Hydraulic bushing and automobile

Abstract

The application provides a hydraulic bushing and a car, and the hydraulic bushing comprises a flow channel plate, two hollow cavities and a flow channel groove connecting the two hollow cavities are arranged on a rubber main spring, a flow channel plate is arranged in each hollow cavity, the inner side of each flow channel plate cooperates with a hollow cavity to form a liquid chamber, the outer side of the rubber main spring and the outer side of the flow channel plate abut against the inner wall of an outer tube, the flow channel plate and the flow channel groove are matched to form an inertia channel connecting the two liquid chambers, and a dynamic adjusting assembly is arranged in the inertia channel. In the application, low-frequency large-damping performance is provided through a non-decoupling channel, low-dynamic stiffness performance is provided by changing the liquid flow direction and flow through a decoupling channel, the use of the dynamic adjusting assembly is controlled, the internal and external pressures of the liquid chamber reach dynamic balance, the stiffness of the hydraulic bushing is decoupled, the required low-frequency and high-frequency performances are obtained, and vibration and noise reduction are facilitated.

Description

TECHNICAL FIELD

[0001] The present application belongs to the technical field of hydraulic bushing structure, and particularly relates to a hydraulic bushing and a vehicle. BACKGROUND

[0002] The traditional rubber bushing has limited damping, which is determined by the rubber material and generally does not exceed 10°, and often cannot quickly attenuate the vehicle body vibration caused by the rapid acceleration or deceleration of the bumpy road, and the use range is more and more limited. The damping hysteresis angle of the hydraulic bushing is much larger than that of the rubber bushing, and can provide large damping characteristics under low-frequency excitation, but the first-generation product with fixed structure is currently applied in the market, and the damping and stiffness adjustment modes are relatively limited. The damping is adjustable only at low frequency and large amplitude, and the stiffness can only be adjusted by the hardness of the rubber itself. In the case of low frequency and large amplitude, large damping can be provided to meet the performance design requirements near a certain frequency, but the vibration isolation performance at high frequency cannot be improved. In addition, the adjustable range of the damping is narrow, and when the steering wheel vibration and brake vibration frequency overlap with the suspension swing vibration frequency, the road noise of the whole vehicle will be large, and the requirements for the whole vehicle NVH need to consider the vibration isolation performance requirements of the low frequency band and the high frequency band. SUMMARY

[0003] The present application provides a hydraulic bushing and a vehicle to solve the problem that the damping and stiffness adjustment modes of the existing hydraulic bushing are limited, which is not conducive to vibration reduction and noise reduction.

[0004] A hydraulic bushing, comprising an inner tube, an outer tube and a rubber main spring, the inner tube and the outer tube are concentrically sleeved to form a containing space, the rubber main spring is filled in the containing space, and the hydraulic bushing further comprises a flow channel plate.

[0005] Two hollow cavities and a flow channel groove communicating the two hollow cavities are arranged on the rubber main spring.

[0006] One flow channel plate is installed in each hollow cavity, and the inner side of each flow channel plate cooperates with the hollow cavity to form a liquid chamber.

[0007] The outer side of the rubber main spring and the outer side of the flow channel plate abut against the inner wall of the outer tube, the flow channel plate and the flow channel groove are matched to form an inertia channel communicating the two liquid chambers.

[0008] A dynamic adjustment assembly is arranged in the inertia channel; when the hydraulic bushing is subjected to low-frequency large-amplitude excitation, the dynamic adjustment assembly is in a static state, and the inertia channel is a non-decoupling channel; when the hydraulic bushing is subjected to high-frequency small-amplitude excitation, the dynamic adjustment assembly is in a motion state, and the inertia channel is a decoupling channel.

[0009] Preferably, the inertia passage comprises a first circulation passage and a second circulation passage arranged circumferentially along the hydraulic bushing;

[0010] The flow channel plate is provided with through holes and stepped holes in the radial direction of the hydraulic bushing;

[0011] The through holes are arranged in the first circulation passage for connecting the liquid chamber and the first circulation passage;

[0012] The stepped holes are arranged in the second circulation passage for connecting the liquid chamber and the second circulation passage; the dynamic adjustment assembly is arranged in the stepped holes.

[0013] Preferably, the flow channel groove comprises three arc-shaped grooves arranged circumferentially along the hydraulic bushing and parallel to each other;

[0014] The first circulation passage comprises two C-shaped passages arranged circumferentially along the hydraulic bushing on the flow channel plate and two of the three arc-shaped grooves, the openings of the two C-shaped passages correspond to each other and are connected through the two arc-shaped grooves;

[0015] The through holes are arranged at the bends of the C-shaped passages;

[0016] The second circulation passage comprises two arc-shaped passages arranged circumferentially along the hydraulic bushing on the flow channel plate and one of the three arc-shaped grooves, the two arc-shaped passages correspond to each other and are connected through the one arc-shaped groove;

[0017] The stepped holes are arranged in the arc-shaped passages;

[0018] The arc-shaped passages are arranged in the middle of the C-shaped passages, and the first circulation passage surrounds the second circulation passage.

