CN201068948Y - Damping adjustable vibration absorber - Google Patents
Damping adjustable vibration absorber Download PDFInfo
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- CN201068948Y CN201068948Y CNU2007200941301U CN200720094130U CN201068948Y CN 201068948 Y CN201068948 Y CN 201068948Y CN U2007200941301 U CNU2007200941301 U CN U2007200941301U CN 200720094130 U CN200720094130 U CN 200720094130U CN 201068948 Y CN201068948 Y CN 201068948Y
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Abstract
The utility model relates to a damping adjustable vibration absorber for a vehicle. The utility model overcomes the problems that the prior vibration absorber cannot effectively ensure that the damping characteristic of a hanging system changes according to the variation of the operation condition of the vehicle and cannot realize the amenity and the operating stability at the same time. The utility model adopts the design that an intermediate cylinder (4) is added and encased between a slave cylinder (1) and an oil storage cylinder (3), the upper end of the intermediate cylinder (4) is communicated with a piston lever chamber of the slave cylinder (1) through a constant through hole (2) of a big channel which is processed at the upper end of the slave cylinder (1), while the lower end of the intermediate cylinder (4) is communicated with the oil storage cylinder (3) through a circulation hole (18) of the intermediate cylinder processed at the lower end of the intermediate cylinder (4). A bypass valve is additionally arranged between the lower end of the intermediate cylinder (4) and the oil storage cylinder (3) to control the circulation flux of oil liquid and the communication of the intermediate cylinder (4) and the oil storage cylinder (3). The symmetrical axis of the arranged bypass valve is collinear with the symmetrical axis of the intermediate circulation hole (18) processed at the lower end of the intermediate cylinder (4).
Description
Technical field
The utility model relates to a kind of damping device that is used on the automotive suspension, and in particular, it relates to a kind of ride control shock absorber that is used on the automobile.
Background technique
Suspension is as the power transmission connection set between vehicle bridge (or wheel) and the vehicle frame (or monocoque body), and its active force will exert an influence to the ground connection property and the body vibrations of tire, and then has influence on the control stability and the run smoothness of car load.But, the effect of the best when can not guarantee control stability and run smoothness owing to traditional passive suspension, thereby produced the controllable suspension system that comprises Active suspension and semi-active suspension.
Be divided into Active suspension and semi-active suspension according to the controlled suspension of controllable degree, wherein Active suspension can be regulated simultaneously to the rigidity and the damping of suspension, and semi-active suspension then only can be regulated damping.
Active suspension can utilize the electric-controlled parts vibration of Control of Automobile on one's own initiative according to the vibration acceleration of sprung mass.Active suspension generally is made up of vibration-isolating spring, controller and actuator, and Active suspension not only can be isolated road vibration well, and can control body movement, and the inclination during turning etc. are bowed in facing upward during such as starting and braking.Can also regulate the height of vehicle body in addition, to adapt to the variation of load and pavement behavior.Though can obtain a more satisfactory vibrating isolation system by Active suspension, the Active suspension energy consumption is big, the cost height, complex structure also is difficult to obtain large-scale promotion and application commercial at present.
Semi-active suspension is meant that one of the rigidity of suspension elastic element and damping constant of vibration damper can regulate the suspension of control as required.At present, semi-active suspension research mainly concentrates on the damping constant aspect of regulating vibration damper, be about to ride control shock absorber as actuator, the automobile running situation and the variation of road conditions and the acceleration of vehicle body that arrive by sensor, send pulse control signal by ECU according to control strategy, realization has level adjustable or stepless adjustable to the resistance of shock absorber coefficient.
The utility model genus is the improvement to common bitubular dydraulic shock absorber.The structure of this common bitubular dydraulic shock absorber as shown in Figure 1.The upper end of vibration damper links to each other with vehicle body, and the lower end links to each other with axletree.During vehicle driving, the relative clutch release slave cylinder of piston moves reciprocatingly, and promptly alternation ground compresses and extension stroke, and liquid flows between clutch release slave cylinder and oil storage cylinder by each valve, kinetic energy is converted into heat energy looses in atmosphere, thereby play damping effect.Because damping is non-adjustable, thus major defect just be that the damping characteristic that can not guarantee suspension system well changes with the variation of the applying working condition of vehicle, can not take into account the travelling comfort and the control stability of automobile simultaneously.
