CN209839051U - Hydraulic bushing - Google Patents
Hydraulic bushing Download PDFInfo
- Publication number
- CN209839051U CN209839051U CN201821773801.1U CN201821773801U CN209839051U CN 209839051 U CN209839051 U CN 209839051U CN 201821773801 U CN201821773801 U CN 201821773801U CN 209839051 U CN209839051 U CN 209839051U
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- CN
- China
- Prior art keywords
- flow passage
- hydraulic
- hydraulic bushing
- channel
- mandrel
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Withdrawn - After Issue
Links
- 239000012530 fluid Substances 0.000 claims abstract description 52
- 239000007788 liquid Substances 0.000 claims abstract description 30
- 238000003825 pressing Methods 0.000 claims abstract description 4
- 238000007789 sealing Methods 0.000 claims description 19
- 238000013016 damping Methods 0.000 description 4
- 230000000694 effects Effects 0.000 description 4
- 230000000712 assembly Effects 0.000 description 2
- 238000000429 assembly Methods 0.000 description 2
- 238000009826 distribution Methods 0.000 description 2
- 230000002708 enhancing effect Effects 0.000 description 2
- 125000006850 spacer group Chemical group 0.000 description 2
- 229910000831 Steel Inorganic materials 0.000 description 1
- 230000001174 ascending effect Effects 0.000 description 1
- 238000004891 communication Methods 0.000 description 1
- 238000004519 manufacturing process Methods 0.000 description 1
- 239000002184 metal Substances 0.000 description 1
- 238000012986 modification Methods 0.000 description 1
- 230000004048 modification Effects 0.000 description 1
- 230000002093 peripheral effect Effects 0.000 description 1
- 239000010959 steel Substances 0.000 description 1
- 239000000725 suspension Substances 0.000 description 1
Landscapes
- Combined Devices Of Dampers And Springs (AREA)
Abstract
The utility model provides a hydraulic pressure bush, include: a mandrel; the hydraulic fluid flow control device comprises a sleeve-shaped first flow passage body sleeved on a mandrel, wherein a gap between the mandrel and the first flow passage body is filled with a first rubber body, and a first flow passage for hydraulic fluid is formed on the outer surface of the first flow passage body; and the outer sleeve is sleeved on the radial outer side of the first flow channel body in a pressing mode. Two main liquid chambers for receiving hydraulic fluid are formed on the first rubber body in diametrically opposite manner, and communicate with each other via a first flow channel. A seal assembly is disposed axially outwardly of at least one of the first flow passage bodies and defines, in cooperation with the outer sleeve, two auxiliary fluid chambers. A second channel body is arranged in the auxiliary fluid chamber, a second channel for hydraulic fluid is formed on the outer surface of the second channel body, and the two auxiliary fluid chambers are communicated with each other through the second channel.
Description
Technical Field
The utility model relates to a hydraulic pressure bush for vehicle, especially rail vehicle.
Background
A hydraulic bushing is a part widely used in vehicles (e.g., automobiles and railway vehicles), and is mainly installed on a suspension or a bogie of a vehicle to absorb vibration and impact, thereby improving the stability and safety of the vehicle in running.
Chinese patent document CN108150536A discloses a hydraulic bushing. The hydraulic bushing comprises a mandrel, a first flow channel body and an outer sleeve, wherein the first flow channel body is sleeved on the outer side of the mandrel, and the outer sleeve is sleeved on the outer side of the first flow channel body in a pressing mode. A gap between the mandrel and the first fluid is filled with a first rubber body, and a groove is formed on the outer surface of the first fluid. Two liquid cavities for containing liquid are oppositely and radially constructed on the first rubber body, wherein the groove and the outer sleeve enclose a flow channel, and the two liquid cavities are communicated through the flow channel. The rigidity of the hydraulic bushing can be adjusted by the fluidity between the hydraulic fluid in the two fluid chambers, thereby achieving an improvement in the stability of the vehicle when running, particularly when the vehicle is turning.
