CN108150591B

CN108150591B - Sealing assembly for hydraulic bushing and hydraulic bushing

Info

Publication number: CN108150591B
Application number: CN201611166402.4A
Authority: CN
Inventors: 罗旦; 邹波; 丁行武; 卜继玲; 张亚新; 刘建勋; 乔·格罗斯; 王涛
Original assignee: Zhuzhou Times New Material Technology Co Ltd
Current assignee: Zhuzhou Times New Material Technology Co Ltd
Priority date: 2016-12-02
Filing date: 2016-12-16
Publication date: 2020-07-14
Anticipated expiration: 2036-12-16
Also published as: CN108150593B; CN108150597B; CN108150596A; CN108150594A; CN108150592B; CN108150598B; CN108150536B; CN108150588A; CN108150536A; CN206361076U; CN108150597A; CN108150598A; CN108150595B; CN108150535A; CN108150590A; CN108150589B; CN108150587A; CN108150585A; CN108150591A; CN108150589A

Abstract

The invention relates to a sealing assembly for a hydraulic bushing and the hydraulic bushing, wherein the sealing assembly comprises a rigid supporting ring assembly and a second rubber body, the supporting ring assembly is provided with an assembling ring and a convex ring which protrudes outwards from the outer wall of the assembling ring in the radial direction, the second rubber body covers the convex ring and is sleeved on the outer side of the assembling ring, and the sealing assembly can improve the axial rigidity of the hydraulic bushing so as to achieve the purpose of adjusting the axial rigidity of the hydraulic bushing by changing the radial rigidity of the sealing assembly.

Description

Sealing assembly for hydraulic bushing and hydraulic bushing

Cross Reference to Related Applications

The present application claims priority to chinese patent application CN201611096400.2 entitled "a hydraulic bushing" filed on year 2016, month 12, 02 and chinese patent application CN201611095592.5 entitled "hydraulic bushing and rail train" filed on year 2016, month 12, 02, which are incorporated herein by reference in their entirety.

Technical Field

The invention relates to the technical field of rail trains, in particular to a sealing assembly for a hydraulic bushing and the hydraulic bushing.

Background

The operation of a rail train can be simply divided into two states, the first being a straight-ahead state and the second being a curve-driving state. In the prior art, wheels are usually connected to a bogie by means of rubber tumblers, so that in a straight-ahead state, the train runs quickly and stably along rails; in the curve running state, the train can smoothly turn along the track.

In order to allow a stable operation of the train in a straight running state, the rubber rotor is generally constructed to have a large stiffness value. However, such rubber tumblers having a large rigidity cause severe wear of wheels and rails in a curve driving state, thereby increasing the operating cost of the train.

Disclosure of Invention

In view of some or all of the above problems, the present invention provides a seal assembly for a hydraulic bushing and a hydraulic bushing. After the sealing assembly is applied to the hydraulic bushing, the axial rigidity of the hydraulic bushing can be greatly improved, so that the purpose of adjusting the axial rigidity of the hydraulic bushing by changing the radial rigidity of the sealing assembly is achieved.

According to an aspect of the present invention, there is provided a seal assembly for a hydraulic bushing, comprising:

a rigid support ring assembly having a mounting ring and a raised ring projecting radially outward from an outer wall of the mounting ring,

the second rubber body is sleeved outside the assembling ring by the coating convex ring. In the application process, the sealing assemblies are arranged at two ends of the mandrel of the hydraulic bushing, so that the axial rigidity of the hydraulic bushing is improved, and meanwhile, the rigidity adjusting capacity of the hydraulic bushing is improved, and the wider use requirements are met.

In one embodiment, the radial thickness of the first end of the mounting ring is greater than the radial thickness of the second end. In the use process of the sealing assembly, the rigidity of the assembling ring can be ensured through the arrangement, and the assembling ring can be prevented from interfering with the movement of the outer sleeve.

