CN1110230A - Frequency adjusting damping suspension for vehicle - Google Patents
Frequency adjusting damping suspension for vehicle Download PDFInfo
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- CN1110230A CN1110230A CN 94112123 CN94112123A CN1110230A CN 1110230 A CN1110230 A CN 1110230A CN 94112123 CN94112123 CN 94112123 CN 94112123 A CN94112123 A CN 94112123A CN 1110230 A CN1110230 A CN 1110230A
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Abstract
The present invention relates to a vehicle suspension. Said suspension uses a variable-stiffness frequency-regulating device whose elastic property has a negative stiffness zone, so that it can make the original frequency of vehicle body keep at ideal value when the vehicle load is changed so as to obtain good vehicle running smoothness. Besides, this variable-stiffness frequency-regulating devcie can be easily installed between the existent vehicle chassis and vehicle body, and has no need of greatly changing original chassis and body.
Description
The present invention relates to a kind of vehicle suspension, this suspension has been owing to adopted change rigidity frequency modulation device, can be so that vehicle when load change, keep the vehicle body natural frequency to be ideal value, thus obtain good vehicle ' ride comfort.And this change rigidity frequency modulation device can be contained between existing vehicle chassis and the vehicle body easily, and does not need former vehicle chassis or vehicle body are done big change.
Suspension is one of important assembly on the vehicle, and it flexibly couples together vehicle frame (or vehicle body) and axletree (or wheel).Its main task is a shear force and the moment of transfer function between wheel and vehicle frame, and relaxes the impact load of being passed to vehicle frame by uneven road surface, and the vibration of the bearing system that decay is caused by impact is to guarantee normal vehicle operation.
Known, suspension is all influential to multiple in-use performances such as the riding comfort of vehicle, stability, crossing ability, fuels efficiency, thereby suspension is an important ring that influences vehicle performance.
Known, using maximum suspensions on the existing vehicle is the suspension of linear elasticity characteristic, and the natural frequency of its vehicle body changes with load change.Its elastic behavior is to reach the ideal value design-calculated with at full load rigidity, so the natural frequency of suspension just increases when load reduces, so just can't reach the requirement of vehicle ' ride comfort under the load outside fully loaded.
Known, address the above problem, just need to adopt the suspension of nonlinear elasticity characteristic, also claim variable-rate suspension.According to theoretical analysis, no matter how load changes, if keep the vehicle body natural frequency constant, just must keep under the at full load rigidity unmodified condition, progressively reduce by fully loaded suspension rate under the load the zero load, yet this desirable elastic behavior uses existing positive rigidity elastic link to be difficult to realize, in the present suspension design, only makes every effort to reduce the amplitude (or scope) that natural frequency changes with load.Thereby improve the vehicle ' ride comfort to some extent.
Known, the compound steel spring suspension that existing major-minor spring is formed is a kind of change stiffness characteristics suspension commonly used.It also can partly improve the vehicle ' ride comfort.But because in the overall process of distortion, only have two kinds of rigidity, thereby to have under two kinds of load can only guarantee load change at most the time be ideal value.Simultaneously, the rigidity cataclysm meeting before and after the auxiliary spring effect produces an impact load to vehicle, has influenced the vehicle ' ride comfort on the contrary.
Known, existing non-linear laminated spring, non-linear borded pile spring (as variable pitch post spring, column with variable cross-sections spring etc.) though the elastic behavior of improving suspension that can be bigger, reach unloaded be fully loaded with between under the various load natural frequency to be ideal value also be difficult.Also can run in the design simultaneously such as problems such as: spring volume, weight are excessive.So it is not very extensive using on the domestically-made vehicle.
Known, existing air bellow can address the above problem by the method for feedback, but the air bellow complex structure, and cost height, reliability are difficult for guaranteeing.Be difficult on the vehicle popularize and use.
Known, existing vehicle suspension system all is to adopt positive rigidity elastic element as the rigidity control apparatus, the compound steel spring suspension of major-minor spring composition is exactly an example as described above, cost is low, reliability is high so existing vehicle suspension is difficult in, under the condition of compact conformation, guarantee that the vehicle body natural frequency is ideal value in the load range that vehicle allows.
