CN105890884A - Hoist spindle reliability analysis, calculation and evaluation method - Google Patents

Abstract

The invention discloses a hoist spindle reliability analysis, calculation and evaluation method. The method comprises the following steps: S1, strain parameters of the hoist during one hoisting process are detected; S2, cyclic principal stress and cyclic shear stress applied to a drum wheel disc are obtained through the strain parameters; S3, the joint force for a force node is analyzed, torques when the drum wheel disc acts on two load action points of the hoist spindle and a torque when a motor acts on the hoist spindle are analyzed; and S4, a spindle flexural torque diagram and a torque diagram for the hoist spindle are obtained, a distortion energy density criterion for a dangerous section strength formula: a square root of (sigma<2>+3tau<2>)<[sigma] serves as a basis for spindle reliability design, and reliability calculation and evaluation are carried out. According to the hoist spindle reliability analysis, calculation and evaluation method disclosed by the invention, a perturbation method is adopted for reliability design, uncertainty of the load is considered, a reliability index is easy to solve, and more practical value is provided for reliability analysis on the hoist spindle.

Description

A kind of analytical calculation appraisal procedure of main shaft of hoister reliability

Technical field

The present invention relates to main shaft of hoister reliability prediction technical field, relate in particular to a kind of main shaft of hoister reliable The analytical calculation appraisal procedure of property.

Background technology

Along with manufacturing accelerated development, the demand of various raw materials and the energy is increasing, friction-type mine hoist Being undertaken of task increases the weight of the most day by day, and therefore the reliability of elevator receives much attention.In practical work process, km deep-well carries The lifting device of the machine of liter works long hours often, and main shaft of hoister is mainly by devices such as deadweight own and main shaft coilings Gravity, the steel wire rope tension being applied to main shaft by reel and motor are applied to the torque of main shaft, so main shaft is rotating through Journey is easily generated fatigue failure, it is therefore necessary to be analyzed calculating assessment to the reliability of main shaft of hoister.

For determining the force-bearing situation of parts on main shaft and carrying out reliability design, there has been proposed many methods.At present, In terms of the fail-safe analysis of main shaft of hoister calculates assessment, mainly there are method of safety coefficients, fuzzy Reliability Model method etc..Use Traditional method of safety coefficients carries out reliability design, it is impossible to preferably consider that the strength of materials has discreteness；Jin Minjie sets up The Fuzzy reliability design model of main shaft of hoister fatigue strength calculates more complicated.

Summary of the invention

It is an object of the invention to the defect for above-mentioned prior art, it is provided that the analysis meter of a kind of main shaft of hoister reliability Calculate appraisal procedure, use perturbation method to carry out reliability design, not only consider the uncertainty of load but also easily try to achieve reliability index, The fail-safe analysis making main shaft of hoister has more practical value.Interference fit is used with the main shaft shaft shoulder in view of reel disc, In a lifting process, main shaft is synchronized with the movement with reel and the maximum stress moment suffered by the two is identical, by disc loading process And mathematical model characterizes the loading process of main shaft accordingly, determine therefrom that the danger position in main shaft rotary course and carry out reliable Property design, the method had not only avoided load and through the error of wire rope transfers to main shaft but also had characterized the stress feelings of main shaft more really Condition.

To achieve these goals, the technical scheme is that

The analytical calculation appraisal procedure of a kind of main shaft of hoister reliability, comprises the steps:

At static, acceleration and the strain parameter of decelerating phase reel disc in S1, detection lifting process of elevator；

A1, reel disc based on elevator and the main shaft shaft shoulder use interference fit, in lifting process of elevator Main shaft of hoister is synchronized with the movement with reel and the maximum stress moment suffered by the two is identical, by reel disc loading process and corresponding Mathematical model characterize main shaft of hoister loading process；

A2, use perturbation method, by strain detecting get a promotion in lifting process of machine static, accelerate and deceleration rank The strain parameter ε of section reel disc_0°、ε_90°、ε₄₅；