[0019] Preferably, the stepped holes comprise a first mounting hole, a second mounting hole and a third mounting hole arranged from outside to inside in the radial direction of the hydraulic bushing, the diameter of the first mounting hole is smaller than that of the second mounting hole, and the diameter of the second mounting hole is smaller than that of the third mounting hole;

[0020] The dynamic adjustment assembly comprises a flow guide valve and a floating diaphragm;

[0021] The flow guide valve is mounted in the third mounting hole, the floating diaphragm is movably mounted in the second mounting hole, and the floating diaphragm can reciprocate in the radial direction of the hydraulic bushing; when the hydraulic bushing is subjected to low-frequency large-amplitude excitation, the floating diaphragm is in a static state, and when the hydraulic bushing is subjected to high-frequency small-amplitude excitation, the floating diaphragm is in a dynamic state.

[0022] Preferably, the floating diaphragm is a circular flat structure, and a recess is arranged at the middle of the two ends of the floating diaphragm.

[0023] The thickness of the floating diaphragm is 1-3 mm.

[0024] Preferably, the flow guide valve is provided with a flow hole.

[0025] Preferably, the hydraulic bushing further comprises a limiting coating layer, which is arranged between the inner tube and the rubber main spring.

[0026] The limiting coating layer comprises a coating body and a limiting protrusion extending outward from the middle of the coating body along the radial direction of the inner tube, and the coating body and the limiting protrusion cooperate to form a limiting support body.

[0027] Preferably, the rubber main spring comprises a main body and a sealing protrusion extending from the edges of the two ends of the main body, and the two hollow cavities and the flow channel groove are arranged on the main body.

[0028] The hydraulic bushing further comprises a main spring skeleton, which is arranged outside the main body and outside the sealing protrusion.

[0029] Preferably, the inner side of the inner tube is provided with a groove, and the groove points to the liquid chamber.

[0030] The outer side of the inner tube is provided with a wave-shaped structure.

[0031] The automobile comprises the hydraulic bushing.

[0032] In the present application, the inner tube and the outer tube are concentrically sleeved to form a containing space, 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. The inner tube is a cylindrical steel tube, the outer tube is a thin-walled steel tube, the rubber main spring is vulcanized between the inner tube and the outer tube, the outer tube is in interference fit with the rubber main spring, and the outer tube is shrunk and riveted to ensure the sealing property.

[0033] In the example, the rubber main spring is provided with two hollow cavities and a flow channel slot connecting the two hollow cavities; each hollow cavity is provided with a flow channel plate, and the inner side of each flow channel plate cooperates with a hollow cavity to form a liquid chamber; the outer side of the rubber main spring and the outer side of the flow channel plate abut against the inner wall of the outer tube, and the flow channel plate and the flow channel slot are matched to form an inertia passage connecting the two liquid chambers; the two liquid chambers and the inertia passage are encapsulated with liquid, and the liquid is mixed by water and ethylene glycol in a certain proportion and can flow in the liquid chamber and the inertia passage. When the hydraulic bushing is subjected to external force, the rubber main spring is deformed, the volume of the liquid chamber changes, the pressure in the liquid chamber changes, and the liquid in the liquid chamber flows and exchanges under pressure in the inertia passage. The friction loss, inertia loss and local loss generated in the flow process can effectively attenuate the vibration energy.

[0034] The damping and stiffness adjustment modes of the existing hydraulic bushing are relatively limited. For example, when the hydraulic bushing is used on a vehicle, the damping of the hydraulic bushing can be adjusted only at low frequency and large amplitude excitation (the frequency band is between 15Hz and 20Hz), and the stiffness can only be adjusted by the hardness of the rubber itself, which is not conducive to vibration reduction and noise reduction. The dynamic adjustment assembly is arranged in the inertia passage. At low frequency and large amplitude excitation (the frequency band is between 15Hz and 20Hz), the dynamic adjustment assembly is in a static state, the inertia passage is a non-decoupling passage, and low frequency and large damping performance is provided through the non-decoupling passage. At high frequency and small amplitude excitation (the frequency band is greater than 20Hz), the dynamic adjustment assembly is in a moving state, the inertia passage is a decoupling passage, the stiffness is decoupled, the flow direction and flow rate of the liquid are changed through the decoupling passage, lower dynamic stiffness is obtained, and dynamic balance of pressure is achieved. In the example, the dynamic adjustment assembly is arranged in the inertia passage. According to the excitation received by the hydraulic bushing, the dynamic adjustment assembly is switched to be in a static state or a moving state to switch the large damping performance and high dynamic stiffness performance, so that the pressure inside and outside the liquid chamber reaches dynamic balance, the stiffness of the hydraulic bushing is decoupled, the required damping performance and dynamic stiffness performance are obtained, and vibration reduction and noise reduction are facilitated.