Summary of the invention
Technology to be solved in the utility model is asked and is provided a kind of ride control shock absorber, especially provides a kind of and can realize damping the two poles of the earth or multistage adjustable ride control shock absorber.
Consult Fig. 1 to Figure 11, for solving the problems of the technologies described above, the present invention adopts following technological scheme to be achieved.Original vibration damper includes clutch release slave cylinder, oil storage cylinder, piston valve system and bottom valve system, ride control shock absorber be between clutch release slave cylinder and the oil storage cylinder by on screw shell and following screw shell increase and adorn a middle cylinder that is sleeved on the clutch release slave cylinder, the upper end of middle cylinder is communicated with the rod end chamber of clutch release slave cylinder by the major path normal open hole of processing in the clutch release slave cylinder upper end, and the lower end of middle cylinder is communicated with oil storage cylinder by the middle cylinder opening of processing in the middle cylinder lower end.
Increase between the lower end of middle cylinder and oil storage cylinder and adorn the whether bypass valve of connected sum fluid discharge value size of a control middle cylinder and oil storage cylinder, the axis of symmetry of the bypass valve after the installation is wanted conllinear with the axis of symmetry of processing at the middle cylinder opening of middle cylinder lower end.
Bypass valve described in the technological scheme includes valve body, bypass valve sleeve, adjusts piston, valve seat, adjustment bolt, helical spring, by pass vavle piston and annulus boss.The annulus boss is fixed on the lower end of middle cylinder external cylindrical surface, the axis of symmetry of annulus boss is wanted conllinear with processing at the axis of symmetry of the middle cylinder opening of middle cylinder lower end, the bypass valve sleeve is fixed on the annulus boss by screw thread, by pass vavle piston is packed into, and the bypass valve sleeve is interior to be connected with the interior edge face contact of bypass valve sleeve, helical spring is also packed into, and the bypass valve sleeve is interior to be connected with the by pass vavle piston contact, reinstalling the adjustment piston is connected with the helical spring contact, valve body be sleeved on the bypass valve sleeve around, the one end is fixed on the oil storage cylinder, the other end of valve body is connected with valve seat by screw thread, adjust bolt by being threaded on the valve seat, the end face of adjusting bolt is connected with the contact of adjustment piston; Described 25 the screw shell of being labeled as is made up of two different cirque body of diameter with the screw shell that is labeled as 26, on major diameter cirque body inner cylindrical surface, be processed with the screw thread that is connected with clutch release slave cylinder, the external diameter nominal size of toric internal diameter of minor diameter and clutch release slave cylinder is identical, the toric external diameter of minor diameter is identical with the internal diameter nominal size of middle cylinder, but two sizes all will have the magnitude of interference of 10 μ m-52 μ m; Described valve seat is made up of three different cylindrical bodys of diameter, three cylindrical axis conllinear, on valve seat, process a screw that is connected with the adjustment bolt along axis, the screw thread that processing and valve body are connected on the cylindrical cylndrical surface of middle diameter, the size of small diameter cylinders body connects movingly with the identical one-tenth of internal diameter of bypass valve sleeve; Described middle cylinder is a cylindrical piece, and two ends inner cylindrical surface is that the interference stationary fit is connected with last screw shell and the toric contact of the minor diameter of following screw shell about it, and its lower end edge is radially processed a middle cylinder opening; Described by pass vavle piston is a disc-like structural member, be uniformly distributed along the circumference in its outer rim and be processed with the by pass vavle piston opening, on by pass vavle piston one end face, be processed with the endless belt of protrusion, be processed with boss on the by pass vavle piston other end, the external diameter of by pass vavle piston is identical with the internal diameter of bypass valve sleeve; Described bypass valve sleeve is a cup shell, the uniform draining hole that is processed with on the sleeve wall of one end, bottom at the bypass valve sleeve is processed with a through hole along its axis, ring body at a protrusion of bottom outside face processing, the axis conllinear of the axis of bottom through-hole and the ring body of protrusion, on the ring body external cylindrical surface that protrudes, be processed with the screw thread that is connected with the annulus boss, and the one-tenth movingly connection identical of the barrel internal diameter of bypass valve sleeve with the adjustment piston external diameter.
The beneficial effects of the utility model:
For the damping force characteristic that contrasts the ride control shock absorber after the improvement and the difference of original vibration damper, we have carried out the contrast experiment to original vibration damper and our ride control shock absorber of development.
