CN108150591A - A kind of seal assembly and hydraulic bushing for hydraulic bushing - Google Patents

A kind of seal assembly and hydraulic bushing for hydraulic bushing Download PDF

Info

Publication number
CN108150591A
CN108150591A CN201611166402.4A CN201611166402A CN108150591A CN 108150591 A CN108150591 A CN 108150591A CN 201611166402 A CN201611166402 A CN 201611166402A CN 108150591 A CN108150591 A CN 108150591A
Authority
CN
China
Prior art keywords
rubber
seal assembly
peak potion
mandrel
hydraulic bushing
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.)
Granted
Application number
CN201611166402.4A
Other languages
Chinese (zh)
Other versions
CN108150591B (en
Inventor
罗旦
邹波
丁行武
卜继玲
张亚新
刘建勋
乔·格罗斯
王涛
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Zhuzhou Times New Material Technology Co Ltd
Original Assignee
Zhuzhou Times New Material Technology Co Ltd
Priority date (The priority date 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 date listed.)
Filing date
Publication date
Application filed by Zhuzhou Times New Material Technology Co Ltd filed Critical Zhuzhou Times New Material Technology Co Ltd
Publication of CN108150591A publication Critical patent/CN108150591A/en
Application granted granted Critical
Publication of CN108150591B publication Critical patent/CN108150591B/en
Active legal-status Critical Current
Anticipated expiration legal-status Critical

Links

Classifications

    • 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
    • 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
    • F16F13/14—Units of the bushing type, i.e. loaded predominantly radially
    • F16F13/1481—Units of the bushing type, i.e. loaded predominantly radially characterised by features of plastic springs, e.g. presence of cavities or stiffeners; characterised by features of flexible walls of equilibration chambers, i.e. membranes
    • 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
    • F16F13/14—Units of the bushing type, i.e. loaded predominantly radially
    • 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
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C32/00—Bearings not otherwise provided for
    • F16C32/06—Bearings not otherwise provided for with moving member supported by a fluid cushion formed, at least to a large extent, otherwise than by movement of the shaft, e.g. hydrostatic air-cushion bearings
    • F16C32/0629—Bearings not otherwise provided for with moving member supported by a fluid cushion formed, at least to a large extent, otherwise than by movement of the shaft, e.g. hydrostatic air-cushion bearings supported by a liquid cushion, e.g. oil cushion
    • F16C32/0633—Bearings not otherwise provided for with moving member supported by a fluid cushion formed, at least to a large extent, otherwise than by movement of the shaft, e.g. hydrostatic air-cushion bearings supported by a liquid cushion, e.g. oil cushion the liquid being retained in a gap
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B61—RAILWAYS
    • B61F—RAIL VEHICLE SUSPENSIONS, e.g. UNDERFRAMES, BOGIES OR ARRANGEMENTS OF WHEEL AXLES; RAIL VEHICLES FOR USE ON TRACKS OF DIFFERENT WIDTH; PREVENTING DERAILING OF RAIL VEHICLES; WHEEL GUARDS, OBSTRUCTION REMOVERS OR THE LIKE FOR RAIL VEHICLES
    • B61F5/00—Constructional details of bogies; Connections between bogies and vehicle underframes; Arrangements or devices for adjusting or allowing self-adjustment of wheel axles or bogies when rounding curves
    • B61F5/38—Arrangements or devices for adjusting or allowing self- adjustment of wheel axles or bogies when rounding curves, e.g. sliding axles, swinging axles
    • B61F5/42—Adjustment controlled by buffer or coupling gear
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B61—RAILWAYS
    • B61F—RAIL VEHICLE SUSPENSIONS, e.g. UNDERFRAMES, BOGIES OR ARRANGEMENTS OF WHEEL AXLES; RAIL VEHICLES FOR USE ON TRACKS OF DIFFERENT WIDTH; PREVENTING DERAILING OF RAIL VEHICLES; WHEEL GUARDS, OBSTRUCTION REMOVERS OR THE LIKE FOR RAIL VEHICLES
    • B61F5/00—Constructional details of bogies; Connections between bogies and vehicle underframes; Arrangements or devices for adjusting or allowing self-adjustment of wheel axles or bogies when rounding curves
    • B61F5/50—Other details
    • 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
    • F16F13/14—Units of the bushing type, i.e. loaded predominantly radially
    • F16F13/1445—Units of the bushing type, i.e. loaded predominantly radially characterised by method of assembly, production or treatment
    • 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
    • F16F13/14—Units of the bushing type, i.e. loaded predominantly radially
    • F16F13/1463—Units of the bushing type, i.e. loaded predominantly radially characterised by features of passages between working chambers
    • 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
    • F16F15/00—Suppression of vibrations in systems; Means or arrangements for avoiding or reducing out-of-balance forces, e.g. due to motion
    • F16F15/10—Suppression of vibrations in rotating systems by making use of members moving with the system
    • F16F15/16—Suppression of vibrations in rotating systems by making use of members moving with the system using a fluid or pasty material
    • F16F15/165—Sealing arrangements
    • 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
    • F16F9/00—Springs, vibration-dampers, shock-absorbers, or similarly-constructed movement-dampers using a fluid or the equivalent as damping medium
    • F16F9/32—Details
    • F16F9/43—Filling or drainage arrangements, e.g. for supply of gas
    • 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
    • F16F2222/00—Special physical effects, e.g. nature of damping effects
    • F16F2222/12—Fluid damping
    • 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
    • F16F2230/00—Purpose; Design features
    • F16F2230/06—Fluid filling or discharging

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Physics & Mathematics (AREA)
  • Acoustics & Sound (AREA)
  • Aviation & Aerospace Engineering (AREA)
  • Manufacturing & Machinery (AREA)
  • Combined Devices Of Dampers And Springs (AREA)
  • Moulds For Moulding Plastics Or The Like (AREA)
  • Sealing Devices (AREA)
  • Springs (AREA)

Abstract

The present invention relates to a kind of seal assemblies and hydraulic bushing for hydraulic bushing, seal assembly includes rigid support ring assemblies and the second rubber bodies, support ring assemblies have mounting ring and the bulge loop projected radially outward by the outer wall of mounting ring, second rubber bodies cladding bulge loop formula is set in the outside of mounting ring, the seal assembly can improve the axial rigidity of hydraulic bushing, and the purpose of the axial rigidity of hydraulic bushing is adjusted by changing the radial rigidity of seal assembly to realize.

