosure provide a valve device in which the damping force overcome by the oil can be adjusted by setting the state of the first movable member B3. If the oil flow rate is high, the first movable member B3 can be set to an energized state, which can effectively achieve a buffering effect. If the oil flow rate is low, the first movable member B3 can be set to an de-energized state, which can achieve both a buffering effect and reduce energy consumption.

[0089] In some embodiments, the first movable member includes a first portion B31 and a second portion B32. The first portion B31 is mounted on the first base 2111, and one end of the second portion B32 abuts against the first base 2111, while the other end abuts against the first portion B31 and has a degree of freedom of movement relative to the first portion B31. In the power-off state, oil flowing from the first connection portion 110 can push the second portion B32 to move closer to the first portion B31 and flow through the gap between the second portion B32 and the first base 2111. In the second state, oil flowing from the first connection portion 110 can push the second portion B32 to move closer to the first portion B31 and flow through the gap between the second portion B32 and the first base 2111.

[0090] This disclosure provides a valve device in some embodiments. By configuring a first movable member B3 including a first part B31 and a second part B32, the force required for the oil to push the second part B32 toward the first part B31 in the de-energized state is less than the force required for the oil to push the second part B32 toward the first part B31 in the second state. The configuration of the first part B31 and the second part B32 enables the switching between the two states of the first movable member B3, which simplifies the number of components and improves the working efficiency of the valve device.

[0091] In some embodiments, the first movable member B3 further includes a second elastic member, the two ends of which are connected to the second part B32 and the first base 2111 respectively. In the power-off state and the second state, the second elastic member is in the recovery state. The oil flowing out from the first connection part 110 pushes the second part B32 to move closer to the first part B31 and compresses the second elastic member.

[0092] Some embodiments of this disclosure provide a valve device in which, by providing a second elastic element, the second part B32 can be abutted against the first base 2111 when the oil is not flowing. The restoration of the second elastic element can quickly abut the second part B32 against the first base 2111, thereby improving the response speed of the entire system and increasing its reliability.

[0093] In some embodiments, the first movable member B3 further includes a first elastic member, the two ends of which are connected to the first part B31 and the first base 2111, respectively. The first channel B2 is located at least in the first part B31. In the first state, the first elastic member is in the restored state. The oil flowing out from the first connection 110 passes through the first channel located in the first part B31 and pushes the first part B31 to move away from the second part B32 while compressing the first elastic member. The oil flows out from the gap between the first part B31 and the second part B32.

[0094] Some embodiments of this disclosure provide a valve device in which the first channel B2 is located at least in the first part, eliminating the need to set the first channel B2 in other positions of the valve device. Furthermore, setting the first channel B2 in the first part B31 facilitates manufacturing. In addition, the provision of the first elastic element can improve the response speed to the oil pushing the first part B31 to move away from the second part B32, thus having high reliability.

[0095] In some embodiments, the first base 2111 includes a first opening A1, the first switch assembly 2112 includes a first one-way member B1, and oil can flow from the first connection 110 through the first one-way member B1 and from the first opening A1 to the second connection 120.

[0096] The first one-way component B1 includes, but is not limited to, the structure of a one-way valve plate and a one-way valve.

[0097] Some embodiments of this disclosure provide a valve device in which the flow of oil through the first one-way member B1 is provided with damping force, and no energy is required, thus reducing costs.

[0098] Referring to Figures 9 to 12, in some embodiments, one end of the first one-way member B1 is connected to the first base 2111, and the other end is in contact with the first base 2111. The flow of oil can separate the other end of the first one-way member B1 from the first base 2111, and the oil flows from the gap between the first one-way member B1 and the first base 2111 to the first opening A1.

[0099] Some embodiments of this disclosure provide a valve device in which, through the structure of the first one-way member B1, when oil flows from the first connection 110 through the first one-way member B1 and out of the first opening A1, the oil drives the first one-way member B1 to separate from the first base 2111; when oil does not flow from the first connection 110 through the first one-way member B1 and out of the first opening A1, the first one-way member B1 contacts the first base 2111. The switching of the above states is easy to achieve.

[0100] Referring to Figures 2, 13 to 15, in some embodiments, the second damping valve section 212 includes a second base 2121 and a second switching assembly 2122. The second base 2121 is disposed on the base 100 and encloses to form a second inner cavity, which communicates with the first connecting portion 110 and the second connecting portion 120. The second switching assembly 2122 is installed in the second inner cavity and is adapted to adjust the damping of the oil flow in the second inner cavity.

[0101] This disclosure provides a valve device in some embodiments. By setting a second base 2121 and a second switch assembly 2122, the damping force of oil flowing in the second inner cavity can be adjusted by the second switch assembly 2122. The structure is simple and compact.

[0102] In some embodiments, the second switch assembly 2122 includes a second channel D2, the two ends of which are connected to the first connecting portion 110 and the second connecting portion 120. The second switch assembly 2122 includes a second movable member D3, which has an open state and a closed state. In the open state, the second movable member D3 is separated from the second base 2121, and oil can flow through the gap between the second movable member D3 and the second base 2121 to flow from the second connecting portion 120 to the first connecting portion 110. The damping coefficient of the second switch assembly 2122 is N3. In the closed state, the second movable member D3 is in contact with the second base 2121, and the damping coefficient of the second switch assembly 2122 is N4. Oil can flow through the second channel D2 to flow from the second connecting portion 120 to the first connecting portion 110. N3 is less than N4.

[0103] Some embodiments of this disclosure provide a valve device that, through the above-described configuration, allows for setting the damping coefficient of the second switching assembly 2122, and the damping coefficient can be adjusted by the state of the second moving member D3, thereby enabling buffering of vehicle 1A under different conditions and improving the shock resistance of vehicle 1A.

[0104] In some embodiments, the second switch assembly 2122 includes a second channel D2, the two ends of which are connected to the second connection portion 120 and the first connection portion 110. The second switch assembly 2122 includes a second movable member D3, and the second base 2121 includes a second opening A2. The second movable member D3 includes an energized state and an de-energized state. In the de-energized state, the oil flowing out of the second connection portion 120 reaches the second opening C1, and the damping force overcome by the oil is M4. The energized state includes a third state and a fourth state. In the third state, the oil flowing out of the second connection portion 120 flows through the second channel D2, and the damping force overcome by the oil is M5. In the fourth state, the oil flowing out of the second connection portion 120 reaches the second opening C1, and the damping force overcome by the oil is M6. M6 is greater than M5, and M5 is greater than M4.

[0105] Some embodiments of this disclosure provide a valve device in which the damping force overcome by the oil can be adjusted by setting the state of the second movable member D3. If the oil flow rate is high, the second movable member D3 can be set to an energized state, which can effectively achieve a buffering effect. If the oil flow rate is low, the second movable member D3 can be set to an de-energized state, which can achieve both a buffering effect and reduce energy consumption.

[0106] In some embodiments, the second movable member D3 includes: a third part D31, mounted on the second base 2121; and a fourth part D32, one end of which abuts against the second base 2121, and the other end of which abuts against the third part D31 and has a degree of freedom of movement relative to the third part D31. In the power-off state, the oil flowing out from the second connection 120 can push the fourth part D32 to move closer to the third part D31 and flow through the gap between the fourth part D32 and the second base 2121. In the fourth state, the oil flowing out from the second connection 120 can push the fourth part D32 to move closer to the third part D31 and flow through the gap between the fourth part D32 and the second base 2121.

[0107] This disclosure provides a valve device in some embodiments. By configuring the second movable member D3, which includes a third part D31 and a fourth part D32, the force required for the oil to push the fourth part D32 towards the third part D31 in the de-energized state is less than the force required for the oil to push the fourth part D32 towards the third part D31 in the fourth state. The configuration of the third part D31 and the fourth part D32 enables the switching between the two states of the second movable member D3, which simplifies the number of components and improves the working efficiency of the valve device.

[0108] In some embodiments, the second movable member D3 further includes a third elastic member, the two ends of which are connected to the third part D31 and the second base 2121 respectively. The first channel is located at least in the third part D31. In the third state, the third elastic member is in the restored state. The oil flowing out from the second connection 120 passes through the first channel located in the third part D31 and pushes the third part D31 to move away from the fourth part D32 while compressing the third elastic member. The oil flows out from the gap between the third part D31 and the fourth part D32.

[0109] Some embodiments of this disclosure provide a valve device in which, by providing a third elastic element, the fourth part D32 is abutted against the second base 2121 when the oil is not flowing, due to the restoration of the third elastic element. The restoration of the third elastic element can quickly abut the fourth part D32 against the second base, thereby improving the response speed of the entire system and increasing its reliability.

[0110] In some embodiments, the second base 2121 includes a second opening C1, the second switch assembly 2122 includes a second one-way member D1, and oil can flow from the second connection 120 through the second one-way member D1 and from the second opening C1 to the first connection 110.

[0111] Some embodiments of this disclosure provide a valve device in which the flow of oil through the second one-way member D1 provides damping force for the flow of oil in the second inner cavity without consuming energy, thus reducing costs.

[0112] In some embodiments, one end of the second one-way member D1 is connected to the second base 2121, and the other end is in contact with the second base 2121. The flow of oil can separate the other end of the second one-way member D1 from the second base 2121, and the oil flows from the gap between the second one-way member D1 and the second base 2121 to the second opening C1.

[0113] Some embodiments of this disclosure provide a valve device in which, through the arrangement of the structure of the second one-way member D1, when oil flows from the second connection 120 through the second one-way member D1 and out of the second opening C1, the oil drives the second one-way member D1 to separate from the second base 2121; when oil does not flow from the second connection 120 through the second one-way member D1 and out of the second opening C1, the second one-way member D1 contacts the second base 2121. The switching of the above states is easily achieved.

[0114] In some embodiments, the valve body assembly 200 further includes a first one-way valve portion 220 and a second one-way valve portion 230, wherein the first one-way valve portion 220 allows oil to flow from the first connection portion 110 to the second connection portion 120, and the second one-way valve portion 230 allows oil to flow from the second connection portion 120 to the first connection portion 110.

[0115] Some embodiments of this disclosure provide a valve device, in which the valve body assembly 200 further includes a first one-way valve portion 220 and a second one-way valve portion 230, which respectively allow oil to flow from the first connecting portion 110 to the second connecting portion 120 and from the second connecting portion 120 to the first connecting portion 110.

[0116] In some embodiments, a first check valve 220 is connected between a second damping valve 212 and a second connecting portion 120. The second damping valve 212 includes a second inlet end and a second outlet end. The second inlet end is connected to the first check valve 220, and the second outlet end is connected to the first damping valve 211. The first check valve 220 allows oil to flow unidirectionally from the first damping valve 211 to the second connecting portion 120.

[0117] This disclosure provides a valve device through some embodiments. The above-described configuration simplifies the assembly and manufacturing process of the valve device and makes its structure more compact.

[0118] In some embodiments, the first one-way valve portion 220 includes a first connecting seat 221 and a first valve body 222. The first connecting seat 221 is connected between the second connecting portion 120 and the second inlet end, and the first connecting seat 221 is provided with a third opening; the first valve body 222 is capable of opening or closing the third opening.

[0119] Some embodiments of this disclosure provide a valve device in which a third opening can be opened to allow oil to flow smoothly when oil flows to and contacts the first valve body 222, by the arrangement of a first one-way valve part 220 including a first connecting seat 221 and a first valve body 222, thereby preventing oil backflow.

[0120] In some embodiments, the second one-way valve section 230 is connected between the first damping valve section 211 and the first connecting seat 221. The first damping valve section 211 includes a first inlet end and a first outlet end. The first inlet end is connected to the second one-way valve section 230, and the first outlet end is connected to the second damping valve section 212. The first one-way valve section 220 allows oil to flow unidirectionally from the second damping valve section 212 to the first connecting seat 110.

[0121] This disclosure provides a valve device through some embodiments. The above-described configuration simplifies the assembly and manufacturing process of the valve device and makes its structure more compact.

[0122] In some embodiments, the second one-way valve portion 230 includes a second connecting seat 231 and a second valve body 232. The second connecting seat 231 is connected between the first connecting portion 110 and the first inlet end, and the second connecting seat 231 is provided with a fourth opening; the second valve body 232 is capable of opening or closing the fourth opening.

[0123] Some embodiments of this disclosure provide a valve device in which, by providing a second one-way valve part 230 including a second connecting seat 231 and a first valve body, when oil flows to and contacts the second valve body 232, a fourth opening can be opened to allow smooth flow and prevent backflow of oil.

[0124] In some embodiments, the base 100 further includes a third connecting portion 130, one end of which can be connected to an energy storage device, and the other end of which communicates with the second one-way valve portion 230 and the first connecting portion 110.

[0125] Some embodiments of this disclosure provide a valve device in which, through the provision of the third connection portion 130, when the oil flow rate and pressure inside the valve device are too high, a portion can flow into the accumulator, thereby playing a protective role for the first module.

[0126] In some embodiments, the base 100 further includes a fourth connecting portion 140, one end of which can be connected to a stiffness switching valve, and the other end of which communicates with the first one-way valve portion 220 and the second connecting portion 120.

[0127] Some embodiments of this disclosure provide a valve device in which, through the provision of the fourth connection portion 140, when the oil flow rate and pressure inside the valve device are too high, a portion can flow into the stiffness switching valve, thereby playing a protective role for the second module.

[0128] This disclosure provides a damping system in some embodiments, including the valve device of any of the above.

[0129] This disclosure provides a damping system through some embodiments. With the above settings, the damping inside the damping system can be precisely controlled, thereby improving the reliability of the damping system.

[0130] In some embodiments, the damping system includes a first module and a second module. The first module is used for shock absorption; the second module is used for oil storage.

[0131] This disclosure provides a damping system in some embodiments, which ensures the integrity of the internal circuit of the damping system through the setting of a first module and a second module.

[0132] In some embodiments, the damping system includes an accumulator and a stiffness switching valve. The accumulator is used to buffer the oil flowing from the second module to the first module, and the stiffness switching valve is used to buffer the oil flowing from the first module to the second module.

[0133] Some embodiments of this disclosure provide a damping system that, through the installation of an accumulator and a stiffness switching valve, can provide buffer protection for the damping system and reduce the probability of damage to the first and second modules of the damping system.

[0134] Some embodiments of this disclosure also provide a vehicle 1A including any of the above-described damping systems.

[0135] This disclosure provides a vehicle 1A in some embodiments, which improves the stability of the vehicle 1A during driving by setting the damping system described above.

[0136] In some embodiments, vehicle 1A includes wheels 12A and a body 11A, with the body 11A mounted on the wheels 12A and a valve device mounted on the body 11A. The body 11A is connected to the wheels 12A via a first module.

[0137] This disclosure provides a vehicle 1A with some embodiments that improve the stability of the vehicle body 11A during driving through the above-described configuration.

[0138] In related technologies, the sealing surface of the check valve seat is a large flat surface, typically wider than 0.5 mm. The wide contact area between the sealing surface and the valve disc results in high surface tension of the fluid at the contact surface between the valve disc and the valve seat. This leads to a large instantaneous impact force during fluid flow, generating significant impact noise and failing to meet noise reduction requirements. In other words, the check valve seat in related technologies suffers from the technical problem of excessive noise during fluid flow.

[0139] Please refer to Figure 16. In some embodiments of this disclosure, the one-way valve seat 1B is provided with a first one-way valve passage 3B and a one-way valve through hole 4B. The one-way valve seat 1B has at least one sealing surface 2B, which is adapted to abut against the first one-way valve disc 5B so that the first one-way valve disc 5B is adapted to allow fluid to flow unidirectionally from the one-way valve through hole 4B to the first one-way valve passage 3B. For example, the width of each sealing surface 2B is less than or equal to 0.4 mm.

[0140] It is understandable that when the width of the sealing surface 2B is greater than 0.4 mm, the sealing surface 2B has a large surface adhesion when it is in contact, making it difficult for the first one-way valve plate 5B to open.

[0141] In some embodiments, the width of the sealing surface 2B of the one-way valve seat 1B is set to be less than or equal to 0.4 mm, so that the instantaneous impact force generated when the fluid flows at the sealing surface 2B is small and the noise can meet the noise requirements.

[0142] In some embodiments, the width of the sealing surface 2B is greater than or equal to 0.05 mm.

[0143] It is understandable that when the width of the sealing surface 2B is less than 0.05 mm, the sealing effect is poor and the manufacturing process becomes more difficult, making mass production inconvenient.

[0144] It is understandable that when the width of the sealing surface 2B is less than 0.4 mm, the tension between the fluid and the sealing surface 2B of the first check valve plate 5B is small, the instantaneous acceleration of the fluid during flow is small, and the impact noise generated by the impact force during fluid flow is small, so as to meet the noise requirements.

[0145] In some embodiments, the sealing surface 2B is a plane.

[0146] It is understandable that the sealing surface 2B is a plane, which can enhance the sealing effect between the sealing surface 2B and the first one-way valve plate 5B.

[0147] In some embodiments, the flatness of the sealing surface 2B is less than or equal to 0.005 mm.

[0148] For example, the flatness of the sealing surface 2B can be any one of 0.001 mm, 0.003 mm, or 0.005 mm.

[0149] It is understandable that the smaller the flatness of the sealing surface 2B, the smoother the surface of the sealing surface 2B, and the better the sealing effect between the sealing surface 2B and the first one-way valve plate 5B.

[0150] In some embodiments, the one-way valve seat 1B has two sealing surfaces 2B, and a one-way valve through hole 4B is provided between the two sealing surfaces 2B. For example, the interval between the two sealing surfaces 2B is in the range of 0.5 mm to 5 mm.

[0151] For example, the distance between the two sealing surfaces 2B can be any of 0.5 mm, 2 mm, 3 mm, or 5 mm.

[0152] Understandably, when the gap between the two sealing surfaces 2B is less than 0.5 mm, the small size increases the difficulty of the manufacturing process and is not conducive to mass production; when the gap between the two sealing surfaces 2B is greater than 5 mm, the large gap between the two sealing surfaces 2B will result in a smaller cross-sectional area of ​​the first one-way valve channel 3B, affecting the flow rate of the first one-way valve channel 3B.

[0153] In some embodiments, please refer to FIG16, the one-way valve seat 1B includes a body portion 21B and a sealing portion 22B connected to the body portion 21B. The body portion 21B is provided with a first one-way valve passage 3B, and both the body portion 21B and the sealing portion 22B have a sealing surface 2B.

[0154] For example, the sealing part 22B may be disposed around the outer periphery of the body part 21B.

[0155] For example, the shape of the sealing surface 2B can be annular.

[0156] It is understood that the main body 21B and the sealing part 22B each have a sealing surface 2B, and the two sealing surfaces 2B are arranged around each other and spaced apart, thereby sealing the position between the two sealing surfaces 2B.

