Hydraulic bushing and automobile

Abstract

The invention provides a hydraulic bushing and an automobile, the hydraulic bushing comprises an inner pipe, an outer pipe and a rubber main spring, the inner pipe and the outer pipe are concentrically sleeved to form an accommodating space, the accommodating space is filled with the rubber main spring, and the hydraulic bushing further comprises a runner plate; three recesses are formed in the rubber main spring in the circumferential direction; the rubber main spring is sleeved with the runner plate, and the inner side of the runner plate is matched with the three pits to form an energy storage hydraulic cavity and two main hydraulic cavities located on the two sides of the energy storage hydraulic cavity. The outer side of the runner plate abuts against the inner wall of the outer pipe to form a first fluid channel and a second fluid channel. The two main hydraulic cavities communicate with the energy storage hydraulic cavity through first fluid channels correspondingly, and the two main hydraulic cavities communicate with each other through a second fluid channel. According to the invention, through the series connection of the two main hydraulic cavities and the parallel connection circulation principle of the energy storage hydraulic cavity, the volume and the viscosity of liquid are changed, double peaks of damping at low-frequency and high-frequency bands are realized, and performance supplement is realized.

Description

Technical Field

[0001] The invention belongs to the technical field of hydraulic bushings, and in particular relates to a hydraulic bushing and an automobile. Background Art

[0002] With the use of automotive electronic control components, intelligence and convenience have also brought about unfavorable factors such as increased unsprung mass and high-frequency excitation, which have a great negative effect on the vehicle's smoothness and handling stability. As a barrier to block the transmission of unsprung vibration to the vehicle body, hydraulic bushings are a powerful tool to ensure that the vehicle has good comfort and handling stability. Under normal circumstances, the resonance frequency range of the unsprung mass of a car is approximately between 15Hz and 20Hz. Ordinary hydraulic bushings can provide large damping characteristics to attenuate vibration under this low-frequency excitation, and the peak value of the damping lag angle can reach more than 40°. However, when the unsprung mass continues to increase, multiple factors are superimposed to produce high-frequency excitation. Ordinary hydraulic bushings are limited by the structure and cannot improve the seismic isolation performance at high frequencies. The damping peak cannot be adjusted, which affects the comfort rating.

[0003] The existing hydraulic bushing structure has limited adjustment for damping, and only provides a fixed damping value at low frequency and large amplitude, and cannot meet more complex working performance requirements; the adjustable damping range is narrow, and when the steering wheel vibration, brake jitter frequency and suspension swing arm vibration frequency overlap, impact noise problems are likely to occur. Summary of the invention

[0004] The invention provides a hydraulic bushing to solve the problem that the damping and stiffness adjustment of the existing hydraulic bushing is limited and abnormal impact noise is easy to occur.

[0005] A hydraulic bushing comprises an inner tube, an outer tube and a rubber main spring, wherein the inner tube and the outer tube are concentrically sleeved to form an accommodation space, the rubber main spring is filled in the accommodation space, and further comprises a flow channel plate;

[0006] The rubber main spring is provided with three depressions along the circumferential direction;

[0007] The flow channel plate is sleeved on the outside of the rubber main spring, and the inner side of the flow channel plate cooperates 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 to form a first fluid channel and a second fluid channel;

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

[0010] Preferably, the first fluid channel is a straight-line channel, and the second fluid channel is an annular channel, and the second fluid channel surrounds the first fluid channel.

[0011] Preferably, the flow channel plate is provided with a first flow channel groove and a second flow channel groove which are arranged along the circumference 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 form a first fluid channel and a second fluid channel respectively;

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

[0013] The second fluid channel is provided with two third through holes which are arranged opposite to each other, and one of the third through holes is communicated with one of the main hydraulic chambers.

[0014] Preferably, the flow channel plate comprises two mutually symmetrical semicircular plates;

[0015] Each of the semicircular plates is provided with an arc-shaped channel and a C-shaped channel along the circumference, and the C-shaped channel is provided 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 arranged at the junction of the two arc-shaped channels, the second through hole is arranged on an end of the arc-shaped channel away from the first through hole, and the third through hole is arranged at the bend of the C-shaped channel.