At first done the stand test of original forward and backward vibration damper.
The stroke of vibration damper is: ± 50mm
Vibration damper Test frequency (hz) before original:
f：0.17，0.32，0.64，0.95，1.27，1.67，2，2.55，3.18
Corresponding speed (m/s):
V：0.0534，0.101，0.201，0.3，0.4，0.525，0.628，0.801，1
Test result:
Table 1 (vibration damper before original)
| Frequency | The stretching damping force | Compression damping power |
| 0.17 | 756 | -275 |
| 0.32 | 932 | -402 |
| 0.64 | 1049 | -473 |
| 0.95 | 1144 | -542 |
| 1.27 | 1200 | -630 |
| 1.67 | 1466 | -684 |
| 2 | 1519 | -802 |
| 2.55 | 1607 | -819 |
| 3.18 | 1706 | -842 |
Original rear shock absorber Test frequency (hz):
f：0.15，0.4，0.83，1.08，1.35，1.67，2，2.17，2.55，3.31
Corresponding speed (m/s):
V：0.047，0.126，0.261，0.34，0.424，0.525，0.63，0.68，0.8 1.04
Test result: table 2 (original rear shock absorber)
| Frequency | The stretching damping force | Compression damping power |
| 0.15 | 350 | -185 |
| 0.4 | 1080 | -238 |
| 0.83 | 1230 | -311 |
| 1.08 | 1290 | -366 |
| 1.35 | 1350 | -410 |
| 1.67 | 1540 | -460 |
| 2 | 1650 | -550 |
| 2.165 | 1600 | -530 |
| 2.546 | 1750 | -580 |
| 3.31 | 2000 | -700 |
According to the characteristic curve of the original front and back vibration damper that laboratory data drew as shown in Figure 5.
Be at the experiment that ride control shock absorber carried out of being developed below.
During experiment, the spacer thickness that the rebound valve spring increases is 2.5mm, and pre compressed magnitude is total up to 5.9mm, and when rebound valve was opened maximum, the decrement of rebound valve spring was 1mm.Simultaneously the rigidity of compression valve is strengthened, increase the damping force of compression type.The bypass valve maximum compressibility is 5mm.
Damping test frequency (hz):
f：0.17，0.32，0.64，0.95，1.27，1.67，2，2.55，3.18
Corresponding speed (m/s):
V：0.0534，0.101，0.201，0.3，0.4，0.525，0.628，0.801，1
Test result:
Table 3 (amount of spring compression maximum)
| Frequency | The stretching damping force | Compression damping power |
| 0.17 | 503 | -429 |
| 0.32 | 704 | -436 |
| 0.64 | 1581 | -491 |
| 0.95 | 1872 | -537 |
| 1.27 | 1941 | -602 |
| 1.67 | 2094 | -568 |
| 2 | 2153 | -720 |
| 2.55 | 2403 | -739 |
| 3.18 | 2545 | -968 |
Table 4 (case of by-pass valve does not have pretension)
| Frequency | The stretching damping force | Compression damping power |
| 0.17 | 605 | -111 |
| 0.32 | 504 | -295 |
| 0.64 | 632 | -331 |
| 0.95 | 745 | -384 |
| 1.27 | 835 | -422 |
| 1.67 | 963 | -486 |
| 2 | 1072 | -558 |
| 2.55 | 1221 | -622 |
| 3.18 | 1485 | -766 |
According to the characteristic curve of the ride control shock absorber that laboratory data drew as shown in Figure 6.
By the result curve among the figure as can be seen, because this test added spacer thickness on rebound valve is 2.5mm, make the pre compressed magnitude of spring not surpass 6mm, so the stretching damping force-speed characteristic curve of vibration damper is better.And along with the pretightening force of case of by-pass valve changes, the stretching damping force of vibration damper has realized continuous variation in a scope.This illustrates by the two poles of the earth that can realize damping at bypass valve increase preloading spring or multistage adjustable.Simultaneously, can play the purpose that increases compression damping power by the rigidity that increases compression valve.
In addition, method of the present utility model and structure can promote the use of other vehicles fully, have stronger versatility.
