Hydraulic bushing and automobile

Abstract

This invention provides a hydraulic bushing and an automobile. The hydraulic bushing includes an inner tube, an outer tube, and a rubber main spring. The inner and outer tubes are concentrically fitted to form a receiving space, and the rubber main spring fills the receiving space. It also includes a flow channel plate. Three recesses are provided along the circumferential direction on the rubber main spring. The flow channel plate is fitted onto the outside of the rubber main spring, and its inner side mates with the three recesses to form an energy storage hydraulic chamber and two main hydraulic chambers located on either side of the energy storage hydraulic chamber. The outer side of the flow channel plate abuts against the inner wall of the outer tube, forming a first fluid channel and a second fluid channel. The two main hydraulic chambers are respectively connected to the energy storage hydraulic chamber through the first fluid channel and to each other through the second fluid channel. In this invention, by using the series connection of the two main hydraulic chambers and the parallel flow principle of the energy storage hydraulic chamber, the volume and viscosity of the liquid are changed, achieving peak damping at both low and high frequencies, thus enhancing performance.

Description

Technical Field

[0001] This invention belongs to the field of hydraulic bushing technology, specifically relating to a hydraulic bushing and an automobile. Background Technology

[0002] With the use of electronic control components in automobiles, while bringing intelligence and convenience, it also brings adverse factors such as increased unsprung mass and the generation of high-frequency excitation, which have a significant negative impact on vehicle ride comfort and handling stability. Hydraulic bushings, as a barrier to prevent unsprung vibrations from being transmitted to the vehicle body, are a powerful tool for ensuring good vehicle comfort and handling stability. Under normal circumstances, the resonance frequency range of the unsprung mass in a car is approximately between 15Hz and 20Hz. Ordinary hydraulic bushings can provide high damping characteristics to attenuate vibrations under this low-frequency excitation, with a peak damping hysteresis angle exceeding 40°. However, as the unsprung mass increases, multiple factors combine to generate high-frequency excitation. Ordinary hydraulic bushings, limited by their structure, cannot improve vibration isolation performance at high frequencies, and the damping peak value is not adjustable, affecting comfort ratings.

[0003] The existing hydraulic bushing structure has limited damping adjustment, providing a fixed damping value only at low frequencies and large amplitudes, which cannot meet the performance requirements of more complex working conditions; the damping adjustment range is narrow, and when the frequencies of steering wheel vibration, brake vibration and suspension arm vibration overlap, impact noise is likely to occur. Summary of the Invention

[0004] This invention provides a hydraulic bushing to solve the problem that existing hydraulic bushings have limited damping and stiffness adjustment, and are prone to impact noise.

[0005] A hydraulic bushing includes an inner tube, an outer tube, and a rubber main spring. The inner tube and the outer tube are concentrically fitted to form an accommodating space. The rubber main spring fills the accommodating space. The bushing also includes a flow channel plate.

[0006] The rubber main spring has three recesses along the circumferential direction.

[0007] The flow channel plate is fitted on the outside of the rubber main spring, and the inner side of the flow channel plate is engaged with the three recesses to form an energy storage hydraulic chamber and two main hydraulic chambers located on both sides of the energy storage hydraulic chamber.

[0008] The outer side of the flow channel plate abuts against the inner wall of the outer tube, forming a first fluid channel and a second fluid channel;

[0009] The two main hydraulic chambers are respectively connected to the energy storage hydraulic chamber through the first fluid channel, and the two main hydraulic chambers are connected through the second fluid channel.

[0010] Preferably, the first fluid channel is a straight channel, and the second fluid channel is an annular channel, with the second fluid channel surrounding the first fluid channel.

[0011] Preferably, the flow channel plate is provided with a first flow channel groove and a second flow channel groove arranged circumferentially and parallel to each other, and the outer side of the flow channel plate abuts against the inner wall of the outer tube, so that the first flow channel groove and the second flow channel groove respectively form a first fluid channel and a second fluid channel.

[0012] A first through hole is provided in the middle of the first fluid channel, and the first through hole is connected to the energy storage hydraulic chamber. A second through hole is provided at each end of the first fluid channel, and a second through hole is connected to a main hydraulic chamber.

[0013] The second fluid channel is provided with two oppositely arranged third through holes, one of which is connected to one of the main hydraulic chambers.

[0014] Preferably, the flow channel plate comprises two mutually symmetrical semi-circular plates;

[0015] Each of the semi-circular plates is provided with an arc-shaped channel and a C-shaped channel along its circumference, and the C-shaped channel is located on the outside of the arc-shaped channel;

[0016] The openings of the two arc-shaped channels correspond to each other to form the first fluid channel, and the openings of the two C-shaped channels correspond to each other to form the second fluid channel.

