CN110185735B - Liquid composite lining - Google Patents
Liquid composite lining Download PDFInfo
- Publication number
- CN110185735B CN110185735B CN201910414300.7A CN201910414300A CN110185735B CN 110185735 B CN110185735 B CN 110185735B CN 201910414300 A CN201910414300 A CN 201910414300A CN 110185735 B CN110185735 B CN 110185735B
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- Prior art keywords
- flow channel
- liquid
- runner
- radial
- rubber body
- Prior art date
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- 239000007788 liquid Substances 0.000 title claims abstract description 73
- 239000002131 composite material Substances 0.000 title claims abstract description 36
- 239000012530 fluid Substances 0.000 claims abstract description 41
- 230000002093 peripheral effect Effects 0.000 claims description 7
- 230000003247 decreasing effect Effects 0.000 claims description 2
- 238000002347 injection Methods 0.000 description 10
- 239000007924 injection Substances 0.000 description 10
- 238000007789 sealing Methods 0.000 description 10
- 208000002740 Muscle Rigidity Diseases 0.000 description 9
- 230000000694 effects Effects 0.000 description 9
- 206010052904 Musculoskeletal stiffness Diseases 0.000 description 8
- 238000009434 installation Methods 0.000 description 7
- 230000007423 decrease Effects 0.000 description 3
- 238000004519 manufacturing process Methods 0.000 description 3
- 230000007246 mechanism Effects 0.000 description 3
- 230000007704 transition Effects 0.000 description 3
- 238000004073 vulcanization Methods 0.000 description 3
- 229910000831 Steel Inorganic materials 0.000 description 2
- 238000006073 displacement reaction Methods 0.000 description 2
- 238000012423 maintenance Methods 0.000 description 2
- 230000004048 modification Effects 0.000 description 2
- 238000012986 modification Methods 0.000 description 2
- 230000007480 spreading Effects 0.000 description 2
- 239000010959 steel Substances 0.000 description 2
- 230000000712 assembly Effects 0.000 description 1
- 238000000429 assembly Methods 0.000 description 1
- 230000003139 buffering effect Effects 0.000 description 1
- 230000006835 compression Effects 0.000 description 1
- 238000007906 compression Methods 0.000 description 1
- 230000001747 exhibiting effect Effects 0.000 description 1
- 230000006872 improvement Effects 0.000 description 1
- 238000000034 method Methods 0.000 description 1
- 239000000725 suspension Substances 0.000 description 1
Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
- F16F13/00—Units comprising springs of the non-fluid type as well as vibration-dampers, shock-absorbers, or fluid springs
- F16F13/04—Units comprising springs of the non-fluid type as well as vibration-dampers, shock-absorbers, or fluid springs comprising both a plastics spring and a damper, e.g. a friction damper
- F16F13/06—Units comprising springs of the non-fluid type as well as vibration-dampers, shock-absorbers, or fluid springs comprising both a plastics spring and a damper, e.g. a friction damper the damper being a fluid damper, e.g. the plastics spring not forming a part of the wall of the fluid chamber of the damper
- F16F13/08—Units comprising springs of the non-fluid type as well as vibration-dampers, shock-absorbers, or fluid springs comprising both a plastics spring and a damper, e.g. a friction damper the damper being a fluid damper, e.g. the plastics spring not forming a part of the wall of the fluid chamber of the damper the plastics spring forming at least a part of the wall of the fluid chamber of the damper
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
- F16F2228/00—Functional characteristics, e.g. variability, frequency-dependence
- F16F2228/06—Stiffness
- F16F2228/066—Variable stiffness
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Combined Devices Of Dampers And Springs (AREA)
Abstract
The present invention provides a liquid composite liner comprising: a mandrel; the rubber body is sleeved on the periphery of the mandrel, and two radial protrusions extending in the circumferential direction are formed on the rubber body in a radial opposite mode; two runner bodies which are respectively sleeved on the rubber body and are positioned at the outer sides of the radial protrusions in the axial direction, wherein a runner for hydraulic fluid is constructed on the outer surface of the runner bodies; and a jacket which is tightly sleeved on the radial outer side of the runner body; wherein the rubber body, the runner body and the jacket together define two liquid chambers for containing hydraulic fluid, the two liquid chambers being located between the two radial protrusions in the circumferential direction and communicating with each other through the runner.