Description of drawings
The utility model is described in further detail below in conjunction with accompanying drawing:
Fig. 1 is original double barreled damper structure schematic representation;
Fig. 2 is the ride control shock absorber structural representation;
Fig. 3 is the structural representation of ride control shock absorber middle cylinder top and bottom;
Fig. 4 is the bypass valve arrangement schematic representation;
Fig. 5 is the damping force-speed characteristic curve of original front and back vibration damper;
Fig. 6 is the damping force-speed characteristic curve of adjustable shock absorber;
Fig. 7 is the whole-cutaway view on the plan view among the bypass valve sleeve part figure;
Fig. 8-a is the whole-cutaway view on the plan view in the by pass vavle piston parts drawing;
Fig. 8-b is the left view in the by pass vavle piston parts drawing;
Fig. 9 is the whole-cutaway view on the plan view of adjusting in the bypass valve among the piston details figure;
Figure 10 is the whole-cutaway view on the plan view in the valve seat parts drawing in the bypass valve;
Figure 11 is the whole-cutaway view on the plan view among the valve body piece figure in the bypass valve;
Among the figure: 1, clutch release slave cylinder, 2, major path normal open hole, 3, oil storage cylinder, 4, middle cylinder, 5, piston valve system, 6, valve body, 7, the bypass valve sleeve, 8, fine thread, 9, the by pass vavle piston opening, 11, bottom valve system, 12, the draining hole, 13, adjust piston, 14, valve seat, 15, adjust bolt, 16, helical spring, 17, by pass vavle piston, 18, the middle cylinder opening, 19, endless belt, 20, the annulus boss, 21, O type rubber seal, 22, O type rubber seal, 23, O type rubber seal, 24, last middle cylinder cover tube fixing device, 25, last screw shell, 26, following screw shell, 27 times middle cylinder cover tube fixing devices.
Embodiment
Below in conjunction with accompanying drawing the utility model is described in further detail:
Consult Fig. 1, original vibration damper mainly by clutch release slave cylinder 1, oil storage cylinder 3, piston valve be 5 and bottom valve be 11 and form.Piston valve is 5 to be provided with rebound valve, flowing valve and normal open hole, and bottom valve is 11 to be provided with compression valve, recuperation valve and normal open hole.
Consult Fig. 2 to Figure 11, ride control shock absorber be between clutch release slave cylinder 1 and the oil storage cylinder 3 by on middle cylinder cover tube fixing device 24, last screw shell 25 and following screw shell 26, following middle cylinder cover tube fixing device 27 increases adorns a middle cylinder 4 that is sleeved on the clutch release slave cylinder 1, last middle cylinder cover tube fixing device 24, last screw shell 25 and following screw shell 26, following middle cylinder cover tube fixing device 27 structures are identical, last screw shell 25 and following screw shell 26 are made up of two different cirque body of diameter, on major diameter cirque body inner cylindrical surface, be processed with the internal thread that matches and be connected with clutch release slave cylinder 1 upper and lower end outside thread, the toric internal diameter of minor diameter is identical with the external diameter nominal size of the clutch release slave cylinder 1 that is connected of matching, but 10 μ m-52 μ m magnitude of interference are arranged, reach stationary fit after the installation and play effect fixing and sealing.The toric external diameter of minor diameter is identical with the internal diameter nominal size of the middle cylinder 4 that is connected of matching, but 10 μ m-52 μ m magnitude of interference will be arranged, and reaches stationary fit after the installation and plays effect fixing and sealing.Middle cylinder 4 is cylindrical pieces, the upper end of middle cylinder 4 is communicated with the rod end chamber of clutch release slave cylinder 1 in 6 major path normal open holes 2 of clutch release slave cylinder 1 upper end by processing, and the lower end of middle cylinder 4 is communicated with oil storage cylinder 3 by the middle cylinder opening of radially processing in middle cylinder 4 lower ends 18.The outside thread of going up internal thread screw-in clutch release slave cylinder 1 two ends on screw shell 25 and the following screw shell 26 major diameter cirque body inner cylindrical surfaces during assembling matches and is connected, going up simultaneously screw shell 25 and following screw shell 26 minor diameter cirque body inserts between clutch release slave cylinder 1 and the middle cylinder 4 and becomes stationary fit, both played middle cylinder 4 suits had been fixed on the clutch release slave cylinder 1, play the seal action of middle cylinder 4 simultaneously, last middle cylinder cover tube fixing device 24 is gone up screw shell 25 and following screw shell 26 with following middle cylinder cover tube fixing device 27 from two ends locking.
