Hydraulic bushing

Abstract

The application provides a hydraulic bushing, which comprises an inner tube, a main spring rubber and an outer tube coaxially assembled, a first liquid cavity, a second liquid cavity and a transition flow channel are formed between the inner circumferential surface of the outer tube and the outer circumferential surface of the main spring rubber, the first liquid cavity and the second liquid cavity are filled with working fluid and are communicated with each other through the transition flow channel; a first liquid guide is arranged in the first liquid cavity, an inertial flow channel is formed on the first liquid guide, used for connecting the first liquid cavity and the transition flow channel, and a pressure relief hole is arranged in the inertial flow channel. The hydraulic bushing can significantly reduce the resonance or cavity abnormal sound risk under the condition of having larger damping, the damping peak of the product is obviously shifted backward, the deformation amount is more reasonable when the same excitation is borne, the transmission of vibration to the vehicle body and the cabin can be effectively reduced, and the driving and riding experience is softer.

Description

Technical Field

[0001] This invention relates to the field of automotive suspension technology, and more specifically, to a hydraulic bushing. Background Technology

[0002] Hydraulic bushings, as core components of automotive suspension systems, achieve vibration damping and impact buffering through the synergistic effect of internal fluid flow and rubber elastic deformation, which is crucial for improving vehicle ride comfort, handling stability, and NVH performance.

[0003] To address this, Chinese Patent Application No. 201410068497.0 discloses a hydraulic bushing comprising an outer tube, an inner tube, a rubber portion disposed between the outer tube and the inner tube, and stoppers disposed at both ends. The bushing includes: a liquid chamber formed and filled with working fluid between the inner circumferential surface of the outer tube and the outer circumferential surface of the rubber portion; and a flow path formed between the inner circumferential surface of the outer tube and the outer circumferential surface of the rubber portion and connected to the liquid chamber to guide the movement of the working fluid; the flow path includes a protrusion extending inward. This design can extend the fluid flow distance without increasing the product volume, thereby optimizing dynamic characteristics.

[0004] Chinese Patent Application No. 202310279878.2 discloses a damping adjustable hydraulic bushing and its control method, which consists of a hydraulic bushing body and a solenoid valve. The hydraulic bushing body includes a bushing bracket, a main spring rubber, a cast aluminum inner tube, an aluminum outer tube, and a cage-shaped frame. The cast aluminum inner tube, the main spring rubber, and the aluminum outer tube are arranged coaxially from the inside to the outside. The cage-shaped frame is placed inside the main spring rubber to support it. Two flow channel plates are assembled between the aluminum outer tube and the main spring rubber, so that a brake fluid chamber and an acceleration fluid chamber are formed between the main spring rubber and the flow channel plates, respectively. The brake flow channel on the brake side flow channel plate and the acceleration flow channel on the acceleration side flow channel plate cooperate to form a passage. A connecting bridge is provided on the cage-shaped frame, and the solenoid valve is bolted to the connecting bridge. An axial actuation hole is provided on the cage-shaped frame, and an actuation rod is installed in the axial actuation hole. The actuation rod is controlled by the solenoid valve. This solution can change the flow channel opening by controlling the position of the actuator rod through a solenoid valve, thereby achieving real-time adjustment of dynamic stiffness and damping under different working conditions.

[0005] Furthermore, Chinese patent application number 202510950399.8 discloses a dual-rubber hydraulic bushing for new energy vehicles, including an inner tube and an outer tube, with a first liquid chamber and a second liquid chamber horizontally arranged between the inner and outer tubes; it also includes a flow channel plate with an inertial channel. This solution, through the adoption of a dual-rubber structure design, balances vibration reduction, noise reduction, and durability.

[0006] All of the above solutions use the flow channels of the guide plate to implement the flow between different chambers in order to improve product damping and quickly eliminate vibration; however, under certain working conditions, excessive excitation can lead to excessive pressure in the chamber, and as the temperature rises, the small gas in the liquid chamber will burst, resulting in abnormal noise in the cavity; in addition, the large shock wave generated by the excessive fluid flow velocity can cause severe deformation of the rubber membrane in the liquid chamber, which will also affect the fatigue durability of the rubber. Summary of the Invention

[0007] The problem solved by this invention is to avoid cavity noise under certain working conditions due to excessive excitation, while ensuring that the hydraulic bushing has sufficient damping.

