CN106548003B - The simulation calculation method of the offset frequencys type three-level progressive rate leaf spring such as non-root maximum stress - Google Patents
The simulation calculation method of the offset frequencys type three-level progressive rate leaf spring such as non-root maximum stress Download PDFInfo
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Abstract
The present invention relates to the simulation calculation methods of the offset frequencys type three-level progressive rate leaf spring such as non-root maximum stress, belong to vehicle suspension leaf spring technical field.The present invention can be according to the structural parameters of each main spring and auxiliary spring at different levels, elasticity modulus, U-bolts clamp away from, initial tangential camber, rated load, on the basis of leaf spring maximum gauge leaf springs at different levels determination and contact load simulation calculation, simulation calculation is carried out to the leaf spring roots at different levels maximum stress of the offset frequencys type three-level progressive rate leaf spring such as non-.By model machine loading stress is tested, the simulation calculation method of the offset frequencys type three-level progressive rate leaf spring root maximum stress such as non-provided by the present invention is correct, available accurately and reliably root maximum stress simulation calculation value, provides reliable technical method for leaf spring root maximum stress simulation calculations at different levels.The design level, q&r and vehicle safety of product can be improved using this method；Meanwhile design and testing expenses are reduced, accelerate product development speed.
Description
Technical field
The present invention relates to vehicle suspension leaf springs, are especially the offset frequencys type three-level progressive rate leaf spring such as non-root maximum stresses
Simulation calculation method.
Background technique
It, can be by the main spring and pair of former first-order gradient rigidity leaf spring in order to meet the vehicle driving ride comfort under different loads
Spring is split as two-stage respectively, that is, uses three-level progressive rate leaf spring；Meanwhile in order to meet the stress intensity of main spring, usually pass through
Main spring and three-level auxiliary spring initial tangential camber and three-level gradual change gap, make three-level auxiliary spring suitably undertake load in advance, to reduce
The stress of main spring, i.e., using the offset frequencys type three-level progressive rate plate spring suspension brackets such as non-, wherein leaf spring roots at different levels maximum stress, no
It is only related with the structural parameters and load of each of main spring and auxiliary spring at different levels, it is also related with contact load, and influence leaf spring stress
Intensity, reliability and service life and vehicle safety.It is rigid for the offset frequencys type three-level gradual change such as non-of given design structure
Spend leaf spring, if meet stress intensity requirement, it is necessary to checking computations are emulated to it.However, due to the offset frequencys type three-level progressive rate such as non-
The leaf spring roots at different levels maximum stress calculating of leaf spring is extremely complex, and is calculated by leaf spring root lap equivalent thickness at different levels
With the restriction of contact load simulation calculation problem, the offset frequencys type three-level progressive rate leaf spring root such as non-is not provided always inside and outside predecessor State
The simulation calculation method of portion's maximum stress, it is thus impossible to meet, the offset frequencys type three-level progressive rate leaf spring such as non-is designed and CAD software is opened
Hair requires.With Vehicle Speed and its continuous improvement required ride comfort, progressive rate plate spring suspension brackets are proposed more
High request, therefore, it is necessary to establish, one kind is accurate, reliably the offset frequencys type three-level progressive rate leaf spring root maximum stress such as non-is imitative
True calculating method, the root maximum stress simulation calculation for the offset frequencys type three-level progressive rate leaf spring such as non-provide reliable technical side
Method meets fast-developing Vehicle Industry, vehicle driving ride comfort and wants to the design of the offset frequencys type three-level progressive rate leaf spring such as non-
It asks, improves design level, quality, reliability and the service life and vehicle safety of product；Meanwhile reducing design and examination
Expense is tested, product development speed is accelerated.