In order to realize the adjustable of damping force, increase between the lower end of middle cylinder 4 and oil storage cylinder 3 and adorn the whether bypass valve of connected sum fluid discharge value size of a control middle cylinder 4 and oil storage cylinder 3, the axis of symmetry of the bypass valve after the installation is wanted conllinear with processing at the axis of symmetry of the middle cylinder opening 18 of middle cylinder 4 lower ends.
Bypass valve includes valve body 6, bypass valve sleeve 7, adjustment piston 13, valve seat 14, adjusts bolt 15, helical spring 16, by pass vavle piston 17, annulus boss 20, O type rubber seal 21, O type rubber seal 22 and O type rubber seal 23.
Described valve seat 14 is made up of three different cylindrical bodys of diameter, three cylindrical axis conllinear, on valve seat 14, process a screw that is connected with adjustment bolt 15 along axis, on the cylindrical cylndrical surface of middle diameter, be processed with the screw thread that is connected with valve body 6, the size of small diameter cylinders body connects movingly with the identical one-tenth of internal diameter of bypass valve sleeve 7, respectively processes a seal groove that O type rubber seal figure is installed at small diameter cylinders body and middle diameter circle cylinder root.
Described by pass vavle piston 17 is disc-like structural members, be uniformly distributed along the circumference in its outer rim and be processed with by pass vavle piston opening 9, on by pass vavle piston 17 1 end faces, be processed with the endless belt 19 of protrusion, the endless belt of this protrusion cooperates with the interior edge face of bypass valve sleeve 7, play the effect of blocking-up fluid, be processed with boss on by pass vavle piston 17 other ends, in order to helical spring 16 to be installed, the external diameter of by pass vavle piston 17 is identical with the internal diameter of bypass valve sleeve 7.
Described bypass valve sleeve 7 is cup shells, the uniform draining hole 12 that is processed with on the sleeve wall of one end, bottom at bypass valve sleeve 7 is processed with a through hole along its axis, because the length of through hole surpasses the thickness of bottom, therefore, ring body at a protrusion of bottom outside face formation is processed with the screw thread that is connected with annulus boss 20 on the ring body external cylindrical surface.And the one-tenth movingly connection identical of the internal diameter of bypass valve sleeve 7 barrels with adjustment piston 13 external diameters.
The working principle of ride control shock absorber:
Screwed in fully when adjusting screw rod 15, up to revolve motionless till, spring 16 is killed fully, at this moment, the valve road of bypass valve is by complete closed, the fluid passage is identical with original vibration damper function, forms hard damping; When adjustment screw rod 15 was screwed out fully, promptly spring was not compressed, and this moment, the valve road of bypass valve was opened fully, all can become the step-down runner in extension and compression stroke, made the deliquescing of ride control shock absorber damping value, realized soft damping.When the length of spring compressed degree is in a certain state between the two, certain pretension amount is promptly arranged, but does not kill fully, damping this moment be in soft hard between.Stretch at ride control shock absorber, in the compression process, fluid flows to 4 li of middle cylinders from the ride control shock absorber rod end chamber through major path normal open hole 2, middle cylinder opening 18 by middle cylinder 4 lower ends acts directly on the end face of by pass vavle piston 17 again, when the pressure of fluid reaches certain value, will push by pass vavle piston 17 open by helical spring 16 pretensions, and by pass vavle piston 17 peripheries have been processed 6 by pass vavle piston openings 9 that diameter is 3mm, fluid has just flow to the bypass valve sleeve 7 from these by pass vavle piston openings 9, sleeve 7 has also been opened 6 draining holes 12 that diameter is 4mm at its periphery, fluid finally flows to 3 li of oil storage cylinders through these draining holes 12, thereby realize the adjusting of damping, the pretightening force of spring can be by adjusting decrement that screw rod 15 realizes springs from 0 to any adjusting the maximum value, thereby make ride control shock absorber realize that multistage damping regulates.
Need to prove, in order to estimate the correctness of above-mentioned two-stage adjustable shock absorber principle reliably, we have at first adopted this mechanical ride control shock absorber, regulate by the manual two-stage that realizes of manpower, when real vehicle is used, can realize regulating automatically by magnetic switch or stepper motor etc.