Description

A kind of seal assembly and hydraulic bushing for hydraulic bushing
Cross reference to related applications
This application claims enjoy in the Chinese patent Shen of entitled " a kind of hydraulic bushing " submitted on December 02nd, 2016 The China for entitled " hydraulic bushing and the track train " that please be submitted on December 02nd, CN201611096400.2 and 2016 is specially The priority of profit application CN201611095592.5, all the contents of the application are herein incorporated by reference.
Technical field
The present invention relates to track train technical field, more particularly to a kind of seal assembly and hydraulic pressure for hydraulic bushing Bushing.
Background technology
The operation of track train can be simply divided into two states, the first is straight-going state, and second is negotiation of bends State.In the prior art, wheel is connected with bogie generally by means of rubber pivoted arm, so that in straight-going state, row Vehicle is travelled along rail fast and stable；In negotiation of bends state, train can be along the smooth steering of track.
In order to enable the train stable operation in straight-going state, rubber pivoted arm is usually configured with to larger rigidity Value.But this rubber pivoted arm with greater stiffness can cause in negotiation of bends state, the serious mill of wheel and track Damage, so as to increase the operation cost of train.
Invention content
Regarding to the issue above part or all of, the present invention propose a kind of seal assembly and hydraulic pressure for hydraulic bushing Bushing.After by the seal applications to hydraulic bushing of the present invention, the axial rigidity of hydraulic bushing can be greatly improved, To realize the purpose of the axial rigidity of hydraulic bushing is adjusted by changing the radial rigidity of seal assembly.
According to an aspect of the present invention, a kind of seal assembly for hydraulic bushing is provided, including：
Rigid support ring assemblies, support ring assemblies have mounting ring and are projected radially outward by the outer wall of mounting ring convex Ring,
Cladding bulge loop formula is set in second rubber bodies in the outside of mounting ring.In application process, which is set At the both ends of the mandrel of hydraulic bushing, so as to improve the axial rigidity of hydraulic bushing, while the rigidity of hydraulic bushing is increased Regulating power, to meet wider use demand.
In one embodiment, the radial thickness of the first end of mounting ring is more than the radial thickness of second end.In the sealing During component use, it can either ensure the rigidity of mounting ring by above-mentioned setting, moreover it is possible to place mounting ring and housing movement is dry It relates to.
In one embodiment, on the direction from first end to second end, the second rubber bodies have what is projected radially outward The the first rubber peak potion and third rubber peak potion of compartment setting, and formed between the first rubber peak potion and third rubber peak potion First allows bit space.After seal assembly is arranged on the mandrel of hydraulic bushing, first allows bit space can help to outside reduction The suffered resistance of motion of set so that housing is moved in certain amplitude relative to mandrel and is easier, so as to improve track column The excessively curved ability of vehicle flexibility.
In one embodiment, the second rubber bodies have the be arranged between the first rubber peak potion and third rubber peak potion Two rubber peak potions, the second rubber peak potion is opposite with bulge loop position, and radially protruding allows to first in bit space.The second rubber peak Portion can prevent housing relative to mandrel motion amplitude it is excessive the problem of.
In one embodiment, setting second allows bit space on the outer end face of the second end of the second rubber bodies, and second allows Bit space is configured to annular groove.Bit space is allowed to increase the excessively curved ability of track train flexibility by setting second.
In one embodiment, rigid first pad coaxial with mounting ring of clad type setting at the first rubber peak potion Ring.By setting the first gasket ring, while increasing the rigidity of seal assembly, sealing effect can be improved.
In one embodiment, it is set at the corresponding position of the first gasket ring in the first rubber peak potion radially outward convex The first protrusion gone out.Sealing effect is further increased by this set.
In one embodiment, it is embedded in rigid second gasket ring coaxial with mounting ring in third rubber peak potion.Pass through Second gasket ring is set, while increasing the rigidity of seal assembly, can more improve sealing effect.
In one embodiment, it is set at the corresponding position of the second gasket ring in third rubber peak potion radially outward convex The second protrusion gone out.Sealing effect is further increased by this set.
According to another aspect of the present invention, a kind of hydraulic bushing is provided, including：
Mandrel, mandrel have First terrace using by mandrel structure for interlude diameter more than both ends diameter ladder Axis,
The first rubber bodies being set on the outer wall of the interlude of mandrel, there are two compartments for setting in the first rubber bodies Distribution axially through sap cavity,
The sleeve being set on the outer wall of the first rubber bodies, set on the outer wall of sleeve it is fluted,
Above-mentioned seal assembly, the mounting ring of seal assembly are set in the both ends of mandrel,
The housing in the outside of sleeve and seal assembly is set in, housing forms to connect two liquid in groove with sleeve The runner of chamber.The hydraulic bushing causes train to have the flexibility of bigger during negotiation of bends, meanwhile, it can be so that train be being kept straight on In the process, stable operation.
Compared with prior art, the advantage of the invention is that：The rigidity of seal assembly axial direction with the structure is larger, and Rigidity radially is smaller, it is possible to apply on hydraulic bushing, to increase the axial rigidity of hydraulic bushing, and realize and pass through Change the rigidity of seal assembly to adjust the rigidity of hydraulic bushing.
Description of the drawings
The invention will be described in more detail below based on embodiments and refering to the accompanying drawings.Wherein：
Fig. 1 schematically shows the stereogram of hydraulic bushing according to an embodiment of the invention；
Fig. 2 is the A-A sectional views from Fig. 1；
Fig. 3 is the B-B sectional views from Fig. 1；
Fig. 4 is the C-C sectional views from Fig. 1；
Fig. 5 shows the stereogram of main spring；
Fig. 6 shows the left view of main spring；
Fig. 7 shows the sectional view of another embodiment of main spring；
Fig. 8 shows the front view of sleeve；
Fig. 9 shows the right view of sleeve；
Figure 10 shows the sectional view for the housing for not carrying out flange processing；
Figure 11 shows the stereogram of seal assembly；
Figure 12 is the D-D sectional views from Figure 11；
Figure 13 is the E-E sectional views from Figure 11；
Figure 14 shows the stereogram of support ring assemblies；
Figure 15 is enlarged drawing at the F from Figure 12；
Figure 16 shows the stereogram of the first ligand；
In the accompanying drawings, identical component uses identical reference numeral.Attached drawing is not according to practical ratio.
Specific embodiment
The present invention will be further described with reference to the accompanying drawings.
As shown in Figure 1, hydraulic bushing 1 includes the housing 200 of main spring 100 and tubular.As shown in Figures 2 and 3, main spring 100 has There are mandrel 101, the first rubber bodies 102 and sleeve 103.First rubber bodies 102 are set on the outer wall of mandrel 101.In the first rubber Two sap cavities 104 are set on colloid 102, each sap cavity 104 is the through-hole axially penetrated through along the first rubber bodies 102, and Radially, two 104 relative type motors of sap cavity are spaced apart first rubber bodies 102.Sleeve 103 is set in the first rubber bodies 102 On outer wall.Meanwhile fluted 110 are set on the wall of sleeve 103.Wherein, main spring 100 is arranged in the inner cavity of housing 300, from And housing 300 forms runner 105 with sleeve 103 at groove 110, for connecting two sap cavities 104.
When the hydraulic bushing 1 is mounted on track train, wherein, the mandrel 101 of hydraulic bushing 1 and turning for track train It is connected to the framework of frame, and housing 300 is connect with the registration arm of wheel, simultaneously so that two sap cavities 104 are in the row of track train Front and rear on into direction to be oppositely arranged, it is, using current of traffic to refer to, a sap cavity 104 is located at front, and another It is located behind.In track train turning process, wheel occur turn to simultaneously registration arm is driven to move, and actuate housing 300 relative to Mandrel 101 moves, the steering of bogie being then connected with mandrel 101 and the negotiation of bends of train.In the process so that One sap cavity 104 of hydraulic bushing 1 becomes smaller when being squeezed, another sap cavity 104 is stretched and becomes larger, because being squeezed And the liquid in the sap cavity 104 to become smaller can be flowed by runner 105 and is stretched in the sap cavity 104 to become larger, to comply with core The relative motion and steering of axis 101 and housing 300.So as to, during train curve travels, hydraulic bushing 1 according to the present invention The components such as rubber pivoted arm than in the prior art have the flexibility of bigger, so that wheel can be turned to more swimmingly, so as to reduce The abrasion of wheel and track.In track train straight-going state, the extruding force that sap cavity 104 is subject to is smaller, sap cavity 104 and runner Liquid in 105 hardly flows.This causes the rigidity of hydraulic bushing 1 relative to components such as rubber pivoted arms of the prior art Rigidity does not have significant change, and train is enabled to keep stable operation.The hydraulic bushing 1 has good stiffness tuning as a result, Ability meets track train and more stably keeps straight on more flexible excessively curved purpose.
