CN109941057A - It is supported on damper - Google Patents
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- CN109941057A CN109941057A CN201711381291.3A CN201711381291A CN109941057A CN 109941057 A CN109941057 A CN 109941057A CN 201711381291 A CN201711381291 A CN 201711381291A CN 109941057 A CN109941057 A CN 109941057A
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- vibration isolation
- isolation element
- face
- supported
- damper according
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Abstract
The invention discloses support on a kind of damper, including shell, vibration isolation element, partition and top cover, in the housing, shape is hollow revolving body for the vibration isolation element installation, material is polyurethane elastomer, and structure includes outer surface, lubrication groove profile surface, the main side end face Mian Hefu；The outer surface is cylindrical surface, is cooperated with the inner wall of shell；Groove is opened up in the lubrication groove profile surface；The bottom surface in the main side face and top cover；The bottom surface of the pair end face and shell；Radially design has annular projection on the main side face；The partition is mounted on the center of vibration isolation element, is connect by the groove with vibration isolation element；Partition is integrally in circle ring column, center opening, and outer contour shape is corresponding with the lubrication groove profile surface shape of vibration isolation element.The present invention improves the anti-vibration performance of vibration isolation element, simplifies the manufacture of part by the annular protrusion that radially design height rises and falls on vibration isolation element end face.
Description
Technical field
The present invention relates to auto parts field, more particularly to being supported on the damper for rear overhang rack.
Background technique
It supports, is applied in automobile chassis, for connecting automotive suspension on damper using polyurethane elastomer manufacture
Damper and automobile chassis and/or chassis part are the important elastic elements of attenuating automobile vibration (referring to WO2006/
056382A1, DE102005009667A1, DE102007011209A1, US2004/0017035A1 etc.).By being propped up on damper
The vibration isolation element of support can decay, decouple, being isolated and evoked from road surface and passed through what wheel and piston lever of reducer were transmitted toward vehicle body
The vibration and noise that vibration and noise and damper itself generate, make to be passed to by shell the power of vehicle body or chassis, vibration or
Noise is reduced to minimum, improves the ride comfort and comfort of vehicle.The vibration isolation element also provides for the beat movement of damper
May, and meet vehicle to movement of the damper on axial direction, radial direction and beat direction and bearing requirements.Damper
The performance parameter of upper support has a significant impact to the dynamic performance tool of vehicle, it is necessary to carry out for different chassis designs accurate
Adjustment.By supporting on damper with the Proper Match between damper, the following performance of vehicle can be improved: reducing internal car noise
Level reduces Oscillation Amplitude, reduction wheel dynamic load, the raising driving safety, offer of vehicle body and wheel near intrinsic frequency
Laterally and in the front-back direction trackability improves driving safety.
There are certain precompressed stresss under compression for the general intracorporal assembly of vibration isolation element supporting shell on damper.It is propped up on damper
The vibration isolation element of support is clamped axially between shell and top cover, and bears certain precompressed stress under compression.The radial inner wall with shell
Cooperation, can bear certain precompressed stress under compression.So-called precompressed stress under compression refers to being supported on damper not by any external world
In the case where active force, there are certain compression stresses inside vibration isolation element.Compression stress is by the way that vibration isolation element to be mounted on
It is realized in space small in size than its.Wherein, axial pre compressed magnitude refers to the height and peace of vibration isolation element in a free state
Ratio of the difference in height with free height after dress.For example, the vibration isolation element of high 30mm is mounted on shell of the 24mm high with diameter
In, axial pre compressed magnitude is (30-24)/30=20%.Axial pre compressed magnitude can be 5%-70%, and common range is
15% to 45%.The radial precompressed difference for referring to diameter after vibration isolation element diameter in a free state and installation is the same as free shape
The ratio of diameter under state.For example, the vibration isolation element of diameter 50mm is mounted in the shell of diameter 48mm, and partition diameter is
45mm, then its radial precompressed amount is (50-48)/(50-45)=40%.Radial precompressed amount can be 0.1% to 70%, often
It is 15% to 45% with range.