Claims (7)
1. a ride control shock absorber includes clutch release slave cylinder, oil storage cylinder, piston valve system and bottom valve system, it is characterized in that between clutch release slave cylinder (1) and oil storage cylinder (3) increasing and adorn a middle cylinder (4) that is sleeved on the clutch release slave cylinder (1) by last screw shell (25) and following screw shell (26), the upper end of middle cylinder (4) is communicated with the rod end chamber of clutch release slave cylinder (1) by the major path normal open hole (2) of processing in clutch release slave cylinder (1) upper end, and the lower end of middle cylinder (4) is communicated with oil storage cylinder (3) by the middle cylinder opening (18) of processing in middle cylinder (4) lower end;
Increase between the lower end of middle cylinder (4) and oil storage cylinder (3) and adorn the whether bypass valve of connected sum fluid discharge value size of a control middle cylinder (4) and oil storage cylinder (3), the axis of symmetry of the bypass valve after the installation is wanted conllinear with processing at the axis of symmetry of the middle cylinder opening (18) of middle cylinder (4) lower end.
2. according to the described ride control shock absorber of claim 1, it is characterized in that described bypass valve includes valve body (6), bypass valve sleeve (7), adjustment piston (13), valve seat (14), adjusts bolt (15), helical spring (16), by pass vavle piston (17) and annulus boss (20);
Annulus boss (20) is fixed on the lower end of middle cylinder (4) external cylindrical surface, the axis of symmetry of annulus boss (20) is wanted conllinear with processing at the axis of symmetry of the middle cylinder opening (18) of middle cylinder (4) lower end, bypass valve sleeve (7) is fixed on the annulus boss (20) by screw thread, by pass vavle piston (17) is packed into, and bypass valve sleeve (7) is interior to be connected with the interior edge face contact of bypass valve sleeve (7), helical spring (16) is also packed into, and bypass valve sleeve (7) is interior to be connected with by pass vavle piston (17) contact, reinstalling adjustment piston (13) is connected with helical spring (16) contact, valve body (6) be sleeved on bypass valve sleeve (7) around, the one end is fixed on the oil storage cylinder (3), the other end of valve body (6) is connected with valve seat (14) by screw thread, adjust bolt (15) by being threaded on the valve seat (14), the end face of adjusting bolt (15) is connected with adjustment piston (13) contact.
3. according to the described ride control shock absorber of claim 1, it is characterized in that described screw shell (25) and screw shell (26) be made up of two different cirque body of diameter, on major diameter cirque body inner cylindrical surface, be processed with the screw thread that is connected with clutch release slave cylinder (1), the toric internal diameter of minor diameter is identical with the external diameter nominal size of clutch release slave cylinder (1), the toric external diameter of minor diameter is identical with the internal diameter nominal size of middle cylinder (4), but two sizes are all wanted the magnitude of interference of 10 μ m-52 μ m.
4. according to the described ride control shock absorber of claim 1, it is characterized in that described valve seat (14) is made up of three different cylindrical bodys of diameter, three cylindrical axis conllinear, go up screw that is connected with adjustment bolt (15) of processing along axis at valve seat (14), be processed with the screw thread that is connected with valve body (6) on the cylindrical cylndrical surface of middle diameter, the size of small diameter cylinders body connects movingly with the identical one-tenth of internal diameter of bypass valve sleeve (7).
5. according to the described ride control shock absorber of claim 1, it is characterized in that described middle cylinder (4) is a cylindrical piece, two ends inner cylindrical surface is that the interference stationary fit is connected with last screw shell (25) with the toric contact of minor diameter of following screw shell (26) about it, and its lower end edge is radially processed a middle cylinder opening (18).
6. according to the described ride control shock absorber of claim 1, it is characterized in that described by pass vavle piston (17) is a disc-like structural member, be uniformly distributed along the circumference in its outer rim and be processed with by pass vavle piston opening (9), on by pass vavle piston (17) one end faces, be processed with the endless belt (19) of protrusion, be processed with boss on by pass vavle piston (17) other end, the external diameter of by pass vavle piston (17) is identical with the internal diameter of bypass valve sleeve (7) barrel.