In one embodiment, as shown in Fig. 2, mandrel 101 has First terrace 107, during mandrel 101 is configured to Section diameter is more than the multi-diameter shaft of both ends diameter.First rubber bodies 102 are arranged on the interlude of mandrel 101.At one preferably Embodiment in, the interlude of mandrel 101 projects radially outward, protrude part contour line be arc-shaped.It is, mandrel 101 interlude is configured to drum type.First rubber bodies 102 are set on interlude.Also, the madial wall of the first rubber bodies 102 The interlude for adapting to drum type formula is connect with mandrel 101, and the contour line of the lateral wall of the first rubber bodies 102 is straight line on section To be connect with 103 formula of sleeve.By this set on the one hand, 101 and first rubber bodies of mandrel, 102 contact position is avoided Stress concentration improves the service life of hydraulic bushing 1.On the other hand, the amplitude of oscillation of the mandrel 101 relative to housing 200 is improved, The deflection angle of mandrel 101 is increased, so as to finally improve the excessively curved ability of track train flexibility.
Since the interlude of mandrel 101 is configured to drum type structure, also, in the axial direction, between sap cavity 104 and mandrel 101 The first rubber bodies 102 thickness is substantially the same everywhere other than axial end portion.So as to, in the axial direction, 104 middle part of sap cavity Width be less than both ends width.It can effectively avoid the problem that sap cavity 104 is easily torn at axial both ends by this set, from And improve the service life of hydraulic bushing 1.In addition, this setup also improves being quick on the draw for the liquid in sap cavity 104 Degree assists the excessively curved ability of train flexibility so as to increase hydraulic bushing 1.
As shown in figs. 4 and 6, sap cavity 104 is along the circumferentially distributed of the first rubber bodies 102.It is, on radial section, Sap cavity 104 extends in arcuation.In addition, limit protrusion 106 is set in the radial direction middle of sap cavity 104, so that, sap cavity 104 At circumferential both ends, the radial dimension of section is more than the radial dimension of interlude, it is preferable that limit protrusion 106 is positioned close to mandrel On the inner wall of the sap cavity 104 of 101 sides.101 corresponding housing 200 of mandrel move when, limit protrusion 106 be possible at first with sap cavity The madial wall contact of 104 close sleeve 103, plays the role of stop.Especially when overload, limit protrusion can be passed through 106 top resists the madial wall of the close sleeve 103 of sap cavity 104 and prevents 101 corresponding 200 transition shift of housing of mandrel, So as to ensure the safety in utilization of hydraulic bushing 1.Meanwhile sap cavity 104 is larger in the radial dimension of circumferential both ends section, so as to be formed It is larger to allow bit space, so that the madial wall of the close mandrel 101 of sap cavity 104 and the madial wall close to sleeve 103 are not easy It is torn, so as to improve the service life of hydraulic bushing 1.
In addition, on radial section, each section of sap cavity 104 smoothly transits, especially, structure at the circumferential both ends of sap cavity 104 It makes as circular shape.The problem of stress concentration of sap cavity 104 is effectively improved by this set, so as to further improve hydraulic pressure The service life of bushing 1.
In one embodiment, mandrel 101, the first rubber bodies 102 and sleeve 103 are fixed together by vulcanization, with shape Into main spring 100, as shown in Figure 5.
According to another embodiment of the invention, mandrel 101 is it is so structured that split structure.For example, as shown in fig. 7, Mandrel 101 includes first part 108 and second part 109.Wherein, first part 108 is configured to multi-diameter shaft.Second part 109 It is configured to tubular and is set on the outer wall of first part 108.It is simple in structure also, in order to easy to process, first part 108 Outside wall surface and the internal face of second part 109 be configured to cylindric face.And the outside wall surface of second part 109 can be according to not With needs and be configured to cylindric face or arch arcuation face.It, can in the production process of hydraulic bushing 1 according to this structure To individually produce first part 108 and second part 109, then only by second part 109, the first rubber bodies 102 and sleeve 103 It fits together to form assembly, finally assembles up to form main spring 100 by assembly and first part 108 again.Due to core The size of axis 101 is often larger (such as 84 millimeters of diameter, 226 millimeters of length), and cause the production of main spring 100 highly difficult and Producing cost is high.However, according to the present embodiment, do not need to operate entire mandrel 101 when producing main spring 100, but only It needs to operate second part 109 (for example, length is 70 millimeters), this greatly reduces production difficulty and reduces production expense With.In addition, during by vulcanizing the main spring 100 of processing, since mandrel 101 is split structure, therefore only to second part 109th, the first rubber bodies 102 and sleeve 103 vulcanize, so as to effectively reduce vulcanization heating time, so as to save vulcanization Processing cost.Simultaneously as the size of mandrel 101 for needing to vulcanize is greatly reduced, so as to which the sulphur of main spring 100 is substantially improved Change effect, improve the service life of hydraulic bushing 1.
Gap 111 is provided on the end face of sleeve 103, to be connected with groove 110, as figure 9.One end of gap 111 It is connected with groove 110, the other end is connected with sap cavity 104.Preferably, groove 110 is spirally arranged on the outer wall of sleeve 103, As shown in Figure 8.The length of groove 110 can suitably be increased by this set, and easily the length of runner 105 is carried out It adjusts, to meet design requirement.
It is further preferred that the cross-sectional configuration of groove 110 is rectangular configuration, sectional dimension can be according to different needs It is configured.It is this to have the advantages of simple structure and easy realization.For example, the section of groove 110 can be structured as square, and its section side Length can be arranged between 2 millimeters to 5 millimeters.It should be noted that the cross sectional shape of groove 110 may be configured to other knots Structure, for example, " V " shape, trapezoidal, " u "-shaped or semicircle etc..The length of groove 110 can be arranged between 2-5 meters.For example, runner 105 length is set as 3.4 meters.It should be noted that the length of groove 110 can be set as different according to actual needs Size.On the outer wall of sleeve 103, the helix angle of groove 110 can be 3 to 10 degree.
Again as shown in Fig. 2, being arranged seal assembly 300 respectively at the both ends of staged mandrel 101, to realize 105 He of runner The sealing of 104 grade fluid passages of sap cavity.
In one embodiment, as shown in Figure 11,12 and 13, seal assembly 300 have it is rigid support ring assemblies 301, Second rubber bodies 302 and the first ligand 305.Wherein, support ring assemblies 301 have mounting ring 303 and bulge loop 304, such as Figure 14 It is shown.Mounting ring 303 is substantially cylindrical in shape, for being socketed in the outer wall of mandrel 101.Bulge loop 304 is arranged on the outer of mounting ring 303 It on wall and projects radially outward, and in axial direction, bulge loop 304 is approximately located at the axial middle of mounting ring 303.Second rubber bodies 302 are set in the outside of mounting ring 303 and coat bulge loop 304.It is, bulge loop 304 is inserted into the second rubber bodies 302.Tool Body, the axial inner ends face of the second rubber bodies 302 and the First terrace 107 of the axial end face of sleeve 103 and mandrel 101 connect It touches, so as to achieve the effect that axial seal runner 105 and sap cavity 104.
The radial thickness of the first end of mounting ring 303 is more than the radial thickness of second end.It is it should be noted that described herein " first end " and " axial inner ends " in the same end, and " second end " with " first end " on the contrary, and being in " axial outer end " The same end.It is, when seal assembly 300 are assembled, first end is close to the First terrace 107 of mandrel 101.Separately Outside, between the inclined formula of the outer wall of mounting ring 303 is set, and inclined slope is 0.75 to 0.9, for example, mounting ring 303 The inclined slope of outer wall is 0.85.By this set, while ensureing to increase the axial rigidity of hydraulic bushing 1, not Influence the relative motion of housing 300 and mandrel 101.
First ligand 305 is arranged in the second rubber bodies 302, and from the axial inner ends face upper edge of the second rubber bodies 302 Axial male extension, for (as seen from Figure 2) sealed with the second ligand 112 being arranged in the first rubber bodies 102 Cooperation contact, to avoid the connection of the sap cavity 104 in same axial end face.By the way that seal assembly 300 is set not only to realize The sealing of flow channel for liquids 105 and sap cavity 104 in hydraulic bushing 1, and liquid is avoided on the sap cavity 104 in same axial end face Connection, ensureing liquid is passed in another sap cavity 104 from a sap cavity 104 by runner 105.In addition, the seal assembly 300 increase the axial rigidity of hydraulic bushing 1, the matching of the multi-direction rigidity of hydraulic bushing 1 are realized, so as to meet the need of client It will.So as to, the radial rigidity of hydraulic bushing 1 and the ratio of axial rigidity can be adjusted flexibly by adjusting seal assembly 300, from And optimize the performance of hydraulic bushing 1.
It should be noted that above-mentioned only describe the example that the first ligand 305 is raised structure.And the first cooperation Body 305 is also designed to female structure, and correspondingly, the second ligand 112 is configured to male structure, this setup It is equally reached the purpose that two sap cavities 104 of barrier connect in the same axial end face of the first rubber bodies 102.
In a preferred embodiment, as shown in figure 16, it is bowed convex that the first ligand 305, which is configured to radial section, Go out body, and the bowed circular arc of the first ligand 305 is towards extending in the second ligand 112.Correspondingly, the second ligand 112 are configured to female radial section as bowed body structure.It is further preferred that in the bowed circular arc of the first ligand 305 Prominent item 316 is set on face.Radially, which matches the bowed arc surface extension of the first ligand 305.It is logical It crosses the protrusion item 316 and plays better seal effect.In addition, he is 112 tight for above-mentioned first ligand, 305 and second cooperation It is close, on the basis of leakage is effectively prevent, stress concentration can be lowered.
