CN103148149A - Design method for thickness of limiting clearance gasket of automobile damper compression valve - Google Patents

Design method for thickness of limiting clearance gasket of automobile damper compression valve Download PDF

Info

Publication number
CN103148149A
CN103148149A CN2013100821418A CN201310082141A CN103148149A CN 103148149 A CN103148149 A CN 103148149A CN 2013100821418 A CN2013100821418 A CN 2013100821418A CN 201310082141 A CN201310082141 A CN 201310082141A CN 103148149 A CN103148149 A CN 103148149A
Authority
CN
China
Prior art keywords
valve
compression
maximum
compression valve
thickness
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.)
Granted
Application number
CN2013100821418A
Other languages
Chinese (zh)
Other versions
CN103148149B (en
Inventor
周长城
袁光明
石沛林
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Shandong University of Technology
Original Assignee
Shandong University of Technology
Priority date (The priority date 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 date listed.)
Filing date
Publication date
Application filed by Shandong University of Technology filed Critical Shandong University of Technology
Priority to CN201310082141.8A priority Critical patent/CN103148149B/en
Publication of CN103148149A publication Critical patent/CN103148149A/en
Application granted granted Critical
Publication of CN103148149B publication Critical patent/CN103148149B/en
Expired - Fee Related legal-status Critical Current
Anticipated expiration legal-status Critical

Links

Images

Abstract

The invention relates to a design method for thickness of a limiting clearance gasket of an automobile damper compression valve, and belongs to the technical field of hydraulic dampers. At present, the accurate and reliable design method for the thickness of the limiting clearance gasket of the damper compression valve does not exist at home and abroad. The design method is characterized in that the design method comprises the step that the thickness of the limiting clearance gasket of the damper superposed compression valve is designed according to the thickness and the number of a superposed valve plate of the compression valve, an oil way after first valve opening, and design requirements of first valve opening and maximum valve opening speed characteristics. With the adoption of the design method, an accurate and reliable design value of the thickness of the limiting clearance gasket of the compression valve can be obtained; the design requirement of the maximum valve opening speed characteristic of a damper compression travel is met; repeated testing, verification and modification are avoided; design and test expenses are lowered; a development period is shortened; the design quality and property of the damper can be improved; and the riding comfort and the safety of an automobile can be improved.

