Hydraulic control system and hydraulic control method for stabilizer bar, vehicle

Abstract

The application discloses a hydraulic control system and method of a stabilizer bar, and a vehicle, and belongs to the field of vehicle engineering. The system comprises a stabilizer bar assembly, a coupling assembly and a hydraulic drive device. The coupling assembly comprises a first coupling body, a first rotating body and a first ring gear, the first ring gear being movable along the axial direction and surrounding the first rotating body; a second coupling body, a second rotating body and a second ring gear, the second rotating body being coaxially connected with the first rotating body, and the second ring gear being arranged around the second rotating body; and a housing. The first ring gear is arranged in the housing, and first control liquid cavities and second control liquid cavities are formed on both sides of the first ring gear. The hydraulic drive device drives the first ring gear to move between the meshing state and the disengaging state through a hydraulic pressure difference, the first ring gear is in meshing with the second ring gear in the meshing state, and the first ring gear is disengaged from the second ring gear in the disengaging state. The hydraulic control system of the stabilizer bar according to the embodiment of the application can realize dynamic adjustment of the lateral stability of the vehicle.

Description

TECHNICAL FIELD

[0001] The present application belongs to the field of vehicle engineering, and particularly relates to a hydraulic control system and hydraulic control method of a stabilizer bar, and a vehicle with the hydraulic control system of the stabilizer bar. BACKGROUND

[0002] The stabilizer bar on a vehicle is used to increase the roll stiffness of the suspension and reduce the roll of the vehicle. The stiffness of a common stabilizer bar is fixed, and the ride experience of the vehicle is general. For example, the roll stiffness of the stabilizer bar is irrelevant to the roll angle of the vehicle body. When the roll angle of the vehicle body is small, the stabilizer bar provides a large roll stiffness, which causes a large roll angle vibration of the vehicle and affects the ride comfort of the vehicle. When the roll angle of the vehicle body is large or the vehicle is changing lanes in an emergency, the roll stiffness provided by the stabilizer bar is fixed, and the force for reducing the roll of the vehicle body is insufficient, which affects the driving safety of the vehicle. To solve the above problems, the stabilizer bar needs to be able to adjust the roll stiffness of the stabilizer bar according to the driving state of the vehicle.

[0003] In the prior art, a hydraulic control system is provided on the stabilizer bar, and a clutch structure is provided to control the roll stiffness of the stabilizer bar. However, the clutch structure is complex, and the reliability and control effectiveness need to be improved. SUMMARY

[0004] The present application aims to at least solve one of the technical problems in the prior art. To this end, the present application proposes, in one aspect, a hydraulic control system of a stabilizer bar, which simplifies the clutch structure and improves the reliability and control effectiveness of the clutch.

[0005] The present application proposes, in another aspect, a control method of a stabilizer bar suitable for the above hydraulic control system.

[0006] The present application proposes, in still another aspect, a vehicle suitable for the above hydraulic control system.

[0007] The hydraulic control system of the stabilizer bar according to the embodiment of the present application comprises: a stabilizer bar assembly comprising a first bar body and a second bar body; a coupling assembly arranged between the first bar body and the second bar body, and comprising: a first coupling body comprising a first rotating body and a first ring gear, the first rotating body being connected to the first bar body, and the first ring gear being arranged around the first rotating body and being movable in the axial direction; a second coupling body comprising a second rotating body and a second ring gear, the second rotating body being connected to the second bar body, the second rotating body being coaxially rotatably connected to the first rotating body, and the second ring gear being arranged around the second rotating body; a housing, which at least surrounds the outer sides of the first ring gear and the second ring gear, and in which a first control liquid cavity is formed on the side of the first ring gear away from the second ring gear, and a second control liquid cavity is formed between the first ring gear and the second ring gear; and a hydraulic drive device having a first connecting end and a second connecting end, the first connecting end being in communication with the first control liquid cavity, and the second connecting end being in communication with the second control liquid cavity, so as to drive the first ring gear to move between the meshing state and the disengaging state through the hydraulic pressure difference, in the meshing state the first ring gear is in meshing with the second ring gear, and in the disengaging state the first ring gear is disengaged from the second ring gear.

[0008] The hydraulic control system of the stabilizer bar according to the first aspect of the embodiment of the present application drives the first ring gear to move in the axial direction by controlling the hydraulic pressure difference between the second control liquid cavity and the first control liquid cavity, so as to change the coupling state of the stabilizer bar. In this way, the stabilizer bar can selectively play its role of stabilizing and balancing according to the design requirements, for example, when the vehicle is normally driving straight on the road, the stabilizer bar is in the disengaging state, the stabilizer bar does not work, and the left and right wheels of the vehicle do not interfere with each other, so as to meet the comfort requirement of the vehicle when driving straight; when the vehicle is turning, the stabilizer bar is in the coupling state, the stabilizer bar is effective, and the stability requirement of the vehicle when rolling is met.

[0009] By surrounding the first ring gear outside the first rotating body and surrounding the second ring gear outside the second rotating body, the diameters of the teeth are large, the bending moment resistance is strong when the two gears are combined, the two gears are not easy to slip and break, and the coupling state of the coupling has strong resistance to external impact and high reliability.

[0010] In some embodiments, the hydraulic control system further comprises: a detection device for obtaining the driving parameters of the vehicle; and the detection device is electrically connected to the hydraulic drive device, so as to adjust the hydraulic pressure difference between the first connecting end and the second connecting end.

[0011] In some embodiments, one of the first rotating body and the second rotating body is a matching cylinder, and the other is a matching column, the matching column being assembled in the matching cavity through the matching opening;

[0012] The inner wall of the matching cylinder and the outer wall of the matching column form a liquid flow channel, the first connecting end communicates with the first control liquid cavity through the liquid flow channel, when the angle difference between the matching cylinder and the matching column is zero, the passage of the liquid flow channel to the first control liquid cavity is disconnected, when the angle difference between the matching cylinder and the matching column reaches a set angle range, the passage of the liquid flow channel to the first control liquid cavity is connected.

[0013] Specifically, the liquid flow channel is a plurality of channels distributed along the circumference of the matching cylinder, and each of the channels is: a high-pressure channel connected to the first connecting end; a low-pressure channel connected to the second connecting end; a first adjusting channel and a second adjusting channel, the circumferential sides of the high-pressure channel are the first adjusting channel and the second adjusting channel respectively, and the circumferential sides of the low-pressure channel are the second adjusting channel and the first adjusting channel respectively; when the angle difference between the matching cylinder and the matching column is zero, the plurality of liquid flow channels are not connected to each other; when the matching cylinder is turned to a first angle range relative to the matching column, the high-pressure channel is connected to the first adjusting channel, and the low-pressure channel is connected to the second adjusting channel; when the matching cylinder is turned to a second angle range relative to the matching column, the high-pressure channel is connected to the second adjusting channel, and the low-pressure channel is connected to the first adjusting channel. One of the first adjusting channel and the second adjusting channel connected to the high-pressure channel is connected to the first control liquid cavity.

[0014] Further, the hydraulic control system further comprises: a hydraulic control check valve, the hydraulic control check valve comprises: a first input port, a second input port and a high-pressure output port, the first input port is connected to the first adjusting channel, the second input port is connected to the second adjusting channel, the high-pressure output port is connected to the first input port and the second input port with higher hydraulic pressure, and the high-pressure output port is connected to the first control liquid cavity.

[0015] In some embodiments, the coupling assembly further comprises: a guide structure, the guide structure comprises: a guide rib and a guide groove extending in the axial direction;

[0016] The guide rib is arranged on the inner circumferential surface of the first ring gear, and the guide groove is arranged on the outer circumferential surface of at least one of the first rotating body and the second rotating body;

[0017] Or the guide rib is arranged on the outer circumferential surface of at least one of the first rotating body and the second rotating body, and the guide groove is arranged on the inner circumferential surface of the first ring gear.

[0018] In some embodiments, the hydraulic control system further comprises: an elastic member connected to the first ring gear to drive the first ring gear to disengage from the second ring gear.

[0019] The vehicle according to the embodiment of the present application comprises the hydraulic control system of the stabilizer bar as described in the above embodiments of the present application.

[0020] The hydraulic control method of the stabilizer bar according to the embodiment of the present application is used in the hydraulic control system of the stabilizer bar as described above, comprising: acquiring lateral acceleration of the vehicle; and adjusting a hydraulic pressure difference between the first connecting end and the second connecting end of the hydraulic drive device according to the lateral acceleration.