The chamfered shape of the axial end face of the vibration isolation element supported on damper provides help to meet damping behavior,
But the vibration isolation element of these types is all the protrusion that specific shape (such as wavy) is distributed uniformly and circumferentially on end face,
As shown in Figure 1, therefore shape is extremely complex, mold processing difficulties, efficiency is very low；Simultaneously because it is complex-shaped, improve life
Difficulty is produced, is caused with high costs.In performance, since contact surface is circumferentially discontinuous, small manufacturing defect is likely to result in
Big part axial characteristic variations cause on damper support performance unstable and noise problem.
Summary of the invention
The technical problem to be solved in the present invention is to provide supporting on a kind of damper, its performance is stablized, vibration isolation and sound insulation effect
Fruit is good, and design and manufacture are easy, at low cost.
In order to solve the above technical problems, supported on damper of the invention, including shell, vibration isolation element, partition and top cover,
Wherein:
The vibration isolation element is mounted in the shell, and shape is hollow revolving body, and material is polyurethane elastomer, structure
Including outer surface, lubrication groove profile surface, the main side end face Mian Hefu；The outer surface is cylindrical surface, is matched with the inner wall of the shell
It closes；It is opened up in the lubrication groove profile surface fluted；The bottom surface in the main side face and the top cover；The pair end face and the shell
The bottom surface of body；Radially design has annular projection on the main side face；
The partition is mounted on the center of the vibration isolation element, is connect by the groove with the vibration isolation element；It should be every
The overall structure of plate is in circle ring column, and center opening, outer contour shape is corresponding with the lubrication groove profile surface shape of the vibration isolation element.
Preferably, the material of the vibration isolation element uses cellular polyurethane foaming elastomer, the material of the partition is gold
Belong to.
Preferably, annular projection, the main side end face Mian Hefu also radially further can also be designed on the secondary end face
On annular projection it is symmetrical.Annular projection is all designed in two end faces can be further improved vibration and the decaying of noise.
Preferably, can also be designed on the bottom surface of the top cover and/or the bottom surface of the shell and main side face and/or secondary end
The annular projection that annular projection on face matches.
Annular projection on the end face is upwardly formed wave in the end-face diameter, and the wave crest number of the wave is 1 or more,
Height of the wave crest in the central axial direction of the vibration isolation element can gradually decrease, gradually rise or remain unchanged.
When the vertex of the wave crest is located at approximately the same plane, the line on wave crest vertex is preferably -15 °~45 ° with the angle α of end face.
The shape of the single wave-shaped cross-section of wave include but is not limited to triangle, semicircle, trapezoidal, sinusoidal waveform,
Rectangular or these shapes are by a part after rule segmentation.
The outer diameter of the vibration isolation element is 40~70mm, and internal diameter is 20~50mm, and the diameter of the groove is 30~60mm.
The height of the annular projection is 0~15mm.Defining height of the end face in central axial direction is face height H0, fixed
The distance of the highest point of adopted central axial direction upper surface to groove is unilateral elastomer high H, then H0It is the 0~50% of H, it is excellent
It is selected as 0~40%, further preferably 35%.
Outside by the center of vibration isolation element, each annular projection can successively be in equal ratios in the width of vibration isolation element radially
Ordered series of numbers, the common ratio of the Geometric Sequence is 1~2, preferably 1~1.5, for having the case where 3 annular projections, the common ratio into
One step is preferably 1.4.
The annular projection is in vibration isolation element width radially and to account for the ratio of vibration isolation element outer diameter be 10%~35%,
Preferably 12%~20%, further preferably 14%~18%.
The present invention improves vibration isolation element by the annular protrusion that radially design height rises and falls on vibration isolation element end face
Anti-vibration performance, simplify the manufacture of part.With support phase ratio on existing damper, on damper of the invention support have with
Lower advantages and beneficial effects:
1. vibration isolation/sound insulation effect is good.The circular ring shape protrusion that radially distributed height rises and falls on vibration isolation element end face, guarantees
It supports and is more uniformly stressed on damper, passed over so as to preferably absorb and decay by wheel and damper
Vibration and noise as caused by road surface and damper itself provide good vibration isolation/sound insulation effect between damper and vehicle body
Fruit.