However, in the above-described hydraulic bushing, the range of stiffness and damping adjustment thereof is still limited. It would be desirable in the art to provide a hydraulic bushing having a stiffness and damping that can be varied over a greater range to provide greater ride stability and safety for the vehicle.
SUMMERY OF THE UTILITY MODEL
The utility model aims at providing a novel hydraulic pressure bush, it can realize the variable stiffness on a wider range.
According to the utility model discloses, a hydraulic pressure bush is provided, include: a mandrel; the first fluid is sleeved on the mandrel, a first rubber body is filled in a gap between the mandrel and the first fluid, and a first flow channel for hydraulic fluid is constructed on the outer surface of the first fluid; and the outer sleeve is sleeved on the radial outer side of the first flow channel body in a pressing mode. Wherein two main liquid chambers for containing hydraulic fluid are configured on the first rubber body in a radial direction and oppositely, and the two main liquid chambers are communicated with each other through the first flow passage. A sealing arrangement is arranged on at least one axially outer side of the first channel body, which sealing arrangement defines together with the jacket two auxiliary fluid chambers, in which auxiliary fluid chambers a second channel body is arranged, on the outer surface of which second channel bodies a second channel for hydraulic fluid is formed, wherein the two auxiliary fluid chambers communicate with one another via the second channel.
In a preferred embodiment, both auxiliary chambers extend only partially in the circumferential direction and are diametrically opposite one another.
In a preferred embodiment, the seal assembly includes a support ring fitted over the mandrel, the support ring including a radial projection within the auxiliary fluid chamber.
In a preferred embodiment, the second fluid channel is configured as an annular member having a radially inner surface supported by the radial projection and a radially outer surface in sealing contact with a radially inner surface of the outer sleeve.
In a preferred embodiment, the seal assembly further comprises a second rubber body vulcanized onto the support ring, the second rubber body including a first portion in sealing contact with an axial end of the first runner body and a second portion in sealing contact with an axial end of the outer sleeve, wherein the radial projection is axially between the first and second portions.
In a preferred embodiment, said second rubber body further comprises a third portion vulcanized on said radial protrusion.
In a preferred embodiment, rigid shims are embedded in both the first and second portions of the second rubber body.
In a preferred embodiment, the inner surface of said second flow passage body includes an intermediate flat portion of reduced radial dimension for sealing contact with said third portion.
In a preferred embodiment, the same sealing assembly is provided on both axially outer sides of the first flow passage body.
In a preferred embodiment, the cross-sectional area and the length of the first and second flow passages are determined according to the required radial dynamic stiffness of the hydraulic bushing.
According to the utility model discloses a hydraulic pressure bush includes supplementary sap cavity and sets up the second runner body at supplementary sap cavity, can further enlarge the rigidity control range of hydraulic pressure bush in radial ascending to the variable rigidity characteristic and the damping effect that hydraulic pressure bush can provide have been improved.
Drawings
The present invention will be described in more detail hereinafter based on embodiments and with reference to the accompanying drawings. Wherein:
fig. 1 schematically shows a cross-sectional view of a hydraulic bushing according to an embodiment of the invention.
Fig. 2 is an enlarged view showing an auxiliary fluid chamber in the hydraulic bushing shown in fig. 1.
In the drawings, like parts are denoted by like reference numerals. The figures are not drawn to scale.
Detailed Description
The present invention will be further explained with reference to the accompanying drawings. It should be noted that the terms "axial" and "radial" in this document refer to the horizontal and vertical directions in fig. 1, respectively.
Fig. 1 schematically shows a hydraulic bushing 100 according to an embodiment of the invention. As shown in fig. 1, the hydraulic bushing 100 includes a core shaft 10, a first flow passage body 20 disposed radially outside the core shaft 10, and an outer sleeve 30 that is fitted over the first flow passage body 20 in a compressed manner. The first flow passage body 20 is generally configured in the form of a sleeve member. The mandrel 10 is typically a preform and, in the embodiment shown in fig. 1, is configured in the form of a stepped shaft. The mandrel 10 can be connected at both ends, for example, to a bogie of a rail train, while the outer jacket 30 is connected to the positioning jib. An optional inner sleeve 15 may also be provided over the mandrel 10, as shown in FIG. 1. Both axial ends of the outer sleeve 30 are radially bent towards the mandrel 10 to form a flange 32 to facilitate sealing of the hydraulic bushing 100, as will be described in detail below.