[0021] Specifically, the hydraulic drive device comprises a hydraulic pump with adjustable rotating speed, the rotating speed of the hydraulic pump has at least two gears, and the lateral acceleration is divided into at least two intervals; the adjusting of the hydraulic pressure difference between the first connecting end and the second connecting end of the hydraulic drive device comprises: judging the interval of the measured lateral acceleration in real time, and adjusting the rotating speed gear of the hydraulic pump according to the interval.

[0022] Additional aspects and advantages of the present application will be made apparent by the following description and the accompanying drawings. BRIEF DESCRIPTION OF DRAWINGS

[0023] The above and / or additional aspects and advantages of the present application will become apparent and be readily understood by considering the following detailed description, including the accompanying drawings, in which:

[0024] Figure 1 Structure diagram of the hydraulic control system according to the embodiment of the present application;

[0025] Figure 2 Structure diagram of the coupling assembly of the stabilizer bar according to the embodiment of the present application;

[0026] Figure 3 Structure diagram of the first ring gear and the second ring gear when engaged (hidden housing) according to the embodiment of the present application;

[0027] Figure 4 Structure diagram of the first coupling body according to the embodiment of the present application;

[0028] Figure 5 Distribution diagram of the plurality of liquid flow channels in the first coupling body (hidden first ring gear) according to the embodiment of the present application;

[0029] Figure 6 Structure diagram of the second coupling body according to the embodiment of the present application;

[0030] Figure 7 Cooperation diagram of the cooperating cylinder and the cooperating column (when the rotation angle difference is zero) according to the embodiment of the present application;

[0031] Figure 8Figs. 2 and 3 are schematic views of the coupling between the coupling cylinder and the coupling column of the coupling assembly of some embodiments of the present application;

[0032] Figure 9 Figs. 4 and 5 are schematic views of the coupling between the coupling cylinder and the coupling column of the coupling assembly of some embodiments of the present application;

[0033] Figure 10 Fig. 6 is an exploded view of the coupling assembly of some embodiments of the present application;

[0034] Figure 11 Fig. 7 is an exploded view of the first coupling body and the first ring gear of some embodiments of the present application;

[0035] Figure 12 Fig. 8 is a flow chart of the hydraulic control method of the stabilizer bar of some embodiments of the present application;

[0036] Figure 13 Fig. 9 is a control flow chart of the stabilizer bar of some embodiments of the present application.

[0037] Reference signs:

[0038] hydraulic control system 100,

[0039] stabilizer bar assembly 10, first bar body 101, second bar body 102,

[0040] coupling assembly 20,

[0041] first coupling body 21, first rotating body 210, coupling cylinder 211, coupling opening 2111, coupling cavity 2112, groove 2113, partition block 2114, cylinder bottom wall 2115, first ring gear 212, first meshing tooth 2121,

[0042] second coupling body 24, second rotating body 240, coupling column 241, protruding block 2411, partition groove 2412, second ring gear 242, guide structure 25, guide rib 251, guide groove 252,

[0043] housing 22, elastic member 23, second control liquid cavity 26, first control liquid cavity 27,

[0044] liquid flow channel 28, high-pressure channel 281, low-pressure channel 282, first adjusting channel 283, second adjusting channel 284.

[0045] hydraulic drive device 30, first connecting end 301, second connecting end 302, liquid delivery pipe 31, hydraulic pump 33, hydraulic tank 34,

[0046] detection device 40,

[0047] hydraulic control one-way valve 50, first input port 51, second input port 52, high-pressure output port 53. DETAILED DESCRIPTION

[0048] Embodiments of the present application are described below in detail with reference to the accompanying drawings, wherein the same or similar components or components having the same or similar functions are denoted by the same or similar reference numerals throughout the drawings. The embodiments described below by reference to the drawings are exemplary and are only used to explain the present application and cannot be understood as a limitation of the present application.

[0049] In the description of the present application, it should be understood that the orientation or positional relationship indicated by the terms "upper", "lower", "front", "back", "left", "right", "top", "bottom", "inner", "outer", "axial", "radial", "circumferential", "clockwise", "counterclockwise", etc. are based on the orientation or positional relationship shown in the drawings, and are only for the convenience of describing the present application and simplifying the description, and therefore cannot be understood as indicating or implying that the device or component referred to must have a particular orientation, be constructed and operated in a particular orientation, and therefore cannot be understood as a limitation of the present application. In addition, features defined with "first" and "second" can explicitly or implicitly include one or more of the features. In the description of the present application, the meaning of "a plurality of" is two or more, unless otherwise specified.

[0050] In the description of the present application, it should be noted that, unless otherwise explicitly specified and limited, the terms "mounting", "connection", "connecting" should be understood broadly, for example, it can be fixed connection, or detachable connection, or integrally connected; it can be mechanical connection, or electrical connection; it can be directly connected, or indirectly connected through an intermediate medium, or it can be the communication inside two elements. For those skilled in the art, the specific meaning of the above terms in the present application can be understood according to the specific circumstances.

[0051] The hydraulic control system 100 and the hydraulic control method of the stabilizer bar according to the embodiments of the present application are described below with reference to the accompanying drawings.

[0052] As shown in Figure 1 The hydraulic control system 100 according to the embodiments of the present application includes a stabilizer bar assembly 10, a coupling assembly 20, and a hydraulic drive device 30. In the stabilizer bar applied to a vehicle, the coupling assembly 20 drives the engagement and disengagement of the stabilizer bar assembly 10, and the hydraulic drive device 30 provides the necessary power, i.e. the coupling assembly 20 switches the clutching state of the stabilizer bar under the drive of the hydraulic drive device 30, so the coupling assembly 20 of the present application is a kind of clutch.

[0053] As shown in Figure 1 The stabilizer bar assembly 10 includes a first bar body 101 and a second bar body 102. The first bar body 101 and the second bar body 102 are two independent bar bodies, and the ends of the first bar body 101 and the second bar body 102 away from each other are connected to the suspension of the vehicle.

[0054] When the vehicle is in a steady driving state, the first rod body 101 and the second rod body 102 are free to rotate relative to each other, and there is no significant roll torque acting on the vehicle body, the circumferences of the first rod body 101 and the second rod body 102 will remain relatively static or undergo slight relative rotation. At this time, they will not pull each other and will not have a significant impact on the driving state of the vehicle. Therefore, the driver and passengers can enjoy a smooth and comfortable ride experience.

[0055] As shown in Figure 2 - Figure 3 The coupling assembly 20 according to the embodiment of the present application includes a first coupling body 21, a second coupling body 24, and a housing 22.

[0056] The first coupling body 21 includes a first rotating body 210 connected to the first rod body 101 and a first ring gear 212 disposed around the first rotating body 210 and movable in the axial direction. The second coupling body 24 includes a second rotating body 240 connected to the second rod body 102 and a second ring gear 242 disposed around the second rotating body 240. The housing 25 at least surrounds the outer sides of the first ring gear 212 and the second ring gear 242.

[0057] When the first coupling body 21 and the second coupling body 24 are locked by the ring gears, the coupling assembly 20 enters the coupled state. Conversely, when the first coupling body 21 and the second coupling body 24 are free to rotate by disengaging the ring gears, the coupling assembly 20 enters the decoupled state.

[0058] In combination Figure 1 , the direction in which the first rotating body 210 extends along the length of the stabilizer bar is referred to as the axial direction, the direction perpendicular to the axial direction is referred to as the radial direction, and the direction around the axial direction is referred to as the circumferential direction.

[0059] The first ring gear 212 is disposed around the first rotating body 210 and is movable in the axial direction. The second coupling body 24 includes a second rotating body 240 and a second ring gear 242 disposed around the second rotating body 240. The second rotating body 240 is coaxially rotatably connected to the first rotating body 210, that is, the second rotating body 240 is connected to the first rotating body 210 but can rotate relative to each other without restriction. When the first ring gear 212 moves in the axial direction of the first rotating body 210, the second coupling body 24 can be locked or unlocked.

[0060] The coupling function is realized by setting the matching structure between the first coupling body 21 and the second coupling body 24. By adjusting the position of the first ring gear 212 in the axial direction, the coupling assembly 20 can be freely switched between two states: when the first ring gear 212 is in close engagement with the second ring gear 242, the coupling assembly 20 is in the coupled state and can efficiently transmit power or torque; when the first ring gear 212 moves away from the second ring gear 242 in the axial direction and the two are out of contact, the coupling assembly 20 enters the decoupled state, and at this time the transmission of power or torque is cut off.