[0008] To address the aforementioned problems, this invention provides a hydraulic bushing comprising an inner tube, a main spring rubber, and an outer tube coaxially assembled. A first liquid cavity, a second liquid cavity, and a transition channel are formed between the inner circumferential surface of the outer tube and the outer circumferential surface of the main spring rubber. The first and second liquid cavities are filled with working fluid and are interconnected through the transition channel. A first fluid guide is provided in the first liquid cavity, and an inertial flow channel is formed on the first fluid guide for connecting the first liquid cavity and the transition channel. The inertial flow channel is provided with a pressure relief hole.

[0009] This application utilizes a pressure relief hole to divert some fluid, slowing down the fluid flow rate, weakening the shock wave intensity, and preventing abnormal increases in chamber pressure. Simultaneously, it promptly discharges residual fine gas from the first liquid chamber, preventing gas explosions when temperatures rise, significantly reducing the risk of resonance or cavity noise, and further lowering market complaints and defect rates. Furthermore, the pressure relief hole enables rapid drainage and reduces chamber pressure, minimizing the deformation of the main spring rubber and preventing damage to the rubber diaphragm due to excessive stretching or compression, significantly improving the long-term durability of the hydraulic bushing. The inertial flow channel ensures sufficient damping in the hydraulic bushing, enabling rapid vibration decay. This solves the problem of excessive pressure under special operating conditions such as high excitation and high temperatures without fundamentally altering the damping characteristics of the main flow channel.

[0010] Preferably, the inertial flow channel includes an inlet section, a connecting section, and an outlet section connected together. The inlet section is connected to the transition flow channel at the end furthest from the connecting section, and the outlet section is located near the transition flow channel at the end furthest from the connecting section. The pressure relief hole is located in the inlet section or the connecting section.

[0011] This design can release high pressure in a timely manner, preventing a sharp increase in pressure caused by shock waves in the first chamber; at the same time, it can also prevent excessive leakage from affecting the mainstream efficiency of fluid flowing from the inertial channel to the transition channel or from the transition channel to the inertial channel, while ensuring the damping characteristics of the mainstream channel and suppressing abnormal noise in the cavity.

[0012] Preferably, the pressure relief hole extends radially along the hydraulic bushing and communicates with the first liquid chamber.

[0013] This design prevents excessive fluid buildup in the flow channel from generating strong shock waves, reducing abnormal noises caused by sudden pressure changes at the source. Meanwhile, the pressure relief hole is a "micro-through hole," only functioning to release fluid when pressure is abnormal. Under normal operating conditions, fluid flow still relies on the flow channel of the guide plate, ensuring the product's original vibration attenuation and impact buffering capabilities. It also prevents excessive deformation of the rubber diaphragm from causing dynamic characteristic deviations, ensuring the dynamic stiffness stability of the hydraulic bushing under different excitations, and improving vehicle driving comfort and handling stability.

[0014] Preferably, the hydraulic bushing further includes a second liquid guide, which is located inside the second liquid cavity. The second liquid guide and the second liquid guide have the same structure and are symmetrically arranged on both sides of the inner tube.

[0015] This design can divert high-speed fluids in the first and second liquid chambers, significantly reducing the intensity of shock waves under high-excitation conditions. By simultaneously depressurizing the first and second liquid chambers, the pressure fluctuation amplitude can be reduced to further improve NVH performance, significantly reducing market complaints and defect rates caused by cavity noise. In addition, it makes the pressure on both sides of the main spring rubber more balanced, avoiding excessive local stretching or compression of the rubber caused by excessive pressure on one side, and extending the overall service life of the hydraulic bushing.

[0016] Preferably, the first liquid guiding component includes an arc-shaped liquid guiding plate, on the side of the liquid guiding plate near the inner tube, a liquid guiding rubber is provided, the liquid guiding plate is metal and integrally formed with the liquid guiding rubber through a vulcanization process, and the liquid guiding plate is provided with the inertial flow channel on the side of the liquid guiding plate near the outer tube.

