CN105370794A - Double-frequency damper - Google Patents
Double-frequency damper Download PDFInfo
- Publication number
- CN105370794A CN105370794A CN201510967104.4A CN201510967104A CN105370794A CN 105370794 A CN105370794 A CN 105370794A CN 201510967104 A CN201510967104 A CN 201510967104A CN 105370794 A CN105370794 A CN 105370794A
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- China
- Prior art keywords
- frequency modulation
- frequency
- double
- damper
- shaped
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Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
- 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
Abstract
The invention relates to a double-frequency damper. The double-frequency damper comprises a shaft-sleeve-shaped body, and frequency modulation protrusions are manufactured on the outer surface and/or the inner surface of the body. Four outer frequency modulation protrusions are manufactured on the annular faces at the two ends of the body in a mirror symmetry mode, two outer frequency modulation protrusions are manufactured on each annular face in a radial symmetry mode, and inner frequency modulation protrusions are manufactured at the positions, corresponding to the inner sides of the outer frequency modulation protrusions, on the inner annular wall of the body in a radial symmetry mode. The double-frequency damper has a synergistic effect through the inner and outer frequency modulation protrusions, two different inherent frequencies can be achieved, and requirements of some special working conditions can be met.
Description
Technical field
The invention belongs to automobile axle shaft NVH technical field, relate to damper, especially a kind of double frequency damper.
Background technique
In vehicle travel process, its half shaft vibration has two kinds of modes, as shown in Figure 1 and Figure 2, generally semiaxis rumble spectrum as shown in Figure 1, the damper of single-frequency is used to meet the demands, make its natural frequency=FN1, but semiaxis rumble spectrum as shown in Figure 2,1 single-frequency damper is used to be unsatisfactory, because its natural frequency can only corresponding FN1 or FN2, this situation can only fill two dampers, and a natural frequency is FN1, another one is FN2, problem can solve, but cost waste is too large, and domestic is all generally adopt this way.
By retrieval, not yet find the Patents bibliographical information about solving the problems of the technologies described above.
Summary of the invention
The object of the invention is to overcome the deficiencies in the prior art part, provide a kind of and there are two natural frequencys and the large double frequency damper of difference on the frequency.
The technological scheme that technical solution problem of the present invention adopts is:
A kind of double frequency damper, comprises axle sleeve shape body, is shaped with frequency modulation projection in the outside of body and/or inner face.
And specular is shaped with four outer frequency modulation projections on the two terminal circle anchor ring of body, on each toroidal surface, radial symmetric is shaped with two outer frequency modulation projections, and on the internal ring wall of body, the inner side radial symmetric of corresponding outer frequency modulation projection is shaped with interior frequency modulation projection.
And, two that described interior frequency modulation projection is radial symmetric setting or 4,6,8,10 of being divided into by two.
And described interior frequency modulation projection is 4, it is two right that 4 interior frequency modulation projections are divided into, two pairs of radial symmetric, the protruding axially spaced-aparts of two interior frequency modulation of often pair and symmetrical.
And the axial end of described outer frequency modulation projection is symmetric shape.
And the axial end of described outer frequency modulation projection is fan-shaped or rectangle.
And described body comprises metal skeleton and rubber two-part are formed.
And, axially extending symmetry respectively to two ends and be shaped with two clip fixing parts at body, or only extend to one end and make one end clip fixing part or two ends all without clip fixing part.
And the protruding profile of described frequency modulation, sized data are as required by calculating, and formula is:
fN is natural frequency, and Kd is rubber dynamic stiffness, and M is damper quality, obtains Kd by FN, by the springrate ratio numerical constant d of rubber material, according to formula Kd/Ks=d, obtains rubber Static stiffness Ks
1, setting up the damper CAE model with frequency modulation projection, by analyzing the relation curve obtaining FN direction load and the displacement of FN direction, calculating Ks from relation curve
2, correction model, changes protruding size, shape, until Ks
2=Ks
1, profile, the sized data of frequency modulation projection is drawn from the model met the demands.
Advantage of the present invention and good effect are:
1, when semiaxis rumble spectrum has two frequencies, use a double frequency damper both can meet FN1, FN2 simultaneously.Without the need to installing two single-frequency dampers, cost-saving can more than 40%.
2, this damper is by inside and outside frequency modulation projection synergy, can realize two different natural frequencys, can meet the requirement of some special operation condition.
Accompanying drawing explanation
Fig. 1 is the semiaxis rumble spectrum with a frequency;
Fig. 2 is the semiaxis rumble spectrum with two frequencies;
Fig. 3 is three-dimensional structure diagram of the present invention;
Fig. 4 is generalized section of the present invention;
Fig. 5 is the directional diagram of the present invention's two frequencies;
Fig. 6 is CAE model schematic of the present invention;
Fig. 7 is the graph of relation of displacement and load.