[0061] By surrounding the first ring gear 212 on the outside of the first rotating body 210 and the second ring gear 242 on the outside of the second rotating body 240, the tooth matching diameter is large, the bending moment resistance is strong when combined, and the two teeth are not easy to slip and break. This kind of clutch has strong anti-external impact ability and high reliability in the coupled state.

[0062] As shown in Figure 4 Figure 5 The first coupling body 21 includes a matching cylinder 211 and a first ring gear 212, and a matching cavity 2112 is formed in the matching cylinder 211. Figure 3 Figure 4 The axial ends of the matching cylinder 211 are respectively a cylinder bottom wall 2115 and a matching port 2111, and the first ring gear 212 is arranged around the matching cylinder 211.

[0063] As shown in Figure 6 The second coupling body 24 includes a matching column 241 and a second ring gear 242, the matching column 241 is assembled in the matching cavity 2112 through the matching port 2111, and the second ring gear 242 is located outside the matching cylinder 211 and is arranged around the matching column 241.

[0064] The matching cavity 2112 provides a certain movement space for the matching column 241, which can avoid interference of the matching column 241 during movement and ensure the matching effect.

[0065] The matching column 241 of the second coupling body 24 is configured to be inserted into the matching cavity 2112 of the first coupling body 21, which allows the two coupling bodies to have relative rotation while maintaining a certain connection strength. The shaft matching of the matching cylinder 211 and the matching column 241 allows them to rotate relative to each other but not to move axially relative to each other, which is conducive to ensuring the reliable rotational connection of the first coupling body 21 and the second coupling body 24 in the disengaged state of the clutch.

[0066] ​​Specifically, the bottom wall 2115 of the fitting cylinder 211 is connected with the first rod body 101 at one end of the bottom wall 2115, the fitting column 241 is connected with the second rod body 102, and the delivery pipe 31 of the hydraulic drive device 30 is connected with the coupling assembly 20. When the driving state of the vehicle changes, such as turning or driving on uneven road, the vehicle body will generate a roll torque. At this time, the hydraulic drive device 30 delivers the hydraulic medium to the coupling assembly 20 through the delivery pipe 31 thereof to activate the work of the coupling assembly 20. With the flow of the hydraulic medium in the coupling assembly 20, the interaction between the first coupling body 21 and the second coupling body 24 begins to strengthen.

[0067] Optionally, at least one of the outer surface of the fitting column 241 and the inner surface of the fitting cavity 2112 is provided with a coating. The coating is a lubricating layer to reduce friction and prolong service life. Of course, in some other embodiments, the materials of the fitting column 241 and the fitting cavity 2112 are wear-resistant materials to prolong the service life of the coupling assembly 20.

[0068] In combination Figure 3 The second ring gear 242 surrounds the fitting column 241 and is located outside the fitting cylinder 211, and is arranged opposite to the first ring gear 212. The tooth shape and arrangement of the second ring gear 242 are matched with those of the first ring gear 212 to ensure that the two can be accurately meshed or disengaged. When the clutch needs to be switched to the coupling state to limit the relative rotation of the two ends of the coupling assembly 20, the first ring gear 212 and the second ring gear 242 are meshed.

[0069] The housing 22 at least surrounds the outside of the first ring gear 212 and the second ring gear 242. In combination Figure 1 Figure 2 The housing 22 surrounds and covers the outside of the first ring gear 212 and the second ring gear 242 to form a closed cavity. The construction of this closed cavity can accurately control and maintain the pressure environment inside the cavity, ensuring that the hydraulic medium can stably and efficiently transmit power within the preset pressure range, thereby realizing the function of dynamic adjustment of the stabilizer bar. At the same time, the closed design of the housing 22 also improves the protection effect of the first ring gear 212 and the second ring gear 242. It can isolate foreign matter, dust and impurities in the external environment, prevent them from invading between the first ring gear 212 and the second ring gear 242, and thus avoid the potential influence of these adverse factors on the meshing effect of the ring gears. This protection mechanism not only guarantees the cleanliness and working accuracy of the coupling assembly 20, but also prolongs its service life and reduces maintenance costs.

[0070] Here, the housing 22 can be a single part or can be composed of multiple parts. For example, Figure 2 ​For example, one end of the shell 22 is sleeved outside the first coupling body 21, and the other end is connected to the second coupling body 24. The two ends of the shell 22 are respectively in sealed connection with the first coupling body 21 and the second coupling body 24. For example, the shell 22 is welded to the first coupling body 21, and the shell 22 is rotatably connected to the second coupling body 24, and a sealing element is arranged therebetween. For another example, the shell 22 is rotatably connected to the first coupling body 21, and the shell 22 is rotatably connected to the second coupling body 24, and a sealing element is arranged at the rotatable connection, and the sealing element can be a sealing ring. The rotatable connection can also be provided with a bearing, as long as it does not affect the sealing and relative rotation. Further optionally, the rotatable connection is also provided with a retaining ring for limiting the sealing element.

[0071] As shown in Figure 2 , inside the shell 22, the side of the first ring gear 212 away from the second ring gear 242 forms a first control liquid cavity 27, and a second control liquid cavity 26 is formed between the first ring gear 212 and the second ring gear 242, so as to drive the first ring gear 212 to move axially when there is a hydraulic pressure difference between the second control liquid cavity 26 and the first control liquid cavity 27.

[0072] As shown in Figure 1 , the hydraulic drive device 30 has a first connecting end 301 and a second connecting end 302, the first connecting end 301 communicates with the first control liquid cavity 27, and the second connecting end 302 communicates with the second control liquid cavity 26, so as to drive the first ring gear 212 to move between the meshing state and the disengaging state through the hydraulic pressure difference, in the meshing state, the first ring gear 212 is engaged with the second ring gear 242, and in the disengaging state, the first ring gear 212 is disengaged from the second ring gear 242.

[0073] It can be understood that the second control liquid cavity 26 is filled with hydraulic medium, which is used to directly transmit power to the first ring gear 212. At the same time, the side of the first ring gear 212 away from the second ring gear 242 constitutes the first control liquid cavity 27, which is arranged so that the two liquid cavities are independent of each other in structure, and together constitute the clutch switching implementation structure of the coupling assembly 20.

[0074] When there is a hydraulic pressure difference between the second control liquid cavity 26 and the first control liquid cavity 27, the pressure difference will immediately be converted into a power source to push the first ring gear 212 to move axially. Specifically, if a high pressure is applied to the first control liquid cavity 27 by the external hydraulic driving device 30, assuming that the pressure of the first control liquid cavity 27 is P1, while the pressure of the second control liquid cavity 26 is kept or reduced, assuming that the pressure of the second control liquid cavity 26 is P2, so that P1>P2, the hydraulic pressure difference between the two cavities, i.e. (P1-P2), will generate a pushing force to push the first ring gear 212 towards the second ring gear 242, driving the first ring gear 212 to move axially until it engages with the second ring gear 242. Conversely, if the direction of the hydraulic pressure difference is adjusted, the reverse movement of the first ring gear 212 can also be achieved, thereby disengaging the engagement state.

[0075] In some alternative embodiments, as shown in FIG. 4, Figure 6 The second ring gear 242 is integrally formed on the matching column 241 or the matching cylinder 211. For example, the second ring gear 242 is integrally formed on the outer circumferential surface of the matching column 241. By providing the integrally formed second ring gear 242, the problems of insufficient connection strength and easy loosening caused by welding, bolt connection and other assembly methods in traditional designs can be avoided. It is known that in the process of integral molding, the material is directly molded in the mold, so that there is almost no bonding surface between the ring gear and the cylinder or column, thereby realizing seamless connection. This seamless connection greatly enhances the overall integrity and stability of the structure, so that the hydraulic control system 100 can maintain stability and reliability when subjected to various complex working conditions.

[0076] Secondly, integral molding also improves the utilization rate of raw materials. Since the ring gear and the cylinder or column are molded at the same time, there is no need for additional processing of connecting parts, thereby saving material costs and production time.

[0077] In addition, since there are no potential weak points of traditional connection methods, such as welding cracks and bolt loosening, at the connection site, the performance output can be maintained stably for a long time, reducing the failure and maintenance costs caused by connection failure.

[0078] In combination Figure 7 - Figure 8 As shown in FIG. 2, according to the coupling assembly 20 of some embodiments of the present application, a plurality of liquid flow channels 28 are formed between the inner wall of the matching cylinder 211 and the outer wall of the matching column 241, which are distributed in the circumferential direction in sequence, and are respectively: a high-pressure channel 281, a low-pressure channel 282, a first adjusting channel 283 and a second adjusting channel 284.