[0157] In some embodiments, referring to FIG16, the one-way valve seat 1B further includes a connecting portion 23B connected between the body portion 21B and the sealing portion 22B, and the connecting portion 23B is provided with a one-way valve through hole 4B.

[0158] It is understandable that the one-way valve through hole 4B is located in the connecting part 23B between the main body part 21B and the sealing part 22B, and the one-way valve through hole 4B located between the two sealing surfaces 2B is sealed by the two sealing surfaces 2B to improve the sealing effect.

[0159] In some embodiments, please refer to FIG16, the connecting part 23B is provided with a groove 24B, and the one-way valve through hole 4B is provided on the bottom wall of the groove 24B.

[0160] For example, groove 24B is the recessed position between the two sealing surfaces 2B.

[0161] It is understandable that the one-way valve through hole 4B is located in the groove 24B, and the first one-way valve plate 5B abuts against the sealing surface 2B to seal the groove 24B and the one-way valve through hole 4B located in the groove 24B.

[0162] In some embodiments, the flexibility of the one-way valve seat 1B is adapted to be greater than the flexibility of the first one-way valve disc 5B.

[0163] It is understandable that the greater the flexibility of the one-way valve seat 1B, the less wear on the mold used to prepare the one-way valve seat 1B, and the more good one-way valve seats 1B that can be prepared by the same mold, thereby reducing costs.

[0164] Please refer to Figures 16 and 17. Some embodiments of this disclosure provide a one-way valve 25B, which includes a one-way valve seat 1B and a first one-way valve disc 5B as described above.

[0165] It is understandable that the sealing surface 2B of the one-way valve seat 1B abuts against the valve plate 5B of the first one-way valve to achieve the effect of one-way flow of fluid by the one-way valve 25B.

[0166] In some embodiments, referring to FIG17, a one-way valve body 6B and a second one-way valve plate 25B are also included. The one-way valve body 6B is provided with a second one-way valve passage 8B. The second one-way valve plate 25B is mounted on the one-way valve body 6B to allow fluid to flow unidirectionally from the first one-way valve passage 3B to the second one-way valve passage 8B.

[0167] For example, the valve plate of the second check valve 25B is located on the side of the valve plate 5B of the first check valve that is close to the first valve (valve) 12.

[0168] Understandably, the second check valve passage 8B is used to allow fluid to flow unidirectionally from the first check valve passage 3B to the second check valve passage 8B, preventing fluid from flowing back from the second check valve passage 8B to the first check valve passage 3B.

[0169] In some embodiments, referring to FIG17, the system further includes a one-way valve body 6B and an elastic element 9. The one-way valve body 6B is connected to the one-way valve seat 1B, and the elastic element 9 abuts between the first one-way valve plate 5B and the one-way valve body 6B.

[0170] For example, the elastic element 9 is located between the first one-way valve plate 5B and the one-way valve body 6B, and is in a compressed state, so that the first one-way valve plate 5B is pressed against the sealing surface 2B by the elastic element 9, and the first one-way valve plate 5B is pushed open toward the one-way valve body 6B, which requires at least overcoming the elastic force of the elastic element 9 itself.

[0171] It is understandable that the elastic element 9 is used to make the first one-way valve plate 5B and the sealing surface 2B more tightly abut against each other, so as to better achieve the one-way flow effect of the one-way valve 25B.

[0172] Please refer to Figure 17. Some embodiments of this disclosure provide a valve assembly 10, including a one-way valve seat 1B as described above, or a one-way valve 25B as described above.

[0173] For example, valve assembly 10 may include at least one of check valve 25B, relief valve, solenoid valve, and pilot valve 34.

[0174] In one embodiment, referring to FIG17, it further includes a control component 11B and a first valve 12B; for example, when the control component 11B is in a first state, the first valve 12B forms a first channel 26, and fluid is adapted to flow sequentially through a first check valve channel 3B and the first channel 26; when the control component 11B is in a second state, the first valve 12B forms a second channel 27, and fluid is adapted to flow sequentially through the first check valve channel 3B and the second channel 27; the first channel 26 and the second channel 27 are different.

[0175] For example, control component 11B can be a solenoid valve.

[0176] Understandably, in the first state, the fluid flows through the first one-way valve channel 3B and the first channel 26 in sequence, and in the second state, the fluid flows through the first one-way valve channel 3B and the second channel 27 in sequence. This allows the fluid to travel through different paths under different operating conditions, so that the shock absorber 18 can behave in different ways to suit different road conditions.

[0177] In some embodiments, the first state is a power-off state and the second state is a power-on state.

[0178] It is understandable that the first state is the power-off state, at which time the current of the solenoid valve is 0, and the opening of the valve port of the first valve 12B is relatively large, which makes the flow resistance of the fluid small and suitable for flat road conditions.

[0179] It is understandable that the second state is the energized state. At this time, the solenoid valve has a current value. The larger the current value, the smaller the opening of the valve port of the first valve 12B, which makes the flow resistance of the fluid greater, and is suitable for potholes.

[0180] In some embodiments, the pressure of the fluid when the control component 11B is in the second state is greater than the pressure of the fluid when the control component 11B is in the first state.

[0181] Understandably, in the second state, the solenoid valve is energized, causing the first valve body 30 of the first valve 12B to abut more tightly against the first valve seat 31 of the first valve 12B. The fluid requires greater pressure to open the first valve body 30 of the first valve 12B, thus opening the valve port of the first valve 12B. In the first state, the solenoid valve is not energized. At this time, the first valve body 30 of the first valve 12B abuts against the first valve seat 31 of the first valve 12B only through another spring located between the first valve body 30 of the first valve 12B and the guide sleeve 32 of the first valve 12B. At this time, the fluid only needs a smaller pressure to open the valve port.

[0182] In some embodiments, referring to FIG17, the control component 11B includes a push rod 13B; for example, the push force of the push rod 13B on the first valve 12B when the control component 11B is in the second state is greater than the push force of the push rod 13B on the first valve 12B when the control component 11B is in the first state.

[0183] Understandably, push rod 13B is used to press the first valve body 30 of the first valve 12B against the first valve seat 31 of the first valve 12B under the control of the solenoid valve. When the solenoid valve is energized, the push rod 13B increases the thrust of the first valve 12B towards the valve body of the first valve 12B toward the check valve 25B, making it more difficult to open the valve port of the first valve 12B.

[0184] In some embodiments, when the control component 11B is in the second state, the push rod 13B is adapted to be fluid-pushed away from the first valve 12B, such that the first valve 12B forms a second channel 27.

[0185] Understandably, in the second state, the solenoid valve is energized, which increases the thrust of the push rod 13B on the valve body of the first valve 12B toward the check valve 25B. The valve port of the first valve 12B is more difficult to open, so that the first valve 12B forms a second channel 27 for fluid to pass through.

[0186] In one embodiment, when the control component 11B is in the second state, the second channel 27 includes the first sub-channel 28 during the first time period, and the second channel 27 includes the first sub-channel 28 and the second sub-channel 29 during the second time period after the first time period.

[0187] Understandably, in the first time period, the fluid pressure is insufficient to open the second sub-channel 29, and the fluid only passes through the first sub-channel 28; when the fluid pressure reaches the level required to open the second sub-channel 29, the first sub-channel 28 and the second sub-channel 29 open simultaneously, and the fluid passes through both the first sub-channel 28 and the second sub-channel 29 at the same time.

[0188] In some embodiments, as shown in Figures 19 and 20, the second sub-channel 29 is the same as the first channel 26.

[0189] It is understood that both the second sub-channel 29 and the first channel 26 are valve ports formed at the contact point between the first valve body 30 and the first valve seat 31 of the first valve 12B. When the first valve body 30 and the first valve seat 31 of the first valve 12B move away from each other, the valve ports open. For example, in the first state, the valve ports open to form the first channel 26; in the second state, the valve ports open to form the second sub-channel 29.

[0190] In some embodiments, the pressure of the fluid flowing through the second channel 27 during a first time period is less than the pressure of the fluid flowing through the second channel 27 during a second time period.

[0191] Understandably, the pressure of the fluid in the second time period is greater than that in the first time period, making the pressure of the fluid in the second time period sufficient to open the second sub-channel 29.

[0192] In some embodiments, the first valve 12B is an overflow valve.

[0193] It is understandable that the relief valve adjusts the resistance to fluid flow by regulating the opening of the valve port. A larger valve opening results in lower fluid flow resistance, while a smaller valve opening results in higher fluid flow resistance.

[0194] Please refer to Figures 18 to 20. Some embodiments of this disclosure provide a damping controller 33, including a one-way valve seat 1B as described above, or a one-way valve 25B as described above, or a valve assembly 10 as described above.

[0195] In some embodiments, referring to Figures 19 and 20, the valve assembly 10 further includes a control assembly 11B and a first valve 12B; for example, when the control assembly 11B is in a first state, the first valve 12B forms a first channel 26, through which fluid is adapted to flow sequentially through a first check valve channel 3B and the first channel 26; when the control assembly 11B is in a second state, the first valve 12B forms a second channel 27, through which fluid is adapted to flow sequentially through the first check valve channel 3B and the second channel 27; the first channel 26 and the second channel 27 are different.

[0196] For example, in the first state, the fluid passes through the first one-way valve channel 3B and the first channel 26; in the second state, the fluid passes through the first one-way valve channel 3B and the second channel 27, so that the damping controller 33 can have different flow resistances for different road conditions, thereby achieving better vibration reduction effect under different road conditions.

[0197] In some embodiments, referring to FIG18, the damping controller 33 further includes a housing 14B and two valve assemblies 10. The housing 14B has two first connecting chambers 15B, a second connecting chamber 16 and a third connecting chamber 17. The two valve assemblies 10 are respectively installed in the two first connecting chambers 15B; for example, the second connecting chamber 16 is connected to the third connecting chamber 17 through the two valve assemblies 10.

[0198] It is understood that the valve assembly 10 controls the connection between the second connecting chamber 16 and the third connecting chamber 17, thereby allowing fluid to flow from the second connecting chamber 16 to the third connecting chamber 17, or from the third connecting chamber 17 to the second connecting chamber 16, as needed.

[0199] In some embodiments, referring to FIG19, when the two control components 11B are in the first state, the second connection cavity 16 is connected to the third connection cavity 17 through, for example, the first one-way valve passage 3B and the first passage 26 of one valve assembly 10, and the one-way valve through hole 4B and the first one-way valve passage 3B of another valve assembly 10.

[0200] Understandably, in the first state, the fluid in the second connecting cavity 16 flows sequentially through, for example, the first one-way valve passage 3B and the first passage 26 of a valve assembly 10, and the one-way valve through hole 4B and the first one-way valve passage 3B of another valve assembly 10, to the third connecting cavity 17, so as to achieve unidirectional flow from the second connecting cavity 16 to the third connecting cavity 17, so that the damping controller 33 is suitable for flat road conditions.

[0201] In some embodiments, referring to FIG5, when the two control components 11B are in the second state, the second connection cavity 16 is connected to the third connection cavity 17 through, for example, the first one-way valve channel 3B and the second channel 27 of one valve assembly 10, and the one-way valve through hole 4B and the first one-way valve channel 3B of another valve assembly 10.

[0202] Understandably, in the second state, the fluid in the second connecting cavity 16 flows sequentially through, for example, the first one-way valve passage 3B and the second passage 27 of a valve assembly 10, the one-way valve through hole 4B of another valve assembly 10, and the first one-way valve passage 3B, to the third connecting cavity 17, so as to achieve unidirectional flow from the second connecting cavity 16 to the third connecting cavity 17, so that the damping controller 33 is suitable for pothole conditions.

[0203] In some embodiments, referring to FIG18, the second connecting cavity 16 is adapted to connect the vibration damper 18, and the third connecting cavity 17 is adapted to connect the central control cylinder 19 and the stiffness conversion valve 20.

[0204] The vehicle provided in some embodiments of this disclosure includes the one-way valve seat 1B described above, or the one-way valve 25B described above, or the valve assembly 10 described above, or the damping controller 33 described above.

[0205] The vehicle may be a gasoline vehicle, a plug-in hybrid vehicle, or a new energy vehicle, etc., and this disclosure does not limit it.

[0206] In related technologies, valve devices are used in damping controllers. When the valve device is not energized or is energized under low current, the internal oil fluctuates greatly, causing the positions of the pilot valve plug and the first valve body inside the valve device to change with the oil fluctuation, resulting in unstable system damping force.

[0207] To address the aforementioned problems, some embodiments of this disclosure provide a valve device 10C, a damping controller 100C, a suspension damping control system 1000, and a vehicle 10000.

[0208] The valve device 10C, damping controller 100C, suspension damping control system 1000, and vehicle 10000 according to some embodiments of the present disclosure are described in detail below with reference to Figures 21-39.

[0209] Referring to Figures 21-22 and 25-26, the valve device 10C according to some embodiments of the present disclosure may include: a first channel, a second channel, a first valve body 11C, a pilot valve plug 2C, a drive assembly 8C, and a first elastic element 3C.

[0210] Here, the first valve body 11C is movable to adjust the flow damping between the first channel and the second channel. For example, by changing the position of the first valve body 11C, the communication area between the first channel and the second channel can be adjusted to change the communication damping between the first channel and the second channel, for example, to increase or decrease the flow damping between the first channel and the second channel. The first valve body 11C has a pilot channel 111C, which is connected to the second channel.

[0211] The pilot valve plug 2C is located on one side of the first valve body 11C. The pilot valve plug 2C is adapted to open or block the pilot passage 111C. When the pilot valve plug 2C opens the pilot passage 111C, the pilot passage 111C can be connected to the first passage through the third passage. In this way, the medium in the second passage can reach the third passage through the pilot passage 111C and then enter the first passage from the third passage. When the pilot valve plug 2C closes the pilot passage 111C, the pilot passage 111C cannot be connected to the first passage through the third passage.

[0212] The drive assembly 8C is used to drive the pilot valve plug 2C to move. One end of the first elastic member 3C abuts against the pilot valve plug 2C to reduce the fluctuations caused by the medium on the pilot valve plug 2C. Specifically, the first elastic member 3C applies elastic force to the pilot valve plug 2C to stabilize the position of the pilot valve plug 2C as much as possible, so that the fluctuations caused by the medium on the pilot valve plug 2C are small.

[0213] Taking the valve device 10C as an example, which is used in the damping controller 100C and the medium flowing inside the valve device 10C is oil, when the flow resistance of the oil fluctuates greatly inside the damping controller 100C, the elastic force applied by the first elastic element 3C to the pilot valve plug 2C controls the axial fluctuation of the pilot valve plug 2C. At the same time, since the pilot valve plug 2C is suitable for contacting or separating from the first valve body 11C, when the axial fluctuation of the pilot valve plug 2C is small, it is beneficial to reduce the axial displacement fluctuation of the first valve body 11C, so that the damping force of the system is stable and meets the stable power value requirement of the shock absorber of vehicle 10000.

[0214] It is understood that the above-mentioned "axial direction" refers to the arrangement direction of the pilot valve plug 2C and the first valve body 11C, that is, the up and down direction shown in Figures 21-22 and 25-26.

[0215] According to some embodiments of the present disclosure, the valve device 10C, by providing a first elastic element 3C, makes the fluctuations caused by the medium to the pilot valve plug 2C smaller, reduces the influence of the medium on the position of the pilot valve plug 2C and the first valve body 11C, and makes the damping force inside the valve device 10C stable. When the valve device 10C is applied to the damping controller 100C and the damping controller 100C is applied to the suspension damping control system 1000, the damping force of the system can be stabilized.

[0216] In some embodiments, the first elastic element 3C may be a spring, a wave spring, etc., as shown in Figures 21-22, 25-26, and 29, where the first elastic element 3C is a spring.

[0217] In some embodiments of this disclosure, referring to Figures 21-22, one end of the first elastic member 3C abuts against the pilot valve plug 2C to apply a force toward the first valve body 11C to the pilot valve plug 2C. The elastic force of the first elastic member 3C applied to the pilot valve plug 2C reduces the fluctuations caused by the oil to the pilot valve plug 2C. The pilot valve plug 2C pushes the first valve body 11C to move axially downward. The downward force applied by the first elastic member 3C to the first valve body 11C interacts with the upward flow damping force of the system oil, improving the fluctuation amplitude of the system's damping force, stabilizing the system's damping force, and meeting the stable indicated power value requirement of the shock absorber for vehicle 10000.

[0218] In some embodiments, referring to Figures 25-26, one end of the first elastic member 3C abuts against the pilot valve plug 2C to apply a force to the pilot valve plug 2C away from the first valve body 11C. The elastic force of the first elastic member 3C applied to the pilot valve plug 2C reduces the fluctuations caused by the oil to the pilot valve plug 2C. At the same time, since the pilot valve plug 2C is adapted to contact or separate from the first valve body 11C, it is beneficial to reduce the axial displacement fluctuations of the first valve body 11C when the axial fluctuation of the pilot valve plug 2C is small, thereby stabilizing the damping force of the system and meeting the stable indication power value requirements of the shock absorber of vehicle 10000.

[0219] In some embodiments, referring to Figures 21-22 and 25-26, the valve device 10C further includes a first valve seat 12C, and a first valve body 11C is movable relative to the first valve seat 12C. Oil in the system is used to drive the first valve body 11C. For example, oil below the first valve body 11C can push the first valve body 11C to move axially.

[0220] In some embodiments, referring to Figures 21-22, 25-26, and 30, one of the first valve body 11C and the first valve seat 12C has a guide cavity, and the other of the first valve body 11C and the first valve seat 12C extends at least partially into the guide cavity for guided engagement with one of them. The first valve body 11C is movable relative to the first valve seat 12C in a direction approaching or away from the pilot valve plug 2C. The guided engagement design of the first valve body 11C and the first valve seat 12C reduces the wobbling and offset of the first valve body 11C, improves the stability and accuracy of the first valve body 11C during movement, thereby improving the overall stability and reliability of the first valve assembly 1C. In the examples of Figures 21-22, 25-26, and 30, the first valve seat 12C has a guide cavity, the first valve body 11C extends into the first valve seat 12C, and the first valve body 11C and the first valve seat 12C are in guided engagement.

[0221] In some embodiments, referring to Figures 21-22, 25-26, and 30, a first sealing ring 15C is provided at the guide mating point between the first valve body 11C and the first valve seat 12C. Therefore, the first sealing ring 15C significantly enhances the sealing effect between the first valve body 11C and the first valve seat 12C. The first sealing ring 15C can tightly fit against the mating surface of the first valve body 11C and the first valve seat 12C, effectively preventing media leakage and ensuring the stable operation of the valve device 10C. The first sealing ring 15C also serves as a guide for the first valve body 11C. The first sealing ring 15C can effectively improve sliding damping to suppress chattering after the first valve body 11C is opened.

