CN108150593B

CN108150593B - Hydraulic bushing

Info

Publication number: CN108150593B
Application number: CN201611166938.6A
Authority: CN
Inventors: 邹波; 钟海兵; 吴明珠; 凌斗; 罗旦; 邹宇; 姜其斌
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: 2020-07-07
Anticipated expiration: 2036-12-16
Also published as: CN206555348U; CN108150598B; CN108150535A; CN108150593A; CN108150585A; CN108150597B; CN108150589B; CN108150595A; CN206555347U; CN108150598A; CN108150588A; CN108150595B; CN108150596A; CN108150536A; CN108150536B; CN108150590A; CN108150597A; CN108150535B; CN108150592A; CN206361076U

Abstract

The invention relates to a hydraulic bushing, comprising a mandrel; the first rubber body is sleeved on the outer wall of the mandrel, and two axially-penetrating liquid cavities are arranged on the first rubber body in a radially opposite and spaced manner; the sleeve is sleeved on the outer wall of the first rubber body, and a groove is formed in the wall of the sleeve; the outer sleeve is sleeved on the outer side of the sleeve, a flow channel for communicating the two liquid cavities is formed at the groove of the outer sleeve and the sleeve, the hydraulic bushing is beneficial to realizing the stable running of the rail train, and the abrasion of wheels and a rail in a curve running state can be reduced.

Description

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 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 proposes a hydraulic bushing. After the hydraulic bushing is used on a rail train, the hydraulic bushing not only can ensure that the train stably moves forwards in a straight running state, but also can reduce the abrasion of wheels and rails in a curve running state.

The hydraulic bushing according to the present invention comprises:

a mandrel is arranged on the upper surface of the shell,

a first rubber body sleeved on the outer wall of the mandrel, two axially-penetrating liquid cavities arranged on the first rubber body in a radially opposite and spaced manner,

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

an outer sleeve sleeved on the outer side of the sleeve,

wherein, the outer sleeve and the sleeve form a flow channel for communicating the two liquid cavities at the groove.

In one embodiment, the mandrel has a first step surface to configure the mandrel as a stepped shaft having a middle section diameter larger than diameters of both end sections, the first rubber body is disposed in the middle section of the mandrel, and seal assemblies having a second rubber body and a first fitting body are respectively sleeved on both ends of the mandrel, the second rubber body is in contact with an axial end surface of the sleeve and the first step surface, and the first fitting body is used for hermetically isolating the two liquid chambers on the same end.

In one embodiment, the end face of the first rubber body is configured with circumferentially distributed annular grooves, and the first rubber body, the second rubber body, the sleeve and the first fitting body form auxiliary liquid chambers at the annular grooves.

In one embodiment, the seal assembly further comprises a rigid support ring assembly having a mounting ring sleeved on the mandrel and a protruding ring protruding radially outward from an outer wall of the mounting ring, wherein the second rubber body covers the protruding ring and is sleeved outside the mounting ring.

In one embodiment, the second rubber body has at least one rubber peak with an interference fit with the jacket.

In one embodiment, in the axial direction from inside to outside, the second rubber body sequentially forms a first rubber peak, a second rubber peak and a third rubber peak, the first rubber peak and the third rubber peak are in interference fit with the outer sleeve, the second rubber peak is opposite to the convex ring in position, a rigid first cushion ring coaxial with the assembling ring is arranged at the first rubber peak in a covering mode, and the first cushion ring is close to the sleeve and opposite to the end face of the sleeve.

In one embodiment, the outer sleeve includes a cylindrical outer sleeve body and a radially extending portion connected to the outer sleeve body, the radially extending portion being formed by press fitting and contacting the seal assembly.

In one embodiment, the second step surface is provided on the jacket main body such that the inner diameter dimension of both end sections of the jacket main body is larger than the inner diameter dimension of the middle section, a rigid second grommet coaxial with the fitting ring is embedded in the third rubber peak portion, and the second grommet and the third rubber peak disposed radially outward of the second grommet radially extend into a space formed by the second step surface and the radially extending portion.