[0079] The high-pressure passage 281 is used to connect the high-pressure end of the hydraulic driving device 30, and the low-pressure passage 282 is used to connect the low-pressure end of the hydraulic driving device 30. It should be noted that the terms "high pressure" and "low pressure" in the present application are relative terms, and no specific value is given in the entire text. For example, the pressure of the high-pressure end of the hydraulic driving device 30 is higher than that of the low-pressure end of the hydraulic driving device 30, the pressure of the high-pressure passage mentioned below is higher than that of the low-pressure passage, and the pressure of the high-pressure liquid mentioned below is higher than that of the low-pressure liquid. For example, in Figure 7 , the hydraulic driving device 30 includes a hydraulic tank 34, and the hydraulic tank 34 has two liquid flow ports, i.e., a first connecting end 301 and a second connecting end 302. One of them constitutes a low-pressure port, i.e., the low-pressure end mentioned above. The other is provided with a hydraulic pump 33, which constitutes a high-pressure port, i.e., the high-pressure end mentioned above.

[0080] As shown in Figure 7 , the circumferential two sides of the high-pressure passage 281 are respectively a first adjusting passage 283 and a second adjusting passage 284, and the circumferential two sides of the low-pressure passage 282 are respectively the second adjusting passage 284 and the first adjusting passage 283. That is, in the clockwise direction, the upstream of the high-pressure passage 281 is the first adjusting passage 283, and the downstream is the second adjusting passage 284; in the clockwise direction, the upstream of the low-pressure passage 282 is the second adjusting passage 284, and the downstream is the first adjusting passage 283. Alternatively, in the counterclockwise direction, the upstream of the high-pressure passage 281 is the first adjusting passage 283, and the downstream is the second adjusting passage 284; in the counterclockwise direction, the upstream of the low-pressure passage 282 is the second adjusting passage 284, and the downstream is the first adjusting passage 283.

[0081] In combination Figure 7 , when the angle difference between the matching cylinder 211 and the matching column 241 is zero, the plurality of liquid flow passages 28 are not connected to each other. Each liquid flow passage 28 remains independent and not connected to each other, ensuring the stability of the hydraulic system in the static state, and at this time, the coupling assembly 20 maintains the current state. Specifically, when the angle difference between the matching cylinder 211 and the matching column 241 is zero, the first ring gear 212 and the second ring gear 242 are disengaged, the plurality of liquid flow passages 28 are not connected to each other, and the stability of the disengaged state of the clutch is maintained.

[0082] In combination Figure 8When the coupling sleeve 211 is rotated to the first angle range a1 relative to the coupling column 241, the high-pressure passage 281 is communicated with the first adjusting passage 283, and the low-pressure passage 282 is communicated with the second adjusting passage 284. Since the high-pressure passage 281 is used to connect the high-pressure end of the hydraulic drive device 30, when the coupling sleeve 211 is rotated to the first angle range a1 relative to the coupling column 241, the first adjusting passage 283 constitutes the high-pressure passage. That is, the hydraulic medium of the high-pressure end can directly flow into the first adjusting passage 283, and then the pressure is transmitted according to the demand of the coupling assembly 20. At the same time, since the low-pressure passage 282 is used to connect the low-pressure end of the hydraulic drive device 30, when the coupling sleeve 211 is rotated to the first angle range a1 relative to the coupling column 241, the second adjusting passage 284 constitutes the low-pressure passage. That is, the hydraulic medium of the low-pressure end is guided to the second adjusting passage 284, and then the pressure is transmitted according to the demand of the coupling assembly 20. Here, the range of the first angle range a1 can be set according to actual needs.

[0083] In combination Figure 9 When the coupling sleeve 211 is rotated to the second angle range a2 relative to the coupling column 241, the high-pressure passage 281 is communicated with the second adjusting passage 284, and the low-pressure passage 282 is communicated with the first adjusting passage 283. Since the high-pressure passage 281 is used to connect the high-pressure end of the hydraulic drive device 30, when the coupling sleeve 211 is rotated to the second angle range a2 relative to the coupling column 241, the second adjusting passage 284 constitutes the high-pressure passage. Since the low-pressure passage 282 is used to connect the low-pressure end of the hydraulic drive device 30, when the coupling sleeve 211 is rotated to the second angle range a2 relative to the coupling column 241, the first adjusting passage 283 constitutes the low-pressure passage. Here, the range of the second angle range a2 can be set according to actual needs.

[0084] The plurality of liquid flow passages 28 between the inner wall of the coupling sleeve 211 and the outer wall of the coupling column 241 are thus distributed and arranged, so that when the coupling sleeve 211 and the coupling column 241 are rotated at different angles, different feedbacks are obtained through the pressure difference changes of the first adjusting passage 283 and the second adjusting passage 284. That is, the angle difference signal of the first coupling body 21 and the second coupling body 24 is converted into a hydraulic pressure difference signal.

[0085] Therefore, the hydraulic pressure difference signal can be used to control the hydraulic pressure difference between the second control liquid cavity 26 and the first control liquid cavity 27, so as to control the movement of the first ring gear 212 and realize the state switching of the clutch. This signal conversion method can directly feedback the angle difference between the coupling sleeve 211 and the coupling column 241 through the torque changes of the left and right ends of the stabilizing rod when the stabilizing rod is affected by the external environment, and finally control the movement of the first ring gear 212 to realize the switching of the clutch from the disengaged state to the coupled state. This control method is direct and has high reliability.

[0086] It can be understood that the pressure difference of the first adjusting channel 283 and the second adjusting channel 284 changes, and how to control the hydraulic pressure difference of the second control liquid cavity 26 and the first control liquid cavity 27 specifically involves the hydraulic control part. The hydraulic control part is not the protection point of the present application, and therefore how the first adjusting channel 283 and the second adjusting channel 284 generate a pressure difference to affect the second control liquid cavity 26 and the first control liquid cavity 27 is not limited or described.

[0087] Of course, in order to facilitate the understanding of the implementability of the scheme of the present application, an example is listed here. Specifically, as shown in Figure 7 The first adjusting channel 283 and the second adjusting channel 284 are connected with the hydraulic control check valve 50. The hydraulic control check valve 50 includes a first input port 51, a second input port 52, and a high-pressure output port 53. The first input port 51 is connected with the first adjusting channel 283, the second input port 52 is connected with the second adjusting channel 284, the high-pressure output port 53 is connected with the first input port 51 and the second input port 52 with higher hydraulic pressure, and the high-pressure output port 53 is connected with the first control liquid cavity 27. The structure of the hydraulic control check valve 50 is prior art, and therefore is not described here.

[0088] In this way, when the matching cylinder 211 is rotated relative to the matching column 241 to the first angle range α1, the first adjusting channel 283 is a high-pressure channel, the second adjusting channel 284 is a low-pressure channel, the high-pressure output port 53 is connected with the first input port 51, and the first control liquid cavity 27 becomes a high-pressure cavity. At this time, the hydraulic pressure of the first control liquid cavity 27 is higher than that of the second control liquid cavity 26, the two gear rings are driven to engage, and the clutch is switched to the coupling state.

[0089] When the matching cylinder 211 is rotated relative to the matching column 241 to the second angle range α2, the first adjusting channel 283 is a low-pressure channel, the second adjusting channel 284 is a high-pressure channel, the high-pressure output port 53 is connected with the second input port 52, and the first control liquid cavity 27 becomes a high-pressure cavity. At this time, the hydraulic pressure of the first control liquid cavity 27 is higher than that of the second control liquid cavity 26, the two gear rings are driven to engage, and the clutch is switched to the coupling state.

[0090] On this basis, in some embodiments, the low pressure end of the hydraulic drive device 30 is connected to the second control liquid chamber 26 and the first control liquid chamber 27 at the same time, and the coupling assembly 20 has a driving member to drive the first ring gear 212 to move in a direction away from the second ring gear 242. When the hydraulic control check valve 50 has no high pressure liquid flowing into the first control liquid chamber 27, the second control liquid chamber 26 and the first control liquid chamber 27 are both kept at a low pressure state, and the first ring gear 212 is kept in a disengaged state by the driving member. When the cooperating cylinder 211 has a certain range of angular difference (such as the first angular range α1 and the second angular range α2) relative to the cooperating column 241, the hydraulic control check valve 50 has high pressure liquid flowing into the first control liquid chamber 27, and the second control liquid chamber 26 is still kept at a low pressure state, while the first control liquid chamber 27 has a rapid rise in pressure, resulting in a pressure difference between the two ends of the first ring gear 212. The pressure difference overcomes the driving force of the driving member, and the first ring gear 212 is driven to switch to a coupled state.