[0017] Preferably, the first through hole is located at the junction of the two arc-shaped channels, the second through hole is located at the upper end of the arc-shaped channel away from the first through hole, and the third through hole is located at the bend of the C-shaped channel.

[0018] Preferably, the hydraulic bushing further includes a main spring skeleton, which is vulcanized inside the rubber main spring. The main spring skeleton has three hollowed-out areas that correspond one-to-one with the three recesses.

[0019] Preferably, the hydraulic bushing further includes a limiting covering layer, which is disposed between the inner tube and the rubber main spring;

[0020] The limiting covering layer includes a covering body and a limiting block extending outward from the middle of the covering body along the radial direction of the inner tube. The covering body and the limiting block cooperate to form a limiting support.

[0021] Preferably, the limiting block includes at least two limiting protrusions, and a first groove is formed between two adjacent limiting protrusions arranged along the axial direction of the inner tube.

[0022] Preferably, the rubber main spring at the location of the main hydraulic chamber is in contact with the limiting block, so that the rubber main spring has a buffer protrusion and a second groove that match the limiting protrusion and the first groove, and a floating point is provided between two adjacent buffer protrusions.

[0023] Preferably, a layer of magnetic particles is provided on the rubber main spring at the location of the energy storage hydraulic chamber.

[0024] Preferably, the outer surface of the inner tube has a wave-like structure.

[0025] An automobile includes the aforementioned hydraulic bushing.

[0026] In this invention, the inner and outer tubes are concentrically fitted to form a accommodating space. A rubber main spring is filled within this space, forming a hydraulic bushing that provides damping and attenuates vibration energy transmitted from the outside. The inner tube is a cylindrical steel tube, and the outer tube is a thin-walled steel tube. The rubber main spring is a solid structure, vulcanized and molded, and is filled between the inner and outer tubes. The outer tube and the rubber main spring are interference-fitted and press-fitted with a reduced-diameter riveted joint to ensure a tight seal. It primarily bears the torsional force during the up-and-down movement of the swing arm and the lateral force during forward and backward impacts. Three recesses are provided on the rubber main spring along the circumferential direction. A flow channel plate is fitted on the outside of the rubber main spring, and the inner side of the flow channel plate mates with the three recesses to form an energy storage hydraulic chamber and two main hydraulic chambers located on both sides of the energy storage hydraulic chamber. The energy storage hydraulic chamber and the main hydraulic chambers are encapsulated with liquid, which is a mixture of water and ethylene glycol in a certain proportion, and can flow in the energy storage hydraulic chamber and the main hydraulic chambers. The outer side of the flow channel plate abuts against the inner wall of the outer tube to form a first fluid channel and a second fluid channel arranged in a circumferential direction and parallel to each other. The two main hydraulic chambers are connected to the energy storage hydraulic chamber through the first fluid channel and the two main hydraulic chambers are connected through the second fluid channel. When the hydraulic bushing is subjected to external force, the rubber main spring deforms, the volume of the two main hydraulic chambers changes, and the pressure in the two main hydraulic chambers changes. The liquid in the two main hydraulic chambers is pressurized and flows and exchanges through the second fluid channel. The two main hydraulic chambers flow and exchange with the energy storage hydraulic chamber through the first fluid channel. The friction loss, inertial loss and local loss generated during this flow process can effectively attenuate vibration energy.

[0027] The two main hydraulic chambers are connected in series through a second fluid channel, while the energy storage hydraulic chamber is connected in parallel with the two main hydraulic chambers through a first fluid channel. During low-frequency, large-amplitude vibrations, the two main hydraulic chambers are interconnected, while during high-frequency, small-amplitude vibrations, the energy storage hydraulic chamber is interconnected with the two main hydraulic chambers. By altering the flow principle of the series connection of the two main hydraulic chambers and the parallel connection of the energy storage hydraulic chamber, the volume and viscosity of the liquid are changed, achieving peak damping in both low-frequency and high-frequency ranges. This results in performance enhancement and maintains high damping characteristics over a wide frequency range, providing good vibration isolation performance, improving comfort, and reducing road noise. Attached Figure Description

[0028] Figure 1 This is a top view of the hydraulic bushing in this invention;

[0029] Figure 2 yes Figure 1 Sectional view of AA;

[0030] Figure 3 yes Figure 2 Sectional view of BB;

[0031] Figure 4 This is an axonometric view of the hydraulic bushing from a first perspective in this invention;

[0032] Figure 5 This is an axonometric view of the hydraulic bushing from a second perspective in this invention;

[0033] Figure 6 This is a front view of the flow channel plate in this invention;

[0034] Figure 7 This is a multi-channel performance prediction diagram of the hydraulic bushing in this invention;

[0035] Figure 8 This is a prediction diagram of the series and parallel performance of the hydraulic bushing in this invention.