Description
Technical Field
The present invention relates to a liquid composite bushing for a vehicle, in particular a rail vehicle.
Background
Hydraulic bushings are a component widely used in vehicles (e.g., automobiles and railway vehicles), and are mainly mounted on a suspension or a bogie of the vehicle for buffering vibration and impact to improve the stability and safety of the running of the vehicle.
Chinese patent document CN108150536a discloses a hydraulic bushing. The hydraulic bushing comprises a mandrel, a first fluid sleeved outside the mandrel, and an outer sleeve tightly sleeved outside the first fluid. 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 formed on the first rubber body in a radial opposite mode, wherein the grooves and the outer sleeve enclose a flow channel, and the two liquid cavities are communicated through the flow channel. By means of the flowability between the hydraulic fluid in the two fluid chambers, the stiffness of the hydraulic bushing can be adjusted, so that an improved stability of the vehicle in driving, in particular when the vehicle is cornering, is achieved.
However, in the above-mentioned hydraulic bushing, its structure is complicated, the number of parts is very large, the manufacturing cost is high, and the installation is inconvenient, and the application sealing requirement is high. In addition, the two ends of the outer sleeve are sealed by the sealing assemblies, so that the sealing cost is high.
Therefore, it is desirable to provide a liquid composite bushing that has a simple structure, can simplify the number of parts, is convenient to install, and can ensure a sealing effect.
Disclosure of Invention
Aiming at the technical problems, the invention aims to provide a novel liquid composite bushing, the structure of which can remarkably reduce the number of parts and simplify a hydraulic mechanism. Meanwhile, the liquid composite bushing can ensure that the liquid composite bushing has good rigidity changing performance and good sealing effect. Furthermore, the special structure of the mandrel can provide secondary stiffness and a stopping effect in the radial direction.
To this end, according to the invention, there is provided a liquid composite bushing comprising: a mandrel; the rubber body is sleeved on the periphery of the mandrel, and two radial protrusions extending in the circumferential direction are formed on the rubber body in a radial opposite mode; two runner bodies which are respectively sleeved on the rubber body and are positioned at the outer sides of the radial protrusions in the axial direction, wherein a runner for hydraulic fluid is constructed on the outer surface of the runner bodies; and a jacket which is tightly sleeved on the radial outer side of the runner body; wherein the rubber body, the runner body and the jacket together define two liquid chambers for containing hydraulic fluid, the two liquid chambers being located between the two radial protrusions in the circumferential direction and communicating with each other through the runner.
In a preferred embodiment, the flow passage is provided on an outer surface of the flow passage body, and both ends of the flow passage extend to two diametrically opposite positions on an axial end face of the flow passage body facing the liquid chamber, respectively, so as to form flow passage ports communicating with the liquid chamber, respectively.
In a preferred embodiment, the flow channel is arranged in a smooth curve on the spreading plane of the flow channel body, and the curvature radius of the smooth curve is set to be not less than 48mm.
In a preferred embodiment, the flow passage is provided to extend in a circumferential direction of the flow passage body, and flow passage ports at both end portions of the flow passage are provided to extend in an axial direction to communicate with the liquid chamber.
In a preferred embodiment, a filling hole for filling the hydraulic fluid into the fluid chamber is provided in a side wall of the outer jacket.
In a preferred embodiment, the mandrel is configured as a stepped shaft with a central boss, and the rubber body is integrally provided with the central boss of the mandrel by vulcanization.
In a preferred embodiment, the diameter of the intermediate boss remains unchanged in the axial direction.
In a preferred embodiment, a raised portion is provided between two of the radial projections in the circumferential direction of the rubber body, the raised portion having a maximum outer diameter smaller than the outer diameter of the radial projections.
In a preferred embodiment, the intermediate boss is configured such that its diameter decreases and then increases from both ends to the middle in the axial direction, and the rubber body is adaptively vulcanized on the outer peripheral surface of the intermediate boss.
In a preferred embodiment, a convex portion is formed in an axial middle portion of the intermediate boss, the convex portion having a diameter larger than a maximum outer diameter of the intermediate boss at both sides in the axial direction.