[0017] This design utilizes a metal guide plate as the rigid framework of the first guide component, giving it high strength and resistance to deformation to withstand the fluid impact under high-excitation conditions and prevent sealing failure caused by inertial flow channel deformation. The guide plate and the guide rubber are integrally molded through a vulcanization process to achieve a seamless fit, eliminating assembly gaps and significantly improving sealing performance. At the same time, the arc-shaped guide plate can be adapted to the inner and outer pipes, reducing turbulence around the flow channel and allowing the fluid to flow more smoothly along the inertial flow channel. Combined with the diversion effect of the pressure relief hole, it further weakens the shock wave and improves the uniformity of vibration attenuation.

[0018] Preferably, the liquid-guiding rubber has a groove on the side away from the liquid-guiding plate, and there are multiple grooves that extend along the central axis of the inner tube.

[0019] This design increases the elastic deformation space of the fluid-conducting rubber, allowing it to deform better when subjected to vibrations or fluid pressure impacts transmitted from the inner tube, thereby improving buffering and energy absorption efficiency. At the same time, it reduces the impact of thermal stress on the vulcanized connection surface between the fluid-conducting rubber and the fluid-conducting plate, preventing separation due to thermal stress and enhancing structural reliability.

[0020] Preferably, the hydraulic bushing further includes a metal skeleton disposed on the outer periphery of the main spring rubber, wherein the main spring rubber is integrally formed with the metal skeleton and the inner tube through a vulcanization process. This arrangement can effectively transmit the vibration force to the main spring rubber when the hydraulic bushing is impacted, and the main spring rubber converts and absorbs the vibration force; at the same time, the metal skeleton also increases the stress strength of the outer tube, preventing it from deforming under stress and ensuring the stability of the hydraulic bushing in use.

[0021] Preferably, the inner tube has a protrusion on its circumference, and the main spring rubber has a mating part for limiting the assembly of the protrusion. This design helps reduce the transmission of external vibrations to the vehicle body, greatly improving the durability and vibration damping / noise reduction function of the hydraulic bushing, and increasing the service life of the hydraulic bushing.

[0022] Preferably, the outer tube includes a second tube made of rubber, and the second tube is covered with a first tube made of metal. The first tube and the second tube are integrally formed by a vulcanization process.

[0023] This setup uses the rigidity of the first tube to prevent the outer tube from resonating on its own, and can also withstand various complex loads transmitted by the suspension system, ensuring the stability of the connection with the frame. At the same time, the second tube can absorb the small vibrations and noise generated by the internal fluid flow, effectively blocking and attenuating the transmission of high-frequency vibrations and noise from the wheels to the vehicle body.

[0024] Compared with the prior art, the hydraulic bushing described in this embodiment of the invention has the following beneficial effects: 1) By setting a pressure relief hole, the risk of resonance or cavity noise can be significantly reduced under conditions of large damping; 2) By optimizing the position of the relief hole, the damping peak of the product can be significantly shifted backward, and the deformation is more reasonable when subjected to the same excitation, which can effectively reduce the transmission of vibration to the vehicle body and cabin, making the driving experience smoother; 3) The structural modification is small and it is easy to manufacture and process. Attached Figure Description

[0025] Figure 1 This is a top view of the hydraulic bushing described in an embodiment of the present invention;

[0026] Figure 2 for Figure 1 Schematic diagram of the cross section along the AA side;

[0027] Figure 3 for Figure 1 Schematic diagram of the cross section along the BB side;

[0028] Figure 4 This is a schematic diagram of the internal structure of the hydraulic bushing according to an embodiment of the present invention;

[0029] Figure 5 for Figure 4 A schematic diagram of the structure of the hydraulic bushing rotated 180 degrees along the central axis;

[0030] Figure 6 This is a schematic diagram of the structure of the first liquid guiding component in an embodiment of the present invention;

[0031] Figure 7 This is another perspective view of the first liquid guiding component in an embodiment of the present invention;

[0032] Figure 8 The results of bench noise verification of the hydraulic bushing described in this invention before and after improvement;

[0033] Figure 9 This invention relates to the influence of the location of the pressure relief hole on dynamic stiffness and damping angle.