[0036] Among them, 1. Inner tube; 2. Outer tube; 3. Rubber main spring; 4. Flow channel plate; 41. Semi-circular plate; 42. Arc-shaped channel; 43. C-shaped channel; 5. Recess; 6. Energy storage hydraulic chamber; 7. Main hydraulic chamber; 8. First fluid channel; 9. Second fluid channel; 10. First through hole; 11. Second through hole; 12. Third through hole; 13. Main spring skeleton; 14. Hollowed-out; 15. Limiting covering layer; 151. Covering body; 152. Limiting block; 153. Limiting protrusion; 16. First groove; 17. Buffer protrusion; 18. Second groove; 19. Floating point; 20. Magnetic particle layer. Detailed Implementation

[0037] To make the technical problems solved, the technical solutions, and the beneficial effects of this invention clearer, the invention will be further described in detail below with reference to the accompanying drawings and embodiments. It should be understood that the specific embodiments described herein are merely illustrative of the invention and are not intended to limit the invention.

[0038] In the description of this invention, it should be understood that the terms "longitudinal," "radial," "length," "width," "thickness," "upper," "lower," "front," "rear," "left," "right," "vertical," "horizontal," "top," "bottom," "inner," and "outer," etc., indicating orientation or positional relationships, are based on the orientation or positional relationships shown in the accompanying drawings and are only for the convenience of describing the invention and simplifying the description, and do not indicate or imply that the device or element referred to must have a specific orientation, or be constructed and operated in a specific orientation, and therefore should not be construed as a limitation of the invention. In the description of this invention, unless otherwise stated, "a plurality of" means two or more.

[0039] In the description of this invention, it should be noted that, unless otherwise explicitly specified and limited, the terms "installation," "connection," and "linking" should be interpreted broadly. For example, they can refer to a fixed connection, a detachable connection, or an integral connection; they can refer to a mechanical connection or an electrical connection; they can refer to a direct connection or an indirect connection through an intermediate medium; and they can refer to the internal connection of two components. Those skilled in the art can understand the specific meaning of the above terms in this invention based on the specific circumstances.

[0040] This invention provides a hydraulic bushing, see reference. Figure 1-8 The hydraulic bushing includes an inner tube 1, an outer tube 2, and a rubber main spring 3. The inner tube 1 and the outer tube 2 are concentrically fitted to form an accommodating space, and the rubber main spring 3 is filled in the accommodating space. The hydraulic bushing also includes a flow channel plate 4. Three recesses 5 are provided on the rubber main spring 3 along the circumferential direction. The flow channel plate 4 is fitted on the outside of the rubber main spring 3. The inner side of the flow channel plate 4 cooperates with the three recesses 5 to form an energy storage hydraulic chamber 6 and two main hydraulic chambers 7 located on both sides of the energy storage hydraulic chamber 6. The outer side of the flow channel plate 4 abuts against the inner wall of the outer tube 2 to form a first fluid channel 8 and a second fluid channel 9. The two main hydraulic chambers 7 are respectively connected to the energy storage hydraulic chamber 6 through the first fluid channel 8 and the two main hydraulic chambers 7 are connected through the second fluid channel 9.

[0041] As an example, the inner tube 1 and outer tube 2 are concentrically fitted together to form a receiving space. The rubber main spring 3 is filled in the receiving space to form a hydraulic bushing, which can provide damping and attenuate the vibration energy transmitted from the outside. Among them, the inner tube 1 is a cylindrical steel tube, the outer tube 2 is a thin-walled steel tube, and the rubber main spring 3 is a solid structure, vulcanized and filled between the inner tube 1 and the outer tube 2. The outer tube 2 and the rubber main spring 3 are interference fit, and the diameter reduction riveting is press-fitted to ensure sealing. It mainly bears the torsional force when the swing arm jumps up and down and the lateral force when it is impacted from front to back.

[0042] In this example, three recesses 5 are provided on the rubber main spring 3 along the circumferential direction. The flow channel plate 4 is fitted on the outside of the rubber main spring 3, and the inner side of the flow channel plate 4 cooperates with the three recesses 5 to form an energy storage hydraulic chamber 6 and two main hydraulic chambers 7 located on both sides of the energy storage hydraulic chamber 6. The energy storage hydraulic chamber 6 and the main hydraulic chambers 7 are filled with liquid, which is a mixture of water and ethylene glycol in a certain proportion, and can flow in the energy storage hydraulic chamber 6 and the main hydraulic chambers 7. The outer side of the flow channel plate 4 abuts against the inner wall of the outer tube 2 to form a first fluid channel 8 and a second fluid channel 9 arranged in the circumferential direction and parallel to each other. The pressure chamber 7 is connected to the energy storage hydraulic chamber 6 through the first fluid channel 8, and the two main hydraulic chambers 7 are connected through the second fluid channel 9. When the hydraulic bushing is subjected to external force, the rubber main spring 3 deforms, and the volume of the two main hydraulic chambers 7 changes, resulting in a change in the pressure inside the two main hydraulic chambers 7. The liquid in the two main hydraulic chambers 7 is pressurized and flows and exchanges through the second fluid channel 9. The two main hydraulic chambers 7 are respectively connected to the energy storage hydraulic chamber 6 through the first fluid channel 8. The friction loss, inertia loss and local loss generated during this flow process can effectively attenuate the vibration energy.

