CN107657120A - A kind of linear superelasticity large deformation spring - Google Patents
A kind of linear superelasticity large deformation spring Download PDFInfo
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- CN107657120A CN107657120A CN201710906333.4A CN201710906333A CN107657120A CN 107657120 A CN107657120 A CN 107657120A CN 201710906333 A CN201710906333 A CN 201710906333A CN 107657120 A CN107657120 A CN 107657120A
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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
- G06F30/17—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
- 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
- F16F1/04—Wound springs
- F16F1/08—Wound springs with turns lying in mainly conical surfaces, i.e. characterised by varying diameter
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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
- F16F2238/026—Springs wound- or coil-like
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Abstract
The invention provides a kind of linear superelasticity large deformation spring, belong to mechanical spring design field.A kind of new linear superelasticity large deformation spring, the defects of linear superelasticity spring is difficult to control α in the past is overcome, designer need to only determine a suitable helical angle numerical value, and the shearing and extruding that the change without worrying α again comes to spring band destroy；The spring designed with this method still falls within equal helix angle taper spring, has there is the manufacturing technology of maturation for equal helix angle taper spring, manufactures enhanced convenience；Designer only needs to ensure that wire diameter d meets d=AR0.5Large-scale linear elasticity can be realized, the influence brought without considering further that other specification.
Description
Technical field
The present invention relates to a kind of design method of linear superelasticity large deformation spring, belong to mechanical spring design field.
Background technology
Spring is a kind of common machine components, and it is used for storing and releasing energy more in mechanical device, such as in vapour
Suspension, very important effect is suffered from MEMS (MEMS) and anti-seismic structure.The conical helical spring in engineering
Deformability is most strong, and most compressed state can be a plane, and all coils all fall in fulcrum bearing, and its height is only single
Coil diameter, taken up space compared to other springs smaller.The rigidity of conical helical spring mainly with wire diameter d, pitch angle alpha
With end coil diameter D1、D2It is relevant, have related researcher at present and be designed for pitch angle alpha, give α satisfactions
Relational expression so that the rigidity of spring meets large-scale linear elasticity.
But there is following defect in this linear elasticity spring：1st, pitch angle alpha is change in whole spring, is difficult to control α
Size, α, which crosses conference, causes spring that failure by shear easily occurs, and α is too small to cause coil-span to diminish, easily occur extruding destroy；
2nd, this spring had both been not belonging to equal pitch taper spring or had been not belonging to equal helix angle taper spring, and there is presently no the manufacture of maturation
Technology；3rd, this spring is in the design process in addition to the relational expressions that should meet of α are considered, it is also contemplated that helical line of spring and coil
The relational expression that radius meets, design parameter are excessive and complicated.
The content of the invention
The technical problem to be solved in the present invention is to propose a kind of new linear superelasticity large deformation spring, overcomes mesh
The defects of preceding large deformation linear elasticity taper spring is present.For equal helix angle conical helical spring, (pitch angle alpha is can be controlled in properly
Size), load and the calculating formula of deformation are provided, probes into wire diameter d, and end coil diameter D1、D2To the shadow of spring rate
Ring, obtain the analytic solutions that spring rate is a wide range of linear elasticity.