S2, strain parameter by reel disc obtain the circulation principal stress σ suffered by reel disc_y、σ_zWith circulation shear stress τ_yz；Main shaft of hoister is transferred force to by the steel wire rope being wrapped on reel, it may be determined that main shaft of hoister in view of load Stress be:

$\left\{\begin{array}{c}\mathrm{\&sigma;}={\mathrm{\&sigma;}}_z+{\mathrm{\&tau;}}_{yz}\\ \mathrm{\&tau;}={\mathrm{\&sigma;}}_y+{\mathrm{\&tau;}}_{yz}\end{array}\right.$

S3, bearing is acted on the supporting function point of main shaft of hoister, reel disc acts on the load of main shaft of hoister The G that makes a concerted effort of each part being arranged in main shaft of hoister and the gravity of main shaft own, as stress node, is decomposed and carries by application point The reel disc of analyzing with joint efforts, in the lump rising on each stress node of owner's axle and analyzing these stress nodes acts on lifting owner The torque of two load points of axle and motor act on the torque of main shaft of hoister；

S4, the main shaft bending moment diagram of the owner's axle that gets a promotion and torque diagram, determined elevator by main shaft bending moment diagram and torque diagram The dangerouse cross-section of main shaft, with the strength formula of dangerouse cross-sectionDistortional strain energy concentration criterion is as main shaft reliability The foundation of design, obtains:

In formula: the elastic modelling quantity of E reel disc material；The modulus of shearing of G reel disc material；μ volume The Poisson's ratio of cylinder disc material；

S5, Calculation of Reliability are assessed:

B1, according to following formula calculate main shaft of hoister target reliability degree R:

R=∫_{G (X) ＞ 0}f_X(X)dX

In formula: f_X(X) essentially random parameter vector X=(X₁, X₂..., X_n)^TJoint probability density, g (X) Function of state, represents the two states of parts,

B2, according to following formula calculate main shaft of hoister target reliabilities index β:

$\mathrm{\&beta;}=\frac{{\mathrm{\&mu;}}_g}{{\mathrm{\&sigma;}}_g}=\frac{E\&lsqb;g\left(X\right)\&rsqb;}{\sqrt{Var\&lsqb;g\left(X\right)\&rsqb;}}$

In formula: μ_g, the average of E [g (X)] function of state g (X)；σ_g, the institute of Var [g (X)] function of state g (X) There is variance and covariance；

B3, result of calculation from target reliability degree R Yu reliability index β draw the reliability of main shaft of hoister；

B4, according to stress-strength interference theory, with the main shaft of hoister state equation of limiting range of stress state representation:

In formula, r is the strength of materials of main shaft of hoister, basic random variables vector X=(r ε_0°ε_90°ε_45°E G μ)^T, these Average E (X)=(μ of basic random variables vector X_rμ_ε0°μ_ε90°μ_ε45°μ_Eμ_Gμ_μ)^T；Variance and covariance

And think that these stochastic variables are the most independent stochastic variables of Normal Distribution；

${\mathrm{\&mu;}}_g=E\&lsqb;g\left(X\right)\&rsqb;=g\left(\stackrel{\&OverBar;}{X}\right)+\frac{1}{2}\frac{{\&part;}^{2}g\left(\stackrel{\&OverBar;}{X}\right)}{\&part;X^{T2}}Var\left(X\right)$

${{\mathrm{\&sigma;}}^2}_g=Var\&lsqb;g\left(X\right)\&rsqb;={\&lsqb;\frac{\&part;g\left(\stackrel{\&OverBar;}{X}\right)}{\&part;X^T}\&rsqb;}^{\&lsqb;2\&rsqb;}Var\left(X\right).$

As the improvement to technique scheme, during perturbation method strain detecting, strain gauge adhesion step and strain Signal acquisition method sees reel disc strain detecting experiment in friction-type mine hoist key rotary body Research on Dynamic Characteristic In strain gauge adhesion step and strain signal acquisition method.The China delivered in June, 2014 in Wang Chong autumn seen from the method Mining industry University Ph.D. Dissertation.