Description

The design method of the spacing clearance ring thickness of vehicle shock absorber compression valve
Technical field
The present invention relates to dydraulic shock absorber, particularly the design method of the spacing clearance ring thickness of vehicle shock absorber compression valve.
Background technique
The structure of the spacing clearance ring of compression valve has material impact to the damping characteristic of dydraulic shock absorber compression stroke, wherein, the outer radius of spacing clearance ring is determining the inner circle effective radius of compression valve valve block, the thickness of spacing clearance ring is determining that the maximum of vibration damper compression stroke opens the valve speed characteristics, thereby affects the run smoothness of vehicle.then, due to the restriction that is subjected to the distortion of vibration damper valve block and the non-linear restriction loss problem of fluid, and the oil circuit of compression stroke is more complicated than restoring stroke, the structure influence of valve seat assembly and compression valve by compression not only, but also be subjected to the piston gap and restore the impact of normal open hole area, therefore, domestic at present, outward to the spacing clearance ring thickness of hydraulic shock absorber compression valve also not accurately, reliable design method, mostly to determine at first by rule of thumb a compression valve block one-tenth-value thickness 1/10, then pass through repetition test, checking and the method for revising are finally determined design parameter, therefore, be difficult to obtain spacing clearance ring thickness parameter value accurately and reliably, satisfy the vibration damper maximum and open the requirement of valve speed characteristics.Along with the fast development of automotive industry and improving constantly of Vehicle Speed, higher designing requirement has been proposed absorber designing.Therefore, must set up a kind of design method of accurate, the reliable spacing clearance ring thickness of vehicle shock absorber compression valve, to satisfy the quick and accurate requirement that designs of dydraulic shock absorber, improve the absorber designing quality and performance, improve the run smoothness of vehicle.
Summary of the invention
For the defective that exists in above-mentioned prior art, technical problem to be solved by this invention is to provide the design method of the spacing clearance ring thickness of a kind of easy, accurate, reliable vehicle shock absorber compression valve, and its design cycle as shown in Figure 1.
In order to solve the problems of the technologies described above, the design method of the spacing clearance ring thickness of vehicle shock absorber compression valve provided by the present invention, its technological scheme implementation step is as follows:
(1) determine the equivalent thickness of compression valve of shock absorber stack valve block h e:
According to the thickness of compression valve stack valve block and sheet number ( h 1, n 1 h 2, n 2 h n , n n), determine the equivalent thickness of compression valve of shock absorber stack valve block
Figure 383679DEST_PATH_IMAGE001
;
(2) calculate the choke pressure that compression stroke is opened valve and maximum flowing valve when driving valve for the first time p lk1 , p lk2 :
Open for the first time oil circuit after valve, piston diameter according to compression valve of shock absorber
Figure 831977DEST_PATH_IMAGE002
, diameter of piston rod d g, the piston gap
Figure 674032DEST_PATH_IMAGE003
, gap length
Figure 600399DEST_PATH_IMAGE004
, the piston eccentricity , the fluid kinetic viscosity
Figure 830709DEST_PATH_IMAGE006
, fluid density , rebuilt valve normal open hole area , flow coefficient , the circulation throttle slice thickness h l , exradius
Figure 614678DEST_PATH_IMAGE010
, the valve port radius
Figure 900165DEST_PATH_IMAGE011
, valve port radius deformation coefficient
Figure 699494DEST_PATH_IMAGE012
, and open for the first time valve speed
Figure 754038DEST_PATH_IMAGE013
, the choke pressure of the flowing valve when setting up compression stroke and driving valve for the first time p lk1 Equation, that is:
Figure 715041DEST_PATH_IMAGE014
；
Separate above-mentioned equation, just can obtain the choke pressure of the flowing valve when compression stroke is driven valve for the first time p lk1
In like manner, with in equation V k1yWith p lk1 Use respectively V k2yWith p lk2 Replace choke pressure equation and the choke pressure of the flowing valve in the time of just can obtaining the compression stroke maximum and drive valve p lk2 Value;
The choke pressure in compression valve seat hole when (3) calculating maximum is driven valve p Hyk2And flow Q Hyk2:
Open valve speed according to maximum V k2y, diameter of piston rod d g, the diameter in compression valve seat hole
Figure 487824DEST_PATH_IMAGE015
And number , flow coefficient
Figure 999894DEST_PATH_IMAGE009
, fluid density
Figure 866219DEST_PATH_IMAGE007
, the choke pressure in compression valve seat hole when calculating vibration damper compression stroke maximum is driven valve p Hyk2, that is:
Figure 126299DEST_PATH_IMAGE017
；
Open valve speed according to maximum V k2y, diameter of piston rod d g, calculate flow through when vibration damper compression stroke maximum is driven valve compression valve seat hole Q Hyk2, that is:
Q hyk2=
Figure 267431DEST_PATH_IMAGE018
；
(4) calculate the choke pressure in compression valve seat hole when driving valve for the first time p Hyk1:
According to diameter of piston rod d g, the diameter in compression valve seat hole
Figure 139309DEST_PATH_IMAGE015
And number
Figure 442115DEST_PATH_IMAGE016
, flow coefficient , fluid density , open for the first time the valve speed point V k1y, calculate the choke pressure in compression valve seat hole when opening valve point for the first time p Hyk1, be distributed as:
Figure 752376DEST_PATH_IMAGE019
；
The choke pressure of compression valve throttle hole when (5) calculating maximum is driven valve
Figure 226083DEST_PATH_IMAGE020
And flow :
Damping force when driving valve according to vibration damper compression stroke maximum
Figure 678110DEST_PATH_IMAGE022
, the piston bore internal diameter D H, diameter of piston rod d g, in step (3)
Figure 693557DEST_PATH_IMAGE023
, and in step (2) p lk2 , the choke pressure of compression valve throttle hole when the calculating maximum is driven valve
Figure 869323DEST_PATH_IMAGE020
, that is:
Figure 856871DEST_PATH_IMAGE024
According to compression valve normal open hole area
Figure 612337DEST_PATH_IMAGE025
, flow coefficient
Figure 736151DEST_PATH_IMAGE009
, fluid density
Figure 551660DEST_PATH_IMAGE007
, and choke pressure
Figure 495345DEST_PATH_IMAGE020
, the flow of compression valve throttle hole when the calculating maximum is driven valve
Figure 585661DEST_PATH_IMAGE021
, that is:
Figure 298402DEST_PATH_IMAGE026
；
(6) calculate the choke pressure of compression valve throttle hole when driving valve for the first time
Figure 19234DEST_PATH_IMAGE027