[0035] The hydraulic bushing in the embodiment utilizes the dynamic adjustment assembly arranged in the inertia passage to provide large damping in a wider frequency range, and the damping hysteresis angle delay appears near the resonance frequency band to reach a peak value. The stiffness design of the structure itself can realize large damping in a wider frequency range, and solves the problems of large road noise and high frequency noise during vehicle driving. BRIEF DESCRIPTION OF DRAWINGS

[0036] Figure 1 is the axial side view of the internal structure of the hydraulic bushing in the application;

[0037] Figure 2 is the top view of the hydraulic bushing in the application;

[0038] Figure 3 isFigure 2 A-A cross-sectional view in the middle of

[0039] Figure 4 Figure 2 B-B cross-sectional view in the middle of

[0040] Figure 5 A front view of the flow channel plate in the present application

[0041] Figure 6 Figure 5 C-C cross-sectional view in the middle of

[0042] Figure 7 A shaft side view of the flow guide valve in the present application

[0043] Figure 8 A shaft side view of the floating diaphragm in the present application

[0044] Figure 9 Performance prediction a comparison chart of the hydraulic bushing in the present application

[0045] Figure 10 Performance prediction b comparison chart of the hydraulic bushing in the present application

[0046] Figure 11 Parameter model chart of the hydraulic bushing channel in the present application

[0047] Figure 12 Comparison chart of damping and stiffness performance of the hydraulic bushing before and after decoupling in the present application

[0048] Figure 13 Comparison chart of vibration isolation and road noise performance of the hydraulic bushing before and after decoupling in the present application

[0049] Wherein, 1, inner tube; 11, groove; 12, wave structure; 2, outer tube; 3, rubber main spring; 31, hollow cavity; 32, flow channel groove; 33, main body part; 34, sealing protrusion; 35, main spring framework; 4, flow channel plate; 5, liquid chamber; 6, inertia channel; 61, first circulation channel; 62, second circulation channel; 63, C-shaped channel; 64, arc-shaped channel; 7, dynamic adjustment assembly; 71, flow guide valve; 72, floating diaphragm; 8, through hole; 9, stepped hole; 91, first mounting hole; 92, second mounting hole; 93, third mounting hole; 10, limiting cladding layer; 101, cladding main body; 102, limiting protrusion. DETAILED DESCRIPTION

[0050] In order to make the technical problems solved by the present application, technical solutions and beneficial effects more clear and explicit, the present application will be further described in detail below in combination with the drawings and examples. It should be understood that the specific examples described herein are only used to explain the present application and do not limit the present application. ​​

[0051] In the description of the present application, it is to be understood by those skilled in the art that the orientation or positional relationship indicated by the terms "longitudinal", "radial", "length", "width", "thickness", "upper", "lower", "front", "rear", "left", "right", "vertical", "horizontal", "top", "bottom", "inner", "outer" and the like are based on the orientation or positional relationship shown in the drawings, and are only for the convenience of describing the present application and simplifying the description, and do not indicate or imply that the devices or elements referred to must have a particular orientation, be constructed and operated in a particular orientation, and therefore cannot be understood as a limitation on the present application. In the description of the present application, the meaning of "a plurality of" is two or more, unless otherwise specified.

[0052] In the description of the present application, it is to be understood that, unless otherwise specified and limited, the terms "mounting", "connecting", "connecting" should be understood broadly, for example, it can be fixedly connected, or it can be detachably connected, or integrally connected; it can be mechanically connected, or it can be electrically connected; it can be directly connected, or it can be indirectly connected through an intermediate medium; it can be the communication inside two elements. For those skilled in the art, the specific meaning of the above terms in the present application can be understood according to the specific circumstances.

[0053] The hydraulic bushing provided by the embodiment of the present application comprises 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 sleeved to form a containing space, the rubber main spring 3 is filled in the containing space, and the hydraulic bushing further comprises a flow channel plate 4. Figures 1-5 The rubber main spring 3 is provided with two hollow cavities 31 and a flow channel groove 32 communicating the two hollow cavities 31; one flow channel plate 4 is installed in each hollow cavity 31, and the inner side of each flow channel plate 4 cooperates with one hollow cavity 31 to form one liquid chamber 5; the outer side of the rubber main spring 3 and the outer side of the flow channel plate 4 abut against the inner wall of the outer tube 2, the flow channel plate 4 and the flow channel groove 32 are matched to form an inertia passage 6 communicating the two liquid chambers 5; a dynamic adjusting assembly 7 is arranged in the inertia passage 6; when the hydraulic bushing is subjected to low-frequency large-amplitude excitation, the dynamic adjusting assembly 7 is in a static state, and the inertia passage 6 is a non-decoupling passage; when the hydraulic bushing is subjected to high-frequency small-amplitude excitation, the dynamic adjusting assembly 7 is in a motion state, and the inertia passage 6 is a decoupling passage.

[0054] As an example, the inner tube 1 and the outer tube 2 are concentrically sleeved 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 vulcanized between the inner tube 1 and the outer tube 2, the outer tube 2 is in interference fit with the rubber main spring 3, and the outer tube 2 is shrunk riveting and press-fitted to ensure the sealing property.