First purpose of the present invention is the shortcoming that overcomes above-mentioned existing vehicle suspension, provides a kind of linear rigidity spring to add the suspension that becomes the rigidity frequency modulation device.This suspension can make vehicle unloaded be fully loaded with between under the various load, natural frequency is ideal value.
Second purpose of the present invention is the shortcoming that overcomes above-mentioned existing vehicle suspension, a kind of simple in structure, good reliability is provided, can be contained in the variable-rate suspension on the existing vehicle easily.Guarantee that vehicle has good vehicle ' ride comfort.
The present invention realizes as follows:
Accompanying drawing 1 is the elastic characteristic curve of common positive rigidity constant characteristic spring.F wherein
1Be the stress value of positive rigid spring, δ
1Deflection for positive rigid spring.
Accompanying drawing 2 is the elastic characteristic curves that become the rigidity frequency modulation device.F wherein
2Be the stress value that becomes the rigidity frequency modulation device, δ
2For becoming the deflection of rigidity frequency modulation device.
Accompanying drawing 3 is the elastic characteristic curves after common positive rigidity constant characteristic spring and the parallel connection of change rigidity frequency modulation device.It is the elastic characteristic curve of frequency adjusting damping suspension for vehicle.Wherein F is the stress value of frequency adjusting damping suspension for vehicle, and δ is the deflection of frequency adjusting damping suspension for vehicle.
Shown in accompanying drawing 2, become rigidity frequency modulation device elastic behavior and have non-linear negative stiffness zone, in this zone, this device can be regarded a negative stiffness spring as, this device power of bearing increases with deflection and reduces like this, when this device is in parallel with positive rigid spring, chief and vice rigidity can be offset a part, when not changing the at full load suspension rate, reduce fully loaded suspension rate under each load between zero load thereby just can reach, reach and be suspended in the purpose that natural frequency under any load is ideal value.Moreover, the use of negative stiffness spring can be so that frequency modulation device compact conformation, simple can be contained on the existing vehicle easily.Simple owing to the manufacturing of negative stiffness spring simultaneously, good reliability, thereby the present invention has the reliability height, and the advantage that cost is low, thus an aforementioned techniques difficult problem solved.
Below in conjunction with the embodiment explanation.
Accompanying drawing 4 has been described the present invention and has been applied in a kind of embodiment on the automobile
Chassis side rail (1) still keeps primary car structure with the type of attachment of leaf spring (2), so the Joint strenght of suspension is identical with former chassis with the safe reliability of travelling.Change rigidity frequency modulation device is formed in regulating spring (3), (4) and adjusting connecting rod (5), (6), (7), (8).Wherein, leaf spring (2) has the positive rigidity linear elasticity characteristic shown in the accompanying drawing 1, regulating spring (3), (4) are the spring of positive rigidity elastic behavior, but it and the change rigidity frequency modulation device of regulating connecting rod (5), (6), (7), (8) composition, by the mode shown in the accompanying drawing 4 and chassis side rail (1) with just had notable feature of the present invention after axletree (9) links to each other, i.e. elastic behavior shown in the accompanying drawing 2.Thereby the suspension shown in the accompanying drawing 4 can make and use the automobile of this suspension to have good riding comfort so that automobile when load change, keeps the vehicle body natural frequency to be ideal value.
Obviously, this suspension has the safe reliability identical with former car simultaneously, can be contained in easily between existing vehicle chassis and the vehicle body, and compact conformation, make simple, cost is low.
Though being the automobile that is used in combination the leaf spring suspension, inventive embodiments recited above describes.The present invention also can be applied to the suspension of other form.
Be to be understood that the present invention is not limited to the foregoing description, and under the condition of claim scope of the present invention, the personnel that are familiar with this professional technique can make change type of the present invention and improved type at an easy rate.
