CN103678832A - Method for calculating composite stress of non-equal structure superposed valve plates of vehicle shock absorber - Google Patents

Method for calculating composite stress of non-equal structure superposed valve plates of vehicle shock absorber Download PDF

Info

Publication number
CN103678832A
CN103678832A CN201410000605.0A CN201410000605A CN103678832A CN 103678832 A CN103678832 A CN 103678832A CN 201410000605 A CN201410000605 A CN 201410000605A CN 103678832 A CN103678832 A CN 103678832A
Authority
CN
China
Prior art keywords
valve plate
shock absorber
valve block
superimposed
composite stress
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
CN201410000605.0A
Other languages
Chinese (zh)
Other versions
CN103678832B (en
Inventor
周长城
宋群
刘小亭
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 CN201410000605.0A priority Critical patent/CN103678832B/en
Publication of CN103678832A publication Critical patent/CN103678832A/en
Application granted granted Critical
Publication of CN103678832B publication Critical patent/CN103678832B/en
Expired - Fee Related legal-status Critical Current
Anticipated expiration legal-status Critical

Links

Images

Landscapes

  • Vehicle Body Suspensions (AREA)

Abstract

本发明涉及汽车减振器非等构叠加阀片复合应力的计算方法，属于减振器技术领域，其特征在于：根据非等等构叠加阀片的内半径、外半径、厚度和片数，确定出不等外半径率系数、当量厚度、等效厚度及各叠加阀片的厚度比例系数，根据结构参数和材料特性参数，计算出非等构叠加阀片的复合应力系数，从而实现对各非等构叠加阀片在均布压力下在任意半径处的复合应力进行计算。通过与ANSYS仿真结果比较可知，该计算方法是正确的，为汽车减振器非等构叠加阀片的拆分设计和强度校核，提供了可靠的复合应力计算方法，可提高减振器的设计水平、质量和性能，在满足特性设计要求前提下，确保阀片应力强度设计要求，降低设计和试验费用及生产成本。

The invention relates to a method for calculating the composite stress of non-isostructural superimposed valve plates of automobile shock absorbers, which belongs to the technical field of shock absorbers, and is characterized in that: according to the inner radius, outer radius, thickness and number of non-isostructural superimposed valve plates, Determine the unequal outer radius rate coefficient, equivalent thickness, equivalent thickness and the thickness proportional coefficient of each superimposed valve plate, and calculate the composite stress coefficient of the non-isostructural superimposed valve plate according to the structural parameters and material characteristic parameters, so as to realize the control of each Composite stress of non-isomorphic superimposed valve plates at any radius under uniform pressure is calculated. By comparing with the simulation results of ANSYS, it can be seen that the calculation method is correct, and it provides a reliable composite stress calculation method for the split design and strength check of the non-isomorphic stacked valve plate of the automobile shock absorber, which can improve the performance of the shock absorber. Design level, quality and performance, on the premise of meeting the characteristic design requirements, ensure the design requirements of the stress strength of the valve plate, reduce design and test costs and production costs.

Description

汽车减振器非等构叠加阀片复合应力的计算方法Calculation Method of Composite Stress of Non-isostructural Superimposed Valve Plate of Automobile Shock Absorber

技术领域 technical field

本发明涉及汽车液压减振器，特别是汽车减振器非等构叠加阀片复合应力的计算方法。 The invention relates to an automobile hydraulic shock absorber, in particular to a calculation method for the composite stress of non-isostructural superimposed valve plates of the automobile shock absorber.

背景技术 Background technique

为了满足减振器特性及阀片应力强度，实际汽车减振器经常会采用多片非等构叠加阀片，即内圆半径相等外圆半径不等的叠加阀片，同时，采用设计合理的非等构叠加阀片，可免用“间隙限位垫圈”，因此可降低生产制造成本，具有显著的经济效益和社会效益。要真正实现汽车减振器非等构叠加阀片的拆分设计及强度校核，必须解决非等构叠加阀片的复合应力计算问题。尽管我国在减振器叠加阀片应力计算方面进行了大量研究并取得了突破，例如，山东理工大学曾对等构叠加阀片研究，并给出了减振器等构叠加阀片复合应力的计算方法，然而，对非等构叠加阀片的复合应力计算，目前国内、外却一直没有给出简便、可靠的计算方法，大都只能利用ANSYS有限元仿真软件，通过建立非等构叠加阀片的实体仿真模型，对复合应力进行数值仿真计算。尽管利用有限元仿真软件可得到可靠的值解，但是由于有限元仿真软件不能给出计算式，因此，不能满足汽车减振器及叠加阀片现代化CAD设计和强度校核的要求。随着汽车工业的快速发展及行驶速度的不断提高，对减振器及叠加阀片设计提出了更高的要求，要实现汽车减振器及非等构叠加阀片的现代化CAD设计，必须提供一种可靠的非等构叠加阀片复合应力的计算方法，从而满足减振器及非等构叠加阀片的实际设计、生产和强度校核的要求。 In order to meet the characteristics of the shock absorber and the stress intensity of the valve plate, the actual automobile shock absorber often uses multiple non-isostructural superimposed valve plates, that is, the superimposed valve plates with the same inner circle radius and different outer circle radius. Non-isostructural stacked valve plates can avoid the use of "gap limit washers", so the production cost can be reduced, and it has significant economic and social benefits. In order to truly realize the split design and strength check of non-isostructural superimposed valve plates of automobile shock absorbers, it is necessary to solve the problem of composite stress calculation of non-isostructural superimposed valve plates. Although our country has done a lot of research and made breakthroughs in the calculation of the stress calculation of the superimposed valve plate of the shock absorber, for example, Shandong University of Technology once studied the superimposed valve plate of the isostructure, and gave the composite stress of the superimposed valve plate of the shock absorber. However, for the calculation of the composite stress of non-isostructural superimposed valve plates, there is no simple and reliable calculation method at home and abroad. Most of them can only use ANSYS finite element simulation software to establish non-isostructural superimposed valves The solid simulation model of the sheet is used for numerical simulation calculation of the composite stress. Although a reliable value solution can be obtained by using the finite element simulation software, because the finite element simulation software cannot provide calculation formulas, it cannot meet the requirements of modern CAD design and strength check of automobile shock absorbers and superimposed valve plates. With the rapid development of the automobile industry and the continuous improvement of driving speed, higher requirements are put forward for the design of shock absorbers and superimposed valve plates. To realize the modern CAD design of automobile shock absorbers and non-isostructural superimposed valve plates, it is necessary to provide A reliable calculation method for the composite stress of the non-isostructural superimposed valve plate meets the requirements of the actual design, production and strength check of the shock absorber and the non-isostructural superimposed valve plate.

发明内容 Contents of the invention

针对上述现有技术中存在的缺陷，本发明所要解决的技术问题是提供一种简便、准确、可靠的汽车减振器非等构叠加阀片复合应力的计算方法，其计算流程如图1所示。 In view of the defects in the above-mentioned prior art, the technical problem to be solved by the present invention is to provide a simple, accurate and reliable calculation method for the composite stress of the non-isostructural superimposed valve plate of the automobile shock absorber, and its calculation process is shown in Figure 1 Show.

为了解决上述技术问题，本发明所提供的汽车减振器非等构叠加阀片复合应力的计算方法，非等叠加阀片的力学模型如图2所示,其技术方案实施步骤如下： In order to solve the above-mentioned technical problems, the calculation method of the composite stress of the non-isostructural superimposed valve plate of the automobile shock absorber provided by the present invention, the mechanical model of the non-equal superimposed valve plate is shown in Figure 2, and the implementation steps of the technical scheme are as follows:

（1）确定各非等构叠加阀片的外半径不等率系数η i : (1) Determine the outer radius non-uniformity coefficient η i of each non-isomorphic stacked valve plate:

根据汽车减振器非等构叠加阀片的外半径r b1, r b2,…, r bn,其中, r b1> r b2>… > r bn , 确定各叠加阀片的外半径不等率η i ,即: According to the outer radius r b1 , r b2 ,…, r bn of the non-isomorphic stacked valve slices of the automobile shock absorber, among them, r b1 > r b2 >… > r bn , determine the non-uniformity ratio η of the stacked valve slices i , namely:

                                                          

Figure 6237DEST_PATH_IMAGE001
,
Figure 359596DEST_PATH_IMAGE002
,…, 
Figure 77016DEST_PATH_IMAGE003
；
Figure 6237DEST_PATH_IMAGE001
,
Figure 359596DEST_PATH_IMAGE002
,…,
Figure 77016DEST_PATH_IMAGE003
;

（2）计算汽车减振器各非等构叠加阀片的当量厚度h ie: (2) Calculate the equivalent thickness h i e of each non-isostructural stacked valve plate of the automobile shock absorber:

根据汽车减振器各非等构叠加阀片的厚度h 1, h 2,…, h n ，及步骤（1）中的外半径不等率η i ，计算各非等构叠加阀片的当量厚度h ie，即: According to the thickness h 1 , h 2 ,…, h n of each non-isosteric superimposed valve plate of the automobile shock absorber, and the unequal ratio η i of the outer radius in step (1), calculate the equivalent of each non-isosteric superimposed valve plate Thickness h i e , namely:

    h 1e= h 1，h 2e=

Figure 409909DEST_PATH_IMAGE004
Figure 161964DEST_PATH_IMAGE005
，h 3e=
Figure 420645DEST_PATH_IMAGE006
,…, h ne=
Figure 430823DEST_PATH_IMAGE009
； h 1e = h 1 , h 2e =
Figure 409909DEST_PATH_IMAGE004
Figure 161964DEST_PATH_IMAGE005
, h 3e =
Figure 420645DEST_PATH_IMAGE006
,..., h n e =
Figure 430823DEST_PATH_IMAGE009
;

（3）计算非等构叠加阀片的等效厚度h E和厚度比例系数k hi ： (3) Calculate the equivalent thickness h E and thickness proportional coefficient k hi of non-isosteric stacked valve plates:

根据非等构叠加阀片的片数n 1，n 2，…，n n，及步骤（2）中的各叠加阀片的当量厚度h ie，计算汽车减振器非等构叠加阀片的等效厚度h E和各叠加阀片的厚度比例系数k hi ，即：  According to the number n 1 , n 2 ,…, n n of non-isosteric superimposed valve plates and the equivalent thickness h i e of each superimposed valve plate in step (2), calculate the non-isosteric superimposed valve plate of the automobile shock absorber The equivalent thickness h E and the thickness proportional coefficient k hi of each superimposed valve plate, that is:

Figure 361870DEST_PATH_IMAGE010
；
Figure 361870DEST_PATH_IMAGE010
;

Figure 552418DEST_PATH_IMAGE011
，
Figure 227113DEST_PATH_IMAGE012
，…，
Figure 688181DEST_PATH_IMAGE013
；
Figure 552418DEST_PATH_IMAGE011
,
Figure 227113DEST_PATH_IMAGE012
,...,
Figure 688181DEST_PATH_IMAGE013
;

（4）汽车减振器非等构叠加阀片在任意半径r处的复合应力系数

Figure 55708DEST_PATH_IMAGE014
计算： (4) Composite stress coefficient of non-isostructural stacked valve plate of automobile shock absorber at any radius r
Figure 55708DEST_PATH_IMAGE014
calculate:

根据第1片非等构叠加阀片的内圆半径r a，外圆半径r b1，弹性模量E和泊松比μ，计算汽车减振器非等构叠加阀片在任意半径r（r a≤r≤r b1）处的复合应力系数

Figure 733552DEST_PATH_IMAGE014
，即： According to the inner radius r a , outer radius r b1 , elastic modulus E and Poisson's ratio μ of the first non-isosteric superimposed valve plate, calculate the non-isosteric superimposed valve plate of the automobile shock absorber at any radius r ( r a ≤ r ≤ r b1 ) composite stress coefficient
Figure 733552DEST_PATH_IMAGE014
,Right now:

Figure 946359DEST_PATH_IMAGE015
Figure 946359DEST_PATH_IMAGE015

式中，

Figure 527513DEST_PATH_IMAGE016
，
Figure 236580DEST_PATH_IMAGE017
； In the formula,
Figure 527513DEST_PATH_IMAGE016
,
Figure 236580DEST_PATH_IMAGE017
;

Figure 965502DEST_PATH_IMAGE018
，
Figure 965502DEST_PATH_IMAGE018
,

Figure 982000DEST_PATH_IMAGE019
；
Figure 982000DEST_PATH_IMAGE019
;

Figure 417660DEST_PATH_IMAGE020
,
Figure 189307DEST_PATH_IMAGE021
, 
Figure 77629DEST_PATH_IMAGE022
,
Figure 417660DEST_PATH_IMAGE020
,
Figure 189307DEST_PATH_IMAGE021
,
Figure 77629DEST_PATH_IMAGE022
,

Figure 396352DEST_PATH_IMAGE023
， 
Figure 396352DEST_PATH_IMAGE023
,

Figure 686519DEST_PATH_IMAGE024
，
Figure 566751DEST_PATH_IMAGE025
，，，
Figure 209456DEST_PATH_IMAGE028
，
Figure 260589DEST_PATH_IMAGE029
，
Figure 123503DEST_PATH_IMAGE030
，；
Figure 686519DEST_PATH_IMAGE024
,
Figure 566751DEST_PATH_IMAGE025
, , ,
Figure 209456DEST_PATH_IMAGE028
,
Figure 260589DEST_PATH_IMAGE029
,
Figure 123503DEST_PATH_IMAGE030
, ;

其中，当r=r a的复合应力系数

Figure 783209DEST_PATH_IMAGE014
，即为非等构叠加阀片在内圆半径r a处的最大复合应力系数
Figure 67560DEST_PATH_IMAGE032
，即： where, when r = r the composite stress coefficient of a
Figure 783209DEST_PATH_IMAGE014
, which is the maximum composite stress coefficient at the radius r a of the inner circle of the non-isostructural superimposed valve plate
Figure 67560DEST_PATH_IMAGE032
,Right now:

Figure 417770DEST_PATH_IMAGE033
Figure 417770DEST_PATH_IMAGE033

式中， 

Figure 383452DEST_PATH_IMAGE034
，； In the formula,
Figure 383452DEST_PATH_IMAGE034
, ;

Figure 128609DEST_PATH_IMAGE036
，
Figure 128609DEST_PATH_IMAGE036
,

Figure 966115DEST_PATH_IMAGE037
；
Figure 966115DEST_PATH_IMAGE037
;

（5）汽车减振器各非等构叠加阀片复合应力

Figure 906126DEST_PATH_IMAGE038
的计算： (5) Composite stress of non-isostructural superimposed valve plates of automobile shock absorbers
Figure 906126DEST_PATH_IMAGE038
The calculation of:

       根据汽车减振器非等构叠加阀片所受的压力p，步骤（3）中的等效厚度h E和厚度比例系数

Figure 207795DEST_PATH_IMAGE039
，及步骤（4）中的复合应力系数
Figure 506052DEST_PATH_IMAGE014
，对汽车减振器各非等构叠加阀片在任意半径r处的复合应力量进行计算，即： According to the pressure p of the non-isosteric superimposed valve plate of the automobile shock absorber, the equivalent thickness h E and the thickness proportional coefficient in step (3)
Figure 207795DEST_PATH_IMAGE039
, and the composite stress coefficient in step (4)
Figure 506052DEST_PATH_IMAGE014
, the composite stress of each non-isostructural stacked valve plate at any radius r of the automobile shock absorber Do the calculation, that is:

Figure 138339DEST_PATH_IMAGE040
；
Figure 138339DEST_PATH_IMAGE040
;

其中，当

Figure 465153DEST_PATH_IMAGE014
为内圆半径r a处的最大复合应力系数
Figure 262207DEST_PATH_IMAGE041
，则
Figure 808726DEST_PATH_IMAGE038
即为非叠加阀片在内圆半径位置处的最大复合应力
Figure 868266DEST_PATH_IMAGE043
。 Among them, when
Figure 465153DEST_PATH_IMAGE014
is the maximum composite stress coefficient at the radius r a of the inner circle
Figure 262207DEST_PATH_IMAGE041
,but
Figure 808726DEST_PATH_IMAGE038
non-stacked valve Maximum composite stress at the radius of the inner circle
Figure 868266DEST_PATH_IMAGE043
.

本发明比现有技术具有的优点： The present invention has the advantage over prior art:

目前，国内外对汽车减振器非等构叠加阀片的复合应力计算一直没有给出简便、可靠的计算方法，大都只能利用ANSYS有限元仿真软件，通过建立非等构叠加阀片的实体仿真模型，对复合应力进行数值仿真计算，得到近似的复合应力值，然而，由于有限元仿真软件不能给出计算式或计算方法，因此，不能满足汽车减振器及非等构叠加阀片实际设计和生产及强度校核的要求。本发明对于汽车减振器非等构叠加阀片复合应力的计算方法，首先，根据各非等构叠加阀片的内半径

Figure 272441DEST_PATH_IMAGE044
、外半径
Figure 306256DEST_PATH_IMAGE045
、厚度
Figure 955543DEST_PATH_IMAGE047
和片数，确定出各叠加阀片的不等外半径率系数
Figure 333489DEST_PATH_IMAGE051
、当量厚度h ie，并计算出非等构叠加阀片的等效厚度
Figure 854600DEST_PATH_IMAGE052
和各叠加阀片的厚度比例系数；然后，根据叠加阀片的结构和材料特性参数，计算出非等构叠加阀片的复合应力系数
Figure 27273DEST_PATH_IMAGE054
；随后，根据非等构叠加阀片的压力p，复合应力系数
Figure 274715DEST_PATH_IMAGE054
、等效厚度
Figure 345439DEST_PATH_IMAGE052
及各非等构叠加阀片的厚度比例系数，利用
Figure 550210DEST_PATH_IMAGE055
对各非等构叠加阀片的复合应力
Figure 968553DEST_PATH_IMAGE056
进行计算。通过与ANSYS仿真结果比较可知，该汽车减振器非等构叠加阀片复合应力的计算方法是正确的，为实际汽车减振器非等构叠加阀片的拆分设计和强度校核，提供了可靠的非等构叠加阀片复合应力的计算方法。 At present, no simple and reliable calculation method has been given for the composite stress calculation of non-isostructural superimposed valve plates of automobile shock absorbers at home and abroad. Most of them can only use ANSYS finite element simulation software to establish the entity The simulation model performs numerical simulation calculations on the composite stress to obtain an approximate composite stress value. However, since the finite element simulation software cannot provide calculation formulas or calculation methods, it cannot meet the actual conditions of automobile shock absorbers and non-isostructural superimposed valve plates. Requirements for design and production and strength check. For the calculation method of the composite stress of the non-isostructural superimposed valve plates of the automobile shock absorber in the present invention, firstly, according to the inner radius of each non-isostructural superimposed valve plate
Figure 272441DEST_PATH_IMAGE044
, outer radius
Figure 306256DEST_PATH_IMAGE045
,thickness
Figure 955543DEST_PATH_IMAGE047
and number of pieces , to determine the unequal outer radius ratio coefficients of each superimposed valve plate
Figure 333489DEST_PATH_IMAGE051
, equivalent thickness h i e , and calculate the equivalent thickness of non-isostructural stacked valve plates
Figure 854600DEST_PATH_IMAGE052
and the thickness proportional coefficient of each superimposed valve plate ; Then, according to the structure and material characteristic parameters of the superimposed valve disc, the composite stress coefficient of the non-isosteric superimposed valve disc is calculated
Figure 27273DEST_PATH_IMAGE054
; Subsequently, according to the pressure p of the non-isosteric stacked valve plates, the composite stress coefficient
Figure 274715DEST_PATH_IMAGE054
, equivalent thickness
Figure 345439DEST_PATH_IMAGE052
and the thickness proportional coefficient of each non-isomorphic stacked valve plate ,use
Figure 550210DEST_PATH_IMAGE055
Composite stress for each non-isostructural superimposed valve plate
Figure 968553DEST_PATH_IMAGE056
Calculation. By comparing with the ANSYS simulation results, it can be seen that the calculation method of the composite stress of the non-isostructural superimposed valve plate of the automobile shock absorber is correct, and it provides a reference for the split design and strength check of the non-isostructural superimposed valve plate of the actual automobile shock absorber. A reliable calculation method for the composite stress of non-isosteric superimposed valve plates is presented.