[0043] The two main hydraulic chambers 7 are connected in series through the second fluid channel 9, and the energy storage hydraulic chamber 6 is connected in parallel with the two main hydraulic chambers 7 through the first fluid channel 8. During low-frequency, large-amplitude vibrations, the two main hydraulic chambers 7 are interconnected, while during high-frequency, small-amplitude vibrations, the energy storage hydraulic chamber 6 is interconnected with the two main hydraulic chambers 7. By changing the flow principle of the series connection of the two main hydraulic chambers 7 and the parallel connection of the energy storage hydraulic chamber 6, the volume and viscosity of the liquid are changed, achieving peak damping in both low-frequency and high-frequency ranges, thus enhancing performance. Furthermore, it maintains high damping characteristics over a wide frequency range, exhibiting good vibration isolation performance, improving comfort, and reducing road noise.

[0044] Existing hydraulic bushings have limited damping and stiffness adjustment, making them prone to impact noise. For example, when using hydraulic bushings in automobiles, the damping is only adjustable during low-frequency, high-amplitude excitation (frequency range between 15Hz and 20Hz), and the stiffness can only be adjusted by the hardness of the rubber material itself, which is not conducive to vibration reduction and noise reduction. In this embodiment, the hydraulic bushing is connected in series with two main hydraulic chambers 7, and the energy storage hydraulic chamber 6 is connected in parallel with the two main hydraulic chambers 7 (e.g., Figure 7 Multi-channel performance prediction can shift the dynamic characteristic curve backward, that is, shift the frequency at which the peak occurs backward. This shift is beneficial for obtaining greater damping and lower dynamic stiffness in the required frequency range (such as the engine's second-order frequency of 25-30Hz). Simultaneously, through the magnetorheological volume effect of the energy storage hydraulic chamber 6, the pressure and viscosity of the liquid are changed, allowing the peak to be reached again in the high-frequency range (such as the subframe resonance frequency of 40-70 Hz). The entire process achieves adjustable and shiftable damping, and the ability to reach the peak multiple times, achieving more complex performance optimization goals (such as...). Figure 8The series-parallel performance prediction shows a double peak value for damping and dynamic stiffness characteristics, where A and B represent the two main hydraulic chambers 7 and C represents the energy storage hydraulic chamber 6. This is beneficial for comfort adjustment under complex working conditions, and the performance is expandable (the viscosity of the liquid flow can be further adjusted by adding electrodes). It is convenient to adjust the damping and stiffness of the hydraulic bushing, which is limited, and avoids impact noise.

[0045] In one embodiment, reference is made to Figure 4 , Figure 5 and Figure 6 The first fluid channel 8 is a straight channel, and the second fluid channel 9 is an annular channel, surrounding the first fluid channel 8.

[0046] As an example, the first fluid channel 8 is a straight channel used to realize fluid exchange between the energy storage hydraulic chamber 6 and the two main hydraulic chambers 7. The second fluid channel 9 is an annular channel used to realize fluid exchange between the two main hydraulic chambers 7. The second fluid channel 9 surrounds the first fluid channel 8, which can ensure the overall force balance of the flow channel plate 4 and avoid uneven deformation of the hydraulic bushing, which would cause channel blockage. The fluid channels are distributed on the flow channel plate 4. The number and shape of the fluid channels can be adjusted according to actual needs. The more complex the shape of the fluid channel, the greater the flow resistance, and the larger the peak value of the damping hysteresis angle. The more fluid channels there are, the more lag the damping characteristics, that is, the damping curve shifts backward and the higher the frequency of peak values.

[0047] In one embodiment, reference is made to Figure 4 , Figure 5 and Figure 6 The flow channel plate 4 is provided with a first flow channel groove and a second flow channel groove arranged circumferentially and parallel to each other. The outer side of the flow channel plate 4 abuts against the inner wall of the outer tube 2, so that the first flow channel groove and the second flow channel groove form a first fluid channel 8 and a second fluid channel 9. A first through hole 10 is provided in the middle of the first fluid channel 8, which is connected to the energy storage hydraulic chamber 6. A second through hole 11 is provided at each end of the first fluid channel 8, and a second through hole 11 is connected to a main hydraulic chamber 7. Two oppositely arranged third through holes 12 are provided on the second fluid channel 9, and a third through hole 12 is connected to a main hydraulic chamber 7.