A first rubber body 40 is filled in the gap between the mandrel 10 and the first fluid 20. However, it is understood that in the case where the inner case 15 is provided, the first rubber body 40 may be filled between the inner case 15 and the first fluid passage 20. Two main liquid chambers 45 for containing hydraulic fluid are provided on the first rubber body 40, which are preferably configured to be diametrically opposed. That is, both the main liquid chambers 45 extend only partially in the circumferential direction and are opposed in the radial direction. Grooves are formed on the outer surface of the first flow channel body 20, which may be in the form of a spiral circumferential distribution. In the assembled state, the outer sleeve 30 is pressed against the first flow passage body 20, so that the groove in the first flow passage body 20 forms a first flow passage 42 for the hydraulic fluid to flow therein. Both ends of the first flow path 42 communicate with the two main liquid chambers 45, respectively. In addition, a liquid charging hole (not shown) for charging the hydraulic fluid is constructed on the outer sleeve 30 in communication with the first flow passage 42.
When the rail train runs in the straight-line section snake-shaped resisting operation stage, the wheel set can bear high-frequency vibration, and when the rail train runs in a curve at a low speed, the wheel rim of the wheel set can be attached to a steel rail, and the vibration frequency is obviously reduced. Under the two working conditions, the movement of the wheel drives the mandrel 10 and the outer sleeve 30 to move relatively, so that the main liquid cavity at the front and the main liquid cavity at the rear can expand and contract respectively. Thus, hydraulic fluid can flow between the two main liquid chambers 45 through the first flow passage 42, and accordingly the radial rigidity of the hydraulic bushing 100 is adjusted, so that the train keeps stable operation. This varying stiffness is an important property of the hydraulic bushing 100.
The above-mentioned features and functions of the hydraulic bushing are known in the art, for example, see the applicant's chinese patent document CN108150536A, which is incorporated herein by reference.
According to the present invention, as shown in fig. 1, both ends of the first flow passage body 20 in the axial direction are closed by the seal assembly 50 so as to form a closed chamber for containing the hydraulic fluid, i.e., the main liquid chamber 45. The seal assembly 50 includes a rigid support ring 60 mounted on the mandrel 10. In the illustrated embodiment, the mandrel 10 is configured as a stepped shaft, and thus, the support ring 60 is preferably installed at the stepped structure of the mandrel 10 so as to form a good location and be more stably supported. A second rubber body 70 is vulcanized onto the support ring 60, and rigid gaskets 55, 56 (see fig. 2) are embedded in the second rubber body 70. In this way, the support ring 60 and the spacers 55, 56 are integrated by the second rubber body 70.
As shown more clearly in fig. 2, the cured second rubber body 70 includes two axially spaced apart portions, an inner portion 72 adjacent the axial end of the first runner body 20 and an outer portion 74 adjacent the axial end of the outer sleeve 30. With this arrangement, the inner portion 72 of the second rubber body 70 forms a seal with the outer surface of the axial end of the first flow path body 20, while the outer portion 74 of the second rubber body 70 forms a seal with the inner surface of the flange 32 formed at the axial end of the outer sheath 30. Thus, a sealed auxiliary fluid chamber 80 is formed between the inner portion 72 of the second rubber body 70, the outer portion 74 of the second rubber body 70, the support ring 60 and the outer sleeve 30, in which hydraulic fluid can be accommodated. As with the primary liquid chamber 45, two secondary liquid chambers 80 are formed within each seal assembly 50, each extending only partially in the circumferential direction and preferably configured to be diametrically opposed. It should be noted that both of the auxiliary liquid chambers 80 are configured not to communicate with the main liquid chamber 45.
According to the utility model, a second flow channel body 90 is also arranged in the auxiliary liquid cavity 80. The second flow passage body 90 is configured as an annular member and is mounted in the outer casing 30 by interference fit. Thus, the outer surface of the second flow path body 90 and the inner surface of the outer sleeve are brought into sealing contact.