In one embodiment, the second rubber body has first rubber peak portions and third rubber peak portions arranged at intervals and protruding outwards in the radial direction from the first end to the second end, and a first yielding space is formed between the first rubber peak portions and the third rubber peak portions. After sealing assembly sets up on the dabber of hydraulic pressure bush, the first space of stepping down can help reducing the motion resistance that the overcoat received for the overcoat moves more easily in certain range for the dabber, thereby has improved the flexible ability of bending of rail train.

In one embodiment, the second rubber body has a second rubber crest disposed between the first rubber crest and the third rubber crest, the second rubber crest being located opposite the torus and projecting radially into the first yield space. The second rubber peak can prevent the problem that the movement amplitude of the outer sleeve relative to the mandrel is too large.

In one embodiment, a second relief space is provided on an outer end face of the second end of the second rubber body, the second relief space being configured as an annular groove. The flexible over-bending capability of the rail train is increased by arranging the second abdicating space.

In one embodiment, a rigid first grommet coaxial with the mounting ring is disposed over the first rubber peak. Through setting up first backing ring, when increasing seal assembly's rigidity, can improve sealed effect.

In one embodiment, a first projection projecting radially outward is provided on the first rubber peak at a position corresponding to the first grommet. The sealing effect is further improved by this arrangement.

In one embodiment, a rigid second grommet coaxial with the mounting ring is embedded within the third rubber peak. Through setting up the second backing ring, when increasing seal assembly's rigidity, can improve sealed effect more.

In one embodiment, a second projection projecting radially outward is provided on the third rubber peak at a position corresponding to the second grommet. The sealing effect is further improved by this arrangement.

According to another aspect of the present invention, there is provided a hydraulic bushing comprising:

a mandrel having a first step surface to configure the mandrel as a stepped shaft having a middle section diameter greater than two end sections diameter,

a first rubber body sleeved on the outer wall of the middle section of the mandrel, two axially-through liquid cavities distributed at intervals are arranged on the first rubber body,

a sleeve sleeved on the outer wall of the first rubber body, a groove arranged on the outer wall of the sleeve,

in the sealing component, the assembling rings of the sealing component are sleeved at the two end parts of the mandrel,

the outer sleeve is sleeved on the outer sides of the sleeve and the sealing assembly, and a flow channel for communicating the two liquid cavities is formed in the groove of the outer sleeve and the sleeve. The hydraulic bushing enables the train to have higher flexibility during the running process of a curve, and meanwhile, the train can stably run in the straight running process.

Compared with the prior art, the invention has the advantages that: the sealing assembly with the structure has higher axial rigidity and lower radial rigidity, so that the sealing assembly can be applied to the hydraulic bushing to increase the axial rigidity of the hydraulic bushing and realize that the rigidity of the hydraulic bushing is adjusted by changing the rigidity of the sealing assembly.

Drawings

The invention will be described in more detail hereinafter on the basis of embodiments and with reference to the accompanying drawings. Wherein:

FIG. 1 schematically illustrates a perspective view of a hydraulic bushing according to one embodiment of the present invention;

FIG. 2 is a cross-sectional view A-A from FIG. 1;

FIG. 3 is a cross-sectional view B-B from FIG. 1;

FIG. 4 is a cross-sectional view C-C from FIG. 1;

FIG. 5 shows a perspective view of the main spring;

FIG. 6 shows a left side view of the main spring;

FIG. 7 shows a cross-sectional view of another embodiment of the main spring;

FIG. 8 shows a front view of the sleeve;

FIG. 9 shows a right side view of the sleeve;

FIG. 10 shows a cross-sectional view of the jacket without flanging;

FIG. 11 shows a perspective view of the seal assembly;

FIG. 12 is a cross-sectional view D-D from FIG. 11;

FIG. 13 is a cross-sectional view E-E from FIG. 11;

FIG. 14 shows a perspective view of a support ring assembly;

FIG. 15 is an enlarged view at F from FIG. 12;

FIG. 16 shows a perspective view of a first mating body;

in the drawings, like parts are provided with like reference numerals. The drawings are not to scale.

Detailed Description

The invention will be further explained with reference to the drawings.