Summary of the invention
For above-mentioned defect existing in the prior art, technical problem to be solved by the invention is to provide it is a kind of it is easy,
The reliably simulation calculation method of the offset frequencys type three-level progressive rate leaf spring root maximum stress such as non-, simulation calculation flow process such as Fig. 1
It is shown.The half symmetrical structure of three-level progressive rate leaf spring is as shown in Fig. 2, be by main spring 1, first order auxiliary spring 2 and second level pair
Composed by spring 3 and third level auxiliary spring 4, the half of the total span of three-level progressive rate leaf spring is equal to the half effect of first main spring
Length L1T, U-bolts clamp away from half be L0, the width of leaf spring is b, elasticity modulus E, allowable stress [σ].Wherein, main
The piece number n piece of spring 1, each of main spring with a thickness of hi, the half action length of each of main spring is LiT, half clamping length Li=
L1iT-L0/ 2, i=1,2 ..., n.The piece number of first order auxiliary spring 2 is n1, first order auxiliary spring each with a thickness of hA1j, half effect
Length is LA1jT, half clamping length LA1j=LA1jT-L0/ 2, j=1,2 ..., n1.The piece number of second level auxiliary spring 3 is n2, the second level
Auxiliary spring each with a thickness of hA2k, half action length LA2kT, half clamping length LA2k=LA2kT-L0/ 2, k=1,2 ..., n2。
The piece number of third level auxiliary spring 4 is n3, third level auxiliary spring each with a thickness of hA3l, the half action length L of l pieceA3lT, half folder
Tight length LA3l=LA3lT-L0/ 2, l=1,2 ..., n3.By the initial tangential camber of main spring and auxiliary spring at different levels, at the end of main spring 1
First order gradual change gap delta is provided between piece lower surface and first upper surface of first order auxiliary spring 2MA1；The end of first order auxiliary spring 2
Second level gradual change gap delta is provided between piece lower surface and first upper surface of second level auxiliary spring 3A12；The end of second level auxiliary spring 3
Third level gradual change gap delta is provided between piece lower surface and first upper surface of third level auxiliary spring 4A23, to meet progressive rate plate
The contact load of spring, progressive rate, stress intensity, the design requirement of suspension offset frequency and vehicle driving ride comfort and safety.Root
According to the structural parameters of each of main spring and auxiliary springs at different levels, elasticity modulus, U-bolts is clamped away from, initial tangential camber, rated load,
In the determination of the thickness of leaf spring root lap equivalent thickness at different levels and maximum gauge leaf spring and the base of contact load simulation calculation
On plinth, simulation calculation is carried out to the root maximum stress of the leaf springs at different levels of the offset frequencys type three-level progressive rate leaf spring such as non-, it is ensured that set
Meter leaf spring meets stress intensity design requirement.
In order to solve the above technical problems, the offset frequencys type three-level progressive rate leaf spring root maximum such as non-provided by the present invention is answered
The simulation calculation method of power, it is characterised in that use following simulation calculation step:
(1) main spring and its with the maximum gauge leaf spring of the root lap equivalent thickness of auxiliary springs at different levels and leaf spring at different levels
Thickness determines: step A: main spring and its with the determination of the root lap equivalent thickness of auxiliary springs at different levels according to main reed number n, it is main
The thickness h that spring is eachi, i=1,2 ..., n；First order auxiliary spring the piece number n1, thickness h that first order auxiliary spring is eachA1j, j=1,
2,...,n1；Second level auxiliary spring the piece number n2, thickness h that second level auxiliary spring is eachA2k, k=1,2 ..., n2；Third level auxiliary spring the piece number
n3, thickness h that third level auxiliary spring is eachA3l, l=1,2 ..., n3；To the equivalent thickness h of the root lap of main springMe, it is main
The equivalent thickness h of the root lap of spring and auxiliary springs at different levelsMA1e、hMA2eAnd hMA3eIt is determined, it may be assumed that
Step B: the determination of the thickness of the maximum gauge leaf spring of leaf springs at different levels
1) step: the thickness h of the maximum gauge leaf spring of main springmaxDetermination according to main reed number n, the thickness of each of main spring
hi, i=1,2 ..., n determine the thickness h of the maximum gauge leaf spring of main springmax, i.e.,
hmax=max (hi)；
2) step: the thickness h of the maximum gauge leaf spring of first order auxiliary springA1maxDetermination according to first order auxiliary spring the piece number n1,
The thickness h that first order auxiliary spring is eachA1j, j=1,2 ..., n1, determine the thickness h of the maximum gauge leaf spring of first order auxiliary springA1max,
I.e.
hA1max=max (hA1j), j=1,2 ..., n1；
3) step: the thickness h of the maximum gauge leaf spring of second level auxiliary springA2maxDetermination according to second level auxiliary spring the piece number n2,
The thickness h that second level auxiliary spring is eachA2k, k=1,2 ..., n2, determine the thickness h of the maximum gauge leaf spring of second level auxiliary springA2max,
I.e.
hA2max=max (hA2k), k=1,2 ..., n2；
4) step: the thickness h of the maximum gauge leaf spring of third level auxiliary springA3maxDetermination according to third level auxiliary spring the piece number n3,
The thickness h that third level auxiliary spring is eachA3l, l=1,2 ..., n3, determine the thickness h of the maximum gauge leaf spring of third level auxiliary springA3max,
I.e.