:
According to the piston bore internal diameter D H, diameter of piston rod d g, open for the first time the valve damping force
Figure 981373DEST_PATH_IMAGE028
, in step (4)
Figure 78642DEST_PATH_IMAGE029
, and in step (2) p lk1 , the choke pressure of compression valve throttle hole when calculating is driven valve for the first time , that is:
Figure 334360DEST_PATH_IMAGE030
The flow in compression valve ring-shaped throttling gap when (7) calculating maximum is driven valve And aperture
Figure 153598DEST_PATH_IMAGE032
:
According in step (3) Q Hyk2, in step (5)
Figure 106510DEST_PATH_IMAGE021
, the flow in compression valve ring-shaped throttling gap when the calculating maximum is driven valve
Figure 434723DEST_PATH_IMAGE031
, that is:
Figure 574718DEST_PATH_IMAGE033
；
Exradius according to the compression valve block , the valve port radius , oil viscosity , the flow in compression valve ring-shaped throttling gap
Figure 9930DEST_PATH_IMAGE031
, and in step (5) , calculate the maximum opening in compression valve ring-shaped throttling gap
Figure 649039DEST_PATH_IMAGE036
, that is:
Figure 850213DEST_PATH_IMAGE037
；
(8) the spacing clearance ring thickness of compression valve of shock absorber h gDesign:
According to the deformation coefficient of compression valve block in the valve port radius
Figure 964799DEST_PATH_IMAGE038
, in step (1) h e, in step (6)
Figure 745674DEST_PATH_IMAGE027
, and in step (7)
Figure 793264DEST_PATH_IMAGE036
, to the spacing clearance ring thickness of compression valve of shock absorber h gDesign, that is:
Figure 634181DEST_PATH_IMAGE039
。
The present invention has advantages of than prior art:
due to the restriction that is subjected to the distortion of vibration damper valve block and the non-linear restriction loss problem of fluid, and the oil circuit of compression stroke is more complicated than restoring stroke, the structure influence of valve seat assembly and compression valve by compression not only, but also be subjected to the piston gap and restore the impact of normal open hole area, therefore, domestic at present, outward to the spacing clearance ring thickness of hydraulic shock absorber compression valve also not accurately, reliable design method, mostly to determine at first by rule of thumb a compression valve block one-tenth-value thickness 1/10, then pass through repetition test, checking and the method for revising are finally determined design parameter, therefore, be difficult to obtain spacing clearance ring thickness parameter value accurately and reliably, satisfy the vibration damper maximum and open the requirement of valve speed characteristics.The present invention utilizes valve block Deformation analyses calculating formula and the non-linear restriction loss segmentation of fluid analytical formula, thickness and sheet number according to compression stack valve block, compression valve is opened the oil circuit after valve for the first time, and the vibration damper compression stroke opens valve and maximum designing requirement of opening the valve speed characteristics for the first time, and the thickness of the spacing clearance ring of vibration damper stacked compression valve is designed.Utilize this design method, can obtain the design load of the spacing clearance ring thickness of compression valve of shock absorber accurately and reliably, guarantee the designing requirement that vibration damper compression stroke maximum is opened the valve speed characteristics, can avoid repetition test, checking and modification, reduce absorber designing and testing expenses, shorten the construction cycle, simultaneously, utilize this design method can improve designing quality, the performance of vibration damper, improve the Vehicle Driving Cycle smoothness.
Be further described below in conjunction with accompanying drawing in order to understand better the present invention.
The spacing clearance ring thickness of Fig. 1 vehicle shock absorber compression valve h gDesign flow diagram;
Fig. 2 is damper piston assembly and compression valve structure figure;
Fig. 3 is the spacing clearance ring figure of compression valve of shock absorber;
Fig. 4 is the oil circuit figure after compression valve of shock absorber is driven valve for the first time;
Fig. 5 is embodiment one the desired speed characteristic curve of design vibration damper;
Fig. 6 is the speed characteristic curve that embodiment one design shock absorber gear performance test obtains;
Fig. 7 is embodiment two the desired speed characteristic curve of design vibration damper;
Fig. 8 is the speed characteristic curve that embodiment two design shock absorber gear performance test obtains.
Specific embodiments
Below by embodiment, the present invention is described in further detail.
Embodiment one: certain compression valve of shock absorber seat assembly and compression valve structure as shown in Figure 2, recuperation valve spring 1, compensation valve block 2, compression valve seat hole 3, the fastening rivet 4 of compression valve, compression valve block 5, the spacing back-up ring 6 of compression valve; Compression valve body 7, the spacing clearance ring 8 of compression valve, recuperation valve is crossed oily passage 9, recuperation valve spring seat 10, wherein, the relation between the spacing clearance ring 8 of compression valve and the spacing back-up ring 6 of compression valve and the fastening rivet 4 of compression valve, as shown in Figure 3.The structural parameter of this vibration damper and valve body structure and fluid parameter are as follows: the piston bore internal diameter , diameter of piston rod d g=20mm, the annulus area between piston bore and piston rod
Figure 820629DEST_PATH_IMAGE041
The piston gap length
Figure 722726DEST_PATH_IMAGE042
The piston mean gap
Figure 734544DEST_PATH_IMAGE043
Eccentricity
Figure 558144DEST_PATH_IMAGE044
Fluid kinematical viscosity viscosity =
Figure 703003DEST_PATH_IMAGE046
m 2/ s, density
Figure 885723DEST_PATH_IMAGE047
, kinetic viscosity
Figure 462198DEST_PATH_IMAGE048
The diameter in compression valve seat hole
Figure 919724DEST_PATH_IMAGE049
, number The exradius of compression valve block
Figure 618875DEST_PATH_IMAGE051
, interior circle radius
Figure 948226DEST_PATH_IMAGE052
, the valve port radius
Figure 209443DEST_PATH_IMAGE053
, valve port radial location deformation coefficient
Figure 143901DEST_PATH_IMAGE054
Thickness and the sheet number of compression valve stack valve block are h 1=0.10mm, n 1=1; h 2=0.15mm, n 2=1; Compression valve normal open hole area
Figure 934002DEST_PATH_IMAGE055
Rebuilt valve normal open hole area
Figure 219490DEST_PATH_IMAGE056
, normal open orifice flow flow coefficient
Figure 487660DEST_PATH_IMAGE057
The interior circle radius of circulation valve block
Figure 85081DEST_PATH_IMAGE058
, exradius
Figure 46084DEST_PATH_IMAGE059
, the valve port radius , valve port radial location deformation coefficient
Figure 625150DEST_PATH_IMAGE061
7.72
Figure 197262DEST_PATH_IMAGE063
The desired speed characteristics of absorber designing, as shown in Figure 5, wherein, compression valve of shock absorber is opened valve speed for the first time