Technical scheme：
A kind of linear superelasticity large deformation spring, step are as follows：
(1) equal helix angle taper spring load and the calculating formula of deformation
As shown in figure 1, for equal helix angle taper spring, linear, turning point, non-linear is divided into the presence of axial force
With complete pressure and four-stage；The deformation of linear stage, based on cylindrical spring, each coil of taper spring is considered as
The number of turns is a cylindrical spring, and according to the rigidity expression formula of cylindrical spring, it is integrated, and calculates taper spring in axial load
Deformation under lotus effect；The deformation of nonlinear phase, it is constant according to the helical angle of spring, it is straight by critical coil and critical coil
Footpath connects linear and nonlinear phase, the deformation of linear processes part is overlapped, obtaining total deformation is：
P represents axial load, D in formula1、D2Represent end coil diameter, N0Represent the active line number of turns, L0Represent spring pole
Deformation length is limited, G represents modulus of shearing, and d represents wire diameter, N1Represent that (calculating formula is critical coil number),
DTRepresent that (calculating formula is cut off diameter).Work as DT=D2When, critical load can be obtained
Work as DT=D1When, maximum load can be obtained
Spring pressure completely and when the condition that is met by plane be：
R(θ+2π)-R(θ)≥d (2)
In formula θ be spring coil spiral polar angle, R represent spring coil function of radius and
(2) functional relation that fairly linear spring d meets
From formula (1), camber of spring and D1、D2, N0, G, d is relevant, and wherein G belongs to the base attribute of spring material, no
Change the variation tendency of spring rate.And for spring, D1、D2And N0For definite value, belong to the basic design parameters of spring,
Understood howsoever to change D by formula (1)1、D2, N0Size, spring still has nonlinear phase, therefore problem concentrates on bullet
On spring filament diameter d.It should meet that certain functional relation make it that spring is complete linear elasticity through analyzing d, therefore in spiral shells such as derivations
It is different with formula (1) during the deformation calculating formula of swing angle taper spring.Flexibility (the unit axial direction masterpiece of known single spring coil
Deflection under) calculating formula is：
Axial spacing between known each coil is：
he=2 π Rtan α (4)
Under axial load P effects, the limit of deflection that Free Transform is capable of between coil is he=keP, bring into formula (3) and
(4), can obtain：
R can change with the change of coil in formula, it can be found that when d meets d=AR0.5When (A is setup parameter), band
Entering formula (4) can obtain：
From formula (5), now load p is constant, and d is the situation of constant before contrast, it is known that no longer has critical half
Footpath, its meaning represented is turning point load pTWith maximum load PMIt is equal, therefore spring there will be no non-linear partial, only deposit
In linear segment, when load reaches PcDuring value, all coils of spring are pressed simultaneously and the coil to bottom forms a plane.
By d=AR0.5Bringing camber of spring calculating formula into can obtain：
From formula (6), proportional relation between the deformation of spring and axial load, then d=AR0.5When, equal helix angle circle
The rigidity for boring spring is constant, and size is expressed as：
Beneficial effects of the present invention：The invention provides a kind of new linear superelasticity large deformation spring, overcome
Former linear superelasticity spring is difficult to control the defects of α, and designer need to only determine a suitable helical angle numerical value, without carrying on a shoulder pole again
The shearing and extruding that heart α change comes to spring band destroy；The spring designed with this method still falls within equal helix angle taper spring,
There is the manufacturing technology of maturation for equal helix angle taper spring, manufactured enhanced convenience；Designer only needs to ensure spring
Silk diameter d meets d=AR0.5Large-scale linear elasticity can be realized, the influence brought without considering further that other specification.
Brief description of the drawings
Fig. 1 is the indicatrix and deformation process of equal helix angle taper spring.
Fig. 2 is the design diagram of linear superelasticity large deformation spring.
Fig. 3 (a) is the linear superelasticity large deformation spring before deformation.
Fig. 3 (b) is the linear superelasticity large deformation spring after deformation.
Fig. 4 is general spring and A=0.46,0.48,0.50mm0.5The indicatrix of linear superelasticity large deformation spring.
In figure：1. bottom coil radius D2/2；2. upper end coil radius D1/2；3. pitch angle alpha；4. wire diameter
(meet d=AR0.5)；5. end coil；6. active coil N0；7. ultimate deformation length L0；8. spring total length Ls。
Embodiment
Below in conjunction with accompanying drawing and technical scheme, embodiment of the invention is further illustrated.
Exemplified by designing certain linear superelasticity large deformation spring, embodiment of the invention is：
(1) shear modulus G of spring, coil number N are determined according to engineering demand0, end coil diameter D1、D2, pitch angle alpha
These basic design parameters, with G=81500MPa, N0=4, D1=30mm, D2=50mm, exemplified by α=5 °.
(2) spring can completely press and when being plane, the condition that parameter A meets, numerical value in (1) be brought into formula (2)
Row can be calculated：A≤0.52756mm0.5。
(3) numerical value in (1) is brought into formula (8), calculates the rigidity of spring, select to close according to the design requirement of spring rate
Suitable A values, take A=0.46,0.48,0.50mm respectively here0.5Exemplified by.
(4) equal helix angle taper spring fabrication schedule is called, writes wire diameter d=AR0.5Design program, start
Program is until spring manufacture is completed.