As the improvement to technique scheme, described dangerouse cross-section is that the reel disc of close motor side acts on lifting Cross section residing for the load point of owner's axle.

As the improvement to technique scheme, use ladder according to impact theory of control, the acceleration of lifting and decelerating phase Shape acceleration method controls.

Compared with prior art, provide the benefit that acquired by the present invention:

The analytical calculation appraisal procedure of the main shaft of hoister reliability of the present invention, uses perturbation method to carry out reliability design, Not only consider the uncertainty of load but also easily try to achieve reliability index, make the fail-safe analysis of main shaft of hoister have more practical valency Value.Use interference fit in view of reel disc and the main shaft shaft shoulder, in a lifting process main shaft and reel be synchronized with the movement and The two suffered maximum stress moment is identical, characterizes the loading process of main shaft by disc loading process and corresponding mathematical model, Determining therefrom that the danger position in main shaft rotary course and carry out reliability design, the method had both avoided load and had passed through steel wire rope The error being delivered to main shaft characterizes the stressing conditions of main shaft the most really.

Accompanying drawing explanation

In order to be illustrated more clearly that the embodiment of the present invention or technical scheme of the prior art, below will be to embodiment or existing In having technology to describe, the required accompanying drawing used is briefly described, it should be apparent that, the accompanying drawing in describing below is only this Some embodiments of invention, for those of ordinary skill in the art, on the premise of not paying creative work, also may be used To obtain other accompanying drawing according to these accompanying drawings.

Fig. 1 is that in a lifting process, No. 1 foil gauge (0 ° of direction) strains time dependent graph of relation；

Fig. 2 is that in a lifting process, No. 2 foil gauges (90 ° of directions) strain time dependent graph of relation；

Fig. 3 is that in a lifting process, No. 3 foil gauges (45 ° of directions) strain time dependent graph of relation；

Fig. 4 is the three-dimensional strain of detection, stress state analysis result figure；

Fig. 5 is main shaft of hoister structure and force analysis figure；

Fig. 6 is that main shaft of hoister Force Calculation analyzes sketch；

Fig. 7 is main shaft of hoister Bending Moment Analysis sketch；

Fig. 8 is main shaft of hoister torsional analysis sketch；

Fig. 9 is the time dependent graph of relation of main shaft of hoister stress in a lifting process；

Figure 10 is the time dependent graph of relation of main shaft of hoister rotational angle in a lifting process.

Detailed description of the invention

Below in conjunction with the accompanying drawing in the embodiment of the present invention, the technical scheme in the embodiment of the present invention is carried out clear, complete Describe, it is clear that described embodiment is only a part of embodiment of the present invention rather than whole embodiments wholely.Based on Embodiment in the present invention, it is every other that those of ordinary skill in the art are obtained under not making creative work premise Embodiment, any modification, equivalent substitution and improvement etc. made, should be included within the scope of the present invention.

The analytical calculation appraisal procedure of the main shaft of hoister reliability of the present invention, comprises the steps:

The simulation of 1 disc strain detecting result

First passing through strain detecting and obtain the stressing conditions of reel disc in a lifting process, concrete strain gauge adhesion walks Rapid and strain signal acquisition method sees the experiment of reel disc strain detecting.According to impact theory of control, use trapezoidal adding The acceleration and deceleration process of speed controlling elevator, can reduce the tension force amplitude of steel wire rope and elastic vibration thus reach steadily to promote Effect, therefore use trapezoidal acceleration control promote acceleration and the decelerating phase.The strain stress of No. 1, No. 2, No. 3 foil gauge_0°、 ε_90°、ε_45°Corresponding testing result as shown in Figure 1, Figure 2, Figure 3 shows, be illustrated respectively in a lifting process three direction strains with The relation curve of time change.In Fig. 1, Fig. 2, Fig. 3,0-1s is the elevator resting state before experiment starts, and each foil gauge is not examined Measure data；1-67s, for once promoting the cycle, represents boost phase, each strain measurement knot in constant velocity stage and decelerating phase Really.