[0018] Preferably, the hydraulic bushing further comprises a main spring skeleton, the main spring skeleton is vulcanized in the rubber main spring, and three hollows are arranged on the main spring skeleton, corresponding one to one with the three depressions.

[0019] Preferably, the hydraulic bushing further comprises a limiting coating layer, and the limiting coating layer is arranged between the inner tube and the rubber main spring;

[0020] The limiting coating layer comprises a coating body and a limiting block extending outward from the middle of the coating body along the radial direction of the inner tube. The coating body cooperates with the limiting block to form a limiting support body.

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

[0022] Preferably, the rubber main spring at the location of the main hydraulic chamber fits with the limit block, so that a buffer protrusion and a second groove matching the limit protrusion and the first groove are formed on the rubber main spring, and a floating point is arranged between two adjacent buffer protrusions.

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

[0024] Preferably, the outer side surface of the inner tube is a corrugated structure.

[0025] A car comprises the hydraulic bushing.

[0026] In the present invention, the inner tube and the outer tube are concentrically mounted to form a containing space, and the rubber main spring is filled in the containing space to form a hydraulic bushing, which can provide damping and attenuate the vibration energy transmitted from the outside. Among them, the inner tube is a cylindrical steel tube, the outer tube is a thin-walled steel tube, the rubber main spring is a solid structure, vulcanized and filled between the inner tube and the outer tube, the outer tube and the rubber main spring are interference fit, and the reduced diameter riveted mouth is pressed to ensure the sealing performance, which mainly bears the torsional force when the swing arm jumps up and down and the lateral force when it impacts forward and backward. Three depressions are arranged on the rubber main spring along the circumferential direction. The flow channel plate is sleeved on the outer side of the rubber main spring. The inner side of the flow channel plate cooperates with the three depressions to form an energy storage hydraulic chamber and two main hydraulic chambers located on both sides of the energy storage hydraulic chamber. Liquid is encapsulated in the energy storage hydraulic chamber and the main hydraulic chamber. The liquid is a mixture of water and ethylene glycol in proportion and can flow in the energy storage hydraulic chamber and the main hydraulic chamber. 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 along the circumferential direction and parallel to each other. The two main hydraulic chambers are respectively connected with 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 is deformed, the volume of the two main hydraulic chambers changes, resulting in a change in the pressure in the two main hydraulic chambers. The liquid in the two main hydraulic chambers is pressurized to flow exchange through the second fluid channel, and the two main hydraulic chambers are respectively exchanged with the energy storage hydraulic chamber through the first fluid channel. The friction loss, inertia loss and local loss generated in the flow process can effectively attenuate the vibration energy.

[0027] The two main hydraulic chambers are connected in series through the second fluid channel, the energy storage hydraulic chamber and the two main hydraulic chambers are connected in parallel through the first fluid channel, the two main hydraulic chambers are interconnected at low frequency and large amplitude, and the energy storage hydraulic chamber and the two main hydraulic chambers are interconnected at high frequency and small amplitude; through the flow principle of the series connection of the two main hydraulic chambers and the parallel connection of one energy storage hydraulic chamber, the volume and viscosity of the liquid are changed, and the damping reaches double peaks in the low frequency and high frequency bands, thereby achieving performance enhancement and maintaining large damping characteristics in a wider frequency range, having better seismic isolation performance, improving comfort and reducing road noise. BRIEF DESCRIPTION OF THE DRAWINGS

[0028] Figure 1 is a top view of the hydraulic bushing of the present invention;

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

[0030] Figure 3 yes Figure 2 Cross-sectional view of the middle BB;

[0031] Figure 4 is an isometric view of the hydraulic bushing in the present invention from a first viewing angle;

[0032] Figure 5 is an isometric view of the hydraulic bushing in the present invention from a second viewing angle;

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

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

[0035] Figure 8 It is a series-parallel performance prediction diagram of the hydraulic bushing in the present invention.

