CN104455160A - Amplitude-dependent damper - Google Patents
Amplitude-dependent damper Download PDFInfo
- Publication number
- CN104455160A CN104455160A CN201310446234.4A CN201310446234A CN104455160A CN 104455160 A CN104455160 A CN 104455160A CN 201310446234 A CN201310446234 A CN 201310446234A CN 104455160 A CN104455160 A CN 104455160A
- Authority
- CN
- China
- Prior art keywords
- intermediate cavity
- end cap
- vibration damper
- piston
- piston rod
- 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.)
- Pending
Links
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
- F16F9/00—Springs, vibration-dampers, shock-absorbers, or similarly-constructed movement-dampers using a fluid or the equivalent as damping medium
- F16F9/10—Springs, vibration-dampers, shock-absorbers, or similarly-constructed movement-dampers using a fluid or the equivalent as damping medium using liquid only; using a fluid of which the nature is immaterial
- F16F9/14—Devices with one or more members, e.g. pistons, vanes, moving to and fro in chambers and using throttling effect
- F16F9/16—Devices with one or more members, e.g. pistons, vanes, moving to and fro in chambers and using throttling effect involving only straight-line movement of the effective parts
- F16F9/18—Devices with one or more members, e.g. pistons, vanes, moving to and fro in chambers and using throttling effect involving only straight-line movement of the effective parts with a closed cylinder and a piston separating two or more working spaces therein
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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
- F16F9/00—Springs, vibration-dampers, shock-absorbers, or similarly-constructed movement-dampers using a fluid or the equivalent as damping medium
- F16F9/32—Details
- F16F9/50—Special means providing automatic damping adjustment, i.e. self-adjustment of damping by particular sliding movements of a valve element, other than flexions or displacement of valve discs; Special means providing self-adjustment of spring characteristics
- F16F9/512—Means responsive to load action, i.e. static load on the damper or dynamic fluid pressure changes in the damper, e.g. due to changes in velocity
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- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Physics & Mathematics (AREA)
- Fluid Mechanics (AREA)
- Vehicle Body Suspensions (AREA)
Abstract
The invention relates to an amplitude-dependent damper. The damper 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, and is characterized by further comprising a piston rod, an intermediate cavity upper end cover connected with the piston rod through threads, a one-way valve assembly assembled between the piston rod and the intermediate cavity upper end cover and composed of a spring and a small ball, an intermediate cavity outer barrel connected with the intermediate cavity upper end cover and an intermediate cavity lower end cover connected with the intermediate cavity outer barrel. An upper conical spring, a floating piston and a lower conical spring are arranged in an intermediate cavity, and the upper conical spring and the lower conical spring are connected with the intermediate cavity upper end cover and the intermediate cavity lower end cover respectively. The piston assembly is fixed to the intermediate cavity lower end cover through a fastening nut. The damper can recognize different running conditions of a vehicle and adjust the damping characteristics according to the different running conditions of the vehicle, so that high riding comfort, high steering stability and high running safety are guaranteed.
Description
Technical field
The present invention relates to a kind of vibration damper on automotive suspension, the amplitude that a kind of damping characteristic can change with excitation amplitude is specifically correlated with vibration damper.
Background technique
The different performance of automobile is to the demand of suspension damping contradiction often: for improving riding comfort, reducing the vibration of sprung weight, suspension damping should be made to arrange lower; Move stroke for reduction tyre dynamic load lotus and suspension, suspension damping should be made to arrange higher; From the viewpoint of the control stability of car load, for reach reduce turn to time car body obliqueness and the object of steering response time, also should make suspension design obtain " firmly " some.Therefore the coupling of automotive suspension damping is generally consider the half-way house that automobile various aspects of performance takes.
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 make corresponding change according to the different applying working condition of vehicle, therefore be difficult to the contradiction dissolved between the different performance such as control stability, riding comfort, driving safety of vehicle, vehicle performance under different applying working condition can not be made all to reach best.
The Active suspension technology of rising in recent years can according to the motion of automobile and pavement behavior, and in time the rigidity of adjustable suspension and damping, make it be in best vibration damping state all the time.But this kind of technology needs to install complicated sensor detector, actuator and controller on vehicle.Compared with common passive suspension, it is with high costs, poor reliability, is difficult to popularize.
The present invention proposes amplitude that a kind of damping characteristic can change with Suspension movement amplitude to be correlated with vibration damper, when vehicle travels in good road surface, this vibration damper can provide less damping, ensures good riding comfort; When Vehicular turn or jolt road surface travels time, this vibration damper can provide larger damping, ensures good control stability and driving safety.There is provided different damping characteristics by distinguishing the different driving cycle of vehicle, this vibration damper can solve the different performance of vehicle preferably to the contradiction of suspension damping demand.