2 main shaft reliability designs

2.1 principal stress analyses

As shown in Figure 4, the three-dimensional strain stress to detection_0°、ε_45°、ε_90°After being analyzed, obtain friction-type mine hoist volume Cylinder disc suffered by be two differ in size, the mutually perpendicular asymmetric circulation principal stress σ in direction_y、σ_z, and two size phases Deng, the mutually perpendicular asymmetric circulation shear stress τ in direction_yz.Power is passed by the steel wire rope being wrapped on reel in view of load It is delivered to main shaft of hoister, so reel disc stress can characterize the size promoting load, therefore can be by disc Stress analyzes the stress of main shaft.

$\left\{\begin{array}{c}\mathrm{\&sigma;}={\mathrm{\&sigma;}}_z+{\mathrm{\&tau;}}_{yz}\\ \mathrm{\&tau;}={\mathrm{\&sigma;}}_y+{\mathrm{\&tau;}}_{yz}\end{array}\right.---\left(1\right)$

According to above formula, the stress on reel disc is synthesized in the direct stress σ and the same plane that are perpendicularly oriented to main-shaft axis Shearing stress τ vertical with direct stress σ, in order to main shaft is carried out force analysis.

$\left\{\begin{array}{c}P=q(L_1+L_2/2)\&times;g\\ p_2=q(L_2+L_3)/2\&times;g\\ p_3=q(L_3+L_4)/2\&times;g\\ p_4=q(L_5+L_4/2)\&times;g\end{array}\right.---\left(2\right)$

In formula: every meter of quality of q main shaft (kg/m), g acceleration of gravity (m/s²)

P_1-4It is assigned to the partical gravity (kN) of each stress node

L_1-5By the length (m) of every section of main shaft after stress node allocation

Fig. 5 show main shaft of hoister structure and force diagram, the gravity G of each part being arranged on main shaft and main shaft itself Belong to the load being applied on main shaft, main shaft is carried out force analysis therefore to convenient and determine dangerouse cross-section, gravity G is pressed Formula (2) is assigned on each stress node of main shaft.

Fig. 6 show main shaft calculation diagram, the wherein F in A, D cross section₁、F₄The holding power provided for bearing and P in formula (2)₁、 P₄Make a concerted effort, direction is along y-axis positive direction；The F in B, C cross section₂、F₃The pressure provided for reel disc and P in formula (2)₂、P₃Conjunction Power, direction is along y-axis negative direction, and B, C cross section also has the big torque T the most in the same direction such as two that reel disc provides₁、T₂(along X-axis Negative direction is viewed as clockwise)；The torque T that E cross section provides for motor₃(being viewed as counterclockwise along X-axis negative direction).In conjunction with figure Main shaft stressing conditions shown in 6 obtains main shaft bending moment diagram as shown in Figure 7 and main-shaft torque figure as shown in Figure 8, and determines The dangerouse cross-section of main shaft of hoister is C cross section, i.e. the cross section of reel disc near motor side and main shaft interference fit.

$\sqrt{{\mathrm{\&sigma;}}^2+3{\mathrm{\&tau;}}^2}\&le;\&lsqb;\mathrm{\&sigma;}\&rsqb;---\left(3\right)$

Spindle material uses 45Mn, owing to main shaft is primarily subjected to bending and reverses, therefore makees with above formula distortional strain energy concentration criterion Foundation for main shaft reliability design.

In formula: the elastic modelling quantity of E reel disc material

The modulus of shearing of G reel disc material

The Poisson's ratio of μ reel disc material

Disc strain stress with detection_0°、ε_45°、ε_90°ExpressionIn stress σ, τ can get formula (4) with And the time dependent relation curve of main shaft of hoister stress in a lifting process as shown in Figure 9, and combine shown in Figure 10 The time dependent relation curve of main axis angle, obtaining the maximum stress moment suffered by reel disc is 57.9s, this moment Spindle rotation angle degree is 86 ° (horizontal level shown in Fig. 4 is 0 °, is positive direction clockwise), carries out reliability design the most accordingly.

