CN106907416A - The gradual change gap design method of the offset frequency type progressive rate leaf spring such as two-stage auxiliary spring formula is non- - Google Patents
The gradual change gap design method of the offset frequency type progressive rate leaf spring such as two-stage auxiliary spring formula is non- Download PDFInfo
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- CN106907416A CN106907416A CN201710022125.8A CN201710022125A CN106907416A CN 106907416 A CN106907416 A CN 106907416A CN 201710022125 A CN201710022125 A CN 201710022125A CN 106907416 A CN106907416 A CN 106907416A
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
- F16F3/00—Spring units consisting of several springs, e.g. for obtaining a desired spring characteristic
- F16F3/02—Spring units consisting of several springs, e.g. for obtaining a desired spring characteristic with springs made of steel or of other material having low internal friction
- F16F3/023—Spring units consisting of several springs, e.g. for obtaining a desired spring characteristic with springs made of steel or of other material having low internal friction composed only of leaf springs
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
- F16F1/00—Springs
- F16F1/02—Springs made of steel or other material having low internal friction; Wound, torsion, leaf, cup, ring or the like springs, the material of the spring not being relevant
- F16F1/18—Leaf springs
- F16F1/185—Leaf springs characterised by shape or design of individual leaves
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
- F16F1/00—Springs
- F16F1/02—Springs made of steel or other material having low internal friction; Wound, torsion, leaf, cup, ring or the like springs, the material of the spring not being relevant
- F16F1/18—Leaf springs
- F16F1/26—Attachments or mountings
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- G—PHYSICS
- G06—COMPUTING; CALCULATING OR COUNTING
- G06F—ELECTRIC DIGITAL DATA PROCESSING
- G06F30/00—Computer-aided design [CAD]
- G06F30/10—Geometric CAD
- G06F30/15—Vehicle, aircraft or watercraft design
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- G06F—ELECTRIC DIGITAL DATA PROCESSING
- G06F30/00—Computer-aided design [CAD]
- G06F30/10—Geometric CAD
- G06F30/17—Mechanical parametric or variational design
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
- F16F2238/00—Type of springs or dampers
- F16F2238/02—Springs
- F16F2238/022—Springs leaf-like, e.g. of thin, planar-like metal
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- G—PHYSICS
- G06—COMPUTING; CALCULATING OR COUNTING
- G06F—ELECTRIC DIGITAL DATA PROCESSING
- G06F2119/00—Details relating to the type or aim of the analysis or the optimisation
- G06F2119/06—Power analysis or power optimisation
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Abstract
The present invention relates to the gradual change gap design method of the offset frequency type progressive rate leaf spring such as two-stage auxiliary spring formula is non-, belong to suspension leaf spring technical field.The present invention can be clamped away from, each contact load according to the structural parameters of each main spring and auxiliary spring, elastic modelling quantity, U-bolts and is left cotangent bank high request value in rated load, the two-stage gradual change gap of the offset frequency type progressive rate leaf spring such as non-to two-stage auxiliary spring formulaδ MA1Withδ A12It is designed.By model machine load deflection result of the test, the gradual change gap design method of the offset frequency type progressive rate leaf spring such as two-stage auxiliary spring formula provided by the present invention is non-is correct, is that reliable technical foundation has been established in the design and CAD software exploitation of the offset frequency type progressive rate leaf springs such as two-stage auxiliary spring formula is non-.Using the available accurately and reliably two-stage gradual change gap design load of the method, the design level and vehicle ride performance and security of product are improved;Meanwhile, design and testing expenses can be also reduced, accelerate product development speed.
Description
Technical field
The present invention relates to the offset frequency type progressive rate leaf spring such as vehicle suspension leaf spring, particularly two-stage auxiliary spring formula be non-gradually
Varied clearance design method.
Background technology
In order to improve the design requirement of ride performance of the vehicle under rated load, by former first-order gradient rigidity leaf spring
Auxiliary spring splits and is designed as two-stage auxiliary spring, i.e., using two-stage auxiliary spring formula progressive rate leaf spring;Simultaneously as the system of acceptor's spring intensity
About, generally by main spring initial tangential camber, first order auxiliary spring and second level auxiliary spring initial tangential camber, main spring and first order pair
Two-stage gradual change gap between spring and between the first auxiliary spring and second level auxiliary spring, makes auxiliary spring suitably undertake load in advance, so as to drop
Low main spring stress, the suspension offset frequency under contact load is unequal, i.e., the offset frequency type progressive rate leaf spring such as two-stage auxiliary spring formula is non-, its
In, two-stage gradual change gap determined by the initial tangential camber of main spring and auxiliary spring at different levels, and influence leaf spring contact load,
Progressive rate and maximum stress, suspension offset frequency and vehicle ride performance and security.However, because the non-grade of two-stage auxiliary spring formula is inclined
Amount of deflection of the frequency type progressive rate leaf spring in progressive formation is extremely complex, and by the design of initial tangential camber and leaf spring curved
The restriction that shape and at an arbitrary position curved surface camber are calculated, understands according to consulting reference materials, and previously fails to provide two-stage auxiliary spring formula non-always
Etc. the gradual change gap design method of offset frequency type progressive rate leaf spring, it is thus impossible to meet Vehicle Industry fast development and bearing spring
Suspension modernizes the requirement of CAD design and software development.With Vehicle Speed and its continuous improvement to ride comfort requirement,
Requirements at the higher level are proposed to progressive rate plate spring suspension brackets, therefore, it is necessary to it is non-etc. partially to set up a kind of accurate, reliable two-stage auxiliary spring formula
The gradual change gap design method of frequency type progressive rate leaf spring, is the offset frequency type progressive rate leaf springs such as two-stage auxiliary spring formula is non-design and modern
Change CAD software exploitation and establish reliable technical foundation, meet Vehicle Industry fast-developing, vehicle ride performance and firm to gradual change
The design requirement of leaf spring is spent, design level, product quality and the property of the offset frequency type progressive rate leaf springs such as two-stage auxiliary spring formula is non-is improved
Energy and vehicle ride performance and security;Meanwhile, design and testing expenses are reduced, accelerate product development speed.