On axial direction from inside to outside, the second rubber bodies 302 construct at least one rubber peak potion, with housing 200 Interference type coordinates, so as to achieve the purpose that axial seal.In a specific embodiment, two are formed in the second rubber bodies 302 A peak potion, both the first rubber peak potion 306 and third rubber peak potion 308.Wherein, the first rubber peak potion 306 and 200 interference type of housing Cooperation to ensure the sealing effect for runner 105, prevents liquid from passing through the gap between the second rubber bodies 302 and housing 200 It leaks out.Further, third rubber peak potion 308 and 200 interference type of housing coordinate, so as to be further ensured that and improve for The sealing effect of runner 105.
In the axial direction, third rubber peak potion 308 is located at the outside of the first rubber peak potion 306.Meanwhile without being fitted on housing When in 200 inner cavity, the diameter dimension of third rubber peak potion 308 is more than the diameter dimension of the first rubber peak potion 306.Preferably, The diameter of third rubber peak potion 308 is 6 to 10 millimeters bigger than the diameter of the first rubber peak potion 306.In assembling, seal assembly 300 It can be set by way of press fitting in the inner cavity of housing 200, and above-mentioned setting ensure that being smoothed out for assembling, while energy It is enough to form two seals in the axial direction, fully ensure that sealing effect.
First rubber peak potion 306 and the setting of 308 compartment of third rubber peak potion.Also, in the first rubber peak potion 306 and First is formd between three rubber peak potions 308 and allows bit space 309.During track train crosses bend, housing 200 relative to Mandrel 101 moves, and the second rubber bodies 302 can be squeezed, and bit space 309 is allowed to reduce 200 institute of housing by setting first The resistance of motion being subject to so that housing 200 is moved in certain amplitude relative to mandrel 101 and is easier, so as to improve track The excessively curved ability of train flexibility.
Second rubber peak potion 307, the second rubber peak are set between the first rubber peak potion 306 and third rubber peak potion 308 Portion 307 is formed at 304 position of bulge loop.Meanwhile second rubber peak potion 307 protrude into first and allow in bit space 309, and in nature Under state, the second rubber peak potion 307 has certain distance apart from housing 200.It is, the second rubber peak potion 307 not with outside Set 200 is in direct contact.Preferably, the second rubber peak potion 307 is apart from about 3 to 10 millimeters of housing 200, for example, can be 5 millis Rice.When housing 200 is bigger relative to 101 motion amplitude of mandrel, the second rubber peak potion 307 can resist housing 200 from And prevent motion amplitude from further increasing.First bit space 309 is allowed to be provided for mandrel 101 and the relative motion of housing 200 as a result, Certain space, meanwhile, the rigid bulge loop 304 at the second rubber peak potion 307 can also prevent motion amplitude excessive.In addition, Above-mentioned set-up mode can also improve the rigidity of seal assembly 300 relatively, so as to optimize the axial rigidity of hydraulic bushing 1.
Clad type sets the first gasket ring 310 at the first rubber peak potion 306.First gasket ring 310 be stiffening ring, and with dress It is set with 303 coaxial-type of ring.Meanwhile in the axial direction, the first gasket ring 310 is close to sleeve 103 and opposite with the end face of sleeve 103. Radially, the first gasket ring 310 is close to housing 200.By the way that the first gasket ring 310 is set to ensure that the second rubber bodies 302 radially The upper contact with housing 200 further improves the sealability of seal assembly 300.Preferably, in the first rubber peak potion 306 The first protrusion 311 projected radially outward is set at upper and 310 corresponding position of the first gasket ring, as shown in figure 15.This One protrusion 311 further increases the sealability of seal assembly 300, and ensures sealing effect.
Housing 200 includes outer body 201 and extension 202, as shown in Figure 2.Wherein, outer body 201 is configured to cylinder Shape, and be socketed on the outer wall of sleeve 103, and extension 202 is arranged on axial both ends and the outer body of outer body 201 201 are fixedly connected, and are configured to circular and axially extend internally.Outer body 201 and extension 202 are integral type structure Part as shown in Figure 10, and is contacted by press-loading process with seal assembly 300.Extension 202 define the first rubber bodies 102, The axial position of 300 grade components of sleeve 103 and seal assembly, ensure that seal assembly 300 and sleeve 103 are closely connected, so that it is guaranteed that Sealing effect.In addition, radially, inner wall distance support 301 certain distance of ring assemblies of extension 202 is (for example, 5 to 10 Millimeter).In housing 200 relative in 101 motion process of mandrel, the distance between extension 202 and support ring assemblies 301 can Rigid extension 202 is avoided to be connected on rigid support ring assemblies 301, so as to ensure that the flexibility of hydraulic bushing 1 is excessively curved The ability in road.
As shown in Figure 10, in process of production, second step face 203 is set on housing 200 so that the two of housing 200 The internal diameter size of section is held to be more than the internal diameter size of interlude.It is, the wall thickness at 200 interlude of housing is more than at the section of both ends Wall thickness.Extension 202 is formed at the section of both ends by being pressed.This set causes press fitting operation to become easy.Meanwhile third Inner wall of the rubber peak potion 308 not only with housing 200 contacts, but also is contacted with second step face 203, so as to improve sealing effect Fruit.In addition, it is embedded in the second gasket ring 313 in third rubber peak potion 308.Second gasket ring 313 is for stiffening ring and same with mounting ring 303 Axis is set.In the axial direction, the second gasket ring 313 is arranged between second step face 203 and extension 202.Radially, the second pad Ring 313 is close to housing 200.Also, the axial outer end face of the second gasket ring 313 is in direct contact with radial extension 202.Pass through this Kind setting further improves the sealability of seal assembly.
It is connected between the axial outer end face of second gasket ring 313 and the outer end face of radial direction by arc surface, it can from Figure 15 To find out.Contribute to carry out press fitting operation to housing 200 by this set, and ensure that extension 202 can be press-fit into place.
The second protrusion 314 projected radially outward is set in third rubber peak potion 308, as shown in figure 15.Second is convex Go out portion 314 between the second gasket ring 313 and housing 200, then improve the sealability of seal assembly 300 further.
Third protruding portion 315 is set on the axial inner ends face of the second rubber bodies 302, as shown in figure 15.Third protruding portion 315 between the second rubber bodies 302 and the First terrace 107 of mandrel 101, to ensure the sealing of auxiliary sap cavity 114.
In addition, in the second rubber bodies 302, it is additionally provided with second and allows bit space 312, as shown in figure 12.Second resigning is empty Between 312 be arranged on the axial outer end face of the second rubber bodies 302, and be configured to the annular groove of indent.This second allows bit space 312 Increase the radial deformation capabilities of seal assembly 300, which thereby enhance the excessively curved ability of flexibility of hydraulic bushing 1.
As shown in Figure 1, liquid injection hole 204 is set on housing 200.The liquid injection hole 204 is configured to logical on the wall of housing 200 Hole, and connected with runner 105.The liquid injection hole 204 has the advantages of simple structure and easy realization, and be easily achieved refueling operation.In addition, The sealed setting plug 205 at liquid injection hole 204, as shown in Figure 2.For example, plug 205 can be with sealed spiral shell with liquid injection hole 204 Line connects.
The edge face structure of first rubber bodies 102 has circumferentially distributed annular groove 113, as shown in Figure 5.First rubber bodies 102nd, the second rubber bodies 302, sleeve 103 and first coordinate 305 bodies to form auxiliary sap cavity 114 at annular groove 113, such as Fig. 3 It is shown.The auxiliary sap cavity 114 is arranged among sap cavity 104 and runner 105 and with both connecting.On the one hand, the auxiliary sap cavity 114 increase the liquid storage capacity of hydraulic bushing 1, improve the stiffness equivalent effect of hydraulic bushing 1.On the other hand, the auxiliary liquid Chamber 114 increases the safety in utilization of hydraulic bushing 1, even if for example, sap cavity 104 by block in the case of, in hydraulic bushing 1 The liquid in portion can still flow.
Main spring 100 is arranged on by way of press fitting in the inner cavity of housing 200.This mode can guarantee the close of runner 105 Envelope.According to the present invention, before not being pressed, the overall diameter of main spring 100 is 1.5-2.3 millimeters bigger than the interior diameter of housing 200.For example, The interior diameter design size of housing 200 isMillimeter, and the overall diameter of main spring 100 isMillimeter.It is set by this It puts and both can guarantee that main spring 100 is successfully pressed into housing 200, moreover it is possible to ensure the sealing between main spring 100 and housing 200.
In a preferred embodiment, sleeve 103 is made of nylon66 fiber.This setup utilization rate nylon66 fiber has The advantages of fatigue resistance and rigidity are higher, and heat resistance is preferable, while wearability is good improves the service life of hydraulic bushing 1.
For the description of the present application, abstract and claims, it is noted that singulative " one ", "the" etc. also includes plural form, unless expressly stated otherwise,.
Although by reference to preferred embodiment, invention has been described, in the situation for not departing from the scope of the present invention Under, various improvement can be carried out to it and component therein can be replaced with equivalent.Especially, it to be rushed as long as there is no structures Prominent, items technical characteristic mentioned in the various embodiments can be combined in any way.The invention is not limited in texts Disclosed in specific embodiment, but all technical solutions including falling within the scope of the appended claims.

