CN203847618U - Sliding piston type amplitude correlation damper valve - Google Patents
Sliding piston type amplitude correlation damper valve Download PDFInfo
- Publication number
- CN203847618U CN203847618U CN201420283569.9U CN201420283569U CN203847618U CN 203847618 U CN203847618 U CN 203847618U CN 201420283569 U CN201420283569 U CN 201420283569U CN 203847618 U CN203847618 U CN 203847618U
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- piston
- piston rod
- amplitude
- valve
- auxiliary flow
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Abstract
The utility model discloses a sliding piston type amplitude correlation damper valve which comprises a piston rod, a piston arranged at the lower end of the piston rod, a nut fixed to the lower end of the piston rod and a work cylinder arranged on the outer side of the piston in an embedded and sleeved mode. The piston and the piston rod are connected in a sliding mode, and the piston rod is provided with an auxiliary flow channel; the auxiliary flow channel is opened when the piston vibrates in a small amplitude and is closed when the piston vibrates in a large amplitude; an upper spring is disposed between the upper side of the piston and a shaft shoulder of the piston rod, a lower spring is arranged between the lower side of the piston and the nut, and the two springs are in a compressed state; the piston is provided with a restoring valve system and a compression valve system. When the damper valve is used for a vehicle suspension vibration damper, the damper valve can provide small suspension damping when a vehicle runs on a good road, so that vibration transmitted to a vehicle body is reduced and ride comfort is improved. When the vehicle runs on a bumpy cross-country road, large suspension damping is provided, driving safety is improved, and the damper valve is simple and reliable in structure, low in cost and easy to popularize.
Description
Technical field
The utility model belongs to orifice valve technical field, is specifically related to the relevant orifice valve of sliding piston formula amplitude that a kind of damping characteristic can change with excitation amplitude.
Background technique
The different performance of automobile is to the demand of suspension damping contradiction often: if wish to improve riding comfort, reduce the vibration of sprung weight, should make the suspension damping arrange lowlyer; If wish 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, if wish 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, be provided with rebound valve, compression valve, recuperation valve and flowing valve.When vehicle frame (or monocoque body) and vehicle bridge relative movement, the piston of vibration damper will be reciprocating in cylinder barrel, and the fluid in active chamber can be by each valve, produce damping force, thus vibration and the impact of decay ground and motor.The size of its damping depends on the flexible size of each valve member valve block group, and after shock absorber valve sheet assembles, the damping property of vibration damper is also just definite, and its performance generally can not automatically be adjusted according to operating mode in Vehicle Driving Cycle process.Above-mentioned valve is after determining, the damping force of common vibration damper 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.Adopt Active suspension or semi-active suspension to address this problem preferably, but need to add large quantity sensor, and need outside energy input, cost is higher.
U. S. Patent (US8201669B2) discloses a kind of amplitude Sensitive Damping device, and it adopts double-piston mechanism, and wherein upper piston is sliding piston, and lower piston is traditional damper piston, and upper piston does not play damping function when little amplitude, and now damping is less; When excitation amplitude is larger, lower piston and upper piston are equivalent to series damped hole, and damping force is provided together, and damping is larger.Owing to having adopted double-piston, make the complexity of package unit increase, the upper piston of slip has also occupied the stroke of vibration damper.
U. S. Patent (US20070125610) discloses a kind of damper of selecting damping device with amplitude, its upside piston rod at traditional damper piston is provided with one with the cavity of auxiliary flow, cavity inside is provided with the small piston of floating drum, at excitation amplitude hour, auxiliary flow is equivalent in parallel with main piston valve system, fluid circulation area is larger, and little damping is provided; When excitation amplitude continues to increase, unsteady small piston moves to the limit, closes auxiliary flow, and large damping is provided.The balance preferably of this scheme vehicle travelling comfort and control stability, and be successfully applied to the C series car of benz.But its scheme is more complicated, and cost is higher.
For the accuracy of follow-up introduction, " amplitude " defined: described " amplitude " refers to " instantaneous stroke ", piston rod starts reversing motion from lastrow journey terminal herein, and then the displacement forming.
Summary of the invention
The purpose of this utility model is to propose the relevant orifice valve of sliding piston formula amplitude that a kind of damping characteristic can change with excitation amplitude, can when little excitation amplitude, provide less damping, and larger damping is provided while encouraging amplitude greatly.