[0048] As an example, the flow channel plate 4 is provided with a first flow channel groove and a second flow channel groove arranged circumferentially and parallel to each other. The outer side of the flow channel plate 4 abuts against the inner wall of the outer pipe 2, so that the first flow channel groove and the second flow channel groove form a first fluid channel 8 and a second fluid channel 9. A first through hole 10 is provided in the middle of the first fluid channel 8, and a second through hole 11 is provided at each end of the first fluid channel 8. The first through hole 10 is connected to the energy storage hydraulic chamber 6, and the two second through holes 11 are connected to the two main hydraulic chambers 7, respectively, to facilitate the flow exchange of liquid in the two main hydraulic chambers 7 with the liquid in the energy storage hydraulic chamber 6. The second fluid channel 9 is provided with two oppositely arranged... The third through hole 12 connects to the two main hydraulic chambers 7, facilitating fluid exchange within them. This configuration connects the two main hydraulic chambers 7 in series, with the energy storage hydraulic chamber 6 connected in parallel. During low-frequency, high-amplitude vibrations, the two main hydraulic chambers 7 are interconnected, while during high-frequency, low-amplitude vibrations, the energy storage hydraulic chamber 6 is interconnected with the two main hydraulic chambers 7. By utilizing the series connection of the two main hydraulic chambers 7 and the parallel connection of the energy storage hydraulic chamber 6, the volume and viscosity of the fluid are altered, achieving peak damping at both low and high frequencies. This enhances performance and maintains high damping characteristics over a wide frequency range, resulting in better vibration isolation, improved comfort, and reduced road noise.

[0049] In one embodiment, reference is made to Figure 3 , Figure 4 , Figure 5 and Figure 6 The flow channel plate 4 includes two mutually symmetrical semi-circular plates 41; each semi-circular plate 41 is provided with an arc-shaped channel 42 and a C-shaped channel 43 along the circumference, and the C-shaped channel 43 is located outside the arc-shaped channel 42; the openings of the two arc-shaped channels 42 correspond to each other to form a first fluid channel 8, and the openings of the two C-shaped channels 43 correspond to each other to form a second fluid channel 9.

[0050] As an example, the flow channel plate 4 includes two semi-circular plates 41, which are symmetrically combined to form a circular flow channel plate 4, which is fitted onto the rubber main spring 3. Each semi-circular plate 41 has an arc-shaped channel 42 and a C-shaped channel 43 along its circumference. The openings of the two arc-shaped channels 42 correspond to each other to form a first fluid channel 8, which is a straight channel used to realize the fluid exchange between the energy storage hydraulic chamber 6 and the two main hydraulic chambers 7. The openings of the two C-shaped channels 43 correspond to each other to form a second fluid channel 9, which is an annular channel used to realize the fluid exchange between the two main hydraulic chambers 7. The C-shaped channel 43 is located outside the arc-shaped channel 42, so the second fluid channel 9 surrounds the first fluid channel 8, which can ensure the overall force balance of the flow channel plate 4 and avoid uneven deformation of the hydraulic bushing, which would cause channel blockage. The flow channel plate 4 is a split type, with good flow channel damping adjustment, sealing, and stability, which can improve the NVH performance of the whole vehicle.

[0051] In one embodiment, reference is made to Figure 4 , Figure 5 and Figure 6 The first through hole 10 is located at the junction of the two arc-shaped channels 42, the second through hole 11 is located at the end of the arc-shaped channel 42 away from the first through hole 10, and the third through hole 12 is located at the bend of the C-shaped channel 43.

[0052] As an example, a first through-hole 10 is located at the junction of two arc-shaped channels 42, and a second through-hole 11 is located at the upper end of the arc-shaped channel 42 away from the first through-hole 10, which facilitates the flow exchange of liquid between the two main hydraulic chambers 7 and the accumulator hydraulic chamber 6. A third through-hole 12 is located at the bend of the C-shaped channel 43, which also facilitates the flow exchange of liquid within the two main hydraulic chambers 7. This configuration connects the two main hydraulic chambers 7 in series and the accumulator hydraulic chamber 6 in parallel with the two main hydraulic chambers 7. During low-frequency, high-amplitude vibrations, the two main hydraulic chambers 7 are interconnected, while during high-frequency, low-amplitude vibrations, the accumulator hydraulic chamber 6 is interconnected with the two main hydraulic chambers 7. By utilizing the series connection of the two main hydraulic chambers 7 and the parallel connection of the accumulator hydraulic chamber 6, the volume and viscosity of the liquid are changed, achieving peak damping in both low-frequency and high-frequency ranges, thus enhancing performance. Furthermore, it maintains high damping characteristics over a wide frequency range, exhibiting good vibration isolation performance, improving comfort, and reducing road noise.

[0053] In one embodiment, reference is made to Figure 2 and Figure 3 The hydraulic bushing also includes a main spring skeleton 13, which is vulcanized inside the rubber main spring 3. The main spring skeleton 13 has three hollows 14, which correspond one-to-one with three recesses 5.