[0034] Explanation of reference numerals in the attached figures:

[0035] 1-Inner tube; 11-Protrusion; 2-Outer tube; 21-First tube; 22-Second tube; 3-Main spring rubber; 31-Matching part; 32-Transition flow channel; 33-Separator; 4-First liquid guide; 41-Liquid guide plate; 411-Inertial flow channel; 4111-Inlet section; 4112-Connecting section; 4113-Outlet section; 412-Pressure relief hole; 413-Overlapping part; 42-Liquid guide rubber; 421-Matching hole; 422-Groove; 5-First liquid chamber; 6-Second liquid chamber; 7-Metal skeleton; 8-Second liquid guide. Detailed Implementation

[0036] To make the above-mentioned objects, features, and advantages of the present invention more apparent and understandable, specific embodiments of the present invention will be described in detail below with reference to the accompanying drawings. Without conflict, the technical features of the embodiments of the present invention can be combined with each other.

[0037] Existing liquid seal bushings utilize guide plates to direct liquid flow between chambers, thereby improving damping performance and achieving rapid vibration reduction. However, while improving damping, this can lead to a series of problems under certain operating conditions: excessive excitation can cause a sudden increase in chamber pressure, generating strong shock waves due to high-speed liquid flow; rising temperatures can cause tiny gases within the liquid chamber to burst, leading to abnormal noises; and if the liquid cannot drain in time, it can cause severe deformation of the rubber diaphragm in the liquid chamber, impairing the rubber's fatigue durability. Therefore, the applicant proposes the following technical solution:

[0038] like Figure 1-7As shown, a hydraulic bushing includes an inner tube 1, a main spring rubber 3, and an outer tube 2 coaxially assembled. A first liquid cavity 5, a second liquid cavity 6, and a transition channel 32 are formed between the inner circumferential surface of the outer tube 2 and the outer circumferential surface of the main spring rubber 3. The first liquid cavity 5 and the second liquid cavity 6 are filled with working fluid and are interconnected through the transition channel 32. A first liquid guide 4 is provided in the first liquid cavity 5. An inertial flow channel 41 is formed on the first liquid guide 4 to connect the first liquid cavity 5 and the transition channel 32. The inertial flow channel 41 is provided with a pressure relief hole 412.

[0039] This application utilizes a pressure relief hole 412 to divert some fluid, slowing down the fluid flow rate, weakening the shock wave intensity, and preventing abnormal increases in chamber pressure. Simultaneously, it promptly discharges residual fine gas from the first liquid chamber 5, preventing gas explosions when temperatures rise, significantly reducing the risk of resonance or cavity noise, and further lowering market complaints and defect rates. Furthermore, the pressure relief hole 412 enables rapid drainage and reduces chamber pressure, minimizing the deformation amplitude of the main spring rubber 3 and preventing damage to the rubber diaphragm due to excessive stretching or compression, significantly improving the long-term durability of the hydraulic bushing. The inertial flow channel 41 ensures sufficient damping in the hydraulic bushing, enabling rapid vibration decay, while the pressure relief hole 412 serves only as an "auxiliary drainage channel," solving the problem of excessive pressure under special operating conditions such as high excitation and high temperature without fundamentally altering the damping characteristics of the main flow channel.

[0040] As an example of the present invention, the main spring rubber 3 is provided with a separator 33, and the first liquid chamber 5 and the second liquid chamber 6 are separated by the separator 33 at the end away from the transition channel 32. This arrangement can prevent the fluid in the two chambers from flowing randomly at the end, ensuring that the fluid can only flow in a directional manner through the preset transition channel 32 and inertial channel 411; it also prevents the fluid shock waves in the first liquid chamber 5 and the second liquid chamber 6 from colliding and superimposing at the end away from the transition channel, dispersing the pressure concentration area and reducing the overall pressure peak of the chamber.