[0055] In the present example, with reference to Figure 1 ,Figure 3 and Figure 4 The rubber main spring 3 is provided with two hollow cavities 31 and a flow channel groove 32 connecting the two hollow cavities 31; each hollow cavity 31 is provided with a flow channel plate 4, and the inner side of each flow channel plate 4 cooperates with a hollow cavity 31 to form a liquid chamber 5; the outer side of the rubber main spring 3 and the outer side of the flow channel plate 4 abut against the inner wall of the outer tube 2, and the flow channel plate 4 and the flow channel groove 32 are matched to form an inertia passage 6 connecting the two liquid chambers 5; the two liquid chambers 5 and the inertia passage 6 are filled with liquid, and the liquid is a mixture of water and ethylene glycol in a certain proportion and can flow in the liquid chamber 5 and the inertia passage 6. When the hydraulic bushing is subjected to external force, the rubber main spring 3 deforms, the volume of the liquid chamber 5 changes, the pressure in the liquid chamber 5 changes, and the liquid in the liquid chamber 5 flows and exchanges in the inertia passage 6. The friction loss, inertia loss and local loss generated in the flowing process can effectively attenuate vibration energy.

[0056] The damping and stiffness adjustment modes of the existing hydraulic bushing are relatively limited. For example, when the hydraulic bushing is used on a vehicle, the damping of the hydraulic bushing can be adjusted only at low frequency and large amplitude excitation (the frequency band is between 15 Hz and 20 Hz), and the stiffness can only be adjusted by the hardness of the rubber itself, which is not conducive to vibration and noise reduction. The dynamic adjustment assembly 7 is arranged in the inertia passage 6. At low frequency and large amplitude excitation (the frequency band is between 15 Hz and 20 Hz), the dynamic adjustment assembly 7 is in a static state, the inertia passage 6 is a non-decoupling passage, and low frequency and large damping performance is provided through the non-decoupling passage; at high frequency and small amplitude excitation (the frequency band is greater than 20 Hz), the dynamic adjustment assembly 7 is in a moving state, the inertia passage 6 is a decoupling passage, the stiffness is decoupled, the flow direction and flow rate of the liquid are changed through the decoupling passage, lower dynamic stiffness is obtained, and dynamic balance of pressure is achieved. In the example, the dynamic adjustment assembly 7 is arranged in the inertia passage 6, and the dynamic adjustment assembly 7 is switched to be in a static state or a moving state according to the excitation received by the hydraulic bushing, so as to switch the large damping performance and the high dynamic stiffness performance, to achieve dynamic balance of the pressure in the liquid chamber 5, to realize stiffness decoupling of the hydraulic bushing, to obtain the required damping performance and dynamic stiffness performance, and to be conducive to vibration and noise reduction.

[0057] The hydraulic bushing in the embodiment uses the dynamic adjustment assembly 7 arranged in the inertia passage 6 to provide large damping in a wider frequency range, and makes the damping hysteresis angle delay appear near the resonance frequency band to reach a peak value. The stiffness design of the structure itself can realize large damping in a wider frequency range, and solve the problems of large road noise and high frequency noise of the vehicle.

[0058] In an embodiment, with reference to Figure 1 and Figure 5, the inertia passage 6 comprises a first circulation passage 61 and a second circulation passage 62 arranged along the circumference of the hydraulic bushing; the flow channel plate 4 is provided with a through hole 8 and a stepped hole 9 along the radial direction of the hydraulic bushing, the through hole 8 is arranged in the first circulation passage 61 and used for connecting the liquid chamber 5 and the first circulation passage 61; the stepped hole 9 is arranged in the second circulation passage 62 and used for connecting the liquid chamber 5 and the second circulation passage 62; the dynamic adjustment assembly 7 is arranged in the stepped hole 9.

[0059] As an example, it is introduced that the inertia passage 6 comprises a first circulation passage 61 and a second circulation passage 62 arranged along the circumference of the hydraulic bushing, the through hole 8 is arranged in the first circulation passage 61 and used for connecting the liquid chamber 5 and the first circulation passage 61, under low-frequency large-amplitude excitation (the frequency range is between 15 Hz and 20 Hz), the dynamic adjustment assembly 7 is in a static state, the liquid in the two liquid chambers 5 exchanges fluid through the first circulation passage 61 and the through hole 8, and the inertia passage 6 is a non-decoupling passage; the stepped hole 9 is arranged in the second circulation passage 62 and used for connecting the liquid chamber 5 and the second circulation passage 62, under high-frequency small-amplitude excitation (the frequency range is greater than 20 Hz), the liquid in the two liquid chambers 5 exchanges fluid through the first circulation passage 61 and the through hole 8, which cannot realize the required characteristics of the hydraulic bushing, at this time, the second circulation passage 62 and the stepped hole 9 play a role to realize the flow exchange of the liquid in the two liquid chambers 5. The dynamic adjustment assembly 7 is arranged in the stepped hole 9, when the dynamic adjustment assembly 7 is in a static state, the first circulation passage 61 is the main flow passage of the liquid, and the inertia passage 6 is a non-decoupling passage, when the dynamic adjustment assembly 7 is in a motion state, the second circulation passage 62 is the main flow passage of the liquid, and the inertia passage 6 is a decoupling passage; the first circulation passage 61 and the second circulation passage 62 cooperate to provide low-frequency large-damping performance through the non-decoupling passage, to change the flow direction and flow of the liquid through the decoupling passage to provide low-dynamic stiffness performance, to control the use of the dynamic adjustment assembly 7, to make the internal and external pressures of the liquid chamber 5 reach a dynamic balance, to realize the stiffness decoupling of the hydraulic bushing, to obtain the required low-frequency range and high-frequency range performance, and to be beneficial to vibration and noise reduction.