[0054] As an example, the hydraulic bushing also includes a main spring skeleton 13, which is vulcanized with the rubber main spring 3 to provide support and shape, so that the rubber main spring 3 can have greater radial stiffness in the solid direction to resist deformation and improve service life; the main spring skeleton 13 has three hollows 14, which correspond one-to-one with three recesses 5, leaving enough space to store liquid, such as hydraulic oil.

[0055] In one embodiment, reference is made to Figure 2 and Figure 3 The hydraulic bushing also includes a limiting cover layer 15, which is disposed between the inner tube 1 and the rubber main spring 3. The limiting cover layer 15 includes a cover body 151 and a limiting block 152 extending outward from the middle of the cover body 151 along the radial direction of the inner tube 1. The cover body 151 and the limiting block 152 cooperate to form a limiting support.

[0056] As an example, the hydraulic bushing also includes a limiting covering layer 15 disposed between the inner tube 1 and the rubber main spring 3. The limiting covering layer 15 includes a covering body 151 and a limiting block 152 extending outward from the middle of the covering body 151 along the radial direction of the inner tube 1. The limiting covering layer 15 is a layer of hard nylon or resin wrapped around the outer layer of the inner tube 1. The covering body 151 and the limiting block 152 cooperate to form a limiting support for the rubber main spring 3. When an impact occurs, it can play a buffering role, provide limiting support for the rubber main spring 3, and improve the service life of the rubber main spring 3.

[0057] In one embodiment, reference is made to Figure 2 and Figure 3 The limiting block 152 includes at least two limiting protrusions 153, and a first groove 16 is formed between two adjacent limiting protrusions 153 along the axial direction of the inner tube 1.

[0058] As an example, the limiting block 152 includes at least two limiting protrusions 153, and a first groove 16 is formed between two adjacent limiting protrusions 153 along the axial direction of the inner tube 1. The at least two limiting protrusions 153 are symmetrically distributed with the inner tube 1 as the axis of symmetry, which can change the flow resistance in the circumferential direction, improve the buffering function, and provide limiting support for the rubber main spring 3, thereby improving the service life of the rubber main spring 3. The at least two limiting protrusions 153 can be set as six-lobed, which can form six first grooves 16, further improving the buffering function.

[0059] In one embodiment, reference is made to Figure 2 and Figure 3 The rubber main spring 3 at the location of the main hydraulic chamber 7 is in contact with the limiting block 152, so that the rubber main spring 3 has a buffer protrusion 17 and a second groove 18 corresponding to the limiting protrusion 153 and the first groove 16, and a floating point 19 is provided between two adjacent buffer protrusions 17.

[0060] As an example, the rubber main spring 3 at the location of the main hydraulic chamber 7 is in contact with the limiting block 152, so that the rubber main spring 3 has a buffer protrusion 17 and a second groove 18 corresponding to the limiting protrusion 153 and the first groove 16. A floating point 19 is provided between two adjacent buffer protrusions 17. The buffer protrusion 17 can also be formed into a six-lobed shape. The six-lobed protrusion can change the flow resistance in the circumferential direction. The second groove 18 and the floating point 19 can change the contact mode during radial impact. The floating point 19 contacts first, then the line contacts, and finally the surface contacts. This can effectively reduce the probability of abnormal noise and play a role in bidirectional buffering and eliminating abnormal noise.

[0061] In one embodiment, reference is made to Figure 2 and Figure 3 A magnetic particle layer 20 is provided on the rubber main spring 3 at the location of the energy storage hydraulic chamber 6.

[0062] As an example, the volume of the energy storage hydraulic chamber 6 is smaller than that of the main hydraulic chamber 7. When one main hydraulic chamber 7 is impacted by a load PA, part of the liquid is squeezed into the other main hydraulic chamber 7, and the other part is squeezed into the energy storage hydraulic chamber 6 for storage. The flow resistance squeezed into the other main hydraulic chamber 7 generates a large damping hysteresis angle, which reaches a peak value near a low frequency (around 15-20°). The liquid squeezed into the energy storage hydraulic chamber 6 rubs against the magnetic particle layer 20 inside the energy storage hydraulic chamber 6, causing the liquid viscosity to change instantaneously within a limited volume. When it is excited again by a high frequency or small amplitude PC, the liquid in the energy storage hydraulic chamber 6 is squeezed out and flows into both main hydraulic chambers 7 simultaneously, generating a damping hysteresis angle peak value (around 80-100°) again.

[0063] In one embodiment, reference is made to Figure 2 and Figure 3 The outer surface of the inner tube 1 has a wave-like structure.

[0064] As an example, the outer surface of the inner tube 1 has a corrugated structure, which can increase the contact area with the limiting coating layer 15 and improve the adhesion.