In a preferred embodiment, the included angle of the outer peripheral surfaces of both sides at the diameter turning point of the intermediate boss is set to be in the range of 0 ° -90 °, and the diameter turning point of the intermediate boss is rounded transition treated.
In a preferred embodiment, the inner wall of the flow channel body is configured to be able to adapt to the peripheral structure of the intermediate boss.
Compared with the prior art, the invention has the advantages that:
the structure of the liquid composite bushing according to the invention can remarkably reduce the number of parts and simplify the hydraulic mechanism. Meanwhile, the liquid composite bushing can ensure that the liquid composite bushing has good radial variable stiffness performance and good sealing performance. In addition, the secondary radial rigidity can be provided by the arched portion constructed on the rubber body, and the secondary axial rigidity and the stopping effect in the radial direction can be provided by the special structure of the mandrel. The liquid composite bushing has the advantages of simple structure, convenient installation, convenient sealing and good sealing effect, and in addition, the cost of production, installation and maintenance is low.
Drawings
The present invention will be described below with reference to the accompanying drawings.
FIG. 1 illustrates the structure of a liquid composite liner according to one embodiment of the invention.
Fig. 2 is a cross-sectional view taken along line A-A in fig. 1.
FIG. 3 is a schematic illustration of the jacket in the liquid composite liner removed to show the configuration of the liquid outlet chamber and radial projections.
Fig. 4 shows a structure of a flow channel on a flow channel body in the liquid composite liner shown in fig. 1.
FIG. 5 shows another configuration of the flow channels on the flow channel body in the liquid composite liner of FIG. 1
Fig. 6 shows a structure of a liquid composite liner according to another embodiment of the present invention.
In the present application, all of the figures are schematic drawings which are intended to illustrate the principles of the application only and are not to scale.
Detailed Description
The invention is described below with reference to the accompanying drawings. The terms "axial" and "radial" herein refer to the horizontal and vertical directions in fig. 1, respectively.
Fig. 1 shows the structure of a liquid composite liner 100 according to one embodiment of the invention. As shown in fig. 1, the liquid composite liner 100 includes a mandrel 110. The mandrel 110 is typically a preform, and in the embodiment shown in fig. 1, the mandrel 110 is configured as a stepped shaft with an intermediate boss, the diameter of which remains unchanged in the axial direction. Both ends of the mandrel 110 may be connected to a bogie frame of a rail train, for example.
According to the present invention, the liquid composite liner 100 further includes a rubber body 120. As shown in fig. 1 and 2, the rubber body 120 is sleeved on the outer circumference of the mandrel 110. In one embodiment, the rubber body 120 is integrally provided with the mandrel 110 by vulcanization. In the axial middle of the rubber body 120, two radial projections 121 are formed, which extend in the circumferential direction, and the two radial projections 121 are preferably configured to be radially opposed. Two sleeve-shaped runner bodies 130 are sleeved on the radial outer side of the rubber body 120, and the two runner bodies 130 are sleeved on the rubber body 120 and are positioned on the axial outer side of the radial protrusion 121. An outer jacket 140 is provided on the radially outer side of the flow path body 130 in a compression-type manner. Thus, on the radially outer side of the rubber body 120, two fluid chambers 150 for receiving hydraulic fluid are defined by the two radial protrusions 121 on the rubber body 120, the two flow path bodies 130 and the outer jacket 140 together, the two fluid chambers 150 being radially opposed on the rubber body 120 and being located between the two radial protrusions 121 in the circumferential direction. According to the present invention, a flow passage 131 for hydraulic fluid is constructed on the outer circumferential surface of the flow passage body 130, and the two liquid chambers 150 communicate with each other through the flow passage 131.
For ease of understanding, FIG. 3 more clearly shows a schematic illustration of the configuration of the liquid discharge chamber 150 and radial projections 121 with the outer jacket 140 removed from the liquid composite liner.
Further, a liquid injection hole 141 for injecting hydraulic fluid is formed in outer jacket 140. The filling hole 141 is provided in a side wall region of the outer jacket 140 located in the liquid chamber 150. When in installation, the liquid injection hole 141 is correspondingly communicated with the liquid cavity 150. During application, hydraulic fluid is injected into fluid chamber 150 using injection port 141. After the injection is completed, the injection hole 141 may be blocked, for example, by a plug (not shown).