[0222] In some embodiments, referring to Figures 25-26, one end of the first elastic member 3C abuts against the pilot valve plug 2C, and the other end of the first elastic member 3C abuts against the first valve seat 12C. The first elastic member 3C applies a force to the pilot valve plug 2C away from the first valve body 11C. For example, in Figures 25-26, the first elastic member 3C applies an upward force to the pilot valve plug 2C to reduce the fluctuations caused by the oil to the pilot valve plug 2C.

[0223] In some embodiments, referring to Figures 21-22 and 25-26, the valve device 10C further includes a valve housing 6C. A first valve body 11C is movable relative to the valve housing 6C, and a first valve seat 12C is fixed relative to the valve housing 6C. The valve housing 6C has a medium outlet 61, which is configured as at least a part of a first channel. A pressure relief chamber 64 is provided inside the valve housing 6C, and the medium outlet 61 communicates with the pressure relief chamber 64. The medium outlet 61 also communicates with the external space of the valve device 10C, and the oil in the pressure relief chamber 64 can flow out of the valve device 10C through the medium outlet 61.

[0224] In some embodiments, referring to Figures 21-22 and 25-26, the valve device 10C further includes a base valve seat 5C, a drive assembly 8C disposed on the side of the base valve seat 5C opposite to the pilot valve plug 2C, a valve housing 6C connected to the base valve seat 5C, a first valve seat 12C connected to the base valve seat 5C, a base valve hole 51 provided on the base valve seat 5C, a first chamber 52 formed between the first valve seat 12C and the base valve seat 5C, the base valve hole 51 connecting the first chamber 52 and the pressure relief chamber 64, and the oil in the first chamber 52 can flow through the base valve hole 51 to the pressure relief chamber 64, and then flow out of the valve device 10C through the medium outlet 61. The base valve hole 51 and the first chamber 52 are configured as at least part of a third channel. When the pilot valve plug 2C opens the pilot channel 111C, the pilot channel 111C can be connected to the pressure relief chamber 64 through the first chamber 52 and the base valve hole 51. In this way, the medium in the second channel can reach the first chamber 52 through the pilot channel 111C, and the oil in the first chamber 52 can flow to the pressure relief chamber 64 through the base valve hole 51, and then flow out to the outside of the valve device 10C through the medium outlet 61.

[0225] In some embodiments, referring to Figures 21-22 and 25-26, a valve passage 62 is formed within the valve housing 6C. The valve passage 62 is configured as at least a portion of a second passage, and the pressure relief chamber 64 is configured as at least a portion of a first passage. The first valve body 11C is movable to adjust the communication damping between the valve passage 62 and the pressure relief chamber 64. When the first valve body 11C is movable, it can change the size of its overflow valve port, thereby changing the communication damping between the valve passage 62 and the pressure relief chamber 64.

[0226] In some embodiments, referring to Figures 21-22, 25-26, and 30, a receiving cavity 13C is formed between the first valve seat 12C and the first valve body 11C, and the pilot channel 111C is connected to the receiving cavity 13C, so that the oil in the receiving cavity 13C can flow into the pilot channel 111C.

[0227] The first valve body 11C is provided with a first valve hole (preset valve hole) 112, and the valve passage 62 is connected to the receiving cavity 13C through the first valve hole 112C. Oil in the valve passage 62 can flow into the receiving cavity 13C through the first valve hole 112C, and the oil in the receiving cavity 13C can further flow into the pilot passage 111C. The receiving cavity 13C is used to achieve pressure balance between the pilot passage 111C and the valve passage 62. If the receiving cavity 13C is not provided and the pilot passage 111C is directly connected to 62, it will cause an imbalance in the upper and lower air pressures of the first valve body 11C.

[0228] In some embodiments, referring to Figures 21-22, 25-26, and 30, the valve device 10C further includes a second elastic member 14C. The second elastic member 14C is disposed within the receiving cavity 13C, axially along the first valve body 11C. One end of the second elastic member 14C abuts against the first valve body 11C, and the other end of the second elastic member 14C abuts against the first valve seat 12C. Specifically, the first valve body 11C, the first valve seat 12C, and the second elastic member 14C constitute the first valve assembly 1C. The second elastic member 14C abuts against the first valve body 11C and the first valve seat 12C, providing an elastic force to the first valve body 11C. This elastic force causes the first valve body 11C and the first valve seat 12C to maintain a tendency to move away from each other at all times.

[0229] For example, the second elastic element 14C can be a spring, a wave spring, etc., as shown in Figures 21-22, 25-26, and 30, where the second elastic element 14C is a spring.

[0230] In some embodiments, referring to Figures 21-22, 25-26, and 30, the pilot channel 111C includes an axial channel 1111 and a radial channel 1112. A pilot valve plug 2C is used to selectively block the axial channel 1111. The radial channel 1112 is connected to the axial channel 1111 and extends radially along the first valve body 11C to the receiving cavity 13C. In other words, the medium can reach the radial channel 1112 through the receiving cavity 13C and flow from the radial channel 1112 to the axial channel 1111. When the pressure of the medium in the axial channel 1111 does not reach the second pressure threshold, the pilot valve plug 2C blocks the axial channel 1111. When the pressure of the medium in the axial channel 1111 reaches the second pressure threshold, the pilot valve plug 2C opens the axial channel 1111. At this time, the medium in the receiving cavity 13C can flow through the radial channel 1112 and the axial channel 1111 to the first chamber 52, and then through the base valve hole 51 to the pressure relief chamber 64.

[0231] The arrangement of radial channel 1112 and axial channel 1111 improves the flow flexibility of the medium. By optimizing the flow path of the medium, it enhances the stability of the medium during the flow process, helping to reduce fluctuations and vibrations, and lowering noise and wear. The arrangement of radial channel 1112 reduces the axial dimension of valve device 10C. The axial channel 1111 and radial channel 1112 are formed within the first valve body 11C, making full use of the internal space of the first valve body 11C.

[0232] For example, there can be one, two, three or more radial channels 1112. For example, there can be four radial channels 1112 arranged in a ring.

[0233] In some embodiments, as shown in Figures 21-22 and 25-26, a radially extending protruding structure 63 is formed on the inner peripheral wall of the valve housing 6C. The protruding structure 63 forms a valve passage 62. The first valve body 11C is selectively attached to or separated from the protruding structure 63. The pressure relief chamber 64 and the valve passage 62 are adapted to communicate through the gap between the first valve body 11C and the protruding structure 63. Specifically, the protruding structure 63 extends radially toward the axis of the first valve body 11C relative to the inner peripheral wall of the valve housing 6C. The first valve body 11C is located on the upper side of the protruding structure 63. The gap between the first valve body 11C and the protruding structure 63 is the overflow valve port. The axial dimension of the overflow valve port is L. The elastic force of the first elastic element 3C controls the axial fluctuation of the pilot valve plug 2C, thereby reducing the axial displacement fluctuation of the first valve body 11C, that is, reducing the axial dimension fluctuation of the overflow valve port, stabilizing the damping force of the system, and meeting the stable power value requirement of the shock absorber of vehicle 10000.

[0234] In some embodiments, the pressure relief chamber 64 and the valve passage 62 are in a normally open state, that is, the first valve body 11C moves up and down to adjust the damping magnitude, and even when the first valve body 11C abuts against the protruding structure 63, the pressure relief chamber 64 and the valve passage 62 are connected with a small flow rate.

[0235] In Figures 21 and 23, the first valve body 11C is fitted to the protruding structure 63, and the gap between the first valve body 11C and the protruding structure 63 is small. This results in a large flow resistance between the first valve body 11C and the protruding structure 63, leading to a large flow damping between the first channel and the second channel. In Figures 22 and 24, a gap exists between the first valve body 11C and the protruding structure 63, forming an overflow valve port. The flow resistance between the first valve body 11C and the protruding structure 63 is smaller than that shown in Figures 21 and 23, resulting in less flow damping between the first channel and the second channel. The medium in the valve channel 62 can flow through the overflow valve port to the pressure relief chamber 64, and then out through the medium outlet 61 to the outside of the valve device 10C. For example, when the oil pressure in the valve channel 62 reaches the third pressure threshold, a larger gap appears between the first valve body 11C and the protruding structure 63, and the overflow valve port opens significantly.

[0236] In some embodiments, referring to Figures 21-22 and 25-26, the valve device 10C further includes a second valve assembly 7C. The second valve assembly 7C includes a second valve body 71, which is mounted on the valve housing 6C. The second valve body 71 has a second chamber 713, and the communication damping between the second chamber 713 and the valve passage 62 is adjustable. For example, the communication area between the second chamber 713 and the valve passage 62 is adjustable to change the communication damping between the second chamber 713 and the valve passage 62. When the second chamber 713 is in communication with the valve passage 62, the oil in the second chamber 713 can flow to the valve passage 62.

[0237] In some embodiments, referring to Figures 21-22 and 25-26, the second valve assembly 7C includes a first valve plate 72, and the second valve body 71 has a first channel 7111 for communicating with the second chamber 713 and the valve channel 62. The first valve plate 72 can block or open the first channel 7111. When the first valve plate 72 blocks the first channel 7111, the second chamber 713 is isolated from the valve channel 62. When the first valve plate 72 opens the first channel 7111, the second chamber 713 and the valve channel 62 are connected through the first channel 7111. When the oil pressure in the second chamber 713 reaches a first pressure threshold, the first valve plate 72 opens the first channel 7111.

[0238] In some embodiments, referring to Figures 21-22 and 25-26, the second valve body 71 has a second channel 7121 and a third channel 7122, the second chamber 713 is in communication with the second channel 7121, and the third channel 7122 is selectively in communication with the second chamber 713.

[0239] In some embodiments, referring to Figures 21-22 and 25-26, the second valve assembly 7C further includes a second valve plate 73, which is capable of blocking or opening the third channel 7122. When the second valve plate 73 blocks the third channel 7122, the third channel 7122 is isolated from the second chamber 713. When the second valve plate 73 opens the third channel 7122, the third channel 7122 is connected to the second chamber 713.

[0240] In some embodiments, referring to Figures 21-22 and 25-26, the second valve assembly 7C further includes a third elastic member 74 disposed within the second chamber 713. The third elastic member 74 applies an elastic force to the second valve disc 73 in a direction toward blocking the third channel 7122. In other words, the third elastic member 74 applies an elastic force to the second valve disc 73 toward the second valve body 712 to drive the valve disc to block the third channel 7122. When the medium pressure in the third channel 7122 reaches a preset pressure threshold, the medium in the third channel 7122 can push the second valve disc 73 to separate from the second valve body 712. For example, the medium can push the second valve disc 73 upward, separating the second valve disc 73 from the second valve body 712, allowing the medium to enter the second chamber 713 from the third channel 7122.

[0241] For example, the third elastic element 74 can be a spring, a wave spring, etc., as shown in Figures 21-22 and 25-26, where the third elastic element 74 is a spring.

[0242] For example, the second valve plate 73 is constructed as a ring structure, with a hollow second valve plate hole at the center of the second valve plate 73, and the second channel 7121 is connected to the second chamber 713 through the second valve plate hole.

[0243] In some embodiments, referring to Figures 21-22 and 25-26, the second valve body 71 includes: a second valve seat 711 and a second valve body 712. The second valve seat 711 is mounted on the valve housing 6C, and a first channel 7111 is formed on the second valve seat 711. The second valve body 712 is mounted on the second valve seat 711, and a second channel 7121 and a third channel 7122 are formed on the second valve body 712.

[0244] For example, the connection between the second valve seat 711 and the valve housing 6C can be a threaded connection, a snap-fit ​​connection, a fastener connection, etc.

[0245] For example, the connection between the second valve body 712 and the second valve seat 711 can be a threaded connection, a snap-fit ​​connection, a fastener connection, etc.

[0246] In some embodiments, referring to Figures 21-22 and 25-26, the third channel 7122 is separated from the second channel 7121 in the radial direction of the second valve body 712.

[0247] In some embodiments, referring to Figures 21-22 and 25-26, the valve device 10C further includes a push rod 4C connected to the side of the pilot valve plug 2C away from the first valve body 11C. A drive assembly 8C drives the push rod 4C to move towards the first valve body 11C, thereby moving the pilot valve plug 2C. When the valve device 10C is not energized or is energized at a low current, the first valve body 11C experiences an axial displacement L under the hydraulic pressure of the lower oil. Under the action of the first elastic element 3C on the pilot valve plug 2C, the influence of the first valve body 11C and the oil on the axial distance D between the push rod 4C and the pilot valve plug 2C is reduced.

[0248] In some embodiments, referring to Figures 21-22 and 25-26, the pilot valve plug 2C has a push rod groove 23C, and one end of the push rod 4C extends into the push rod groove 23C. The axial distance D between the push rod 4C and the pilot valve plug 2C is the distance between the lower bottom wall of the push rod 4C and the bottom wall of the push rod groove 23C.

[0249] For example, the outer peripheral wall of push rod 4C and the peripheral wall of push rod groove 23C can be clearance fitted so that the relative axial distance between push rod 4C and pilot valve plug 2C can be adjusted.

[0250] In some embodiments, referring to Figures 21-28, the pilot valve plug 2C includes a valve plug body 21 and a valve plug skirt 22C. The valve plug skirt 22C is connected to the valve plug body 21 and extends radially outward along the valve plug body 21. The valve plug body 21 is adapted to open or block the pilot passage 111C, and one end of the first elastic member 3C abuts against the valve plug skirt 22C. By providing the valve plug skirt 22C, the elastic force of the first elastic member 3C on the pilot valve plug 2C can be made more uniform, and the pilot valve plug 2C is less prone to deflection.

[0251] In some embodiments, referring to Figures 23-24 and 27-28, the valve plug body 21 has a push rod guide surface 211C, an elastic element guide surface 212C, and a sealing surface 214. The outer peripheral wall of the push rod 4C is clearance-fitted with the push rod guide surface 211C. The first elastic element 3C is sleeved outside the elastic element guide surface 212C, and the elastic element guide surface 212C can limit the first elastic element 3C to prevent it from detaching from the pilot valve plug 2C. The valve plug skirt 22C has an elastic element abutment surface 213, and one end of the first elastic element 3C abuts against the elastic element abutment surface 213.

[0252] In some embodiments, the elastic contact surface 213 may be a plane, an arc surface, or the like.

[0253] In some embodiments, the sealing surface 214 may be a conical surface, an arc surface, etc.

[0254] In some embodiments, referring to Figures 21-22 and 25-26, the valve device 10C further includes a base valve seat 5C, and a drive assembly 8C is disposed on the side of the base valve seat 5C opposite to the pilot valve plug 2C. The base valve seat 5C has a push rod hole through which a push rod 4C passes.

[0255] In some embodiments, referring to Figures 21-22, one end of the first elastic member 3C abuts against the valve plug skirt 22C, and the other end of the first elastic member 3C abuts against the base valve seat 5C. The first elastic member 3C applies a force toward the first valve body 11C to the pilot valve plug 2C. By providing the valve plug skirt 22C on the outside of the pilot valve plug 2C and the first elastic member 3C in the upper region on the outside of the pilot valve plug 2C, when the valve device 10C is not energized or is energized at a low current, the first valve body 11C moves axially upward under the hydraulic action of the oil below. Under the action of the first elastic member 3C on the pilot valve plug 2C, the influence of the first valve body 11C on the push rod 4C and the pilot valve plug 2C in the axial distance D is reduced. When the flow resistance of the oil fluctuates greatly inside the damping controller 100C, the elastic force of the first elastic element 3C controls the axial fluctuation of the pilot valve plug 2C, thereby reducing the axial displacement fluctuation of the first valve body 11C, stabilizing the damping force of the system, and meeting the stable requirements of the shock absorber indication force value of vehicle 10000.

[0256] In some embodiments, referring to Figures 25-26, one end of the first elastic member 3C abuts against the valve plug skirt 22C, and the other end abuts against the first valve seat 12C. By providing the valve plug skirt 22C on the outside of the pilot valve plug 2C and providing the first elastic member 3C in the lower region on the outside of the pilot valve plug 2C, the first elastic member 3C ensures stable contact between the pilot valve plug 2C and the push rod 4C. When the flow resistance of the oil fluctuates greatly inside the damping controller 100C, the elastic force of the first elastic member 3C controls the axial fluctuation of the pilot valve plug 2C, thereby reducing the axial displacement fluctuation of the first valve body 11C, stabilizing the damping force of the system, and meeting the stable power value requirement of the shock absorber of vehicle 10000.

[0257] In some embodiments, referring to Figures 21-22 and 25-26, the drive assembly 8C is located on the side of the pilot valve plug 2C away from the first valve body 11C, for example, the drive assembly 8C is located above the pilot valve plug 2C. The drive assembly 8C includes a coil 81 and a magnetic core 82, the magnetic core 82 being fixedly connected to the push rod 4C, and the coil 81 being used to drive the magnetic core 82 to move.

[0258] For example, coil 81 is installed on base valve seat 5C, and magnetic core 82 is fixedly installed on the outer periphery of push rod 4C. When coil 81 drives magnetic core 82 to move, magnetic core 82 drives push rod 4C to move synchronously.

[0259] In some embodiments, referring to Figures 21-22 and 25-26, the drive assembly 8C further includes a fourth elastic member 83 and a fifth elastic member 84. The fourth elastic member 83 abuts against the magnetic core 82 to apply a force toward the pilot valve plug 2C to the magnetic core 82, and the fifth elastic member 84 abuts against the magnetic core 82 to apply a force away from the pilot valve plug 2C to the magnetic core 82. For example, the fourth elastic member 83 abuts against the end of the magnetic core 82 away from the pilot valve plug 2C, and the fifth elastic member 84 abuts against the end of the magnetic core 82 near the pilot valve plug 2C. Referring to Figure 21, the fourth elastic member 83 abuts against the upper end of the magnetic core 82, and the fifth elastic member 84 abuts against the lower end of the magnetic core 82.

[0260] Specifically, referring to Figures 21-22 and 25-26, the magnetic core 82 and the push rod 4C form a moving component. When the coil 81 is energized, the electromagnetic force drives the magnetic core 82 to move, which in turn moves the push rod 4C, thus moving the entire component and changing the opening state of the pilot valve plug 2C. When the coil 81 is de-energized, the fourth elastic element 83 and the fifth elastic element 84 work together to push the magnetic core 82 back to its original position. The magnetic core 82 then moves the push rod 4C back to its original position, changing the force exerted by the push rod 4C on the pilot valve plug 2C. The fourth elastic element 83 and the fifth elastic element 84 also provide double elastic support for the magnetic core 82, enabling it to remain stable under electromagnetic force and preventing deviation or wobbling, thereby improving the control accuracy and stability of the valve device 10C. The clearance fit between push rod 4C and pilot valve plug 2C can act as a damping effect, suppressing the vibration of pilot valve plug 2C during the opening process. In addition, push rod 4C acts as a guide structure, restricting the non-axial movement of pilot valve plug 2C and improving the stability of valve device 10C.