The utility model, for solving the problems of the technologies described above, is achieved through the following technical solutions:
The sliding piston formula amplitude orifice valve of being correlated with, comprises piston rod 1, is arranged on the piston 3 of piston rod 1 lower end, be fixed on the nut 5 of piston rod 1 lower end, and the clutch release slave cylinder 6 that is nested in piston 3 outsides, described piston 3 is slidably connected with piston rod 1, and piston rod 1 is provided with auxiliary flow 1-1; Described auxiliary flow 1-1 opens when piston 3 small amplitude motion, when piston 3 large-amplitude vibration, closes.
Described piston 3 is provided with resetting valve system 3-1 and compression valves system 3-2.
Preferably, between described piston 3 upsides and the shaft shoulder of piston rod 1, upper spring 2 is installed, 4, two springs of lower spring is installed all in compressive state between piston 3 downsides and nut 5.
Preferably, described auxiliary flow 1-1 is the bypass groove on piston rod 1 downside outer wall, now piston rod 1 part that is formed in one.
Orifice valve of the present utility model can be applicable to the sprung parts such as automobile single-tube inflating shock absorber, dual-tube shock absorber and hydro pneumatic suspension, also can be used for automotive seat vibration damper, also can be used in other parts that damping need to be provided.
Below with the utility model for shock absorber of automobile suspension, and piston rod 1 is example in restoring stroke, introduces working procedure of the present utility model:
When piston rod 1 small amplitude motion, the high-voltage oil liquid of piston 3 epicoeles flows into piston 3 cavity of resorptions by resetting valve system 3-1 and auxiliary flow 1-1 simultaneously; Meanwhile, piston 3 is down sliding under oil liquid pressure effect, and upper spring 2 is stretched, and lower spring 4 is compressed; But because excitation amplitude is less, piston 3 is not enough to stop up the downside aperture of auxiliary flow 1-1; Now, the circulation area of fluid is larger, so the damping force that piston rod 1 is subject to is less;
When the amplitude of piston rod 1 continues to increase, piston 3 continues down sliding under oil liquid pressure effect, and piston 3 will stop up the downside aperture of auxiliary flow 1-1; Now, the high-voltage oil liquid of piston 3 epicoeles can only flow into piston 3 cavity of resorptions by resetting valve system 3-1, and the circulation area of fluid is less, and will overcome the cracking pressure that resetting valve system 3-1 is larger, so the damping force that piston rod 1 is subject to is larger;
Working principle and the said process of piston rod 1 when compression stroke is similar.
The beneficial effects of the utility model are:
When the utility model is used for shock absorber of automobile suspension, while travelling, provide less suspension damping in good road surface, thereby reduce the vibration that is passed to vehicle body, improve riding comfort; Larger suspension damping is provided while travelling on the cross-country road of big rise and fall, improves driving safety.And without as semi-active suspension and Active suspension, extra sensor, actuator and control system are installed on vehicle, simple and reliable for structure, cost is low, be easy to promote.
Accompanying drawing explanation
Fig. 1 is the fluid mobility status (take restore stroke as example) of the utility model when instantaneous stroke is little amplitude
Fig. 2 is the fluid mobility status (take restore stroke as example) of the utility model when instantaneous stroke is large amplitude
Fig. 3 is another kind of embodiment of the present utility model
Fig. 4 is the sectional shape of auxiliary flow 1-1 embodiment illustrated in fig. 3
Fig. 5 is the relation curve (F-s curve) between damping force F of the present utility model and piston rod displacement s
Fig. 6 is the relation curve (F-v curve) between damping force F of the present utility model and piston rod speed v
In figure:
1, piston rod; 2, upper spring; 3, piston; 4, lower spring; 5, nut; 6, clutch release slave cylinder;
1-1, auxiliary flow; 3-1, resetting valve system; 3-2, compression valves system;
F, damping force; The displacement of s, piston rod; The movement velocity of v, piston rod;
F-s curved section when a, instantaneous stroke are little amplitude;
B, the instantaneous stroke F-s curved section during from little amplitude to large amplitude transition;
F-s curved section when c, instantaneous stroke are large amplitude;
F-s curve when d, instantaneous stroke are little amplitude always;
Y. the F-s curve of traditional vibration damper;
F-v curve when m, instantaneous stroke are large amplitude;
F-v curve when n, instantaneous stroke are little amplitude;
G, the instantaneous stroke F-v curved section during from little amplitude to large amplitude transition;
The F-v curve of t, traditional vibration damper.