[0036] Among them, 1. inner tube; 2. outer tube; 3. rubber main spring; 4. flow channel plate; 41. semicircular plate; 42. arc channel; 43. C-shaped channel; 5. groove; 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. hollowing; 15. limiting coating layer; 151. coating body; 152. limiting block; 153. limiting protrusion; 16. first groove; 17. buffer protrusion; 18. second groove; 19. floating point; 20. magnetic particle layer. DETAILED DESCRIPTION

[0037] In order to make the technical problems, technical solutions and beneficial effects solved by the present invention more clearly understood, the present invention is further described in detail below in conjunction with the accompanying drawings and embodiments. It should be understood that the specific embodiments described herein are only used to explain the present invention and are not used to limit the present invention.

[0038] In the description of the present invention, it should be understood that the terms "longitudinal", "radial", "length", "width", "thickness", "up", "down", "front", "back", "left", "right", "vertical", "horizontal", "top", "bottom", "inside", "outside" and the like indicate positions or positional relationships based on the positions or positional relationships shown in the drawings, and are only for the convenience of describing the present invention and simplifying the description, rather than indicating or implying that the device or element referred to must have a specific orientation, be constructed and operated in a specific orientation, and therefore cannot be understood as limiting the present invention. In the description of the present invention, unless otherwise specified, "plurality" means two or more.

[0039] In the description of the present invention, it should be noted that, unless otherwise clearly specified and limited, the terms "installed", "connected", and "connected" should be understood in a broad sense, for example, it can be a fixed connection, a detachable connection, or an integral connection; it can be a mechanical connection or an electrical connection; it can be a direct connection, or it can be indirectly connected through an intermediate medium, or it can be the internal communication of two components. For ordinary technicians in this field, the specific meanings of the above terms in the present invention can be understood according to specific circumstances.

[0040] The embodiment of the present invention provides a hydraulic bushing, referring to 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 mounted 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 arranged on the rubber main spring 3 along the circumferential direction, and the flow channel plate 4 is mounted on the outer side 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 with 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 the outer tube 2 are concentrically mounted to form a containing space, and the rubber main spring 3 is filled in the containing 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, 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 reduced diameter riveted mouth is pressed to ensure the sealing, which mainly bears the torsional force when the swing arm jumps up and down and the lateral force when it impacts forward and backward.

[0042] In this example, three depressions 5 are arranged on the rubber main spring 3 along the circumferential direction, the flow channel plate 4 is sleeved on the outer side of the rubber main spring 3, and the inner side of the flow channel plate 4 cooperates with the three depressions 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. Liquid is encapsulated in the energy storage hydraulic chamber 6 and the main hydraulic chamber 7. The liquid is a mixture of water and ethylene glycol in proportion and can flow in the energy storage hydraulic chamber 6 and the main hydraulic chamber 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 two main liquid The pressure chamber 7 is connected with 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 is deformed, and the volumes of the two main hydraulic chambers 7 change, resulting in changes in the pressures in the two main hydraulic chambers 7. The liquids in the two main hydraulic chambers 7 are pressurized to flow exchange through the second fluid channel 9, and the two main hydraulic chambers 7 are respectively exchanged with the energy storage hydraulic chamber 6 through the first fluid channel 8. The friction loss, inertia loss and local loss generated in the 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, the energy storage hydraulic chamber 6 and the two main hydraulic chambers 7 are connected in parallel through the first fluid channel 8, the two main hydraulic chambers 7 are interconnected at low frequency and large amplitude, and the energy storage hydraulic chamber 6 and the two main hydraulic chambers 7 are interconnected at high frequency and small amplitude; through the flow principle of the series connection of the two main hydraulic chambers 7 and the parallel connection of one energy storage hydraulic chamber 6, the volume and viscosity of the liquid are changed, and the damping reaches double peaks in the low frequency and high frequency bands, thereby achieving performance enhancement and maintaining large damping characteristics in a wider frequency range, having better seismic isolation performance, improving comfort and reducing road noise.