Figure 457342DEST_PATH_IMAGE064
, open for the first time the valve damping force Maximum is opened valve speed
Figure 627610DEST_PATH_IMAGE066
, maximum is opened the valve damping force
Figure 664836DEST_PATH_IMAGE067
The design method of the spacing clearance ring thickness of vehicle shock absorber compression valve that example of the present invention provides, its design cycle as shown in Figure 1, concrete steps are as follows:
(1) determine the equivalent thickness of compression valve of shock absorber stack valve block h e:
According to thickness and the sheet number of compression valve stack valve block be h 1=0.10mm, n 1=1; h 2=0.15mm, n 2=1; Determine the equivalent thickness of compression valve of shock absorber stack valve block
Figure 412212DEST_PATH_IMAGE068
, for:
Figure 357034DEST_PATH_IMAGE069
=0.16355mm；
(2) calculate the choke pressure that compression stroke is opened valve and maximum flowing valve when driving valve for the first time p lk1 , p lk2 :
Shown in Figure 4 according to the oil circuit that compression valve of shock absorber is opened after valve for the first time, the piston bore internal diameter =28mm, diameter of piston rod d g=20mm, the piston gap
Figure 714383DEST_PATH_IMAGE003
=0.04mm, gap length
Figure 683476DEST_PATH_IMAGE004
=9mm, the piston eccentricity =1.0, the fluid kinetic viscosity
Figure 170138DEST_PATH_IMAGE048
, fluid density
Figure 549167DEST_PATH_IMAGE047
, rebuilt valve normal open hole area
Figure 5556DEST_PATH_IMAGE008
=0.8mm 2, flow coefficient
Figure 292181DEST_PATH_IMAGE009
=0.62; The circulation throttle slice thickness h l =0.1mm, exradius
Figure 150416DEST_PATH_IMAGE010
=11.0mm, the valve port radius
Figure 965925DEST_PATH_IMAGE011
=10.5mm, the deformation coefficient of valve port radius
Figure 440769DEST_PATH_IMAGE061
7.72
Figure 734347DEST_PATH_IMAGE062
, and open for the first time valve speed
Figure 433498DEST_PATH_IMAGE013
=0.3m/s, the choke pressure of the flowing valve when setting up compression stroke and driving valve for the first time p lk1 Equation, that is:
Figure 864480DEST_PATH_IMAGE070
；
Separate above-mentioned equation, just can obtain the choke pressure of the flowing valve when compression stroke is driven valve for the first time p lk1 =1.9658 * 10 4Pa;
In like manner, with in equation V k1yWith p lk1 Use respectively V k2yWith p lk2 Replace choke pressure equation and the choke pressure of the flowing valve in the time of just can obtaining the compression stroke maximum and drive valve p lk2 =2.6737 * 10 4Pa;
The choke pressure in compression valve seat hole when (3) calculating maximum is driven valve p Hyk2And flow Q Hyk2:
According to diameter of piston rod d g=20mm, the diameter in compression valve seat hole
Figure 492907DEST_PATH_IMAGE015
=2.0mm and number
Figure 60155DEST_PATH_IMAGE016
=4, flow coefficient
Figure 217466DEST_PATH_IMAGE009
=0.62, fluid density , maximum is opened valve speed V k2y=1.0m/s, the choke pressure in compression valve seat hole when calculating vibration damper compression stroke maximum is driven valve p Hyk2, that is:
Figure 302283DEST_PATH_IMAGE017
=?7.2353×10 5?Pa；
Open valve speed according to maximum V k2y=1.0m/s, diameter of piston rod d g=20mm calculates flow through when vibration damper compression stroke maximum is driven valve compression valve seat hole Q Hyk2, that is:
Q hyk2=
Figure 989616DEST_PATH_IMAGE018
=?3.1416×10 -4?m 3/s；
(4) calculate the choke pressure in compression valve seat hole when driving valve for the first time p Hyk1:
According to diameter of piston rod d g=20mm, the diameter in compression valve seat hole
Figure 848988DEST_PATH_IMAGE015
=2.0mm and number
Figure 988982DEST_PATH_IMAGE016
=4, flow coefficient
Figure 693633DEST_PATH_IMAGE009
=0.62, fluid density
Figure 235473DEST_PATH_IMAGE047
, open for the first time the valve speed point V k1y=0.3m/s calculates the choke pressure in compression valve seat hole when opening valve point for the first time p Hyk1, be distributed as:
Figure 265746DEST_PATH_IMAGE019
=?6.5118×10 4?Pa；
The choke pressure of compression valve throttle hole when (5) calculating maximum is driven valve
Figure 893036DEST_PATH_IMAGE020
And flow
Figure 870219DEST_PATH_IMAGE021
:
Damping force when driving valve according to vibration damper compression stroke maximum
Figure 532145DEST_PATH_IMAGE022
=650N, the piston bore internal diameter D H=28mm, diameter of piston rod d g=20mm, in step (3)
Figure 733319DEST_PATH_IMAGE023
=7.2353 * 10 5Pa, and in step (2) p lk2 =2.6737 * 10 4Pa, the choke pressure of compression valve throttle hole when the calculating maximum is driven valve
Figure 847906DEST_PATH_IMAGE020
, that is:
Figure 628780DEST_PATH_IMAGE024
=1.3198×10 6Pa；
Area according to compression valve normal open hole
Figure 676370DEST_PATH_IMAGE025
=1.2mm 2, flow coefficient =0.62, fluid density , and choke pressure
Figure 703735DEST_PATH_IMAGE020
=1.3198 * 10 6Pa, the flow of compression valve throttle hole when the calculating maximum is driven valve
Figure 74674DEST_PATH_IMAGE021
, that is:
Figure 617650DEST_PATH_IMAGE026
=4.0518×10 -5?m 3/s；
(6) calculate the choke pressure of compression valve throttle hole when driving valve for the first time :
According to the damper piston internal diameter of cylinder D H=28mm, diameter of piston rod d g=20mm opens the valve damping force for the first time =260N, in step (4)
Figure 66670DEST_PATH_IMAGE029
=6.5118
Figure 780548DEST_PATH_IMAGE071
, and in step (2) p lk1 =1.9658
Figure 357023DEST_PATH_IMAGE071
, the choke pressure of compression valve throttle hole when calculating is driven valve for the first time , that is:
Figure 363342DEST_PATH_IMAGE030
=7.4362
Figure 513700DEST_PATH_IMAGE072
；
The flow in compression valve ring-shaped throttling gap when (7) calculating maximum is driven valve
Figure 311892DEST_PATH_IMAGE031
And aperture
Figure 776371DEST_PATH_IMAGE032
:
According in step (3) Q Hyk2=3.1416 * 10 -4m 3/ s, in step (5)
Figure 976409DEST_PATH_IMAGE021
==4.0518 * 10 -5m 3/ s, the flow in compression valve ring-shaped throttling gap when the calculating maximum is driven valve , that is:
Figure 317577DEST_PATH_IMAGE033
=2.7364×10 -4?m 3/s；
Exradius according to the compression valve of shock absorber sheet
Figure 851327DEST_PATH_IMAGE034
=3.8mm, the valve port radius
Figure 905870DEST_PATH_IMAGE035
=6.4mm, oil viscosity
Figure 601294DEST_PATH_IMAGE048
, the flow in compression valve ring-shaped throttling gap
Figure 905236DEST_PATH_IMAGE031
=2.7364 * 10 -4m 3/ s, and in step (5)
Figure 977098DEST_PATH_IMAGE020
==1.3198 * 10 6Pa calculates the maximum opening in compression valve ring-shaped throttling gap
Figure 417306DEST_PATH_IMAGE036
, that is:
Figure 549210DEST_PATH_IMAGE037
=0.092303mm；
(8) the spacing clearance ring thickness of compression valve of shock absorber h gDesign:
According to the deformation coefficient of compression valve block in the valve port radius
Figure 74869DEST_PATH_IMAGE054
, in step (1) h e=0.1636mm, in step (6)
Figure 950422DEST_PATH_IMAGE027
=7.4362
Figure 510716DEST_PATH_IMAGE072
, and in step (7)
