CN203477157U - Amplitude related shock absorber - Google Patents
Amplitude related shock absorber Download PDFInfo
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- CN203477157U CN203477157U CN201320584376.2U CN201320584376U CN203477157U CN 203477157 U CN203477157 U CN 203477157U CN 201320584376 U CN201320584376 U CN 201320584376U CN 203477157 U CN203477157 U CN 203477157U
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- intermediate cavity
- end cap
- middle cavity
- vibration damper
- piston
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Abstract
The utility model relates to an amplitude related shock absorber. The shock absorber comprises an upper end cover, a framework oil seal, a guider, an inner cylinder barrel, an outer cylinder barrel, a piston assembly, a bottom valve assembly and a lifting lug. The shock absorber is characterized by further comprising a piston rod, a middle cavity upper end cover, a one-way valve assembly, a middle cavity outer barrel and a middle cavity lower end cover, wherein the middle cavity upper end cover is in threaded connection with the piston rod, the one-way valve assembly is assembled between the piston rod and the middle cavity upper end cover and composed of a spring and a small ball, the middle cavity outer barrel is connected with the middle cavity upper end cover, and the middle cavity lower end cover is connected with the middle cavity outer barrel. An upper conical spring, a floating piston and a lower conical spring are arranged in a middle cavity. The upper conical spring and the lower conical spring are connected with the middle cavity upper end cover and the middle cavity lower end cover respectively. The piston assembly is fixed to the middle cavity lower end cover through a fastening nut. According to the shock absorber, different running working conditions of an automobile can be identified, meanwhile, damping characteristics of the automobile can be adjusted according to the different running working conditions of the automobile, and therefore good riding comfort, good steering stability and running safety are ensured.
Description
Technical field
The present invention relates to a kind of for the vibration damper on automotive suspension, the relevant vibration damper of a kind of damping characteristic can change with excitation amplitude specifically amplitude.
Background technique
The different performance of automobile is to the demand of suspension damping contradiction often: wish improves riding comfort, reduces the vibration of sprung weight, should make the suspension damping arrange lowlyer; Want to reduce the moving stroke of tire dynamic load and suspension, should make suspension damping arrange higherly; From the viewpoint of the control stability of car load, want to reach car body obliqueness and the object of steering response time while reducing to turn to, also should make suspension design obtain " firmly " some.Therefore the coupling of automotive suspension damping is generally to consider the half-way house that automobile various aspects of performance is taked.
At present, be widely used in the common vibration damper on automotive suspension, damping force only depends on the speed of related movement between vehicle body and wheel, its damping characteristic cannot be made corresponding variation according to the different applying working conditions of vehicle, therefore be difficult to dissolve the contradiction between the different performances such as control stability, riding comfort, driving safety of vehicle, can not make vehicle performance under different applying working conditions all reach best.
The Active suspension technology of rising in recent years can be according to the motion of automobile and pavement behavior, and the in time rigidity of adjustable suspension and damping makes it all the time in best vibration damping state.But this kind of Technology Need installed complicated sensor detector, actuator and controller on vehicle.Compare with common passive suspension, it is with high costs, and poor reliability is difficult to popularize.
The present invention proposes the relevant vibration damper of amplitude that a kind of damping characteristic can change with suspension motion amplitude, when vehicle travels in good road surface, this vibration damper can provide less damping, guarantees good riding comfort; While travelling on Vehicular turn or the road surface of jolting, this vibration damper can provide larger damping, guarantees good control stability and driving safety.By distinguishing the different driving cycles of vehicle, provide different damping characteristics, the contradiction of the different performance that this vibration damper can solve vehicle preferably to suspension damping demand.
Summary of the invention
The relevant vibration damper of amplitude that will provide a kind of damping characteristic to change with suspension motion amplitude is provided, it can pick out the different driving cycle of vehicle, as good road surface, severe road surface, significantly roll etc., and can regulate its damping characteristic according to the different driving cycle of vehicle.Hour, the damping that this vibration damper provides is also less, thereby guarantees good riding comfort for suspension motion amplitude; When suspension motion amplitude is larger, the damping that this vibration damper provides is also larger, thereby guarantees good control stability and driving safety.