[0044] The damping and stiffness adjustment of existing hydraulic bushings are limited, and impact noise is prone to occur. For example, when hydraulic bushings are used in automobiles, the damping of hydraulic bushings can only be adjusted when low-frequency and large-amplitude excitation (frequency range between 15Hz and 20Hz) is applied, and the stiffness can only be adjusted by the hardness of the rubber material itself, which is not conducive to shock absorption and noise reduction. The hydraulic bushing in this embodiment is connected in series through two main hydraulic chambers 7, and the energy storage hydraulic chamber 6 is connected in parallel with the two main hydraulic chambers 7 (such as Figure 7 Multi-channel performance prediction) can realize the backward shift of the dynamic characteristic curve, that is, the frequency of the peak value is shifted backward, which is conducive to obtaining greater damping and lower dynamic stiffness in the required frequency range (such as the second-order frequency of the engine 25-30Hz). At the same time, through the magnetorheological volume effect of the energy storage hydraulic chamber 6, the pressure and viscosity of the liquid are changed, and the peak value is reached again in the high frequency range (such as the subframe resonance frequency 40-70Hz). The entire action process realizes adjustable and movable damping, and can reach the peak value multiple times, achieving more complex performance optimization goals (such as Figure 8Series-parallel performance prediction, double peak values ​​of damping and dynamic stiffness characteristics, where A and B represent two main hydraulic chambers 7, and C represents the energy storage hydraulic chamber 6), is conducive to comfort adjustment under complex working conditions, and the performance is scalable (the viscosity of the liquid flow can be further adjusted by adding electrodes), which is convenient for adjusting the damping and stiffness of the hydraulic bushing to avoid impact and abnormal noise.

[0045] In one embodiment, referring to Figure 4 , Figure 5 and Figure 6 The first fluid channel 8 is a straight-line channel, the second fluid channel 9 is an annular channel, and the second fluid channel 9 surrounds the first fluid channel 8 .

[0046] As an example, it is introduced that the first fluid channel 8 is a straight-line channel for realizing liquid exchange between the energy storage hydraulic chamber 6 and the two main hydraulic chambers 7, and the second fluid channel 9 is an annular channel for realizing liquid 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 to cause channel blockage; the fluid channels are distributed on the flow channel plate 4, and the number and shape of the fluid channels can be adjusted according to actual needs. The more complex the shape of the fluid channel and the greater the flow resistance, the greater the peak value of the damping lag angle; the more the number of fluid channels, the more delayed the damping characteristics, that is, the damping curve moves backward and the frequency of peaks increases.

[0047] In one embodiment, referring 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 which are arranged along the circumference 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, and the first through hole 10 is connected to the energy storage hydraulic chamber 6, and a second through hole 11 is respectively provided at both ends of the first fluid channel 8, and a second through hole 11 is connected to a main hydraulic chamber 7; two third through holes 12 which are arranged oppositely 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 which are arranged along the circumference 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, and a second through hole 11 is provided at both ends 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 respectively connected to the two main hydraulic chambers 7, so as to facilitate the flow exchange of the liquids in the two main hydraulic chambers 7 with the liquids in the energy storage hydraulic chamber 6; the second fluid channel 9 is provided with two relatively arranged The third through hole 12 and the two third through holes 12 are respectively connected with the two main hydraulic chambers 7, so as to facilitate the flow exchange of the liquid in the two main hydraulic chambers 7; the two main hydraulic chambers 7 are arranged in series, and the energy storage hydraulic chamber 6 is connected in parallel with the two main hydraulic chambers 7. The two main hydraulic chambers 7 are interconnected at low frequency and large amplitude, and the energy storage hydraulic chamber 6 is interconnected with the two main hydraulic chambers 7 at high frequency and small amplitude; through the flow principle of the series connection of the two main hydraulic chambers 7 and the parallel connection of an energy storage hydraulic chamber 6, the volume and viscosity of the liquid are changed, and the damping reaches double peaks in the low frequency and high frequency bands, thereby achieving performance enhancement, and maintaining large damping characteristics in a wider frequency range, with better seismic isolation performance, improved comfort, and reduced road noise.