Embodiment
Below in conjunction with accompanying drawing, also by specific embodiment, the invention will be further described, and following examples are descriptive, are not determinate, can not limit protection scope of the present invention with this.
A kind of double frequency damper, comprise axle sleeve shape body 2, on the two terminal circle anchor ring of body, specular is shaped with four outer frequency modulation projections 1, and on each toroidal surface, radial symmetric is shaped with two outer frequency modulation projections.In order to increase difference on the frequency, on the internal ring wall of body, the inner side radial symmetric of corresponding outer frequency modulation projection is shaped with interior frequency modulation projection 3.Described interior frequency modulation is protruding is cambered surface with the tactile face that is coupling.
The axial end of described outer frequency modulation projection is symmetric shape, as fan-shaped, rectangle etc.
Described interior frequency modulation is protruding can be two of radial symmetric or the integral multiple of 4,6,8, more than 10 or 10 2 be divided into by two, determines as required.Preferably 4, it is two right that 4 interior frequency modulation projections are divided into, two pairs of radial symmetric, the protruding axially spaced-aparts of two interior frequency modulation of often pair and symmetrical.The hoop width of described interior frequency modulation projection is less than outer frequency modulation projection.
Described body comprises metal skeleton 5 and rubber 6 two-part are formed.
And, extend symmetry at the axial two ends of body and be shaped with two clip fixing parts 4.
Conventional damper does not have projection, and only have a natural frequency, this double frequency damper is shaped with projection in the outside of body and/or inner face, makes damper not only have two natural frequencys, and high frequency, a low frequency, can meet the requirement of some specific operation.
The computational methods of inside and outside frequency modulation bump sizes and shape are: (namely the structure of product is determined according to formulae discovery below)
Kd refers to rubber dynamic stiffness; M refers to damper quality
Such as designing requirement FN1=110Hz, FN2=300Hz, M=480g, as shown in Figure 5.
Springrate ratio value according to existing rubber material determines Ks, and Kd/Ks=d, d value is known constant, Kd=d*Ks.
99N/mm (following work is all meet for the purpose of Ks=99N/mm) is should be by calculating K s
Illustrate with FN1
(1) first carry out scheme discuss and determine initial CAE model, as shown in Figure 6, this model possible is not optimized to stress and strain model, and desired value exists certain deviation.
(2) by software analysis, the relation curve of displacement and load is drawn, as shown in Figure 7, linearity range Ks=10.4/0.1=104N/mm.
(3) remodify model, repeat step (1), the action of step (2) is until Ks reaches 99KN/mm.
The same FN1 of computational methods of FN2.
Natural frequency adopts electromagnetic vibration generator system to carry out frequency or phasescan to damper
There is FN1 and FN2 characteristic in a certain vehicle semiaxis, use two dampers for its supply of material, monthly order is 20000, and the quantity required of damper is 40000, if adopt patented product damper quantity to be 2000 simultaneously.
Contrast on effect
Contrast material saving aspect
Adopt patented product to save direct material cost=(400000-280000)/400000*100%=30%, as considered man-hour, equipment investment, mould drops into, energy consumption and personal expenditures estimate cost-saving can more than 40%.
Above-described is only the preferred embodiment of the present invention, it should be pointed out that for the person of ordinary skill of the art, and under the prerequisite not departing from inventive concept, can also make some distortion and improvement, these all belong to protection scope of the present invention.
Claims (9)
1. a double frequency damper, comprises axle sleeve shape body, it is characterized in that: be shaped with frequency modulation projection in the outside of body and/or inner face.
2. double frequency damper according to claim 1, it is characterized in that: on the two terminal circle anchor ring of body, specular is shaped with four outer frequency modulation projections, on each toroidal surface, radial symmetric is shaped with two outer frequency modulation projections, and on the internal ring wall of body, the inner side radial symmetric of corresponding outer frequency modulation projection is shaped with interior frequency modulation projection.
3. double frequency damper according to claim 2, is characterized in that: two that described interior frequency modulation projection is radial symmetric setting or 4,6,8,10 of being divided into by two.
4. double frequency damper according to claim 3, is characterized in that: described interior frequency modulation projection is 4, and it is two right that 4 interior frequency modulation projections are divided into, two pairs of radial symmetric, the protruding axially spaced-aparts of two interior frequency modulation of often pair and symmetrical.
5. double frequency damper according to claim 2, is characterized in that: the axial end of described outer frequency modulation projection is symmetric shape.
6. double frequency damper according to claim 5, is characterized in that: the axial end of described outer frequency modulation projection is fan-shaped or rectangle.