2. axial rigidity adjustment is easy.By adjusting the height distribution of radial protrusion on vibration isolation element end face, can be convenient
The roll-off characteristic of the axial rigidity supported on ground adjustment damper can according to need and be designed to progressive stiffness characteristic or decrescence rigid
Spend characteristic.
3. it is simple to manufacture, it is at low cost.Due to poromeric polyurethane material handling ease and at low cost, using it as raw material
Polyurethane elastomer vibration isolation element be easier to design and manufacture, the production of mold has very big simplification, be more suitable for polyurethane hair
The production process of bubble, homogeneity of product is higher, and performance is more stable, economically more advantage.
4. installation is easy.Since the radial protrusion on vibration isolation element end face is at the ring-type of an entirety, during installation
Vibration isolation element is not necessarily to consider the position of its diametrically other part, to facilitate the assembly of part.
Detailed description of the invention
Fig. 1 is a kind of structural schematic diagram of existing typical vibration isolation element.
Fig. 2 is the schematic structural cross-sectional view supported on the damper of the embodiment of the present invention.
Fig. 3 is the schematic perspective view for the sub-assembly that the vibration isolation element supported on the damper by Fig. 2 and partition are constituted.
Fig. 4 is the structural schematic diagram of the vibration isolation element supported on the damper of Fig. 2.
Fig. 5 is the shape critical size characteristic schematic diagram of the vibration isolation element end face annular projection of Fig. 4.
Fig. 6 is the critical size parameter of the vibration isolation element of Fig. 4.
Fig. 7 is the vibration isolation element end face annular protrusion vertex line same level face angle schematic diagram of Fig. 4.
Fig. 8 is several typical cross sectional shape diagrams of vibration isolation element end face annular protrusion.
The reference numerals are as follows in figure:
1: being supported on damper
10: shell
12: top cover
20: vibration isolation element
221: main side face
222: secondary end face
24: annular projection
26: outer surface
28: lubrication groove profile surface
30: partition
40: groove
50: central axis
60: piston rod
70: nut
α: angle of the vertex line of annular projection with vibration isolation element end face
Specific embodiment
To have more specific understanding to technology contents of the invention, feature and effect, now in conjunction with drawings and the specific embodiments,
Technical solution of the present invention is further described in detail.
Support applications are in barrel type hydraulic shock absorber on the damper of the present embodiment.Barrel type hydraulic shock absorber mainly includes living
Plug and piston rod, and limitation piston are axially moved two limited blocks of amplitude along damper cylinder barrel.Support passes through on damper
Bolt is fixed on vehicle body, and structure is as shown in Figure 2,3, mainly includes shell 10, elastomer vibration isolation element 20,30 and of partition
Top cover 12.
The installation of vibration isolation element 20 is the hollow revolving body with central axis 50 in the housing 10, and material is
Cellular polyurethane foaming elastomer (most handy NDI type, but be not limited to NDI type).The specific structure of vibration isolation element 20 such as Fig. 3,4 institutes
Show, mainly includes outer surface 26, lubrication groove profile surface 28, main side face 221 and secondary end face 222.The outer surface 26 is cylinder
Face cooperates with the inner wall of the shell 10.The groove 40 cooperated with partition 30 is offered in the lubrication groove profile surface 28.The main side
The bottom surface in face 221 and top cover 12.The bottom surface of the pair end face 222 and the shell 10.
Radially symmetric design haves three layers annular projection respectively on the main side face 221 of the vibration isolation element 20 and secondary end face 222
24.Axial direction along vibration isolation element 20 sees that these annular projections 24 form complete circular protrusion；Radial direction along end face sees, this
A little annular projections 24 form the wave gradually decreased to 50 height of central axis.The wave crest number of wave is respectively 3.Annular projection
24 shape critical size is as shown in figure 5, face height H0(i.e. on 50 direction of central axis, all annular projections on end face
Distance of the minimum point to highest point) be unilateral elastomer thickness H (i.e. on 50 direction of central axis, the highest point of end face to groove
40 distance) 35%.First annular projection 24 defined on 20 end face of vibration isolation element by central axis 50 is in the radial direction
Width is T1, from inside to outside, subsequent annular projection 24 is successively defined as T in radial width2, T3..., then T1, T2, T3...