As shown in fig. 1, the hydraulic bushing 1 includes a main spring 100 and a cylindrical housing 200. As shown in fig. 2 and 3, the main spring 100 has a core shaft 101, a first rubber body 102, and a sleeve 103. The first rubber body 102 is sleeved on the outer wall of the mandrel 101. Two liquid chambers 104 are provided in the first rubber body 102, each liquid chamber 104 is a through hole penetrating in the axial direction of the first rubber body 102, and the two liquid chambers 104 are distributed at intervals in the radial direction of the first rubber body 102 in an opposing manner. The sleeve 103 is sleeved on the outer wall of the first rubber body 102. Meanwhile, a groove 110 is provided on the wall of the sleeve 103. Wherein the main spring 100 is arranged in the inner cavity of the outer sleeve 300, such that the outer sleeve 300 and the sleeve 103 form a flow channel 105 at the groove 110 for communicating the two liquid chambers 104.

When the hydraulic bushing 1 is mounted on a railway train, the mandrel 101 of the hydraulic bushing 1 is connected to the frame of the bogie of the railway train, and the outer sleeve 300 is connected to the alignment arm of the wheel, while the two fluid chambers 104 are disposed opposite to each other in the traveling direction of the railway train, that is, one fluid chamber 104 is located in front and the other is located in rear with reference to the running direction of the train. During the turning of the rail train, the wheels turn and drive the positioning arms to move, the outer sleeve 300 is driven to move relative to the mandrel 101, and then the bogie connected with the mandrel 101 turns and the train turns. In the process, one liquid chamber 104 of the hydraulic bushing 1 is made smaller by being pressed, and the other liquid chamber 104 is made larger by being stretched, and the liquid in the liquid chamber 104 made smaller by being pressed can flow into the liquid chamber 104 made larger by being stretched through the flow passage 105 to conform to the relative movement and turning of the mandrel 101 and the outer sleeve 300. Thus, the hydraulic bushing 1 according to the present invention has greater flexibility than a rubber tumbler or the like in the related art during the running of a train on a curve, so that the wheel can be steered more smoothly, thereby reducing the wear of the wheel and the rail. In the rail train straight running state, the pressing force applied to the liquid chamber 104 is small, and the liquid in the liquid chamber 104 and the flow passage 105 hardly flows. This allows the rigidity of the hydraulic bushing 1 to be not significantly changed from that of the rubber tumbler and the like in the prior art, enabling the train to maintain stable operation. Therefore, the hydraulic bushing 1 has good rigidity adjusting capacity and meets the aims of enabling the rail train to be straight more stably and to be bent more flexibly.

In one embodiment, as shown in FIG. 2, the mandrel 101 has a first step surface 107 to configure the mandrel 101 as a stepped shaft with a middle section diameter that is larger than the diameter of the two end sections. The first rubber body 102 is disposed in the middle section of the core shaft 101. In a preferred embodiment, the central section of the mandrel 101 projects radially outward, the contour of the projecting portion being arcuate. That is, the middle section of the mandrel 101 is configured in a drum shape. The first rubber body 102 is sleeved on the middle section. Further, the inner side wall of the first rubber body 102 is connected to the core shaft 101 at the middle section corresponding to the drum shape, and the contour line of the outer side wall of the first rubber body 102 is linear in cross section to be connected to the sleeve 103 in a fitting manner. By means of the arrangement, on one hand, stress concentration at the contact part of the mandrel 101 and the first rubber body 102 is avoided, and the service life of the hydraulic bushing 1 is prolonged. On the other hand, the swing of the mandrel 101 relative to the jacket 200 is increased, and the deflection angle of the mandrel 101 is increased, so that the flexible over-bending capability of the rail train is finally improved.

Since the middle section of the mandrel 101 is configured as a drum-shaped structure, and the first rubber body 102 between the liquid chamber 104 and the mandrel 101 is substantially the same in thickness everywhere except for the axial ends in the axial direction. Thus, the width of the middle of the liquid chamber 104 is smaller than the width of the two ends in the axial direction. Through the arrangement, the problem that the liquid cavity 104 is easy to tear at the two axial ends can be effectively avoided, so that the service life of the hydraulic bushing 1 is prolonged. In addition, this arrangement also increases the response sensitivity of the liquid in the liquid chamber 104, thereby increasing the ability of the hydraulic bushing 1 to assist in the flexible over-bending of the train.