Claims (3)
1. a frequency adjusting damping suspension for vehicle is made up of spring with positive rigidity elastic behavior and change rigidity frequency modulation device, it is characterized in that the elastic behavior that becomes the rigidity frequency modulation device has the negative stiffness zone.
2. frequency adjusting damping suspension for vehicle as claimed in claim 1 is characterized in that, becomes the rigidity frequency modulation device and is made up of regulating spring (3), (4) and adjusting connecting rod (5), (6), (7), (8).
3. frequency adjusting damping suspension for vehicle as claimed in claim 2 is characterized in that keeping the leaf spring of former chassis suspension fork of vehicle.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN 94112123 CN1110230A (en) | 1994-04-15 | 1994-04-15 | Frequency adjusting damping suspension for vehicle |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN 94112123 CN1110230A (en) | 1994-04-15 | 1994-04-15 | Frequency adjusting damping suspension for vehicle |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN1110230A true CN1110230A (en) | 1995-10-18 |
Family
ID=5035926
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN 94112123 Pending CN1110230A (en) | 1994-04-15 | 1994-04-15 | Frequency adjusting damping suspension for vehicle |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN1110230A (en) |
Cited By (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN101811527A (en) * | 2010-04-19 | 2010-08-25 | 新大洋机电集团有限公司 | Forward design method for rigidity of helical spring of automobile |
| CN101263018B (en) * | 2005-09-12 | 2011-01-26 | Gm全球科技运作股份有限公司 | Control method for adjusting electronically controlled damping system in motor vehicles and an electronically controlled damping system |
| CN102555721A (en) * | 2010-12-28 | 2012-07-11 | 通用汽车环球科技运作有限责任公司 | Vehicle with a leaf spring element for the spring suspension of the vehicle |
| CN112064507A (en) * | 2020-08-07 | 2020-12-11 | 中铁大桥局集团有限公司 | Vertical impact buffering device |
| CN113771574A (en) * | 2021-11-15 | 2021-12-10 | 溧阳常大技术转移中心有限公司 | Vehicle suspension with flexibility adaptively adjusted along with gravity height |
-
1994
- 1994-04-15 CN CN 94112123 patent/CN1110230A/en active Pending
Cited By (9)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN101263018B (en) * | 2005-09-12 | 2011-01-26 | Gm全球科技运作股份有限公司 | Control method for adjusting electronically controlled damping system in motor vehicles and an electronically controlled damping system |
| US8280585B2 (en) | 2005-09-12 | 2012-10-02 | GM Global Technology Operations LLC | Control method for adjusting electronically controlled damping system in motor vehicles and an electronically controlled damping system |
| CN101811527A (en) * | 2010-04-19 | 2010-08-25 | 新大洋机电集团有限公司 | Forward design method for rigidity of helical spring of automobile |
| CN101811527B (en) * | 2010-04-19 | 2012-08-22 | 鲍文光 | Forward design method for rigidity of helical spring of automobile |
| CN102555721A (en) * | 2010-12-28 | 2012-07-11 | 通用汽车环球科技运作有限责任公司 | Vehicle with a leaf spring element for the spring suspension of the vehicle |
| CN102555721B (en) * | 2010-12-28 | 2016-04-13 | 通用汽车环球科技运作有限责任公司 | There is the automobile for the laminated spring element for automobile shock |
| CN112064507A (en) * | 2020-08-07 | 2020-12-11 | 中铁大桥局集团有限公司 | Vertical impact buffering device |
| CN112064507B (en) * | 2020-08-07 | 2022-04-08 | 中铁大桥局集团有限公司 | Vertical impact buffering device |
| CN113771574A (en) * | 2021-11-15 | 2021-12-10 | 溧阳常大技术转移中心有限公司 | Vehicle suspension with flexibility adaptively adjusted along with gravity height |
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| PB01 | Publication | ||
| C10 | Entry into substantive examination | ||
| SE01 | Entry into force of request for substantive examination | ||
| C01 | Deemed withdrawal of patent application (patent law 1993) | ||
| WD01 | Invention patent application deemed withdrawn after publication |