The content of the invention
For defect present in above-mentioned prior art, the technical problems to be solved by the invention be to provide it is a kind of easy,
The gradual change gap design method of the offset frequency type progressive rate leaf spring such as reliable two-stage auxiliary spring formula is non-, design cycle is as shown in Figure 1.Two-stage
The half symmetrical structure of the offset frequency type progressive rate leaf spring such as auxiliary spring formula is non-is as shown in Fig. 2 be by main spring 1, first order auxiliary spring 2 and
Two grades of auxiliary springs 3 are constituted.Using two-stage auxiliary spring, two are provided between main spring and first order auxiliary spring and first order auxiliary spring and second level auxiliary spring
Level gradual change gap deltaMA1And δA12, to improve the vehicle ride performance under rated load;In order to ensure meeting main spring stress intensity
Design requirement, first order auxiliary spring and second level auxiliary spring suitably undertake load in advance, and suspension gradual change load offset frequency is unequal, i.e., non-etc.
Offset frequency type progressive rate leaf spring.The half total span of leaf spring is equal to the first half action length L of main spring1T, U-bolts clamping
Away from half be L0, width is b, and elastic modelling quantity is E.The piece number of main spring 1 is n, and the i-th main spring thickness of main spring is hi, half work
It is L with lengthiT, half clamping length Li=LiT-L0/ 2, i=1,2 ..., n.First order auxiliary spring piece number is m1, jth piece one-level pair
The thickness of spring is hA1j=hn+j, half action length is LA1jT, half clamping length LA1j=LA1jT-L0/ 2, j=1,2 ..., m1。
The piece number sum N of main spring and first order auxiliary spring1=n+m1.Second level auxiliary spring piece number is m2, wherein, the thickness of kth piece auxiliary spring is
hA2k=hN1+k, half action length is LA2kT, half clamping length LA2k=LA2kT-L0/ 2, k=1,2 ..., m2.Major-minor spring it is total
Piece number N=n+m1+m2.By main spring and the initial tangential camber of first order auxiliary spring and second level auxiliary spring, it is ensured that meet two-stage gradual change
Gap gap δMA1And δA12, and start contact load P the 1st timek1, start contact load P the 2nd timek2, completely attach to load the 2nd time
Pw2, progressive rate KkwP1And KkwP2Design requirement.Structural parameters, elastic modelling quantity according to each main spring and auxiliary spring, spiral shell of riding
Bolt clamp away from, each contact load, rated load and be left cotangent bank high request value in rated load, it is non-to two-stage auxiliary spring formula
Etc. the two-stage gradual change gap delta of offset frequency type progressive rate leaf springMA1And δA12It is designed.
In order to solve the above technical problems, the offset frequency type progressive rate leaf spring such as two-stage auxiliary spring formula provided by the present invention is non-is gradually
Varied clearance design method, it is characterised in that use following design procedure:
(1) the two-stage gradual change of the offset frequency type progressive rate leaf spring such as two-stage auxiliary spring formula is non-clamps stiffness KkwP1And KkwP2Calculating:
Step A:First order gradual change clamps stiffness KkwP1Calculating
Start contact load P according to the 1st timek1, the 2nd beginning contact load Pk2, main spring clamping stiffness KM, main spring and first
The compound clamping stiffness K of level auxiliary springMA1, to load p in [Pk1,Pk1] scope when first order gradual change clamp stiffness KkwP1Counted
Calculate, i.e.,
Step B:Second level gradual change clamps stiffness KkwP2Calculating
Start contact load P according to the 2nd timek2, the 2nd full contact load pw2, the compound folder of main spring and first order auxiliary spring
Tight stiffness KMA1, the total compound clamping stiffness K of major-minor springMA2, to load p in [Pk2,Pw2] in the range of when second level gradual change clamp
Stiffness KkwP2Calculated, i.e.,
(2) the main spring initial tangential camber H of the offset frequency type progressive rate leaf spring such as two-stage auxiliary spring formula is non-gM0Design:
Start contact load P according to the 1st timek1, the 2nd beginning contact load Pk2, the 2nd full contact load pw2, it is specified
Load pN, main spring clamping stiffness KM, the total compound clamping stiffness K of major-minor springMA, in rated load PNUnder remaining tangent line camber
HgMN, and the K being calculated in step (1)kwP1And KkwP2, at the beginning of the main spring of offset frequency type progressive rate leaf spring such as non-to two-stage auxiliary spring formula
Beginning tangent line camber HgM0It is designed, i.e.,
(3) first order auxiliary spring initial tangential camber H of the offset frequency type progressive rate leaf spring such as two-stage auxiliary spring formula is non-gA10Set
Meter:
I steps:Main spring tailpiece lower surface radius of curvature RM0bCalculating
According to main reed number n, each thickness h of main springi, i=1,2 ..., n;The first half clamping length L of main spring1, step
Suddenly the H that design is obtained in (2)gM0, to main spring tailpiece lower surface radius of curvature RM0bCalculated, i.e.,
Ii steps:First upper surface radius of curvature R of first order auxiliary springA10aCalculate
According to the width b of the offset frequency type progressive rate leaf spring such as two-stage auxiliary spring formula is non-, elastic modulus E;Main reed number n, each