hA3max=max (hA3l), l=1,2 ..., n3；
(2) each secondary contact load P of the offset frequencys type three-level progressive rate leaf spring such as non-k1、Pk2And Pk3Simulation calculation:
I step: the first order main spring tailpiece lower surface initial curvature radius RM0bIt calculates according to main reed number n, each of main spring
Thickness hi, i=1,2 ..., n；The half clamping length L of first of main spring1, the initial tangential camber H of main springgM0, under main spring tailpiece
Surface initial curvature radius RM0bIt is calculated, i.e.,
II step: first upper surface initial curvature radius R of first order auxiliary springA10aCalculate one according to first order auxiliary spring first
Half clamping length LA11, the initial tangential camber H of first order auxiliary springgA10, to first order auxiliary spring tailpiece upper surface initial curvature radius
RA10aIt is calculated, i.e.,
III step: first order auxiliary spring tailpiece lower surface initial curvature radius RA10bIt calculates according to first order auxiliary spring the piece number n1,
The thickness h that first order auxiliary spring is eachA1j, j=1,2 ..., n1；The R being calculated in II stepA10a, under first order auxiliary spring tailpiece
Surface initial curvature radius RA10bIt is calculated, i.e.,
IV step: first upper surface initial curvature radius R of second level auxiliary springA20aCalculating according to second level auxiliary spring first
Half clamping length LA21, the initial tangential camber design value H of second level auxiliary springgA20, at the beginning of second level auxiliary spring first upper surface
Beginning radius of curvature RA20aIt is calculated, i.e.,
V step: first lower surface initial curvature radius R of second level auxiliary springA20bCalculating very according to second level auxiliary spring the piece number n2,
The thickness h that second level auxiliary spring is eachA2k, k=1,2 ..., n2And R determined by IV stepA20a, to first following table of second level auxiliary spring
Face initial curvature radius RA20bIt is calculated, i.e.,
VI step: first upper surface initial curvature radius R of third level auxiliary springA30aCalculating according to third level auxiliary spring first
Half clamping length LA31, the initial tangential camber H of third level auxiliary springgA30, to first upper surface initial curvature of third level auxiliary spring half
Diameter RA30aIt is calculated, i.e.,
VII step: the 1st beginning contact load Pk1Simulation calculation according to the offset frequencys type three-level progressive rate leaf spring such as non-
Width b, elastic modulus E；The half clamping length L of first of main spring1, the h that is calculated in step (1)Me, calculate in I step
The R arrivedM0b, the R that is calculated in II stepA10a, to the 1st beginning contact load Pk1Simulation calculation is carried out, i.e.,
VIII step: the 2nd beginning contact load Pk2Simulation calculation according to the offset frequencys type three-level progressive rate leaf spring such as non-
Width b, elastic modulus E；The half clamping length L of first of main spring1, identified h in step (1)MA1e, calculate in III step
Obtained RA10b, the R that is calculated in IVA20a, the P that checks in VII stepk1, to the 2nd beginning contact load Pk2It carries out
Simulation calculation, i.e.,
IX step: the 3rd beginning contact load Pk3Simulation calculation according to the offset frequencys type three-level progressive rate leaf spring such as non-
Width b, elastic modulus E, the half clamping length L of first of main spring1, identified h in step (1)MA2e, it is calculated in V step
RA20b, the R that is calculated in VIA30a, the P that checks in VIII stepk2, to the 3rd beginning contact load Pk3It is imitated
It is true to calculate, i.e.,
(3) the main spring root maximum stress σ of the offset frequencys type three-level progressive rate leaf spring such as non-MmaxSimulation calculation:
According to the width b of the offset frequencys type three-level progressive rate leaf spring such as non-, the half clamping length L of first of main spring1, specified load
Lotus PN, identified h in step (1)Me、hMA1e、hMA2e、hMA3eAnd hmax, simulation calculation obtains in step (2) Pk1, Pk2With
Pk3；To the main spring root maximum stress σ under different loads PMmaxSimulation calculation is carried out, i.e.,
(4) first order auxiliary spring root maximum stress σ of the offset frequencys type three-level progressive rate leaf spring such as non-A1maxSimulation calculation:
According to the width b of the offset frequencys type three-level progressive rate leaf spring such as non-, the half clamping length L of first of main spring1, specified load
Lotus PN；Identified h in step (1)MA1e、hMA2、hMA3eAnd hA1max；The P that simulation calculation obtains in step (2)k1, Pk2And Pk3, right
First order auxiliary spring root maximum stress σ at different loads PMA1maxSimulation calculation is carried out, i.e.,
(5) second level auxiliary spring root maximum stress σ of the offset frequencys type three-level progressive rate leaf spring such as non-A2maxSimulation calculation:
According to the width b of the offset frequencys type three-level progressive rate leaf spring such as non-, the half clamping length L of first of main spring1, specified load
Lotus PN；Identified h in step (1)MA2e、hMA3eAnd hA2max, simulation calculation obtains in step (2) Pk2And Pk3；To different loads
Second level auxiliary spring root maximum stress σ under lotus PA2maxSimulation calculation is carried out, i.e.,
(6) third level auxiliary spring root maximum stress σ of the offset frequencys type three-level progressive rate leaf spring such as non-A3maxSimulation calculation:
According to the width b of the offset frequencys type three-level progressive rate leaf spring such as non-, the half clamping length L of first of main spring1, specified load
Lotus PN；Identified h in step (1)MA3eAnd hA3max；The P that simulation calculation obtains in step (2)k3, under different loads P
The root maximum stress σ of three-level auxiliary springA3maxSimulation calculation is carried out, i.e.,
The present invention has the advantage that than the prior art
Since the leaf spring roots at different levels maximum stress calculating of the offset frequencys type three-level progressive rate leaf spring such as non-is extremely complex, and
It is calculated by leaf spring root lap equivalent thickness at different levels and contact load simulation calculation problem is restricted, inside and outside predecessor State always
The simulation calculation method for not providing the offset frequencys type three-level progressive rate leaf spring such as non-root maximum stress, is not able to satisfy the offset frequencys type three such as non-
The design of grade progressive rate leaf spring and CAD software exploitation require.The present invention can according to the structural parameters of each of main spring and auxiliary springs at different levels,
Elasticity modulus, U-bolts are clamped away from initial tangential camber, rated load in leaf spring maximum gauge leaf springs determinations at different levels and connects
On the basis of touching load simulation calculation, the leaf spring roots at different levels maximum stress of the offset frequencys type three-level progressive rate leaf spring such as non-is carried out
Simulation calculation.It is tested by model machine loading stress it is found that the offset frequencys type three-level progressive rate leaf spring root such as non-provided by the present invention
The simulation calculation method of portion's maximum stress is correctly, leaf spring root maximum stress simulation calculations accurately and reliably at different levels to can be obtained
Value, provides reliable technical method for leaf spring root maximum stress simulation calculations at different levels.Product can be improved using this method
Design level, q&r and vehicle safety；Meanwhile design and testing expenses are reduced, accelerate product development speed
Degree.
Detailed description of the invention
For a better understanding of the present invention, it is described further with reference to the accompanying drawing.
Fig. 1 is the simulation calculation flow process figure of the offset frequencys type three-level progressive rate leaf spring such as non-root maximum stress；
Fig. 2 is the half symmetrical structure schematic diagram of the offset frequencys type three-level progressive rate leaf spring such as non-；
Fig. 3 is the main spring root maximum stress σ of embodimentMmaxThe characteristic curve changed with load p；
Fig. 4 is the first order auxiliary spring root maximum stress σ of embodimentA1maxThe characteristic curve changed with load p；
Fig. 5 is the second level auxiliary spring root maximum stress σ of embodimentA2maxThe characteristic curve changed with load p；
Fig. 6 is the third level auxiliary spring root maximum stress σ of embodimentA3maxThe characteristic curve changed with load p.
Specific embodiment
Below by embodiment, invention is further described in detail.
Embodiment: the width b=63mm of certain offset frequencys type three-level progressive rate leaf spring such as non-, U-bolts clamp away from half
L0=50mm, elastic modulus E=200GPa.Total the piece number N=5 of major-minor spring, wherein main reed number n=2, each thickness h1=h2
=8mm；The half action length of first main spring is L1T=525mm, half clamping length are L1=L1T-L0/ 2=500mm.First
The piece number n of grade auxiliary spring1=1, thickness hA11=8mm.The piece number n of second level auxiliary spring2=1, thickness hA21=13mm.Third level auxiliary spring
The piece number n3=1, thickness hA31=13mm.The initial tangential camber H of main springgM0=102.3mm, the initial tangential of first order auxiliary spring
Camber HgA10=18.8mm, the initial tangential camber H of second level auxiliary springgA20=6mm, the initial tangential camber of third level auxiliary spring
HgA30=1.6mm.Rated load PN=7227N.According to the structural parameters of each of main spring and auxiliary springs at different levels, elasticity modulus, spiral shell of riding
Bolt is clamped away from, rated load, the initial tangential camber of main spring and auxiliary spring at different levels, to the offset frequencys type three-level progressive rate leaf spring such as non-
Leaf spring roots at different levels maximum stress under different loads carries out simulation calculation.
The simulation calculation method of the offset frequencys type three-level progressive rate leaf spring such as non-root maximum stress provided by present example,
Its simulation calculation flow process is as shown in Figure 1, specifically steps are as follows for simulation calculation:
(1) main spring and its with the maximum gauge leaf spring of the root lap equivalent thickness of auxiliary springs at different levels and leaf spring at different levels
Thickness determines: step A: main spring and its with the determination of the root lap equivalent thickness of auxiliary springs at different levels according to main reed number n=
2, the thickness h of each of main spring1=h2=8mm；First order auxiliary spring the piece number n1=1, thickness hA11=8mm；Second level auxiliary spring the piece number n2
=1, thickness hA21=13mm；Third level auxiliary spring the piece number n3=1, thickness hA31=13mm；To the root lap of main spring etc.