7. double frequency damper according to claim 1, is characterized in that: described body comprises metal skeleton and rubber two-part are formed.
8. double frequency damper according to claim 1, is characterized in that: axially extending symmetry respectively to two ends and be shaped with two clip fixing parts at body, or only extends to one end and make one end clip fixing part or two ends all without clip fixing part.
9. double frequency damper according to claim 1, is characterized in that: the protruding profile of described frequency modulation, sized data are as required by calculating, and formula is:
fN is natural frequency, and Kd is rubber dynamic stiffness, and M is damper quality, obtains Kd by FN, by the springrate ratio numerical constant d of rubber material, according to formula Kd/Ks=d, obtains rubber Static stiffness Ks
1, setting up the damper CAE model with frequency modulation projection, by analyzing the relation curve obtaining FN direction load and the displacement of FN direction, calculating Ks from relation curve
2, correction model, changes protruding size, shape, until Ks
2=Ks
1, profile, the sized data of frequency modulation projection is drawn from the model met the demands.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201510967104.4A CN105370794B (en) | 2015-12-18 | 2015-12-18 | Double frequency damper |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201510967104.4A CN105370794B (en) | 2015-12-18 | 2015-12-18 | Double frequency damper |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN105370794A true CN105370794A (en) | 2016-03-02 |
| CN105370794B CN105370794B (en) | 2018-01-16 |
Family
ID=55373278
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201510967104.4A Expired - Fee Related CN105370794B (en) | 2015-12-18 | 2015-12-18 | Double frequency damper |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN105370794B (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| KR20170136314A (en) * | 2016-06-01 | 2017-12-11 | 현대자동차주식회사 | Dynamic damper |
Citations (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH0262442A (en) * | 1988-08-27 | 1990-03-02 | Tokai Rubber Ind Ltd | Dynamic damper |
| JPH02190641A (en) * | 1989-01-17 | 1990-07-26 | Kinugawa Rubber Ind Co Ltd | Dynamic damper for drive shaft |
| CN1139186A (en) * | 1995-06-26 | 1997-01-01 | 东海橡胶工业株式会社 | Double-mass type dynamic damper having two damper systems connected to each other, and drive shaft equipped with dynamic damper |
| JPH0989047A (en) * | 1995-09-28 | 1997-03-31 | Tokai Rubber Ind Ltd | Dynamic damper |
| FR2847320A1 (en) * | 2002-11-19 | 2004-05-21 | Caoutchouc Tech & Ind Soc Du | Vibration damper for vehicles drive shaft, has body with two elastic rings connecting mass to shaft, where latter ring stretches radially with respect to shaft and is subjected to compressive deformation between mass and shaft |
| US20140251074A1 (en) * | 2011-09-20 | 2014-09-11 | General Electric Company | System for adjusting torsional frequency of a power train |
| CN205745093U (en) * | 2015-12-18 | 2016-11-30 | 环宇东海橡塑（天津）有限公司 | Double frequency antivibrator |
-
2015
- 2015-12-18 CN CN201510967104.4A patent/CN105370794B/en not_active Expired - Fee Related
Patent Citations (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH0262442A (en) * | 1988-08-27 | 1990-03-02 | Tokai Rubber Ind Ltd | Dynamic damper |
| JPH02190641A (en) * | 1989-01-17 | 1990-07-26 | Kinugawa Rubber Ind Co Ltd | Dynamic damper for drive shaft |
| CN1139186A (en) * | 1995-06-26 | 1997-01-01 | 东海橡胶工业株式会社 | Double-mass type dynamic damper having two damper systems connected to each other, and drive shaft equipped with dynamic damper |
| JPH0989047A (en) * | 1995-09-28 | 1997-03-31 | Tokai Rubber Ind Ltd | Dynamic damper |
| FR2847320A1 (en) * | 2002-11-19 | 2004-05-21 | Caoutchouc Tech & Ind Soc Du | Vibration damper for vehicles drive shaft, has body with two elastic rings connecting mass to shaft, where latter ring stretches radially with respect to shaft and is subjected to compressive deformation between mass and shaft |
| US20140251074A1 (en) * | 2011-09-20 | 2014-09-11 | General Electric Company | System for adjusting torsional frequency of a power train |
| CN205745093U (en) * | 2015-12-18 | 2016-11-30 | 环宇东海橡塑（天津）有限公司 | Double frequency antivibrator |
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| KR20170136314A (en) * | 2016-06-01 | 2017-12-11 | 현대자동차주식회사 | Dynamic damper |
| KR102496692B1 (en) * | 2016-06-01 | 2023-02-06 | 현대자동차주식회사 | Dynamic damper |
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| Publication number | Publication date |
|---|---|
| CN105370794B (en) | 2018-01-16 |
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