The elastic range of the present invention design spring of table 1
Understood with reference to table 1 and figure (4), in theory, (d be constant, other conditions all same) general bullet under the same terms
The elastic range of spring accounts for the 65.33% of total deformation, and meets d=AR0.5Equal helix angle taper spring elastic range it is reachable
100%, and adjusting parameter A big I effectively changes the rigidity and bearing capacity of spring.
Claims (1)
1. a kind of linear superelasticity large deformation spring, it is characterised in that step is as follows：
(1) equal helix angle taper spring load and the calculating of deformation
For equal helix angle taper spring, linear, turning point, non-linear and complete pressure simultaneously four are divided into the presence of axial force
Stage；The deformation of linear stage, based on cylindrical spring, it is a cylinder that each coil of taper spring is considered as into the number of turns
Spring, according to the rigidity expression formula of cylindrical spring, it is integrated, calculate change of the taper spring under Axial Loads
Shape；The deformation of nonlinear phase, it is constant according to the helical angle of spring, by critical coil and critical coil diameter connecting line and
Nonlinear phase, the deformation of linear processes part is overlapped, obtaining total deformation is：
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In formula：P represents axial load, D1、D2Represent end coil diameter, N0Represent the active line number of turns, L0Represent that spring limit becomes
Shape length, G represent modulus of shearing, and d represents wire diameter；
N1Critical coil number is represented, calculating formula is
DTCut off diameter is represented, calculating formula is
Work as DT=D2When, obtain critical load
Work as DT=D1When, obtain maximum load
Taper spring pressure completely and when the condition that is met by plane be：
R(θ+2π)-R(θ)≥d (2)
In formula：R represents the radius of taper spring coil；
(2) functional relation that fairly linear spring d meets
Because d meets certain functional relation, thus when deriving the deformation calculating formula of equal helix angle taper spring with formula (1)
It is different；The flexibility of known single spring coil is the deflection under unit responsive to axial force, and calculating formula is：
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Axial spacing between known coil is：
he=2 π R tan α (4)
Under axial load P effects, the limit of deflection that Free Transform is capable of between coil is he=keP, bring formula (3) and (4) into,
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Known by formula (5), now load p is constant, and d is the situation of constant before contrast, it is known that critical radius no longer be present, its generation
The meaning of table is turning point load pTWith maximum load PMIt is equal, therefore spring there will be no non-linear partial, only exist linear portion
Point, when load reaches PcDuring value, all coils of spring are pressed simultaneously and the coil to bottom forms a plane；By d=
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Known by formula (6), proportional relation between the deformation of spring and axial load, then d=AR0.5When, equal helix angle taper spring
Rigidity be constant, size is expressed as：
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| CN201710906333.4A CN107657120B (en) | 2017-09-29 | 2017-09-29 | Design method of spring with high elastic deformation of superline |
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| CN201710906333.4A CN107657120B (en) | 2017-09-29 | 2017-09-29 | Design method of spring with high elastic deformation of superline |
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| CN107657120B CN107657120B (en) | 2019-12-27 |
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Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN108875209A (en) * | 2018-06-18 | 2018-11-23 | 西北工业大学 | Polycarbonate thin plate large deformation ductile failure problem emulation mode under a kind of High Loading Rate |
| IT201800005017A1 (en) * | 2018-05-03 | 2019-11-03 | Improved Coil Spring | |
| CN111895010A (en) * | 2020-08-05 | 2020-11-06 | 南开大学 | Metal nano conical spring device |
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| WO2006034210A3 (en) * | 2004-09-21 | 2008-07-31 | Thomas Sugar | Adjustable stiffness jack spring actuator |
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| CN102519798A (en) * | 2011-12-05 | 2012-06-27 | 西安理工大学 | Device and method for measuring stiffness of canted coil spring |
| CN105808846A (en) * | 2016-03-08 | 2016-07-27 | 西北工业大学 | Interference fit quantitative calculation method based on spring model |
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| IT201800005017A1 (en) * | 2018-05-03 | 2019-11-03 | Improved Coil Spring | |
| CN108875209A (en) * | 2018-06-18 | 2018-11-23 | 西北工业大学 | Polycarbonate thin plate large deformation ductile failure problem emulation mode under a kind of High Loading Rate |
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