为了更好地理解本发明下面结合附图作进一步的说明。 In order to better understand the present invention, the following will be further described in conjunction with the accompanying drawings.

图1是汽车减振器非等构叠加阀片复合应力的计算方法流程图； Figure 1 is a flow chart of the calculation method for the composite stress of the non-isostructural superimposed valve plate of the automobile shock absorber;

图2是汽车减振器非等构叠加阀片的力学模型； Figure 2 is the mechanical model of the non-isostructural stacked valve plate of the automobile shock absorber;

图3是实施例一的汽车减振器非等构叠加阀片的复合应力系数

Figure 697212DEST_PATH_IMAGE057
； Fig. 3 is the composite stress coefficient of the non-isostructural stacked valve plate of the automobile shock absorber of embodiment one
Figure 697212DEST_PATH_IMAGE057
;

图4是实施例一的汽车减振器非等构叠加阀片的复合应力

Figure 491993DEST_PATH_IMAGE058
曲线； Fig. 4 is the composite stress of the non-isostructural stacked valve plate of the automobile shock absorber of embodiment one
Figure 491993DEST_PATH_IMAGE058
curve;

图5是实施例一的汽车减振器非等构叠加阀片复合应力仿真云图； Fig. 5 is the composite stress simulation cloud diagram of the non-isostructural stacked valve plate of the automobile shock absorber of embodiment one;

图6是实施例二的汽车减振器非等构叠加阀片的复合应力

Figure 186279DEST_PATH_IMAGE058
曲线； Fig. 6 is the composite stress of the non-isostructural superimposed valve plate of the automobile shock absorber of the second embodiment
Figure 186279DEST_PATH_IMAGE058
curve;

图7是实施例二的汽车减振器非等构叠加阀片复合应力仿真云图； Fig. 7 is the composite stress simulation cloud diagram of the non-isostructural superimposed valve plate of the automobile shock absorber of embodiment two;

图8是实施例三的汽车减振器非等构叠加阀片的复合应力

Figure 775524DEST_PATH_IMAGE058
曲线； Fig. 8 is the composite stress of the non-isostructural stacked valve plate of the automobile shock absorber of the third embodiment
Figure 775524DEST_PATH_IMAGE058
curve;

图9是实施例三的汽车减振器非等构叠加阀片复合应力仿真云图； Fig. 9 is the composite stress simulation cloud diagram of the non-isostructural superimposed valve plate of the automobile shock absorber of the third embodiment;

图10是实施例四的汽车减振器非等构叠加阀片的复合应力系数

Figure 758523DEST_PATH_IMAGE057
； Fig. 10 is the composite stress coefficient of the non-isostructural superimposed valve plate of the automobile shock absorber of the fourth embodiment
Figure 758523DEST_PATH_IMAGE057
;

图11是实施例四的汽车减振器非等构叠加阀片的复合应力曲线； Figure 11 is the composite stress of the non-isostructural stacked valve plate of the automobile shock absorber of the fourth embodiment curve;

图12是实施例四的汽车减振器非等构叠加阀片复合应力仿真云图。 Fig. 12 is a simulation cloud diagram of the composite stress of the non-isostructural superimposed valve plate of the automobile shock absorber of the fourth embodiment.

 具体实施方案 Specific implementation plan

下面通过实施例对本发明作进一步详细说明。 The present invention will be described in further detail below by way of examples.

实施例一：某汽车减振器非等构叠加阀片的内圆半径r a＝5.0mm，弹性模量E=200GPa，泊松比μ＝0.3，叠加阀片的厚度、片数和外半径分别为h 1=0.25mm，n 1=1，r b1=8.5mm；h 2=0.20mm，n 2=1，r b2=7.0mm；h 3=0.15mm，n 3=1，r b3=6.0mm；阀片所受压力p=3.0MPa，计算该汽车减振器非等构叠加阀片的复合应力。 Example 1: The inner circle radius r a of an automobile shock absorber non-isomorphic superimposed valve plate = 5.0mm, the elastic modulus E = 200GPa, Poisson’s ratio μ = 0.3, the thickness, number and outer radius of the superimposed valve plate h 1 =0.25mm, n 1 =1, r b1 =8.5mm; h 2 =0.20mm, n 2 =1, r b2 =7.0mm; h 3 =0.15mm, n 3 =1, r b3 = 6.0mm; the pressure on the valve plate p = 3.0MPa, calculate the composite stress of the non-isostructural stacked valve plate of the automobile shock absorber.

（1）确定各非等构叠加阀片的外半径不等率系数η i : (1) Determine the outer radius non-uniformity coefficient η i of each non-isomorphic stacked valve plate:

根据汽车减振器非等构叠加阀片的外半径

Figure 99864DEST_PATH_IMAGE059
=8.5mm,
Figure 125589DEST_PATH_IMAGE060
=7.0mm,
Figure 330306DEST_PATH_IMAGE061
=6.0mm,确定各叠加阀片的外半径不等率η i ,即 According to the outer radius of non-isostructural superimposed valve plate of automobile shock absorber
Figure 99864DEST_PATH_IMAGE059
=8.5mm,
Figure 125589DEST_PATH_IMAGE060
=7.0mm,
Figure 330306DEST_PATH_IMAGE061
=6.0mm, determine the outer radius unequal ratio η i of each superimposed valve plate, that is

                      η 1=0, 

Figure 529206DEST_PATH_IMAGE062
=0.4286，
Figure 368724DEST_PATH_IMAGE063
=0.7143； η 1 =0,
Figure 529206DEST_PATH_IMAGE062
=0.4286,
Figure 368724DEST_PATH_IMAGE063
=0.7143;

（2）计算各非等构叠加阀片的当量厚度h ie: (2) Calculate the equivalent thickness h i e of each non-isostructural superimposed valve plate:

根据汽车减振器各非等构叠加阀片的厚度h 1=0.25mm, h 2=0.20mm，h 3=0.15mm,, 及步骤（1）中的外半径不等率η 1=0，η 2=0.1286，η 3=0.7143，分别计算各非等构叠加阀片的当量厚度h ie，即 According to the thickness h 1 =0.25mm, h 2 =0.20mm, h 3 =0.15mm, and the outer radius unequal ratio η 1 =0 in the step (1), η 2 =0.1286, η 3 =0.7143, respectively calculate the equivalent thickness h i e of each anisotropic superimposed valve plate, namely

    h 1e=0.25mm，h 2e= =0.19206mm，h 3e=

Figure 932057DEST_PATH_IMAGE006
Figure 829344DEST_PATH_IMAGE007
=0.12227； h 1e =0.25mm, h 2e = =0.19206mm, h 3e =
Figure 932057DEST_PATH_IMAGE006
Figure 829344DEST_PATH_IMAGE007
=0.12227;

（3）计算非等构叠加阀片的等效厚度h E和厚度比例系数k hi ： (3) Calculate the equivalent thickness h E and thickness proportional coefficient k hi of non-isosteric stacked valve plates:

根据某汽车减振器非等构叠加阀片的当量厚度和片数h 1e=0.25mm，n 1=1；h 2e=0.19206mm，n 2=1；h 3e=0.12227mm，n 3=1，计算非等构叠加阀片的等效厚度h E为： According to the equivalent thickness and number of non-isomorphic superimposed valve plates of an automobile shock absorber h 1e =0.25mm, n 1 =1; h 2e =0.19206mm, n 2 =1; h 3e =0.12227mm, n 3 =1 , calculate the equivalent thickness h E of the non-isosteric superimposed valve plate as:

=0.29059mm； =0.29059mm;

各非等构叠加阀片的厚度比例系数k hi 分别为； The thickness proportional coefficients k hi of each non-isomorphic superimposed valve plate are respectively;

Figure 172917DEST_PATH_IMAGE011
=0.8603，
Figure 651303DEST_PATH_IMAGE012
= 0.6609，
Figure 730992DEST_PATH_IMAGE065
= 0.4208；
Figure 172917DEST_PATH_IMAGE011
=0.8603,
Figure 651303DEST_PATH_IMAGE012
= 0.6609,
Figure 730992DEST_PATH_IMAGE065
= 0.4208;

（4）计算非等构叠加阀片在任意半径r的复合应力系数

Figure 66159DEST_PATH_IMAGE014
： (4) Calculating the composite stress coefficient of the non-isomorphic stacked valve plate at any radius r
Figure 66159DEST_PATH_IMAGE014
:

根据第1片叠加阀片的内圆半径

Figure 732764DEST_PATH_IMAGE044
=5.0mm，外圆半径=8.5mm，弹性模量E=2.0
Figure 184922DEST_PATH_IMAGE067
和泊松比μ=0.3，计算非等构叠加阀片在任意半径r（r a ≤r≤r b1）的复合应力系数，即： According to the inner circle radius of the first superimposed valve plate
Figure 732764DEST_PATH_IMAGE044
=5.0mm, outer circle radius =8.5mm, elastic modulus E =2.0
Figure 184922DEST_PATH_IMAGE067
and Poisson's ratio μ =0.3, calculate the composite stress coefficient of the non-isosteric stacked valve plate at any radius r ( r a ≤ r ≤ r b1 ) ,Right now:

Figure 281108DEST_PATH_IMAGE068
Figure 281108DEST_PATH_IMAGE068

式中，，

Figure 453781DEST_PATH_IMAGE017
； In the formula, ,
Figure 453781DEST_PATH_IMAGE017
;

Figure 770230DEST_PATH_IMAGE018
，
Figure 770230DEST_PATH_IMAGE018
,

Figure 145848DEST_PATH_IMAGE019
；
Figure 145848DEST_PATH_IMAGE019
;

Figure 504148DEST_PATH_IMAGE069
，
Figure 914401DEST_PATH_IMAGE070
，
Figure 504148DEST_PATH_IMAGE069
,
Figure 914401DEST_PATH_IMAGE070
,

 

Figure 198490DEST_PATH_IMAGE071
,
Figure 198490DEST_PATH_IMAGE071
,

Figure 61403DEST_PATH_IMAGE072
=
Figure 223394DEST_PATH_IMAGE074
；       
Figure 61403DEST_PATH_IMAGE072
=
Figure 223394DEST_PATH_IMAGE074
;

Figure 488154DEST_PATH_IMAGE024
=200，
Figure 208723DEST_PATH_IMAGE025
=
Figure 558933DEST_PATH_IMAGE075
，
Figure 259035DEST_PATH_IMAGE026
=0.01，
Figure 378301DEST_PATH_IMAGE027
=5.0
Figure 833553DEST_PATH_IMAGE077
，
Figure 169594DEST_PATH_IMAGE028
=
Figure 673388DEST_PATH_IMAGE079
，
Figure 709477DEST_PATH_IMAGE029
=
Figure 273314DEST_PATH_IMAGE080
，
Figure 598116DEST_PATH_IMAGE081
=2.6，
Figure 138556DEST_PATH_IMAGE031
=
Figure 232414DEST_PATH_IMAGE083
；
Figure 488154DEST_PATH_IMAGE024
=200,
Figure 208723DEST_PATH_IMAGE025
=
Figure 558933DEST_PATH_IMAGE075
,
Figure 259035DEST_PATH_IMAGE026
=0.01,
Figure 378301DEST_PATH_IMAGE027
=5.0
Figure 833553DEST_PATH_IMAGE077
,
Figure 169594DEST_PATH_IMAGE028
=
Figure 673388DEST_PATH_IMAGE079
,
Figure 709477DEST_PATH_IMAGE029
=
Figure 273314DEST_PATH_IMAGE080
,
Figure 598116DEST_PATH_IMAGE081
=2.6,
Figure 138556DEST_PATH_IMAGE031
=
Figure 232414DEST_PATH_IMAGE083
;

       计算得到的复合应力系数

Figure 967152DEST_PATH_IMAGE014
随半径r（r a ≤r≤r b1）的变化曲线，如图3所示，其中，在内圆半径r a处的最大复合应力系数
Figure 575988DEST_PATH_IMAGE084
= 42.419mm2； The calculated composite stress factor
Figure 967152DEST_PATH_IMAGE014
Variation curve with radius r ( r a ≤ r ≤ r b1 ), as shown in Figure 3, where the maximum composite stress coefficient at the inner circle radius r a
Figure 575988DEST_PATH_IMAGE084
= 42.419mm 2 ;

（5）汽车减振器各非等构叠加阀片复合应力

Figure 687163DEST_PATH_IMAGE038
的计算： (5) Composite stress of non-isostructural superimposed valve plates of automobile shock absorbers
Figure 687163DEST_PATH_IMAGE038
The calculation of:

根据叠加阀片所受的压力p=3.0MPa，步骤（3）中的叠加阀片的等效厚度h E=0.29059mm和厚度比例系数k h1＝0.8603，k h2＝0.6609，k h3＝0.4208，及步骤（4）中的复合应力系数

Figure 134063DEST_PATH_IMAGE014
，对各非等构叠加阀片在任意半径r处的复合应力
Figure 39702DEST_PATH_IMAGE038
进行计算，即： According to the pressure p =3.0MPa on the stacked valve plate, the equivalent thickness h E =0.29059mm and the thickness proportional coefficient k h 1 =0.8603, k h 2 =0.6609, k h 3 of the stacked valve plate in step (3) =0.4208, and the composite stress coefficient in step (4)
Figure 134063DEST_PATH_IMAGE014
, for the composite stress of each non-isosteric superimposed valve plate at any radius r
Figure 39702DEST_PATH_IMAGE038
Do the calculation, that is:

Figure 73517DEST_PATH_IMAGE040
；
Figure 73517DEST_PATH_IMAGE040
;

    计算所得到的各非等构叠加阀片的复合应力

Figure 457225DEST_PATH_IMAGE038
曲线，如图4所示，其中，各非等构叠加阀片的最大复合应力分别为
Figure 24210DEST_PATH_IMAGE085
1296.6MPa、
Figure 100751DEST_PATH_IMAGE086
996.09MPa、
Figure 684179DEST_PATH_IMAGE087
634.1MPa。 Composite stress of each non-isosteric superimposed valve plate obtained by calculation
Figure 457225DEST_PATH_IMAGE038
curve, as shown in Figure 4, where the maximum composite stress of each non-isostructural superimposed valve plate is
Figure 24210DEST_PATH_IMAGE085
1296.6MPa,
Figure 100751DEST_PATH_IMAGE086
996.09MPa,
Figure 684179DEST_PATH_IMAGE087
634.1MPa.

根据汽车减振器非等构叠加阀片的内圆半径r a＝5.0mm，弹性模型E＝200GPa，泊松比μ＝0.3，及各非等构叠加阀片的厚度、片数和外半径分别为h 1=0.25mm，n 1=1，r b1=8.5mm；h 2=0.20mm，n 2=1，r b2=7.0mm；h 3=0.15mm，n 3=1，r b3=6.0mm，利用ANSYS建立叠加阀片仿真模型，网格划分单位为0.1mm，在施加相同均布压力p＝3.0MPa情况下，仿真所得到的叠加阀片复合应力仿真云图，如图5所示。 According to the inner circle radius r a = 5.0mm of the non-isomorphic stacked valve plates of the automobile shock absorber, the elastic model E = 200GPa, Poisson’s ratio μ = 0.3, and the thickness, number and outer radius of each non-isomorphic stacked valve plate h 1 =0.25mm, n 1 =1, r b1 =8.5mm; h 2 =0.20mm, n 2 =1, r b2 =7.0mm; h 3 =0.15mm, n 3 =1, r b3 = 6.0mm, using ANSYS to establish a simulation model of the superimposed valve plate, the grid division unit is 0.1mm, and under the same uniform pressure p = 3.0MPa, the simulation cloud diagram of the composite stress of the superimposed valve plate obtained by simulation is shown in Figure 5 .

由图5可知，在均布压力p＝3.0MPa下，该汽车减振器非等构叠加阀片最大复合应力的仿真值为1270MPa，与利用该计算方法所得到的第1片叠加阀片的最大复合应力1296.6MPa相吻合，相对偏差仅为2.05%，表明本发明所建立的汽车减振器非等构叠加阀片复合应力的计算方法是可靠的。 It can be seen from Figure 5 that under the uniform pressure p = 3.0MPa, the simulated value of the maximum composite stress of the non-isomorphic superimposed valve plate of the automobile shock absorber is 1270MPa, which is different from the value of the first superimposed valve plate obtained by this calculation method. The maximum composite stress is 1296.6MPa, and the relative deviation is only 2.05%, which shows that the calculation method for the composite stress of the non-isomorphic superimposed valve plate of the automobile shock absorber established by the present invention is reliable.

实施例二：某汽车减振器非等构叠加阀片的内圆半径r a＝5.0mm，弹性模量E=200GPa，泊松比μ＝0.3，叠加阀片的厚度、片数和外半径分别为h 1=0.30mm，n 1=1，r b1=8.5mm；h 2=0.20mm，n 2=1，r b2=7.0mm；非等构叠加阀片所受压力p=3.0MPa，计算该汽车减振器非等构叠加阀片的复合应力。 Example 2: The inner circle radius r a of an automobile shock absorber non-isomorphic superimposed valve plate = 5.0mm, the elastic modulus E = 200GPa, Poisson’s ratio μ = 0.3, the thickness, number and outer radius of the superimposed valve plate Respectively h 1 =0.30mm, n 1 =1, r b1 =8.5mm; h 2 =0.20mm, n 2 =1, r b2 =7.0mm; pressure p =3.0MPa, Calculate the composite stress of the non-isostructural stacked valve plate of the automobile shock absorber.