In the preferred embodiment as shown, support ring 60 also includes radially outwardly projecting tabs 62. The projection 62 is located axially between an inner portion 72 and an outer portion 74 of the second rubber body 70. In the assembled state, the radially outwardly projecting tabs 62 of the support ring 60 are located within the auxiliary liquid chamber 80. As shown in fig. 2, the outer peripheral end surface of the projection 62 terminates in the auxiliary liquid chamber 80. That is, the protrusion 62 does not contact the inner surface of the second flow passage body 90 in the radial direction.
According to the present invention, the second flow passage body 90 is provided with a groove on its outer circumferential surface, thereby forming the second flow passage 92 for the hydraulic fluid. Like the first flow passage 42, the second flow passage 92 may also be in the form of a helical circumferential distribution. Both ends of a second flow path 92 formed by a groove on the outer circumferential surface of the second flow path body 90 are connected to the two auxiliary liquid chambers 80, respectively, in the same manner as both ends of the first flow path 42 are connected to the two main liquid chambers 45, respectively. In this way, hydraulic fluid may flow back and forth between the two auxiliary fluid chambers 80 through the second flow passage 92, thereby further enhancing the radial stiffness characteristics of the hydraulic bushing 100.
By adding the auxiliary fluid chamber 80 and the second flow path body 90, hydraulic fluid can flow between the other two auxiliary fluid chambers 80 in addition to the two main fluid chambers 45. By the hydraulic fluid flowing between the two auxiliary fluid chambers 80, the rigidity of the hydraulic bushing 100 in the radial direction can be adjusted and varied over a larger range, further enhancing the effect of the variable rigidity and damping in the radial direction of the hydraulic bushing 100.
According to the present invention, the geometric parameters of the cross-sectional area and length of the first and second flow passages 42, 92 depend on the requirement for axial stiffness of the hydraulic bushing 100. The geometric parameters of the first and second flow passages 42, 92 may be selected to be the same as each other or different from each other, depending on the requirements of a particular application.
According to an alternative embodiment of the invention, in the preferred embodiment shown in fig. 2, a third portion 76 of the second rubber body 70 is also provided on the projection 62 of the support ring 60. In this way, the support ring 60 is in contact with the second flow passage body 90 through the third portion 76 of the second rubber body 70, thereby being able to provide a more flexible support for the second flow passage body 90.
In addition, in the preferred embodiment as shown in fig. 2, the second flow passage body 90, which is configured as an annular member, has a recessed flat intermediate region 94 on its inner circumferential surface. The third portion 76 of the second rubber body 70 comes into contact with the middle area 94 of the second fluid channel 90. In this way, more stable support can be provided for the second fluid passage 90.
According to the present invention, rigid spacers 55 and 56 are embedded within the outer portion 74 and inner portion 72 of the rubber body 70, respectively, to provide a degree of axial stiffness to the hydraulic bushing 100. In addition to the function of providing axial rigidity, the gasket 56 can also press the adjacent second rubber body 70, thereby sufficiently securing the sealing effect of the hydraulic fluid in the main liquid chamber 45 and the auxiliary liquid chamber 80. The insert 55 can then form a seal with the flange 32 of the metal casing 30 and the outer portion 74 of the second rubber body 70 located therebetween for the auxiliary liquid chamber 80. This further improves the sealing performance of the auxiliary liquid chamber 80.
During the manufacturing process of the hydraulic bushing 100, the second runner body 90, the support ring 60, and the gaskets 55 and 56 may be pre-embedded together in the mold cavity, and then the seal assembly 50 may be formed by vulcanizing the second rubber body 70. Finally, the seal assembly 50 is press fit into the outer sleeve 30.
It should be noted that a seal assembly is required to be provided at both axial ends of the first fluid passage. Both seal assemblies may be seal assemblies 50 as described above, or only one of them may employ a seal assembly 50 as described above, while the other employs a conventional seal. Such a common seal need only provide a sealing effect to form a closed primary liquid chamber and is readily designed by a person skilled in the art.