Imitate thickness hMe, main spring and auxiliary springs at different levels root lap equivalent thickness hMA1e、hMA2e、hMA3eIt is determined, it may be assumed that
Step B: the determination of the thickness of the maximum gauge leaf spring of leaf springs at different levels
1) step: the thickness h of the maximum gauge leaf spring of main springmaxDetermination according to main reed number n=2, the thickness of each of main spring
Spend h1=h2=8mm determines the thickness h of the maximum gauge leaf spring of main springmax, i.e.,
hmax=max (h1,h2)=8mm；
2) step: the thickness h of the maximum gauge leaf spring of first order auxiliary springA1maxDetermination according to first order auxiliary spring the piece number n1=
1, thickness hA11=8mm determines the thickness h of the maximum gauge leaf spring of first order auxiliary springA1max, i.e.,
hA1max=max (hA11)=8mm；
3) step: the thickness h of the maximum gauge leaf spring of second level auxiliary springA2maxDetermination according to second level auxiliary spring the piece number n2=
1, thickness hA21=13mm determines the thickness h of the maximum gauge leaf spring of second level auxiliary springA2max, i.e.,
hA2max=max (hA21)=13mm；
4) step: the thickness h of the maximum gauge leaf spring of third level auxiliary springA3maxDetermination according to third level auxiliary spring the piece number n3=
1, thickness hA31=13mm determines the thickness h of the maximum gauge leaf spring of third level auxiliary springA3max, i.e.,
hA3max=max (hA31)=13mm.
(2) each secondary contact load P of the offset frequencys type three-level progressive rate leaf spring such as non-k1、Pk2And Pk3Simulation calculation:
I step: the first order main spring tailpiece lower surface initial curvature radius RM0bIt calculates according to main reed number n=2, main spring is each
The thickness h of piecei=8mm, i=1,2 ..., n；The half clamping length L of first of main spring1=500mm, the initial tangential camber of main spring
HgM0=102.3mm, to main spring tailpiece lower surface initial curvature radius RM0bIt is calculated, i.e.,
II step: first upper surface initial curvature radius R of first order auxiliary springA10aCalculate one according to first order auxiliary spring first
Half clamping length LA11=325mm, the initial tangential camber H of first order auxiliary springgA10=18.8mm, on first order auxiliary spring tailpiece
Surface initial curvature radius RA10aIt is calculated, i.e.,
III step: first order auxiliary spring tailpiece lower surface initial curvature radius RA10bIt calculates according to first order auxiliary spring the piece number n1=
1, thickness hA11=8mm；The R being calculated in II stepA10a=2818.6mm, it is initially bent to first order auxiliary spring tailpiece lower surface
Rate radius RA10bIt is calculated, i.e.,
RA10b=RA10a+hA11=2826.6mm；
IV step: first upper surface initial curvature radius R of second level auxiliary springA20aCalculating according to second level auxiliary spring first
Half clamping length LA21=225mm, the initial tangential camber H of second level auxiliary springgA20=6mm, to second level auxiliary spring head on piece table
Face initial curvature radius RA20aIt is calculated, i.e.,
V step: first lower surface initial curvature radius R of second level auxiliary springA20bCalculating very according to second level auxiliary spring the piece number n2=
1, thickness hA21R determined by=13mm and IV stepA20a=4221.8mm, to first lower surface initial curvature of second level auxiliary spring
Radius RA20bIt is calculated, i.e.,
RA20b=RA20a+hA21=4234.8mm；
VI step: first upper surface initial curvature radius R of third level auxiliary springA30aCalculating according to third level auxiliary spring first
Half clamping length LA31=125mm, the initial tangential camber H of third level auxiliary springgA30=1.6mm, to third level auxiliary spring head on piece
Surface initial curvature radius RA30aIt is calculated, i.e.,
VII step: the 1st beginning contact load Pk1Simulation calculation according to the offset frequencys type three-level progressive rate leaf spring such as non-
Width b=63mm, elastic modulus E=200GPa；The half clamping length L of first of main spring1=500mm, step (1) is middle to be determined
HMeThe R being calculated in=10.1mm, I stepM0bThe R being calculated in=1289mm, II stepA10a=2818.6mm is right
1st beginning contact load Pk1Simulation calculation is carried out, i.e.,
VIII step: the 2nd beginning contact load Pk2Simulation calculation according to the offset frequencys type three-level progressive rate leaf spring such as non-
Width b=63mm, elastic modulus E=200GPa；The half clamping length L of first main spring1=500mm, the middle institute of step (1) is really
Fixed hMA1eThe R being calculated in=11.5mm, III stepA10bThe R being calculated in=2826.6mm, IVA20a=
The P that simulation calculation obtains in 4221.8mm, VII stepk1=1810N, the 2nd beginning to the three-level leaf spring with gradually changing stiffness
Contact load Pk2Simulation calculation is carried out, i.e.,
IX step: the 3rd beginning contact load Pk3Simulation calculation according to the offset frequencys type three-level progressive rate leaf spring such as non-
Width b=63mm, elastic modulus E=200GPa；The half clamping length L of first of main spring1=500mm, step (1) is middle to be determined
HMA2eThe R being calculated in=15.5mm, V stepA20bThe R being calculated in=4234.8mm, VIA30a=4883.6mm,
The P that simulation calculation obtains in VIII stepk2=2564.8N, to the 3rd beginning contact load Pk3Simulation calculation is carried out, i.e.,
(3) the main spring root maximum stress σ of the offset frequencys type three-level progressive rate leaf spring such as non-MmaxSimulation calculation:
According to the width b=63mm of the offset frequencys type three-level progressive rate leaf spring such as non-, the half clamping length L of first of main spring1
=500mm, rated load PN=7227N determines obtained h in step (1)Me=10.1mm, hMA1e=11.5mm, hMA2e=
15.5mm、hMA3e=18.1mm and hmax=8mm, the P that simulation calculation obtains in step (2)k1=1831N, Pk2=2586N and Pk3
=3077N, to the main spring root maximum stress σ under different loads PMmaxSimulation calculation is carried out, i.e.,
Using Matlab calculation procedure, the main spring of the obtained offset frequencys type three-level progressive rate leaf spring such as non-of simulation calculation
Root maximum stress σMmaxWith P lotus change curve is carried, as shown in Figure 3；Wherein, in rated load PNMain spring root under=7227N
Maximum stress σMmax=592.5MPa.