Figure 79100DEST_PATH_IMAGE036
==0.092303mm is to the spacing clearance ring thickness of compression valve of shock absorber h gDesign, that is:
Figure 357635DEST_PATH_IMAGE039
=0.237mm。
Utilize the electro-hydraulic servo vibration damper comprehensive performance test bed, the vibration damper model machine of designed processing is carried out characteristic test, measured vibration damper speed characteristic curve as shown in Figure 6.
By Fig. 6 and Fig. 5 as can be known, test the maximum of measured vibration damper and open the valve speed characteristics, with desired the matching of design, illustrate that the spacing clearance ring Thickness Design of this compression valve of shock absorber value is reliably, shows that the design method of the spacing clearance ring thickness of vehicle shock absorber compression valve of setting up is correct.
Embodiment two: certain vibration damper is not except compression valve seat hole and embodiment one identical, and other structural parameter and fluid parameter are all identical with embodiment one, wherein, and the diameter in compression valve seat hole d hy=2.0mm, number n hy=6; Thickness and the sheet number of compression stack valve block are h 1=0.10mm, n 1=2; h 2=0.15mm, n 2=2; The desired speed characteristics of absorber designing, as shown in Figure 7, wherein, the valve speed of opening for the first time of compression stroke V k1y=0.10m/s opens the valve damping force for the first time F Dk1y=180N, maximum is opened valve speed V k2y=1.0m/s, maximum is opened the valve damping force F Dk2y=700N.
Adopt embodiment one design procedure, the spacing clearance ring thickness of this compression valve of shock absorber is designed, that is:
(1) determine the equivalent thickness of compression valve of shock absorber stack valve block h e:
According to thickness and the sheet number of compression valve stack valve block be h 1=0.10mm, n 1=2; h 2=0.15mm, n 2=2; Determine the equivalent thickness of compression valve of shock absorber stack valve block
Figure 302457DEST_PATH_IMAGE068
, for:
Figure 186100DEST_PATH_IMAGE069
=0.2061mm；
(2) calculate the choke pressure that compression stroke is opened valve and maximum flowing valve when driving valve for the first time p lk1 , p lk2 :
Shown in Figure 4 according to the oil circuit that vibration damper is opened after valve for the first time, the piston bore internal diameter
Figure 394227DEST_PATH_IMAGE002
=28mm, diameter of piston rod d g=20mm, the piston gap =0.04mm, gap length
Figure 111833DEST_PATH_IMAGE004
=9mm, the piston eccentricity
Figure 849982DEST_PATH_IMAGE005
=1.0, the fluid kinetic viscosity
Figure 25749DEST_PATH_IMAGE048
, fluid density
Figure 482138DEST_PATH_IMAGE047
, rebuilt valve normal open hole area
Figure 768763DEST_PATH_IMAGE008
=0.8mm 2, flow coefficient
Figure 626997DEST_PATH_IMAGE009
=0.62; The circulation throttle slice thickness h l =0.1mm, exradius
Figure 442506DEST_PATH_IMAGE010
=11.0mm, the valve port radius
Figure 182929DEST_PATH_IMAGE011
=10.5mm, the deformation coefficient of valve port radius 7.72
Figure 517145DEST_PATH_IMAGE062
, and open for the first time valve speed
Figure 465695DEST_PATH_IMAGE013
=0.1m/s, the choke pressure of the flowing valve when setting up compression stroke and driving valve for the first time p lk1 Equation, that is:
Figure 562964DEST_PATH_IMAGE070
；
Separate above-mentioned equation, just can obtain the choke pressure of the flowing valve when compression stroke is driven valve for the first time p lk1 =1.469 * 10 4Pa;
In like manner, with in equation V k1yWith p lk1 Use respectively V k2yWith p lk2 Replace choke pressure equation and the choke pressure of the flowing valve in the time of just can obtaining the compression stroke maximum and drive valve p lk2 =2.6737 * 10 4Pa;
The choke pressure in compression valve seat hole when (3) calculating maximum is driven valve p Hyk2And flow Q Hyk2:
According to diameter of piston rod d g=20mm, the diameter in compression valve seat hole
Figure 130212DEST_PATH_IMAGE015
=2.0mm and number =6, flow coefficient
Figure 471380DEST_PATH_IMAGE009
=0.62, fluid density
Figure 384059DEST_PATH_IMAGE047
, maximum is opened valve speed V k2y=1.0m/s, the choke pressure in compression valve seat hole when calculating vibration damper compression stroke maximum is driven valve p Hyk2, that is:
Figure 602550DEST_PATH_IMAGE017
=3.2157×10 5?Pa；
Open valve speed according to maximum V k2y=1.0m/s, diameter of piston rod d g=20mm calculates flow through when vibration damper compression stroke maximum is driven valve compression valve seat hole Q Hyk2, that is:
Q hyk2=
Figure 930764DEST_PATH_IMAGE018
=?3.1416×10 -4?m 3/s；
(4) calculate the choke pressure in compression valve seat hole when driving valve for the first time p Hyk1:
According to diameter of piston rod d g=20mm, the diameter in compression valve seat hole
Figure 70758DEST_PATH_IMAGE015
=2.0mm and number
Figure 40988DEST_PATH_IMAGE016
=6, flow coefficient
Figure 582828DEST_PATH_IMAGE009
=0.62, fluid density
Figure 613101DEST_PATH_IMAGE047
, open for the first time the valve speed point V k1y=0.1m/s calculates the choke pressure in compression valve seat hole when opening valve point for the first time p Hyk1, be distributed as:
Figure 240391DEST_PATH_IMAGE019
=3.2157×10 3?Pa；
The choke pressure of compression valve throttle hole when (5) calculating maximum is driven valve
Figure 483154DEST_PATH_IMAGE020
And flow
Figure 145079DEST_PATH_IMAGE021
:
Damping force when driving valve according to vibration damper compression stroke maximum
Figure 815095DEST_PATH_IMAGE022
=700N, the piston bore internal diameter D H=28mm, diameter of piston rod d g=20mm, in step (3) =3.2157 * 10 5Pa, and in step (2) p lk2 =2.6737 * 10 4Pa, the choke pressure of compression valve throttle hole when the calculating maximum is driven valve
Figure 241714DEST_PATH_IMAGE020
, that is:
Figure 758146DEST_PATH_IMAGE024
=1.8809×10 6Pa；
Area according to compression valve normal open hole
Figure 599063DEST_PATH_IMAGE025
=1.2mm 2, flow coefficient
Figure 935366DEST_PATH_IMAGE009
=0.62, fluid density
Figure 51090DEST_PATH_IMAGE047
, and choke pressure
Figure 422028DEST_PATH_IMAGE020
=1.8809 * 10 6Pa, the flow of compression valve throttle hole when the calculating maximum is driven valve
Figure 433847DEST_PATH_IMAGE021
, that is:
Figure 523026DEST_PATH_IMAGE026
=4.837×10 -5?m 3/s；
(6) calculate the choke pressure of compression valve throttle hole when driving valve for the first time
Figure 176861DEST_PATH_IMAGE027
:
According to the damper piston internal diameter of cylinder D H=28mm, diameter of piston rod d g=20mm opens the valve damping force for the first time =180N, in step (4)
Figure 850605DEST_PATH_IMAGE029
=3.2157 * 10 3Pa, and in step (2) p lk1 =1.469 * 10 4Pa, the choke pressure of compression valve throttle hole when calculating is driven valve for the first time
Figure 692659DEST_PATH_IMAGE027
, that is:
=5.5564
Figure 964557DEST_PATH_IMAGE072
；
The flow in compression valve ring-shaped throttling gap when (7) calculating maximum is driven valve And aperture
Figure 647528DEST_PATH_IMAGE032