The object of the present invention is achieved like this, this vibration damper comprises: upper end cap, outside framework oil seal, guider, inner cylinder tube, outer cylinder, piston assembly, bottom valve assembly, hanger, it is characterized in that: it also comprises piston rod, the intermediate cavity upper end cap being connected with piston rod thread, be assemblied in the one-way valve assembly being formed by spring and bead between piston rod and intermediate cavity upper end cap, the intermediate cavity urceolus being connected with intermediate cavity upper end cap, the intermediate cavity lower end cap being connected with intermediate cavity urceolus, in described intermediate cavity, be provided with upper conical spring, floating piston and inferior pyramidal spring, upper conical spring is connected with intermediate cavity lower end cap with intermediate cavity upper end cap respectively with inferior pyramidal spring, tightening nut is fixed on piston assembly on intermediate cavity lower end cap.
On described piston rod, have sulculus, and having aperture near sulculus bottom, check valve spring and one-way valve bead are assemblied in sulculus, and piston rod is connected with intermediate cavity upper end cap.
Described intermediate cavity upper end cap, intermediate cavity urceolus, intermediate cavity lower end cap, upper conical spring, floating piston and inferior pyramidal spring form intermediate cavity assembly, and described intermediate cavity assembly is arranged between piston rod and piston assembly.
Described intermediate cavity upper end cap is connected with piston rod, has the aperture for fluid circulation on it.
Described intermediate cavity urceolus is connected with intermediate cavity upper end cap, is connected with intermediate cavity lower end cap, has the aperture for fluid circulation on it.
On described intermediate cavity lower end cap, have fluid opening, and be punctured into thin wall small hole in bottom.
Described intermediate cavity upper end cap, intermediate cavity urceolus, intermediate cavity lower end cap surround an intermediate cavity jointly, and floating piston is divided into epicoele A and cavity of resorption B by intermediate cavity, and floating piston and intermediate cavity urceolus are Spielpassung.
The present invention has the following advantages and good effect:
When 1, vehicle travels in good road surface, vibration damper of the present invention can provide less suspension damping, thereby reduces the vibration that is passed to vehicle body, reduces vehicle body vertical acceleration root-mean-square value, improves riding comfort.
When 2, vehicle runs into unexpected bump, vibration damper of the present invention can provide less damping in suspension initial compression stroke, thereby significantly reduces the most responsive vehicle body vertical acceleration peak value of human body, greatly improves ride quality.
When 3, vehicle travels on the cross-country road of big rise and fall, vibration damper of the present invention can provide larger suspension damping, thereby reduces the moving stroke of suspension and tire dynamic load, reduces the probability that suspension punctures, guarantee that good road surface adheres to condition, improve driving safety.
4, during Vehicular turn, suspension motion amplitude is larger, vibration damper of the present invention can provide larger suspension damping, make vehicle there is less inclination angle, turn side and shorter yaw velocity peak response time, thereby guarantee that vehicle has good control stability, driving safety and the subjective sensation of driving.
5, the present invention, without complicated sensor detector, actuator and control system are installed on vehicle, is a kind of pure passive vibration damper scheme, simple and reliable for structure, with low cost, is easy to popularize.
6, vibration damper scheme of the present invention can get through simple transformation on existing common dual-tube shock absorber, monotubular shock absorber or hydro-pneumatic spring, both be suitable for personal preference person and carried out simple suspension repacking, also be suitable for enterprise and quantize to produce, to obtain good economic benefit.
7, the present invention is specially adapted to the higher vehicles of barycenter such as SUV, MPV, lorry, these vehicles are to prevent that vehicle body from excessively rolling and guaranteeing good control stability, it is harder that suspension all designs, and often to sacrifice the cost of riding comfort, exchanges good control stability and driving safety for.The relevant vibration damper of amplitude can make a distinction the different driving cycle of car load, not reducing under the prerequisite of control stability and driving safety, farthest improves travelling comfort.
Accompanying drawing explanation
Fig. 1 is the overall structure figure of the relevant vibration damper of amplitude.
Fig. 2 is the partial enlarged drawing of the relevant vibration damper of amplitude.