[0041] As an example of the present invention, the inertial flow channel 411 includes an inlet section 4111, a connecting section 4112, and an outlet section 4113 connected together. The inlet section 4111 is connected to the transition flow channel 32 at one end away from the connecting section 4112. The outlet section 4113 is disposed near the transition flow channel 32 at one end away from the connecting section 4112. The pressure relief hole 412 is disposed at either the inlet section 4111 or the connecting section 4112.

[0042] This design can release high pressure in a timely manner, preventing the shock wave in the first chamber 5 from causing a sharp increase in pressure; at the same time, it can also prevent excessive leakage from affecting the mainstream efficiency of fluid flowing from the inertial channel 411 to the transition channel 32 or from the transition channel 32 to the inertial channel 411, while ensuring the damping characteristics of the mainstream channel and suppressing abnormal noise in the cavity.

[0043] Preferably, the pressure relief hole 412 is located in the connecting section 4112. Figure 8 It can be seen that this setting can further shift the damping peak value, and the dynamic stiffness and damping angle decrease more significantly, thus achieving a better effect in suppressing cavity noise.

[0044] As an example of the present invention, the first liquid guiding member 4 includes an arc-shaped liquid guiding plate 41. The liquid guiding plate 41 is provided with a liquid guiding rubber 42 on the side near the inner tube 1. The liquid guiding plate 41 is made of metal and is integrally formed with the liquid guiding rubber 42 through a vulcanization process. The liquid guiding plate 41 is provided with the inertial flow channel 411 on the side near the outer tube 2.

[0045] This design utilizes a metal liquid guide plate 41 as the rigid frame of the first liquid guide component 4, giving it high strength and resistance to deformation to withstand the fluid impact under high excitation conditions and prevent sealing failure caused by deformation of the inertial flow channel 411. The liquid guide rubber 42 is integrally molded through a vulcanization process to achieve a seamless fit between the two, eliminating assembly gaps and significantly improving sealing performance. At the same time, the arc-shaped liquid guide plate 41 can be adapted to the inner tube 1 and the outer tube 2, reducing the generation of turbulence around the flow channel and making the fluid flow more smoothly along the inertial flow channel 411. Combined with the diversion effect of the pressure relief hole 412, it further weakens the shock wave and improves the uniformity of vibration attenuation.

[0046] Preferably, the liquid-guiding rubber 42 has a groove 422 on the side away from the liquid-guiding plate 41, and there are multiple grooves 422 that extend along the central axis of the inner tube 1.

[0047] This design increases the elastic deformation space of the fluid-conducting rubber 42, allowing it to deform better when subjected to vibrations or fluid pressure impacts transmitted by the inner tube 1, thereby improving buffering and energy absorption efficiency. At the same time, it reduces the impact of thermal stress on the vulcanized connection surface between the fluid-conducting rubber 42 and the fluid-conducting plate 41, preventing separation of the two due to thermal stress and enhancing structural reliability.

[0048] As an example of the present invention, the pressure relief hole 412 penetrates the liquid guide plate 41 and communicates with the first liquid cavity 5, or the pressure relief hole 412 penetrates the liquid guide plate 41, and a mating hole 421 is provided on the liquid guide rubber 42 at a position corresponding to the pressure relief hole 412, and the mating hole 421 communicates with the first liquid cavity 5.

[0049] As an example of the present invention, the liquid guide plate 41 is provided with an overlap portion 413 at one end away from the transition channel 32, and the overlap portion 413 is limited to the main spring rubber 3.

[0050] This design ensures the precise circumferential and axial positioning of the guide plate 41 within the hydraulic bushing, preventing misalignment between the inertial flow channel 411 and the transition flow channel 32 due to installation deviation. It also increases the contact area between the guide plate 41 and the main spring rubber 3, thereby dispersing the concentrated stress generated by fluid impact to a larger area. Simultaneously, it limits the movement space of the guide plate 41, reduces the relative friction between the guide plate and the main spring rubber 3 during vibration, and better resists fluid shock waves under high excitation conditions, ensuring the structural stability of the hydraulic bushing under complex conditions and guaranteeing dynamic response accuracy.