按实施例一的步骤进行计算，即： Calculate according to the steps of Example 1, namely:

（1）确定各非等构叠加阀片的外半径不等率系数η i ： (1) Determine the outer radius non-uniformity coefficient η i of each non-isostructural stacked valve plate:

根据汽车减振器非等构叠加阀片的外半径

Figure 871578DEST_PATH_IMAGE059
=8.5mm,=7.0mm, 确定各叠加阀片的外半径不等率η i ,即： According to the outer radius of non-isostructural superimposed valve plate of automobile shock absorber
Figure 871578DEST_PATH_IMAGE059
=8.5mm, =7.0mm, determine the outer radius unequal ratio η i of each superimposed valve plate, namely:

                      η 1=0, 

Figure 540511DEST_PATH_IMAGE088
=0.4286； η 1 =0,
Figure 540511DEST_PATH_IMAGE088
=0.4286;

（2）计算各非等构叠加阀片的当量厚度h ie: (2) Calculate the equivalent thickness h i e of each non-isostructural superimposed valve plate:

根据汽车减振器各非等构叠加阀片的厚度

Figure 548919DEST_PATH_IMAGE090
=0.30mm,
Figure 602325DEST_PATH_IMAGE091
=0.20mm，及步骤（1）中的外半径不等率η 1=0，η 2=0.4286，分别计算各非等构叠加阀片的当量厚度h ie，即： According to the thickness of the non-isostructural superimposed valve plate of the automobile shock absorber
Figure 548919DEST_PATH_IMAGE090
=0.30mm,
Figure 602325DEST_PATH_IMAGE091
=0.20mm, and the outer radius unequal ratio in step (1) η 1 =0, η 2 =0.4286, respectively calculate the equivalent thickness h i e of each anisotropic stacked valve plate, namely:

    h 1e=0.30mm，h 2e=

Figure 379788DEST_PATH_IMAGE004
Figure 798131DEST_PATH_IMAGE092
=0.19312mm； h 1e =0.30mm, h 2e =
Figure 379788DEST_PATH_IMAGE004
Figure 798131DEST_PATH_IMAGE092
=0.19312mm;

（3）计算非等构叠加阀片的等效厚度h E和厚度比例系数k hi ： (3) Calculate the equivalent thickness h E and thickness proportional coefficient k hi of non-isosteric stacked valve plates:

根据某汽车减振器非等构叠加阀片的当量厚度和片数h 1e=0.30mm，n 1=1；h 2e=0.19312mm，n 2=1，计算非等构叠加阀片的等效厚度h E为： According to the equivalent thickness and number of non-isostructural superimposed valve plates of an automobile shock absorber h 1e =0.30mm, n 1 =1; h 2e =0.19312mm, n 2 =1, calculate the equivalent non-isostructural superimposed valve plate The thickness h E is:

Figure 526791DEST_PATH_IMAGE093
=0.3246mm；
Figure 526791DEST_PATH_IMAGE093
=0.3246mm;

各非等构叠加阀片的厚度比例系数k hi 分别为； The thickness proportional coefficients k hi of each non-isomorphic superimposed valve plate are respectively;

Figure 383888DEST_PATH_IMAGE011
= 0.9242，= 0.5949；
Figure 383888DEST_PATH_IMAGE011
= 0.9242, = 0.5949;

（4）计算非等构叠加阀片在任意半径r的复合应力系数

Figure 605102DEST_PATH_IMAGE014
： (4) Calculating the composite stress coefficient of the non-isomorphic stacked valve plate at any radius r
Figure 605102DEST_PATH_IMAGE014
:

由于第1片非等构叠加阀片的结构、材料特性与实施例一的相同，因此，该汽车减振器非等构叠加阀片在任意半径r的复合应力系数

Figure 588102DEST_PATH_IMAGE014
，也与实施例一的相同，如图3所示； Since the structure and material properties of the first non-isomorphic superimposed valve plate are the same as those in Example 1, the composite stress coefficient of the non-isomorphic superimposed valve plate of the automobile shock absorber at any radius r
Figure 588102DEST_PATH_IMAGE014
, is also the same as that of Embodiment 1, as shown in Figure 3;

（5）汽车减振器各非等构叠加阀片复合应力

Figure 983311DEST_PATH_IMAGE038
的计算： (5) Composite stress of non-isostructural superimposed valve plates of automobile shock absorbers
Figure 983311DEST_PATH_IMAGE038
The calculation of:

       根据汽车减振器非等构叠加阀片所受的压力p=3.0MPa，步骤（3）中的叠加阀片等效厚度h E=0.3246mm和各非等构叠加阀片的厚度比例系数

Figure 968322DEST_PATH_IMAGE094
0.9242，
Figure 994047DEST_PATH_IMAGE095
0.5949，及步骤（4）中的复合应力系数，对各非等构叠加阀片在任意半径r处的复合应力
Figure 132084DEST_PATH_IMAGE038
进行计算，即： According to the pressure p =3.0MPa on the non-isomorphic stacked valve slices of the automobile shock absorber, the equivalent thickness h E of the stacked valve slices in step (3) =0.3246mm and the thickness proportional coefficient of each non-isomorphic stacked valve slice
Figure 968322DEST_PATH_IMAGE094
0.9242,
Figure 994047DEST_PATH_IMAGE095
0.5949, and the composite stress coefficient in step (4) , for the composite stress of each non-isosteric superimposed valve plate at any radius r
Figure 132084DEST_PATH_IMAGE038
Do the calculation, that is:

                                  

Figure 738646DEST_PATH_IMAGE040
，
Figure 738646DEST_PATH_IMAGE040
,

    计算所得到的各非等构叠加阀片的复合应力

Figure 433807DEST_PATH_IMAGE038
曲线，如图6所示，其中，各非等构叠加阀片的最大复合应力分别为
Figure 922558DEST_PATH_IMAGE096
1116.2MPa，
Figure 862832DEST_PATH_IMAGE097
718.55MPa。 Composite stress of each non-isosteric superimposed valve plate obtained by calculation
Figure 433807DEST_PATH_IMAGE038
Curve, as shown in Figure 6, where the maximum composite stress of each non-isostructural superimposed valve plate is
Figure 922558DEST_PATH_IMAGE096
1116.2MPa,
Figure 862832DEST_PATH_IMAGE097
718.55 MPa.

根据汽车减振器非等构叠加阀片的内圆半径r a＝5.0mm，弹性模型E＝200GPa，泊松比μ＝0.3，及各非等构叠加阀片的厚度、片数和外半径分别为h 1=0.30mm，n 1=1，r b1=8.5mm；h 2=0.20mm，n 2=1，r b2=7.0mm，利用ANSYS建立叠加阀片仿真模型，网格划分单位为0.1mm，在施加相同均布压力p＝3.0MPa情况下，仿真所得到的叠加阀片复合应力仿真云图，如图7所示。 According to the inner circle radius r a = 5.0mm of the non-isomorphic stacked valve plates of the automobile shock absorber, the elastic model E = 200GPa, Poisson’s ratio μ = 0.3, and the thickness, number and outer radius of each non-isomorphic stacked valve plate Respectively h 1 =0.30mm, n 1 =1, r b1 =8.5mm; h 2 =0.20mm, n 2 =1, r b2 =7.0mm, using ANSYS to establish a simulation model of superimposed valve slices, the grid division unit is 0.1mm, in the case of applying the same uniform pressure p = 3.0MPa, the simulation cloud diagram of the composite stress of the superimposed valve plate obtained by simulation is shown in Figure 7.

由图7可知，在均布压力p＝3.0MPa下，该汽车减振器非等构叠加阀片最大复合应力

Figure 323900DEST_PATH_IMAGE098
的仿真值为1110MPa，与利用该计算方法所得到的第1片叠加阀片的最大复合应力
Figure 425848DEST_PATH_IMAGE099
1116.2MPa相吻合，相对偏差仅为0.56%，表明本发明所建立的汽车减振器非等构叠加阀片复合应力的计算方法是可靠的。 It can be seen from Figure 7 that under the uniform pressure p = 3.0MPa, the maximum composite stress of the non-isomorphic stacked valve plate of the automobile shock absorber
Figure 323900DEST_PATH_IMAGE098
The simulation value of is 1110MPa, which is the same as the maximum composite stress of the first superimposed valve plate obtained by this calculation method
Figure 425848DEST_PATH_IMAGE099
1116.2MPa coincides with each other, and the relative deviation is only 0.56%, which shows that the calculation method for the composite stress of the non-isomorphic superimposed valve plate of the automobile shock absorber established by the present invention is reliable.

实施例三：某汽车减振器非等构叠加阀片的内圆半径r a＝5.0mm，弹性模量E=200GPa，泊松比μ＝0.3，叠加阀片的厚度、片数和外半径分别为h 1=0.2mm，n 1=1，r b1=8.5mm；h 2=0.15mm，n 2=1，r b2=7.0mm；叠加阀片所受压力p=2.5MPa，计算该汽车减振器非等构叠加阀片的复合应力。 Embodiment 3: The inner circle radius r a of a certain automobile shock absorber non-isostructural superimposed valve plate = 5.0mm, elastic modulus E = 200GPa, Poisson’s ratio μ = 0.3, the thickness, number and outer radius of the superimposed valve plate Respectively h 1 =0.2mm, n 1 =1, r b1 =8.5mm; h 2 =0.15mm, n 2 =1, r b2 =7.0mm; pressure p =2.5MPa on the superimposed valve plate, calculate the vehicle The composite stress of the non-isostructural superimposed valve plate of the shock absorber.

按实施例一的步骤进行计算，即： Calculate according to the steps of Example 1, namely:

（1）确定各非等构叠加阀片的外半径不等率系数η i ： (1) Determine the outer radius non-uniformity coefficient η i of each non-isostructural stacked valve plate:

根据汽车减振器非等构叠加阀片的外半径=8.5mm,

Figure 667832DEST_PATH_IMAGE060
=7.0mm, 确定各叠加阀片的外半径不等率η i ,即 According to the outer radius of non-isostructural superimposed valve plate of automobile shock absorber =8.5mm,
Figure 667832DEST_PATH_IMAGE060
=7.0mm, determine the outer radius unequal ratio η i of each superimposed valve plate, that is

                      η 1=0,    η 2=

Figure 983407DEST_PATH_IMAGE100
=0.4286； η 1 =0, η 2 =
Figure 983407DEST_PATH_IMAGE100
=0.4286;

（2）计算各非等构叠加阀片的当量厚度h ie: (2) Calculate the equivalent thickness h i e of each non-isostructural superimposed valve plate:

根据汽车减振器各非等构叠加阀片的厚度

Figure 521836DEST_PATH_IMAGE090
=0.20mm,
Figure 922861DEST_PATH_IMAGE091
=0.15mm，及步骤（1）中的外半径不等率η 1=0，η 2=0.4286，分别计算各非等构叠加阀片的当量厚度h ie，即 According to the thickness of the non-isostructural superimposed valve plate of the automobile shock absorber
Figure 521836DEST_PATH_IMAGE090
=0.20mm,
Figure 922861DEST_PATH_IMAGE091
=0.15mm, and the outer radius unequal ratio in step (1) η 1 =0, η 2 =0.4286, respectively calculate the equivalent thickness h i e of each non-isomorphic superimposed valve plate, namely

    h 1e=0.2mm，h 2e=

Figure 201451DEST_PATH_IMAGE092
=0. 14438mm； h 1e =0.2mm, h 2e =
Figure 201451DEST_PATH_IMAGE092
=0.14438mm;