Embodiment
Below in conjunction with accompanying drawing, model utility is described in detail.
Fig. 1 is a kind of embodiment of the present utility model, the relevant orifice valve of shown a kind of sliding piston formula amplitude, comprise piston rod 1, be arranged on the piston 3 of piston rod 1 lower end, be fixed on the nut 5 of piston rod 1 lower end, and the clutch release slave cylinder 6 that is nested in piston 3 outsides, described piston 3 is slidably connected with piston rod 1, and piston rod 1 is provided with auxiliary flow 1-1; Described auxiliary flow 1-1 opens when piston 3 small amplitude motion, when piston 3 large-amplitude vibration, closes.
Described piston 3 is provided with resetting valve system 3-1 and compression valves system 3-2.
Between described piston 3 upsides and the shaft shoulder of piston rod 1, upper spring 2 is installed, 4, two springs of lower spring is installed all in compressive state between piston 3 downsides and nut 5.
The utility model can be applicable to the sprung parts such as automobile single-tube inflating shock absorber, dual-tube shock absorber and hydro pneumatic suspension, also can be used for automotive seat vibration damper, also can be used in other parts that damping need to be provided.
Below with the utility model for shock absorber of automobile suspension, and piston rod 1 is example in restoring stroke, introduces working procedure of the present utility model:
In conjunction with Fig. 1, Fig. 5 and Fig. 6, when piston rod 1 small amplitude motion, the high-voltage oil liquid of piston 3 epicoeles flows into piston 3 cavity of resorptions by resetting valve system 3-1 and auxiliary flow 1-1 simultaneously; Meanwhile, piston 3 is down sliding under oil liquid pressure effect, and upper spring 2 is stretched, and lower spring 4 is compressed; But because excitation amplitude is less, piston 3 is not enough to stop up the downside aperture of auxiliary flow 1-1; Now, the circulation area of fluid is larger, so the damping force that piston rod 1 is subject to is less; Be a curved section in Fig. 5 and the leading portion of the n curve in Fig. 6; If instantaneous stroke is little amplitude always, form whole section of n curve in the F-s curve shown in the d in Fig. 5 and Fig. 6.
In conjunction with Fig. 2, Fig. 5 and Fig. 6, when the amplitude of piston rod 1 continues to increase, piston 3 continues down sliding under oil liquid pressure effect, and piston 3 will stop up the downside aperture of auxiliary flow 1-1; Now, the high-voltage oil liquid of piston 3 epicoeles can only flow into piston 3 cavity of resorptions by resetting valve system 3-1, and the circulation area of fluid is less, and will overcome the cracking pressure that resetting valve system 3-1 is larger, so the damping force that piston rod 1 is subject to is larger; Wherein, at instantaneous stroke, the transient process from little amplitude to large amplitude, form b curved section in Fig. 5 and the g curved section in Fig. 6; Instantaneous stroke switches to after large amplitude completely, the c curved section in formation Fig. 5 and the m curve in Fig. 6.
It should be noted that, y in Fig. 5 is the F-s curve of traditional vibration damper, t in Fig. 6 is the F-v curve of traditional vibration damper, and the utility model is when instantaneous stroke is little amplitude, the damping force (a curved section in Fig. 5 and the leading portion of n curve in Fig. 6) less than traditional vibration damper is provided, improved riding comfort; When instantaneous stroke is large amplitude, the damping force (c curved section in Fig. 5 and m curve in Fig. 6) larger than traditional vibration damper is provided, improved control stability and driving safety.
Due to the elastic reaction of upper spring 2 and lower spring 4, and the effect of the circulation area gradual change of auxiliary flow 1-1, making the transient process of instantaneous stroke from little amplitude to large amplitude, transition is mild, and pause and transition in rhythm or melody sense is less.
Working principle and the said process of piston rod 1 when compression stroke is similar, repeats no more herein.
As another kind of embodiment, as shown in Figure 3 and Figure 4, described auxiliary flow 1-1 is the bypass groove on piston rod 1 downside outer wall, now piston rod 1 part that is formed in one.