[0060] In an embodiment, referring to Figure 1 and Figure 5The flow channel groove 32 comprises three arc grooves arranged along the circumference of the hydraulic bushing and parallel to each other; the first circulation channel 61 comprises two C-shaped channels 63 arranged along the circumference of the hydraulic bushing on the two flow channel plates 4 and two arc grooves of the three arc grooves, the two C-shaped channels 63 are opposite to each other and are connected through the two arc grooves; the through hole 8 is arranged at the bend of the C-shaped channel 63; the second circulation channel 62 comprises two arc channels 64 arranged along the circumference of the hydraulic bushing on the two flow channel plates 4 and one arc groove of the three arc grooves, the two arc channels 64 are opposite to each other and are connected through the one arc groove; the stepped hole 9 is arranged in the arc channel 64; the arc channel 64 is arranged in the middle of the C-shaped channel 63, and the first circulation channel 61 surrounds the second circulation channel 62.

[0061] As an example, it is introduced that the first circulation channel 61 comprises two C-shaped channels 63 arranged along the circumference of the hydraulic bushing on the two flow channel plates 4 and two arc grooves of the three arc grooves, the two C-shaped channels 63 are opposite to each other and are connected through the two arc grooves, forming a loop-shaped circulation channel, the C-shaped channel 63 is replaced by a bow-shaped channel, the two bow-shaped channels are opposite to each other and are connected through the two arc grooves, forming a bow-shaped circulation channel, increasing the length of liquid flow and improving the damping characteristics of the equipment; the length of the flow channel is designed according to the space and the damping characteristics, the more the number of flow channel rings is, the longer the length is, and the better the damping characteristics are; the through hole 8 is arranged at the bend of the C-shaped channel 63, which is convenient for the liquid in the two liquid chambers 5 to flow and exchange.

[0062] The second circulation channel 62 comprises two arc channels 64 arranged along the circumference of the hydraulic bushing on the two flow channel plates 4 and one arc groove of the three arc grooves, the two arc channels 64 are opposite to each other and are connected through the one arc groove, forming a complete circular arc channel, the stepped hole 9 is arranged in the arc channel 64, realizing the flow exchange of the liquid in the two liquid chambers 5; the arc channel 64 is arranged in the middle of the C-shaped channel 63, and the first circulation channel 61 surrounds the second circulation channel 62, which can keep the equipment balanced and avoid uneven deformation of the equipment, causing channel blockage.

[0063] In an embodiment, with reference to Figure 3 and Figure 6, the stepped hole 9 comprises a first mounting hole 91, a second mounting hole 92 and a third mounting hole 93 arranged from outside to inside along the radial direction of the hydraulic bushing, the hole diameter of the first mounting hole 91 is smaller than that of the second mounting hole 92, and the hole diameter of the second mounting hole 92 is smaller than that of the third mounting hole 93; the dynamic adjustment assembly 7 comprises a flow guide valve 71 and a floating diaphragm 72; the flow guide valve 71 is mounted in the third mounting hole 93, and the floating diaphragm 72 is movably mounted in the second mounting hole 92 and can reciprocate along the radial direction of the hydraulic bushing, so that the floating diaphragm 72 is in a static state when the hydraulic bushing is subjected to low-frequency large-amplitude excitation, and the floating diaphragm 72 is in a dynamic state when the hydraulic bushing is subjected to high-frequency small-amplitude excitation.

[0064] As an example, the dynamic adjustment assembly 7 comprises the flow guide valve 71 and the floating diaphragm 72, wherein the stepped hole 9 comprises the first mounting hole 91, the second mounting hole 92 and the third mounting hole 93, the stepped hole 9 is a three-step hole, the hole diameters sequentially increase from outside to inside along the radial direction of the hydraulic bushing, and the height interval of each step is about 3 mm; the flow guide valve 71 is mounted in the third mounting hole 93, and the floating diaphragm 72 is movably mounted in the second mounting hole 92 and can reciprocate along the radial direction of the hydraulic bushing; the flow direction of the liquid is changed by the flow guide valve 71 and the floating diaphragm 72 in the stepped hole 9. The opening and closing amount of the stepped hole 9 is dynamically adjusted by the change of the movement gap of the floating diaphragm 72 in the second mounting hole 92, so that the dynamic balance of the pressure in the liquid chamber 5 is achieved, the stiffness decoupling of the hydraulic bushing is realized, the required low-frequency and high-frequency performances are obtained, and vibration and noise reduction are facilitated. In the low-frequency large-amplitude excitation (the frequency band is between 15 Hz and 20 Hz), the floating diaphragm 72 is in a static state, the liquids in the two liquid chambers 5 are exchanged by the first circulation channel 61 and the through hole 8, and the inertia channel 6 is a non-decoupling channel; in the high-frequency small-amplitude excitation (the frequency value is greater than 20 Hz), the floating diaphragm 72 is in a dynamic state, the liquids in the two liquid chambers 5 are exchanged by the first circulation channel 61 and the through hole 8, and the required characteristics of the hydraulic bushing cannot be achieved, at this time, the second circulation channel 62 and the stepped hole 9 play a role to realize the flow exchange of the liquids in the two liquid chambers 5.