（3）计算非等构叠加阀片的等效厚度h E和厚度比例系数k hi ： (3) Calculate the equivalent thickness h E and thickness proportional coefficient k hi of non-isosteric stacked valve plates:

根据某汽车减振器非等构叠加阀片的当量厚度和片数h 1e=0.30mm，n 1=1；h 2e=0.19312mm，n 2=1，计算非等构叠加阀片的等效厚度h E为： According to the equivalent thickness and number of non-isostructural superimposed valve plates of an automobile shock absorber h 1e =0.30mm, n 1 =1; h 2e =0.19312mm, n 2 =1, calculate the equivalent non-isostructural superimposed valve plate The thickness h E is:

= 0.2224mm； = 0.2224mm;

       各非等构叠加阀片的厚度比例系数k hi 分别为； The thickness proportional coefficients k hi of each non-isomorphic superimposed valve plate are respectively;

Figure 799102DEST_PATH_IMAGE011
=0.899，= 0.649；
Figure 799102DEST_PATH_IMAGE011
=0.899, = 0.649;

（4）计算非等构叠加阀片在任意半径r的复合应力系数

Figure 971775DEST_PATH_IMAGE014
： (4) Calculating the composite stress coefficient of the non-isomorphic stacked valve plate at any radius r
Figure 971775DEST_PATH_IMAGE014
:

由于第1片非等构叠加阀片的结构、材料特性与实施例一的相同，因此，该汽车减振器非等构叠加阀片在任意半径r的复合应力系数

Figure 84962DEST_PATH_IMAGE014
，也与实施例一的相同，如图3所示； Since the structure and material properties of the first non-isomorphic superimposed valve plate are the same as those in Example 1, the composite stress coefficient of the non-isomorphic superimposed valve plate of the automobile shock absorber at any radius r
Figure 84962DEST_PATH_IMAGE014
, is also the same as that of Embodiment 1, as shown in Figure 3;

（5）汽车减振器各非等构叠加阀片复合应力

Figure 460580DEST_PATH_IMAGE038
的计算： (5) Composite stress of non-isostructural superimposed valve plates of automobile shock absorbers
Figure 460580DEST_PATH_IMAGE038
The calculation of:

根据叠加阀片所受压力p=2.5MPa，步骤（3）中的叠加阀片等效厚度h E= 0.2224mm和各非等构叠加阀片的厚度比例系数k h1=0.899，k h2=0.649，及步骤（4）中的的复合应力系数

Figure 84459DEST_PATH_IMAGE014
，对各非等构叠加阀片在任意半径r处的复合应力
Figure 291449DEST_PATH_IMAGE038
进行计算，即： According to the pressure p =2.5MPa on the stacked valve slices, the equivalent thickness h E of the stacked valve slices in step (3) = 0.2224mm and the thickness proportional coefficient k h 1 =0.899 of each non-isomorphic stacked valve slices, k h 2 =0.649, and the composite stress coefficient in step (4)
Figure 84459DEST_PATH_IMAGE014
, for the composite stress of each non-isosteric superimposed valve plate at any radius r
Figure 291449DEST_PATH_IMAGE038
Do the calculation, that is:

                                  

Figure 342582DEST_PATH_IMAGE040
，
Figure 342582DEST_PATH_IMAGE040
,

计算所得到的各非等构叠加阀片的复合应力

Figure 704031DEST_PATH_IMAGE038
曲线，如图8所示，其中，非等构叠加阀片在内圆半径处的最大复合应力分别为
Figure 866022DEST_PATH_IMAGE085
1926.5MPa，1390.7MPa。 Composite stress of each non-isosteric superimposed valve plate obtained by calculation
Figure 704031DEST_PATH_IMAGE038
curve, as shown in Figure 8, where the maximum composite stress at the inner radius of the non-isomorphic superimposed valve plate is respectively
Figure 866022DEST_PATH_IMAGE085
1926.5MPa, 1390.7MPa.

根据汽车减振器非等构叠加阀片的内圆半径r a＝5.0mm，弹性模型E＝200GPa，泊松比μ＝0.3，及各非等构叠加阀片的厚度、片数和外半径分别为h 1=0.20mm，n 1=1，r b1=8.5mm；h 2=0.15mm，n 2=1，r b2=7.0mm，利用ANSYS建立叠加阀片仿真模型，网格划分单位为0.1mm，在施加相同均布压力p＝2.5MPa情况下，仿真所得到的叠加阀片复合应力仿真云图，如图9所示。 According to the inner circle radius r a = 5.0mm of the non-isomorphic stacked valve plates of the automobile shock absorber, the elastic model E = 200GPa, Poisson’s ratio μ = 0.3, and the thickness, number and outer radius of each non-isomorphic stacked valve plate Respectively h 1 =0.20mm, n 1 =1, r b1 =8.5mm; h 2 =0.15mm, n 2 =1, r b2 =7.0mm, using ANSYS to establish a simulation model of superimposed valve slices, the grid division unit is 0.1mm, in the case of applying the same uniform pressure p = 2.5MPa, the simulated cloud diagram of the composite stress of the superimposed valve plate is shown in Figure 9.

由图9可知，在均布压力p＝2.5MPa下，该汽车减振器非等构叠加阀片最大复合应力的仿真值为1870MP，与利用该计算方法所得到的第1片叠加阀片的最大复合应力1926.5MPa相吻合，相对偏差仅为2.93%，表明本发明所建立的汽车减振器非等构叠加阀片复合应力的计算方法是可靠的。 It can be seen from Fig. 9 that under the uniform pressure p = 2.5MPa, the simulated value of the maximum composite stress of the non-isomorphic superimposed valve plate of the automobile shock absorber is 1870MP, which is different from the value of the first superimposed valve plate obtained by this calculation method. The maximum composite stress is 1926.5MPa, and the relative deviation is only 2.93%, which shows that the calculation method for the composite stress of the non-isomorphic stacked valve plate of the automobile shock absorber established by the present invention is reliable.

实施例四：某汽车减振器非等构叠加阀片的内圆半径r a＝5.0mm，弹性模量E=200GPa，泊松比μ＝0.3，叠加阀片的厚度、片数和外半径分别为h 1=0.25mm，n 1=1，r b1=10mm；h 2=0.20mm，n 2=2，r b2=8.5mm; h 3=0.15mm，n 2=3，r b2=7.0mm，非等构叠加阀片所受压力p=3.0MPa。 Embodiment 4: The radius of the inner circle of a non-isostructural superimposed valve plate of an automobile shock absorber r a = 5.0mm, the elastic modulus E = 200GPa, Poisson’s ratio μ = 0.3, the thickness, number and outer radius of the superimposed valve plate Respectively h 1 =0.25mm, n 1 =1, r b1 =10mm; h 2 =0.20mm, n 2 =2, r b2 =8.5mm; h 3 =0.15mm, n 2 =3, r b2 =7.0 mm, the pressure p =3.0MPa on non-isomorphic stacked valve slices.

按实施例一的步骤进行计算，即： Calculate according to the steps of Example 1, namely:

（1）确定各非等构叠加阀片的外半径不等率系数η i : (1) Determine the outer radius non-uniformity coefficient η i of each non-isomorphic stacked valve plate:

根据汽车减振器非等构叠加阀片的外半径r b1=10.0mm, r b2=8.5mm, r b3=7.0mm, 确定各叠加阀片的外半径不等率η i ,即 According to the outer radius r b1 =10.0mm, r b2 =8.5mm, r b3 =7.0mm of the non-isomorphic stacked valve slices of the automobile shock absorber, determine the non-uniformity ratio η i of the stacked valve slices, namely

                      η 1=0,   η 2=

Figure 415132DEST_PATH_IMAGE100
=0.3，  η 3==0.6； η 1 =0, η 2 =
Figure 415132DEST_PATH_IMAGE100
=0.3, η 3 = =0.6;

（2）计算各非等构叠加阀片的当量厚度h ie: (2) Calculate the equivalent thickness h i e of each non-isostructural superimposed valve plate:

根据汽车减振器各非等构叠加阀片的厚度h 1=0.25mm, h 2=0.20mm，h 3=0.15mm, 及步骤（1）中的外半径不等率η 1=0，η 2=0.3，η 3=0.6，分别计算各非等构叠加阀片的当量厚度h ie，即 According to the thickness h 1 =0.25mm, h 2 =0.20mm, h 3 =0.15mm of the non-isomorphic stacked valve plates of the automobile shock absorber, and the unequal ratio of the outer radius in step (1) η 1 =0, η 2 =0.3, η 3 =0.6, respectively calculate the equivalent thickness h i e of each non-isomorphic superimposed valve plate, namely

    h 1e=0.25mm，h 2e=

Figure 935981DEST_PATH_IMAGE004
Figure 901663DEST_PATH_IMAGE005
=0.19728mm，h 3e=
Figure 20929DEST_PATH_IMAGE006
Figure 413864DEST_PATH_IMAGE007
=0.13419； h 1e =0.25mm, h 2e =
Figure 935981DEST_PATH_IMAGE004
Figure 901663DEST_PATH_IMAGE005
=0.19728mm, h 3e =
Figure 20929DEST_PATH_IMAGE006
Figure 413864DEST_PATH_IMAGE007
=0.13419;

（3）计算非等构叠加阀片的等效厚度h E和厚度比例系数k hi (3) Calculating the equivalent thickness h E and thickness proportional coefficient k hi of the non-isosteric superimposed valve plate

根据某汽车减振器非等构叠加阀片的当量厚度和片数h 1e=0.25mm，n 1=1；h 2e=0.19728mm，n 2=2；h 3e=0.13419，n 3=3，计算非等构叠加阀片的等效厚度h E为： According to the equivalent thickness and number of non-isomorphic superimposed valve plates of an automobile shock absorber h 1e =0.25mm, n 1 =1; h 2e =0.19728mm, n 2 =2; h 3e =0.13419, n 3 =3, Calculate the equivalent thickness h E of the non-isosteric superimposed valve plate as:

=0.33688mm； =0.33688mm;

各非等构叠加阀片的厚度比例系数k hi 分别为； The thickness proportional coefficients k hi of each non-isomorphic superimposed valve plate are respectively;

=0.7421，=0.5856，

Figure 227471DEST_PATH_IMAGE065
=0.3983； =0.7421, =0.5856,
Figure 227471DEST_PATH_IMAGE065
=0.3983;

（4）计算非等构叠加阀片在任意半径r的复合应力系数

Figure 853624DEST_PATH_IMAGE014
： (4) Calculating the composite stress coefficient of the non-isomorphic stacked valve plate at any radius r
Figure 853624DEST_PATH_IMAGE014
:

根据第1片叠加阀片的内圆半径

Figure 912847DEST_PATH_IMAGE044
=5.0mm，外圆半径
Figure 718867DEST_PATH_IMAGE059
=8.5mm，弹性模量E=2.0和泊松比μ=0.3，计算非等构叠加阀片在任意半径r（r a ≤r≤r b1）的复合应力系数
Figure 609780DEST_PATH_IMAGE014
，即： According to the inner circle radius of the first superimposed valve plate
Figure 912847DEST_PATH_IMAGE044
=5.0mm, outer circle radius
Figure 718867DEST_PATH_IMAGE059
=8.5mm, elastic modulus E =2.0 and Poisson's ratio μ =0.3, calculate the composite stress coefficient of the non-isosteric stacked valve plate at any radius r ( r a ≤ r ≤ r b1 )
Figure 609780DEST_PATH_IMAGE014
,Right now:

Figure 156299DEST_PATH_IMAGE068
Figure 156299DEST_PATH_IMAGE068

式中，

Figure 1895DEST_PATH_IMAGE018
， In the formula,
Figure 1895DEST_PATH_IMAGE018
,

Figure 448795DEST_PATH_IMAGE019
；
Figure 448795DEST_PATH_IMAGE019
;

Figure DEST_PATH_IMAGE105
，
Figure DEST_PATH_IMAGE106
，
Figure DEST_PATH_IMAGE105
,
Figure DEST_PATH_IMAGE106
,

 , ,

Figure 229800DEST_PATH_IMAGE072
=；    
Figure 229800DEST_PATH_IMAGE072
= ;

=200，

Figure 411437DEST_PATH_IMAGE025
=
Figure 479887DEST_PATH_IMAGE075
，
Figure 556428DEST_PATH_IMAGE026
=0.01，
Figure 310495DEST_PATH_IMAGE027
=5.0
Figure 763473DEST_PATH_IMAGE077
，=，
Figure 933871DEST_PATH_IMAGE029
＝-8.6734，
Figure 739016DEST_PATH_IMAGE081
=2.6，=
Figure DEST_PATH_IMAGE112
； =200,
Figure 411437DEST_PATH_IMAGE025
=
Figure 479887DEST_PATH_IMAGE075
,
Figure 556428DEST_PATH_IMAGE026
=0.01,
Figure 310495DEST_PATH_IMAGE027
=5.0
Figure 763473DEST_PATH_IMAGE077
, = ,
Figure 933871DEST_PATH_IMAGE029
=-8.6734,
Figure 739016DEST_PATH_IMAGE081
=2.6, =
Figure DEST_PATH_IMAGE112
;

       计算得到的复合应力系数

Figure 943788DEST_PATH_IMAGE014
随半径r（r a ≤r≤r b1）的变化曲线，如图10所示，其中，在内圆半径r a处的最大复合应力系数
Figure 362131DEST_PATH_IMAGE032
=92.563mm2； The calculated composite stress factor
Figure 943788DEST_PATH_IMAGE014
Variation curve with radius r ( r a ≤ r ≤ r b1 ), as shown in Figure 10, where the maximum composite stress coefficient at the inner circle radius r a
Figure 362131DEST_PATH_IMAGE032
=92.563mm 2 ;

（5）汽车减振器各非等构叠加阀片复合应力

Figure DEST_PATH_IMAGE113
的计算： (5) Composite stress of non-isostructural superimposed valve plates of automobile shock absorbers
Figure DEST_PATH_IMAGE113
The calculation of:

根据叠加阀片所受的压力p=3.0MPa，步骤（3）中的叠加阀片的等效厚度h E=0.29059mm和厚度比例系数k h1＝0.7421，k h2＝0.5856，k h3＝0.3983，及步骤（4）中的复合应力系数

Figure 356369DEST_PATH_IMAGE014
，对各非等构叠加阀片在任意半径r处的复合应力进行计算，即： According to the pressure p =3.0MPa on the stacked valve plate, the equivalent thickness h E =0.29059mm and the thickness proportional coefficient k h 1 =0.7421, k h 2 =0.5856, k h 3 of the stacked valve plate in step (3) =0.3983, and the composite stress coefficient in step (4)
Figure 356369DEST_PATH_IMAGE014
, for the composite stress of each non-isosteric superimposed valve plate at any radius r Do the calculation, that is:

Figure DEST_PATH_IMAGE114
；
Figure DEST_PATH_IMAGE114
;

    计算所得到的各非等构叠加阀片的复合应力

Figure 720802DEST_PATH_IMAGE113
曲线，如图11所示，其中，各非等构叠加阀片的最大复合应力分别为
Figure 808582DEST_PATH_IMAGE085
1815.9MPa、1432.9MPa、974.72MPa。 Composite stress of each non-isosteric superimposed valve plate obtained by calculation
Figure 720802DEST_PATH_IMAGE113
Curves, as shown in Figure 11, where the maximum composite stress of each non-isostructural superimposed valve plate is
Figure 808582DEST_PATH_IMAGE085
1815.9MPa, 1432.9MPa, 974.72MPa.

根据汽车减振器非等构叠加阀片的内圆半径r a＝5.0mm，弹性模型E＝200GPa，泊松比μ＝0.3，及各非等构叠加阀片的厚度、片数和外半径分别为h 1=0.25mm，n 1=1，r b1=10mm；h 2=0.20mm，n 2=2，r b2=8.5mm; h 3=0.15mm，n 2=3，r b2=7.0mm，利用ANSYS建立叠加阀片仿真模型，网格划分单位为0.1mm，在施加相同均布压力p＝3.0MPa情况下，仿真所得到的叠加阀片复合应力仿真云图，如图12所示。 According to the inner circle radius r a = 5.0mm of the non-isomorphic stacked valve plates of the automobile shock absorber, the elastic model E = 200GPa, Poisson’s ratio μ = 0.3, and the thickness, number and outer radius of each non-isomorphic stacked valve plate Respectively h 1 =0.25mm, n 1 =1, r b1 =10mm; h 2 =0.20mm, n 2 =2, r b2 =8.5mm; h 3 =0.15mm, n 2 =3, r b2 =7.0 mm, using ANSYS to establish the simulation model of the superimposed valve plate, the grid division unit is 0.1mm, and under the same uniform pressure p = 3.0MPa, the simulation cloud diagram of the composite stress of the superimposed valve plate obtained by simulation is shown in Figure 12.

由图12可知，在均布压力p＝3.0MPa下，该汽车减振器非等构叠加阀片最大复合应力的仿真值为1800MP，与利用该计算方法所得到的第1片叠加阀片的最大复合应力1815.9MPa相吻合，相对偏差仅为0.88%，表明本发明所建立的汽车减振器非等构叠加阀片复合应力的计算方法是可靠的。 It can be seen from Figure 12 that under the uniform pressure p = 3.0MPa, the simulated value of the maximum composite stress of the non-isomorphic superimposed valve plate of the automobile shock absorber is 1800 MPa, which is different from the value of the first superimposed valve plate obtained by this calculation method. The maximum composite stress is 1815.9MPa, and the relative deviation is only 0.88%, which shows that the calculation method for the composite stress of the non-isomorphic superimposed valve plate of the automobile shock absorber established by the present invention is reliable.

Claims (1)