[0261] For example, the fourth elastic element 83 can be a spring, a wave spring, etc., as shown in Figures 21-22 and 25-26, where the fourth elastic element 83 is a spring.

[0262] For example, the fifth elastic element 84 can be a spring, a wave spring, etc., as shown in Figures 21-22 and 25-26, where the fifth elastic element 84 is a spring.

[0263] In some embodiments, referring to Figures 21-22 and 25-26, the drive assembly 8C further includes a housing 852 and an inner housing 851. The housing 852 covers at least a portion of the inner housing 851. The inner housing 851 is connected to the valve housing 6C, and a receiving cavity is formed inside the inner housing 851, where the coil 81 is located. Specifically, the housing 852 provides a safe and enclosed working environment for the inner housing 851, coil 81, magnetic core 82, etc., avoiding interference and damage from the external environment.

[0264] For example, the inner housing 851 and the valve housing 6C can be connected by threads, snap-fit, fasteners, etc.

[0265] In some embodiments, referring to Figures 21-22 and 25-26, the drive assembly 8C further includes coil enamel coating, a first guide sleeve 861, a second guide sleeve 862, an iron core cover 88, a magnetic shielding ring 89, and a locking sleeve 87. The coil enamel coating covers the outer wall of the coil 81. The first guide sleeve 861 guides the upper end of the push rod 4C, and the second guide sleeve 862 guides the upper end of the push rod 4C. The inner wall of the iron core cover 88 is fitted onto the outer wall of the magnetic core 82. The upper end of the magnetic shielding ring 89 abuts against the iron core cover 88, and the lower end of the magnetic shielding ring 89 forms the base valve seat 5C. Specifically, the coil enamel coating provides good protection and insulation. The first guide sleeve 861 and the second guide sleeve 862 enable the push rod 4C to be accurately positioned and supported, maintaining the stability and consistency of the internal structure of the drive assembly 8C. The second guide sleeve 862 can be installed inside the iron core cover 88 and can be installed inside the push rod hole of the base valve seat 5C. The iron core cover 88 provides a closed and stable magnetic field environment for the magnetic core 82, and the magnetic isolation ring 89 effectively isolates magnetic field interference. Through the close cooperation and layout of the above components, the overall structure of the drive assembly 8C is more compact and stable, improving the reliability and durability of the drive assembly 8C.

[0266] In some embodiments, the magnetic core 82 and the push rod 4C are made of soft magnetic materials and are magnetized in the coil 81, oriented in the same direction as the magnetic field of the coil 81, thereby generating an axial electromagnetic force. When the pilot valve plug 2C is working, the lower end face of the push rod 4C can abut against the pilot valve plug 2C. The axial electromagnetic force acts on the pilot valve plug 2C, affecting the second pressure threshold for opening the pilot valve plug 2C, which in turn affects the medium pressure in the receiving cavity 13C, and ultimately affects the third pressure threshold for opening the first valve body 11C, changing the pressure-flow characteristics of the valve device 10C. Different operating currents of the valve device 10C can control the electromagnetic force on the push rod 4C. The electromagnetic force is greater under high current conditions. Different electromagnetic forces result in different third pressure thresholds for opening the first valve body 11C, thus achieving regulation of the pressure-flow characteristics of the valve device 10C. The pressure-flow characteristics of the valve device 10C affect the damping force-velocity characteristics of the shock absorber. Different currents in the valve device 10C can achieve continuous control of the damper's damping, improving comfort and stability.

[0267] Referring to Figures 21-22, 25-26, and 31-37, a damping controller 100C according to some embodiments of the present disclosure includes a controller body 110C, a first valve device 10a, and a second valve device 10b. The controller body 110C has a first cavity 101 and a second cavity 102, which are connected. The first valve device 10a is installed in the first cavity 101, and the second valve device 10b is installed in the second cavity 102. The second valve device 10b is the same as the valve device 10 in the above embodiment. The medium outlet 61 and the third channel 7122 of the first valve device 10a are both connected to the first cavity 101. The medium outlet 61 and the third channel 7122 of the second valve device 10b are both connected to the second cavity 102. The second channel 7121 of the first valve device 10a is used to connect to the first device. The second channel 7121 of the second valve device 10b is used to connect to the second device to adjust the communication damping between the first device and the second device.

[0268] Both the first valve device 10a and the second valve device 10b are provided with a first elastic element 3C to control the smooth flow damping force of the oil between the first device and the second device.

[0269] The first valve device 10a is also called the recovery valve device, and the second valve device 10b is also called the compression valve device.

[0270] According to some disclosed embodiments of the damping controller 100C, its valve device 10C, by providing a first elastic element 3C, makes the fluctuations caused by the medium to the pilot valve plug 2C smaller, reduces the influence of the medium on the position of the pilot valve plug 2C and the first valve body 11C, makes the damping force inside the valve device 10C stable, and thus makes the damping force inside the damping controller 100C stable.

[0271] In some embodiments, referring to Figures 31-37, the controller body 110C further has a third cavity 103, and the first cavity 101 and the second cavity 102 are connected through the third cavity 103.

[0272] In some embodiments, referring to Figures 31-37, the controller body 110C further includes a fourth cavity 104 and a fifth cavity 105. The second channel 7121 of the first valve device 10a is connected to the fourth cavity 104, and the second channel 7121 of the second valve device 10b is connected to the fifth cavity 105. The first device is connected to the fourth cavity 104, and the second device is connected to the fifth cavity 105.

[0273] The damping controller 100C of some embodiments of this disclosure combines the first valve device 10a, the second valve device 10b, the first device, and the second device together through the controller body 110C to form a suspension damping control system 1000.

[0274] In some embodiments, the second channel 7121 of the first valve device 10a is used to connect to the third device, and the second channel 7121 of the second valve device 10b is used to connect to the fourth device. At this time, the third device and the first device are both connected to the fourth cavity 104, and the fourth device and the second device are both connected to the fifth cavity 105.

[0275] In some embodiments, referring to Figures 31-37, the controller body 110C further includes a damper interface 108, a central control cylinder interface 106, a stiffness conversion valve interface 107, and an accumulator interface 109. The central control cylinder interface 106 and the stiffness conversion valve interface 107 are both connected to the fourth cavity 104, and the damper interface 108 and the accumulator interface 109 are both connected to the fifth cavity 105. The first device is the central control cylinder, the second device is the damper, the third device is the stiffness conversion valve, and the fourth device is the accumulator. The damper is connected to the damper interface 108, the central control cylinder is connected to the central control cylinder interface 106, the stiffness conversion valve is connected to the stiffness conversion valve interface 107, and the accumulator is connected to the accumulator interface 109.

[0276] The damping controller 100C, through the controller body 110C, combines the first valve device 10a, the second valve device 10b, the accumulator, the stiffness conversion valve, the central control cylinder, and the shock absorber to form a suspension damping control system 1000.

[0277] In some embodiments, the stiffness switching valve is a normally open valve with a nitrogen-filled stiffness accumulator at the top, and the accumulator is filled with gas at a pressure of 1.7 MPa.

[0278] The central control cylinder is connected to four damping controllers 100C, which is the hydraulic system for the four-wheel balance of the vehicle. The central control cylinder is connected to an external gas compressible accumulator.

[0279] The accumulator interface 109 is for connecting an external gas compressible accumulator with an internal gas filling pressure of 1.5 MPa.

[0280] As shown in Figure 32, when the coil 81 of valve device 10C is not energized, the piston rod in the damper moves upward, and the oil in the central control cylinder and stiffness accumulator flows from the fourth chamber 104 of the damping controller 100C through the first chamber 101, the third chamber 103, and the second chamber 102 to the fifth chamber 105. The oil pushes open the first valve plate 72 in the first valve device 10a, enters the valve passage 62 inside the first valve device 10a, and flows into the pressure relief chamber 64 through the gap between the first valve body 11C and the protruding structure 63. Subsequently, the oil flows out from the medium outlet 61 of the first valve device 10a, first through the first chamber 101, then through the third chamber 103, and reaches the second chamber 102. Next, the oil pressure at the third channel 7122 of the second valve device 10b pushes open the second valve plate 73 of the second valve device 10b, allowing the oil to enter the second chamber 713 of the second valve device 10b. The oil in the second chamber 713 of the second valve device 10b flows from the second channel 7121 into the fifth chamber 105, and finally flows to the damper through the damper interface 108. During this process, the flow resistance through the valve device 10B is relatively small, and the damper exhibits a "soft" behavior. The path is shown in Figure 32 as A1→A2→A3→A4→A5.

[0281] As shown in Figure 33, when the coil 81 of valve device 10B is not energized, the piston rod of the damper moves downward. The oil in the damper flows from the fifth chamber 105 of the damping controller 100C through the second chamber 102, the third chamber 103, and the first chamber 101 to the fourth chamber 104. The oil pushes open the first valve plate 72 in the second valve device 10b and enters the valve passage 62 inside the second valve device 10b. It then flows into the pressure relief chamber 64 through the gap between the first valve body 11C and the protruding structure 63. Subsequently, the oil flows out from the medium outlet 61 of the second valve device 10b, first through the second chamber 102, then through the third chamber 103, and finally to the first chamber 101. Next, the oil pressure at the third channel 7122 of the first valve device 10a pushes open the second valve plate 73 of the first valve device 10a, allowing the oil to enter the second chamber 713 of the first valve device 10a. The oil in the second chamber 713 of the first valve device 10a flows into the fourth chamber 104 through the second channel 7121. Finally, the oil flows to the central control cylinder via the central control cylinder interface 106 and to the stiffness accumulator via the stiffness conversion valve interface 107. During this process, the flow resistance through the valve device 10 is relatively small, and the damper exhibits a "soft" behavior. The path is shown in Figure 33 as A6→A7→A8→A9→A10.

[0282] Referring to Figure 34, when the coil 81 of the valve device 10C is energized, the piston rod of the damper moves upward. The oil in the central control cylinder and stiffness accumulator flows from the fourth chamber 104 of the damping controller 100C through the first chamber 101, the third chamber 103, and the second chamber 102 to the fifth chamber 105. The oil pushes open the first valve plate 72 in the first valve device 10a. Since the valve device 10C is energized, the pilot valve plug 2C is in a state of blocking the pilot passage 111C. The oil pressure needs to overcome the thrust of the pilot valve plug 2C to enter the valve passage 62 inside the first valve device 10a (the damping force can be adjusted by inputting the current of the valve device 10C). Subsequently, the oil flows out from the first valve port 112C and pilot channel 111C into the first chamber 52, first through the base valve port 51 to reach the pressure relief chamber 64, then through the medium outlet 61 into the first chamber 101, and then through the third chamber 103 to reach the second chamber 102. Next, the oil pressure at the third channel 7122 of the second valve device 10b pushes open the second valve plate 73 of the second valve device 10b, entering the second chamber 713 of the second valve device 10b. The oil in the second chamber 713 of the second valve device 10b flows into the fifth chamber 105 through the second channel 7121, and finally flows to the damper through the damper interface 108. During this process, the flow resistance through the valve device 10 is relatively high, and the damper exhibits a "stiff" behavior. The path is shown in Figure 34 as A1→B2→A3→A4→A5.

[0283] Referring to Figure 35, when the oil pressure in the fourth chamber 104 of the damping controller 100C further increases, the oil pushes open the first valve body 11C of the second valve device 10b and flows out from the gap between the first valve body 11C and the protruding structure 63. It then flows through the medium outlet 61 of the second valve device 10b, the first chamber 101, the third chamber 103, the second chamber 102, the third channel 7122 of the second valve device 10b, the second chamber 713 of the second valve device 10b, the second channel 7121 of the second valve device 10b, and the fifth chamber 105 to the shock absorber. The path is shown in Figure 35 as A1→A2→A3→A4→A5.

[0284] Referring to Figure 36, when the coil 81 of the valve device 10 is energized, the piston rod of the damper moves upward. The oil in the central control cylinder and stiffness accumulator flows from the fifth chamber 105 of the damping controller 100C through the second chamber 102, the third chamber 103, and the first chamber 101 to the fourth chamber 104. The oil pushes open the first valve plate 72 in the second valve device 10b. Since the valve device 10C is energized, the pilot valve plug 2C is in the closed state. The oil pressure needs to overcome the thrust of the pilot valve plug 2C to enter the valve passage 62 inside the second valve device 10b (the damping force can be adjusted by inputting the current of the valve device 10C). Subsequently, the oil flows out from the first valve hole 112C and the pilot passage 111C to the first chamber 52, first through the base valve hole 51 to the pressure relief chamber 64, then through the medium outlet 61 into the first chamber 101, and then through the third chamber 103 to the first chamber 101. Next, the oil pressure at the third channel 7122 of the first valve device 10a pushes open the second valve plate 73 of the first valve device 10a, allowing the oil to enter the second chamber 713 of the first valve device 10a. The oil in the second chamber 713 of the first valve device 10a flows into the fourth chamber 104 through the second channel 7121. Finally, the oil flows to the central control cylinder via the central control cylinder interface 106 and to the stiffness accumulator via the stiffness conversion valve interface 107. During this process, the flow resistance through the valve device 10C is relatively high, resulting in a "stiff" vibration damper. The path is shown in Figure 36 as A6→B7→A8→A9→A10.

[0285] Referring to Figure 37, when the oil pressure in the fifth chamber 105 of the damping controller 100C further increases, the oil pushes open the first valve body 11C of the first valve device 10a and flows out from the gap between the first valve body 11C and the protruding structure 63. It then flows through the medium outlet 61 of the first valve device 10a, the second chamber 102, the third chamber 103, the first chamber 101, the third channel 7122 of the first valve device 10a, the second chamber 713 of the first valve device 10a, the second channel 7121 of the first valve device 10a, and the fourth chamber 104, eventually reaching the central control cylinder and the stiffness switching valve. The path is shown in Figure 17 as A6→A7→A8→A9→A10. When the damping force is too large and the pressure exceeds the pressure of the pressure-reducing accumulator, some oil will also flow to the pressure-reducing accumulator, as shown in Figure 37 as A11.

[0286] Referring to Figures 31-38, a suspension damping control system 1000 according to some embodiments of the present disclosure includes the aforementioned damping controller 100C, a first device being a central control cylinder, and a second device being a shock absorber. Here, the shock absorber is connected to the shock absorber interface 108, and the central control cylinder is connected to the central control cylinder interface 106.

[0287] According to some embodiments of the suspension damping control system 1000 of the present disclosure, the valve device 10C of the damping controller 100C is provided with a first elastic element 3C, so that the fluctuation caused by the medium to the pilot valve plug 2C is small, the influence of the medium on the position of the pilot valve plug 2C and the first valve body 11C is reduced, so that the damping force inside the valve device 10 is stable, thereby stabilizing the damping force of the suspension damping control system 1000.

[0288] In some embodiments, the suspension damping control system 1000 further includes a stiffness switching valve, and both the stiffness switching valve and the central control cylinder are connected to the second channel 7121 of the first valve device 10a. The controller body 110C has a stiffness switching valve interface 107 communicating with the fourth chamber 104, and the stiffness switching valve is connected to the stiffness switching valve interface 107.

[0289] In some embodiments, the suspension damping control system 1000 further includes an accumulator, and both the accumulator and the shock absorber are connected to the second channel 7121 of the second valve device 10b. The controller body 110C has an accumulator interface 109 communicating with the fifth chamber 105, and the accumulator is connected to the accumulator interface 109.

[0290] It is understandable that the medium flowing inside the damping controller 100C and the valve device 10C can be oil, gas, gas-liquid mixture or other media.

[0291] Referring to FIG39, a vehicle 10000 according to some embodiments of the present disclosure includes the suspension damping control system 1000 of the above embodiments.

[0292] According to some embodiments of the present disclosure, the valve device 10C of the suspension damping control system 1000 is provided with a first elastic element 3C, which makes the fluctuation of the medium on the pilot valve plug 2C smaller, reduces the influence of the medium on the position of the pilot valve plug 2C and the first valve body 11C, stabilizes the damping force inside the valve device 10C, and thus stabilizes the damping force of the suspension damping control system 1000.

[0293] A gear pump is a rotary pump that transports or pressurizes liquids by relying on the change and movement of the working volume formed between the pump cylinder and meshing gears. It consists of two gears, a pump body, and front and rear covers forming two enclosed spaces. When the gears rotate, the volume of the space on the disengaged side of the gears increases from small to large, creating a vacuum that draws in the liquid. Conversely, the volume of the space on the meshing side of the gears decreases from large to small, forcing the liquid into the pipeline.

[0294] In related technologies, gears are susceptible to undercutting, resulting in reduced transmission overlap and consequently, unstable gear transmission and low volumetric efficiency. To address these issues, this disclosure provides embodiments of a gear pump, a suspension system, and a vehicle.

[0295] The gear pump 100 according to some embodiments of the present disclosure is described below with reference to Figures 40-51.

[0296] As shown in FIG40, a gear pump 100 according to some embodiments of the present disclosure includes a pump body 1 and a gear set 2.

[0297] For example, a first cavity 14 and a second cavity 15 are formed inside the pump body 1. At least a part of the gear set 2 is disposed inside the pump body 1. The gear set 2 includes a first gear 21 and a second gear 22. The teeth of the first gear 21 and the teeth of the second gear 22 mesh with each other. The first cavity 14 and the second cavity 15 are separated by the meshing line of the first gear 21 and the second gear 22. The number of teeth of the first gear 21 and the number of teeth of the second gear 22 are both N. For example, N satisfies: N≥13.

[0298] For example, in the examples of Figures 40, 48, and 49, the upper and middle portions of gear set 2 (i.e., at least a portion of gear set 2) are located inside pump body 1. First cavity 14 is located in front of the meshing line of first gear 21 and second gear 22 (i.e., to the right of first gear 21 in Figure 49), and second cavity 15 is located behind the meshing line of first gear 21 and second gear 22 (i.e., to the left of first gear 21 in Figure 49). For example, first cavity 14 is the low-pressure zone (also known as the oil suction zone) of gear pump 100, and first cavity 14 is the high-pressure zone (also known as the oil discharge zone) of gear pump 100. During the use of gear pump 100, the first gear 21 and the second gear 22 rotate in cooperation within the pump body 1. The front sides of the first gear 21 and the second gear 22 disengage, the volume of the first chamber 14 increases from small to large, the pressure decreases to form a vacuum, and liquid (e.g., oil) is drawn in. The rear sides of the first gear 21 and the second gear 22 mesh, the volume of the second chamber 15 decreases from large to small, and the liquid is squeezed out. The flow path of the liquid is in the direction indicated by arrow A in Figure 49.