[0065] In an embodiment, referring to Figure 6 and Figure 8 , the floating diaphragm 72 is provided in a circular flat structure, recesses are arranged at the middle portions of the two ends of the floating diaphragm 72, and the thickness of the floating diaphragm 72 is 1-3 mm.

[0066] As an example, the floating diaphragm 72 is a circular flat structure, the middle part of both ends of the floating diaphragm 72 is provided with a recess, when the floating diaphragm 72 reciprocates, it is beneficial to liquid flow exchange, the rubber material with hardness of 70° can be used, and the nylon material can also be used, the thickness of the floating diaphragm 72 is 1-3 mm, and the thickness is generally 2 mm, the thickness design can reduce the rigidity of the floating diaphragm 72 itself, and the dynamic rigidity and lag angle when the low-frequency large amplitude vibration are auxiliary adjusted.

[0067] In an embodiment, referring to Figure 6 and Figure 7 , the flow guide valve 71 is provided with a flow hole.

[0068] As an example, the flow guide valve 71 is a circular sheet structure, the flow guide valve 71 is provided with a flow hole, the flow hole can be one, arranged at the center of the circular sheet; the flow hole can also be two, circularly distributed on the circular sheet, the flow hole can also be three or more than three, one of which is arranged at the center of the circular sheet, and the rest are circularly distributed on the circular sheet, the diameter of the flow hole is about 2 mm, which is used for flow guiding and pressure relief, changing the liquid flow direction and flow rate; at the same time, the flow guide valve 71 also has a limiting device to ensure that the floating diaphragm 72 moves horizontally in the second mounting hole 92 without falling out.

[0069] In an embodiment, referring to Figure 3 , the hydraulic bushing further comprises a limiting coating layer 10 arranged between the inner tube 1 and the rubber main spring 3; the limiting coating layer 10 comprises a coating body 101 and a limiting protrusion 102 extending outward from the middle part of the coating body 101 along the radial direction of the inner tube 1, and the coating body 101 cooperates with the limiting protrusion 102 to form a limiting support body.

[0070] As an example, the hydraulic bushing further comprises a limiting coating layer 10 arranged between the inner tube 1 and the rubber main spring 3, the limiting coating layer 10 comprises a coating body 101 and a limiting protrusion 102 extending outward from the middle part of the coating body 101 along the radial direction of the inner tube 1; wherein the limiting coating layer 10 is a hard nylon or resin layer wrapped outside the inner tube 1, and the middle drum-shaped limiting protrusion 102 serves as a limiting support body of the rubber main spring 3. When impact occurs, it can buffer and prevent collision, limit and support the rubber main spring 3, and improve the service life of the rubber.

[0071] In an embodiment, referring to Figure 1 , Figure 2 and Figure 3 , the rubber main spring 3 comprises a main body part 33 and a sealing protrusion 34 extending from the edges of both ends of the main body part 33, and two hollow cavities 31 and flow channel grooves 32 are arranged on the main body part 33; the hydraulic bushing further comprises a main spring skeleton 35 arranged outside the main body part 33 and outside the sealing protrusion 34.

[0072] As an example, the rubber main spring 3 includes a main body part 33 and a sealing protrusion 34; the rubber main spring 3 is of a solid structure, is vulcanization-formed, and mainly bears torsional force when the swing arm jumps up and down and lateral force when the swing arm is impacted front and back. The sealing protrusion 34 extending from the edges of the two ends of the main body part 33 mainly plays a sealing role after the outer tube 2 is assembled. The hydraulic bushing further includes a main spring skeleton 35 arranged outside the main body part 33 and outside the sealing protrusion 34, which mainly plays a supporting and shaping role so that the rubber main spring 3 can have greater radial rigidity in the solid direction to resist deformation and improve the service life.

[0073] In an embodiment, referring to Figure 2 , the inner side of the inner tube 1 is provided with a groove 11 pointing to the liquid chamber 5; and the outer side of the inner tube 1 is provided with a wave-shaped structure 12.

[0074] As an example, the inner side of the inner tube 1 is provided with a groove 11 pointing to the liquid chamber 5, which is used as a manufacturing mark direction, and the purpose is to design a boss or an arrow mark originally formed on the rubber main spring 3 on the inner tube 1, which can avoid stress concentration of the mark body and improve the service life of the rubber main spring 3 according to past real vehicle tests. The outer side of the inner tube 1 is provided with a wave-shaped structure 12, which can increase the contact area with the limiting coating layer 10 and improve the adhesion.