Fig. 3 is the indicator diagram of the relevant vibration damper of amplitude.
Fig. 4 is the speed characteristic figure of the relevant vibration damper of amplitude.
Embodiment
As shown in Figure 1, this vibration damper comprises: upper end cap 1, outside framework oil seal 2, guider 3, inner cylinder tube 4, outer cylinder 5, piston assembly 15, bottom valve assembly 17, hanger 18, it is characterized in that: it also comprises piston rod 6, the intermediate cavity upper end cap 9 being threaded with piston rod 6, be assemblied in the one-way valve assembly being formed by spring 7 and bead 8 between piston rod 6 and intermediate cavity upper end cap 9, the intermediate cavity urceolus 11 being welded to connect with intermediate cavity upper end cap 9, the intermediate cavity lower end cap 14 being threaded with intermediate cavity urceolus 11, in described intermediate cavity, be provided with upper conical spring 10, floating piston 12 and inferior pyramidal spring 13, upper conical spring 10 and inferior pyramidal spring 13 are welded to connect with intermediate cavity upper end cap 9 and intermediate cavity lower end cap 14 respectively, tightening nut 16 is fixed on piston assembly 15 on intermediate cavity lower end cap 14.
As shown in Figure 2, on described piston rod 6, have sulculus 20, and having aperture 21 near sulculus 20 bottoms, check valve spring 7 and one-way valve bead 8 are assemblied in sulculus 20, and piston rod 6 is threaded with intermediate cavity upper end cap 9.
Described intermediate cavity upper end cap 9, intermediate cavity urceolus 11, intermediate cavity lower end cap 14, upper conical spring 10, floating piston 12 and inferior pyramidal spring 13 form intermediate cavity assembly, and described intermediate cavity assembly is arranged between piston rod 6 and piston assembly 15.
Described intermediate cavity upper end cap 9 is threaded with piston rod 6, has the aperture 22 for fluid circulation on it.
Described intermediate cavity urceolus 11 is welded to connect with intermediate cavity upper end cap 9, is threaded with intermediate cavity lower end cap 14, has the aperture 23 for fluid circulation on it.
On described intermediate cavity lower end cap 14, have fluid opening 24, and be punctured into thin wall small hole 25 in bottom.
Described intermediate cavity upper end cap 9, intermediate cavity urceolus 11, intermediate cavity lower end cap 14 surround an intermediate cavity jointly, floating piston 12 is divided into epicoele A and cavity of resorption B by intermediate cavity, floating piston 12 is Spielpassung with intermediate cavity urceolus 11, and center-aisle F and main piston valve are that G has formed the fluid circulation passage between vibration damper rod chamber C and rodless cavity D jointly.
Working principle:
When vehicle travels in good road surface, the road excitation amplitude running into is smaller, and the fluid amount of flow in vibration damper between rod chamber C, rodless cavity D and shoe cream room E is also very little.Now the floating piston in intermediate cavity 12 can slightly fluctuate in scope up and down, and fluid can flow swimmingly by center-aisle F between rod chamber C and rodless cavity D.Because center-aisle F and main piston valve are that G has and can flow oil, the damping force that vibration damper provides is smaller, and Uneven road excitation is difficult to be delivered to vehicle body gets on, thereby has guaranteed good run smoothness.
When vehicle travels on severe road surface, the road excitation amplitude running into is very large, and the fluid amount of flow in vibration damper between rod chamber C, rodless cavity D and shoe cream room E is also very large.Now the floating piston in intermediate cavity 12 moves to soon the spacing position of the upper and lower end cap 9,14 of intermediate cavity under the promotion of fluid.Floating piston 12 moves to behind spacing position, and center-aisle F closes, and fluid can only be that G flows between rod chamber and rodless cavity by main piston valve, and the damping ratio that vibration damper provides is larger.The vibration that so both can guarantee amplitude can promptly attenuate, can guarantee that again the moving stroke of tire dynamic load and suspension is unlikely excessive, there will not be suspension frequently to clash into limiting stopper and jump out of the danger situation that ground cannot apply driving force, braking force and lateral force because of tire.