Claims (10)

1. a kind of seal assembly for hydraulic bushing, which is characterized in that including：
Rigid support ring assemblies, the support ring assemblies have mounting ring and are projected radially outward by the outer wall of the mounting ring Bulge loop,
Coat the second rubber bodies that the bulge loop formula is set in the outside of the mounting ring.
2. seal assembly according to claim 1, which is characterized in that the radial thickness of the first end of the mounting ring is more than The radial thickness of second end.
3. seal assembly according to claim 1 or 2, which is characterized in that described on the direction from first end to second end Second rubber bodies have the first rubber peak potion and third rubber peak potion of compartment setting projected radially outward, and described the First is formd between one rubber peak potion and the third rubber peak potion and allows bit space.
4. seal assembly according to claim 3, which is characterized in that second rubber bodies, which have, is arranged on described first The second rubber peak potion between rubber peak potion and the third rubber peak potion, the second rubber peak potion and bulge loop position phase It is right, and radially protruding allows to described first in bit space.
5. the seal assembly according to claim 1 to 4, which is characterized in that in the outer end face of the second end of the second rubber bodies Upper setting second allows bit space, and described second allows bit space to be configured to annular groove.
6. the seal assembly according to any one of claim 3 to 5, which is characterized in that at the first rubber peak potion Clad type sets rigid first gasket ring coaxial with the mounting ring.
7. seal assembly according to claim 6, which is characterized in that in the described first pad in the first rubber peak potion The first protrusion projected radially outward is set at the corresponding position of ring.
8. the seal assembly according to any one of claim 3 to 7, which is characterized in that in the third rubber peak potion Embedded rigid second gasket ring coaxial with the mounting ring.
9. seal assembly according to claim 8, which is characterized in that in the described second pad in the third rubber peak potion The second protrusion projected radially outward is set at the corresponding position of ring.
10. a kind of hydraulic bushing, which is characterized in that including：
Mandrel, the mandrel have First terrace using by the mandrel structure for interlude diameter more than both ends diameter rank Terraced axis,
The first rubber bodies being set on the outer wall of the interlude of the mandrel, setting is there are two between in first rubber bodies Every formula distribution axially through sap cavity,
The sleeve being set on the outer wall of first rubber bodies, set on the outer wall of the sleeve it is fluted,
Seal assembly according to any one of claim 1 to 9, the mounting ring of the seal assembly are set in described The both ends of mandrel,
The housing in the outside of the sleeve and the seal assembly is set in, the housing is with the sleeve in the groove shape Into the runner for two sap cavities of connection.
CN201611166402.4A 2016-12-02 2016-12-16 Sealing assembly for hydraulic bushing and hydraulic bushing Active CN108150591B (en)