In addition, the sectional shape by the auxiliary flow 1-1 to shown in Fig. 4 carries out appropriate design, can obtain multiple different transient characteristic curve; By the spacing length of the slip of piston 3 is adjusted, can regulate the switch amplitudes of big or small damping.
Above-described embodiment is only for illustrating the utility model; wherein the structure of each parts, Placement etc. all can change to some extent; every equivalents of carrying out on the basis of technical solutions of the utility model and improvement, all should not get rid of outside protection domain of the present utility model.
Claims (4)
1. the relevant orifice valve of a sliding piston formula amplitude, comprise piston rod (1), be arranged on the piston (3) of piston rod (1) lower end, be fixed on the nut (5) of piston rod (1) lower end, and the clutch release slave cylinder (6) that is nested in piston (3) outside, it is characterized in that:
Described piston (3) is slidably connected with piston rod (1), and piston rod (1) is provided with auxiliary flow (1-1);
Described auxiliary flow (1-1) is opened when piston (3) small amplitude motion, when piston (3) large-amplitude vibration, closes.
2. the relevant orifice valve of a kind of sliding piston formula amplitude according to claim 1, is characterized in that:
Upper spring (2) is installed between the shaft shoulder of described piston (3) upside and piston rod (1), between piston (3) downside and nut (5), lower spring (4) is installed, two springs are all in compressive state.
3. the relevant orifice valve of a kind of sliding piston formula amplitude according to claim 1, is characterized in that:
Described piston (3) is provided with resetting valve system (3-1) and compression valves system (3-2).
4. the relevant orifice valve of a kind of sliding piston formula amplitude according to claim 1, is characterized in that:
Described auxiliary flow (1-1) is the bypass groove on piston rod (1) downside outer wall.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201420283569.9U CN203847618U (en) | 2014-05-29 | 2014-05-29 | Sliding piston type amplitude correlation damper valve |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201420283569.9U CN203847618U (en) | 2014-05-29 | 2014-05-29 | Sliding piston type amplitude correlation damper valve |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN203847618U true CN203847618U (en) | 2014-09-24 |
Family
ID=51560640
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201420283569.9U Withdrawn - After Issue CN203847618U (en) | 2014-05-29 | 2014-05-29 | Sliding piston type amplitude correlation damper valve |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN203847618U (en) |
Cited By (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN103982584A (en) * | 2014-05-29 | 2014-08-13 | 张玉新 | Sliding piston type amplitude correlation damping valve |
| CN106402250A (en) * | 2016-06-23 | 2017-02-15 | 爱思恩梯大宇汽车部件(昆山)有限公司 | Movable variable type shock absorber |
| CN107724996A (en) * | 2017-09-22 | 2018-02-23 | 中国海洋石油总公司 | Natural gas wellhead block valve |
| CN113474587A (en) * | 2019-03-04 | 2021-10-01 | Ｋｙｂ株式会社 | Buffer device |
-
2014
- 2014-05-29 CN CN201420283569.9U patent/CN203847618U/en not_active Withdrawn - After Issue
Cited By (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN103982584A (en) * | 2014-05-29 | 2014-08-13 | 张玉新 | Sliding piston type amplitude correlation damping valve |
| CN103982584B (en) * | 2014-05-29 | 2016-03-09 | 张玉新 | Sliding piston formula amplitude is correlated with orifice valve |
| CN106402250A (en) * | 2016-06-23 | 2017-02-15 | 爱思恩梯大宇汽车部件(昆山)有限公司 | Movable variable type shock absorber |
| CN107724996A (en) * | 2017-09-22 | 2018-02-23 | 中国海洋石油总公司 | Natural gas wellhead block valve |
| CN113474587A (en) * | 2019-03-04 | 2021-10-01 | Ｋｙｂ株式会社 | Buffer device |
| CN113474587B (en) * | 2019-03-04 | 2024-02-23 | Ｋｙｂ株式会社 | Buffer device |
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Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| C14 | Grant of patent or utility model | ||
| GR01 | Patent grant | ||
| AV01 | Patent right actively abandoned |
Granted publication date: 20140924 Effective date of abandoning: 20160309 |
|
| C25 | Abandonment of patent right or utility model to avoid double patenting |