In one embodiment, a second projection projecting radially outward is provided on the third rubber peak at a position corresponding to the second grommet.

In one embodiment, the axial outer end face and the radial outer end face of the second backing ring are connected through a circular arc surface.

Compared with the prior art, the invention has the advantages that: the hydraulic bushing of the present invention is configured with a first rubber body, a liquid chamber, and a flow passage. When the train runs on a curve, the liquid cavity and the flow channel not only can enable the wheels to smoothly turn so as to reduce the abrasion of the wheels and the track, but also can provide larger rigidity for the train during the straight running of the train so as to enable the train to keep stable running.

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.

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. By this arrangement, the main part can be ensuredSpring 100 is smoothly pressed into housing 200 and a seal between main spring 100 and housing 200 is also ensured.

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 hydraulic bushing, comprising:

a mandrel is arranged on the upper surface of the shell,

a first rubber body sleeved on the outer wall of the mandrel, two axially-penetrating liquid cavities arranged on the first rubber body in a radial opposite interval manner,

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

an outer sleeve sleeved on the outer side of the sleeve,

wherein the outer sleeve and the sleeve form a flow passage for communicating the two liquid cavities at the groove,

sealing components are respectively arranged at two ends of the mandrel, each sealing component is provided with a supporting ring component sleeved on the mandrel and a second rubber body fixedly arranged on the supporting ring component,

the outer sleeve comprises a cylindrical outer sleeve main body and a radial extension part connected with the outer sleeve main body, the radial extension part is formed by press fitting and is in contact with the sealing component,

and a second step surface is arranged on the jacket main body, so that the inner diameter size of the two end sections of the jacket main body is larger than that of the middle section, a rigid second cushion ring is embedded in the second rubber body, and the second cushion ring and the second rubber body arranged outside the second cushion ring in the radial direction extend to a space formed by the second step surface and the radial extension part in the radial direction.

2. The hydraulic bushing of claim 1, wherein the core shaft has a first step surface to configure the core shaft as a stepped shaft having a middle section diameter larger than both end sections, the first rubber body is disposed at the middle section of the core shaft, and the seal assemblies having first engaging bodies for sealingly isolating the two liquid chambers on the same end are respectively sleeved at both ends of the core shaft, and the second rubber body is in contact with an axial end surface of the sleeve and the first step surface.

3. The hydraulic bushing of claim 2, wherein an end face of the first rubber body is configured with circumferentially distributed annular grooves, the first rubber body, the second rubber body, the sleeve and the first mating body forming auxiliary fluid chambers at the annular grooves.

4. The hydraulic bushing of claim 2 wherein the support ring assembly is rigid and has a mounting ring sleeved over the mandrel and a collar projecting radially outward from an outer wall of the mounting ring, wherein the second rubber body is sleeved over the collar on an outer side of the mounting ring.

5. The hydraulic bushing of claim 4 wherein the second rubber body has at least one rubber peak in an interference fit with the outer jacket.

6. The hydraulic bushing of claim 5, wherein the second rubber body sequentially forms a first rubber peak, a second rubber peak and a third rubber peak in an axial direction from inside to outside, the first rubber peak and the third rubber peak are in interference fit with the outer sleeve, the second rubber peak is opposite to the convex ring, a rigid first backing ring coaxial with the assembling ring is arranged at the first rubber peak in a covering mode, and the first backing ring is close to the sleeve and opposite to the end face of the sleeve.

7. The hydraulic bushing of claim 6, wherein a second protrusion protruding radially outward is provided on the third rubber peak at a position corresponding to the second grommet.

8. The hydraulic bushing of claim 7 wherein the axial outer end surface and the radial outer end surface of the second backing ring are connected by a radius surface.