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
CN2016110964002 2016-12-02
CN2016110955925 2016-12-02
CN201611096400 2016-12-02
CN201611095592 2016-12-02

Publications (2)

Publication Number Publication Date
CN108150591A true CN108150591A (en) 2018-06-12
CN108150591B CN108150591B (en) 2020-07-14

Family

ID=59375728

Family Applications (18)

Application Number Title Priority Date Filing Date
CN201611161939.1A Pending CN108150587A (en) 2016-12-02 2016-12-15 A kind of electrolyte filling method of rail traffic hydraulic bushing
CN201621381050.XU Active CN206555347U (en) 2016-12-02 2016-12-15 A kind of track traffic hydraulic bushing
CN201611162812.1A Pending CN108150588A (en) 2016-12-02 2016-12-15 A kind of rail traffic hydraulic bushing
CN201611168201.8A Active CN108150595B (en) 2016-12-02 2016-12-16 Hydraulic bushing
CN201611166938.6A Active CN108150593B (en) 2016-12-02 2016-12-16 Hydraulic bushing
CN201611168146.2A Withdrawn CN108150594A (en) 2016-12-02 2016-12-16 A kind of hydraulic bushing
CN201611166402.4A Active CN108150591B (en) 2016-12-02 2016-12-16 Sealing assembly for hydraulic bushing and hydraulic bushing
CN201611174053.0A Active CN108150596B (en) 2016-12-02 2016-12-16 Hydraulic bushing
CN201611166343.0A Active CN108150589B (en) 2016-12-02 2016-12-16 Hydraulic bushing
CN201611166520.5A Active CN108150592B (en) 2016-12-02 2016-12-16 Hydraulic bushing
CN201611166346.4A Withdrawn CN108150590A (en) 2016-12-02 2016-12-16 A kind of hydraulic bushing
CN201611205646.9A Active CN108150597B (en) 2016-12-02 2016-12-23 Hydraulic bushing and rail train
CN201621423948.9U Active CN206555348U (en) 2016-12-02 2016-12-23 Hydraulic bushing and track train
CN201621425372.XU Active CN206361076U (en) 2016-12-02 2016-12-23 hydraulic bushing and track train
CN201611206851.7A Active CN108150536B (en) 2016-12-02 2016-12-23 Hydraulic bushing and rail train
CN201611206570.1A Active CN108150598B (en) 2016-12-02 2016-12-23 Hydraulic bushing and rail train
CN201611205014.2A Active CN108150535B (en) 2016-12-02 2016-12-23 Hydraulic bushing and rail train
CN201611206104.3A Withdrawn CN108150585A (en) 2016-12-02 2016-12-23 Hydraulic bushing and track train

Family Applications Before (6)

Application Number Title Priority Date Filing Date
CN201611161939.1A Pending CN108150587A (en) 2016-12-02 2016-12-15 A kind of electrolyte filling method of rail traffic hydraulic bushing
CN201621381050.XU Active CN206555347U (en) 2016-12-02 2016-12-15 A kind of track traffic hydraulic bushing
CN201611162812.1A Pending CN108150588A (en) 2016-12-02 2016-12-15 A kind of rail traffic hydraulic bushing
CN201611168201.8A Active CN108150595B (en) 2016-12-02 2016-12-16 Hydraulic bushing
CN201611166938.6A Active CN108150593B (en) 2016-12-02 2016-12-16 Hydraulic bushing
CN201611168146.2A Withdrawn CN108150594A (en) 2016-12-02 2016-12-16 A kind of hydraulic bushing

Family Applications After (11)

Application Number Title Priority Date Filing Date
CN201611174053.0A Active CN108150596B (en) 2016-12-02 2016-12-16 Hydraulic bushing
CN201611166343.0A Active CN108150589B (en) 2016-12-02 2016-12-16 Hydraulic bushing
CN201611166520.5A Active CN108150592B (en) 2016-12-02 2016-12-16 Hydraulic bushing
CN201611166346.4A Withdrawn CN108150590A (en) 2016-12-02 2016-12-16 A kind of hydraulic bushing
CN201611205646.9A Active CN108150597B (en) 2016-12-02 2016-12-23 Hydraulic bushing and rail train
CN201621423948.9U Active CN206555348U (en) 2016-12-02 2016-12-23 Hydraulic bushing and track train
CN201621425372.XU Active CN206361076U (en) 2016-12-02 2016-12-23 hydraulic bushing and track train
CN201611206851.7A Active CN108150536B (en) 2016-12-02 2016-12-23 Hydraulic bushing and rail train
CN201611206570.1A Active CN108150598B (en) 2016-12-02 2016-12-23 Hydraulic bushing and rail train
CN201611205014.2A Active CN108150535B (en) 2016-12-02 2016-12-23 Hydraulic bushing and rail train
CN201611206104.3A Withdrawn CN108150585A (en) 2016-12-02 2016-12-23 Hydraulic bushing and track train

Country Status (1)

Country Link
CN (18) CN108150587A (en)

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN110185735A (en) * 2019-05-17 2019-08-30 株洲时代新材料科技股份有限公司 A kind of liquid composite bush
CN111232007A (en) * 2020-01-08 2020-06-05 同济大学 Elastic bag active longitudinal positioning and driving device arranged in axle box
CN111706639A (en) * 2020-05-27 2020-09-25 株洲时代新材料科技股份有限公司 Hydraulic composite bushing, runner for hydraulic composite bushing and forming method of runner
CN112065909A (en) * 2020-08-18 2020-12-11 株洲时代瑞唯减振装备有限公司 Dynamic stiffness characteristic adjusting method and liquid rubber composite node with auxiliary cavity
CN113586654A (en) * 2021-08-06 2021-11-02 诺博橡胶制品有限公司 Vehicle body suspension