[0049] In one embodiment, referring to Figure 3 , Figure 4 , Figure 5 and Figure 6 The flow channel plate 4 includes two mutually symmetrical semicircular plates 41; each semicircular plate 41 is provided with an arc channel 42 and a C-shaped channel 43 along the circumference, and the C-shaped channel 43 is provided on the outer side of the arc channel 42; the openings of the two arc 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, it is introduced that the flow channel plate 4 includes two semicircular plates 41, and the two semicircular plates 41 are symmetrically combined into a circular flow channel plate 4, which is mounted on the rubber main spring 3. An arc channel 42 and a C-type channel 43 are arranged along the circumference of each semicircular plate 41. The openings of the two arc channels 42 correspond to each other to form a first fluid channel 8. The first fluid channel 8 is a straight-line channel for realizing liquid exchange between the energy storage hydraulic chamber 6 and the two main hydraulic chambers 7. The openings of the two C-type channels 43 correspond to each other to form a second fluid channel 9. The second fluid channel 9 is an annular channel for realizing liquid exchange between the two main hydraulic chambers 7. The C-type channel 43 is arranged on the outside of the arc channel 42, and 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 to cause channel blockage. The flow channel plate 4 is a split type, and the flow channel damping has good adjustability, sealing and stability, which can improve the NVH performance of the whole vehicle.

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

[0052] As an example, it is introduced that the first through hole 10 is set at the junction of two arc-shaped channels 42, and the second through hole 11 is set at the end of the arc-shaped channel 42 away from the first through hole 10, which can facilitate the flow exchange of the liquid in the two main hydraulic chambers 7 with the liquid in the energy storage hydraulic chamber 6 respectively; the third through hole 12 is set at the bend of the C-shaped channel 43, which is convenient for the flow exchange of the liquid in the two main hydraulic chambers 7; in this way, the two main hydraulic chambers 7 are connected in series, and the energy storage hydraulic chamber 6 is connected in parallel with the two main hydraulic chambers 7. At low frequencies and large amplitudes, the two main hydraulic chambers 7 are interconnected, and at high frequencies and small amplitudes, the energy storage hydraulic chamber 6 is interconnected with the two main hydraulic chambers 7; through the flow principle of the series connection of the two main hydraulic chambers 7 and the parallel connection of one energy storage hydraulic chamber 6, the volume and viscosity of the liquid are changed, and the damping reaches double peaks in the low and high frequency bands, thereby achieving performance enhancement, and maintaining large damping characteristics in a wider frequency range, with better seismic isolation performance, improved comfort, and reduced road noise.

[0053] In one embodiment, referring to Figure 2 and Figure 3 The hydraulic bushing further comprises a main spring skeleton 13 , which is vulcanized in the rubber main spring 3 , and the main spring skeleton 13 is provided with three hollows 14 , which correspond to the three depressions 5 one by one.

[0054] As an example, the hydraulic bushing also includes a main spring frame 13, which is vulcanized into one with the rubber main spring 3 to play a supporting and shaping role so that the rubber main spring 3 can have greater radial stiffness in the solid direction to resist deformation and improve service life; three hollows 14 are provided on the main spring frame 13, corresponding to the three recesses 5 one by one, leaving enough space to store liquid, such as hydraulic oil.

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

[0056] As an example, the hydraulic bushing also includes a limiting coating layer 15 arranged between the inner tube 1 and the rubber main spring 3, and the limiting coating layer 15 includes a coating body 151 and a limiting block 152 extending outward from the middle of the coating body 151 along the radial direction of the inner tube 1; wherein, the limiting coating layer 15 is a layer of hard nylon or resin layer wrapped around the outer layer of the inner tube 1, and the coating body 151 cooperates with the limiting block 152 to form a limiting support body for the rubber main spring 3, which can play a buffering role when an impact occurs, and play a limiting support role for the rubber main spring 3, thereby increasing the service life of the rubber main spring 3.

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

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

[0059] In one embodiment, referring to Figure 2 and Figure 3 The rubber main spring 3 at the position of the main hydraulic chamber 7 fits with the limit block 152, so that a buffer protrusion 17 and a second groove 18 corresponding to the limit protrusion 153 and the first groove 16 are formed on the rubber main spring 3, and a floating point 19 is set between two adjacent buffer protrusions 17.