[0075] The embodiment of the present application provides a vehicle.

[0076] As an example, the complete hydraulic bushing can be directly press-fitted on the swing arm body, connected between the wheel and the auxiliary frame to realize the guiding and force transmission functions of the swing arm, the obtained low-frequency large-damping characteristics can solve the problems of steering wheel vibration and brake judder, and the decoupled high-frequency low-dynamic stiffness characteristics can improve the vibration isolation and road noise influence. The dynamic adjusting assembly 7 is arranged in the inertia channel 6, in a low-frequency large-amplitude excitation (the frequency band is between 15 Hz and 20 Hz), the dynamic adjusting assembly 7 is in a static state, the inertia channel 6 is a non-decoupled channel, and the low-frequency large-damping performance is provided through the non-decoupled channel; in a high-frequency small-amplitude excitation (a frequency band with a frequency value greater than 20 Hz), the dynamic adjusting assembly 7 is in a motion state, the inertia channel 6 is a decoupled channel, the stiffness decoupling is realized, the liquid flow direction and flow are changed through the decoupled channel, lower dynamic stiffness is obtained, and dynamic balance of pressure is achieved. In the example, the dynamic adjusting assembly 7 is arranged in the inertia channel 6, the dynamic adjusting assembly 7 can be switched to be in a static state or a motion state according to the excitation received by the hydraulic bushing, so as to realize switching of the large-damping performance and the high-dynamic stiffness performance, the inner and outer pressures of the liquid chamber 5 reach dynamic balance, the stiffness decoupling of the hydraulic bushing is realized, the required damping performance and dynamic stiffness performance are obtained, and this is beneficial to vibration reduction and noise reduction.

[0077] The hydraulic bushing in the application is provided with a dynamic adjustment assembly 7. The liquid flow mechanism in the liquid chamber 5 is controlled through the dynamic adjustment assembly 7, the stiffness decoupling is realized, the damping and stiffness are dynamically adjusted through the pressure adjustment, and the target requirement of performance optimization is achieved (refer to Figure 9 Performance prediction a); the through hole 8 is used for the liquid to enter the first circulation channel 61 in the non-decoupling mode, and the through hole stepped hole 9 is used for the liquid to enter the second circulation channel 62 in the decoupling mode. The mutual transformation of the first circulation channel 61 and the second circulation channel 62 and the change of the liquid flow direction make the dynamic stiffness-frequency curve and the hysteresis angle-frequency curve have unchanged characteristic points under different amplitude excitations, that is, the performance of the key frequency points is less affected by the amplitude change (for example Figure 10 Performance prediction b). In the low frequency band, due to the large pressure difference, the floating diaphragm 72 is lifted or flattened to the limit position, the stiffness is large, the liquid can only flow through the first circulation channel 61 and the through hole 8 on the flow channel plate 4, and large damping is provided; in the high frequency band, the flow amount of the liquid between the two liquid chambers 5 through the first circulation channel 61 and the through hole 8 is small or almost no flow, the channel tends to be self-locked, and large damping cannot be obtained to attenuate vibration, at this time, the flow guide valve 71 and the floating diaphragm 72 provided in the stepped hole 9 on the second circulation channel 62 play a role. The floating diaphragm 72 is floating and can move in the axial direction of the second mounting hole 92. The liquid flows through the outer edge of the floating diaphragm 72 to change the flow direction. Because the stiffness of the floating diaphragm 72 is small, the flowing liquid can pass through the deformation of the floating diaphragm 72 to achieve dynamic balance of the pressure, and stiffness decoupling is realized (refer to Figure 11 Hydraulic bushing channel parameter model), under high frequency small amplitude excitation, large damping and low dynamic stiffness can also be provided, and the problem of large road noise of the automobile at high frequency is solved, and the cost change of the traditional hydraulic bushing is not large.

[0078] Refer to Figure 12 Decoupling before and after the damping and stiffness performance comparison chart, the resonance frequency band of the automobile unsprung mass is between 15Hz and 20Hz, the first circulation channel 61 and the through hole 8 on the structure realize large damping, and the damping hysteresis angle delay appears near the resonance frequency band to reach the peak value, the stiffness design of the structure itself can realize large damping and wider frequency range. When high frequency small amplitude excitation occurs, the floating diaphragm 72 plays a role, and stiffness decoupling is realized. The first circulation channel 61 in the circumferential direction tends to be self-locked, the floating diaphragm 72 can move in the axial direction of the second mounting hole 92, the flow direction and flow of the liquid are changed through the change of the opening and closing amount and the flow guide valve 71, lower dynamic stiffness is obtained, and dynamic balance of the pressure is achieved. For the fixed structure of the hydraulic bushing, most manufacturers adjust the rubber hardness to realize the stiffness performance, but the decoupling structure can realize performance optimization through pressure adjustment.