The thickness h of main springi, i=1,2 ..., n;The half clamping length L of first of main spring1, the 1st beginning contact load Pk1, and i steps
In the R that is calculatedM0b, to first upper surface radius of curvature R of first order auxiliary springA10aCalculated, i.e.,
In formula, hMeIt is the equivalent thickness of main spring root lap,
Iii steps:First order auxiliary spring initial tangential camber HgA10Design
According to the first order auxiliary spring half clamping length L of firstA11, the R that ii step values are calculatedA0a, to first order pair
Spring initial tangential camber HgA10It is designed, i.e.,
(4) second level auxiliary spring initial tangential camber H of the offset frequency type progressive rate leaf spring such as two-stage auxiliary spring formula is non-gA20Set
Meter:
A steps:First order auxiliary spring tailpiece lower surface radius of curvature RA10Calculating
According to first order auxiliary spring piece number m1, the thickness h that first order auxiliary spring is eachA1j, j=1,2 ..., m1;Calculated in ii steps
The R for obtainingA0a, to the main spring tailpiece lower surface radius of curvature R of the first orderA10bCalculated, i.e.,
B step:R on first upper table curvature radius of second level auxiliary springA20aCalculating
According to the width b of the offset frequency type progressive rate leaf spring such as two-stage auxiliary spring formula is non-, elastic modulus E;Main reed number n, each
The thickness h of main springi, i=1,2 ..., n, the half clamping length L of first of main spring1;First order auxiliary spring piece number m1, first order auxiliary spring
The thickness h of eachA1j, j=1,2 ..., m1;Start contact load P 1st timek1, the 2nd beginning contact load Pk2, and in a steps
The R being calculatedA10b, to first radius of curvature R of upper surface of second level auxiliary springA20aCalculated, i.e.,
In formula, hMA1eIt is the root lap equivalent thickness of main spring and first order auxiliary spring,
Step c:Second level auxiliary spring initial tangential camber HgA20Design
According to the second level auxiliary spring half clamping length L of firstA21, the R that b step value is calculatedA20a, to second level pair
The tangent line camber H of springgA20It is designed, i.e.,
(5) first order gradual change gap delta of the offset frequency type progressive rate leaf spring such as two-stage auxiliary spring formula is non-MA1Design:
I steps:The first main equivalent end points power F of spring based on main spring tangent line camberM1eCalculating
According to the width b of the offset frequency type progressive rate leaf spring such as two-stage auxiliary spring formula is non-, elastic modulus E;The first thickness of main spring
h1, half clamping length L1, the H that design is obtained in step (2)gM0, to the first main equivalent end points of spring based on main spring tangent line camber
Power FM1eCalculated, i.e.,
II steps:Curved surface high H of the main spring tailpiece at the correspondence first order first endpoint location of auxiliary springM1-A1endCalculate
According to the width b of the offset frequency type progressive rate leaf spring such as two-stage auxiliary spring formula is non-, elastic modulus E=200Gpa;Main spring is first
The thickness h of piece1, half clamping length L1;The half clamping length L of first of first order auxiliary springA11, and be calculated in I steps
FM1e, to curved surface height H of the main spring tailpiece at the correspondence first order first endpoint location of auxiliary springM1-A1endCalculated, i.e.,
In formula,It is deformation coefficient of the main spring at the correspondence first order first endpoint location of auxiliary spring,
III steps:The first order gradual change gap delta of the offset frequency type progressive rate leaf spring such as two-stage auxiliary spring formula is non-MA1Design
The H for obtaining is designed in iii steps according to step (3)gA10, the H that II steps are calculatedM1-M2end, to two-stage pair
The first order gradual change gap delta of the offset frequency type progressive rate leaf spring such as spring formula is non-MA1It is designed, i.e.,
δMA1=HM1-A1end-HgA10;
(6) second level gradual change gap delta of the offset frequency type progressive rate leaf spring such as two-stage auxiliary spring formula is non-A12Design:
1. step:The equivalent end points power F of first of first order auxiliary spring based on initial tangential camberA1eCalculate
According to the width b of the offset frequency type progressive rate leaf spring such as two-stage auxiliary spring formula is non-, elastic modulus E;First of first order auxiliary spring
Thickness hA11, the half clamping length L of first of first order auxiliary springA11, the H for obtaining is designed in the iii steps of step (3)gA10, it is right
The equivalent end points power F of first of first order auxiliary spring based on initial tangential camberA1eCalculated, i.e.,
2. step:Curved surface height H of the first order auxiliary spring tailpiece at correspondence first endpoint location of second level auxiliary springA1-A2endMeter
Calculate
According to the width b of the offset frequency type progressive rate leaf spring such as two-stage auxiliary spring formula is non-, elastic modulus E;First of first order auxiliary spring
Thickness hA11, the half clamping length L of first of first order auxiliary springA11;The half clamping length L of first of second level auxiliary springA21, and