(4) first order auxiliary spring root maximum stress σ of the offset frequencys type three-level progressive rate leaf spring such as non-A1maxSimulation calculation:
According to the width b=63mm of the offset frequencys type three-level progressive rate leaf spring such as non-, the half clamping length L of first of main spring1
=500mm, rated load PN=7227N；Identified h in step (1)MA1e=11.5mm, hMA2e=15.5mm, hMA3e=
18.1mm and hA1max=8mm；The P that simulation calculation obtains in step (2)k1=1831N, Pk2=2586N and Pk3=3077N is right
First order auxiliary spring root maximum stress σ under different loads PMA1maxSimulation calculation is carried out, i.e.,
Using Matlab calculation procedure, the first of the obtained offset frequencys type three-level progressive rate leaf spring such as non-of simulation calculation
Grade auxiliary spring root maximum stress σA1maxWith load p change curve, as shown in Figure 4；Wherein, in rated load PNUnder=7227N
The root maximum stress σ of first order auxiliary springM2max=252MPa.
(5) second level auxiliary spring root maximum stress σ of the offset frequencys type three-level progressive rate leaf spring such as non-A2maxSimulation calculation:
According to the width b=63mm of the offset frequencys type three-level progressive rate leaf spring such as non-, the half clamping length L of first of main spring1
=500mm, rated load PN=7227N；Identified h in step (1)MA2e=15.5mm, hMA3e=18.1mm and hA2max=
13mm, the P that simulation calculation obtains in step (2)k2=2586N and Pk3=3077N；To the second level auxiliary spring root under different loads P
Portion maximum stress σA2maxSimulation calculation is carried out, i.e.,
Using Matlab calculation procedure, the second of the obtained offset frequencys type three-level progressive rate leaf spring such as non-of simulation calculation
Grade auxiliary spring root maximum stress σA2maxWith load p change curve, as shown in Figure 5；Wherein, in rated load PNUnder=7227N
The root maximum stress σ of second level auxiliary springA2max=257.3MPa.
(6) third level auxiliary spring root maximum stress σ of the offset frequencys type three-level progressive rate leaf spring such as non-A3maxSimulation calculation:
According to the width b=63mm of the offset frequencys type three-level progressive rate leaf spring such as non-, the half clamping length L of first of main spring1
=500mm, rated load PN=7227N；Identified h in step (1)MA3e=18.1mm and hA3max=13mm；In step (2)
The P that simulation calculation obtainsk3=3077N, to the root maximum stress σ of the third level auxiliary spring under different loads PA3maxIt is emulated
It calculates, i.e.,
Using Matlab calculation procedure, the third of the obtained offset frequencys type three-level progressive rate leaf spring such as non-of simulation calculation
Grade auxiliary spring root maximum stress σA3maxWith load p change curve, as shown in Figure 6, wherein in rated load PNUnder=7227N
Third level auxiliary spring root maximum stress σA3max=216.6MPa.
It is tested by model machine loading stress it is found that the offset frequencys type three-level progressive rate leaf spring root such as non-provided by the present invention
The simulation calculation method of maximum stress is correctly, accurately and reliably root maximum stress simulation calculation value to can be obtained, and is each step
Spring root maximum stress simulation calculation provides reliable technical method.Design level, the matter of product can be improved using this method
Amount and reliability and vehicle safety；Meanwhile design and testing expenses are reduced, accelerate product development speed.