[0079] The application changes the liquid flow mechanism in the liquid chamber 5 through the dynamic adjusting component 7, realizes the characteristics of low frequency large damping and high frequency low dynamic stiffness, provides low frequency performance through the non-decoupling inertia channel 6, and changes the liquid flow through the floating diaphragm 72 to decouple the high frequency performance. Figure 13 The simulation comparison of the decoupling structure can reduce the vibration isolation rate by 50%, reduce the noise by 5dB-8dB, and improve the vehicle comfort index by 30%.

[0080] The above is only a preferred embodiment of the application and is not used to limit the application. Any modification, equivalent replacement, improvement, etc. made within the spirit and principle of the application shall be included in the protection scope of the application.

Claims

1. A hydraulic bushing comprising an inner tube, an outer tube, and a rubber main spring, the inner tube being concentrically fitted with the outer tube to form an accommodation space, the rubber main spring being filled in the accommodation space, characterized in that, The hydraulic bushing further comprises a flow channel plate; The rubber main spring is provided with two hollow cavities and a flow channel groove communicating the two hollow cavities; Each hollow cavity is provided with a flow channel plate, and the inner side of each flow channel plate cooperates with a hollow cavity to form a liquid chamber; The outer side of the rubber main spring and the outer side of the flow channel plate abut against the inner wall of the outer tube, and the flow channel plate and the flow channel groove are matched to form an inertia channel communicating the two liquid chambers, the inertia channel comprising a first circulation channel and a second circulation channel arranged along the circumference of the hydraulic bushing; The flow channel plate is provided with a through hole and a stepped hole along the radial direction of the hydraulic bushing; the through hole is arranged in the first circulation channel and is used for communicating the liquid chamber and the first circulation channel; the stepped hole is arranged in the second circulation channel and is used for communicating the liquid chamber and the second circulation channel; The inertia channel is provided with a dynamic adjustment assembly, and the dynamic adjustment assembly is arranged in the stepped hole; when the hydraulic bushing is subjected to low-frequency large-amplitude excitation, the dynamic adjustment assembly is in a static state, and the inertia channel is a non-decoupling channel; when the hydraulic bushing is subjected to high-frequency small-amplitude excitation, the dynamic adjustment assembly is in a dynamic state, and the inertia channel is a decoupling channel.

2. The hydraulic bushing of claim 1, wherein, The flow channel groove comprises three arc-shaped grooves arranged along the circumference of the hydraulic bushing and parallel to each other; The first circulation channel comprises two C-shaped channels arranged along the circumference of the hydraulic bushing on the flow channel plates and two of the three arc-shaped grooves, and the openings of the two C-shaped channels correspond to each other and are communicated through the two arc-shaped grooves; The through hole is arranged at the bend of the C-shaped channel; The second circulation channel comprises two arc-shaped channels arranged along the circumference of the hydraulic bushing on the flow channel plates and one of the three arc-shaped grooves, and the two arc-shaped channels correspond to each other and are communicated through the one arc-shaped groove; The stepped hole is arranged in the arc-shaped channel; The arc-shaped channel is arranged in the middle of the C-shaped channel, and the first circulation channel surrounds the second circulation channel.

3. The hydraulic bushing of claim 1, wherein, The stepped hole comprises a first mounting hole, a second mounting hole and a third mounting hole arranged from outside to inside along the radial direction of the hydraulic bushing, the diameter of the first mounting hole is smaller than that of the second mounting hole, and the diameter of the second mounting hole is smaller than that of the third mounting hole; The dynamic adjustment assembly comprises a flow guide valve and a floating diaphragm; The flow guide valve is mounted in the third mounting hole, the floating diaphragm is movably mounted in the second mounting hole, and the floating diaphragm can reciprocate along the radial direction of the hydraulic bushing; when the hydraulic bushing is subjected to low-frequency large-amplitude excitation, the floating diaphragm is in a static state, and when the hydraulic bushing is subjected to high-frequency small-amplitude excitation, the floating diaphragm is in a dynamic state.

4. The hydraulic bushing of claim 3, wherein, The middle part of the floating diaphragm at both ends is recessed, and the thickness of the floating diaphragm is 1-3 mm.

5. The hydraulic bushing of claim 3, wherein, The flow guide valve is provided with a flow discharge hole.

6. The hydraulic bushing of claim 1, wherein, The hydraulic bushing further comprises a limiting coating layer arranged between the inner tube and the rubber main spring; The limiting coating layer comprises a coating main body and a limiting protrusion extending outward from the middle of the coating main body along the radial direction of the inner tube, and the coating main body cooperates with the limiting protrusion to form a limiting support body.

7. The hydraulic bushing of claim 1, wherein, The rubber main spring comprises a main body part and a sealing protrusion extending from the edges of both ends of the main body part, and two hollow cavities and a flow channel groove are arranged on the main body part. The hydraulic bushing further comprises a main spring skeleton arranged on the outer side of the main body part and the outer side of the sealing protrusion.

8. The hydraulic bushing of claim 1, wherein, The inner side of the inner tube is provided with a groove, and the groove points to the liquid chamber. The outer side of the inner tube is provided with a wave structure.

9. An automobile characterized by comprising: The hydraulic bushing comprises the hydraulic bushing according to any one of claims 1-8.

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