At Geometric Sequence, the common ratio of Geometric Sequence is 1.4.The width in the radial direction of annular projection 24 and Σ on 20 end face of vibration isolation element
The ratio that Ti (i=1,2,3 ... ...) accounts for 20 outer diameter of vibration isolation element is 14%~18%.The vibration isolation element 20 of the present embodiment its
(unit of each size is mm) to his critical size parameter as shown in Figure 6.
In addition, the present embodiment the top cover 12 cooperated with main side face 221 bottom surface and with secondary end face 222 cooperation shell 10
Bottom surface on also accordingly devise the annular projection to match.
The partition 30 is assemblied in the center of the vibration isolation element 20, passes through the groove in 20 lubrication groove profile surface 28 of vibration isolation element
40 link together with vibration isolation element 20, are fixed on damper in the shell 10 of support 1 that (partition 30 is not and on damper
The shell 10 and top cover 12 of support 1 contact).The whole partition 30 is in circle ring column, center opening, outer contour shape and vibration isolation member
The shape of the lubrication groove profile surface 28 of part 20 is corresponding, and material can be steel, cast aluminium alloy gold or other metal materials.Guaranteeing to be easy
Under the premise of production and assembly, partition 30 should be big as far as possible with the area of the contact surface of vibration isolation element 20.
The above is only the preferred structures supported on damper of the invention.In other embodiments, can only every
Annular projection 24 is designed on the main side face 221 of vibration element 20, and does not design annular projection on secondary end face 222.The bottom surface of top cover 12
Corresponding annular projection can be designed on the bottom surface of shell 10, annular projection can not also be designed.Annular projection on end face
The wave crest number of 24 waves being upwardly formed in end-face diameter is at least 1, and specific wave crest number is non-linear with the axial direction supported on damper
Rigidity property requires related.Wave is also possible to gradually rise to the height of central axis 50 or maintenance level.The vertex of wave
Approximately the same plane can be located at, different planes can also be located at.When wave vertex is located at approximately the same plane, the company on wave vertex
Line is -15 ° to 45 ° with the angle α of end face, as shown in fig. 7, the axial non-linear rigidity supported on specific angle value and damper
Performance requirement is directly related, by selecting suitable angle that suitable axial progressive stiffness characteristic may be implemented, to effectively disappear
Except the impact noise for supporting transmitting on damper.The shape of single wave-shaped cross-section, refering to what is shown in Fig. 8, including but not limited to sample
Curve, triangle, semicircle, trapezoidal, sinusoidal waveform, rectangular and/or these shapes a part.Here " a part " refers to
Be a certain shape it is not complete, but is divided by rule.Shape, the size of each wave-shaped cross-section can be consistent, can also be different
It causes, specific waveform is related with supporting the axial required non-linear rigidity performance requirement realized on damper.
The manufacturing method supported on damper of the invention is as follows:
Raw material use poromeric polyurethane material, and characteristic at least meets any two in following performance requirement: by DIN
The density range of EN ISO845 measurement is 200~1000kg/m3(preferably 300 arrive 750kg/m3), it is surveyed by DIN EN ISO 1798
The tensile strength scope of amount in 2~8MPa, survey 200%~700%, or by DIN ISO 34-1B (b) by elongation at break ranges
The tearing toughness range of amount is 4~12N/mm.
The preparation method of cellular polyurethane elastomer can refer to the prior art, as European patent application EP62835A1,
EP36994A2, EP250969A1, EP1171515A1, German patent application DE19548770A1, DE19548771A1 etc..Usually
It is that first is preferably closed with 2,6- diisocyanate root based on isocyanates diisocyanate base toluene (TDI) or naphthalene diisocyanate (NDI)
Benzene (TODI) or 1 based on 5- naphthalene diisocyanate (5-NDI), prepares cellular polyurethane elastomer.