[0065] This invention provides an automobile, including a hydraulic bushing.

[0066] As an example, the inner tube 1 and outer tube 2 are concentrically fitted together to form a receiving space. The rubber main spring 3 is filled in the receiving space to form a hydraulic bushing, which can provide damping and attenuate the vibration energy transmitted from the outside. Among them, the inner tube 1 is a cylindrical steel tube, the outer tube 2 is a thin-walled steel tube, and the rubber main spring 3 is a solid structure, vulcanized and filled between the inner tube 1 and the outer tube 2. The outer tube 2 and the rubber main spring 3 are interference fit, and the diameter reduction riveting is press-fitted to ensure sealing. It mainly bears the torsional force when the swing arm jumps up and down and the lateral force when it is impacted from front to back.

[0067] In this example, three recesses 5 are provided on the rubber main spring 3 along the circumferential direction. The flow channel plate 4 is fitted on the outside of the rubber main spring 3, and the inner side of the flow channel plate 4 cooperates with the three recesses 5 to form an energy storage hydraulic chamber 6 and two main hydraulic chambers 7 located on both sides of the energy storage hydraulic chamber 6. The energy storage hydraulic chamber 6 and the main hydraulic chambers 7 are filled with liquid, which is a mixture of water and ethylene glycol in a certain proportion, and can flow in the energy storage hydraulic chamber 6 and the main hydraulic chambers 7. The outer side of the flow channel plate 4 abuts against the inner wall of the outer tube 2 to form a first fluid channel 8 and a second fluid channel 9 arranged in the circumferential direction and parallel to each other. The pressure chamber 7 is connected to the energy storage hydraulic chamber 6 through the first fluid channel 8, and the two main hydraulic chambers 7 are connected through the second fluid channel 9. When the hydraulic bushing is subjected to external force, the rubber main spring 3 deforms, and the volume of the two main hydraulic chambers 7 changes, resulting in a change in the pressure inside the two main hydraulic chambers 7. The liquid in the two main hydraulic chambers 7 is pressurized and flows and exchanges through the second fluid channel 9. The two main hydraulic chambers 7 are respectively connected to the energy storage hydraulic chamber 6 through the first fluid channel 8. The friction loss, inertia loss and local loss generated during this flow process can effectively attenuate the vibration energy.

[0068] The two main hydraulic chambers 7 are connected in series through the second fluid channel 9, and the energy storage hydraulic chamber 6 is connected in parallel with the two main hydraulic chambers 7 through the first fluid channel 8. During low-frequency, large-amplitude vibrations, the two main hydraulic chambers 7 are interconnected, while during high-frequency, small-amplitude vibrations, the energy storage hydraulic chamber 6 is interconnected with the two main hydraulic chambers 7. By changing the flow principle of the series connection of the two main hydraulic chambers 7 and the parallel connection of the energy storage hydraulic chamber 6, the volume and viscosity of the liquid are changed, achieving peak damping in both low-frequency and high-frequency ranges, thus enhancing performance. Furthermore, it maintains high damping characteristics over a wide frequency range, exhibiting good vibration isolation performance, improving comfort, and reducing road noise.

[0069] Existing hydraulic bushings have limited damping and stiffness adjustment, making them prone to impact noise. For example, when using hydraulic bushings in automobiles, the damping is only adjustable during low-frequency, high-amplitude excitation (frequency range between 15Hz and 20Hz), and the stiffness can only be adjusted by the hardness of the rubber material itself, which is not conducive to vibration reduction and noise reduction. In this embodiment, the hydraulic bushing is connected in series with two main hydraulic chambers 7, and the energy storage hydraulic chamber 6 is connected in parallel with the two main hydraulic chambers 7 (e.g., Figure 7 Multi-channel performance prediction can shift the dynamic characteristic curve backward, that is, shift the frequency at which the peak occurs backward. This shift is beneficial for obtaining greater damping and lower dynamic stiffness in the required frequency range (such as the engine's second-order frequency of 25-30Hz). Simultaneously, through the magnetorheological volume effect of the energy storage hydraulic chamber 6, the pressure and viscosity of the liquid are changed, allowing the peak to be reached again in the high-frequency range (such as the subframe resonance frequency of 40-70 Hz). The entire process achieves adjustable and shiftable damping, and the ability to reach the peak multiple times, achieving more complex performance optimization goals (such as...). Figure 8The series-parallel performance prediction shows a double peak value for damping and dynamic stiffness characteristics, where A and B represent the two main hydraulic chambers 7 and C represents the energy storage hydraulic chamber 6. This is beneficial for comfort adjustment under complex working conditions, and the performance is expandable (the viscosity of the liquid flow can be further adjusted by adding electrodes). It is convenient to adjust the damping and stiffness of the hydraulic bushing, which is limited, and avoids impact noise.