Fig. 4 shows the structure of the flow path body 130. As shown in fig. 4, the flow path body 130 is configured in a sleeve shape. The flow channel 131 is disposed on an outer surface of the flow channel body 130. Preferably, the flow channel 131 is disposed in a smooth curve on the development plane of the flow channel body 130, and the radius of curvature of the smooth curve is set to be not less than 48mm. This structural arrangement of the runner body 131 can be particularly advantageous for exerting the flow performance of the hydraulic fluid in the runner, and for ensuring the rigidity variation performance of the liquid composite liner 100. Both ends of the flow channel 131 extend to two diametrically opposite positions on the axial end face of the flow channel body 130 facing the liquid chamber 150, respectively, so that flow channel ports 132 communicating with the liquid chamber 150 are formed, respectively. When installed, the respective flow ports 132 of the two flow bodies 130 are axially opposed to each other.
In one embodiment, the flow channels may also be provided as elongate straight flow channels. As shown in fig. 5, the flow passage 331 is provided at an outer circumferential surface of the flow passage body 330, and extends in a circumferential direction of the flow passage body 330. The two ends of the flow channel 331 are respectively provided with a groove extending to the axial end face of the flow channel body 330 towards the liquid cavity 150 along the axial direction, the two grooves are opposite in the radial direction of the flow channel body 330, and the grooves serve as flow channel ports communicated with the liquid cavity 150. The flow passage is also capable of communicating with both fluid chambers 150, thereby exhibiting the flow properties of the hydraulic fluid within the flow passage.
When the rail train runs in a straight-line section snakelike-resistant running stage, the wheel pair can bear high-frequency vibration, and when the rail train runs in a low-speed curve, the rim of the wheel pair can be abutted against the steel rail, and the vibration frequency is obviously reduced. Under the two conditions, the movement of the wheels drives the mandrel 110 and the sleeve 140 to move relatively, so that the liquid cavity at the front and the liquid cavity at the rear expand and contract respectively. In this way, hydraulic fluid can flow between the two fluid chambers 150 through the flow passage 131, thereby adjusting the radial stiffness of the fluid composite liner 100 accordingly, so that the train keeps running stably.
Meanwhile, the rubber body 120 is in flexible contact with the inner circumferential surface of the flow path body 130, providing a varying displacement in the radial direction, thereby providing a varying stiffness effect in the radial direction. Further, a raised portion 122 is provided in the middle of the rubber body 120, the raised portion 122 being located between two radial protrusions 121 in the circumferential direction, and the maximum outer diameter of the raised portion 122 being set smaller than the outer diameter of the radial protrusions 121. The arched portion 122 can provide secondary radial stiffness.
Fig. 6 shows a structure of a liquid composite liner 200 according to another embodiment of the present invention. As shown in fig. 6, the liquid composite liner 200 includes a mandrel 210. The mandrel 210 is typically a preform, and in the embodiment shown in fig. 6, the mandrel 210 is configured as a stepped shaft with intermediate bosses configured such that the diameter thereof decreases and then increases from both ends to the middle in the axial direction. A convex portion 211 is formed at an axially middle position of the middle boss, a diameter of the convex portion 211 is larger than a maximum diameter of the middle boss at both sides in the axial direction, and the convex portion 211 can provide secondary rigidity in the axial direction. The two ends of the mandrel 210 may be connected to a bogie frame of a rail train, for example.
According to the present invention, the rubber body 220 is provided in the circumferential direction of the middle boss of the mandrel 210 to be adapted to the outer circumferential structure of the middle boss, so that the rubber body 220 is provided on the outer circumferential surface of the middle boss in conformity with the structure of the middle boss. In one embodiment, the rubber body 220 is integrally provided with the mandrel 210 by vulcanization. Two radial projections extending in the circumferential direction are formed on the rubber body 220, which are preferably configured to be radially opposite. Two sleeve-shaped runner bodies 230 are arranged on the radial outer side of the rubber body 220, and the two runner bodies 230 are sleeved on the axial outer side of the radial protrusion at intervals along the axial direction. An outer jacket 240 is provided on the radially outer side of the flow path body 230 in a compression-type manner. Thus, on the radially outer side of the rubber body 220, two fluid chambers 250 for receiving hydraulic fluid are defined by two radial projections on the rubber body 220, two flow channel bodies 230 and an outer jacket 240 together, the two fluid chambers 250 being radially opposite on the rubber body 220 and being located between the two radial projections in the circumferential direction. According to the present invention, a flow passage 231 for hydraulic fluid is constructed on the outer circumferential surface of the flow passage body 230, and the two liquid chambers 250 communicate with each other through the flow passage 231.