Summary of the invention
The amplitude that the object of the invention is to provide a kind of damping characteristic to change with Suspension movement amplitude is correlated with vibration damper, it can pick out the different driving cycle of vehicle, as good road surface, severe road surface, significantly roll, and its damping characteristic can be regulated by the driving cycle different according to vehicle.When Suspension movement amplitude is less, the damping that this vibration damper provides is also less, thus ensures good riding comfort; When Suspension movement amplitude is larger, the damping that this vibration damper provides is also comparatively large, thus ensures 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 be connected with piston rod thread, be assemblied in the one-way valve assembly be made up of spring and bead between piston rod and intermediate cavity upper end cap, the intermediate cavity urceolus be connected with intermediate cavity upper end cap, the intermediate cavity lower end cap be connected with intermediate cavity urceolus, upper conical spring is provided with in described intermediate cavity, floating piston and inferior pyramidal spring, upper conical spring is connected with intermediate cavity upper end cap and intermediate cavity lower end cap respectively with inferior pyramidal spring, piston assembly is fixed on intermediate cavity lower end cap by tightening nut.
Described piston rod has sulculus, and is having aperture near little groove 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, it has the aperture for fluid circulation.
Described intermediate cavity urceolus is connected with intermediate cavity upper end cap, is connected with intermediate cavity lower end cap, it has the aperture for fluid circulation.
Described intermediate cavity lower end cap has fluid opening, and is 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 intermediate cavity is divided into epicoele A and cavity of resorption B by floating piston, and floating piston and intermediate cavity urceolus are Spielpassung.
The present invention has the following advantages and good effect:
1, when vehicle travels in good road surface, vibration damper of the present invention can provide less suspension damping, thus reduces the vibration being passed to vehicle body, reduces vehicle body vertical acceleration root-mean-square value, improves riding comfort.
2, when vehicle runs into unexpected bump, vibration damper of the present invention can provide less damping in suspension initial compression stroke, thus significantly reduces the most responsive vehicle body vertical acceleration peak value of human body, greatly improves ride quality.
3, when vehicle travels on the cross-country road of big rise and fall, vibration damper of the present invention can provide larger suspension damping, thus reduction suspension moves stroke and tyre dynamic load lotus, reduces the probability that suspension punctures, ensure good road surface attachment condition, improve driving safety.
4, during Vehicular turn, Suspension movement amplitude is larger, vibration damper of the present invention can provide larger suspension damping, make vehicle have less inclination angle, turn side and shorter yaw velocity peak response time, thus ensure that vehicle has good control stability, driving safety and subjective driving and feels.
5, the present invention without the need to installing complicated sensor detector, actuator and control system on vehicle, is a kind of pure passive vibration damper scheme, simple and reliable for structure, with low cost, is easy to universal.
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 carry out simple suspension repacking, also be suitable for enterprise and carry out quantification production, to obtain good economic benefit.
7, the present invention is specially adapted to the higher vehicle of the barycenter such as SUV, MPV, lorry, these vehicles are prevent vehicle body from excessively rolling and ensure good control stability, it is harder that suspension all designs, and often exchanges good control stability and driving safety for the cost of sacrificing riding comfort.Driving cycles different for car load can make a distinction by amplitude vibration damper of being correlated with, and under the prerequisite not reducing control stability and driving safety, farthest improves travelling comfort.
Accompanying drawing explanation
Fig. 1 is that amplitude is correlated with the overall structure figure of vibration damper.
Fig. 2 is that amplitude is correlated with the partial enlarged drawing of vibration damper.
Fig. 3 is that amplitude is correlated with the indicator diagram of vibration damper.
Fig. 4 is that amplitude is correlated with the speed characteristic figure of vibration damper.
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 be threaded with piston rod 6, be assemblied in the one-way valve assembly be made up of spring 7 and bead 8 between piston rod 6 and intermediate cavity upper end cap 9, the intermediate cavity urceolus 11 be welded to connect with intermediate cavity upper end cap 9, the intermediate cavity lower end cap 14 be threaded with intermediate cavity urceolus 11, upper conical spring 10 is provided with in described intermediate cavity, 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, piston assembly 15 is fixed on intermediate cavity lower end cap 14 by tightening nut 16.
As shown in Figure 2, described piston rod 6 has sulculus 20, and having aperture 21 bottom sulculus 20, 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, it has the aperture 22 for fluid circulation.
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, it has the aperture 23 for fluid circulation.
Described intermediate cavity lower end cap 14 has fluid opening 24, and is 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, intermediate cavity is divided into epicoele A and cavity of resorption B by floating piston 12, floating piston 12 and intermediate cavity urceolus 11 are Spielpassung, and center-aisle F and main piston valve system G together constitutes the fluid circulation passage between vibration damper rod chamber C and rodless cavity D.