There are two types of manufacturing methods for vibration isolation element, and one is the foamings directly in the hermetic type chamber of mold, that is, will prepare
The hermetic type chamber (injection rate number determined by the density of the required part for meeting performance requirement) of good material injecting mould,
(surface temperature of type chamber is usually 40~100 DEG C to foaming to raw material, and part exists in type chamber under certain temperature and time
Heat preservation 5~demoulding after sixty minutes in type chamber).Another method is machining by preforming polyurehane tube.In pole
In the case of limit, i.e., the entire end face of vibration isolation element only one account for the square protruding of entire plane, at this moment, the end face of vibration isolation element
For plane, vibration isolation element is obtained by directly cutting tubular bar with can be convenient.One advantage of this design is part
Structure is simple, easily manufactured.The processing of vibration isolation element end profile can directly be cut with molding cutter and be obtained.
The sub-assembly that vibration isolation element and partition are constituted can by by partition be placed in the mold of vibration isolation element directly at
Type (preferably), assembles again after can also manufacturing respectively.
The installation being supported on damper of the invention on vehicle, and with the connection of damper, with traditional damper
Upper support is consistent.The one end supported on damper is fixed on vehicle body by passing through the bolt of fixed hole position on shell 10.Damping
The hole that device piston rod 60 passes through 30 center of partition is locked at one with partition 30 with nut 70 by the stud on 60 top of piston rod
It rises, realizes that support is the same as the connection of damper on damper.It can be connected by traditional mode between top cover 12 and shell 10, such as spiral shell
It tethers and connects, rivets, welding, being bonded, rolling.The form that the present embodiment is riveted using rolling.
After support is connect with damper on damper, two end faces of vibration isolation element 20 are clamped axially shell 10 and top
Between lid 12, being generated precompressed compression deformation by certain precompression effect, (wave crest of the annular projection 24 of vibration isolation element 20 is by outer
When highly successively decreasing inwards, innermost wave crest bears the precompressed compression deformation of very little, or is not subject to precompressed compression deformation；Axial precommpression
Amount can be consistent with radial precompressed amount, can also be inconsistent), lateral support effect is provided for piston lever of reducer 60.
Claims (16)
1. being supported on damper, which is characterized in that including shell, vibration isolation element, partition and top cover, in which:
The vibration isolation element is mounted in the shell, and shape is hollow revolving body, and material is elastomer, and structure includes outer profile
Face, lubrication groove profile surface, the main side end face Mian Hefu；The outer surface is cylindrical surface, is cooperated with the inner wall of the shell；The lubrication groove
It is opened up in profile surface fluted；The bottom surface in the main side face and the top cover；The pair end face and the bottom surface of the shell are matched
It closes；Radially design has annular projection on the main side face；
The partition is mounted on the center of the vibration isolation element, is connect by the groove with the vibration isolation element；The partition
Overall structure is in circle ring column, and center opening, outer contour shape is corresponding with the lubrication groove profile surface shape of the vibration isolation element.
2. being supported on damper according to claim 1, which is characterized in that the material of the vibration isolation element is porous poly- ammonia
Ester foaming elastomer, the material of the partition are metal.
3. being supported on damper according to claim 1, which is characterized in that radially design has ring-type on the pair end face
Protrusion, the annular projection on the end face the main side Mian Hefu are symmetrical.
4. being supported on damper according to claim 1 or 3, which is characterized in that the bottom surface of the top cover and/or the shell
Design has the annular projection to match with the annular projection on the main side face and/or secondary end face on the bottom surface of body.
5. being supported on damper according to claim 1 or 3, which is characterized in that the annular projection on the end face is at this
End-face diameter is upwardly formed wave, and the wave crest number of the wave is 1 or more, central axis of the wave crest in the vibration isolation element
Height on direction gradually decreases, gradually rises or remains unchanged.
6. being supported on damper according to claim 5, which is characterized in that the vertex of the wave crest is located at approximately the same plane
When, the line on wave crest vertex is -15 °~45 ° with the angle α of end face.
7. being supported on damper according to claim 5, which is characterized in that the shape of the single wave-shaped cross-section of wave
Including triangle, semicircle, trapezoidal, sinusoidal waveform, rectangular or these shapes by a part after rule segmentation.