[0051] Preferably, the hydraulic bushing further includes a second liquid guide 8, which is located inside the second liquid cavity 6. The second liquid guide 8 and the second liquid guide 5 have the same structure and are symmetrically arranged on both sides of the inner tube 1.

[0052] This design can divert high-speed fluids in the first liquid chamber 5 and the second liquid chamber 6, significantly reducing the intensity of shock waves under high excitation conditions. By simultaneously relieving pressure in the first liquid chamber 5 and the second liquid chamber 6, the pressure fluctuation amplitude can be reduced to further improve NVH performance, significantly reducing market complaints and defect rates caused by cavity noise. In addition, it makes the pressure on both sides of the main spring rubber 3 more balanced, avoiding excessive local stretching or compression of the rubber caused by excessive pressure on one side, and extending the overall service life of the hydraulic bushing.

[0053] As an example of the present invention, the hydraulic bushing further includes a metal skeleton 7 disposed on the outer periphery of the main spring rubber 3. The main spring rubber 3 is integrally formed with the metal skeleton 7 and the inner tube 1 through a vulcanization process. This arrangement can effectively transmit the vibration force to the main spring rubber 3 when the hydraulic bushing is impacted, and the main spring rubber 3 converts and absorbs the vibration force; at the same time, the metal skeleton 7 also increases the stress resistance of the outer tube 2, preventing it from deforming under stress and ensuring the stability of the hydraulic bushing in use. The metal skeleton 7 is hollowed out on both sides, and its specific structure is prior art and will not be described again.

[0054] As an example of the present invention, a protrusion 11 is provided on the periphery of the inner tube 1, and a mating part 31 is provided on the main spring rubber 3 for limiting the assembly of the protrusion 11. This arrangement helps to reduce the transmission of external vibrations to the vehicle body, greatly improves the durability and vibration damping and noise reduction function of the hydraulic bushing, and increases the service life of the hydraulic bushing.

[0055] As an example of the present invention, the outer tube 2 includes a second tube 22 made of rubber, and the second tube 22 is covered with a first tube 21 made of metal. The first tube 21 and the second tube 22 are integrally formed by a vulcanization process.

[0056] This setup uses the rigidity of the first tube 21 to prevent the outer tube 2 from resonating on its own, and can also withstand various complex loads transmitted by the suspension system, ensuring the stability of the connection with the frame. At the same time, the second tube 22 can absorb the small vibrations and noise generated by the internal fluid flow, effectively blocking and attenuating the transmission of high-frequency vibrations and noise from the wheels to the vehicle body.

[0057] During assembly, the inner tube 1, the main spring rubber 3, and the metal skeleton 7 are integrally formed by vulcanization. The first tube 22 and the second tube 22 are integrally formed by vulcanization to form the outer tube 2. The liquid guide plate 41 and the liquid guide rubber 42 are integrally formed by vulcanization to form the first liquid guide component 4 and the second liquid guide component 8. The first liquid guide component 4 is assembled into the first liquid cavity 5, and the second liquid guide component 8 is assembled into the second liquid cavity 6. Then, the outer tube 2 is fitted on top to form the final product.

[0058] The hydraulic bushing of this application (with a pressure relief hole 412 in the inlet section 4111) and the hydraulic bushing without a pressure relief hole 412 were subjected to bench noise verification. The results are shown in […]. Figure 8 The "red zone" represents the risk of resonance or cavity noise; by Figure 8 It can be seen that after the hydraulic bushing of the present invention adds a vent hole, the corresponding red high-risk area is significantly reduced or disappears, indicating that it can effectively weaken the intensity of the shock wave and the probability of gas explosion, thereby reducing the risk of abnormal noise in the cavity.