As shown in fig. 4 and 6, the liquid chambers 104 are distributed along the circumferential direction of the first rubber body 102. That is, in radial cross-section, the liquid chamber 104 extends in an arc. In addition, a stopper projection 106 is provided at a radially middle portion of the liquid chamber 104 so that the liquid chamber 104 has a radial dimension larger at both end portions in the circumferential direction than at the middle portion, and preferably, the stopper projection 106 is provided on an inner wall of the liquid chamber 104 on the side close to the mandrel 101. When the mandrel 101 moves relative to the outer sleeve 200, the limiting protrusion 106 may first contact the inner sidewall of the liquid chamber 104 close to the sleeve 103, and thus, the limiting protrusion serves as a stop. Especially in overload, the top end of the limiting bulge 106 is abutted against the inner side wall of the liquid cavity 104 close to the sleeve 103 to prevent the mandrel 101 from excessively deviating relative to the outer sleeve 200, so that the use safety of the hydraulic bushing 1 is ensured. Meanwhile, the radial sizes of the liquid cavity 104 at the two end sections in the circumferential direction are larger, so that a larger yielding space is formed, so that the inner side wall of the liquid cavity 104 close to the mandrel 101 and the inner side wall of the liquid cavity close to the sleeve 103 are not easy to tear, and the service life of the hydraulic bushing 1 is prolonged.

Also, in the radial cross section, the sections of the liquid chamber 104 are smoothly transitioned, and in particular, both circumferential ends of the liquid chamber 104 are configured in the shape of a circular arc. The stress concentration problem of the liquid cavity 104 is effectively improved through the arrangement, so that the service life of the hydraulic bushing 1 is further prolonged.

In one embodiment, the core shaft 101, the first rubber body 102, and the sleeve 103 are fixed together by vulcanization to form the main spring 100, as shown in fig. 5.

According to another embodiment of the present invention, the mandrel 101 may be constructed in a split structure. For example, as shown in fig. 7, the mandrel 101 includes a first portion 108 and a second portion 109. Wherein the first portion 108 is configured as a stepped shaft. The second portion 109 is configured as a cylinder and fits over the outer wall of the first portion 108. Further, for the sake of convenience of processing and a simple structure, both the outer wall surface of the first portion 108 and the inner wall surface of the second portion 109 are configured as cylindrical surfaces. The outer wall surface of the second portion 109 may be configured as a cylindrical surface or an arcuate surface according to different requirements. According to this structure, in the production process of the hydraulic bushing 1, the first portion 108 and the second portion 109 can be produced separately, then only the second portion 109, the first rubber body 102, and the sleeve 103 are fitted together to form an assembly body, and finally the assembly body is assembled with the first portion 108 to form the main spring 100. The main spring 100 is difficult and expensive to produce because the size of the core shaft 101 is often large (e.g., 84 mm in diameter and 226 mm in length). However, according to the present embodiment, the entire core shaft 101 is not required to be operated when producing the main spring 100, but only the second portion 109 (for example, 70 mm in length) is required to be operated, which greatly reduces the production difficulty and reduces the production cost. In addition, in the process of processing the main spring 100 by vulcanization, the mandrel 101 is of a split structure, so that only the second part 109, the first rubber body 102 and the sleeve 103 are vulcanized, the vulcanization heating time can be effectively reduced, and the vulcanization processing cost is saved. Meanwhile, the size of the mandrel 101 to be vulcanized is greatly reduced, so that the vulcanization effect of the main spring 100 can be greatly improved, and the service life of the hydraulic bushing 1 is prolonged.

A gap 111 is provided in the end face of the sleeve 103 to communicate with the recess 110 as shown in figure 9. One end of the gap 111 communicates with the groove 110 and the other end communicates with the chamber 104. Preferably, the grooves 110 are helically disposed on the outer wall of the sleeve 103, as shown in fig. 8. By this arrangement, the length of the groove 110 can be increased appropriately, and the length of the flow passage 105 can be easily adjusted to meet the design requirements.