8. being supported on damper according to claim 5, which is characterized in that the outer diameter of the vibration isolation element be 40~
70mm, internal diameter are 20~50mm, and the diameter of the groove is 30~60mm, and the height of the annular projection is 0~15mm, definition
Height of the end face in central axial direction is H0, define the highest point of the end face in central axial direction to groove away from
From for H, then H0It is the 0~50% of H.
9. being supported on damper according to claim 8, which is characterized in that the H0It is the 0~40% of H.
10. being supported on damper according to claim 9, which is characterized in that the H0It is the 35% of H.
11. being supported on damper according to claim 5, which is characterized in that the center by the vibration isolation element is outside, respectively
A annular projection is successively in Geometric Sequence in the width of vibration isolation element radially, and the common ratio of the Geometric Sequence is 1~2.
12. being supported on damper according to claim 11, which is characterized in that the common ratio of the Geometric Sequence be 1~
1.5。
13. being supported on damper according to claim 12, which is characterized in that the common ratio of the Geometric Sequence is 1.4.
14. being supported on damper according to claim 5, which is characterized in that the annular projection is in vibration isolation element radial direction
On width account for vibration isolation element outer diameter ratio be 10%~35%.
15. being supported on damper according to claim 14, which is characterized in that the annular projection is in vibration isolation element radial direction
On width and account for vibration isolation element outer diameter ratio be 12%~20%.
16. being supported on damper according to claim 15, which is characterized in that the annular projection is in vibration isolation element radial direction
On width and account for vibration isolation element outer diameter ratio be 14%~18%.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201711381291.3A CN109941057A (en) | 2017-12-20 | 2017-12-20 | It is supported on damper |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201711381291.3A CN109941057A (en) | 2017-12-20 | 2017-12-20 | It is supported on damper |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN109941057A true CN109941057A (en) | 2019-06-28 |
Family
ID=67005561
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201711381291.3A Pending CN109941057A (en) | 2017-12-20 | 2017-12-20 | It is supported on damper |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN109941057A (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN110816192A (en) * | 2019-12-06 | 2020-02-21 | 亚新科噪声与振动技术（安徽）有限公司 | Upper supporting seat structure of rear shock absorber of automobile |
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| CN202518055U (en) * | 2012-04-12 | 2012-11-07 | 重庆长安汽车股份有限公司 | Upper support assembly of automobile shock absorber |
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| CN103348160A (en) * | 2011-01-28 | 2013-10-09 | 巴斯夫欧洲公司 | Shock-absorbing bearing comprising a profiled insert |
| CN103770591A (en) * | 2012-10-18 | 2014-05-07 | 广州汽车集团股份有限公司 | Vibration damping support of vehicle vibration damper and vehicle vibration damper |
| CN104019182A (en) * | 2014-06-04 | 2014-09-03 | 安徽中鼎减震橡胶技术有限公司 | Rubber support for front shock absorber of automobile |
| DE102015216075A1 (en) * | 2015-08-24 | 2017-03-02 | Volkswagen Aktiengesellschaft | Shock absorber for a motor vehicle |
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| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH04228944A (en) * | 1990-05-15 | 1992-08-18 | Boge Ag | Leg section supporter for shock absorber |
| CN103348160A (en) * | 2011-01-28 | 2013-10-09 | 巴斯夫欧洲公司 | Shock-absorbing bearing comprising a profiled insert |
| CN202451676U (en) * | 2012-01-13 | 2012-09-26 | 浙江吉利汽车研究院有限公司 | Low support of rear shock absorber of automobile |
| CN202518055U (en) * | 2012-04-12 | 2012-11-07 | 重庆长安汽车股份有限公司 | Upper support assembly of automobile shock absorber |
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| CN103032502A (en) * | 2012-11-29 | 2013-04-10 | 芜湖禾田汽车工业有限公司 | Shock isolation block for automobile shock absorber |
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| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN110816192A (en) * | 2019-12-06 | 2020-02-21 | 亚新科噪声与振动技术（安徽）有限公司 | Upper supporting seat structure of rear shock absorber of automobile |
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Application publication date: 20190628 |