[0091] Once the cooperating cylinder 211 has no angular difference relative to the cooperating column 241, the hydraulic control check valve 50 has no high pressure liquid flowing into the first control liquid chamber 27, and the second control liquid chamber 26 is still kept at a low pressure state, while the first control liquid chamber 27 gradually recovers to a low pressure state as the high pressure liquid slowly flows to the low pressure end of the hydraulic drive device 30, resulting in a pressure balance between the two ends of the first ring gear 212. At this time, the first ring gear 212 is driven by the driving member and switches to a disengaged state.

[0092] Furthermore, in combination with the design of the pipe diameter of the inlet and outlet of the first control liquid chamber 27 (the inlet is connected to the high pressure outlet 53 of the hydraulic control check valve 50, and the outlet is connected to the low pressure end of the hydraulic drive device 30), or the flow resistance design of the inlet and outlet, the first control liquid chamber 27 can also quickly get high pressure liquid through the hydraulic control check valve 50 to increase the pressure when the cooperating cylinder 211 has a certain range of angular difference relative to the cooperating column 241, realizing the quick switching of the clutch to a coupled state when there is an angular difference. When the cooperating cylinder 211 has no angular difference relative to the cooperating column 241, the first control liquid chamber 27 slowly decreases the pressure through the low pressure end of the hydraulic drive device 30, realizing the slow switching of the clutch to a disengaged state when there is no angular difference. In this way, the coupling speed and the disengaging speed of the clutch can be different.

[0093] Of course, the above scheme can also be swapped, that is, the hydraulic control check valve 50 includes: a first input port 51, a second input port 52 and a low-pressure output port, the first input port 51 is communicated with the first adjusting channel 283, the second input port 52 is communicated with the second adjusting channel 284, the low-pressure output port is communicated with the first input port 51 and the second input port 52 with low hydraulic pressure, and the low-pressure output port is communicated with the first control liquid cavity 27. The high-pressure end of the hydraulic drive device 30 is connected with the second control liquid cavity 26 and the first control liquid cavity 27 at the same time, and the coupling assembly 20 has a driving member to drive the first ring gear 212 to move in the direction of combining the second ring gear 242.

[0094] According to some embodiments of the coupling assembly 20 of the application, the high-pressure channels 281 are at least two and are distributed in the ring direction, and the low-pressure channels 282 are consistent in number with the high-pressure channels 281 and are alternately distributed in the ring direction with the high-pressure channels 281.

[0095] In this way, not only the flow of hydraulic medium can be ensured, but also the pressure and power can be more uniformly transmitted when the matching cylinder 211 rotates relative to the matching column 241.

[0096] Corresponding to the high-pressure channels 281, the number of low-pressure channels 282 is consistent with the high-pressure channels 281, and the low-pressure channels 282 are alternately distributed in the ring direction with the high-pressure channels 281. This alternating distribution ensures the balance of the high-pressure channels 281 and the low-pressure channels 282 in the ring direction, avoiding the decline or failure of the system performance caused by uneven pressure distribution. At the same time, as the channel for pressure release and hydraulic medium backflow, the alternating distribution of the low-pressure channels 282 helps to improve the overall stability and response speed of the hydraulic system.

[0097] In addition, the ring-directional interval alternating distribution of the high-pressure channels 281 and the low-pressure channels 282 also makes the coupling assembly 20 more compact and reasonable in structure. By optimizing the layout of the liquid flow channel 28, the integration and power density of the hydraulic system can be improved.

[0098] In combination Figure 7 Figure 9 , the high-pressure channels 281 are two ring-directionally interval distributed. The low-pressure channels 282 are two ring-directionally interval distributed. The low-pressure channels 282 are alternately interval distributed with the high-pressure channels 281.

[0099] Each high-pressure channel 281 is provided with a first adjusting channel 283 between the adjacent low-pressure channels 282 in the first direction and a second adjusting channel 284 between the adjacent low-pressure channels 282 in the second direction, and the first direction and the second direction are opposite in the ring direction.

[0100] ​Firstly, the first regulating passage 283 and the second regulating passage 284 are located on different sides of the high-pressure passage 281 and the low-pressure passage 282, respectively, so that the hydraulic medium can pass through different paths for pressure and flow regulation during the flow process. This diversified regulation mode enhances the flexibility and adaptability of the system, enabling precise control according to the needs of the coupling assembly 20.

[0101] Secondly, since the first direction and the second direction are opposite in the circumferential direction, the layout of the first regulating passage 283 and the second regulating passage 284 forms an interlaced network structure. This structure improves the flow efficiency of the hydraulic medium, helping to reduce energy loss and pressure fluctuations during the flow process.

[0102] In some embodiments, in combination with Figure 5 、 Figure 7 - Figure 9 , the plurality of high-pressure passages 281 are centrally symmetrically distributed relative to the axis of the coupling assembly 20. The plurality of low-pressure passages 282 are centrally symmetrically distributed relative to the axis of the coupling assembly 20. The plurality of first regulating passages 283 are centrally symmetrically distributed relative to the axis of the coupling assembly 20. The plurality of second regulating passages 284 are centrally symmetrically distributed relative to the axis of the coupling assembly 20.

[0103] The centrally symmetric layout ensures that the coupling assembly 20 is balanced in force and consistent in performance in all directions. In various working conditions, the coupling assembly 20 can maintain a stable operating state.

[0104] Secondly, the centrally symmetric layout simplifies the design and manufacturing process of the coupling assembly 20. Due to the similarity of the structures of the various passages, a unified machining process and assembly process can be used, reducing production costs and cycle times. At the same time, this layout helps to improve the interchangeability and maintainability of the assembly, facilitating quick operation during maintenance and replacement.

[0105] In addition, since the various liquid flow passages 28 are balanced in force, the risk of damage due to stress concentration is reduced. At the same time, uniform hydraulic pressure distribution also reduces the impact and vibration inside the coupling assembly 20, prolonging the service life.

[0106] As shown in Figure 4 , according to some embodiments of the coupling assembly 20 of the present application, the inner wall of the matching cylinder 211 is provided with at least two grooves 2113 spaced apart in the circumferential direction. The part of the inner wall of the matching cylinder 211 between the two adjacent grooves 2113 is a partition 2114, and part of the grooves 2113 constitutes a high-pressure passage 281, and part of the grooves 2113 constitutes a low-pressure passage 282.

[0107] The grooves 2113 not only provide channels for the flow of hydraulic medium, but also realize the division of high-pressure channels 281 and low-pressure channels 282 through their different configurations. Specifically, part of the grooves 2113 are configured as high-pressure channels 281 for transmitting high-pressure hydraulic medium, and another part of the grooves 2113 are configured as low-pressure channels 282 for returning low-pressure hydraulic medium or pressure relief.

[0108] In combination Figure 7 When the relative rotation angle difference between the fitting cylinder 211 and the fitting column 241 is zero, the outer wall of the fitting column 241 closes all the grooves 2113, and the outer wall of the fitting column 241 tightly fits on the inner wall of the fitting cylinder 211, thereby closing all the grooves 2113. This design ensures that the hydraulic medium cannot flow through the grooves 2113 without relative rotation, thereby maintaining the stable state of the system.

[0109] When the fitting column 241 rotates relative to the fitting cylinder 211, as shown in Figure 8 - Figure 9 The outer wall of the fitting column 241 will no longer completely close all the grooves 2113. As the rotation angle difference increases, the high-pressure channels 281 and the low-pressure channels 282 will be in an open or closed state with the outer wall of the fitting column 241 in turn, thereby allowing the hydraulic medium to flow between the high-pressure channels 281 and the low-pressure channels 282. This flow process realizes the transmission and conversion of hydraulic energy.

[0110] Referring to Figure 7 , the fitting column 241 includes two protrusions 2411 and two separation grooves 2412. The two protrusions 2411 are arranged on the outer wall of the fitting column 241 and are spaced apart in the circumferential direction, and the separation grooves 2412 are formed between adjacent two protrusions 2411. Part of the separation grooves 2412 constitute the first adjustment channel 283, and part of the separation grooves 2412 constitute the second adjustment channel 284.

[0111] Referring to Figure 7 When the fitting cylinder 211 and the fitting column 241 have a zero rotation angle difference, the outer wall of the fitting column 241 closes all the grooves 2113. Each protrusion 2411 is arranged opposite to one groove 2113, and each separation groove 2412 is arranged opposite to one separation block 2114.