[0060] As an example, the rubber main spring 3 at the position of the main hydraulic chamber 7 is fitted with the limit block 152, so that a buffer protrusion 17 and a second groove 18 corresponding to the limit protrusion 153 and the first groove 16 are formed on the rubber main spring 3, and a floating point 19 is arranged between two adjacent buffer protrusions 17. The buffer protrusion 17 can also be formed in a six-petal type. The six-petal 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, which can effectively reduce the probability of abnormal noise and play a role in bidirectional buffering and eliminating abnormal noise.

[0061] In one embodiment, referring 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 accumulator hydraulic chamber 6 is smaller than that of the main hydraulic chamber 7. When one main hydraulic chamber 7 is impacted by the load PA, part of the liquid is squeezed into the other main hydraulic chamber 7, and the other part is squeezed into the accumulator hydraulic chamber 6 for storage. The flow resistance squeezed into the other main hydraulic chamber 7 produces a larger damping lag angle and reaches a peak value near a lower frequency (about 15-20°). The liquid squeezed into the accumulator hydraulic chamber 6 rubs against the magnetic particle layer 20 in the accumulator hydraulic chamber 6, and the viscosity of the liquid changes instantly in a limited volume. When it is excited by the high frequency or small amplitude of PC again, the liquid in the accumulator hydraulic chamber 6 is squeezed out and flows into the two main hydraulic chambers 7 at the same time, and the damping lag angle peak value (about 80-100°) is generated again.

[0063] In one embodiment, referring to Figure 2 and Figure 3 The outer side surface of the inner tube 1 is a corrugated structure.

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

[0065] An embodiment of the present invention provides an automobile, including a hydraulic bushing.

[0066] As an example, the inner tube 1 and the outer tube 2 are concentrically mounted to form a containing space, and the rubber main spring 3 is filled in the containing 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, 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 reduced diameter riveted mouth is pressed to ensure the sealing, which mainly bears the torsional force when the swing arm jumps up and down and the lateral force when it impacts forward and backward.

[0067] In this example, three depressions 5 are arranged on the rubber main spring 3 along the circumferential direction, the flow channel plate 4 is sleeved on the outer side of the rubber main spring 3, and the inner side of the flow channel plate 4 cooperates with the three depressions 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. Liquid is encapsulated in the energy storage hydraulic chamber 6 and the main hydraulic chamber 7. The liquid is a mixture of water and ethylene glycol in proportion and can flow in the energy storage hydraulic chamber 6 and the main hydraulic chamber 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 two main liquid The pressure chamber 7 is connected with 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 is deformed, and the volumes of the two main hydraulic chambers 7 change, resulting in changes in the pressures in the two main hydraulic chambers 7. The liquids in the two main hydraulic chambers 7 are pressurized to flow exchange through the second fluid channel 9, and the two main hydraulic chambers 7 are respectively exchanged with the energy storage hydraulic chamber 6 through the first fluid channel 8. The friction loss, inertia loss and local loss generated in the 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, the energy storage hydraulic chamber 6 and the two main hydraulic chambers 7 are connected in parallel through the first fluid channel 8, the two main hydraulic chambers 7 are interconnected at low frequency and large amplitude, and the energy storage hydraulic chamber 6 and the two main hydraulic chambers 7 are interconnected at high frequency and small amplitude; through the flow principle of the series connection of the two main hydraulic chambers 7 and the parallel connection of one energy storage hydraulic chamber 6, the volume and viscosity of the liquid are changed, and the damping reaches double peaks in the low frequency and high frequency bands, thereby achieving performance enhancement and maintaining large damping characteristics in a wider frequency range, having better seismic isolation performance, improving comfort and reducing road noise.