It is further preferred that the cross-section of the groove 110 is configured as a rectangular structure, and the cross-sectional dimension thereof can be set according to different requirements. The structure is simple and easy to realize. For example, the cross section of the groove 110 may be configured as a square, and the length of the cross section side may be set between 2 mm and 5 mm. It should be noted that the cross-sectional shape of the groove 110 may be configured in other configurations, such as "V", trapezoid, "U", or semicircle. The length of the groove 110 may be set between 2-5 meters. For example, the length of the flow path 105 is set to 3.4 meters. It should be noted that the length of the groove 110 can be set to different sizes according to actual needs. The helix angle of the grooves 110 may be 3 to 10 degrees on the outer wall of the sleeve 103.

As shown in fig. 2, sealing assemblies 300 are respectively sleeved at two ends of the stepped spindle 101 to seal the fluid passages such as the flow channel 105 and the fluid chamber 104.

In one embodiment, as shown in fig. 11, 12 and 13, the seal assembly 300 has a rigid support ring assembly 301, a second rubber body 302 and a first mating body 305. Wherein the support ring assembly 301 has a mounting ring 303 and a male ring 304, as shown in fig. 14. The mounting ring 303 is generally cylindrical and is adapted to fit over the outer wall of the mandrel 101. The male ring 304 is provided on the outer wall of the fitting ring 303 and projects radially outward, and in the axial direction, the male ring 304 is located approximately at the axial middle of the fitting ring 303. The second rubber body 302 is sleeved outside the assembling ring 303 and covers the convex ring 304. That is, the convex ring 304 is inserted into the second rubber body 302. Specifically, the axial inner end surface of the second rubber body 302 is in contact with both the axial end surface of the sleeve 103 and the first step surface 107 of the mandrel 101, so that the effect of axially sealing the flow channel 105 and the liquid chamber 104 is achieved.

The radial thickness of the first end of the mounting ring 303 is greater than the radial thickness of the second end. It is noted that the "first end" is described herein as being at the same end as the "axially inner end", and the "second end" is opposite the "first end" and is at the same end as the "axially outer end". That is, when the seal assembly 300 is assembled, its first end is adjacent the first step face 107 of the mandrel 101. In addition, the outer wall of the mounting ring 303 is disposed at an inclination, and the inclination of the inclination is between 0.75 and 0.9, for example, the inclination of the outer wall of the mounting ring 303 is 0.85. With this arrangement, the relative movement of the outer sleeve 300 and the mandrel 101 is not affected while ensuring an increase in the axial stiffness of the hydraulic bushing 1.

A first mating body 305 is provided on the second rubber body 302 and extends in an axially convex manner from an axially inner end face of the second rubber body 302 for sealing mating contact with a second mating body 112 (visible in fig. 2) provided on the first rubber body 102 to avoid communication of the liquid chamber 104 within the same axial end face. The sealing assembly 300 is arranged to realize sealing of the liquid flow channel 105 and the liquid cavity 104 in the hydraulic bushing 1, prevent liquid from communicating on the liquid cavity 104 in the same axial end face and ensure that the liquid is transferred from one liquid cavity 104 to the other liquid cavity 104 through the flow channel 105. In addition, the sealing assembly 300 increases the axial rigidity of the hydraulic bushing 1, and realizes the matching of the multidirectional rigidity of the hydraulic bushing 1, thereby meeting the requirements of customers. Thus, the ratio of the radial stiffness to the axial stiffness of the hydraulic bushing 1 can be flexibly adjusted by adjusting the seal assembly 300, thereby optimizing the use performance of the hydraulic bushing 1.

It should be noted that the above only describes an example in which the first mating body 305 has a protruding structure. The first engaging body 305 may be designed to be a concave structure, and correspondingly, the second engaging body 112 may be designed to be a convex structure, which also achieves the purpose of blocking the two liquid chambers 104 from communicating in the same axial end face of the first rubber body 102.