2.2 reliability design

Using perturbation method to carry out reliability design herein, on the one hand the target of reliability design is can according to formula (5) calculating By degree R, formula (6) on the other hand can be used to calculate reliability index β, thus directly weigh the reliability of parts.

R=∫_{G (X) ＞ 0}f_X(X)dX (5)

In formula: f_X(X) essentially random parameter vector X=(X₁, X₂..., X_n)^TJoint probability density；g(X)—— Function of state, represents the two states of parts,

$\mathrm{\&beta;}=\frac{{\mathrm{\&mu;}}_g}{{\mathrm{\&sigma;}}_g}=\frac{E\&lsqb;g\left(X\right)\&rsqb;}{\sqrt{Var\&lsqb;g\left(X\right)\&rsqb;}}---\left(6\right)$

In formula: μ_g, the average of E [g (X)] function of state g (X)；σ_g, the institute of Var [g (X)] function of state g (X) There is variance and covariance

According to stress-strength interference theory, with main shaft of hoister state equation such as formula (7) institute of limiting range of stress state representation Show

In formula, r is the strength of materials of main shaft, basic random variables vector X=(r ε_0°ε_90°ε_45°E Gμ)^T, these substantially with Average E (X)=(μ of machine variable vector X_rμ_ε0°μ_ε90°μ_ε45°μ_Eμ_Gμ_μ)^T；Variance and covariance

And think that these stochastic variables are the most independent stochastic variables of Normal Distribution.

${\mathrm{\&mu;}}_g=E\&lsqb;g\left(X\right)\&rsqb;=g\left(\stackrel{\&OverBar;}{X}\right)+\frac{1}{2}\frac{{\&part;}^{2}g\left(\stackrel{\&OverBar;}{X}\right)}{\&part;X^{T2}}Var\left(X\right)---\left(8\right)$

${{\mathrm{\&sigma;}}^2}_g=Var\&lsqb;g\left(X\right)\&rsqb;={\&lsqb;\frac{\&part;g\left(\stackrel{\&OverBar;}{X}\right)}{\&part;X^T}\&rsqb;}^{\&lsqb;2\&rsqb;}Var\left(X\right)---\left(9\right)$

In formula: []^[2]---Kronecker power

The needs actual according to engineering and mathematical derivation numerous easily, typically as shown in formula (8) and formula (9), take function of state g (X) Two-order approximation average and first approximation variance, therefore seek local derviation function of state g (X) to basic random variables vector X Number.And known conditions substitution formula (8) shown in the partial derivative result tried to achieve and formula (10) and formula (9) are obtained function of state Average and variance, substitute into the expression formula (5) of reliability index β and the expression formula (6) of reliability R the most again, determine that out main shaft Reliability index β=2.5189, reliability R=0.9941.

2.3 sensitive analysis

When engineering goods are carried out Design of Reliability Analysis, affected journey in order to understand each factor to what engineering goods lost efficacy Degree, will study Mechanical Product Reliability sensitivity, in order to evaluate each design parameter pair on the basis of reliability design The influence degree that engineering goods lost efficacy.

By the reliability average to basic random variables, the partial derivative of variance represents sensitivity.If value is for just, representing this ginseng The increase of numerical value can improve the reliability of engineering goods；Otherwise, then reduce.

Random parameter vector X average, the sensitivity expression formula of variance are by reliability

$\frac{dR}{d{\stackrel{\&OverBar;}{X}}^T}=\frac{\&part;R}{\&part;\mathrm{\&beta;}}\frac{\&part;\mathrm{\&beta;}}{\&part;{\mathrm{\&mu;}}_g}\frac{\&part;{\mathrm{\&mu;}}_g}{\&part;{\stackrel{\&OverBar;}{X}}^T}---\left(11\right)$

$\frac{dR}{dVar\left(X\right)}=\frac{\&part;R}{\&part;\mathrm{\&beta;}}\frac{\&part;\mathrm{\&beta;}}{\&part;{\mathrm{\&sigma;}}_g}\frac{\&part;{\mathrm{\&sigma;}}_g}{\&part;Var\left(X\right)}---\left(12\right)$

In formula:

$\frac{\&part;\mathrm{\&beta;}}{\&part;{\mathrm{\&mu;}}_g}=\frac{1}{{\mathrm{\&sigma;}}_g}$

$\frac{\&part;{\mathrm{\&mu;}}_g}{\&part;{\stackrel{\&OverBar;}{X}}^T}=\&lsqb;\frac{\&part;\stackrel{\&OverBar;}{g}}{\&part;X_1}\frac{\&part;\stackrel{\&OverBar;}{g}}{\&part;X_2}\mathrm{...}\frac{\&part;\stackrel{\&OverBar;}{g}}{\&part;X_n}\&rsqb;$

$\frac{\&part;\mathrm{\&beta;}}{\&part;{\mathrm{\&sigma;}}_g}=-\frac{{\mathrm{\&mu;}}_g}{{{\&part;}_g}^2}$

$\frac{\&part;{\mathrm{\&sigma;}}_g}{\&part;Var\left(X\right)}=\frac{1}{2{\mathrm{\&sigma;}}_g}\&lsqb;\frac{\&part;\stackrel{\&OverBar;}{g}}{\&part;X}\&CircleTimes;\frac{\&part;\stackrel{\&OverBar;}{g}}{\&part;X}\&rsqb;$

Wherein:The density function of Standard Normal Distribution；Kronecker amasss.

Reliability index according to the main shaft of hoister drawn above and reliability, calculate about 7 of main shaft reliability The sensitivity of parameter is as follows:

From above sensitivity data, spindle material intensity r and disc strain stress_45°Increase can improve main shaft Reliability；Disc strain stress_0°、ε_90°, the elastic modulus E of reel disc material, the shear modulus G of reel disc material, reel spoke The increase of Poisson's ratio μ of panel material, reduces the reliability of main shaft.The wherein strain stress in three directions_0°、ε_45°、ε_90°To reliability Impact maximum；Poisson's ratio μ of reel disc material, spindle material intensity r are taken second place；The shear modulus G of reel disc material, elasticity Modulus E is minimum to reliability effect.

Additionally, the increase of stochastic variable parameter variance all can make main shaft reliability reduce, stochastic variable parametric covariance Change the impact on main shaft reliability to be not quite similar.

Carrying out force analysis herein by main shaft of hoister, having obtained main shaft dangerouse cross-section is reel disc and main shaft mistake Be full of coordinate cross section, design main shaft time should strengthen emphatically this dangerouse cross-section.Main shaft dangerouse cross-section in lifting process is divided Analysis, obtains the stress suffered by the conversion stage main shaft between the acceleration promoted that slows down increases and acceleration reduces maximum, should To this, the stage carries out appropriate regulation, to reduce failure probability.Additionally, sensitive analysis result shows the strain stress in three directions_0°、 ε_45°、ε_90°Sensitivity is big；Spindle material intensity r and reel disc material Poisson's ratio μ are taken second place；The modulus of shearing of reel disc material G and elastic modulus E are minimum to main shaft reliability effect, should weigh when product maintenance, design.

The above is only the preferred embodiment of the present invention, it is noted that for the ordinary skill people of the art For Yuan, on the premise of without departing from the technology of the present invention principle, it is also possible to make some improvement and replacement, these improve and replace Also should be regarded as protection scope of the present invention.

Claims (3)

1. the analytical calculation appraisal procedure of a main shaft of hoister reliability, it is characterised in that comprise the steps:

At static, acceleration and the strain parameter of decelerating phase reel disc in S1, detection lifting process of elevator；

A1, reel disc based on elevator and the main shaft shaft shoulder use interference fit, promote in lifting process of elevator Owner's axle is synchronized with the movement with reel and the maximum stress moment suffered by the two is identical, by reel disc loading process and counts accordingly Learn model and characterize the loading process of main shaft of hoister；

A2, use perturbation method, by strain detecting get a promotion in lifting process of machine static, accelerate and the decelerating phase rolls up The strain parameter ε of cylinder disc_0°、ε_90°、ε₄₅；