[0112] In some embodiments, the high-pressure channels 281 communicate with the second control liquid cavity 26 through the first adjustment channel 283, and the low-pressure channels 282 communicate with the first control liquid cavity 27 through the second adjustment channel 284. Alternatively, the high-pressure channels 281 communicate with the second control liquid cavity 26 through the second adjustment channel 284, and the low-pressure channels 282 communicate with the first control liquid cavity 27 through the first adjustment channel 283.

[0113] AsFigure 4 As shown, according to the coupling assembly 20 of some embodiments of the present application, the surfaces of the plurality of spacers 2114 facing the axis of the mating cylinder 211 are located on the same cylindrical surface, the surfaces of the plurality of protrusions 2411 facing away from the axis of the mating cylinder 211 are located on the same cylindrical surface, and the diameters of the two cylindrical surfaces are equal. Such design not only simplifies the structure and facilitates sealing of all the flow channels 28 without angular difference, but also helps improve the reliability of the rotational connection between the mating cylinder 211 and the mating column 241, and is conducive to ensuring the coaxiality of the two, and is conducive to the hydraulic control system 100 to withstand the vibration and jolt during vehicle driving.

[0114] According to the coupling assembly 20 of some embodiments of the present application, in combination Figure 3 Figure 4 The opening of each flow channel 28 is provided on the bottom wall 2115 of the cylinder, and is distributed in a circumferential direction.

[0115] As Figure 5 shown, the flow channels 28 include a high-pressure channel 281, a low-pressure channel 282, a first regulating channel 283, and a second regulating channel 284. Providing the openings of the flow channels 28 on the bottom wall 2115 of the cylinder is conducive to smooth flow and effective management of the hydraulic medium.

[0116] Firstly, when the mating cylinder 211 and the mating column 241 rotate relative to each other, the hydraulic medium can quickly enter or exit each flow channel 28 through the openings on the bottom wall, thereby realizing pressure transmission and regulation. Such design reduces the resistance and energy loss of the hydraulic medium during flow, and improves the efficiency of the hydraulic system.

[0117] Secondly, the circumferentially spaced distribution of the openings ensures the uniformity and stability of the hydraulic medium during flow. Since the openings are uniformly distributed in the circumferential direction, the hydraulic medium can flow in multiple directions at the same time, avoiding pressure fluctuations and instability caused by excessive or insufficient local flow. Such design helps maintain the system in a stable operating state and improves its ability to cope with various working conditions. In addition, the openings are arranged here so that the connecting pipes interfere with the housing 22, improving the reliability of the connecting pipes.

[0118] In some embodiments, a sealing ring (not shown in the figure) is arranged at the mating port 2111 of the mating cylinder 211 to cooperate with the mating column 241. Alternatively, a snap ring (not shown in the figure) is arranged at the mating port 2111 of the mating cylinder 211 to cooperate with the mating column 241, and the snap ring is used to define the sealing ring.

[0119] ​The slidable clutching coupling assembly 20 of some embodiments of the present application further comprises a guiding structure 25, which comprises guiding ribs 251 and guiding grooves 252 arranged in an axial direction. By arranging the guiding structure 25, it is ensured that the first ring gear 212 can be smoothly and accurately moved during the coupling and decoupling processes.

[0120] In some embodiments not shown in the figures, the guiding ribs 251 are arranged on the inner circumferential surface of the first ring gear 212. The guiding ribs 251 are arranged in such a way that they can directly act on the rotating body in contact with the first ring gear 212. This direct action mechanism enables the first ring gear 212 to smoothly move along the preset path when moving, reducing the possibility of deviation and shaking.

[0121] The guiding grooves 252 are arranged on the outer circumferential surface of at least one of the first rotating body 210 and the second rotating body 240. Then, the first ring gear 212 can realize stable and reliable guiding effect with at least one of the first rotating body 210 and the second rotating body 240 through the guiding grooves 252.

[0122] Specifically, when the coupling operation is needed, the first ring gear 212 will move axially along the guiding grooves 252 on the first rotating body 210. During this process, the guiding ribs 251 are closely embedded in the guiding grooves 252, providing stable guidance and support for the first ring gear 212. As the first ring gear 212 continues to move, it will gradually approach and eventually mesh with the second ring gear 242 on the second rotating body 240. This meshing process becomes accurate and reliable due to the presence of the guiding structure 25, ensuring the continuity and stability of power transmission.

[0123] Alternatively, the guiding ribs 251 are arranged on the outer circumferential surface of at least one of the first rotating body 210 and the second rotating body 240, and the guiding grooves 252 are arranged on the inner circumferential surface of the first ring gear 212.

[0124] In the design of the slidable clutching coupling assembly 20, there is another configuration scheme of the guiding structure 25, i.e. the guiding ribs 251 are arranged on the outer circumferential surface of at least one of the first rotating body 210 or the second rotating body 240, and the corresponding guiding grooves 252 are arranged on the inner circumferential surface of the first ring gear 212. This reverse configuration can also realize stable and reliable guiding function.

[0125] Specifically, when the first ring gear 212 needs to slide axially to couple or decouple with the second ring gear 242 on the rotating body, the guide grooves 252 on the inner circumferential surface of the first ring gear 212 will closely match the guide ribs 251 on the outer circumferential surface of the rotating body. The guide ribs 251 slide along the track of the guide grooves 252, providing the first ring gear 212 with a clear movement path and stable support. This matching mechanism ensures the accuracy and smoothness of the first ring gear 212 during movement, reducing the negative effects caused by positional deviation or shaking.

[0126] In combination Figure 10 The guide ribs 251 are arranged on the outer circumferential surface of the first rotating body 210.

[0127] Specifically, the outer circumferential surface of the first rotating body 210 is arranged with multiple guide ribs 251 in a circumferential interval, so that the part of the first rotating body 210 provided with the guide ribs 251 constitutes a spline shaft, and the inner circumferential surface of the first ring gear 212 is provided with multiple guide grooves 252, which are arranged one-to-one with the multiple guide ribs 251.

[0128] By arranging the circumferentially spaced guide ribs 251, not only the structural strength of the rotating body is enhanced, but also the part of the rotating body is functionally similar to a spline shaft, providing an accurate guide path for the components cooperating therewith.

[0129] Correspondingly, the inner circumferential surface of the first ring gear 212 is provided with guide grooves 252 corresponding to the guide ribs 251. The shape, size and position of the guide grooves 252 are adapted to the guide ribs 251 to ensure that they can perfectly match the guide ribs 251 on the first rotating body 210. When the first ring gear 212 needs to slide axially, the guide grooves 252 on the inner circumferential surface of the first ring gear 212 will slide along the guide ribs 251 on the outer circumferential surface of the rotating body, thereby achieving a stable and reliable guide function.

[0130] This arrangement not only improves the transmission efficiency and accuracy of the slidable coupling assembly 20, but also enhances its durability and reliability. By ensuring the close match between the guide ribs 251 and the guide grooves 252, friction and wear during sliding can be effectively reduced, prolonging the service life of the assembly.

[0131] Optionally, the circumferential dimension of the guide groove 252 is a width dimension, and the width of the guide groove 252 is greater than the width of the guide rib 251.

[0132] Firstly, the wider width of the guide groove 252 provides more sliding space for the guide rib 251, reducing the jamming phenomenon caused by minor size deviation or manufacturing tolerance, thereby ensuring that the first ring gear 212 and the first rotating body 210 (or the second rotating body 240) can smoothly slide axially.

[0133] Secondly, even when affected by external vibrations, impacts or load changes, etc. adverse factors, the wider guide groove 252 can effectively maintain the stable position of the guide ribs 251 therein, prevent it from deviating from the predetermined sliding track, and further ensure the reliable operation of the coupling assembly 20.

[0134] In addition, in some optional embodiments, a lubricant is also filled between the guide groove 252 and the guide rib 251. Then the wider guide groove 252 is beneficial to the accommodation and distribution of the lubricant. During sliding, the lubricant fills in the gap between the guide groove 252 and the guide rib 251, reduces the friction coefficient, reduces the wear rate, and further improves the sliding efficiency and the service life of the assembly.

[0135] In some specific embodiments, as shown in Figure 10 The end surface of the first ring gear 212 facing the second ring gear 242 forms the first meshing teeth 2121, and the inner peripheral surface of the first ring gear 212 forms the guide groove 252, and the part between the adjacent two guide grooves 252 of the inner peripheral surface of the first ring gear 212 is the spacer rib. The first meshing teeth 2121 and the spacer ribs are arranged one by one.