Working principle:
When vehicle travels in good road surface, the road excitation amplitude com parison run into is little, 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.Floating piston 12 now in intermediate cavity can fluctuate up and down in small size scope, and fluid can be flowed swimmingly by center-aisle F between rod chamber C and rodless cavity D.Because center-aisle F and main piston valve system 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 and gets on, and thus ensure that good run smoothness.
When vehicle travels on severe road surface, the road excitation amplitude run 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.Floating piston 12 now in intermediate cavity moves to the restraining position of the upper and lower end cap 9,14 of intermediate cavity soon under the promotion of fluid.After floating piston 12 moves to restraining position, center-aisle F closes, and fluid can only be flowed between rod chamber and rodless cavity by main piston valve system G, and the damping ratio that vibration damper provides is larger.So both can ensure that the vibration of amplitude can promptly attenuate, can ensure that again tyre dynamic load lotus and suspension move stroke unlikely excessive, there will not be suspension frequently to clash into limiting stopper and the danger situation of driving force, braking force and lateral force cannot be applied because tire jumps out of ground.
When vehicle runs into unexpected bump excitation, although the motion amplitude of vibration damper can be larger, but in the starting stage running into excitation, floating piston 12 moves in the restraining position process of intermediate cavity upper end cap 9 by the Support Position of inferior pyramidal spring 13, and the fluid in rodless cavity D remains and flows into rod chamber C by center-aisle F and main piston valve system G two paths.In this process, there will be first vertical acceleration peak value that road excitation is passed to vehicle body, the damping provided due to vibration damper is smaller, and first the vertical acceleration peak value being passed to vehicle body also can be smaller.Because human body is very responsive to this acceleration peak value, thus making its value reduce can improve riding comfort greatly.Move to after restraining position until floating piston, center-aisle F closes, and resistance of shock absorber increases, and then vibration can be made to attenuate rapidly.
When Vehicular turn, vehicle body rolls to side, if it is larger to roll Amplitude Ratio, the floating piston 12 that the amplitude of left and right side suspension is correlated with in vibration damper can mediate the restraining position of the upper and lower end cap 14 in chamber respectively, damping force is larger, and suspension is harder, thus can prevent vehicle body from producing and further excessively roll, improve vehicle roll stability, ensure that vehicle has the shorter yaw velocity peak response time simultaneously.
Piston rod 6 has sulculus 20, bottom sulculus 20, having aperture 21, the part on dark small holes 21 summit of sulculus 20 is that check valve spring 7 provides fitting seat, 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 projection excitation that vehicle runs into is relatively more violent, one-way valve can be pushed open by aperture 22 by the fluid in A chamber, reduces the damping force that vibration damper provides further, farthest to reduce by first vertical acceleration peak value, improves riding comfort.
As shown in Figure 3, Figure 4, to amplitude be correlated with vibration damper apply standard sine excitation, if excitation amplitude little, the damping force that vibration damper produces is smaller; If excitation amplitude is larger, after the floating piston motion LAP in intermediate cavity, center-aisle F can be closed, make vibration damper produce larger damping force.
Claims (7)
1. an amplitude is correlated with vibration damper, 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 be connected with piston rod thread, be assemblied in the one-way valve assembly be made up of spring and bead between piston rod and intermediate cavity upper end cap, the intermediate cavity urceolus be connected with intermediate cavity upper end cap, the intermediate cavity lower end cap be connected with intermediate cavity urceolus, upper conical spring is provided with in described intermediate cavity, floating piston and inferior pyramidal spring, upper conical spring is connected with intermediate cavity upper end cap and intermediate cavity lower end cap respectively with inferior pyramidal spring, piston assembly is fixed on intermediate cavity lower end cap by tightening nut.
2. a kind of amplitude according to claim 1 is correlated with vibration damper, it is characterized in that: described piston rod has sulculus, and having aperture near little groove bottom, check valve spring and one-way valve bead are assemblied in sulculus, and piston rod is connected with intermediate cavity upper end cap.
3. a kind of amplitude according to claim 1 is correlated with vibration damper, 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. a kind of amplitude according to claim 1 is correlated with vibration damper, it is characterized in that: described intermediate cavity upper end cap is connected with piston rod, it has the aperture for fluid circulation.
5. a kind of amplitude according to claim 1 is correlated with vibration damper, it is characterized in that: described intermediate cavity urceolus is connected with intermediate cavity upper end cap, is connected with intermediate cavity lower end cap, it has the aperture for fluid circulation.
6. a kind of amplitude according to claim 1 is correlated with vibration damper, it is characterized in that: described intermediate cavity lower end cap has fluid opening, and is punctured into thin wall small hole in bottom.