Claims (1)
1. the emulated computation method of the offset frequencys type three-level progressive rate leaf spring such as non-root maximum stress, wherein each leaf spring be with
The symmetrical structure at center keyhole center, installation clamp away from half be U-bolts clamp away from half；Leaf spring be by main spring and
Three-level auxiliary spring is constituted, and passes through the initial tangential camber and three-level gradual change gap of main spring and three-level auxiliary spring, it is ensured that meets leaf spring contact
Load, the compound design requirement for clamping rigidity and stress intensity of gradual change, i.e., non-etc. offset frequencys type three-level progressive rate leaf spring；According to each
The structural parameters of piece leaf spring, elasticity modulus, U-bolts are clamped away from, initial tangential camber, rated load, in leaf spring roots at different levels
On the basis of lap equivalent thickness calculates, the thickness of maximum gauge leaf spring is determining and contact load simulation calculation, to non-etc.
The root maximum stress of the leaf springs at different levels of offset frequency type three-level progressive rate leaf spring carries out simulation calculation, and specific simulation calculation step is such as
Under:
(1) main spring and its thickness with the root lap equivalent thickness of auxiliary springs at different levels and the maximum gauge leaf spring of leaf spring at different levels
It determines: step A: main spring and its determination with the root lap equivalent thickness of auxiliary springs at different levels
According to main reed number n, the thickness h of each of main springi, i=1,2 ..., n；First order auxiliary spring the piece number n1, first order auxiliary spring is each
The thickness h of pieceA1j, j=1,2 ..., n1；Second level auxiliary spring the piece number n2, thickness h that second level auxiliary spring is eachA2k, k=1,2 ...,
n2；Third level auxiliary spring the piece number n3, thickness h that third level auxiliary spring is eachA3l, l=1,2 ..., n3；To the root lap of main spring
Equivalent thickness hMe, main spring and auxiliary springs at different levels root lap equivalent thickness hMA1e、hMA2eAnd hMA3eIt is determined, it may be assumed that
Step B: the determination of the thickness of the maximum gauge leaf spring of leaf springs at different levels
1) step: the thickness h of the maximum gauge leaf spring of main springmaxDetermination
According to main reed number n, the thickness h of each of main springi, i=1,2 ..., n determine the thickness of the maximum gauge leaf spring of main spring
hmax, i.e.,
hmax=max (hi)；
2) step: the thickness h of the maximum gauge leaf spring of first order auxiliary springA1maxDetermination
According to first order auxiliary spring the piece number n1, thickness h that first order auxiliary spring is eachA1j, j=1,2 ..., n1, determine first order auxiliary spring
Maximum gauge leaf spring thickness hA1max, i.e.,
hA1max=max (hA1j), j=1,2 ..., n1；
3) step: the thickness h of the maximum gauge leaf spring of second level auxiliary springA2maxDetermination
According to second level auxiliary spring the piece number n2, thickness h that second level auxiliary spring is eachA2k, k=1,2 ..., n2, determine second level auxiliary spring
Maximum gauge leaf spring thickness hA2max, i.e.,
hA2max=max (hA2k), k=1,2 ..., n2；
4) step: the thickness h of the maximum gauge leaf spring of third level auxiliary springA3maxDetermination
According to third level auxiliary spring the piece number n3, thickness h that third level auxiliary spring is eachA3l, l=1,2 ..., n3, determine third level auxiliary spring
Maximum gauge leaf spring thickness hA3max, i.e.,
hA3max=max (hA3l), l=1,2 ..., n3；
(2) each secondary contact load P of the offset frequencys type three-level progressive rate leaf spring such as non-k1、Pk2And Pk3Simulation calculation:
I step: the first order main spring tailpiece lower surface initial curvature radius RM0bIt calculates
According to main reed number n, the thickness h of each of main springi, i=1,2 ..., n；The half clamping length L of first of main spring1, main spring
Initial tangential camber HgM0, to main spring tailpiece lower surface initial curvature radius RM0bIt is calculated, i.e.,
II step: first upper surface initial curvature radius R of first order auxiliary springA10aIt calculates
According to first order auxiliary spring first half clamping length LA11, the initial tangential camber H of first order auxiliary springgA10, to the first order
Auxiliary spring tailpiece upper surface initial curvature radius RA10aIt is calculated, i.e.,
III step: first order auxiliary spring tailpiece lower surface initial curvature radius RA10bIt calculates
According to first order auxiliary spring the piece number n1, thickness h that first order auxiliary spring is eachA1j, j=1,2 ..., n1；It is calculated in II step
RA10a, to first order auxiliary spring tailpiece lower surface initial curvature radius RA10bIt is calculated, i.e.,
IV step: first upper surface initial curvature radius R of second level auxiliary springA20aCalculating
According to second level auxiliary spring first half clamping length LA21, the initial tangential camber design value H of second level auxiliary springgA20, right
Second level auxiliary spring first upper surface initial curvature radius RA20aIt is calculated, i.e.,