When vehicle runs into unexpected bump excitation, although the motion amplitude of vibration damper can be larger, but in the starting stage that runs into excitation, floating piston 12 is moved in the spacing position process of intermediate cavity upper end cap 9 by the Support Position of inferior pyramidal spring 13, and it is that two paths of G flow into rod chamber C that the fluid in rodless cavity D remains by center-aisle F and main piston valve.In this process, there will be road excitation to be passed to first vertical acceleration peak value of vehicle body, because the damping that vibration damper provides is smaller, first vertical acceleration peak value that is passed to vehicle body also can be smaller.Because human body is very responsive to this acceleration peak value, thereby make its value reduction can greatly improve riding comfort.After floating piston moves to spacing position, center-aisle F closes, and resistance of shock absorber increases, and then can make vibration attenuate rapidly.
When Vehicular turn, vehicle body rolls to a side, if it is larger to roll Amplitude Ratio, can mediate the respectively spacing position of the upper and lower end cap 14 in chamber of floating piston 12 in the relevant vibration damper of the amplitude of left and right side suspension, damping force is larger, and suspension is harder, thereby can prevent that vehicle body from producing further excessively inclination, improved vehicle roll stability, guaranteed that vehicle has the shorter yaw velocity peak response time simultaneously.
On piston rod 6, have sulculus 20, near sulculus 20 bottoms, having aperture 21, the part on sulculus 20 dark small holes 21 summits provides fitting seat for check valve spring 7, and one-way valve bead 8 tightly leans against on intermediate cavity upper end cap 9 under the extruding of check valve spring 7.
If the ground that vehicle runs into projection excitation is more violent, the fluid in A chamber can be pushed one-way valve open by aperture 22, further reduces the damping force that vibration damper provides, to farthest reduce first vertical acceleration peak value, improves riding comfort.
As shown in Figure 3, Figure 4, the relevant vibration damper of amplitude is applied to standard sine excitation, if the amplitude of excitation is little, the damping force that vibration damper produces is smaller; If excitation amplitude is larger, after the floating piston motion LAP in intermediate cavity, can close center-aisle F, make vibration damper produce larger damping force.
Claims (7)
1. the relevant vibration damper of an amplitude, this vibration damper comprises: upper end cap, outside framework oil seal, guider, inner cylinder tube, outer cylinder, piston assembly, bottom valve assembly, hanger, it is characterized in that: it also comprises piston rod, the intermediate cavity upper end cap being connected with piston rod thread, be assemblied in the one-way valve assembly being formed by spring and bead between piston rod and intermediate cavity upper end cap, the intermediate cavity urceolus being connected with intermediate cavity upper end cap, the intermediate cavity lower end cap being connected with intermediate cavity urceolus, in described intermediate cavity, be provided with upper conical spring, floating piston and inferior pyramidal spring, upper conical spring is connected with intermediate cavity lower end cap with intermediate cavity upper end cap respectively with inferior pyramidal spring, tightening nut is fixed on piston assembly on intermediate cavity lower end cap.
2. the relevant vibration damper of a kind of amplitude according to claim 1, it is characterized in that: on described piston rod, have sulculus, and near sulculus bottom, having aperture, check valve spring and one-way valve bead are assemblied in sulculus, and piston rod is connected with intermediate cavity upper end cap.
3. the relevant vibration damper of a kind of amplitude according to claim 1, it is characterized in that: described intermediate cavity upper end cap, intermediate cavity urceolus, intermediate cavity lower end cap, upper conical spring, floating piston and inferior pyramidal spring form intermediate cavity assembly, and described intermediate cavity assembly is arranged between piston rod and piston assembly.
4. the relevant vibration damper of a kind of amplitude according to claim 1, is characterized in that: described intermediate cavity upper end cap is connected with piston rod, has the aperture for fluid circulation on it.
5. the relevant vibration damper of a kind of amplitude according to claim 1, is characterized in that: described intermediate cavity urceolus is connected with intermediate cavity upper end cap, is connected with intermediate cavity lower end cap, has the aperture for fluid circulation on it.