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. The present invention is not limited to the particular embodiments disclosed herein, but encompasses all technical solutions falling within the scope of the claims.
Claims (9)
1. A hydraulic bushing, comprising:
a mandrel;
a sleeve-shaped first flow passage body sleeved on the mandrel, wherein a gap between the mandrel and the first flow passage body is filled with a first rubber body, and a first flow passage for hydraulic fluid is constructed on the outer surface of the first flow passage body; and
the outer sleeve is sleeved on the radial outer side of the first runner body in a pressing mode;
wherein two main liquid chambers for containing hydraulic fluid are configured on the first rubber body in a radial direction and oppositely, the two main liquid chambers are communicated with each other through the first flow passage,
a sealing arrangement is arranged on at least one axially outer side of the first channel body, which sealing arrangement defines together with the jacket two auxiliary fluid chambers, in which a second channel body is arranged, on the outer surface of which a second channel for hydraulic fluid is formed, wherein the two auxiliary fluid chambers communicate with one another via the second channel, each of which extends only partially in the circumferential direction and is diametrically opposite one another.
2. The hydraulic bushing of claim 1 wherein said seal assembly includes a support ring disposed over said mandrel, said support ring including a radial projection within said auxiliary fluid chamber.
3. The hydraulic bushing of claim 2, wherein the second flow passage fluid is configured as an annular member having a radially inner surface supported by the radial projection and a radially outer surface in sealing contact with a radially inner surface of the outer sleeve.
4. The hydraulic bushing of claim 3, wherein the seal assembly further includes a second rubber vulcanized to the support ring, the second rubber including a first portion in sealing contact with an axial end of the first runner body and a second portion in sealing contact with an axial end of the outer sleeve, wherein the radial projection is axially between the first and second portions.
5. The hydraulic bushing of claim 4 wherein the second rubber body further includes a third portion vulcanized onto the radial protrusion.
6. A hydraulic bushing according to claim 4, characterized in that rigid shims are embedded in both the first and second portions of the second rubber body.
7. The hydraulic bushing of claim 5, wherein the inner surface of the second runner body includes an intermediate flat portion of reduced radial dimension for sealing contact with the third portion.
8. A hydraulic bushing according to any one of claims 1 to 7, characterized in that the same sealing assembly is provided on both axially outer sides of the first flow passage body.
9. A hydraulic bushing according to any one of claims 1 to 7, wherein the cross-sectional area and length of the first and second flow passages are determined according to the required radial dynamic stiffness of the hydraulic bushing.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201821773801.1U CN209839051U (en) | 2018-10-30 | 2018-10-30 | Hydraulic bushing |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201821773801.1U CN209839051U (en) | 2018-10-30 | 2018-10-30 | Hydraulic bushing |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN209839051U true CN209839051U (en) | 2019-12-24 |
Family
ID=68889527
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201821773801.1U Withdrawn - After Issue CN209839051U (en) | 2018-10-30 | 2018-10-30 | Hydraulic bushing |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN209839051U (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN109268441A (en) * | 2018-10-30 | 2019-01-25 | 株洲时代新材料科技股份有限公司 | Hydraulic bushing |
-
2018
- 2018-10-30 CN CN201821773801.1U patent/CN209839051U/en not_active Withdrawn - After Issue
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN109268441A (en) * | 2018-10-30 | 2019-01-25 | 株洲时代新材料科技股份有限公司 | Hydraulic bushing |
| CN109268441B (en) * | 2018-10-30 | 2024-04-05 | 株洲时代新材料科技股份有限公司 | Hydraulic bushing |
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Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| GR01 | Patent grant | ||
| GR01 | Patent grant | ||
| AV01 | Patent right actively abandoned | ||
| AV01 | Patent right actively abandoned | ||
| AV01 | Patent right actively abandoned |
Granted publication date: 20191224 Effective date of abandoning: 20240405 |
|
| AV01 | Patent right actively abandoned |
Granted publication date: 20191224 Effective date of abandoning: 20240405 |