Families Citing this family (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US10563722B2 (en) 2016-12-02 2020-02-18 Zhuzhou Times New Material Technology Co., Ltd. Hydraulic bushing
CN108150587A (en) * 2016-12-02 2018-06-12 株洲时代新材料科技股份有限公司 A kind of electrolyte filling method of rail traffic hydraulic bushing
CN107489727A (en) * 2017-08-29 2017-12-19 株洲时代新材料科技股份有限公司 A kind of vibration absorber for track train
CN109436004A (en) * 2018-11-13 2019-03-08 中车长春轨道客车股份有限公司 The bogie of electric-machine directly-driven axle and rail vehicle with the bogie
CN110185706A (en) * 2019-05-17 2019-08-30 株洲时代新材料科技股份有限公司 A kind of includes the hydraulic bushing of metal spacer
CN110397700B (en) * 2019-08-30 2024-06-07 株洲时代瑞唯减振装备有限公司 Method for forming liquid cavity by additionally arranging four-petal type middle spacer bush and cavity structure
CN112332044A (en) * 2020-05-19 2021-02-05 宁德时代新能源科技股份有限公司 End cover assembly, single battery, battery pack, device and liquid injection method
CN111706638B (en) 2020-05-27 2022-01-21 株洲时代新材料科技股份有限公司 Hydraulic composite bushing and sealing method thereof
CN112096776A (en) * 2020-08-18 2020-12-18 株洲时代瑞唯减振装备有限公司 Integral liquid rubber composite node and rigidity adjusting method
CN112112963B (en) * 2020-08-18 2023-05-26 株洲时代瑞唯减振装备有限公司 Dynamic and static stiffness decoupling method for liquid rubber composite node
DE102020211184A1 (en) * 2020-09-04 2022-03-10 Contitech Luftfedersysteme Gmbh Hydraulic bearing bush
CN114857205B (en) * 2022-05-31 2024-05-03 中国第一汽车股份有限公司 Control arm hydraulic bushing and vehicle

Citations (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3936347C2 (en) * 1989-11-02 1991-08-14 Fa. Carl Freudenberg, 6940 Weinheim, De
EP0503687A2 (en) * 1987-07-23 1992-09-16 Firma Carl Freudenberg Bushing-type rubber spring
EP1707842A1 (en) * 2005-03-30 2006-10-04 ZF FRIEDRICHSHAFEN Aktiengesellschaft Hydraulically damped bush with axial sealing
US20070108677A1 (en) * 2005-11-15 2007-05-17 Huettner Toralf Hydraulic bearing and process for manufacturing a hydraulic bearing
CN201013828Y (en) * 2007-02-09 2008-01-30 沈百庆 Hydraulic bushing
CN101253347A (en) * 2005-09-01 2008-08-27 普尔曼公司 Hydraulic bushing
CN101413563A (en) * 2007-10-19 2009-04-22 丰田自动车株式会社 Liquid sealing type vibration insulation device
US20110188790A1 (en) * 2008-07-18 2011-08-04 Zf Friedrichshafen Ag Hydraulically Damping Bushing Bearing
CN104736878A (en) * 2012-07-31 2015-06-24 伯杰橡胶金属有限责任公司 Hydraulically damping bush bearing
CN105705825A (en) * 2013-11-11 2016-06-22 株式会社普利司通 Vibration damping device

Family Cites Families (33)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3605305A1 (en) * 1986-02-19 1987-08-20 Metzeler Kautschuk PRELVETABLE AND HYDRAULICALLY DAMPED BEARING ELEMENT
JPH055305Y2 (en) * 1985-09-18 1993-02-12
FR2616868B1 (en) * 1987-06-19 1989-10-27 Hutchinson IMPROVEMENTS ON HYDRAULIC ANTI-VIBRATION SUPPORT SLEEVES
JPH06103057B2 (en) * 1987-12-07 1994-12-14 東海ゴム工業株式会社 Fluid filled anti-vibration bush
JP2949684B2 (en) * 1988-11-25 1999-09-20 株式会社ブリヂストン Manufacturing method of anti-vibration rubber
JPH0510381A (en) * 1991-06-29 1993-01-19 Kurashiki Kako Co Ltd Bush structure for vehicle
JPH0771513A (en) * 1993-09-03 1995-03-17 Tokai Rubber Ind Ltd High viscousity fluid charged type cylindric mount
FR2830911B1 (en) * 2001-10-16 2004-01-09 Michelin Avs JOINT HYDROELASTIC JOINT
DE10232393B4 (en) * 2002-07-17 2008-06-19 Trelleborg Automotive Technical Centre Gmbh Hydraulically damping bush
DE10315645B4 (en) * 2003-04-04 2005-07-14 Zf Boge Elastmetall Gmbh Hydraulically damping rubber bush bearing for vertical mounting
CN1625661A (en) * 2003-04-21 2005-06-08 东洋橡胶工业株式会社 Liquid sealed vibration damper
JP2005172015A (en) * 2003-12-08 2005-06-30 Toyo Tire & Rubber Co Ltd Liquid sealed vibration control device
CN2781080Y (en) * 2005-03-11 2006-05-17 宁波拓普减震***有限公司 Bush hydraulic damped suspension
DE102007031606B4 (en) * 2007-07-06 2020-10-29 Dr. Ing. H.C. F. Porsche Aktiengesellschaft Hydraulically damping bearing
JP5026999B2 (en) * 2008-02-12 2012-09-19 東海ゴム工業株式会社 Fluid filled cylindrical vibration isolator
DE102009006356B4 (en) * 2009-01-28 2012-04-26 Zf Friedrichshafen Ag Wishbone of a motor vehicle
JP2010270785A (en) * 2009-05-19 2010-12-02 Toyo Tire & Rubber Co Ltd Liquid-filling type vibration-proof device
WO2011013665A1 (en) * 2009-07-28 2011-02-03 株式会社ブリヂストン Vibration-damping device
WO2011111354A1 (en) * 2010-03-08 2011-09-15 株式会社ブリヂストン Liquid seal anti-vibration device and manufacturing method thereof
CN102465989B (en) * 2010-11-05 2014-03-26 上海骆氏减震件有限公司 Cylindrical vibration isolation device
CN102478095A (en) * 2010-11-23 2012-05-30 大连创达技术交易市场有限公司 Hydraulic damping rubber sleeve bearing capable of being automatically arranged
JP5783858B2 (en) * 2011-09-14 2015-09-24 住友理工株式会社 Fluid filled cylindrical vibration isolator
JP5848592B2 (en) * 2011-12-07 2016-01-27 東洋ゴム工業株式会社 Liquid-sealed anti-vibration device and anti-vibration unit
DE102012014318B4 (en) * 2012-07-19 2016-10-20 Anvis Deutschland Gmbh Spring function component for a hydroelastic bearing and hydroelastic bearing
DE102012213446A1 (en) * 2012-07-31 2014-02-06 Zf Friedrichshafen Ag Hydraulically damping bush bearing
CN203158018U (en) * 2013-03-04 2013-08-28 青岛四方车辆研究所有限公司 Elastic bushing for bogie of linear motor vehicle
DE102013204995A1 (en) * 2013-03-21 2014-09-25 Audi Ag Method of manufacturing a bearing and bearing
CN203211041U (en) * 2013-04-27 2013-09-25 浙江国威汽车配件有限公司 Global lining car cantilever
CN203358608U (en) * 2013-07-22 2013-12-25 济南轨道交通装备有限责任公司 Low-power radial welding bogie
CN104912995B (en) * 2014-03-14 2017-04-19 广州汽车集团股份有限公司 Hydraulic bushing in vehicle suspension system guide device and vehicle
CN105276070B (en) * 2014-06-20 2017-12-19 广州汽车集团股份有限公司 Hydraulic mount and its assembly method
CN104191927B (en) * 2014-09-12 2016-03-23 东风小康汽车有限公司重庆分公司 Automotive suspension axialmode damping hydraulic variable lining
CN108150587A (en) * 2016-12-02 2018-06-12 株洲时代新材料科技股份有限公司 A kind of electrolyte filling method of rail traffic hydraulic bushing