7. according to the described ride control shock absorber of claim 1, it is characterized in that described bypass valve sleeve (7) is a cup shell, the uniform draining hole (12) that is processed with on the sleeve wall of one end, bottom at bypass valve sleeve (7) is processed with a through hole along its axis, ring body at a protrusion of bottom outside face processing, the axis conllinear of the axis of bottom through-hole and the ring body of protrusion, on the ring body external cylindrical surface that protrudes, be processed with the screw thread that is connected with annulus boss (20), and the one-tenth movingly connection identical of the barrel internal diameter of bypass valve sleeve (7) with adjustment piston (13) external diameter.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CNU2007200941301U CN201068948Y (en) | 2007-07-26 | 2007-07-26 | Damping adjustable vibration absorber |
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| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CNU2007200941301U CN201068948Y (en) | 2007-07-26 | 2007-07-26 | Damping adjustable vibration absorber |
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| CN201068948Y true CN201068948Y (en) | 2008-06-04 |
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| CNU2007200941301U Expired - Fee Related CN201068948Y (en) | 2007-07-26 | 2007-07-26 | Damping adjustable vibration absorber |
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Cited By (9)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN102076987A (en) * | 2008-07-02 | 2011-05-25 | 奥林斯赛车公司 | Electrically controlled valve arrangement for a shock absorber |
| CN102434616A (en) * | 2010-09-07 | 2012-05-02 | 株式会社万都 | Shock absorber |
| CN102678810A (en) * | 2012-06-01 | 2012-09-19 | 吉林大学 | High/low speed bidirectional damping adjustable mechanical damper |
| CN104165205A (en) * | 2014-07-18 | 2014-11-26 | 北京福田戴姆勒汽车有限公司 | Pilot-operated type shock absorber |
| CN104175828A (en) * | 2014-07-18 | 2014-12-03 | 北京福田戴姆勒汽车有限公司 | Vehicle |
| CN104912991A (en) * | 2014-03-14 | 2015-09-16 | 长春孔辉汽车科技股份有限公司 | Motor drive damping-adjustable shock absorber |
| CN107401576A (en) * | 2017-09-14 | 2017-11-28 | 河海大学常州校区 | A kind of pantograph damper |
| CN108036012A (en) * | 2017-12-30 | 2018-05-15 | 深圳市中车业成实业有限公司 | A kind of high speed motor car oil-pressure damper tune valve module |
| CN109356956A (en) * | 2018-12-07 | 2019-02-19 | 广州海川汽车配件制造有限公司 | A kind of damper and production method of manually adjustable damping |
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| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN102076987A (en) * | 2008-07-02 | 2011-05-25 | 奥林斯赛车公司 | Electrically controlled valve arrangement for a shock absorber |
| CN102434616A (en) * | 2010-09-07 | 2012-05-02 | 株式会社万都 | Shock absorber |
| CN102678810A (en) * | 2012-06-01 | 2012-09-19 | 吉林大学 | High/low speed bidirectional damping adjustable mechanical damper |
| CN104912991A (en) * | 2014-03-14 | 2015-09-16 | 长春孔辉汽车科技股份有限公司 | Motor drive damping-adjustable shock absorber |
| CN104912991B (en) * | 2014-03-14 | 2017-04-05 | 长春孔辉汽车科技股份有限公司 | A kind of Motor drive ride control shock absorber |
| CN104175828B (en) * | 2014-07-18 | 2016-06-29 | 北京福田戴姆勒汽车有限公司 | Vehicle |
| CN104175828A (en) * | 2014-07-18 | 2014-12-03 | 北京福田戴姆勒汽车有限公司 | Vehicle |
| CN104165205B (en) * | 2014-07-18 | 2016-07-06 | 北京福田戴姆勒汽车有限公司 | Pilot-operated type vibroshock |
| CN104165205A (en) * | 2014-07-18 | 2014-11-26 | 北京福田戴姆勒汽车有限公司 | Pilot-operated type shock absorber |
| CN107401576A (en) * | 2017-09-14 | 2017-11-28 | 河海大学常州校区 | A kind of pantograph damper |
| CN107401576B (en) * | 2017-09-14 | 2019-06-11 | 河海大学常州校区 | A kind of pantograph damper |
| CN108036012A (en) * | 2017-12-30 | 2018-05-15 | 深圳市中车业成实业有限公司 | A kind of high speed motor car oil-pressure damper tune valve module |
| CN109356956A (en) * | 2018-12-07 | 2019-02-19 | 广州海川汽车配件制造有限公司 | A kind of damper and production method of manually adjustable damping |
| CN109356956B (en) * | 2018-12-07 | 2023-11-21 | 广州海川汽车配件制造有限公司 | Shock absorber capable of manually adjusting damping and manufacturing method |
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