[0299] When the number of teeth of the first gear 21 and the second gear 22 is less than 13, the relatively small number of teeth in the first gear 21 and the second gear 22 makes it prone to undercutting during the operation of the gear pump 100. This occurs when the intersection of the tooth tip of the first gear 21 and the line of engagement exceeds the limit engagement point of the second gear 22, resulting in the involute tooth profile of the tooth root of the second gear 22 being partially cut off. This reduces the overlap ratio of the gear set 2, decreases the smoothness of the transmission process of the first gear 21 and the second gear 22, causes the gear pump 100 to vibrate during operation, resulting in greater noise from the gear pump 100, and also reduces the volumetric efficiency of the gear pump 100, thereby reducing the performance of the gear pump 100.

[0300] When the number of teeth of the first gear 21 and the second gear 22 are both greater than or equal to 13, for example, according to Table 1, experimental verification shows that when the number of teeth of the first gear 21 and the second gear 22 are both 13, the overlap ratio of the first gear 21 and the second gear 22 can reach 1.683, which is significantly higher than the overlap ratio (1.306) when the number of teeth is 12 in the traditional technology. This effectively reduces the probability of undercutting in the gear pump 100, thereby improving the smoothness of the rotation of the first gear 21 and the second gear 22, further reducing the probability of oil leakage, improving volumetric efficiency, and extending the service life of the gear pump 100. Moreover, while improving the smoothness of the rotation of the first gear 21 and the second gear 22, it also reduces the vibration during the rotation of the first gear 21 and the second gear 22, thereby reducing the noise of the gear pump 100.

[0301] Therefore, by setting the number of teeth of both the first gear 21 and the second gear 22 to satisfy N≥13, the number of teeth of the first gear 21 and the second gear 22 is reasonably set, improving the overlap during the operation of the first gear 21 and the second gear 22. This effectively reduces the probability of undercutting of the first gear 21 and the second gear 22, improves the smoothness of rotation of the first gear 21 and the second gear 22, avoids vibration, and thus reduces the noise of the gear pump 100, reduces the probability of oil leakage, improves volumetric efficiency, and extends the service life of the gear pump 100. For example, in conventional technology, the noise generated by the gear pump 100 is mostly above 75dB, while the noise of the gear pump 100 in this application is below 68dB, making the gear pump 100 more than 10% better than the industry average in terms of noise.

[0302] According to some embodiments of the gear pump 100 disclosed herein, the number of teeth of the first gear 21 and the second gear 22 are reasonably set. Compared with the conventional technology where the number of teeth of the gear is 12, the overlap of the first gear 21 and the second gear 22 is improved, the probability of undercutting of the gear pump 100 is reduced, thereby improving the smoothness of rotation of the first gear 21 and the second gear 22, reducing the noise generated by the gear pump 100, reducing the probability of oil leakage, improving volumetric efficiency, and thus improving the performance of the gear pump 100.

[0303] According to some embodiments of this disclosure, N further satisfies: 13 ≤ N ≤ 17. For example, when the number of teeth N of the first gear 21 and the second gear 22 is both greater than 17, and the dimensions of the first gear 21 and the second gear 22 remain unchanged, the teeth of the first gear 21 and the second gear 22 are relatively thin, which reduces the structural strength of the first gear 21 and the second gear 22. After long-term use, the teeth on the first gear 21 and the second gear 22 are prone to breakage, thereby shortening the service life of the gear pump 100. In addition, the large number of teeth of the first gear 21 and the second gear 22 increases the processing difficulty of the first gear 21 and the second gear 22, making them difficult to manufacture.

[0304] Therefore, by setting N to further satisfy 13≤N≤17, the number of teeth of the first gear 21 and the second gear 22 is reasonably set. While ensuring that the probability of undercutting of the first gear 21 and the second gear 22 is reduced, the thickness of the teeth of the first gear 21 and the second gear 22 is increased, improving the structural strength of the first gear 21 and the second gear 22, reducing the probability of tooth breakage of the first gear 21 and the second gear 22, thereby extending the service life of the first gear 21 and the second gear 22, allowing the gear pump 100 to be used normally for a long time. In addition, the number of teeth of the first gear 21 and the second gear 22 is reduced, reducing the machining difficulty of the first gear 21 and the second gear 22, and improving the production efficiency of the gear pump 100.

[0305] According to some embodiments of this disclosure, N satisfies: 13 ≤ N ≤ 15. This further improves the structural strength of the first gear 21 and the second gear 22, thereby further extending the service life of the gear pump 100 to better meet the actual production and use requirements of the gear pump 100. Moreover, it also further reduces the machining difficulty of the first gear 21 and the second gear 22.

[0306] According to some embodiments of this disclosure, the pressure angle of gear set 2 is w, for example, w satisfies: 20° ≤ w ≤ 28°. For example, when the pressure angle of gear set 2 is less than 20°, the pressure angle of gear set 2 is small, which reduces the overlap ratio of gear pump 100, reduces the transmission efficiency of gear set 2, and increases the noise of gear pump 100. When the pressure angle of gear set 2 is greater than 28°, the pressure angle of gear set 2 is large, which increases the torque of gear pump 100, thereby reducing volumetric efficiency.

[0307] Therefore, by setting the pressure angle w of gear set 2 to satisfy 20°≤w≤28°, the pressure angle of gear set 2 is reasonably set, further increasing the overlap ratio of gear pump 100, improving the transmission efficiency of gear set 2, and further reducing the noise of gear pump 100. Furthermore, it reduces the torque of gear pump 100, thereby further improving the volumetric efficiency of gear pump 100 and further enhancing its performance. For example, the pressure angle could be 24°.

[0308] According to some embodiments of this disclosure, w further satisfies: 23°≤w≤26°. For example, when the displacement of the gear pump 100 is 0.3 ml / r, and the number of teeth on both the first gear 21 shaft and the second gear 22 shaft is 13, the pressure angle is 24°, which has the same performance effect as a pressure angle between 23° and 26°.

[0309] In some embodiments, referring to Figures 40, 44, and 45, the gear set 2 further includes a first gear shaft 23 and a second gear shaft 24, with the first gear 21 and the second gear 22 located on the outer periphery of the first gear shaft 23 and the second gear shaft 24, respectively. For example, in the examples of Figures 40, 44, and 45, the first gear 21 is located on the outer periphery of the first gear shaft 23, and the second gear 22 is located on the outer periphery of the second gear shaft 24. The first gear 21 rotates along the central axis of the first gear shaft 23, and the second gear 22 rotates along the central axis of the second gear shaft 24. Thus, the first gear 21 and the second gear 22 are driven to rotate by the first gear shaft 23 and the second gear shaft 24, respectively, facilitating the meshing of the first gear 21 and the second gear 22.

[0310] Referring to Figures 40 and 41, the gear pump 100 also includes a bushing 25, which includes a first bushing portion 251 and a second bushing portion 252. The first bushing portion 251 and the second bushing portion 252 are respectively sleeved on the first gear shaft 23 and the second gear shaft 24. The bushing 25 is an integral structural component.

[0311] For example, in the examples of Figures 40 and 41, the first bushing 251 is fitted onto the first gear shaft 23, and the lower end face of the first bushing 251 contacts the upper side face of the first gear 21. The second bushing 252 is fitted onto the second gear shaft 24, and the lower end face of the second bushing 252 contacts the upper side face of the second gear 22. This configuration makes the bushing 25 a single integral structure, ensuring a firm connection between the first bushing 251 and the second bushing 252. This helps improve the smoothness of the transmission between the first gear shaft 23 and the second gear shaft 24, and reduces the noise of the gear pump 100. Furthermore, it reduces the manufacturing difficulty of the contact surfaces on the pump body 1 that contact the outer periphery of the bushing 25 (such as the side wall of the second mounting groove 121 on the second pump body 12), thereby reducing the manufacturing difficulty of the gear pump 100 and improving its production efficiency. It should be noted that the bushing 25 can also be a one-piece molded part, which allows the first bushing part 251 and the second bushing part 252 to be quickly connected into one piece, making processing more convenient and improving the production efficiency of the bushing 25. For example, the bushing 25 can be machined into a one-piece molded part by a CNC milling machine, which is efficient and low-cost.

[0312] According to some embodiments of this disclosure, referring to Figures 41 and 43, the first bushing portion 251 and the second bushing portion 252 are arranged along a first direction (the left-right direction as shown in Figure 41). A first unloading groove 253 and a second unloading groove 254 are formed on the side surface of the bushing 25 facing the first gear 21. The first unloading groove 253 and the second unloading groove 254 are arranged at intervals along a second direction (the front-back direction as shown in Figure 41). The first unloading groove 253 and the second unloading groove 254 are asymmetrically arranged about the center line of the bushing 25 along the first direction. The first direction and the second direction are perpendicular.

[0313] For example, in the examples of Figures 41, 42, and 43, the first unloading groove 253 and the second unloading groove 254 are formed at the connection between the first bushing portion 251 and the second bushing portion 252, and the first unloading groove 253 and the second unloading groove 254 are spaced apart. This asymmetrical arrangement of the first unloading groove 253 and the second unloading groove 254 reduces the difficulty of machining the machining center equipment on the CNC milling machine, improves the production efficiency of the bushing 25, and also improves the sealing performance of the gear pump 100, preventing oil leakage and allowing the gear pump 100 to operate normally for a longer period. Furthermore, the asymmetrical arrangement, combined with the high overlap of the gear set 2, solves the oil trapping problem, improves transmission smoothness, and thus improves the volumetric efficiency, flow rate, current, noise, and other performance indicators of the gear pump 100, leading the industry level by 10% to 20%.

[0314] According to some embodiments of this disclosure, referring to FIG43, the first unloading groove 253 and the second unloading groove 254 extend along a second direction (the front-back direction shown in FIG43), and the lengths of the first unloading groove 253 and the second unloading groove 254 are different.

[0315] This configuration, with the first unloading groove 253 and the second unloading groove 254 having different lengths, effectively ensures the asymmetrical arrangement of the first unloading groove 253 and the second unloading groove 254. This effectively reduces the impact of trapped and leaking oil on the performance of the gear pump 100, thereby improving the volumetric efficiency, mechanical efficiency, and overall efficiency of the gear pump 100. It should be noted that the ends of the first unloading groove 253 and the second unloading groove 254 that are far apart from each other penetrate the side wall of the bushing 25. During the use of the gear pump 100, this facilitates the entry of liquid into the first unloading groove 253 and the second unloading groove 254, preventing trapped oil and reducing its impact on the gear pump 100.

[0316] According to some embodiments of this disclosure, referring to FIG43, the distance between the end of the first unloading groove 253 near the center line of the bushing 25 and the center line is L1. For example, L1 satisfies: 1.45mm≤L1≤1.55mm.

[0317] For example, when the distance between the end of the first unloading groove 253 near the centerline of the bushing 25 and the centerline is less than 1.45mm, the distance between the front end of the first unloading groove 253 and the centerline is small, which easily leads to oil leakage and reduces the volumetric efficiency of the gear pump 100. When the distance between the end of the first unloading groove 253 near the centerline of the bushing 25 and the centerline is greater than 1.55mm, the distance between the front end of the first unloading groove 253 and the centerline is large, which easily leads to oil trapping and reduces the volumetric efficiency of the gear pump 100. Therefore, by setting the distance L1 between the end of the first unloading groove 253 near the centerline of the bushing 25 and the centerline to satisfy: 1.45mm≤L1≤1.55mm, the distance between the front end of the first unloading groove 253 and the centerline is reasonably set, effectively reducing the impact of oil trapping and leakage on the performance of the gear pump 100, thereby improving the volumetric efficiency of the gear pump 100 and also improving the overall efficiency. For example, L1 can be 1.50mm.

[0318] According to other embodiments of this disclosure, referring to FIG43, the distance between the end of the second unloading groove 254 near the center line of the bushing 25 and the center line is L2. For example, L2 satisfies: 0.77mm ≤ L2 ≤ 0.83mm. For example, when the distance between the end of the second unloading groove 254 near the center line of the bushing 25 and the center line is less than 0.77mm, the distance between the rear end of the second unloading groove 254 and the center line is small, which easily leads to oil leakage and reduces the volumetric efficiency of the gear pump 100. When the distance between the end of the second unloading groove 254 near the center line of the bushing 25 and the center line is greater than 0.83mm, the distance between the rear end of the second unloading groove 254 and the center line is large, which easily leads to oil trapping and reduces the volumetric efficiency of the gear pump 100. Therefore, by setting the distance L2 between the end of the second unloading groove 254 closest to the centerline of the bushing 25 and the centerline to satisfy 0.77mm≤L2≤0.83mm, the distance between the front end of the second unloading groove 254 and the centerline is reasonably set, effectively reducing the impact of trapped oil and oil leakage on the performance of the gear pump 100, thereby improving the volumetric efficiency of the gear pump 100 and the overall efficiency of the assembly. For example, L2 can be 0.80mm.

[0319] According to further embodiments of this disclosure, referring to FIG43, the distance between the end of the first unloading groove 253 near the centerline of the bushing 25 and the centerline is L1, and the distance between the end of the second unloading groove 254 near the centerline of the bushing 25 and the centerline is L2. For example, L1 and L2 satisfy: 1.45mm≤L1≤1.55mm, 0.77mm≤L2≤0.83mm respectively. Therefore, the distances between the front end of the first unloading groove 253 and the rear end of the second unloading groove 254 and the centerline are reasonably set, effectively reducing the impact of trapped oil and oil leakage on the performance of the gear pump 100, thereby improving the volumetric efficiency of the gear pump 100 and the overall assembly efficiency.

[0320] According to some embodiments of this disclosure, referring to FIG43, the distance between the end of the first unloading groove 253 away from the center line of the bushing 25 and the center line is L3. For example, L3 satisfies: 3.97mm≤L3≤7.10mm. For example, when the distance between the end of the first unloading groove 253 away from the center line of the bushing 25 and the center line is less than 3.97mm, the distance between the rear end of the first unloading groove 253 and the center line is small, which increases the gap between the side wall of the bushing 25 at the first unloading groove 253 and the pump body 1 mounting location (i.e., the side wall of the second mounting groove 121 of the second pump body 12). During use, the gear pump 100 will have oil leakage problems, which reduces the performance of the gear pump 100 in performance tests (e.g., torque, volumetric efficiency, current, flow rate, and pressure). When the distance between the end of the first unloading groove 253 away from the center line of the bushing 25 and the center line is greater than 7.10mm, the distance between the rear end of the first unloading groove 253 and the center line is large, which reduces the gap between the side wall of the bushing 25 at the first unloading groove 253 and the installation location of the pump body 1, and the bushing 25 cannot be installed into the second pump body 12 of the pump body 1.

[0321] Therefore, by setting the distance L3 between the end of the first unloading groove 253 away from the centerline of the bushing 25 and the centerline to satisfy 3.97mm≤L3≤7.10mm, the distance between the rear end of the first unloading groove 253 and the centerline is reasonably set, and the gap between the side wall of the bushing 25 at the first unloading groove 253 and the installation location of the pump body 1 is reasonably set, thus avoiding oil leakage problems, improving the performance of the gear pump 100 in performance testing, and improving the usability of the gear pump 100. Furthermore, it also allows the bushing 25 to be installed into the pump body 1, enabling the gear pump 100 to be installed normally. For example, L3 can further satisfy 5.18mm≤L3≤5.20mm, and L3 can be 5.19mm.

[0322] According to some embodiments of this disclosure, referring to FIG43, the distance between the end of the second unloading groove 254 away from the center line of the bushing 25 and the center line is L4. For example, L4 satisfies: 3.97mm≤L4≤7.10mm. For example, when the distance between the end of the second unloading groove 254 away from the center line of the bushing 25 and the center line is less than 3.97mm, the distance between the front end of the second unloading groove 254 and the center line is small, which increases the gap between the side wall of the bushing 25 and the side wall of the second mounting groove 121 at the second unloading groove 254. This can cause oil leakage in the gear pump 100 during use, reducing the performance of the gear pump 100 in performance tests. When the distance between the end of the second unloading groove 254 away from the center line of the bushing 25 and the center line is greater than 7.10 mm, the distance between the rear end of the second unloading groove 254 and the center line is large, which reduces the gap between the side wall of the bushing 25 at the second unloading groove 254 and the side wall of the second mounting groove 121 of the pump body 1, and the bushing 25 cannot be installed into the pump body 1.

[0323] Therefore, by setting the distance L4 between the end of the second unloading groove 254 away from the centerline of the bushing 25 and the centerline to satisfy 3.97mm≤L4≤7.10mm, the distance between the front end of the second unloading groove 254 and the centerline is reasonably set, and the gap between the side wall of the bushing 25 at the second unloading groove 254 and the side wall of the second mounting groove 121 is reasonably set, thus avoiding oil leakage problems, improving the performance of the gear pump 100 in performance testing, and improving the usability of the gear pump 100. Furthermore, it also allows the bushing 25 to be installed into the pump body 1, enabling the gear pump 100 to be installed normally. For example, L4 further satisfies 5.18mm≤L4≤5.20mm, and L4 can be 5.19mm. For example, the depth of both the first unloading groove 253 and the second unloading groove 254 in the vertical direction can be d, where d satisfies 0.5mm≤d≤1.5mm, thereby eliminating oil trapping and preventing oil leakage. For example, d can be 1mm.

[0324] According to some embodiments of this disclosure, referring to FIG43, the distance between the end of the first unloading groove 253 away from the centerline of the bushing 25 and the centerline is L3, and the distance between the end of the second unloading groove 254 away from the centerline of the bushing 25 and the centerline is L4. For example, L3 and L4 satisfy: 3.97mm≤L3≤7.10mm and 3.97mm≤L4≤7.10mm, respectively. Therefore, the distances between the rear end of the first unloading groove 253 and the front end of the second unloading groove 254 and the centerline are reasonably set, and the gap between the side wall of the bushing 25 and the side wall of the second mounting groove 121 is reasonably set, avoiding oil leakage problems, improving the performance of the gear pump 100 in performance testing, and improving the usability of the gear pump 100. Furthermore, it also allows the bushing 25 to be installed into the pump body 1, enabling the gear pump 100 to be installed normally. It should be noted that the distance between the end of the first unloading groove 253 furthest from the center line of the bushing 25 and the end of the second unloading groove 254 furthest from the center line of the bushing 25 is L5, that is, L5 is the sum of L3 and L4. For example, L5 satisfies: 7.94mm≤L5≤14.2mm. The size setting of the bushing 25 is reasonable, which solves the oil leakage problem and facilitates installation. For example, the single-sided clearance can be set to 0.01mm, and the double-sided clearance can be set to 0.02mm.

[0325] According to some embodiments of this disclosure, referring to FIG43, the inner wall surface of the first unloading groove 253 near the center line transitions with the inner walls of the two sides of the first unloading groove 253 along the first direction (i.e., the left-right direction) at a first fillet 2531; and / or, the inner wall surface of the second unloading groove 254 near the center line transitions with the inner walls of the two sides of the second unloading groove 254 along the first direction at a second fillet 2541.