In a preferred embodiment, as shown in fig. 16, the first fitting body 305 is configured as a convex body having an arcuate radial section, and the arc of the arcuate shape of the first fitting body 305 extends inward facing the second fitting body 112. Correspondingly, the second mating body 112 is configured as a body structure with a concave radial cross section being arcuate. It is further preferable that the protruding strip 316 is provided on the arcuate arc surface of the first fitting body 305. In the radial direction, the projection 316 matches the arcuate curvature of the first fitting body 305. A better sealing effect is achieved by the protruding strip 316. In addition, the first engaging member 305 and the second engaging member 112 are close to each other, so that leakage can be effectively prevented and stress concentration can be reduced.

In the axial direction from inside to outside, the second rubber body 302 forms at least one rubber peak to be in interference fit with the jacket 200, thereby achieving the purpose of axial sealing. In one particular embodiment, two peaks are formed on the second rubber body 302, namely a first rubber peak 306 and a third rubber peak 308. Wherein, the first rubber peak 306 is in interference fit with the outer sleeve 200 to ensure the sealing effect for the flow channel 105 and prevent the liquid from leaking out through the gap between the second rubber body 302 and the outer sleeve 200. Further, the third rubber peak 308 is interference fitted with the sheath 200, thereby further ensuring and improving the sealing effect for the flow channel 105.

The third rubber peak 308 is located outside the first rubber peak 306 in the axial direction. Meanwhile, the diameter size of the third rubber peak 308 is larger than that of the first rubber peak 306 when not fitted into the lumen of the outer sheath 200. Preferably, the diameter of the third rubber peak 308 is 6 to 10 millimeters greater than the diameter of the first rubber peak 306. In the assembly, the sealing assembly 300 can be arranged in the inner cavity of the outer sleeve 200 in a press-fitting manner, and the arrangement ensures the smooth assembly, and meanwhile, two seals can be formed in the axial direction, so that the sealing effect is fully ensured.

The first rubber peak 306 and the third rubber peak 308 are arranged at intervals. Also, a first yielding space 309 is formed between the first rubber peak 306 and the third rubber peak 308. In the process that the rail train passes through a curve, the outer sleeve 200 moves relative to the mandrel 101, the second rubber body 302 can be extruded, and the movement resistance of the outer sleeve 200 is reduced by arranging the first abdicating space 309, so that the outer sleeve 200 can move relative to the mandrel 101 within a certain range more easily, and the flexible bending capability of the rail train is improved.

A second rubber peak 307 is provided between the first rubber peak 306 and the third rubber peak 308, the second rubber peak 307 being formed at the position of the convex ring 304. Meanwhile, the second rubber peak 307 protrudes into the first abdicating space 309, and in a natural state, the second rubber peak 307 has a certain distance from the outer jacket 200. That is, the second rubber peak 307 does not directly contact the jacket 200. Preferably, the second rubber peak 307 is about 3 to 10 mm from the jacket 200, for example, it may be 5 mm. When the movement amplitude of the jacket 200 relative to the mandrel 101 is relatively large, the second rubber peak 307 can abut against the jacket 200 to prevent the movement amplitude from further increasing. Thus, the first yielding space 309 provides a certain movement space for the relative movement of the mandrel 101 and the jacket 200, and the rigid collar 304 at the second rubber peak 307 can prevent the movement from being too large. In addition, the above arrangement also relatively increases the stiffness of the seal assembly 300, thereby optimizing the axial stiffness of the hydraulic bushing 1.

A first grommet 310 is arranged over the first rubber peak 306. The first backing ring 310 is a rigid ring and is arranged coaxially with the mounting ring 303. Meanwhile, the first grommet 310 is close to the sleeve 103 and opposite to the end surface of the sleeve 103 in the axial direction. Radially, the first grommet 310 is adjacent to the outer jacket 200. The provision of the first grommet 310 ensures that the second rubber 302 is in contact with the casing 200 in the radial direction, further improving the sealing ability of the sealing assembly 300. Preferably, a first projecting portion 311 projecting radially outward is provided on the first rubber peak 306 at a position corresponding to the first grommet 310, as shown in fig. 15. The first protrusion 311 further increases the sealing ability of the sealing assembly 300 to ensure the sealing effect.