1. the F being calculated in stepA1e, it is high to curved surface of the first order auxiliary spring tailpiece at correspondence first endpoint location of second level auxiliary spring
Degree HA1-A2endCalculated, i.e.,
In formula,It is deformation coefficient of the first order auxiliary spring at correspondence first endpoint location of second level auxiliary spring, i.e.,
3. step:Second level gradual change gap deltaA12Design
According to the H being calculated in 2. stepA1-A2end, the H for obtaining is designed in the step c of step (4)gA20, to two-stage pair
The second level gradual change gap delta of the offset frequency type progressive rate leaf spring such as spring formula is non-A12It is designed, i.e.,
δA12=HA1-A2end-HgA20。
The present invention has the advantage that than prior art
Because two-stage auxiliary spring formula is non-etc., amount of deflection of the offset frequency type progressive rate leaf spring in progressive formation is extremely complex, and receives
Initial tangential camber is designed and leaf spring curve form and the restriction of curved surface camber calculating at an arbitrary position, is understood according to consulting reference materials,
Previously fail to provide the gradual change gap design method of the offset frequency type progressive rate leaf springs such as two-stage auxiliary spring formula is non-always, it is thus impossible to full
Fast-developing and bearing spring suspension modernization CAD design and software development the requirement of sufficient Vehicle Industry.The present invention can be according to each
The structural parameters of the main spring of piece and auxiliary spring, elastic modelling quantity, U-bolts are clamped away from, each contact load, in clamping rigidity at different levels and
Progressive rate calculating and the design of initially handing over camber and leaf spring curve form meter and the basis that curved surface camber is calculated at an arbitrary position
On, the two-stage gradual change gap delta of the offset frequency type progressive rate leaf spring such as non-to two-stage auxiliary spring formulaMAAnd δA12It is designed.By model machine plus
Carry flexure test result to understand, the gradual change gap of the offset frequency type progressive rate leaf spring such as two-stage auxiliary spring formula provided by the present invention is non-sets
Meter method is correct, is that the design of initial tangential camber and CAD software of the offset frequency type progressive rate leaf springs such as two-stage auxiliary spring formula is non-are opened
Hair has established reliable technical foundation.Using the available accurately and reliably two-stage gradual change gap delta of the methodMAAnd δA12Design load,
Ensure to meet the design requirement of contact load, progressive rate and suspension offset frequency and vehicle ride performance, so as to further improve
The design level of the offset frequency type progressive rate leaf spring such as two-stage auxiliary spring formula is non-, quality and performance and vehicle ride performance and safety
Property;Meanwhile, design and experimental test expense can be also reduced, accelerate product development speed.
Brief description of the drawings
For a better understanding of the present invention, it is described further below in conjunction with the accompanying drawings.
Fig. 1 is the gradual change gap design flow diagram of the offset frequency type progressive rate leaf springs such as two-stage auxiliary spring formula is non-;
Fig. 2 is the half symmetrical structure schematic diagram of the offset frequency type progressive rate leaf springs such as two-stage auxiliary spring formula is non-;
Fig. 3 is the clamping stiffness K of the offset frequency type progressive rate leaf spring such as two-stage auxiliary spring formula is non-of embodiment one with the change of load p
Change curve.
Specific embodiment
The present invention is described in further detail below by embodiment.
Embodiment:The width b=63mm of the offset frequency type progressive rate leaf spring such as certain two-stage auxiliary spring formula is non-, U-bolts clamp away from
Half L0=50mm, elastic modulus E=200GPa, allowable stress [σ]=430MPa.Main reed number n=3 pieces, each main spring
Thickness h1=h2=h3=8mm, half action length is respectively L1T=525mm, L2T=450mm, L3T=350mm;Each master
The half clamping length of spring is respectively L1=L1T-L0/ 2=500mm, L2=L2T-L0/ 2=425mm, L3=L3T-L0/ 2=
325mm.First order auxiliary spring piece number m1=1, thickness hA11=13mm, half action length is LA11T=250mm, half clamps length
It is L to spendA11=LA11T-L0/ 2=225mm.Second level auxiliary spring piece number m2=1, thickness hA21=13mm, half action length is LA21T
=150mm, half clamping length is LA12=LA21T-L0/ 2=125mm.The total tablet number of major-minor spring is N=5.Main spring clamps rigidity
KMThe compound clamping stiffness K of=75.4N/mm, main spring and first order auxiliary springMA1=144.5N/mm, the total compound of major-minor spring is clamped
Stiffness KMA2=172.9N/mm.First order gradual change gap between first upper surface of first order auxiliary spring and main spring tailpiece lower surface is
δMA1And the second level gradual change gap between first upper surface of second level auxiliary spring and first order auxiliary spring tailpiece lower surface is δA12To treat
Design parameter.Start contact load P 1st timek1=1888N, the 2nd beginning contact load Pk2=2641N, the 2nd full contact
Load pw2=3694N, rated load PN=7227N, the remaining tangent line camber required value H under rated loadgMN=26.1mm.