[0059] In addition, the dynamic stiffness and damping angle of the hydraulic bushings prepared with pressure relief holes 412 in the inlet section 4111 and the connecting section 4112 were measured respectively, and the results are shown in […]. Figure 9 .Depend on Figure 9 It is known that the location of the vent hole 412 affects the dynamic stiffness and damping angle of the final product. Specifically, when the vent hole 412 is located in the inlet section 4111 and close to the transition channel 32, its damping peak value shifts backward, and both the dynamic stiffness and damping angle decrease slightly. When the vent hole 412 is located in the connecting section 4112, its damping peak value shifts backward even more, and the dynamic stiffness decreases significantly. This indicates that under the same excitation, the deformation is more reasonable, which can effectively reduce the transmission of vibration to the body and cabin, making the driving experience smoother. In addition, the damping angle also decreases significantly, indicating that the rhythm of damping energy dissipation is more gradual, avoiding the "hard impact" caused by excessive damping, while reducing the fluid shock wave caused by instantaneous strong damping, indirectly alleviating the problem of excessive chamber pressure, and further protecting the life of rubber parts.

[0060] While the present invention has been disclosed above, it is not limited thereto. Any person skilled in the art can make various modifications and alterations without departing from the spirit and scope of the invention; therefore, the scope of protection of the present invention should be determined by the scope defined in the claims.

Claims

1. A hydraulic bushing, comprising an inner tube (1), a main spring rubber (3), and an outer tube (2) coaxially assembled, wherein a first liquid cavity (5), a second liquid cavity (6), and a transition channel (32) are formed between the inner circumferential surface of the outer tube (2) and the outer circumferential surface of the main spring rubber (3), the first liquid cavity (5) and the second liquid cavity (6) are filled with working fluid and are interconnected through the transition channel (32); a first liquid guide (4) is provided in the first liquid cavity (5), and an inertial flow channel (41) is formed on the first liquid guide (4) for connecting the first liquid cavity (5) and the transition channel (32), characterized in that, The inertial flow channel (41) is provided with a pressure relief hole (412).

2. The hydraulic bushing according to claim 1, characterized in that, The inertial flow channel (411) includes an inlet section (4111), a connecting section (4112), and an outlet section (4113). The inlet section (4111) is connected to the transition flow channel (32) at one end away from the connecting section (4112). The outlet section (4113) is located near the transition flow channel (32) at one end away from the connecting section (4112). The pressure relief hole (412) is located in the inlet section (4111) or the connecting section (4112).

3. The hydraulic bushing according to claim 2, characterized in that, The pressure relief hole (412) extends radially along the hydraulic bushing and communicates with the first liquid chamber (5).

4. The hydraulic bushing according to claim 1, characterized in that, The hydraulic bushing also includes a second liquid guide (8), which is located in the second liquid chamber (6). The second liquid guide (8) and the second liquid guide (5) have the same structure and are symmetrically arranged on both sides of the inner tube (1).

5. The hydraulic bushing according to claim 1, characterized in that, The first liquid guiding component (4) includes an arc-shaped liquid guiding plate (41). The liquid guiding plate (41) has a liquid guiding rubber (42) on the side near the inner tube (1). The liquid guiding plate (41) is made of metal and is integrally formed with the liquid guiding rubber (42) through a vulcanization process. The liquid guiding plate (41) has an inertial flow channel (411) on the side near the outer tube (2).

6. The hydraulic bushing according to claim 5, characterized in that, The liquid-guiding rubber (42) has a groove (422) on the side away from the liquid-guiding plate (41), and there are multiple grooves (422) that extend along the central axis of the inner tube (1).

7. The hydraulic bushing according to claim 1, characterized in that, The hydraulic bushing also includes a metal skeleton (7) disposed on the outer periphery of the main spring rubber (3), and the main spring rubber (3) is integrally formed with the metal skeleton (7) and the inner tube (1) through a vulcanization process.

8. The hydraulic bushing according to claim 7, characterized in that, The inner tube (1) has a protrusion (11) on its periphery, and the main spring rubber (3) has a mating part (31) for limiting the assembly of the protrusion (11).

9. The hydraulic bushing according to claim 1, characterized in that, The outer tube (2) includes a second tube (22) made of rubber, and the second tube (22) is covered with a first tube (21) made of metal. The first tube (21) and the second tube (22) are integrally formed by vulcanization process.

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