The outer cover 200 includes a cover main body 201 and an extension 202, as shown in fig. 2. The jacket main body 201 is configured to be cylindrical and is sleeved on the outer wall of the sleeve 103, and the extension portions 202 are provided at both axial ends of the jacket main body 201 and fixedly connected to the jacket main body 201, and are configured to be annular and extend inward in the axial direction. The housing body 201 and the extension 202 are a one-piece member, as shown in fig. 10, and are brought into contact with the seal assembly 300 by a press-fitting process. The extension 202 defines the axial position of the first rubber body 102, the sleeve 103 and the sealing assembly 300, and ensures that the sealing assembly 300 is tightly attached to the sleeve 103, thereby ensuring the sealing effect. Additionally, in the radial direction, the inner wall of the extension 202 is a distance (e.g., 5 to 10 millimeters) from the support ring assembly 301. The distance between the extension 202 and the support ring assembly 301 during the movement of the jacket 200 relative to the mandrel 101 is such as to avoid the rigid extension 202 from abutting on the rigid support ring assembly 301, thus ensuring the flexible ability of the hydraulic bushing 1 to negotiate bends.

As shown in fig. 10, during the manufacturing process, second step surface 203 is provided on outer cover 200 so that the inner diameter dimension of both end sections of outer cover 200 is larger than the inner diameter dimension of the middle section. That is, the wall thickness of the jacket 200 at the middle section is greater than the wall thickness at the end sections. The extension 202 is formed at both end sections by press fitting. This arrangement makes the press-fitting operation easy. Meanwhile, the third rubber peak 308 is in contact with not only the inner wall of the outer jacket 200 but also the second step surface 203, thereby improving the sealing effect. In addition, a second grommet 313 is embedded in the third rubber peak 308. The second backing ring 313 is a rigid ring and is arranged coaxially with the mounting ring 303. In the axial direction, the second grommet 313 is disposed between the second step surface 203 and the extension 202. Radially, second grommet 313 is close to outer jacket 200. Also, the axially outer end face of the second grommet 313 directly contacts the radially extending portion 202. The sealing capacity of the sealing assembly is even further improved by this arrangement.

The outer axial end surface and the outer radial end surface of the second backing ring 313 are connected by a circular arc surface, as can be seen from fig. 15. This arrangement facilitates the press-fitting operation of outer sleeve 200 and ensures that extension 202 is pressed into place.

A second projecting portion 314 that projects radially outward is provided on the third rubber peak 308, as shown in fig. 15. Second projection 314 is positioned between second grommet 313 and outer casing 200, which in turn further improves the sealing ability of seal assembly 300.

A third protrusion 315 is provided on an axially inner end surface of the second rubber body 302, as shown in fig. 15. The third protrusion 315 is located between the second rubber body 302 and the first step surface 107 of the stem 101 to ensure sealing of the auxiliary liquid chamber 114.

In addition, a second relief space 312 is provided in the second rubber body 302, as shown in fig. 12. Second relief space 312 is provided on the axially outer end face of second rubber body 302 and is configured as a concave annular groove. This second relief space 312 increases the radial deformability of the seal assembly 300, thereby increasing the flexible overbending capability of the hydraulic bushing 1.

As shown in fig. 1, the outer case 200 is provided with a pour hole 204. The pour hole 204 is constructed as a through hole in the wall of the outer casing 200 and communicates with the flow passage 105. The liquid injection hole 204 is simple in structure, easy to implement, and easy to implement the oiling operation. In addition, a plug 205 is hermetically arranged at the liquid injection hole 204, as shown in FIG. 2. For example, the plug 205 and the pour hole 204 may be sealingly threaded.