Each main spring and the first order and the structural parameters of second level auxiliary spring according to the leaf spring with gradually changing stiffness, elastic modelling quantity, contact
Load, rated load and the remaining tangent line camber required value under rated load, the offset frequency type gradual change such as non-to the two-stage auxiliary spring formula
The two-stage gradual change gap delta of rigidity leaf springMA1And δA12Design design.
The gradual change gap design method of the offset frequency type progressive rate leaf spring such as two-stage auxiliary spring formula that present example is provided is non-, its
Design cycle is as shown in figure 1, specific design step is as follows:
(1) the two-stage gradual change of the offset frequency type progressive rate leaf spring such as two-stage auxiliary spring formula is non-clamps stiffness KkwP1And KkwP2Calculating:
Step A:First order gradual change clamps stiffness Kkwp1Calculating
Start contact load P according to the 1st timek1=1888N, the 2nd beginning contact load Pk2=2641N, main spring clamps firm
Degree KMThe compound clamping stiffness K of=75.4N/mm, main spring and first order auxiliary springMA1=144.5N/mm, to load p in [Pk1,Pk1]
The first order gradual change of the offset frequency type progressive rate leaf spring such as two-stage auxiliary spring formula during scope is non-clamps stiffness KkwP1Calculated, i.e.,
Step B:Second level gradual change clamps stiffness KkwP2Calculating
Start contact load P according to the 2nd timek2=2641N, the 2nd full contact load pw2=3694N, main spring and first
The compound clamping stiffness K of level auxiliary springMA1=144.5N/mm, the total compound of major-minor spring clamps stiffness KMA2=172.9N/mm, to carrying
Lotus P is in [Pk2,Pw2] in the range of when the second level gradual change of the offset frequency type progressive rate leaf spring such as two-stage auxiliary spring formula is non-clamp rigidity
KkwP2Calculated, i.e.,
Using Matlab calculation procedures, the clamping of the offset frequency type progressive rate leaf spring such as the two-stage auxiliary spring formula that is calculated is non-
Stiffness K with load p change curve, as shown in figure 3, wherein, working as load p<Pk1During=1888N, stiffness K=K is clampedM=
75.4N/mm, as load p=Pk2During=2641N, stiffness K=K is clampedMA1=144.5N/mm, works as load p>Pw2During=3694N,
Clamp stiffness K=KMA2=172.9N/mm.
(2) the main spring initial tangential camber H of the offset frequency type progressive rate leaf spring such as two-stage auxiliary spring formula is non-gM0Design:
Start contact load P according to the 1st timek1=1888N, the 2nd beginning contact load Pk2=2641N, the 2nd time completely
Contact load Pw2=3694N, rated load PN=7227N, in rated load PNUnder remaining camber design requirement value be HgMN
=26.1mm, main spring clamps stiffness KM=75.4N/mm;The total compound of major-minor spring clamps stiffness KMA=172.9N/mm, step (1)
Step A in the K that is calculatedkwP1, the K being calculated in step BkwP2, the offset frequency type progressive rate such as non-to the two-stage auxiliary spring formula
The main spring initial tangential camber H of leaf springgM0It is designed, i.e.,
(3) first order auxiliary spring initial tangential camber H of the offset frequency type progressive rate leaf spring such as two-stage auxiliary spring formula is non-gA10Set
Meter:
I steps:Main spring tailpiece lower surface initial curvature radius RM0bCalculating
According to main reed number n=3, each thickness h of main springi=8mm, i=1,2 ..., n;The half of first of main spring is clamped
Length L1The H that design is obtained in=500mm, step (2)gM0=85.3mm, to main spring tailpiece lower surface initial curvature radius RM0b
Calculated, i.e.,
Ii steps:First radius of curvature R of upper surface of first order auxiliary springA10aCalculate
According to the width b=63mm of the offset frequency type progressive rate leaf spring such as two-stage auxiliary spring formula is non-, elastic modulus E=200GPa;
Main reed number n=3, each thickness h of main springi=8mm, i=1,2 ..., n, the half clamping length L of first of main spring1=
500mm;Start contact load P 1st timek1The R being calculated in=1888N, and i stepsM0b=1531.9mm, to first order pair
First radius of curvature R of upper surface of springA10aCalculated, i.e.,
In formula, hMeIt is the equivalent thickness of main spring root lap,
Iii steps:First order auxiliary spring initial tangential camber HgA10Design
According to the first order auxiliary spring half clamping length L of firstA11The R that=225mm, ii step value are calculatedA0a=
2776.7mm, to first order auxiliary spring initial tangential camber HgA10It is designed, i.e.,
(4) second level auxiliary spring initial tangential camber H of the offset frequency type progressive rate leaf spring such as two-stage auxiliary spring formula is non-gA20Design
A steps:First order auxiliary spring tailpiece lower surface initial curvature radius RA10Calculating
Piece number m according to first order auxiliary spring1=1, thickness hA11The R being calculated in=13mm, ii stepA0a=
2776.7mm, spring tailpiece lower surface initial curvature radius R main to the first orderA10bCalculated, i.e.,
B step:R on first upper surface initial curvature radius of second level auxiliary springA20aCalculating
According to the width b=63mm of the offset frequency type progressive rate leaf spring such as two-stage auxiliary spring formula is non-, elastic modulus E=200GPa;
Main reed number n=3, each thickness h of main springi=8mm, i=1,2 ..., n, the 1st half clamping length L of main spring1=