Patent Citations (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0503687A2 (en) * 1987-07-23 1992-09-16 Firma Carl Freudenberg Bushing-type rubber spring
DE3936347C2 (en) * 1989-11-02 1991-08-14 Fa. Carl Freudenberg, 6940 Weinheim, De
EP1707842A1 (en) * 2005-03-30 2006-10-04 ZF FRIEDRICHSHAFEN Aktiengesellschaft Hydraulically damped bush with axial sealing
US20060220286A1 (en) * 2005-03-30 2006-10-05 Zf Friedrichshafen Ag Hydraulic bushing with axial seal
CN101253347A (en) * 2005-09-01 2008-08-27 普尔曼公司 Hydraulic bushing
US20070108677A1 (en) * 2005-11-15 2007-05-17 Huettner Toralf Hydraulic bearing and process for manufacturing a hydraulic bearing
CN201013828Y (en) * 2007-02-09 2008-01-30 沈百庆 Hydraulic bushing
CN101413563A (en) * 2007-10-19 2009-04-22 丰田自动车株式会社 Liquid sealing type vibration insulation device
US20110188790A1 (en) * 2008-07-18 2011-08-04 Zf Friedrichshafen Ag Hydraulically Damping Bushing Bearing
CN104736878A (en) * 2012-07-31 2015-06-24 伯杰橡胶金属有限责任公司 Hydraulically damping bush bearing
CN105705825A (en) * 2013-11-11 2016-06-22 株式会社普利司通 Vibration damping device

Cited By (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN110185735A (en) * 2019-05-17 2019-08-30 株洲时代新材料科技股份有限公司 A kind of liquid composite bush
CN111232007A (en) * 2020-01-08 2020-06-05 同济大学 Elastic bag active longitudinal positioning and driving device arranged in axle box
CN111232007B (en) * 2020-01-08 2021-05-11 同济大学 Elastic bag active longitudinal positioning and driving device arranged in axle box
CN111706639A (en) * 2020-05-27 2020-09-25 株洲时代新材料科技股份有限公司 Hydraulic composite bushing, runner for hydraulic composite bushing and forming method of runner
CN111706639B (en) * 2020-05-27 2022-03-29 株洲时代新材料科技股份有限公司 Hydraulic composite bushing, runner for hydraulic composite bushing and forming method of runner
CN112065909A (en) * 2020-08-18 2020-12-11 株洲时代瑞唯减振装备有限公司 Dynamic stiffness characteristic adjusting method and liquid rubber composite node with auxiliary cavity
CN112065909B (en) * 2020-08-18 2022-08-26 株洲时代瑞唯减振装备有限公司 Dynamic stiffness characteristic adjusting method and liquid rubber composite node with auxiliary cavity
CN113586654A (en) * 2021-08-06 2021-11-02 诺博橡胶制品有限公司 Vehicle body suspension
CN113586654B (en) * 2021-08-06 2023-02-17 诺博橡胶制品有限公司 Vehicle body suspension

Also Published As

Publication number Publication date
CN108150593A (en) 2018-06-12
CN108150593B (en) 2020-07-07
CN108150592A (en) 2018-06-12
CN108150589A (en) 2018-06-12
CN108150596B (en) 2020-09-22
CN108150536A (en) 2018-06-12
CN108150594A (en) 2018-06-12
CN108150596A (en) 2018-06-12
CN108150597A (en) 2018-06-12
CN108150587A (en) 2018-06-12
CN108150592B (en) 2020-05-08
CN108150585A (en) 2018-06-12
CN108150535B (en) 2020-06-26
CN108150590A (en) 2018-06-12
CN108150591B (en) 2020-07-14
CN108150598A (en) 2018-06-12
CN108150536B (en) 2020-06-26
CN108150595B (en) 2020-05-12
CN206361076U (en) 2017-07-28
CN206555348U (en) 2017-10-13
CN108150535A (en) 2018-06-12
CN108150598B (en) 2020-05-12
CN206555347U (en) 2017-10-13
CN108150595A (en) 2018-06-12
CN108150597B (en) 2020-05-12
CN108150589B (en) 2020-07-14
CN108150588A (en) 2018-06-12

Similar Documents

Publication Publication Date Title
CN108150591A (en) A kind of seal assembly and hydraulic bushing for hydraulic bushing
CN108343701A (en) A kind of hydraulic bushing
CN108343700A (en) A kind of hydraulic bushing
CN101685996B (en) Motor assembly and bearing sleeve thereof
CN203906258U (en) Valve tube, charging valve mechanism applying valve tube, valve pump applying charging valve mechanism
US10563722B2 (en) Hydraulic bushing
CN102689572B (en) Bush for automobile
CN202641286U (en) Lining for automobile
CN108343703A (en) A kind of rigidity adjuster and hydraulic bushing for hydraulic bushing
CN201034220Y (en) Conduit joint accessory and conduit jointing system
CN210510107U (en) Inner sleeve for hydraulic bushing
CN215155002U (en) Steering gear rotary valve structure
CN110185735B (en) Liquid composite lining
CN103335129B (en) High-temp and-pressure ball valve
CN220791886U (en) Shock absorber and vehicle with same
CN105313633A (en) Variable rigidity stabilizer bar structure and automobile
CN214493076U (en) Automobile steering knuckle
CN103982744A (en) Connecting structure and method of corrugated pipe and valve and clamp
CN219427875U (en) Automobile lower cross arm inner bushing
CN210770908U (en) Voltage stabilization type manifold tee joint
CN206937882U (en) A kind of integral type rubber penetrates cylinder body
CN216009289U (en) Motor output shaft direct-connecting structure of centrifugal machine
CN209634216U (en) Ball pin seat is molded into pattern stabilizer bar connecting bar
CN208041402U (en) The bindiny mechanism of rubber tube and connector
CN207333340U (en) Hydraulic cylinder sealing structure and ceding of Taiwan hydraulic cylinder

Legal Events

Date Code Title Description
PB01 Publication
PB01 Publication
SE01 Entry into force of request for substantive examination
SE01 Entry into force of request for substantive examination
GR01 Patent grant
GR01 Patent grant