[0136] In the above technical solution, the spacer ribs not only play the role of separating the guide grooves 252, but also enhance the overall structural strength of the first ring gear 212. They are arranged one by one with the first meshing teeth 2121, which means that each meshing tooth corresponds to a spacer rib. This layout helps to optimize the stress condition of the first ring gear 212, reduce stress concentration, and improve the carrying capacity and service life of the assembly.

[0137] In addition, the spacer rib also provides convenience for the assembly and positioning of the coupling assembly 20. During assembly, the relative position between the first ring gear 212 and the first rotating body 210 (or the second rotating body 240) can be ensured to be correct through the spacer rib, avoiding mispositioning or deflection. At the same time, the spacer rib can also be used as a reference point for adjusting the gap or compensating for wear, so that the coupling assembly 20 can maintain stable performance during long-term use.

[0138] In some embodiments, the surfaces of all first meshing teeth 2121 and all spacer ribs facing the axis of the first ring gear 212 are located on the same cylindrical surface.

[0139] From the direction of the axis of the first ring gear 212, the first meshing teeth 2121 for transmitting power and the spacer ribs for separating, supporting or adjusting the gap between them have perfect edges or contact surfaces on the surface of an imaginary cylinder. This alignment ensures high precision, low noise and long-term stability of the coupling assembly 20 during operation.

[0140] In addition, the arrangement simplifies the manufacturing and assembly process, because all the relevant components follow the same cylindrical surface standard, thereby reducing the assembly difficulties caused by dimensional deviation or position error.

[0141] According to some embodiments of the application, the meshing teeth of the first ring gear 212 and the second ring gear 242 are trapezoidal teeth or triangular teeth.

[0142] In some embodiments, as shown in Figure 10 the meshing teeth of the first ring gear 212 and the second ring gear 242 are trapezoidal teeth. This is because the trapezoidal teeth have a wide tooth surface and a gradually changing tooth shape, which can withstand larger normal load and tangential load, and are suitable for use in high-power and high-torque transmission occasions. The involute tooth shape design of the trapezoidal teeth makes the meshing between teeth more stable, reduces impact and vibration, and improves transmission efficiency and service life. The trapezoidal teeth are relatively simple to process and can be achieved by various methods such as gear hobbing and gear shaping, thereby reducing manufacturing costs.

[0143] In some alternative embodiments, the meshing teeth of the first ring gear 212 and the second ring gear 242 are triangular teeth. This is because the degree of coincidence between the tooth surfaces of the triangular teeth is high, which not only improves the efficiency of the transmission, but also makes the transmission process smooth and less likely to produce impact and vibration. Therefore, the triangular teeth have low noise and long service life.

[0144] As shown in Figure 10 According to some embodiments of the application, the slippable clutch coupling assembly 20 further comprises an elastic member 23 connected between the first rotating body 210 and the first ring gear 212 to drive the first ring gear 212 to engage or disengage the second ring gear 242.

[0145] Specifically, when it is necessary to disengage the first ring gear 212 from the second ring gear 242, the elastic member 23 can store and release energy to drive the first ring gear 212 to slide axially, thereby disengaging from the second ring gear 242. This design makes the clutching operation simple and fast. During the clutching process, the elastic member 23 also acts as a buffer to reduce impact and vibration caused by sudden disengagement, thereby protecting other components of the coupling assembly 20 from damage.

[0146] Of course, in other embodiments, the elastic member 23 connected between the first rotating body 210 and the first ring gear 212 can also be used to drive the first ring gear 212 to approach and engage the second ring gear 242.

[0147] In some alternative embodiments, the elastic member 23 includes but is not limited to a spring member, a rubber member, etc.

[0148] In the above embodiments, when the first rod body 101 and the second rod body 102 have a rotation angle difference, the speed of the hydraulic drive device 30 driving the clutch to be combined can be fixed or controlled by detecting the effective control to improve controllability.

[0149] In some embodiments, as shown in FIG. 1, the hydraulic control system 100 further comprises a detection device 40 for obtaining a driving parameter of the vehicle. The detection device 40 is electrically connected with the hydraulic drive device 30 to adjust the hydraulic pressure difference between the first connecting end 301 and the second connecting end 302. Here, the detection device 40 can be a detection component provided in the vehicle itself, such as an acceleration sensor, an inclination sensor, etc., or a newly added sensor for cooperating with the new function of the hydraulic control system 100, which is not limited here. Figure 1

[0150] The driving parameter of the vehicle is mainly the lateral acceleration of the vehicle, which refers to the left→right and right→left acceleration of the human body.

[0151] In some specific embodiments, one of the first rotating body 210 and the second rotating body 240 is a cooperating cylinder 211, and the other is a cooperating column 241. The cooperating cylinder 211 has a cooperating cavity 2112 formed therein and an axial one end being a cooperating opening 2111. The cooperating column 241 is assembled in the cooperating cavity 2112 through the cooperating opening 2111. A liquid flow channel 28 is formed between the inner wall of the cooperating cylinder 211 and the outer wall of the cooperating column 241. The first connecting end 301 is connected with the first control liquid cavity 27 through the liquid flow channel 28. When the rotation angle difference between the cooperating cylinder 211 and the cooperating column 241 is zero, the path of the liquid flow channel 28 to the first control liquid cavity 27 is disconnected. When the rotation angle difference between the cooperating cylinder 211 and the cooperating column 241 reaches a set angle range, the path of the liquid flow channel 28 to the first control liquid cavity 27 is connected. Thus, the coupling assembly 20 can be used as a driving signal source.

[0152] According to the vehicle of the second aspect of the present application, the vehicle comprises the hydraulic control system 100 of the second aspect of the present application.

[0153] According to the vehicle of some embodiments of the present application, by introducing the hydraulic control system 100, the controllability and driving safety of the vehicle are improved.

[0154] ​When the vehicle encounters a risk of rolling or needs to enhance the driving stability, the hydraulic drive device 30 responds to inject hydraulic medium into the high-pressure channel 281 in the coupling assembly 20, at which time the matching cylinder 211 is turned to the first corner range a1 relative to the matching column 241. The high-pressure channel 281 is in communication with the first adjusting channel 283, and the hydraulic medium flows into the second control liquid cavity 26 through the high-pressure channel 281 and the first adjusting channel 283, so that the hydraulic pressure P1 of the second control liquid cavity 26 is higher than the hydraulic pressure P2 of the first control liquid cavity 27. In turn, the first ring gear 212 and the second ring gear 242 are engaged, the first rod body 101 and the second rod body 102 are locked, effectively limiting the rolling amplitude of the vehicle, and improving the driving stability.

[0155] When the vehicle is in a stable state, the matching cylinder 211 is turned to the second corner range a2 relative to the matching column 241, and the high-pressure channel 281 is in communication with the second adjusting channel 284. At this time, the hydraulic medium is in communication with the first control liquid cavity 27 through the high-pressure channel 281 and the second adjusting channel 284, so that the hydraulic pressure P2 of the first control liquid cavity 27 is higher than the hydraulic pressure P1 of the second control liquid cavity 26. In turn, the first ring gear 212 and the second ring gear 242 are driven away from each other, and the first rod body 101 and the second rod body 102 are automatically rotated relative to each other. At this time, the first rod body 101 and the second rod body 102 will not pull each other, and thus will not significantly affect the driving state of the vehicle. Therefore, the driver and the passengers can enjoy a smooth and comfortable ride experience.

[0156] It is worth noting that the type of vehicle to which the hydraulic control system 100 according to the embodiments of the present application is applied is not limited, and can be a fuel vehicle, a new energy vehicle, or an extended range vehicle. The vehicle can also include a small car, an SUV, an MPV, or a commercial vehicle, etc.

[0157] The hydraulic control system 100 is arranged at the front end and / or the rear end of the vehicle.

[0158] The hydraulic control system 100 is used to improve the ride comfort of the vehicle, while improving the steering stability and driving safety. It can be arranged separately in the front end suspension or the rear end suspension of the vehicle, or simultaneously arranged in both. In the present application, the hydraulic control system 100 is applied to the front end suspension of the vehicle as an example to describe its structure, and the scenarios in which the hydraulic control system 100 is applied to other positions will not be described again.

[0159] According to the hydraulic control method of the stabilizer bar according to the third aspect of the present application, the hydraulic control system 100 of the stabilizer bar described above is used, and the structure thereof will not be described again here.

[0160] The hydraulic control method of the stabilizer bar, with reference to Figure 12 , comprises:

[0161] Obtaining the lateral acceleration of the vehicle;

[0162] According to the lateral acceleration, the hydraulic difference of the first connecting end 301 and the second connecting end 302 of the hydraulic drive device 30 is adjusted.