S2, strain parameter by reel disc obtain the circulation principal stress σ suffered by reel disc_y、σ_zWith circulation shear stress τ_yz；Examine Consider and transfer force to main shaft of hoister to load by the steel wire rope being wrapped on reel, it may be determined that the stress of main shaft of hoister For:

$\left\{\begin{array}{c}\mathrm{\&sigma;}={\mathrm{\&sigma;}}_z+{\mathrm{\&tau;}}_{yz}\\ \mathrm{\&tau;}={\mathrm{\&sigma;}}_y+{\mathrm{\&tau;}}_{yz}\end{array}\right.$

S3, bearing is acted on the supporting function point of main shaft of hoister, reel disc acts on the load effect of main shaft of hoister The G that makes a concerted effort of each part being arranged in main shaft of hoister and the gravity of main shaft own, as stress node, is decomposed elevator by point On each stress node of main shaft and analyze these stress nodes make a concerted effort, in the lump analyze reel disc act on main shaft of hoister The torque of two load points and motor act on the torque of main shaft of hoister；

S4, the main shaft bending moment diagram of the owner's axle that gets a promotion and torque diagram, determined main shaft of hoister by main shaft bending moment diagram and torque diagram Dangerouse cross-section, with the strength formula of dangerouse cross-sectionDistortional strain energy concentration criterion is as main shaft reliability design Foundation, obtain:

In formula: the elastic modelling quantity of E reel disc material；The modulus of shearing of G reel disc material；μ reel spoke The Poisson's ratio of panel material；

S5, Calculation of Reliability are assessed:

B1, according to following formula calculate main shaft of hoister target reliability degree R:

R=∫_{G (X) ＞ 0}f_X(X)dX

In formula: f_X(X) essentially random parameter vector X=(X₁, X₂..., X_n)^TJoint probability density, g (X) state Function, represents the two states of parts,

B2, according to following formula calculate main shaft of hoister target reliabilities index β:

$\mathrm{\&beta;}=\frac{{\mathrm{\&mu;}}_g}{{\mathrm{\&sigma;}}_g}=\frac{E\&lsqb;g\left(X\right)\&rsqb;}{\sqrt{Var\&lsqb;g\left(X\right)\&rsqb;}}$

In formula: μ_g, the average of E [g (X)] function of state g (X)；σ_g, all sides of Var [g (X)] function of state g (X) Difference and covariance；

B3, result of calculation from target reliability degree R Yu reliability index β draw the reliability of main shaft of hoister；

B4, according to stress-strength interference theory, with the main shaft of hoister state equation of limiting range of stress state representation:

In formula, r is the strength of materials of main shaft of hoister, basic random variables vector X=(r, ε_0°, ε_90°, ε_45°, E, G, μ)^T, these Average E (X)=(μ of basic random variables vector X_r με_0° με_90° με_45° μ_E μ_G μ_μ)^T；Variance and covariance And think that these stochastic variables are the most independent stochastic variables of Normal Distribution；

${\mathrm{\&mu;}}_g=E\&lsqb;g\left(X\right)\&rsqb;=g\left(\stackrel{\&OverBar;}{X}\right)+\frac{1}{2}\frac{{\&part;}^{2}g\left(\stackrel{\&OverBar;}{X}\right)}{\&part;X^{T2}}Var\left(X\right)$

${{\mathrm{\&sigma;}}^2}_g=Var\&lsqb;g\left(X\right)\&rsqb;={\&lsqb;\frac{\&part;g\left(\stackrel{\&OverBar;}{X}\right)}{\&part;X^T}\&rsqb;}^{\&lsqb;2\&rsqb;}Var\left(X\right).$

The analytical calculation appraisal procedure of main shaft of hoister reliability the most according to claim 1, it is characterised in that described danger Cross section is the cross section residing for load point acting on main shaft of hoister near the reel disc of motor side.

The analytical calculation appraisal procedure of main shaft of hoister reliability the most according to claim 1, it is characterised in that according to impact Theory of control, the acceleration of lifting and decelerating phase use trapezoidal acceleration method to control.