500mm;The piece number m of first order auxiliary spring1=1, thickness hA11=13mm;Start contact load P 1st timek1=1888N, opens for the 2nd time
Beginning contact load Pk2=2641N, the h being calculated in the I steps of step (1)MA1eIt is calculated in=15.5mm, and a steps
RA10b=2789.7mm, to first of second level auxiliary spring upper surface initial curvature radius RA20aCalculated, i.e.,
In formula, hMA1eIt is the equivalent thickness of main spring and the root lap of first order auxiliary spring,
Step c:Second level auxiliary spring initial tangential camber HgA20Design
According to the second level auxiliary spring half clamping length L of firstA21=125mm, the R that b step value is calculatedA20a=
3221.3mm, to second level auxiliary spring initial tangential camber HgA20It is designed, i.e.,
(5) first order gradual change gap delta of the offset frequency type progressive rate leaf spring such as two-stage auxiliary spring formula is non-MA1Design:
I steps:The first main equivalent end points power F of spring based on main spring tangent line camberM1eCalculate
According to the width b=63mm of the offset frequency type progressive rate leaf spring such as two-stage auxiliary spring formula is non-, elastic modulus E=200Gpa;
The first thickness h of main spring1=8mm, half clamping length L1The H that design is obtained in=500mm, step (2)gM0=85.3mm is right
The first main equivalent end points power F of spring based on main spring tangent line camberM1eCalculated, i.e.,
II steps:Curved surface high H of the main spring tailpiece at the correspondence first order first endpoint location of auxiliary springM1-A1endCalculate
According to the width b=63mm of the offset frequency type progressive rate leaf spring such as two-stage auxiliary spring formula is non-, elastic modulus E=200Gpa;
The thickness h of first of main spring1=8mm, half clamping length L1=500mm;The half clamping length L of first of first order auxiliary springA11=
The F being calculated in 225mm, and I stepsM1e=1100N, to main spring tailpiece at correspondence one-level first endpoint location of auxiliary spring
Curved surface height HM1-A1endCalculated, i.e.,
In formula,It is the first deformation coefficient at the correspondence first order first endpoint location of auxiliary spring of main spring,
III steps:First order gradual change gap deltaMA1Design
The H for obtaining is designed in III steps according to step (3)gA10The H that=9.1mm, II step are calculatedM1-M2end=
22mm, the first order gradual change gap delta of the offset frequency type progressive rate leaf spring such as non-to two-stage auxiliary spring formulaMA1It is designed, i.e.,
δMA1=HM1-A1end-HgA10=12.9mm.
(6) second level gradual change gap delta of the offset frequency type progressive rate leaf spring such as two-stage auxiliary spring formula is non-A12Design:
1. step:The equivalent end points power F of first of first order auxiliary spring based on initial tangential camberA1eCalculate
According to the width b=63mm of the offset frequency type progressive rate leaf spring such as two-stage auxiliary spring formula is non-, elastic modulus E=200Gpa;
The thickness h that first order auxiliary spring is firstA11=13mm, half clamping length LA11=225mm, is designed in the iii steps of step (3)
The H for arrivinggA10=9.1mm, to the equivalent end points power F of first of first order auxiliary spring based on initial tangential camberA1eCalculated, i.e.,
2. step:Curved surface height H of the first order auxiliary spring tailpiece at correspondence first endpoint location of second level auxiliary springA1-A2endMeter
Calculate
According to the width b=63mm of the offset frequency type progressive rate leaf spring such as two-stage auxiliary spring formula is non-, elastic modulus E=200Gpa;
The thickness h that first order auxiliary spring is firstA11=13mm, half clamping length LA11=225mm;The half that second level auxiliary spring is first is clamped
Length LA21=125mm, and the F being 1. calculated in stepA1e=552.9N, to first order auxiliary spring tailpiece in correspondence second level pair
Curved surface height H at first endpoint location of springA1-A2endCalculated, i.e.,
In formula,It is the first deformation coefficient at correspondence first endpoint location of second level auxiliary spring of first order auxiliary spring, i.e.,
3. step:Second level gradual change gap deltaA12Design
According to the H being calculated in 2. stepA1-A2end=3.4mm, the H for obtaining is designed in the step c of step (4)gA20=
2.4mm, the second level gradual change gap delta of the offset frequency type progressive rate leaf spring such as non-to two-stage auxiliary spring formulaA12It is designed, i.e.,
δA12=HA1-A2end-HgA20=1.0mm.
Tested by model machine load deflection, the offset frequency type progressive rate such as two-stage auxiliary spring formula provided by the present invention is non-
The gradual change gap design method of leaf spring is correct, and for two-stage auxiliary spring formula is non-etc., the design of offset frequency type progressive rate leaf spring is provided reliably
Technical method.Reliable two-stage gradual change gap delta is can obtain using the methodMA1And δA12Design load, it is ensured that meet two-stage auxiliary spring
The design requirement of the contact load, progressive rate and suspension offset frequency of the offset frequency type progressive rate leaf spring under rated load such as formula is non-
Value, improves design level, quality and performance and the vehicle ride performance of the offset frequency type progressive rate leaf springs such as two-stage auxiliary spring formula is non-
And security;Meanwhile, reduce design and experimental test takes, accelerate product development speed.