1. non-computing method that wait structure stack valve block compound stress of vehicle shock absorber, its concrete calculation procedure is as follows:
(1) determine each non-external radius diversity factor coefficient that waits structure stack valve block η i :
According to the non-external radius that waits structure stack valve block of vehicle shock absorber r b1, r b2..., r bn, wherein, r b1> r b2> ... > r bn, the external radius diversity factor of definite valve block that respectively superposes η i , that is:
Figure 2014100006050100001DEST_PATH_IMAGE001
,
Figure 2014100006050100001DEST_PATH_IMAGE002
,…,
Figure 2014100006050100001DEST_PATH_IMAGE003
；
(2) calculate each non-equivalent depth that waits structure stack valve block of vehicle shock absorber h ie :
According to each non-thickness that waits structure stack valve block of vehicle shock absorber h 1, h 2..., h n , and the external radius diversity factor in step (1) η i , calculate each non-equivalent depth that waits structure stack valve block h ie , that is:
h 1e= h 1， h 2e=
Figure 2014100006050100001DEST_PATH_IMAGE005
， h 3e=
Figure 2014100006050100001DEST_PATH_IMAGE006
Figure 2014100006050100001DEST_PATH_IMAGE007
,…, h ne =
Figure 2014100006050100001DEST_PATH_IMAGE008
；
(3) calculate the non-equivalent thickness that waits structure stack valve block h ewith thickness proportion coefficient k hi :
According to the non-sheet number that waits structure stack valve block n 1, n 2..., n n, and the equivalent depth of the valve block that respectively superposes in step (2) h ie , calculate the non-equivalent thickness that waits structure stack valve block of vehicle shock absorber h ethickness proportion coefficient with each stack valve block k hi , that is:
Figure 2014100006050100001DEST_PATH_IMAGE010
；
Figure 2014100006050100001DEST_PATH_IMAGE011
，
Figure 2014100006050100001DEST_PATH_IMAGE012
，…，
Figure 2014100006050100001DEST_PATH_IMAGE013
；
(4) the non-structure stack valve block meaning radius in office that waits of vehicle shock absorber rthe compound stress coefficient at place
Figure 2014100006050100001DEST_PATH_IMAGE014
calculate:
According to the 1st non-interior radius of circle that waits structure stack valve block r a, exradius r b1, elastic modulus eand Poisson ratio μ, calculate the non-structure stack valve block meaning radius in office that waits of vehicle shock absorber r( r a≤ r≤ r b1) the compound stress coefficient located
Figure 414257DEST_PATH_IMAGE014
, that is:
Figure 2014100006050100001DEST_PATH_IMAGE015
In formula,
Figure DEST_PATH_IMAGE016
,
Figure 2014100006050100001DEST_PATH_IMAGE017
;
Figure DEST_PATH_IMAGE018
，
Figure DEST_PATH_IMAGE019
；
Figure DEST_PATH_IMAGE020
,
Figure DEST_PATH_IMAGE021
,
Figure DEST_PATH_IMAGE022
,
Figure DEST_PATH_IMAGE023
，
Figure DEST_PATH_IMAGE024
， ，
Figure DEST_PATH_IMAGE026
，
Figure DEST_PATH_IMAGE027
，
Figure DEST_PATH_IMAGE028
，
Figure DEST_PATH_IMAGE029
， ，
Figure DEST_PATH_IMAGE031
；
Wherein, when r= r acompound stress coefficient
Figure 892250DEST_PATH_IMAGE014
, be the non-structure stack valve block that waits at interior radius of circle r athe maximum compound stress coefficient at place , that is:
Figure DEST_PATH_IMAGE033
In formula,
Figure DEST_PATH_IMAGE034
,
Figure DEST_PATH_IMAGE035
;
Figure DEST_PATH_IMAGE036
，
；
(5) each non-structure stack valve block compound stress that waits of vehicle shock absorber
Figure DEST_PATH_IMAGE038
calculating:
According to the non-suffered pressure of structure stack valve block that waits of vehicle shock absorber p, the equivalent thickness in step (3) h ewith thickness proportion coefficient
Figure DEST_PATH_IMAGE039
, and the compound stress coefficient in step (4)
Figure 108205DEST_PATH_IMAGE014
, to each non-structure stack valve block meaning radius in office that waits of vehicle shock absorber rthe compound stress amount at place
Figure 441097DEST_PATH_IMAGE038
calculate, that is:
Figure DEST_PATH_IMAGE040
；
Wherein, when
Figure 442420DEST_PATH_IMAGE014
for interior radius of circle r athe maximum compound stress coefficient at place
Figure 202566DEST_PATH_IMAGE032
,
Figure 469599DEST_PATH_IMAGE038
be non-stack valve block
Figure DEST_PATH_IMAGE041
maximum compound stress in inner circle radial position
Figure DEST_PATH_IMAGE042
.
CN201410000605.0A 2014-01-02 2014-01-02 The non-computational methods waiting structure superposition valve block combined stress of vehicle shock absorber Expired - Fee Related CN103678832B (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
CN201410000605.0A CN103678832B (en) 2014-01-02 2014-01-02 The non-computational methods waiting structure superposition valve block combined stress of vehicle shock absorber

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
CN201410000605.0A CN103678832B (en) 2014-01-02 2014-01-02 The non-computational methods waiting structure superposition valve block combined stress of vehicle shock absorber

Publications (2)

Publication Number Publication Date
CN103678832A true CN103678832A (en) 2014-03-26
CN103678832B CN103678832B (en) 2016-08-31

Family

ID=50316368

Family Applications (1)

Application Number Title Priority Date Filing Date
CN201410000605.0A Expired - Fee Related CN103678832B (en) 2014-01-02 2014-01-02 The non-computational methods waiting structure superposition valve block combined stress of vehicle shock absorber

Country Status (1)

Country Link
CN (1) CN103678832B (en)

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN105912785A (en) * 2016-04-14 2016-08-31 周长城 Method for calculating separate stresses of main and auxiliary springs of non-end contact and few-leaf diagonal type
CN109033708A (en) * 2018-08-29 2018-12-18 华南理工大学 A kind of Calculation of pressure loss method of series-parallel R formula vehicle shock absorber
CN109101748A (en) * 2018-08-29 2018-12-28 华南理工大学 A kind of Calculation of pressure loss method of parallel connection R formula vehicle shock absorber
CN109190240A (en) * 2018-08-29 2019-01-11 华南理工大学 A kind of and R formula vehicle shock absorber of connecting Calculation of pressure loss method

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5769192A (en) * 1993-05-10 1998-06-23 Fichtel & Sachs Ag Shock absorber having a piston permanently attached to its piston rod
CN103106312A (en) * 2013-03-08 2013-05-15 山东理工大学 Calculation method for vibration absorber isodesmic annular superposed valve plate deformation
CN103106349A (en) * 2013-03-08 2013-05-15 山东理工大学 Method for calculating radial stress of annular valve plate of vibration absorber
CN103150434A (en) * 2013-03-08 2013-06-12 山东理工大学 Method for calculating combined stress of annular valve sheet of shock absorber
CN103324824A (en) * 2013-03-08 2013-09-25 山东理工大学 Computing method for equivalent thickness of hydraulic buffer isomorphic annular sandwich valve plates

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5769192A (en) * 1993-05-10 1998-06-23 Fichtel & Sachs Ag Shock absorber having a piston permanently attached to its piston rod
CN103106312A (en) * 2013-03-08 2013-05-15 山东理工大学 Calculation method for vibration absorber isodesmic annular superposed valve plate deformation
CN103106349A (en) * 2013-03-08 2013-05-15 山东理工大学 Method for calculating radial stress of annular valve plate of vibration absorber
CN103150434A (en) * 2013-03-08 2013-06-12 山东理工大学 Method for calculating combined stress of annular valve sheet of shock absorber
CN103324824A (en) * 2013-03-08 2013-09-25 山东理工大学 Computing method for equivalent thickness of hydraulic buffer isomorphic annular sandwich valve plates

Cited By (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN105912785A (en) * 2016-04-14 2016-08-31 周长城 Method for calculating separate stresses of main and auxiliary springs of non-end contact and few-leaf diagonal type
CN109033708A (en) * 2018-08-29 2018-12-18 华南理工大学 A kind of Calculation of pressure loss method of series-parallel R formula vehicle shock absorber
CN109101748A (en) * 2018-08-29 2018-12-28 华南理工大学 A kind of Calculation of pressure loss method of parallel connection R formula vehicle shock absorber
CN109190240A (en) * 2018-08-29 2019-01-11 华南理工大学 A kind of and R formula vehicle shock absorber of connecting Calculation of pressure loss method
CN109101748B (en) * 2018-08-29 2022-12-16 华南理工大学 A Calculation Method for Pressure Loss of Parallel R-Type Automobile Shock Absorber
CN109033708B (en) * 2018-08-29 2022-12-16 华南理工大学 Pressure loss calculation method for series-parallel R type automobile shock absorber
CN109190240B (en) * 2018-08-29 2022-12-16 华南理工大学 Pressure loss calculation method for parallel-series R-type automobile shock absorber

Also Published As

Publication number Publication date
CN103678832B (en) 2016-08-31

Similar Documents

Publication Publication Date Title
CN103678832A (en) Method for calculating composite stress of non-equal structure superposed valve plates of vehicle shock absorber
CN103106312A (en) Calculation method for vibration absorber isodesmic annular superposed valve plate deformation
CN103294919B (en) Vibration damper circular sandwich valve plate determines the method for radial stress under non-uniform distributed pressure
CN103150434A (en) Method for calculating combined stress of annular valve sheet of shock absorber
CN103116683A (en) Superposition computing method for deformation of absorber annular valve sheet under unevenly distributed pressure
CN103116709A (en) Computing method for circumferential stress of absorber annular valve sheet
CN105138806B (en) The strength check methods of hydro-pneumatic spring not uniform thickness annular valve block
CN103678833B (en) The non-computational methods waiting structure superposition valve block radial stress of vehicle shock absorber
CN103106349A (en) Method for calculating radial stress of annular valve plate of vibration absorber
CN103324824A (en) Computing method for equivalent thickness of hydraulic buffer isomorphic annular sandwich valve plates
CN103246791B (en) The computing method of vibration damper circular sandwich valve plate circumferential stress under non-uniform distributed pressure
CN103148148A (en) Method for checking strength of rebound sandwich valve sheet of shock absorber
CN202218127U (en) Motor rotor balance plate
CN103177158A (en) Computing method for circumferential stress of equivalent structure circular sandwich valve plate of absorber
CN103149025A (en) Additional displacement test bench of shaft coupler
CN103678944B (en) The non-intensity check method waiting structure superposition valve block of hydraulic snubber
CN202039103U (en) Superharmonic resonance type vibration aging device for workpieces with high natural frequency
CN103678946B (en) The non-computational methods waiting structure superposition valve block circumferential stress of vehicle shock absorber
CN205056762U (en) Outer tubular construction of stainless steel thermos cup spinning
CN103150478B (en) The computing method of absorber annular valve sheet circumferential stress under non-uniform distributed pressure
CN103678945B (en) The non-defining method waiting the distortion of structure superposition valve block of a kind of vehicle vibration damping device
CN105279319B (en) The computational methods of hydro-pneumatic spring not uniform thickness annular valve block Maximum circumferential stress
CN103617334B (en) Strength check methods under vibroshock valve block meaning in office non-uniform distributed pressure
CN102737136B (en) Finite element design method for rigidity and strength of plastic granulating template
CN103150479B (en) The computing method of absorber annular valve sheet radial stress under non-uniform distributed pressure

Legal Events

Date Code Title Description
PB01 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: 20160831

Termination date: 20200102

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