[0163] In this way, the coupling speed of the coupling assembly 20 can be matched with the degree of roll of the vehicle. The more serious the roll is, the faster the coupling is, and the more timely the stabilizer bar plays the role of stabilizing balance.

[0164] Here, the way of obtaining the lateral acceleration is not limited, which can be directly measured by a lateral acceleration sensor, or obtained according to the left and right wheel jump difference and the steering wheel steering angle. How to calculate the lateral acceleration from the left and right wheel jump difference and the steering wheel steering angle is prior art, which will not be described here.

[0165] As shown in Figure 7 The hydraulic drive device 30 includes a hydraulic pump 33 with adjustable speed, and the speed of the hydraulic pump 33 has at least two gears, and the lateral acceleration is divided into at least two intervals. The hydraulic difference of the first connecting end 301 and the second connecting end 302 of the hydraulic drive device 30 is adjusted, including: judging the interval of the measured lateral acceleration in real time, and adjusting the speed gear of the hydraulic pump 33 according to the interval. In this way, multi-gear control is adopted to improve the flexibility of control.

[0166] Specifically as shown in Figure 13 The operation of the hydraulic pump 33 has three gears, which are gear 1, gear 2 and gear 3, and the operating speeds of the three gears gradually increase.

[0167] During the driving of the vehicle, when the measured lateral acceleration is less than 0.1 times of the gravitational acceleration, the hydraulic pump 33 is in gear 1. When the measured lateral acceleration is greater than or equal to 0.1 times of the gravitational acceleration and less than or equal to 0.3 times of the gravitational acceleration, the hydraulic pump 33 is in gear 2. When the measured lateral acceleration is greater than 0.3 times of the gravitational acceleration, the hydraulic pump 33 is in gear 3. In this way, the coupling assembly 20 can obtain a matched coupling speed according to the lateral acceleration.

[0168] Other configurations of the hydraulic control system according to the embodiments of the present application, such as vehicles, are known to those skilled in the art, and will not be described in detail here.

[0169] In the description of the present specification, the description referring to the terms "embodiment", "example" and the like means that the specific features, structures, materials or characteristics described in connection with the embodiment or example are included in at least one embodiment or example of the present application. In the present specification, the illustrative description of the above terms does not necessarily refer to the same embodiment or example. Moreover, the specific features, structures, materials or characteristics described can be combined in any one or more embodiments or examples in a suitable manner.

[0170] While embodiments of the application have been shown and described, it is to be understood that the embodiments described are merely divergences of the principles and application of the present application and that numerous modifications, changes, substitutions, and alterations can be made thereto without departing from the spirit and scope of the present application, which is defined by the following claims and their equivalents.

Claims

1. A hydraulic control system for a stabilizer bar, characterized by, The application relates to a stabilizer bar assembly, which comprises a first bar body and a second bar body, a coupling assembly arranged between the first bar body and the second bar body, and a housing arranged outside the first gear ring and the second gear ring. The coupling assembly comprises a first coupling body and a second coupling body. The first coupling body comprises a first rotating body and a first gear ring. The second coupling body comprises a second rotating body and a second gear ring. The first rotating body is connected to the first bar body. The second rotating body is coaxially connected to the first rotating body. The second rotating body is connected to the second bar body. The second gear ring is arranged around the second rotating body. The housing is arranged outside the first gear ring and the second gear ring. A first control liquid cavity is formed in the housing on the side of the first gear ring away from the second gear ring. A second control liquid cavity is formed between the first gear ring and the second gear ring. A hydraulic drive device has a first connecting end and a second connecting end. The first connecting end is connected to the first control liquid cavity. The second connecting end is connected to the second control liquid cavity. The first gear ring is driven to move between an engaged state and a disengaged state by a hydraulic pressure difference. In the engaged state, the first gear ring is engaged with the second gear ring. In the disengaged state, the first gear ring is disengaged from the second gear ring. One of the first rotating body and the second rotating body is a matching cylinder, and the other is a matching column. A matching cavity is formed in the matching cylinder, and an axial end of the matching cavity is a matching opening. The matching column is assembled in the matching cavity through the matching opening. A liquid flow channel is formed between the inner wall of the matching cylinder and the outer wall of the matching column. The first connecting end is connected to the first control liquid cavity through the liquid flow channel. When the angle difference between the matching cylinder and the matching column is zero, the liquid flow channel is disconnected from the first control liquid cavity. When the angle difference between the matching cylinder and the matching column reaches a set angle range, the liquid flow channel is connected to the first control liquid cavity. The liquid flow channel is a plurality of channels distributed along the ring direction of the matching cylinder. The first connecting end is connected to the high-pressure channel. The second connecting end is connected to the low-pressure channel. The first adjusting channel and the second adjusting channel are arranged on the two sides of the high-pressure channel along the ring direction. The second adjusting channel and the first adjusting channel are arranged on the two sides of the low-pressure channel along the ring direction. When the angle difference between the matching cylinder and the matching column is zero, the plurality of liquid flow channels are not connected to each other. When the matching cylinder is rotated to a first angle range relative to the matching column, the high-pressure channel is connected to the first adjusting channel, and the low-pressure channel is connected to the second adjusting channel. When the matching cylinder is rotated to a second angle range relative to the matching column, the high-pressure channel is connected to the second adjusting channel, and the low-pressure channel is connected to the first adjusting channel. One of the first adjusting channel and the second adjusting channel is connected to the first control liquid cavity. The inner wall of the matching cylinder is provided with at least two grooves distributed in the circumferential direction, and the part of the inner wall of the matching cylinder between two adjacent grooves is a partition block. Some of the grooves form the high-pressure channel, and some of the grooves form the low-pressure channel. The matching column includes at least two protrusions and at least two partition grooves. The protrusions are arranged on the outer wall of the matching column, and at least two protrusions are distributed in the circumferential direction. The partition grooves are formed between two adjacent protrusions. Some of the partition grooves form the first adjusting channel, and some of the partition grooves form the second adjusting channel. When the corner difference between the matching cylinder and the matching column is zero, the outer wall of the matching column closes all the grooves. Each protrusion is arranged opposite to one groove, and each partition groove is arranged opposite to one partition block.

2. The hydraulic control system of a stabilizer bar according to claim 1, characterized in that, Further comprising: a detection device for obtaining a driving parameter of the vehicle; The detection device is electrically connected with the hydraulic drive device to adjust the hydraulic pressure difference between the first connection end and the second connection end.

3. The hydraulic control system for a stabilizer bar according to claim 1, characterized by, Further comprising: a hydraulic control one-way valve, which includes a first input port, a second input port, and a high-pressure output port. The first input port communicates with the first adjusting channel, the second input port communicates with the second adjusting channel, the high-pressure output port communicates with the input port with higher hydraulic pressure, and the high-pressure output port communicates with the first control liquid chamber.

4. The hydraulic control system of a stabilizer bar according to any one of claims 1 to 3, characterized in that, The coupling assembly further comprises a guide structure, which comprises a guide rib and a guide groove extending in the axial direction; The guide rib is arranged on the inner circumferential surface of the first ring gear, and the guide groove is arranged on the outer circumferential surface of at least one of the first rotating body and the second rotating body. Or the guide rib is arranged on the outer circumferential surface of at least one of the first rotating body and the second rotating body, and the guide groove is arranged on the inner circumferential surface of the first ring gear.

5. The hydraulic control system of a stabilizer bar according to any one of claims 1 to 3, characterized in that, Further comprising: a resilient member connected to the first ring gear to drive the first ring gear to disengage or engage the second ring gear.

6. A vehicle characterized by comprising: Including: a hydraulic control system of the stabilizer bar according to any one of claims 1-5.

7. A hydraulic control method of a stabilizer bar for the hydraulic control system of the stabilizer bar according to any one of claims 1 to 5, characterized by, Including: obtaining a lateral acceleration of the vehicle; adjusting the hydraulic pressure difference between the first connection end and the second connection end of the hydraulic drive device according to the lateral acceleration.

8. The hydraulic control method of a stabilizer bar according to claim 7, characterized by, The hydraulic drive device includes a hydraulic pump with adjustable rotating speed, the rotating speed of the hydraulic pump has at least two gears, and the lateral acceleration is divided into at least two intervals; The adjustment of the hydraulic pressure difference between the first connection end and the second connection end of the hydraulic drive device includes: real-time judging the interval of the measured lateral acceleration, and adjusting the rotating speed gear of the hydraulic pump according to the interval.

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