Claims (1)
1. the gradual change gap design method of the offset frequency type progressive rate leaf spring such as two-stage auxiliary spring formula is non-, wherein, each leaf spring is with center
Mounting hole symmetrical structure, install clamp away from half for U-bolts clamp away from half;Auxiliary spring is designed as two-stage auxiliary spring,
By main spring and the initial tangential camber of auxiliary spring at different levels, it is ensured that main spring and first order auxiliary spring, first order auxiliary spring and second level auxiliary spring
Between two-stage gradual change gap deltaMA1And δA12, improve ride performance of the vehicle under rated load;In order to ensure meeting main spring
Stress intensity design requirement, makes first order auxiliary spring and second level auxiliary spring suitably undertake load in advance, the suspension under gradual change load
Offset frequency is unequal, i.e., the offset frequency type progressive rate leaf spring such as two-stage auxiliary spring formula is non-;According to each structural parameters of leaf spring, springform
Amount, U-bolts clamp away from, each contact load, rated load and be left cotangent bank high request value in rated load, to two
The two-stage gradual change gap of the level offset frequency type progressive rate leaf spring such as auxiliary spring formula is non-is designed, and specific design step is as follows:
(1) the two-stage gradual change of the offset frequency type progressive rate leaf spring such as two-stage auxiliary spring formula is non-clamps stiffness KkwP1And KkwP2Calculating:
Step A:First order gradual change clamps stiffness KkwP1Calculating
Start contact load P according to the 1st timek1, the 2nd beginning contact load Pk2, main spring clamping stiffness KM, main spring and first order pair
The compound clamping stiffness K of springMA1, to load p in [Pk1,Pk1] scope when first order gradual change clamp stiffness KkwP1Calculated, i.e.,
Step B:Second level gradual change clamps stiffness KkwP2Calculating
Start contact load P according to the 2nd timek2, the 2nd full contact load pw2, main spring is firm with the compound clamping of first order auxiliary spring
Degree KMA1, the total compound clamping stiffness K of major-minor springMA2, to load p in [Pk2,Pw2] in the range of when second level gradual change clamp rigidity
KkwP2Calculated, i.e.,
(2) the main spring initial tangential camber H of the offset frequency type progressive rate leaf spring such as two-stage auxiliary spring formula is non-gM0Design:
Start contact load P according to the 1st timek1, the 2nd beginning contact load Pk2, the 2nd full contact load pw2, rated load
PN, main spring clamping stiffness KM, the total compound clamping stiffness K of major-minor springMA, in rated load PNUnder remaining tangent line camber HgMN, and
The K being calculated in step (1)kwP1And KkwP2, the main spring initial tangential of the offset frequency type progressive rate leaf spring such as non-to two-stage auxiliary spring formula
Camber HgM0It is designed, i.e.,
(3) first order auxiliary spring initial tangential camber H of the offset frequency type progressive rate leaf spring such as two-stage auxiliary spring formula is non-gA10Design:
I steps:Main spring tailpiece lower surface radius of curvature RM0bCalculating
According to main reed number n, each thickness h of main springi, i=1,2 ..., n;The first half clamping length L of main spring1, step
(2) H that design is obtained ingM0, to main spring tailpiece lower surface radius of curvature RM0bCalculated, i.e.,
Ii steps:First upper surface radius of curvature R of first order auxiliary springA10aCalculate
According to the width b of the offset frequency type progressive rate leaf spring such as two-stage auxiliary spring formula is non-, elastic modulus E;Main reed number n, each main spring
Thickness hi, i=1,2 ..., n;The half clamping length L of first of main spring1, the 1st beginning contact load Pk1, and i steps fall into a trap
The R for obtainingM0b, to first upper surface radius of curvature R of first order auxiliary springA10aCalculated, i.e.,
In formula, hMeIt is the equivalent thickness of main spring root lap,
Iii steps:First order auxiliary spring initial tangential camber HgA10Design
According to the first order auxiliary spring half clamping length L of firstA11, the R that ii step values are calculatedA0a, at the beginning of first order auxiliary spring
Beginning tangent line camber HgA10It is designed, i.e.,
(4) second level auxiliary spring initial tangential camber H of the offset frequency type progressive rate leaf spring such as two-stage auxiliary spring formula is non-gA20Design:
A steps:First order auxiliary spring tailpiece lower surface radius of curvature RA10Calculating
According to first order auxiliary spring piece number m1, the thickness h that first order auxiliary spring is eachA1j, j=1,2 ..., m1;It is calculated in ii steps
RA0a, to the main spring tailpiece lower surface radius of curvature R of the first orderA10bCalculated, i.e.,
B step:R on first upper table curvature radius of second level auxiliary springA20aCalculating
According to the width b of the offset frequency type progressive rate leaf spring such as two-stage auxiliary spring formula is non-, elastic modulus E;Main reed number n, each main spring
Thickness hi, i=1,2 ..., n, the half clamping length L of first of main spring1;First order auxiliary spring piece number m1, each of first order auxiliary spring
Thickness hA1j, j=1,2 ..., m1;Start contact load P 1st timek1, the 2nd beginning contact load Pk2, and calculating in a steps