[0326] For example, the inner wall surfaces of the first unloading groove 253 and the second unloading groove 254 near their center lines are configured in the following ways: First, the inner wall surface of the first unloading groove 253 near its center line transitions with the inner walls of the first unloading groove 253 on both sides along the first direction using a first fillet 2531. Second, the inner wall surface of the second unloading groove 254 near its center line transitions with the inner walls of the second unloading groove 254 on both sides along the first direction using a second fillet 2541. Third, the inner wall surface of the first unloading groove 253 near its center line transitions with the inner walls of the first unloading groove 253 on both sides along the first direction using a first fillet 2531. Simultaneously, the inner wall surface of the second unloading groove 254 near its center line transitions with the inner walls of the second unloading groove 254 on both sides along the first direction using a second fillet 2541.

[0327] Therefore, the design of the first fillet 2531 and the second fillet 2541 further avoids the problem of oil trapping in the gear pump 100, thereby further improving the performance of the gear pump 100. In addition, the design of the first fillet 2531 and the second fillet 2541 is simple and easy to process, which improves the production efficiency of the bushing 25.

[0328] According to some embodiments of this disclosure, referring to FIG43, the radius of the first fillet 2531 is r1, for example, r1 satisfies: 0.45mm ≤ r1 ≤ 1.05mm. For example, the first fillet 2531 is a part of a circle with radius r1. When the radius of the first fillet 2531 is less than 0.45mm, the radius of the first fillet 2531 is small, the first fillet 2531 is close to a right angle, and enters the oil trapping area, which easily leads to oil leakage. When the radius of the first fillet 2531 is greater than 1.05mm, the radius of the first fillet 2531 is large, far from the oil trapping area, which easily leads to oil trapping problems. Therefore, by setting the radius r1 of the first fillet 2531 to satisfy: 0.45mm ≤ r1 ≤ 1.05mm, the problems of oil leakage and oil trapping are effectively avoided, thereby effectively improving the efficiency of the gear pump 100 and improving the performance of the gear pump 100. For example, r1 can be 0.75mm.

[0329] According to other embodiments of this disclosure, referring to FIG43, the radius of the second fillet 2541 is r2, for example, r2 satisfies: 0.45mm ≤ r2 ≤ 1.05mm. For example, the second fillet 2541 is a part of a circle with radius r2. When the radius of the second fillet 2541 is less than 0.45mm, the radius of the second fillet 2541 is small, the second fillet 2541 is close to a right angle, and it enters the oil trapping area, which easily leads to oil leakage. When the radius of the second fillet 2541 is greater than 1.05mm, the radius of the second fillet 2541 is large, it is far from the oil trapping area, and it is easy to cause oil trapping problems. Therefore, by setting the radius r1 of the second fillet 2541 to satisfy: 0.45mm ≤ r1 ≤ 1.05mm, the problems of oil leakage and oil trapping are effectively avoided, thereby effectively improving the efficiency of the gear pump 100 and improving the performance of the gear pump 100. For example, r2 can be 0.75mm.

[0330] According to further embodiments of this disclosure, referring to FIG43, the radius of the first fillet 2531 is r1, and the radius of the second fillet 2541 is r2. For example, r1 and r2 satisfy: 0.45mm≤r1≤1.05mm, 0.45mm≤r2≤1.05mm respectively. Thus, the radii of the first fillet 2531 and the second fillet 2541 are reasonably set, effectively avoiding oil leakage and oil trapping problems, thereby effectively improving the efficiency and performance of the gear pump 100. Furthermore, the design of the number of teeth of the bushing 25, the first gear 21, and the second gear 22 reduces the difficulty of manufacturing processes, improves sealing performance, and enhances transmission smoothness. The overlap ratio is increased from the industry standard of 1.3 to 1.68. Therefore, due to the gear pump 100 factor, the assembly noise is reduced from the industry standard of 75dB to 68dB, achieving an industry-leading high efficiency of 91% to 99% volumetric efficiency.

[0331] In some embodiments, the inner wall surface of the first unloading groove 253 near the center line is connected to the inner walls of the two sides of the first unloading groove 253 along the first direction by a first arc surface (not shown in the figure), the first arc surface being a part of a first cylindrical surface with a radius of r3, for example, r3 satisfying: 0.45mm≤r3≤1.05mm; and / or, the inner walls of the two sides of the second unloading groove 254 along the first direction are connected by a second arc surface (not shown in the figure), the second arc surface being a part of a second cylindrical surface with a radius of r4, for example, r4 satisfying: 0.45mm≤r4≤1.05mm.

[0332] For example, the inner wall surfaces of the first unloading groove 253 and the second unloading groove 254 near their center lines are configured in the following ways: First, the inner wall surface of the first unloading groove 253 near its center line is connected to the inner walls of both sides of the first unloading groove 253 along the first direction via a first arc surface. The first arc surface is a portion of a first cylindrical surface with a radius of r3, for example, r3 satisfies: 0.45mm ≤ r3 ≤ 1.05mm. Second, the inner walls of the second unloading groove 254 along the first direction are connected to each other via a second arc surface. The second arc surface is a portion of a second cylindrical surface with a radius of r4, for example, r4 satisfies: 0.45mm ≤ r4 ≤ 1.05mm. Third, the inner wall surface of the first unloading groove 253 near the center line is connected to the inner walls of the two sides of the first unloading groove 253 along the first direction through a first arc surface. The first arc surface is a part of a first cylindrical surface with a radius of r3. The inner walls of the two sides of the second unloading groove 254 along the first direction are connected through a second arc surface. The second arc surface is a part of a second cylindrical surface with a radius of r4. For example, r3 and r4 satisfy: 0.45mm≤r3≤1.05mm and 0.45mm≤r4≤1.05mm respectively.

[0333] For example, the first and second cylindrical surfaces are the outer circumferences of a cylinder, and the cross-sectional shapes of the first and second arc surfaces are both arc-shaped. This design ensures that the radii of the first and second arc surfaces are appropriately set, effectively preventing oil leakage and oil trapping, thereby significantly improving the efficiency and performance of the gear pump 100. Furthermore, the simple structure of the first and second arc surfaces facilitates their fabrication, thus increasing the production efficiency of the bushing 25. For example, r3 and r4 can each be 0.75 mm.

[0334] In some embodiments, referring to Figures 41 and 43, the connection between the sidewall of the first unloading groove 253 at the end away from the center line and the side circumferential surface of the bushing 25 is a third rounded corner 255, and the connection between the sidewall of the second unloading groove 254 at the end away from the center line and the side circumferential surface of the bushing 25 is a fourth rounded corner 256. This configuration avoids the formation of burrs during processing at the connection between the first unloading groove 253 and the sidewall of the bushing 25, and at the connection between the second unloading groove 254 and the sidewall of the bushing 25. This prevents burrs from increasing the gap between the bushing 25 and the second mounting groove 121, and also prevents burrs from scratching the sidewall of the second mounting groove 121, thereby preventing oil leakage. For example, as shown in Figure 43, the third fillet 255 is part of a circle with radius r5, where r5 satisfies: 0.25mm ≤ r5 ≤ 45mm. When r5 is 0.25mm, the edge of the third fillet 255 is shown as line C; when r5 is 45mm, the edge of the third fillet 255 is shown as line B. r5 further satisfies: 2.8mm ≤ r5 ≤ 2.82mm. The fourth fillet 255 is part of a circle with radius r6, where r6 satisfies: 0.25mm ≤ r6 ≤ 45mm. When r6 is 0.25mm, the edge of the fourth fillet 256 is shown as line E; when r6 is 45mm, the fourth fillet 256 is shown as line D. r6 further satisfies: 2.5mm ≤ r6 ≤ 2.52mm.

[0335] When the displacement of gear pump 100 is 0.3 ml / r, the number of teeth of the first gear 21 and the second gear 22 are 13 respectively (as shown in Figures 46 and 47), the module is 1.0, the pressure angle is 24°, the shift coefficient is 0.03, the helix angle is 0°, the addendum coefficient is 1.25, the base circle pitch is 2.84, and the base circle diameter is 11.88 mm, the overlap ratio can reach 1.68, thereby improving the transmission smoothness of gear pump 100 and achieving an industry-leading volumetric efficiency of 91% to 99%, while reducing noise from the industry average of 75 dB to 68 dB. For example, gear pump 100's noise level is more than 10% higher than the industry average, its volumetric efficiency is more than 15% higher than the industry average, its flow rate is more than 10% higher than the industry average, and its wear is reduced, extending its service life. See Table 1 below.

[0336] Table 1 Overlapping Degree of Gear Pumps

[0337] It should be noted that, in order to ensure the smoothness of the gear pump 100 transmission, the overlap ratio is generally required to be greater than or equal to 1.2, and the higher the value, the better. In Table 1, compared with the prior art gear pumps where the number of teeth of the first gear and the number of teeth of the second gear are 12, the gear pump 100 of this application has a larger overlap ratio and better performance.

[0338] In some embodiments, referring to Figures 40 and 48, the pump body 1 includes a first pump body 11 and a second pump body 12 arranged and connected along a third direction (the up and down direction as shown in Figure 40). A first mounting groove 111 is formed on the first pump body 11, and a second mounting groove 121 is formed on the second pump body 12. The second mounting groove 121 and the first mounting groove 111 together define an installation space 13. The gear set 2 is disposed in the installation space 13, and the third direction is the extension direction of the first gear shaft 23.

[0339] For example, in the examples of Figures 40 and 48, the first pump body 11 is located above the second pump body 12. After the first pump body 11 and the second pump body 12 are assembled, the first mounting groove 111 and the second mounting groove 121 communicate to jointly define the installation space 13. The upper part of the bushing 25 fits in the first mounting groove 111, and the lower part of the bushing 25 fits in the second mounting groove 121. With this arrangement, the pump body 1 encloses the bushing 25, that is, the pump body 1 protects the bushing 25, avoiding damage to the bushing 25, thereby extending the service life of the bushing 25. Moreover, the arrangement of the bushing 25 also improves the sealing performance of the gear set 2 and the pump body 1 assembly. In addition, the arrangement of the first pump body 11 and the second pump body 12 facilitates the assembly of the pump body 1 and the bushing 25, reduces the installation difficulty of the gear pump 100, and thus improves the installation efficiency of the gear pump 100.

[0340] For example, as shown in Figures 40 and 50, the side wall of the second mounting groove 112 is fitted with the outer peripheral surface of the bushing 25, that is, the shape of the side wall of the second mounting groove 112 is adapted to the shape of the outer peripheral surface of the bushing 25. The side wall of the second mounting groove 121 has a relative fifth fillet 1211 and a sixth fillet (not shown in the figure). The fifth fillet 1211 is concave inward and transitions to an arc surface, that is, the fifth fillet 1211 is part of a circle with radius r7, and r7 satisfies: 0.25mm≤r7≤45mm. The sixth fillet is concave inward to form an arc transition, that is, the sixth fillet is part of a circle with radius r8. The sixth fillet is adapted to the fourth fillet 256, and r8 satisfies: 0.25mm≤r8≤45mm. The fifth fillet 1211 and the sixth fillet are opposite each other along the radial direction of the second pump body 12, so that the fifth fillet 1211 is adapted to the third fillet 255, and the sixth fillet is adapted to the fourth fillet 256, which facilitates the assembly of the bushing 25 and the second pump body 12 and improves the assembly accuracy.

[0341] In some embodiments, referring to FIG51, the sidewall of the second mounting groove 121 includes a first sidewall 1213 and a second sidewall 1214 arranged axially along the second pump body 12. The upper end of the first sidewall 1213 and the lower end of the second sidewall 1214 are connected. The first sidewall 1213 extends in the vertical direction, and the second sidewall 1214 extends obliquely in a direction away from the first sidewall 1213, while the second sidewall 1214 extends obliquely in a direction away from the central axis of the second pump body 12. Therefore, during the assembly of the bushing 25 and the second pump body 12, it facilitates the initial assembly of the bushing 25 and the second pump body 12, reduces the assembly difficulty of the bushing 25 and the second pump body 12, and improves the assembly efficiency of the gear pump 100. For example, the included angle between the first sidewall 1213 and the second sidewall 1214 is α, where α satisfies: 3°≤α≤13°, preferably α is 8°. The height of the second sidewall 1214 along the vertical direction is h, which satisfies: 2.3mm≤h≤2.5mm. Preferably, h is 2.4mm, but it is not limited to this. It can be set according to the actual use situation so that the second pump body 12 can be used and meet the actual use requirements.

[0342] According to some embodiments of this disclosure, referring to Figures 40 and 48, the first gear 21 and the second gear 22 are located within the second mounting groove 121, and the bushing 25 is located on the side of the first gear 21 and the second gear 22 closest to the first pump body 11. The end of the bushing 25 furthest from the second pump body 12 is fitted into the first mounting groove 111. For example, in the examples of Figures 1 and 7, the lower portions of the first gear 21 and the second gear 22 directly fit into the second mounting groove 121, and the upper portions of the first gear 21 and the second gear 22, after being fitted with the bushing 25, are partially installed in the second mounting groove 121 and the other portion is installed in the first mounting groove 111. With this configuration, the outer circumferential surface of the bushing 25 fits against the sidewalls of the first mounting groove 111 and the second mounting groove 121, improving the sealing performance of the gear pump 100, preventing oil leakage, and thus improving the performance of the gear pump 100. Furthermore, the first mounting groove 111 and the second mounting groove 121 have simple structures, are easy to install, and improve installation efficiency.

[0343] According to some embodiments of this disclosure, referring to Figures 40 and 48, a first sealing ring 4 is provided between the outer peripheral side of the first mounting groove 111 and the end of the bushing 25 away from the second pump body 12. For example, in the examples of Figures 40 and 48, the lower end of the sidewall of the first mounting groove 111 is stepped, and the first sealing ring 4 is located between the lower end of the first mounting groove 111 and the upper end of the bushing 25. With this configuration, after the first pump body 11 and the bushing 25 are assembled, the first pump body 11 and the bushing 25 cooperate to compress the first sealing ring 4, improving the sealing performance of the assembly of the first pump body 11 and the bushing 25, and effectively preventing oil leakage of the gear pump 100 during use. In some embodiments, referring to Figures 40 and 48, a retaining ring 3 is provided on the side of the first sealing ring 4 away from the second pump body 12. For example, in the examples of Figures 40 and 48, the retaining ring 3 is located between the lower end of the sidewall of the first mounting groove 111 and the first sealing ring 4. With this configuration, the retaining ring 3 covers the first sealing ring 4, preventing the first sealing ring 4 from slipping out and improving the stability of the first sealing ring 4 in use.

[0344] According to some embodiments of this disclosure, referring to Figures 40 and 48, a groove 112 is formed on the surface of the first pump body 11 facing the second pump body 12. The groove 112 extends circumferentially along the first pump body 11. A second sealing ring 5 is provided between the first pump body 11 and the second pump body 12, and at least a portion of the second sealing ring 5 fits within the groove 112. For example, in the examples of Figures 40 and 48, the groove 112 is formed on the lower side of the first pump body 11, the upper portion of the second sealing ring 5 fits within the groove 112, and the lower portion of the second sealing ring 5 is press-fitted with the upper side of the second pump body 12. With this configuration, after the first pump body 11 and the second pump body 12 are assembled, the second sealing ring 5 is compressed and press-fitted with the first pump body 11 and the second pump body 12, improving the sealing performance between the first pump body 11 and the second pump body 12, and thus improving the sealing performance of the gear pump 100. In addition, the sidewall of the groove 112 limits the second sealing ring 5, preventing the second sealing ring 5 from sliding during the assembly of the pump body 1, thus reducing the installation difficulty of the pump body 1.

[0345] According to some embodiments of this disclosure, referring to Figures 40 and 48, the gear pump 100 further includes at least one positioning post 7, with both ends of the positioning post 7 passing through the first pump body 11 and the second pump body 12, respectively, and extending in a third direction. For example, in the examples of Figures 40 and 48, the upper end of the positioning post 7 passes through the first pump body 11, and the lower end of the positioning post 7 passes through the second pump body 12. This arrangement allows the first pump body 11 and the second pump body 12 to be positioned by the positioning post 7 during installation, enabling pre-installation of the first pump body 11 and the second pump body 12, improving the accuracy of installation, and thus facilitating the long-term normal use of the gear pump 100. It should be noted that multiple positioning posts 7 can be provided, arranged at intervals along the circumference of the pump body 1, further improving positioning accuracy. However, this is not a limitation; the number and arrangement of the positioning posts 7 can be specifically set according to actual usage to meet actual needs. In the description of this disclosure, "multiple" means two or more.

[0346] According to some embodiments of this disclosure, referring to Figures 40 and 48, the gear pump 100 further includes at least one fastener 8, which passes through the first pump body 11 from the side of the first pump body 11 away from the second pump body 12 and connects to the second pump body 12. For example, in the examples of Figures 40 and 48, the fastener 8 passes through both the first pump body 11 and the second pump body 12. This arrangement strengthens the connection between the first pump body 11 and the second pump body 12, preventing separation of the first pump body 11 and the second pump body 12 during use and improving the stability of the pump body 1. It should be noted that multiple fasteners 8 (e.g., bolts) may be provided, arranged at intervals along the circumference of the pump body 1 to further improve the connection strength. However, this is not a limitation; the number and arrangement of the fasteners 8 can be specifically set according to actual usage to meet practical needs.

[0347] According to some embodiments of this disclosure, referring to Figures 40 and 48, a third mounting groove 122 is formed on the second pump body 12. The third mounting groove 122 is located radially outside the second mounting groove 121 and communicates with the second mounting groove 121. The gear pump 100 also includes a filter element 6, which is disposed within the third mounting groove 122. For example, in the examples of Figures 40 and 48, a third mounting groove 122 is formed on the upper side of the second pump body 12, communicating with the second cavity 15. A third mounting groove 122 is also formed on the lower side of the second pump body 12, communicating with the first cavity 14. Both third mounting grooves 122 communicate with the second mounting groove 121, meaning that both the first cavity 14 and the second cavity 15 communicate with the second mounting groove 121. A filter element 6 is installed within each of the two third mounting grooves 122. Therefore, the filter element 6 can filter the oil that passes through, preventing other objects in the oil from clogging the second mounting groove 121, so that the gear pump 100 can be used normally for a long time.