V step: first lower surface initial curvature radius R of second level auxiliary springA20bCalculating
Very according to second level auxiliary spring the piece number n2, thickness h that second level auxiliary spring is eachA2k, k=1,2 ..., n2And determined by IV step
RA20a, to first lower surface initial curvature radius R of second level auxiliary springA20bIt is calculated, i.e.,
VI step: first upper surface initial curvature radius R of third level auxiliary springA30aCalculating
According to third level auxiliary spring first half clamping length LA31, the initial tangential camber H of third level auxiliary springgA30, to the third level
First upper surface initial curvature radius R of auxiliary springA30aIt is calculated, i.e.,
VII step: the 1st beginning contact load Pk1Simulation calculation
According to the width b of the offset frequencys type three-level progressive rate leaf spring such as non-, elastic modulus E；The half clamping length L of first of main spring1,
The h being calculated in step (1)Me, the R that is calculated in I stepM0b, the R that is calculated in II stepA10a, the 1st time is started
Contact load Pk1Simulation calculation is carried out, i.e.,
VIII step: the 2nd beginning contact load Pk2Simulation calculation
According to the width b of the offset frequencys type three-level progressive rate leaf spring such as non-, elastic modulus E；The half clamping length L of first of main spring1,
Identified h in step (1)MA1e, the R that is calculated in III stepA10b, the R that is calculated in IVA20a, check in VII step
Obtained Pk1, to the 2nd beginning contact load Pk2Simulation calculation is carried out, i.e.,
IX step: the 3rd beginning contact load Pk3Simulation calculation
According to the width b of the offset frequencys type three-level progressive rate leaf spring such as non-, elastic modulus E, the half clamping length L of first of main spring1,
Identified h in step (1)MA2e, the R that is calculated in V stepA20b, the R that is calculated in VIA30a, check in VIII step
Obtained Pk2, to the 3rd beginning contact load Pk3Simulation calculation is carried out, i.e.,
(3) the main spring root maximum stress σ of the offset frequencys type three-level progressive rate leaf spring such as non-MmaxSimulation calculation:
According to the width b of the offset frequencys type three-level progressive rate leaf spring such as non-, the half clamping length L of first of main spring1, rated load PN,
Identified h in step (1)Me、hMA1e、hMA2e、hMA3eAnd hmax, simulation calculation obtains in step (2) Pk1, Pk2And Pk3；To not
With the main spring root maximum stress σ under load pMmaxSimulation calculation is carried out, i.e.,
(4) first order auxiliary spring root maximum stress σ of the offset frequencys type three-level progressive rate leaf spring such as non-A1maxSimulation calculation:
According to the width b of the offset frequencys type three-level progressive rate leaf spring such as non-, the half clamping length L of first of main spring1, rated load PN；
Identified h in step (1)MA1e、hMA2、hMA3eAnd hA1max；The P that simulation calculation obtains in step (2)k1, Pk2And Pk3, right
First order auxiliary spring root maximum stress σ at different loads PMA1maxSimulation calculation is carried out, i.e.,
(5) second level auxiliary spring root maximum stress σ of the offset frequencys type three-level progressive rate leaf spring such as non-A2maxSimulation calculation:
According to the width b of the offset frequencys type three-level progressive rate leaf spring such as non-, the half clamping length L of first of main spring1, rated load PN；
Identified h in step (1)MA2e、hMA3eAnd hA2max, simulation calculation obtains in step (2) Pk2And Pk3；To different loads
Second level auxiliary spring root maximum stress σ under PA2maxSimulation calculation is carried out, i.e.,
(6) third level auxiliary spring root maximum stress σ of the offset frequencys type three-level progressive rate leaf spring such as non-A3maxSimulation calculation:
According to the width b of the offset frequencys type three-level progressive rate leaf spring such as non-, the half clamping length L of first of main spring1, rated load PN；
Identified h in step (1)MA3eAnd hA3max；The P that simulation calculation obtains in step (2)k3, to the third under different loads P
The root maximum stress σ of grade auxiliary springA3maxSimulation calculation is carried out, i.e.,
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| CN105956270A (en) * | 2016-05-04 | 2016-09-21 | 山东理工大学 | Computing method of stress of each of end contact type less-leaf end part enhanced main spring and secondary spring |
| CN106246778A (en) * | 2016-10-18 | 2016-12-21 | 山东理工大学 | The non-method for designing waiting structure few sheet two ends spacing amount of deflection of reinforced type leaf spring in end |
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| CN102767585A (en) * | 2011-05-05 | 2012-11-07 | 北汽福田汽车股份有限公司 | Plate spring component for vehicles and manufacturing method thereof |
| CN105956270A (en) * | 2016-05-04 | 2016-09-21 | 山东理工大学 | Computing method of stress of each of end contact type less-leaf end part enhanced main spring and secondary spring |
| CN106246778A (en) * | 2016-10-18 | 2016-12-21 | 山东理工大学 | The non-method for designing waiting structure few sheet two ends spacing amount of deflection of reinforced type leaf spring in end |
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