[0070] The complete hydraulic bushing structure can be directly press-fitted onto the swing arm body and connected between the wheel and the subframe to realize the swing arm's guiding and force transmission functions. The obtained high damping characteristics can reach the maximum peak value in both low and high frequency ranges, which is beneficial for comfort tuning under complex working conditions, and the performance is expandable.

[0071] The above are merely preferred embodiments of the present invention and are not intended to limit the present invention. Any modifications, equivalent substitutions, and improvements made within the spirit and principles of the present invention should be included within the protection scope of the present invention.

Claims

1. A hydraulic bushing, comprising an inner tube, an outer tube, and a rubber main spring, wherein the inner tube and the outer tube are concentrically fitted to form an accommodating space, and the rubber main spring fills the accommodating space, characterized in that, The hydraulic bushing also includes a flow channel plate; The rubber main spring has three recesses along the circumferential direction. The flow channel plate is fitted on the outside of the rubber main spring, and the inner side of the flow channel plate is engaged with the three recesses to form an energy storage hydraulic chamber and two main hydraulic chambers located on both sides of the energy storage hydraulic chamber. The outer side of the flow channel plate abuts against the inner wall of the outer tube, forming a first fluid channel and a second fluid channel; The two main hydraulic chambers are respectively connected to the energy storage hydraulic chamber through the first fluid channel, and the two main hydraulic chambers are connected through the second fluid channel; The two main hydraulic chambers are connected in series through the second fluid channel, and the energy storage hydraulic chamber is connected in parallel with the two main hydraulic chambers through the first fluid channel. During low-frequency, large-amplitude vibrations, the two main hydraulic chambers are interconnected, and during high-frequency, small-amplitude vibrations, the energy storage hydraulic chamber is interconnected with the two main hydraulic chambers, thereby changing the volume and viscosity of the liquid and achieving peak damping in both low-frequency and high-frequency ranges.

2. The hydraulic bushing according to claim 1, characterized in that, The first fluid channel is a straight channel, and the second fluid channel is an annular channel, which surrounds the first fluid channel.

3. The hydraulic bushing according to claim 1, characterized in that, The flow channel plate is provided with a first flow channel groove and a second flow channel groove arranged circumferentially and parallel to each other. The outer side of the flow channel plate abuts against the inner wall of the outer tube, so that the first flow channel groove and the second flow channel groove respectively form a first fluid channel and a second fluid channel. A first through hole is provided in the middle of the first fluid channel, and the first through hole is connected to the energy storage hydraulic chamber. A second through hole is provided at each end of the first fluid channel, and a second through hole is connected to a main hydraulic chamber. The second fluid channel is provided with two oppositely arranged third through holes, one of which is connected to one of the main hydraulic chambers.

4. The hydraulic bushing according to claim 3, characterized in that, The flow channel plate comprises two mutually symmetrical semi-circular plates; Each of the semi-circular plates is provided with an arc-shaped channel and a C-shaped channel along its circumference, and the C-shaped channel is located on the outside of the arc-shaped channel; The openings of the two arc-shaped channels correspond to each other to form the first fluid channel, and the openings of the two C-shaped channels correspond to each other to form the second fluid channel.

5. The hydraulic bushing according to claim 4, characterized in that, The first through hole is located at the junction of the two arc-shaped channels, the second through hole is located at the upper end of the arc-shaped channel away from the first through hole, and the third through hole is located at the bend of the C-shaped channel.

6. The hydraulic bushing according to claim 1, characterized in that, The hydraulic bushing also includes a main spring skeleton, which is vulcanized inside the rubber main spring. The main spring skeleton has three hollows that correspond one-to-one with the three recesses.

7. The hydraulic bushing according to claim 1, characterized in that, The hydraulic bushing also includes a limiting covering layer, which is disposed between the inner tube and the rubber main spring; The limiting covering layer includes a covering body and a limiting block extending outward from the middle of the covering body along the radial direction of the inner tube. The covering body and the limiting block cooperate to form a limiting support.

8. The hydraulic bushing according to claim 7, characterized in that, The limiting block includes at least two limiting protrusions, and a first groove is formed between two adjacent limiting protrusions along the axial direction of the inner tube.

9. The hydraulic bushing according to claim 8, characterized in that, The rubber main spring at the location of the main hydraulic chamber is in contact with the limiting block, so that a buffer protrusion and a second groove are formed on the rubber main spring that match the limiting protrusion and the first groove, and a floating point is provided between two adjacent buffer protrusions.

10. The hydraulic bushing according to claim 1, characterized in that, A layer of magnetic particles is provided on the rubber main spring at the location of the energy storage hydraulic chamber.

11. The hydraulic bushing according to claim 1, characterized in that, The outer surface of the inner tube has a wave-like structure.

12. A car, characterized in that, Includes the hydraulic bushing as described in any one of claims 1-11.

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