[0348] The installation process of gear pump 100 is roughly as follows: First, the lower ends of the first gear 21, second gear 22, first gear shaft 23, and first gear shaft 24 are installed in the second mounting groove 121 of the second pump body 12. The lower end faces of the first gear shaft 23 and second gear shaft 24 protrude from the lower side of the second pump body 121. Then, the bushings 25 are respectively fitted onto the first gear shaft 23 and the second gear shaft 24 and installed in the second mounting groove 121. The filter element 6 is installed into the second pump body 121. At the same time, the first sealing ring 4, the second sealing ring 5, and multiple positioning pins 7 are installed into the first pump body 111. Next, the first pump body 111 and the second pump body 121 are assembled vertically. Finally, the fasteners 8 pass through the first pump body 111 and the second pump body 121 to lock the first pump body 111 and the second pump body 121. It should be noted that the fasteners 8 can be bolts. With this configuration, the structure of gear pump 100 is simple and easy to form. Furthermore, the gear pump 100 has good sealing performance, which improves its mechanical properties. For example, the flow path of liquid entering the gear pump 100 is shown by arrow A in Figure 48, flowing from the first chamber 14 into the second chamber 15. The front side of the meshing line of the first gear 21 and the second gear 22 is the oil suction area of ​​the gear pump 100 (i.e., the first chamber 14), and the rear side of the meshing line of the first gear 21 and the second gear 22 is the high pressure area of ​​the gear pump 100 (i.e., the second chamber 15).

[0349] A suspension system (not shown) according to some embodiments of the present disclosure includes a gear pump 100 according to the first aspect embodiment of the present disclosure described above.

[0350] According to the suspension system disclosed herein, by employing the aforementioned gear pump 100, the smoothness of the suspension system during use is improved, and the noise of the suspension system during use is also reduced.

[0351] According to some embodiments of this disclosure, the suspension system further includes a transmission mechanism (not shown), which is connected to the gear pump 100. The output shaft of the transmission mechanism is connected to one end of either the first gear shaft 23 or the second gear shaft 24 near the second pump body 12. When the output shaft of the transmission mechanism is connected to the first gear shaft 23, the transmission mechanism drives the first gear 21 to rotate actively, and the second gear 22 to rotate passively. When the output shaft of the transmission mechanism is connected to the second gear shaft 24, the transmission mechanism drives the second gear 22 to rotate actively, and the first gear 21 to rotate passively. The transmission structure rotates the first gear 21 and the second gear 22 to enable the gear pump 100 to operate normally.

[0352] In some embodiments, the transmission mechanism includes a brushless motor. Thus, the brushless motor offers advantages such as no brushes, low interference, low noise, smooth operation, long lifespan, and low maintenance costs, thereby improving the performance of the transmission mechanism and facilitating its use in suspension systems.

[0353] In some embodiments, the suspension system further includes an oil reservoir and a control component (e.g., a stop-open valve, a damping valve, or a central control cylinder). The oil reservoir is connected to the first chamber 14, and the control component is connected to the second chamber 15. Thus, under the action of the gear pump 100, liquid can enter from the oil reservoir into the first chamber 14, and then flow from the first chamber 14 into the second chamber 15. The change in volume of the second chamber 15 compresses the liquid, causing it to flow into the control component. This allows the control component to cooperate with other components on the vehicle to control the movement of the vehicle body (e.g., lifting), so that the vehicle body moves according to actual needs. It should be noted that the gear pump 100 can also be used in a rear wing to rotate or twist it, but it is not limited to this. The gear pump 100 can also be used in other devices, specifically configured according to actual usage to meet specific needs.

[0354] A vehicle (not shown) according to some embodiments of the present disclosure includes the suspension system described above.

[0355] According to some embodiments of the present disclosure, by employing the above-described suspension system, the vehicle noise is reduced and the vehicle's performance is improved.

[0356] The gear pump 100, suspension system, and other components and operation of the vehicle according to some embodiments of this disclosure are known to those skilled in the art and will not be described in detail here.

[0357] In the description of this disclosure, it should be understood that the terms "center," "length," "width," "thickness," "upper," "lower," "front," "rear," "left," "right," "vertical," "horizontal," "top," "bottom," "inner," "outer," "axial," "radial," and "circumferential," 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 disclosure and simplifying the description, 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 disclosure.

[0358] In the description of this specification, the references to terms such as "one embodiment," "some embodiments," "illustrative embodiment," "example," "specific example," or "some examples," etc., refer to specific features, structures, materials, or characteristics described in connection with that embodiment or example, which are included in at least one embodiment or example of this disclosure. In this specification, the illustrative expressions of the above terms do not necessarily refer to the same embodiment or example.

[0359] Although embodiments of this disclosure have been shown and described, those skilled in the art will understand that various changes, modifications, substitutions and alterations can be made to these embodiments without departing from the principles and spirit of this disclosure, the scope of which is defined by the claims and their equivalents.

Claims

1. A damping system configured to adjust the flow damping or damping coefficient between a first device and a second device.

2. The damping system according to claim 1, comprising a valve device, wherein, The valve device includes: Base (100), comprising: The first connecting part (110) is adapted to connect the second device, and The second connecting portion (120) is adapted to connect the second device; and A valve body assembly (200) is disposed on the base (100), the valve body assembly being capable of adjusting the damping coefficient of the oil flowing from the first connection (110) to the second connection (120) and from the second connection (120) to the first connection (110).

3. The damping system according to claim 2, wherein, The valve body assembly (200) includes a damping valve assembly (210) adapted to adjust the damping coefficient of the oil flowing from the first connection (110) to the second connection (120) and to adjust the damping coefficient of the oil flowing from the second connection (120) to the first connection (110).

4. The damping system according to claim 3, wherein, The damping valve assembly (210) includes a first damping valve section (211) and a second damping valve section (212). The first damping valve section (211) is adapted to adjust the damping coefficient of the oil flowing from the first connecting part (110) to the second connecting part (120), and the second damping valve section (212) is adapted to adjust the damping coefficient of the oil flowing from the second connecting part (120) to the first connecting part (110).

5. The damping system according to claim 4, wherein, The first damping valve section (211) includes: A first base (2111) is disposed on the base (100) and encloses a first inner cavity, the first inner cavity communicating with the first connecting portion (110) and the second connecting portion (120); and A first switching assembly (2112) is installed in the first inner cavity, and the first switching assembly (2112) is adapted to adjust the damping coefficient of the oil flowing in the first inner cavity.

6. The damping system according to claim 5, wherein, The first switching assembly (2112) includes: A first channel (B2), both ends of which are connected to the first connecting portion (110) and the second connecting portion (120); and First active component (B3); The first movable component (B3) includes an open state and a closed state. In the open state, the first movable component (B3) is separated from the first base (2111), and the oil can flow through the gap between the first movable component (B3) and the first base (2111) to flow from the first connecting part (110) to the second connecting part (120). The damping coefficient of the first switching assembly (2112) is N1. In the closed state, the first movable component (B3) is in contact with the first base (2111), and the damping coefficient of the first switching assembly (2112) is N2. The oil can flow through the first channel (B2) to flow from the first connecting part (110) to the second connecting part (120). The N1 is less than the N2.

7. The damping system according to claim 5, wherein, The first base (2111) includes a first opening (A1), and the first switch assembly (2112) includes: The first channel (B2) is connected at both ends to the first connecting part (110) and the second connecting part (120); The first movable element (B3) includes an on-state and an off-state. In the power-off state, the oil flowing out from the first connection (110) reaches the first opening (A1), and the damping force overcome by the oil is M1; The energized state includes a first state and a second state. In the first state, the oil flowing out from the first connection (110) flows through the first channel (B2), and the damping force overcome by the oil is M2. In the second state, the oil flowing out from the first connection (110) reaches the first opening (A1), and the damping force overcome by the oil is M3. M3 is greater than M2, and M2 is greater than M1.

8. The damping system according to claim 7, wherein, The first active component (B3) includes: The first part (B31) is mounted on the first base (2111); and The second part (B32) has one end abutting against the first base (2111) and the other end abutting against the first part (B31), and has a degree of freedom of movement relative to the first part (B31). In the power-off state and the second state, the oil flowing out from the first connection (110) can push the second part (B32) to move closer to the first part (B31) and flow through the gap between the second part (B32) and the first base (2111).

9. The damping system according to claim 8, wherein, The first movable component (B3) further includes a second elastic component, the two ends of which are respectively connected to the second part (B32) and the first base (2111). In the power-off state and the second state, the second elastic member is in the recovery state, and the oil flowing out from the first connection (110) pushes the second part (B32) to move closer to the first part (B31) and compresses the second elastic member.

10. The damping system according to claim 8, wherein, The first movable component (B3) further includes a first elastic component, the two ends of which are respectively connected to the first part (B31) and the first base (2111), and the first channel (B2) is located at least in the first part (B31). In the first state, the first elastic member is in the restored state, and the oil flowing out from the first connection (110) passes through the first channel (B2) located in the first part (B31) and pushes the first part (B31) to move away from the second part (B32) while compressing the first elastic member. The oil flows out from the gap between the first part (B31) and the second part (B32).

11. The damping system according to any one of claims 5 to 10, wherein, The first base (2111) includes a first opening (A1), and the first switch assembly (2112) includes a first one-way member (B1). The oil can flow from the first connection (110) through the first one-way member (B1) and from the first opening (A1) to the second connection (120).

12. The damping system according to claim 11, wherein, One end of the first one-way component (B1) is connected to the first base (2111), and the other end of the first one-way component (B1) is in contact with the first base (2111). The flow of the oil allows the other end of the first one-way component (B1) to separate from the first base (2111), and the oil flows from the gap between the first one-way component (B1) and the first base (2111) to the first opening (A1).

13. The damping system according to any one of claims 4 to 12, wherein, The second damping valve section (212) includes: A second base (2121) is disposed on the base (100) and encloses a second inner cavity, the second inner cavity communicating with the first connecting portion (110) and the second connecting portion (120); and A second switching assembly (2122) is installed in the second inner cavity, and the second switching assembly (2122) is adapted to adjust the damping coefficient of the oil flowing in the second inner cavity.

14. The damping system according to claim 13, wherein, The second switch assembly (2122) includes a second channel (D2), the two ends of which are connected to the first connecting part (110) and the second connecting part (120), and the second switch assembly (2122) includes a second movable member (D3); The second movable member (D3) includes an open state and a closed state. In the open state, the second movable member (D3) is separated from the second base (2121), and the oil can flow through the gap between the second movable member (D3) and the second base (2121) to flow from the second connection part (120) to the first connection part (110). The damping coefficient of the second switch assembly (2122) is N3. In the closed state, the second movable member (D3) is in contact with the second base (2121), and the damping coefficient of the second switch assembly (2122) is N4. The oil can flow through the second channel (D2) to flow from the second connection part (120) to the first connection part (110). The N3 is less than the N4.

15. The damping system according to claim 13, wherein, The second switch assembly (2122) includes a second channel (D2), the two ends of which communicate with the second connecting portion (120) and the first connecting portion (110). The second switch assembly (2122) includes a second movable member (D3), the second base (2121) includes a second opening (A2), and the second movable member (D3) includes an on-state and an off-state. In the de-energized state, the oil flowing out from the second connection (120) reaches the second opening (C1), and the damping force overcome by the oil is M4. The energized state includes a third state and a fourth state. In the third state, the oil flowing out from the second connection (120) flows through the second channel (D2), and the damping force overcome by the oil is M5. In the fourth state, the oil flowing out from the second connection (120) reaches the second opening (C1), and the damping force overcome by the oil is M6. M6 is greater than M5, and M5 is greater than M4.

16. The damping system according to claim 15, wherein, The second active component (D3) includes: The third part (D31) is installed on the second base (2121); and The fourth part (D32) has one end abutting against the second base (2121), and the other end abutting against the third part (D31), and has a degree of freedom of movement relative to the third part (D31). In the power-off state and the fourth state, the oil flowing out from the second connection (120) can push the fourth part (D32) to move closer to the third part (D31) and flow through the gap between the fourth part (D32) and the second base (2121).

17. The damping system according to claim 16, wherein, The second movable component (D3) further includes a fourth elastic component, the two ends of which are connected to the fourth part (D32) and the second base (2121), respectively. In the power-off state and the fourth state, the fourth elastic element is in the recovery state, and the oil flowing out from the second connection (120) pushes the fourth part (D32) to move closer to the third part (D31) and compresses the fourth elastic element.

18. The damping system according to claim 17, wherein, The second movable member (D3) further includes a third elastic member, the two ends of which are respectively connected to the third part (D31) and the second base (2121), and the second channel (D2) is located at least in the third part (D31); In the third state, the third elastic member is in the restored state, and the oil flowing out from the second connection (120) passes through the first channel (B2) located in the third part (D31) and pushes the third part (D31) to move away from the fourth part (D32) while compressing the third elastic member. The oil flows out from the gap between the third part (D31) and the fourth part (D32).

19. The damping system according to any one of claims 13 to 18, wherein, The second base (2121) includes a second opening (C1), and the second switch assembly (2122) includes a second one-way member (D1), through which the oil can flow from the second connection (120) via the second one-way member (D1) and from the second opening (C1) to the first connection (110).

20. The damping system according to claim 19, wherein, One end of the second one-way member (D1) is connected to the second base (2121), and the other end of the second one-way member (D1) is in contact with the second base (2121). The flow of the oil can separate the other end of the second one-way member (D1) from the second base (2121), and the oil flows from the gap between the second one-way member (D1) and the second base (2121) to the second opening (C1).

21. The damping system according to any one of claims 4 to 20, wherein, The valve body assembly (200) further includes a first one-way valve section (220) and a second one-way valve section (230), wherein the first one-way valve section (220) allows the oil to flow from the first connection section (110) to the second connection section (120), and the second one-way valve section (230) allows the oil to flow from the second connection section (120) to the first connection section (110).

22. The damping system according to claim 21, wherein, The first one-way valve (220) is connected between the second damping valve (212) and the second connecting part (120). The second damping valve (212) includes a second inlet end and a second outlet end. The second inlet end is connected to the first one-way valve (220), and the second outlet end is connected to the first damping valve (211). The first one-way valve (220) allows oil to flow unidirectionally from the first damping valve (211) to the second connecting part (120).

23. The damping system according to claim 22, wherein, The first one-way valve section (220) includes: A first connecting seat (221) is connected between the second connecting portion (120) and the second inlet end, and the first connecting seat (221) is provided with a third opening; and A first valve body (222) is capable of opening or closing the third opening.

24. The damping system according to any one of claims 21 to 23, wherein, The second one-way valve (230) is connected between the first damping valve (211) and the first connecting seat (221). The first damping valve (211) includes a first inlet end and a first outlet end. The first inlet end is connected to the second one-way valve (230), and the first outlet end is connected to the second damping valve (212). The first one-way valve (220) allows oil to flow unidirectionally from the second damping valve (212) to the first connecting seat (110).

25. The damping system according to claim 24, wherein, The second one-way valve section (230) includes: A second connecting seat (231) is connected between the first connecting portion (110) and the first inlet end, and the second connecting seat (231) is provided with a fourth opening; and The second valve body (232) is capable of opening or closing the fourth opening.

26. The damping system according to any one of claims 21 to 25, wherein, The base (100) further includes a third connecting part (130), one end of which can be connected to an energy storage device, and the other end of which communicates with the second one-way valve part (230) and the first connecting part (110).

27. The damping system according to any one of claims 21 to 26, wherein, The base (100) further includes a fourth connecting part (140), one end of which can be connected to a stiffness switching valve, and the other end of which communicates with the first one-way valve part (220) and the second connecting part (120).

28. The damping system according to any one of claims 2 to 27, further comprising: The first device is configured to absorb shock. as well as The second device is configured to store oil.

29. The damping system according to claim 28, further comprising: An accumulator is configured to buffer the oil flowing from the second device to the first device; as well as A stiffness switching valve is configured to buffer the oil flowing from the first device to the second device.

30. The damping system according to claim 1, comprising a damping controller, the damping controller comprising: The controller body (110C) has a first cavity (101) and a second cavity (102), which are connected to each other. A first valve device (10a) is installed in the first cavity (101). The medium outlet (61) and the third channel (7122) of the first valve device (10a) are both connected to the first cavity (101). The second channel (7121) of the first valve device (10a) is configured to connect to the first device. The second valve device (10b) is installed in the second cavity (102). Both the first valve device (10a) and the second valve device (10b) are valve devices (10C). The medium outlet (61) and the third channel (7122) of the second valve device (10b) are connected to the second cavity (102). The second channel (7121) of the second valve device (10b) is configured to connect to the second device to adjust the communication damping between the first device and the second device.

31. The damping system according to claim 30, wherein, The valve device (10C) includes: First passage; Second channel; A first valve body (11C) is movable to adjust the flow damping between the first channel and the second channel. The first valve body (11C) has a pilot channel (111C) that is connected to the second channel. A pilot valve plug (2C) is disposed on one side of the first valve body (11C). The pilot valve plug (2C) is adapted to open or block the pilot channel (111C). When the pilot valve plug (2C) opens the pilot channel (111C), the pilot channel (111C) can be connected to the first channel through a third channel. A drive assembly (8C) configured to drive the pilot valve plug (2C) to move; and A first elastic element (3C) is abutted at one end against the pilot valve plug (2C) to reduce the fluctuations caused by the medium to the pilot valve plug (2C).

32. The damping system according to claim 31, wherein, One end of the first elastic element (3C) abuts against the pilot valve plug (2C) to apply a force toward the first valve body (11C) to the pilot valve plug (2C).

33. The damping system according to claim 31, wherein, One end of the first elastic element (3C) abuts against the pilot valve plug (2C) to apply a force away from the first valve body (11C) to the pilot valve plug (2C).

34. The damping system according to any one of claims 31 to 33, wherein, The valve device (10C) further includes a first valve seat (12C), and the first valve body (11C) is movable relative to the first valve seat (12C).

35. The damping system according to claim 34, wherein, One of the first valve body (11C) and the first valve seat (12C) has a guide cavity, and at least a portion of the other of the first valve body (11C) and the first valve seat (12C) extends into the guide cavity to guide and engage with the other. The first valve body (11) is movable relative to the first valve seat (12C) in a direction toward or away from the pilot valve plug (2C).

36. The damping system according to claim 33 or 34, wherein, The other end of the first elastic element (3C) abuts against the first valve seat (12C), and the first elastic element (3C) applies a force to the pilot valve plug (2C) away from the first valve body (11).

37. The damping system according to any one of claims 34 to 36, wherein, The valve device (10C) further includes a valve housing (6C), the first valve body (11C) is movable relative to the valve housing (6C), the valve housing (6C) is provided with a medium outlet (61), the medium outlet (61) is configured as at least a part of the first channel, the valve housing (6C) is provided with a pressure relief chamber (64), and the medium outlet (61) is connected to the pressure relief chamber (64).

38. The damping system according to claim 37, wherein, The valve device (10C) further includes a base valve seat (5C), the drive assembly (8C) is disposed on the side of the base valve seat (5C) opposite to the pilot valve plug (2C), the valve housing (6C) is connected to the base valve seat (5C), the base valve seat (5C) is provided with a base valve hole (51), a first chamber (52) is formed between the first valve seat (12C) and the base valve seat (5C), the base valve hole (51) communicates the first chamber (52) and the pressure relief chamber (64), and the base valve hole (51) and the first chamber (52) are configured as at least a part of the third channel.