:
According in step (3) Q Hyk2=3.1416 * 10 -4m 3/ s, in step (5)
Figure 377587DEST_PATH_IMAGE021
=4.837 * 10 -5m 3/ s, the flow in compression valve ring-shaped throttling gap when the calculating maximum is driven valve
Figure 577624DEST_PATH_IMAGE031
, that is:
=2.6579×10 -4?m 3/s；
Exradius according to the compression valve of shock absorber sheet
Figure 387634DEST_PATH_IMAGE034
=3.8mm, the valve port radius
Figure 452542DEST_PATH_IMAGE035
=6.4mm, oil viscosity
Figure 507086DEST_PATH_IMAGE048
, the flow in compression valve ring-shaped throttling gap
Figure 202509DEST_PATH_IMAGE031
=2.6579 * 10 -4m 3/ s, and in step (5) =1.8809 * 10 6Pa calculates the maximum opening in compression valve ring-shaped throttling gap
Figure 578313DEST_PATH_IMAGE036
, that is:
=0.081229?mm；
(8) the spacing clearance ring thickness of compression valve of shock absorber h gDesign:
According to the deformation coefficient of compression valve block in the valve port radius
Figure 619267DEST_PATH_IMAGE054
, in step (1) h e=0.2061mm, in step (6)
Figure 144926DEST_PATH_IMAGE027
=5.5564 , and in step (7)
Figure 315194DEST_PATH_IMAGE036
=0.081229 mm is to the spacing clearance ring thickness of compression valve of shock absorber h gDesign, that is:
Figure 617999DEST_PATH_IMAGE039
=0.12723mm。
Utilize the electro-hydraulic servo vibration damper comprehensive performance test bed, the vibration damper model machine of designed processing is carried out characteristic test, measured vibration damper speed characteristic curve as shown in Figure 8.
By Fig. 8 and Fig. 7 as can be known, test the maximum of measured vibration damper and open the valve speed characteristics, with desired the matching of design, illustrate that the spacing clearance ring Thickness Design of this compression valve of shock absorber value is reliably, shows that the design method of the spacing clearance ring thickness of vehicle shock absorber compression valve of setting up is correct.
Embodiment three: the structural parameter of certain vibration damper, fluid parameter all reach out the valve damping characteristic and require identical with embodiment two, and the structure of just compressing valve block is not identical with embodiment's two, compress the interior circle radius of valve block r ay=4.0mm, exradius r by=8.0mm, the valve port radius r ky=6.5mm is at the deformation coefficient of valve port radius G rky =6.083
Figure 99796DEST_PATH_IMAGE073
Adopt embodiment two design procedure, the spacing clearance ring thickness of this compression valve of shock absorber is designed, that is:
(1) determine the equivalent thickness of compression valve of shock absorber stack valve block h e:
Identical according to the thickness of compression valve stack valve block and sheet number and embodiment two, therefore, equivalent thickness
Figure 513460DEST_PATH_IMAGE068
Also identical with embodiment two, that is:
Figure 928261DEST_PATH_IMAGE069
=0.2061mm；
(2) calculate the choke pressure that compression stroke is opened valve and maximum flowing valve when driving valve for the first time p lk1 , p lk2 :
Open valve characteristic because absorber designing is desired, identical with embodiment two, therefore, vibration damper indention journey is opened the choke pressure of valve and maximum flowing valve when driving valve for the first time p lk1 , p lk2 Also identical with embodiment two, that is:
The choke pressure of the flowing valve when the vibration damper compression stroke is driven valve for the first time p lk1 =1.469 * 10 4Pa;
Choke pressure equation and the choke pressure of the flowing valve when maximum is driven valve p lk2 =2.6737 * 10 4Pa;
The choke pressure in compression valve seat hole when (3) calculating maximum is driven valve p Hyk2And flow Q Hyk2:
Because the diameter in the structure of vibration damper, compression valve seat hole and number, fluid characteristic, vibration damper compression stroke are opened the designing requirement of valve speed characteristics, identical with embodiment two all, therefore, the choke pressure in compression valve seat hole when the compression stroke maximum of this vibration damper is driven valve p Hyk2And flow Q Hyk2, also identical with embodiment two, that is:
=3.2157×10 5?Pa；
Q hyk2=
Figure 371060DEST_PATH_IMAGE018
=?3.1416×10 -4?m 3/s；
(4) calculate the choke pressure in compression valve seat hole when driving valve for the first time p Hyk1:
The choke pressure in compression valve seat hole when driving valve for the first time p Hyk1, identical with embodiment two, that is:
=3.2157
Figure 326564DEST_PATH_IMAGE071
；
The choke pressure of compression valve throttle hole when (5) calculating maximum is driven valve And flow
Figure 970438DEST_PATH_IMAGE021
:
Due to the structure of vibration damper, open the identical of valve damping characteristic and embodiment two, therefore, the choke pressure of the compression valve throttle hole when this vibration damper compression stroke maximum is driven valve
Figure 257063DEST_PATH_IMAGE020
And flow
Figure 115297DEST_PATH_IMAGE021
Also identical with embodiment two, that is:
Figure 665228DEST_PATH_IMAGE024
=1.8809×10 6Pa；
Figure 608913DEST_PATH_IMAGE026
=4.837×10 -5?m 3/s；
(6) calculate the choke pressure of compression valve throttle hole when driving valve for the first time
Figure 168070DEST_PATH_IMAGE027
:
The choke pressure of compression valve throttle hole when driving valve for the first time
Figure 411970DEST_PATH_IMAGE027
, identical with embodiment two, that is:
Figure 398380DEST_PATH_IMAGE030
=5.5564 ；
The flow in compression valve ring-shaped throttling gap when (7) calculating maximum is driven valve
Figure 661051DEST_PATH_IMAGE031
And aperture
Figure 493878DEST_PATH_IMAGE032
:
According to Q Hyk2=3.1416 * 10 -4m 3/ s, in step (5)
Figure 182348DEST_PATH_IMAGE021
=4.837 * 10 -5m 3/ s, the flow in compression valve ring-shaped throttling gap when the calculating maximum is driven valve
Figure 835047DEST_PATH_IMAGE031
, that is:
Figure 736006DEST_PATH_IMAGE033
=2.6579×10 -4?m 3/s；
Exradius according to the compression valve of shock absorber sheet
Figure 423340DEST_PATH_IMAGE034
=4.0mm, the valve port radius
Figure 751553DEST_PATH_IMAGE035
=6.5mm, oil viscosity
Figure 422706DEST_PATH_IMAGE048
, the flow in compression valve ring-shaped throttling gap
Figure 861777DEST_PATH_IMAGE031
=2.6579 * 10 -4m 3/ s, and in step (5)
Figure 403617DEST_PATH_IMAGE020
=1.8809 * 10 6Pa calculates the maximum opening in compression valve ring-shaped throttling gap , that is:
Figure 61180DEST_PATH_IMAGE037
=0.079303mm；
(8) the spacing clearance ring thickness of compression valve of shock absorber h gDesign:
According to the deformation coefficient of compression valve block in the valve port radius G rky =6.083
Figure 303943DEST_PATH_IMAGE073
, in step (1) h e=0.2061mm, in step (6)
Figure 231448DEST_PATH_IMAGE027
=5.5564
Figure 901463DEST_PATH_IMAGE072
, and in step (7)
Figure 16050DEST_PATH_IMAGE036
=0.079303mm is to the spacing clearance ring thickness of compression valve of shock absorber h gDesign, that is:
Figure 593662DEST_PATH_IMAGE039
=0.12mm。