[0069] The damping and stiffness adjustment of existing hydraulic bushings are limited, and impact noise is prone to occur. For example, when hydraulic bushings are used in automobiles, the damping of hydraulic bushings can only be adjusted when low-frequency and large-amplitude excitation (frequency range between 15Hz and 20Hz) is applied, and the stiffness can only be adjusted by the hardness of the rubber material itself, which is not conducive to shock absorption and noise reduction. The hydraulic bushing in this embodiment is connected in series through two main hydraulic chambers 7, and the energy storage hydraulic chamber 6 is connected in parallel with the two main hydraulic chambers 7 (such as Figure 7 Multi-channel performance prediction) can realize the backward shift of the dynamic characteristic curve, that is, the frequency of the peak value is shifted backward, which is conducive to obtaining greater damping and lower dynamic stiffness in the required frequency range (such as the second-order frequency of the engine 25-30Hz). At the same time, through the magnetorheological volume effect of the energy storage hydraulic chamber 6, the pressure and viscosity of the liquid are changed, and the peak value is reached again in the high frequency range (such as the subframe resonance frequency 40-70Hz). The entire action process realizes adjustable and movable damping, and can reach the peak value multiple times, achieving more complex performance optimization goals (such as Figure 8Series-parallel performance prediction, double peak values ​​of damping and dynamic stiffness characteristics, where A and B represent two main hydraulic chambers 7, and C represents the energy storage hydraulic chamber 6), is conducive to comfort adjustment under complex working conditions, and the performance is scalable (the viscosity of the liquid flow can be further adjusted by adding electrodes), which is convenient for adjusting the damping and stiffness of the hydraulic bushing to avoid impact and abnormal noise.

[0070] The complete hydraulic bushing structure can be directly pressed onto the swing arm body and connected between the wheel and the subframe to realize the guiding and force transmission functions of the swing arm. The large damping characteristics obtained can reach the maximum peak value in both low-frequency and high-frequency bands, which is conducive to comfort adjustment in complex working conditions and the performance is scalable.

[0071] The above are only 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 in 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 sleeved to form an accommodation space, and the rubber main spring is filled in the accommodation space, characterized in that: The hydraulic bushing also includes a flow channel plate; The rubber main spring is provided with three depressions along the circumferential direction; The flow channel plate is sleeved on the outside of the rubber main spring, and the inner side of the flow channel plate cooperates 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 to form a first fluid channel and a second fluid channel; The two main hydraulic chambers are respectively communicated with the energy storage hydraulic chamber through the first fluid channel, and the two main hydraulic chambers are communicated through the second fluid channel.

2. The hydraulic bushing according to claim 1, characterized in that: The first fluid channel is a straight-line channel, and the second fluid channel is an annular channel. The second fluid channel 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 which are arranged along a circumference and are 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 form a first fluid channel and a second fluid channel respectively; A first through hole is provided in the middle of the first fluid channel, the first through hole is connected to the energy storage hydraulic chamber, and a second through hole is provided at both ends of the first fluid channel, the second through hole is connected to the main hydraulic chamber; The second fluid channel is provided with two third through holes which are arranged opposite to each other, and one of the third through holes is communicated with one of the main hydraulic chambers.

4. The hydraulic bushing according to claim 3, characterized in that: The flow channel plate includes two semicircular plates that are symmetrical to each other; Each of the semicircular plates is provided with an arc-shaped channel and a C-shaped channel along the circumference, and the C-shaped channel is provided 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 arranged at the junction of the two arc-shaped channels, the second through hole is arranged on an end of the arc-shaped channel away from the first through hole, and the third through hole is arranged 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 in the rubber main spring. The main spring skeleton is provided with three hollows corresponding to the three depressions.

7. The hydraulic bushing according to claim 1, characterized in that: The hydraulic bushing further comprises a limiting coating layer, and the limiting coating layer is arranged between the inner tube and the rubber main spring; The limiting coating layer comprises a coating body and a limiting block extending outward from the middle of the coating body along the radial direction of the inner tube. The coating body cooperates with the limiting block to form a limiting support body.

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

9. The hydraulic bushing according to claim 8, characterized in that: The rubber main spring at the position of the main hydraulic chamber fits with the limit block, so that a buffer protrusion and a second groove matching the limit protrusion and the first groove are formed on the rubber main spring, and a floating point is arranged between two adjacent buffer protrusions.

10. The hydraulic bushing according to claim 1, characterized in that: A magnetic particle layer is arranged 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 side surface of the inner tube is a corrugated structure.

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

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