In this embodiment, the diameter turning point of the middle boss is located axially outside the axially inner end face of the flow channel body 230. The included angle beta of the outer peripheral surfaces of both sides at the diameter turning point of the intermediate boss is set to be in the range of 0 deg. -90 deg.. Meanwhile, in order to avoid fatigue damage caused by stress concentration and improve fatigue life, the diameter turning point of the middle boss is subjected to fillet transition treatment. Here, the diameter turning point of the middle boss refers to a node point where the middle boss is gradually decreased from two axial ends to the middle part and gradually increased. In this way, the compression seal of the runner body 230 to the rubber body 220 is facilitated, so that the tightness of the liquid cavity 250 is ensured.
Likewise, a liquid injection hole 241 for injecting hydraulic fluid is formed in the outer jacket 240. The filling hole 241 is provided in a side wall region of the outer jacket 240 located in the liquid chamber 250. When in installation, the liquid injection hole 241 is correspondingly communicated with the liquid cavity 250. During application, hydraulic fluid is injected into the fluid chamber 250 using the injection port 241. After the injection is completed, the injection hole 241 may be blocked, for example, by a plug (not shown).
As shown in fig. 6, the flow channel body 230 is configured to be substantially sleeve-shaped, and an inner wall of the flow channel body 230 is configured to be able to adapt to an outer peripheral structure of the mandrel 210, that is, an inner diameter of the flow channel body 230 is configured to gradually decrease from one axial end face to the other axial end face. And, an angle α between an end surface of the flow path body 230 contacting the rubber body 220 and an outer surface of the flow path body 230 is set to be in a range of 0 ° -90 °. Meanwhile, in order to avoid fatigue damage caused by stress concentration, in order to improve fatigue life, a corner transition treatment is performed at a turning point of the inner surface of the flow channel body 230. The flow channel 231 is disposed on an outer surface of the flow channel body 230. Preferably, the flow channel 231 is disposed in a smooth curve on the spreading plane of the flow channel body 230, and the radius of curvature of the smooth curve is set to be not less than 48mm. This structural arrangement of the flow passage 231 can be particularly advantageous in exerting the flow performance of the hydraulic fluid in the flow passage, and in ensuring the rigidity variation performance of the liquid composite liner 200. Both ends of the flow channel 231 extend to two diametrically opposite positions on the axial end face of the flow channel body 230 facing the liquid chamber 250, respectively, thereby forming the flow channel port 232 communicating with the liquid chamber 250. The respective flow ports 232 of the two flow path bodies 230 are axially opposite to each other. In an embodiment not shown, the flow channel may also be provided as an elongated straight flow channel, which is likewise capable of communicating with both fluid chambers 150, thereby exerting the flow properties of the hydraulic fluid in the flow channel.
Similarly, when the rail train is in a straight-line anti-serpentine running stage, the wheel set can bear high-frequency vibration, and when the rail train passes through a curve at a low speed, the rim of the wheel set can be abutted against the steel rail, and the vibration frequency is obviously reduced. Under the two conditions, the movement of the wheels drives the mandrel 210 and the outer sleeve 240 to move relatively, so that the liquid cavity at the front and the liquid cavity at the rear expand and contract respectively. In this way, hydraulic fluid can flow between the two fluid chambers 250 through the flow passage 231, thereby adjusting the radial stiffness of the fluid composite liner 200 accordingly, so that the train keeps running stably.
Meanwhile, the rubber body 220 is in flexible contact with the inner circumferential surface of the flow path body 230, providing a varying displacement in the radial direction, thereby providing a varying stiffness effect in the radial direction.
According to the liquid composite bushing, the number of parts can be remarkably reduced, a hydraulic mechanism is simplified, and meanwhile, the liquid composite bushing can be guaranteed to have good radial rigidity changing performance. In addition, the secondary radial rigidity can be provided by the arched portion constructed on the rubber body, and the secondary axial rigidity and the stopping effect in the radial direction can be provided by the special structure of the mandrel. The liquid composite bushing has the advantages of simple structure, convenient installation, convenient sealing and good sealing effect, and in addition, the cost of production, installation and maintenance is low.