Claims (2)

1. the design method of the spacing clearance ring thickness of vehicle shock absorber compression valve, its concrete steps are as follows:
(1) determine the equivalent thickness of compression valve of shock absorber stack valve block h e:
According to the thickness of compression valve stack valve block and sheet number ( h 1, n 1 h 2, n 2 h n , n n), determine the equivalent thickness of compression valve of shock absorber stack valve block
Figure 2013100821418100001DEST_PATH_IMAGE002
;
(2) calculate the choke pressure that compression stroke is opened valve and maximum flowing valve when driving valve for the first time p lk1 , p lk2 :
According to piston diameter
Figure 2013100821418100001DEST_PATH_IMAGE004
, diameter of piston rod d g, the piston gap
Figure 2013100821418100001DEST_PATH_IMAGE006
, gap length
Figure 2013100821418100001DEST_PATH_IMAGE008
, the piston eccentricity
Figure 2013100821418100001DEST_PATH_IMAGE010
, the fluid kinetic viscosity
Figure 2013100821418100001DEST_PATH_IMAGE012
, fluid density
Figure 2013100821418100001DEST_PATH_IMAGE014
, rebuilt valve normal open hole area
Figure 2013100821418100001DEST_PATH_IMAGE016
, flow coefficient
Figure 2013100821418100001DEST_PATH_IMAGE018
, the circulation throttle slice thickness h l , exradius
Figure 2013100821418100001DEST_PATH_IMAGE020
, the valve port radius , valve port radius deformation coefficient
Figure 2013100821418100001DEST_PATH_IMAGE024
, and open for the first time valve speed
Figure 2013100821418100001DEST_PATH_IMAGE026
, the choke pressure of the flowing valve when setting up compression stroke and driving valve for the first time p lk1 Equation, that is:
Figure 2013100821418100001DEST_PATH_IMAGE028
；
Separate above-mentioned equation, just can obtain the choke pressure of the flowing valve when compression stroke is driven valve for the first time p lk1
In like manner, with in equation V k1yWith p lk1 Use respectively V k2yWith p lk2 Replace choke pressure equation and the choke pressure of the flowing valve in the time of just can obtaining the compression stroke maximum and drive valve p lk2 Value;
The choke pressure in compression valve seat hole when (3) calculating maximum is driven valve p Hyk2And flow Q Hyk2:
Open valve speed according to maximum V k2y, diameter of piston rod d g, the diameter in compression valve seat hole And number
Figure 2013100821418100001DEST_PATH_IMAGE032
, flow coefficient
Figure 748340DEST_PATH_IMAGE018
, fluid density
Figure 696704DEST_PATH_IMAGE014
, the choke pressure in compression valve seat hole when calculating vibration damper compression stroke maximum is driven valve p Hyk2, that is:
；
Open valve speed according to maximum V k2y, diameter of piston rod d g, calculate flow through when vibration damper compression stroke maximum is driven valve compression valve seat hole Q Hyk2, that is:
Q hyk2= ；
(4) calculate the choke pressure in compression valve seat hole when driving valve for the first time p Hyk1:
According to diameter of piston rod d g, the diameter in compression valve seat hole
Figure 789294DEST_PATH_IMAGE030
And number
Figure 72377DEST_PATH_IMAGE032
, flow coefficient , fluid density
Figure 39381DEST_PATH_IMAGE014
, open for the first time the valve speed point V k1y, calculate the choke pressure in compression valve seat hole when opening valve point for the first time p Hyk1, be distributed as:
Figure 2013100821418100001DEST_PATH_IMAGE038
；
The choke pressure of compression valve throttle hole when (5) calculating maximum is driven valve
Figure 2013100821418100001DEST_PATH_IMAGE040
And flow :
Damping force when driving valve according to vibration damper compression stroke maximum
Figure 2013100821418100001DEST_PATH_IMAGE044
, the piston bore internal diameter D H, diameter of piston rod d g, in step (3)
Figure 2013100821418100001DEST_PATH_IMAGE046
, and in step (2) p lk2 , the choke pressure of compression valve throttle hole when the calculating maximum is driven valve
Figure 365189DEST_PATH_IMAGE040
, that is:
Figure 2013100821418100001DEST_PATH_IMAGE048
According to compression valve normal open hole area , flow coefficient , fluid density
Figure 509918DEST_PATH_IMAGE014
, and choke pressure
Figure 619825DEST_PATH_IMAGE040
, the flow of compression valve throttle hole when the calculating maximum is driven valve
Figure 867267DEST_PATH_IMAGE042
, that is:
Figure 2013100821418100001DEST_PATH_IMAGE052
；
(6) calculate the choke pressure of compression valve throttle hole when driving valve for the first time :
According to the piston bore internal diameter D H, diameter of piston rod d g, open for the first time the valve damping force
Figure 2013100821418100001DEST_PATH_IMAGE056
, in step (4)
Figure 2013100821418100001DEST_PATH_IMAGE058
, and in step (2) p lk1 , the choke pressure of compression valve throttle hole when calculating is driven valve for the first time
Figure 921679DEST_PATH_IMAGE054
, that is:
Figure 2013100821418100001DEST_PATH_IMAGE060
The flow in compression valve ring-shaped throttling gap when (7) calculating maximum is driven valve And aperture :
According in step (3) Q Hyk2, in step (5)
Figure 286670DEST_PATH_IMAGE042
, the flow in compression valve ring-shaped throttling gap when the calculating maximum is driven valve , that is:
；
Exradius according to the compression valve block
Figure 2013100821418100001DEST_PATH_IMAGE068
, the valve port radius , oil viscosity
Figure 856378DEST_PATH_IMAGE012
, the flow in compression valve ring-shaped throttling gap
Figure 352081DEST_PATH_IMAGE062
, and in step (5) , calculate the maximum opening in compression valve ring-shaped throttling gap
Figure 2013100821418100001DEST_PATH_IMAGE072
, that is:
Figure 2013100821418100001DEST_PATH_IMAGE074
；
(8) the spacing clearance ring thickness of compression valve of shock absorber h gDesign:
According to the deformation coefficient of compression valve block in the valve port radius
Figure 2013100821418100001DEST_PATH_IMAGE076
, in step (1) h e, in step (6)
Figure 152733DEST_PATH_IMAGE054
, and in step (7)
Figure 991245DEST_PATH_IMAGE072
, to the spacing clearance ring thickness of compression valve of shock absorber h gDesign, that is:
Figure 2013100821418100001DEST_PATH_IMAGE078
。
2. the step (8) described according to claim 1, it is characterized in that: according to the equivalent thickness of vibration damper stack valve block, the deformation coefficient of valve port radial position, the pressure of compression valve throttle hole when driving valve for the first time, and the maximum opening in the compression valve ring-shaped throttling gap when maximum is driven valve, to the spacing clearance ring thickness of compression valve of shock absorber h gDesign, that is:
Figure 895616DEST_PATH_IMAGE078
。
CN201310082141.8A 2013-03-15 2013-03-15 Design method for thickness of limiting clearance gasket of automobile damper compression valve Expired - Fee Related CN103148149B (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
CN201310082141.8A CN103148149B (en) 2013-03-15 2013-03-15 Design method for thickness of limiting clearance gasket of automobile damper compression valve