39. The damping system according to claim 37 or 38, wherein, A valve passage (62) is formed within the valve housing (6C), the valve passage (62) being configured as at least a portion of the second passage, the pressure relief chamber (64) being configured as at least a portion of the first passage, and the first valve body (11C) being movable to adjust the communication damping between the valve passage (62) and the pressure relief chamber (64).

40. The damping system according to claim 39, wherein, A receiving cavity (13C) is formed between the first valve seat (12C) and the first valve body (11C), and the pilot channel (111C) is connected to the receiving cavity (13C); The first valve body (11C) is provided with a preset valve hole (112), and the valve channel (62) is connected to the receiving cavity (13C) through the preset valve hole (112).

41. The damping system according to claim 40 further includes a second elastic element (14C), the second elastic element (14C) being disposed in the receiving cavity (13C), one end of the second elastic element (14C) abutting against the first valve body (11C) in the axial direction of the first valve body (11C), and the other end of the second elastic element (14C) abutting against the first valve seat (12C).

42. The damping system according to claim 40 or 41, wherein, The pilot channel (111) includes an axial channel (1111) and a radial channel (1112), the pilot valve plug (2C) is configured to selectively block the axial channel (1111), the radial channel (1112) is connected to the axial channel (1111), and the radial channel (1112) extends radially along the first valve body (11C) to the receiving cavity (13C).

43. The damping system according to any one of claims 39 to 42, wherein, A radially extending protruding structure (63) is formed on the inner peripheral wall of the valve housing (6C), and the protruding structure (63) forms the valve passage (62). The first valve body (11) is selectively attached to or separated from the protruding structure (63). The pressure relief chamber (64) and the valve passage (62) are adapted to communicate through the gap between the first valve body (11C) and the protruding structure (63).

44. The damping system according to any one of claims 39 to 43, wherein, The valve device (10C) further includes a second valve assembly (7C), which includes a second valve body (71) mounted on the valve housing (6C). The second valve body (71) has a second chamber (713) with adjustable communication damping between the second chamber (713) and the valve passage (62).

45. The damping system according to claim 44, wherein, The second valve assembly (7C) further includes a first valve plate (72), the second valve body (71) has a first channel (7111) configured to communicate the second chamber (713) with the valve channel (62), and the first valve plate (72) is capable of blocking or opening the first channel (7111).

46. ​​The damping system according to claim 45, wherein, The second valve body (71) has a second channel (7121) and a third channel (7122), the second chamber (713) is connected to the second channel (7121), and the third channel (7122) is selectively connected to the second chamber (713).

47. The damping system according to claim 46, wherein, The second valve assembly (7C) further includes a second valve plate (73) capable of blocking or opening the third channel (7122).

48. The damping system according to claim 47, wherein, The second valve assembly (7C) further includes a third elastic element (74) disposed within the second chamber (713) and configured to apply an elastic force to the second valve plate (73) in a direction that moves toward blocking the third channel (7122).

49. The damping system according to claim 48, wherein, The second valve body (71) includes: A second valve seat (711) is mounted on the valve housing (6C), and the first channel (7111) is formed on the second valve seat (711); and The second valve body (712) is mounted on the second valve seat (711), and the second channel (7121) and the third channel (7122) are formed on the second valve body (712).

50. The damping system according to claim 49, wherein, In the radial direction of the second valve body (712), the third channel (7122) is separated from the second channel (7121).

51. The damping system according to any one of claims 31 to 50, wherein, The valve device (10C) further includes a push rod (4C) connected to the side of the pilot valve plug (2) away from the first valve body (11C), and the drive assembly (8C) is configured to drive the push rod (4) toward the first valve body (11C) to move the pilot valve plug (2C).

52. The damping system according to claim 51, wherein, The pilot valve plug (2C) has a push rod groove (23), and one end of the push rod (4C) extends into the push rod groove (23).

53. The damping system according to claim 51 or 52, wherein, The valve device (10C) further includes a base valve seat (5C), the drive assembly (8C) is disposed on the side of the base valve seat (5) opposite to the pilot valve plug (2C), the base valve seat (5C) has a push rod hole through which the push rod (4C) passes.

54. The damping system according to claim 53, wherein, The other end of the first elastic element (3C) abuts against the base valve seat (5C), and the first elastic element (3C) applies a force toward the first valve body (11C) to the pilot valve plug (2C).

55. The damping system according to any one of claims 51 to 54, wherein, The drive assembly (8C) is located on the side of the pilot valve plug (2C) away from the first valve body (11C). The drive assembly (8C) includes a coil (81) and a magnetic core (82). The magnetic core (82) is connected to the push rod (4C). The coil (81) is configured to drive the magnetic core (82) to move.

56. The damping system according to claim 55, wherein, The drive assembly (8C) further includes a fourth elastic element (83) and a fifth elastic element (84), the fourth elastic element (83) abutting against the magnetic core (82) to apply a force toward the pilot valve plug (2C) to the magnetic core (82), and the fifth elastic element (84) abutting against the magnetic core (82) to apply a force away from the pilot valve plug (2C) to the magnetic core (82).

57. The damping system according to any one of claims 31 to 56, wherein, The pilot valve plug (2C) includes a valve plug body (21C) and a valve plug skirt (22C). The valve plug skirt (22C) is connected to the valve plug body (21C). The valve plug skirt (22C) extends radially outward along the valve plug body (21C). The valve plug body (21C) is adapted to open or block the pilot channel (111). One end of the first elastic member (3C) abuts against the valve plug skirt (22C).

58. The damping system according to any one of claims 31 to 57, wherein, The controller body (110) also has a third cavity (103), through which the first cavity (101) and the second cavity (102) are connected.

59. A damping system comprising a one-way valve seat (1C), or a one-way valve (25), or a valve assembly (10).

60. The damping system according to claim 59, comprising the one-way valve seat (1B), wherein, The one-way valve seat (1B) is provided with a first one-way valve passage (3B) and a one-way valve through hole (4B). The one-way valve seat (1B) has at least one sealing surface (2B), which is adapted to abut against a first one-way valve disc (5B) so that the first one-way valve disc (5B) is adapted to allow fluid to flow unidirectionally from the one-way valve through hole (4B) to the first one-way valve passage (3B). The width of each of the at least one sealing surface (2B) is less than or equal to 0.4 mm.

61. The damping system according to claim 60, wherein, The width of the sealing surface (2B) is greater than or equal to 0.05 mm.

62. The damping system according to claim 60 or 61, wherein, The sealing surface (2) is a plane.

63. The damping system according to claim 62, wherein, The flatness of the sealing surface (2B) is less than or equal to 0.005 mm.

64. The damping system according to any one of claims 60 to 63, wherein, The at least one sealing surface (2B) includes two sealing surfaces (2B), and the one-way valve through hole (4B) is provided between the two sealing surfaces (2B), wherein the distance between the two sealing surfaces (2B) is any value from 0.5 mm to 5 mm.

65. The damping system according to any one of claims 60 to 64, wherein, The one-way valve seat (1B) includes a body portion (21B) and a sealing portion (22B) connected to the body portion (21B). The body portion (21B) is provided with the first one-way valve passage (3B). Either the body portion (21B) or the sealing portion (22B) has a sealing surface (2B) of the at least one sealing surface.

66. The damping system according to claim 65, wherein, The one-way valve seat (1B) further includes a connecting part (23B) connecting the body part (21B) and the sealing part (22B), and the connecting part (23B) is provided with the one-way valve through hole (4B).

67. The damping system according to claim 66, wherein, The connecting part (23B) is provided with a groove (24B), and the one-way valve through hole (4B) is provided on the bottom wall of the groove (24B).

68. The damping system according to any one of claims 60 to 67, wherein, The flexibility of the one-way valve seat (1B) is adapted to be greater than that of the first one-way valve disc (5B).

69. The damping system according to any one of claims 60 to 68, comprising the one-way valve (25B), wherein, The one-way valve (25B) includes the one-way valve seat (1B) and the first one-way valve disc (5B).

70. The damping system according to claim 69, wherein, The one-way valve (25B) further includes a one-way valve body (6B) and a second one-way valve disc (7B). The one-way valve body (6B) is provided with a second one-way valve passage (8B). The second one-way valve disc (7B) is mounted on the one-way valve body (6B) to allow fluid to flow unidirectionally from the first one-way valve passage (3C) to the second one-way valve passage (8B).

71. The damping system according to claim 69, wherein, The one-way valve (25B) further includes a one-way valve body (6B) and an elastic element (9). The one-way valve body (6B) is connected to the one-way valve seat (1B), and the elastic element (9) abuts between the first one-way valve plate (5B) and the one-way valve body (6B).

72. The damping system according to any one of claims 60 to 61, comprising the valve assembly, wherein, The valve assembly (10) includes the one-way valve seat (1) or the one-way valve (25).

73. The damping system according to claim 72, wherein, The valve assembly (10) further includes a control assembly (11B) and a valve (12B); wherein, when the control assembly (11B) is in a first state, the valve (12B) forms a first channel (26), and fluid is adapted to flow sequentially through the first one-way valve channel (3B) and the first channel (26); when the control assembly (11B) is in a second state, the valve (12B) forms a second channel (27), and fluid is adapted to flow sequentially through the first one-way valve channel (3) and the second channel (27); the first channel (26) and the second channel (27) are different.

74. The damping system according to claim 73, wherein, The first state is the power-off state, and the second state is the power-on state.

75. The damping system according to claim 73 or 74, wherein, The pressure of the fluid when the control component (11) is in the second state is greater than the pressure of the fluid when the control component (11) is in the first state.

76. The damping system according to any one of claims 73 to 75, wherein, The control component includes a push rod (13B); wherein, when the control component (11B) is in the second state, the push force of the push rod (13B) on the valve (12B) is greater than the push force of the push rod (13B) on the valve (12B) when the control component (11B) is in the first state.

77. The damping system according to claim 76, wherein, When the control component (11B) is in the second state, the push rod (13B) is adapted to be pushed away from the valve (12B) by the fluid, such that the valve (12B) forms the second channel (27).

78. The damping system according to any one of claims 73 to 77, wherein, When the control component (11B) is in the second state, the second channel (27) includes a first sub-channel (28) during a first time period, and the second channel (27) includes the first sub-channel (28) and the second sub-channel (29) during a second time period after the first time period.

79. The damping system according to claim 78, wherein, The second sub-channel (29) is the same as the first channel (26).

80. The damping system according to claim 78 or 79, wherein, The pressure of the fluid flowing through the second channel (27) during the first time period is less than the pressure of the fluid flowing through the second channel (27) during the second time period.

81. The damping system according to any one of claims 74 to 80, wherein, The valve (12) is an overflow valve.

82. The damping system according to any one of claims 60 to 81, wherein, The valve assembly (10B) further includes a control assembly (11B) and a valve (12B); wherein, when the control assembly (11B) is in a first state, the valve (12B) forms a first channel (26B), through which fluid is adapted to flow sequentially through the first one-way valve channel (3) and the first channel (26); when the control assembly (11B) is in a second state, the valve (12B) forms a second channel (27), through which fluid is adapted to flow sequentially through the first one-way valve channel (3) and the second channel (27); the first channel (26) and the second channel (27) are different.

83. The damping system according to claim 82, further comprising a housing (14B), the at least one valve assembly (10) comprising two valve assemblies (10), the housing (14B) having two first connecting chambers (15B), a second connecting chamber (16), and a third connecting chamber (17), the two valve assemblies (10B) respectively mounted in the two first connecting chambers (15B); wherein, The second connecting chamber (16) is connected to the third connecting chamber (17) via the two valve assemblies (10B).

84. The damping system according to claim 83, wherein, When the two control components (11B) are in the first state, the second connection cavity (16) is connected to the third connection cavity (17) through the first one-way valve passage (3B) and the first passage (26) of one of the two valve components (10B), and the one-way valve through hole (4B) and the first one-way valve passage (3B) of the other valve component (10B).

85. The damping system according to claim 83 or 84, wherein, When the two control components (11B) are in the second state, the second connection cavity (16) is connected to the third connection cavity (17) through the first one-way valve passage (3B) and the second passage (27) of one of the two valve components (10B), and the one-way valve through hole (4B) and the first one-way valve passage (3B) of the other valve component (10B) of the two valve components (10).

86. The damping system according to any one of claims 83 to 85, wherein, The second connecting cavity (16) is adapted to connect the shock absorber (18), and the third connecting cavity (17) is adapted to connect the central control cylinder (19) and the stiffness conversion valve (20).

87. A suspension system comprising a damping system according to any one of claims 30 to 58, or a gear pump, wherein, The suspension system is configured to transmit forces and torques to support the vehicle body.

88. The suspension system of claim 87, comprising the damping system of any one of claims 30 to 58, wherein the first device comprises a central control cylinder and the second device comprises a shock absorber.

89. The suspension system according to claim 88 further includes a stiffness switching valve, wherein both the stiffness switching valve and the central control cylinder are connected to the second channel (7121) of the first valve device (10a).

90. The suspension system according to claim 88 or 89 further includes an accumulator, the accumulator and the shock absorber being connected to the second channel (7121) of the second valve device (10b).

91. The suspension system of claim 87, comprising the gear pump, wherein, The gear pump includes: Pump body, wherein a first chamber and a second chamber are formed within the pump body; and A gear set, at least a portion of which is disposed within the pump body, the gear set including a first gear and a second gear, the teeth of the first gear and the teeth of the second gear meshing, the first cavity and the second cavity being separated by the meshing line of the first gear and the second gear, the number of teeth of the first gear and the number of teeth of the second gear being N, wherein N satisfies: N≥13.

92. The suspension system according to claim 91, wherein, The condition N satisfies: 13≤N≤17.

93. The suspension system according to claim 91 or 92, wherein, The pressure angle of the gear set is w, where w satisfies: 20°≤w≤28°.

94. The suspension system according to claim 93, wherein, The condition w satisfies: 23°≤w≤26°.

95. The suspension system according to any one of claims 91 to 94, wherein the gear set further comprises a first gear shaft and a second gear shaft, the first gear and the second gear being located on the outer peripheral sides of the first gear shaft and the second gear shaft, respectively. The gear pump also includes: The bushing includes a first bushing portion and a second bushing portion, which are respectively sleeved on the first gear shaft and the second gear shaft, and the bushing is a single piece.

96. The suspension system according to claim 95, wherein, The first bushing portion and the second bushing portion are arranged along a first direction. A first unloading groove and a second unloading groove are formed on the side surface of the bushing facing the first gear. The first unloading groove and the second unloading groove are arranged at intervals along a second direction. The first unloading groove and the second unloading groove are asymmetrically arranged about the center line of the bushing along the first direction. The first direction and the second direction are perpendicular.

97. The suspension system according to claim 96, wherein, The first unloading groove and the second unloading groove extend along the second direction, and the lengths of the first unloading groove and the second unloading groove are different.

98. The suspension system according to claim 97, wherein, The first unloading groove and the second unloading groove satisfy at least one of the following: The distance between one end of the first unloading groove near the center line of the bushing and the center line is L1, wherein L1 satisfies: 1.45mm ≤ L1 ≤ 1.55mm; and The distance between the end of the second unloading groove near the center line of the bushing and the center line is L2, wherein L2 satisfies: 0.77mm≤L2≤0.83mm.

99. The suspension system according to claim 97 or 98, wherein, The distance between the end of the first unloading groove away from the center line of the bushing and the center line is L3, wherein L3 satisfies: 3.97mm ≤ L3 ≤ 7.10mm; and The distance between the end of the second unloading groove away from the center line of the bushing and the center line is L4, wherein L4 satisfies: 3.97mm≤L4≤7.10mm.

100. The suspension system according to any one of claims 96 to 99, wherein, The first unloading groove and the second unloading groove satisfy at least one of the following: The inner wall surface of the first unloading groove near the center line transitions with the inner walls of both sides of the first unloading groove along the first direction at a first rounded corner; and The inner wall surface of the second unloading groove near the center line transitions with the inner walls of the two sides of the second unloading groove along the first direction at a second rounded corner.

101. The suspension system according to claim 100, wherein, The first fillet and the second fillet satisfy at least one of the following: The radius of the first fillet is r1, wherein r1 satisfies: 0.45mm ≤ r1 ≤ 1.05mm; and The radius of the second fillet is r2, wherein r2 satisfies: 0.45mm≤r2≤1.05mm.

102. The suspension system according to any one of claims 95 to 101, wherein, The pump body includes a first pump body and a second pump body arranged and connected along a third direction. A first mounting groove is formed on the first pump body, and a second mounting groove is formed on the second pump body. The second mounting groove and the first mounting groove together define an installation space. The gear set is disposed in the installation space, and the third direction is the extension direction of the first gear shaft.

103. The suspension system according to claim 102, wherein, The first gear and the second gear are located in the second mounting groove, and the bushing is located on the side of the first gear and the second gear closer to the first pump body. The end of the bushing away from the second pump body is fitted into the first mounting groove.

104. The suspension system according to claim 102 or 103, wherein, A first sealing ring is provided between the first mounting groove and the outer peripheral side of the end of the bushing away from the second pump body.

105. The suspension system according to claim 104, wherein, A retaining ring is provided on the side of the first sealing ring away from the second pump body.

106. The suspension system according to any one of claims 102 to 105, wherein, A groove is formed on the side surface of the first pump body facing the second pump body, and the groove extends circumferentially along the first pump body. A second sealing ring is provided between the first pump body and the second pump body, and at least a portion of the second sealing ring fits into the groove.

107. The suspension system according to any one of claims 102 to 106, wherein, The gear pump also includes: At least one positioning post, the two ends of which are respectively inserted into the first pump body and the second pump body, and the positioning post extends along the third direction.

108. The suspension system according to any one of claims 102 to 107, wherein, The gear pump also includes: At least one fastener passes through the first pump body and connects to the second pump body from the side of the first pump body away from the second pump body.

109. The suspension system according to any one of claims 102 to 108, wherein, The second pump body has a third mounting groove formed thereon, the third mounting groove being located radially outside the second mounting groove and communicating with the second mounting groove; the gear pump further includes: A filter element is disposed in the third mounting slot.

110. The suspension system according to any one of claims 91 to 109, further comprising: A transmission mechanism, which is connected to the gear pump.

111. The suspension system according to claim 110, wherein, The transmission mechanism includes a brushless motor.

112. A vehicle comprising a damping system according to any one of claims 1 to 86, or a suspension system according to any one of claims 87 to 111.

113. The vehicle according to claim 112, comprising: Damping system according to any one of claims 2 to 29; Wheel (12); as well as The vehicle body (11) is mounted on the wheel (12), the valve device is mounted on the vehicle body (11), and the vehicle body is connected to the wheel (12) through the first device of the damping system.

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