The end face of the first rubber body 102 is configured with circumferential grooves 113 distributed in the circumferential direction, as shown in fig. 5. First rubber body 102, second rubber body 302, sleeve 103, and first mating body 305 form auxiliary fluid chamber 114 at annular groove 113, as shown in FIG. 3. The auxiliary fluid chamber 114 is disposed intermediate and in communication with both fluid chamber 104 and flow channel 105. On the one hand, the auxiliary fluid chamber 114 increases the fluid storage capacity of the hydraulic bushing 1, and improves the stiffness adjustment effect of the hydraulic bushing 1. On the other hand, the auxiliary fluid chamber 114 increases the safety of the hydraulic bushing 1 in use, for example, even in the case of a blocked fluid chamber 104, the fluid inside the hydraulic bushing 1 can still flow.

Main spring 100 is press-fitted into the inner cavity of casing 200. This way sealing of the flow channel 105 can be ensured. According to the present invention, the outer diameter of the main spring 100 is 1.5-2.3 mm larger than the inner diameter of the cover 200 before press-fitting. For example, the inner diameter of the sheath 200 is sized to

Mm, and the outer diameter of the main spring 100 is

And (4) millimeter. This arrangement ensures that main spring 100 is smoothly pressed into case 200 and also ensures sealing between main spring 100 and case 200.

In a preferred embodiment, the sleeve 103 is made of nylon 66. The nylon 66 with the utilization rate in the arrangement mode has the advantages of high fatigue resistance and rigidity, high heat resistance and high wear resistance, and the service life of the hydraulic bushing 1 is prolonged.

For the purposes of the specification, abstract and claims of this application, it is noted that the singular forms "a," "an," and the like include the plural forms as well, unless expressly stated otherwise.

While the invention has been described with reference to a preferred embodiment, various modifications may be made and equivalents may be substituted for elements thereof without departing from the scope of the invention. In particular, the technical features mentioned in the embodiments can be combined in any way as long as there is no structural conflict. It is intended that the invention not be limited to the particular embodiments disclosed, but that the invention will include all embodiments falling within the scope of the appended claims.

Claims

1. A seal assembly for a hydraulic bushing, comprising:

a rigid support ring assembly having a mounting ring and a collar projecting radially outwardly from an outer wall of the mounting ring at a location axially intermediate the mounting ring,

a second rubber body which covers the convex ring and is sleeved outside the assembling ring,

in the direction from the first end to the second end, the second rubber body is provided with a first rubber peak and a third rubber peak which are arranged at intervals and protrude outwards in the radial direction, and a first yielding space is formed between the first rubber peak and the third rubber peak.

2. The seal assembly of claim 1, wherein a radial thickness of the first end of the mounting ring is greater than a radial thickness of the second end.

3. The seal assembly of claim 1, wherein the second rubber body has a second rubber peak disposed between the first rubber peak and the third rubber peak, the second rubber peak being located opposite the torus and projecting radially into the first yield space.

4. A seal assembly according to any one of claims 1 to 3, wherein a second relief space is provided on the outer end face of the second end of the second rubber body, the second relief space being configured as an annular groove.

5. The seal assembly of any one of claims 1 to 3, wherein a rigid first grommet coaxial with the mounting ring is disposed over the first rubber peak.

6. The seal assembly of claim 5, wherein a first projection projecting radially outward is provided on the first rubber peak at a location corresponding to the first grommet.

7. The seal assembly of any one of claims 1 to 3, wherein a rigid second grommet coaxial with the mounting ring is embedded within the third rubber peak.

8. The seal assembly of claim 7, wherein a second projection projecting radially outward is provided on the third rubber peak at a location corresponding to the second grommet.

9. A hydraulic bushing, comprising:

a mandrel having a first stepped surface to configure the mandrel as a stepped shaft having a middle section diameter greater than two end sections diameters,

a sleeve sleeved on the outer wall of the first rubber body, wherein the outer wall of the sleeve is provided with a groove,

the seal assembly according to any one of claims 1 to 8, wherein the fitting rings of the seal assembly are sleeved on both ends of the mandrel,

the sleeve is sleeved with the outer sleeve on the outer side of the sealing assembly, and the outer sleeve and the sleeve are arranged in the groove to form a flow channel for communicating the two liquid cavities.