The R for obtainingA10b, to first radius of curvature R of upper surface of second level auxiliary springA20aCalculated, i.e.,
In formula, hMA1eIt is the root lap equivalent thickness of main spring and first order auxiliary spring,
Step c:Second level auxiliary spring initial tangential camber HgA20Design
According to the second level auxiliary spring half clamping length L of firstA21, the R that b step value is calculatedA20a, second level auxiliary spring is cut
Bank H highgA20It is designed, i.e.,
(5) first order gradual change gap delta of the offset frequency type progressive rate leaf spring such as two-stage auxiliary spring formula is non-MA1Design:
I steps:The first main equivalent end points power F of spring based on main spring tangent line camberM1eCalculating
According to the width b of the offset frequency type progressive rate leaf spring such as two-stage auxiliary spring formula is non-, elastic modulus E;The first thickness h of main spring1, one
Half clamping length L1, the H that design is obtained in step (2)gM0, to the first main equivalent end points power F of spring based on main spring tangent line camberM1e
Calculated, i.e.,
II steps:Curved surface high H of the main spring tailpiece at the correspondence first order first endpoint location of auxiliary springM1-A1endCalculate
According to the width b of the offset frequency type progressive rate leaf spring such as two-stage auxiliary spring formula is non-, elastic modulus E=200Gpa;First of main spring
Thickness h1, half clamping length L1;The half clamping length L of first of first order auxiliary springA11, and the F being calculated in I stepsM1e,
To curved surface height H of the main spring tailpiece at the correspondence first order first endpoint location of auxiliary springM1-A1endCalculated, i.e.,
In formula,It is deformation coefficient of the main spring at the correspondence first order first endpoint location of auxiliary spring,
III steps:The first order gradual change gap delta of the offset frequency type progressive rate leaf spring such as two-stage auxiliary spring formula is non-MA1Design
The H for obtaining is designed in iii steps according to step (3)gA10, the H that II steps are calculatedM1-M2end, to two-stage auxiliary spring formula
The first order gradual change gap delta of the offset frequency type progressive rate leaf spring such as non-MA1It is designed, i.e.,
δMA1=HM1-A1end-HgA10;
(6) second level gradual change gap delta of the offset frequency type progressive rate leaf spring such as two-stage auxiliary spring formula is non-A12Design:
1. step:The equivalent end points power F of first of first order auxiliary spring based on initial tangential camberA1eCalculate
According to the width b of the offset frequency type progressive rate leaf spring such as two-stage auxiliary spring formula is non-, elastic modulus E;The thickness that first order auxiliary spring is first
Degree hA11, the half clamping length L of first of first order auxiliary springA11, the H for obtaining is designed in the iii steps of step (3)gA10, to being based on
The equivalent end points power F of first of first order auxiliary spring of initial tangential camberA1eCalculated, i.e.,
2. step:Curved surface height H of the first order auxiliary spring tailpiece at correspondence first endpoint location of second level auxiliary springA1-A2endCalculate
According to the width b of the offset frequency type progressive rate leaf spring such as two-stage auxiliary spring formula is non-, elastic modulus E;The thickness that first order auxiliary spring is first
Degree hA11, the half clamping length L of first of first order auxiliary springA11;The half clamping length L of first of second level auxiliary springA21, and 1. walk
The F being calculated in rapidA1e, to curved surface of the first order auxiliary spring tailpiece at correspondence first endpoint location of second level auxiliary spring highly
HA1-A2endCalculated, i.e.,
In formula,It is deformation coefficient of the first order auxiliary spring at correspondence first endpoint location of second level auxiliary spring, i.e.,
3. step:Second level gradual change gap deltaA12Design
According to the H being calculated in 2. stepA1-A2end, the H for obtaining is designed in the step c of step (4)gA20, to two-stage auxiliary spring formula
The second level gradual change gap delta of the offset frequency type progressive rate leaf spring such as non-A12It is designed, i.e.,
δA12=HA1-A2end-HgA20。
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JPH08326809A (en) * | 1995-05-31 | 1996-12-10 | Isuzu Motors Ltd | Leaf spring |
JP2003306019A (en) * | 2002-04-11 | 2003-10-28 | Nissan Motor Co Ltd | Leaf spring type suspension device |
CN201621219U (en) * | 2009-07-22 | 2010-11-03 | 长沙福田汽车科技有限公司 | Front leaf spring for engineering vehicles |
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CN104696403A (en) * | 2015-01-06 | 2015-06-10 | 成都客车股份有限公司 | Composite spring structure realizing equal offset frequency of variable stiffness |
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2017
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JPH08326809A (en) * | 1995-05-31 | 1996-12-10 | Isuzu Motors Ltd | Leaf spring |
JP2003306019A (en) * | 2002-04-11 | 2003-10-28 | Nissan Motor Co Ltd | Leaf spring type suspension device |
CN201621219U (en) * | 2009-07-22 | 2010-11-03 | 长沙福田汽车科技有限公司 | Front leaf spring for engineering vehicles |
CN102799780A (en) * | 2012-07-17 | 2012-11-28 | 山东理工大学 | Automobile steel plate spring stiffness checking method |
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