7. a kind of amplitude according to claim 1 is correlated with vibration damper, it is characterized in that: described intermediate cavity upper end cap, intermediate cavity urceolus, intermediate cavity lower end cap surround an intermediate cavity jointly, intermediate cavity is divided into epicoele A and cavity of resorption B by floating piston, and floating piston and intermediate cavity urceolus are Spielpassung.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201310446234.4A CN104455160A (en) | 2013-09-22 | 2013-09-22 | Amplitude-dependent damper |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201310446234.4A CN104455160A (en) | 2013-09-22 | 2013-09-22 | Amplitude-dependent damper |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN104455160A true CN104455160A (en) | 2015-03-25 |
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Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201310446234.4A Pending CN104455160A (en) | 2013-09-22 | 2013-09-22 | Amplitude-dependent damper |
Country Status (1)
| Country | Link |
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| CN (1) | CN104455160A (en) |
Cited By (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN106286676A (en) * | 2015-06-10 | 2017-01-04 | 广州汽车集团股份有限公司 | Vibroshock, vehicle suspension and vehicle |
| CN106763428A (en) * | 2017-03-07 | 2017-05-31 | 汽-大众汽车有限公司 | A kind of double offset frequency mutative damp shock absorbers of passive type |
| CN107013621A (en) * | 2017-05-03 | 2017-08-04 | 浙江正裕工业股份有限公司 | Vibration damper with adjustable damping |
| CN108488304A (en) * | 2018-06-20 | 2018-09-04 | 河南工学院 | Lightweight suspension damping |
Citations (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US4535877A (en) * | 1982-07-14 | 1985-08-20 | Tokico Ltd. | Hydraulic damper of adjustable damping force type |
| US20050011712A1 (en) * | 2003-04-11 | 2005-01-20 | Ole Gotz | Dashpot with amplitude-dependent shock absorption |
| CN101451585A (en) * | 2007-12-05 | 2009-06-10 | 株式会社万都 | Shock absorber |
| CN202790291U (en) * | 2012-07-18 | 2013-03-13 | 宁波南方减震器制造有限公司 | Double-cylinder high-pressure shock absorber with floating piston assembly |
-
2013
- 2013-09-22 CN CN201310446234.4A patent/CN104455160A/en active Pending
Patent Citations (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US4535877A (en) * | 1982-07-14 | 1985-08-20 | Tokico Ltd. | Hydraulic damper of adjustable damping force type |
| US20050011712A1 (en) * | 2003-04-11 | 2005-01-20 | Ole Gotz | Dashpot with amplitude-dependent shock absorption |
| CN101451585A (en) * | 2007-12-05 | 2009-06-10 | 株式会社万都 | Shock absorber |
| CN202790291U (en) * | 2012-07-18 | 2013-03-13 | 宁波南方减震器制造有限公司 | Double-cylinder high-pressure shock absorber with floating piston assembly |
Cited By (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN106286676A (en) * | 2015-06-10 | 2017-01-04 | 广州汽车集团股份有限公司 | Vibroshock, vehicle suspension and vehicle |
| CN106286676B (en) * | 2015-06-10 | 2018-07-06 | 广州汽车集团股份有限公司 | Damper, vehicle suspension and vehicle |
| CN106763428A (en) * | 2017-03-07 | 2017-05-31 | 汽-大众汽车有限公司 | A kind of double offset frequency mutative damp shock absorbers of passive type |
| CN106763428B (en) * | 2017-03-07 | 2019-03-08 | 一汽-大众汽车有限公司 | A kind of double offset frequency variable damping dampers of passive type |
| CN107013621A (en) * | 2017-05-03 | 2017-08-04 | 浙江正裕工业股份有限公司 | Vibration damper with adjustable damping |
| CN108488304A (en) * | 2018-06-20 | 2018-09-04 | 河南工学院 | Lightweight suspension damping |
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| C06 | Publication | ||
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| C53 | Correction of patent of invention or patent application | ||
| CB02 | Change of applicant information |
Address after: 130312 Jilin province Changchun Chaoda high tech Industrial Development Zone, Road No. 5177 Applicant after: Changchun Konghui Automative Technology Co., Ltd. Address before: 130012 Jilin province Changchun Chaoda high tech Industrial Development Zone, Road No. 5177 Applicant before: KH Automotive Technologies (Changchun) Co., Ltd. |
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| COR | Change of bibliographic data |
Free format text: CORRECT: APPLICANT; FROM: KH AUTOMOTIVE TECHNOLOGIES (CHANGCHUN) CO., LTD. TO: CHANGCHUN KONGHUI AUTOMATIVE TECHNOLOGY CO., LTD. Free format text: CORRECT: ADDRESS; FROM: 130012 CHANGCHUN, JILIN PROVINCE TO: 130312 CHANGCHUN, JILIN PROVINCE |
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| RJ01 | Rejection of invention patent application after publication |
Application publication date: 20150325 |
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| RJ01 | Rejection of invention patent application after publication |