Finally, it should be noted that the above description is only of a preferred embodiment of the invention and is not to be construed as limiting the invention in any way. Although the invention has been described in detail with reference to the foregoing embodiments, it will be apparent to those skilled in the art that modifications may be made to the techniques described in the foregoing examples, or equivalents may be substituted for elements thereof. Any modification, equivalent replacement, improvement, etc. made within the spirit and principle of the present invention should be included in the protection scope of the present invention.
Claims (5)
1. A liquid composite liner comprising:
a mandrel;
the rubber body is sleeved on the periphery of the mandrel, and two radial protrusions extending in the circumferential direction are formed on the rubber body in a radial opposite mode;
Two runner bodies which are respectively sleeved on the rubber body and are positioned at the outer sides of the radial protrusions in the axial direction, wherein a runner for hydraulic fluid is constructed on the outer surface of the runner bodies; and
An outer sleeve sleeved on the radial outer side of the runner body in a pressing mode;
wherein the rubber body, the runner body and the jacket together define two liquid chambers for containing hydraulic fluid, the two liquid chambers are circumferentially located between the two radial protrusions and are communicated with each other through the runners,
The two ends of the flow channel extend to two diametrically opposite positions on the axial end face of the flow channel body facing the liquid cavity so as to form flow channel ports communicated with the liquid cavity respectively, the flow channel extends along the circumferential direction of the flow channel body, the flow channel ports at the two ends of the flow channel extend along the axial direction to be communicated with the liquid cavity,
The mandrel is configured as a stepped shaft having a middle boss configured such that its diameter is gradually decreased and then gradually increased from both axial ends toward the middle, the rubber body is adaptively vulcanized on an outer circumferential surface of the middle boss, and a convex portion having a diameter larger than a maximum outer diameter of the middle boss at both axial sides is formed in an axial middle portion of the middle boss.
2. The liquid composite liner according to claim 1, wherein the flow channel is provided in a smooth curve on a development plane of the flow channel body, and a radius of curvature of the smooth curve is set to be not less than 48mm.
3. A liquid composite bushing according to claim 1 or 2, wherein a filling hole for filling hydraulic fluid into the liquid chamber is provided in a side wall of the outer jacket.
4. A liquid composite bushing according to claim 1 or 2, wherein the included angle of the outer peripheral surfaces of both sides at the diameter turning point of the intermediate boss is set to be in the range of 0 ° -90 °, and the diameter turning point of the intermediate boss is rounded.
5. The liquid composite liner according to claim 1 or 2, wherein the inner wall of the flow channel body is configured to be able to fit the peripheral structure of the intermediate boss.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201910414300.7A CN110185735B (en) | 2019-05-17 | 2019-05-17 | Liquid composite lining |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201910414300.7A CN110185735B (en) | 2019-05-17 | 2019-05-17 | Liquid composite lining |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN110185735A CN110185735A (en) | 2019-08-30 |
| CN110185735B true CN110185735B (en) | 2024-07-23 |
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| Application Number | Title | Priority Date | Filing Date |
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| CN201910414300.7A Active CN110185735B (en) | 2019-05-17 | 2019-05-17 | Liquid composite lining |
Country Status (1)
| Country | Link |
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| CN (1) | CN110185735B (en) |
Families Citing this family (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN114251409A (en) * | 2021-12-01 | 2022-03-29 | 株洲时代新材料科技股份有限公司 | Saddle-shaped rubber hydraulic composite node and assembling method thereof |
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| CN105501242A (en) * | 2015-12-01 | 2016-04-20 | 唐山轨道客车有限责任公司 | Rubber node, power bogie and rail vehicle |
| CN205273076U (en) * | 2015-12-10 | 2016-06-01 | 广州汽车集团股份有限公司 | Lower swing arm assembly and have its vehicle |
| 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 |
| CN210484496U (en) * | 2019-05-17 | 2020-05-08 | 株洲时代新材料科技股份有限公司 | Liquid composite bushing |
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|---|---|
| CN110185735A (en) | 2019-08-30 |
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