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
CN201310082141.8A CN103148149B (en) 2013-03-15 2013-03-15 Design method for thickness of limiting clearance gasket of automobile damper compression valve

Publications (2)

Publication Number Publication Date
CN103148149A true CN103148149A (en) 2013-06-12
CN103148149B CN103148149B (en) 2014-10-08

Family

ID=48546400

Family Applications (1)

Application Number Title Priority Date Filing Date
CN201310082141.8A Expired - Fee Related CN103148149B (en) 2013-03-15 2013-03-15 Design method for thickness of limiting clearance gasket of automobile damper compression valve

Country Status (1)

Country Link
CN (1) CN103148149B (en)

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3844389A (en) * 1972-07-17 1974-10-29 C Bourcier Pistons for hydraulic shock absorbers
CN2859080Y (en) * 2005-12-31 2007-01-17 南阳金冠汽车减振器有限公司 Hydraulic vibration damper restoration damp valve
CN102840265A (en) * 2012-07-18 2012-12-26 山东理工大学 Optimal design method for parameter of controllable cylinder type hydraulic buffer of semi-active suspension

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3844389A (en) * 1972-07-17 1974-10-29 C Bourcier Pistons for hydraulic shock absorbers
CN2859080Y (en) * 2005-12-31 2007-01-17 南阳金冠汽车减振器有限公司 Hydraulic vibration damper restoration damp valve
CN102840265A (en) * 2012-07-18 2012-12-26 山东理工大学 Optimal design method for parameter of controllable cylinder type hydraulic buffer of semi-active suspension

Non-Patent Citations (3)

* Cited by examiner, † Cited by third party
Title
周长城等: ""最佳阻尼匹配减振器阀片厚度优化设计与特性试验"", 《振动工程学报》 *
周长城等: ""油气弹簧阀系参数设计及特性试验"", 《汽车工程》 *
徐伟等: ""汽车悬架阻尼匹配研究及减振器设计"", 《农业装备与车辆工程》 *

Also Published As

Publication number Publication date
CN103148149B (en) 2014-10-08

Similar Documents

Publication Publication Date Title
CN102840265B (en) Optimal design method for parameter of controllable cylinder type hydraulic buffer of semi-active suspension
CN102748418B (en) Method for designing stiffness of helical spring of combined valve for shock absorbers
CN103363008B (en) Hydraulic shock absorber
CN104156547A (en) Method for designing optimal damping characteristics of shock absorber of vehicle steel plate spring suspension system
CN206770497U (en) A kind of shock absorber structure for automobile
CN103161871B (en) Intensity checking method of overlaying valve plates of compression valve of vehicle buffer
CN103148148B (en) Method for checking strength of rebound sandwich valve sheet of shock absorber
Hou et al. Shock absorber modeling and simulation based on modelica
CN103148149B (en) Design method for thickness of limiting clearance gasket of automobile damper compression valve
CN103133590A (en) Design method of vehicle damper compression valve limiting checking ring curved surface shape
CN103148150A (en) Design method of normal through hole area of compression valve of automobile damper
CN103115105B (en) Splitting design method for absorber recovery sandwich plate valve sheet
CN103116709A (en) Computing method for circumferential stress of absorber annular valve sheet
CN103133589A (en) Method for designing maximum limiting interval of rebound valve of hydraulic vibration absorber
CN103174789B (en) Designing method of magneto-rheological absorber damping channel width based on characteristic requirements
CN103498885A (en) Method for designing area of hydraulic shock absorber rebuilt valve normal through hole based on speed characteristics
CN103148147B (en) Design method for rebound valve plate thickness of hydraulic oscillating damper
CN103148152B (en) Optimization design method for hole diameter and hole number of compression valve seat of hydraulic damper
CN103148154A (en) Design method for annular superposed valve plate of automobile damper compression valve
CN103148153B (en) Design method for predeformation amount of compression valve plate of hydraulic damper
CN103161870B (en) Design method of automobile semi-active suspension magneto-rheological shock absorber damping channel width
CN103115104B (en) Design method for maximum allowable thickness of absorber recovery sandwich plate valve sheet
CN202251627U (en) Damper bottom valve seat
CN203641375U (en) Low-cost high-sealing-performance tray double-barrel type automobile shock absorber
CN103133588A (en) Method for calculating local pressure loss and piston hole equivalent length of hydraulic vibration absorber

Legal Events

Date Code Title Description
C06 Publication
PB01 Publication
C10 Entry into substantive examination
SE01 Entry into force of request for substantive examination
C14 Grant of patent or utility model
GR01 Patent grant
CF01 Termination of patent right due to non-payment of annual fee

Granted publication date: 20141008

Termination date: 20190315

CF01 Termination of patent right due to non-payment of annual fee