6. the relevant vibration damper of a kind of amplitude according to claim 1, is characterized in that: on described intermediate cavity lower end cap, have fluid opening, and be punctured into thin wall small hole in bottom.
7. the relevant vibration damper of a kind of amplitude according to claim 1, it is characterized in that: described intermediate cavity upper end cap, intermediate cavity urceolus, intermediate cavity lower end cap surround an intermediate cavity jointly, floating piston is divided into epicoele A and cavity of resorption B by intermediate cavity, and floating piston and intermediate cavity urceolus are Spielpassung.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201320584376.2U CN203477157U (en) | 2013-09-22 | 2013-09-22 | Amplitude related shock absorber |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201320584376.2U CN203477157U (en) | 2013-09-22 | 2013-09-22 | Amplitude related shock absorber |
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| Publication Number | Publication Date |
|---|---|
| CN203477157U true CN203477157U (en) | 2014-03-12 |
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| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201320584376.2U Expired - Lifetime CN203477157U (en) | 2013-09-22 | 2013-09-22 | Amplitude related shock absorber |
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| CN (1) | CN203477157U (en) |
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN104455164A (en) * | 2014-12-15 | 2015-03-25 | 重庆东安渠强机械制造有限公司 | Damping shock absorber for motorcycle |
| CN112145603A (en) * | 2019-06-26 | 2020-12-29 | 广州汽车集团股份有限公司 | Vehicle shock absorber, vehicle suspension structure and vehicle |
| CN112747063A (en) * | 2019-10-31 | 2021-05-04 | 比亚迪股份有限公司 | Vibration damper, energy conversion device and vehicle |
-
2013
- 2013-09-22 CN CN201320584376.2U patent/CN203477157U/en not_active Expired - Lifetime
Cited By (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN104455164A (en) * | 2014-12-15 | 2015-03-25 | 重庆东安渠强机械制造有限公司 | Damping shock absorber for motorcycle |
| CN104455164B (en) * | 2014-12-15 | 2016-06-22 | 重庆东安渠强机械制造有限公司 | Motorcycle damping shock absorber |
| CN112145603A (en) * | 2019-06-26 | 2020-12-29 | 广州汽车集团股份有限公司 | Vehicle shock absorber, vehicle suspension structure and vehicle |
| CN112747063A (en) * | 2019-10-31 | 2021-05-04 | 比亚迪股份有限公司 | Vibration damper, energy conversion device and vehicle |
| CN112747063B (en) * | 2019-10-31 | 2022-06-14 | 比亚迪股份有限公司 | Vibration damper, energy conversion device and vehicle |
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Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| GR01 | Patent grant | ||
| GR01 | Patent grant | ||
| C56 | Change in the name or address of the patentee |
Owner name: CHANGCHUN KONGHUI AUTOMATIVE TECHNOLOGY CO., LTD. Free format text: FORMER NAME: KH AUTOMOTIVE TECHNOLOGIES (CHANGCHUN) CO., LTD. |
|
| CP01 | Change in the name or title of a patent holder |
Address after: 130012 Jilin province Changchun Chaoda high tech Industrial Development Zone, Road No. 5177 Patentee after: KH AUTOMOTIVE TECHNOLOGIES (CHANGCHUN) CO.,LTD. Address before: 130012 Jilin province Changchun Chaoda high tech Industrial Development Zone, Road No. 5177 Patentee before: KH AUTOMOTIVE TECHNOLOGIES (CHANGCHUN) Co.,Ltd. |
|
| TR01 | Transfer of patent right | ||
| TR01 | Transfer of patent right |
Effective date of registration: 20230827 Address after: 313000 Building 1, No. 788 Xifeng Road, South Taihu New District, Wuxing District, Huzhou City, Zhejiang Province Patentee after: Zhejiang Kong Hui Automobile Technology Co.,Ltd. Address before: 130012 No. 5177 Chaoda Road, Changchun High-tech Industrial Development Zone, Jilin Province Patentee before: KH AUTOMOTIVE TECHNOLOGIES (CHANGCHUN) CO.,LTD. |
|
| CX01 | Expiry of patent term | ||
| CX01 | Expiry of patent term |
Granted publication date: 20140312 |