CN110502765A - A kind of correction method and roller bearing of tapered roller bearing - Google Patents
A kind of correction method and roller bearing of tapered roller bearing Download PDFInfo
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Abstract
The present invention relates to bearing applied technical fields, the correction method and roller bearing of especially a kind of tapered roller bearing, the roller bearing after a kind of correction method correction of the flank shape by obtaining, the correction method carries out correction of the flank shape to using roller and raceway contact point as the part for extending setting length along contact line length direction of origin using logarithmic curve, correction of the flank shape is carried out to the remainder set except length is extended using quadratic polynomial curve, the optimal parameter that simulation calculation determines quadratic polynomial equation is carried out to roller bearing by physical simulation again, correction of the flank shape is carried out to bearing according to optimal parameter corresponding modification curve equation, realize the correction of the flank shape to tapered roller bearing, prevent end contact stress when gauche bearings from excessively concentrating, the tapered roller bearing for solving existing logarithm correction of the flank shape, which occurs end thereof contacts stress concentration in serious unbalance loading, causes bearing to make The problem of with longevity.
Description
Technical field
The present invention relates to bearing applied technical field, the correction method and Roller Shaft of especially a kind of tapered roller bearing
It holds.
Background technique
Many key areas replace traditional straight edge line roller bearing, traditional straight edge line roller to relieved end roller bearing
Exposed earlier fatigue equivalent between the rolling element and raceway of bearing occurs often in the area on roller or raceway close to roller end
Domain, this is because there are edge concentration stress at rolling element both ends after loaded for straight edge line roller bearing, i.e., " edge effect ".Research
7 powers in the service life and stress that show bearing are inversely proportional, and the generation of " edge effect " substantially reduces the fatigue life of bearing, are
Overcome this " edge effect ", people have carried out a large amount of theoretical and experimental study.Early in the 19th-century end of the thirties
Lundberg just proposes the basic theories of bus correction of the flank shape, until the SKF Company twentieth century sixties further develops
The correction of the flank shape technology of roller bearing can avoid or reduce rolling element by using contour curved surface outside special roller and Internal and external cycle contacts
Caused edge stress is concentrated.
Currently, the modification curve used in engineering mainly has: circular curve, straight line add circular arc (to be straight in the middle part of roller bus
Line, both ends are circular arcs) and logarithmic curve.There is Chinese patent notification number to disclose one kind for the patent document of CN103810354B
The optimum design method of cylinder roller bearing logarithm modification curve first deforms logarithm modification curve equation simplification, for letter
The logarithm modification curve equation for changing deformation is handled, and is converted into optimization design to the logarithm modification curve equation for simplifying deformation
The optimization problem of a parameter in formula obtains best modification curve, however is repaired by logarithmic curve to tapered roller bearing
Shape, although middle part, than more gentle, curvature growth in end is larger, for such tapered roller bearing in serious unbalance loading situation
Under still will appear end thereof contacts stress concentration phenomenon, therefore, simple logarithm correction of the flank shape can not be fully solved tapered roller bearing
Stress concentrate and problem, cause the bearing capacity of bearing and service life limited.
Summary of the invention
The object of the present invention is to provide a kind of correction method of tapered roller bearing and roller bearings, existing right to solve
The tapered roller bearing of number correction of the flank shape, which occurs end thereof contacts stress concentration in serious unbalance loading, causes bearing service life limited
The problem of.
In order to realize the correction of the flank shape to tapered roller bearing, prevents end contact stress when gauche bearings from excessively concentrating, solve
The tapered roller bearing of existing logarithm correction of the flank shape, which occurs end thereof contacts stress concentration in serious unbalance loading, causes bearing to use the longevity
The limited problem of life, the present invention provides a kind of correction method of tapered roller bearing, using logarithmic curve to roller and raceway
Contact point is that the part for extending setting length along contact line length direction of origin carries out correction of the flank shape, utilizes quadratic polynomial curve pair
Extend the remainder except setting length and carries out correction of the flank shape.
Further, the modification curve equation of logarithmic curve and quadratic polynomial curve combining are as follows:
Wherein, x is using roller and coordinate value of the raceway contact point as origin along contact line length direction, and y is abscissa value x
Corresponding radial coordinate value, LweFor roller contact effective length, L 'weFor logarithm correction of the flank shape effective length, that is, setting length,
R is roller chamfer radius, and P is to contact full load, γ1And γ2The respectively Poisson's ratio of contact element 1 and contact element 2, E1With
E2The respectively elasticity modulus of contact element 1 and contact element 2, a, b, c are respectively the parameter of quadratic polynomial equation.
Further, according to logarithmic curve equation and quadratic polynomial equation in unbalance loading stress mutation coordinate points (x0,y0)
The slope of curve is identical with curve numerical value, and the parameters relationship for obtaining quadratic polynomial equation is as follows:
Wherein,
Further, the excellent of multiple parameters in modification curve equation is converted by the optimization design problem of modification curve
Change, the variation relation of quadratic polynomial parameter Yu distribution of contact law curve is obtained by physical simulation, by comparing
To with by the corresponding optimal parameter of correction of the flank shape element, the corresponding modification curve of the optimal parameter is best modification curve.
The roller bearing that end contact stress is not concentrated excessively when in order to realize a kind of unbalance loading solves existing logarithm correction of the flank shape and obtains
To tapered roller bearing occur end thereof contacts stress in serious unbalance loading and concentrate cause bearing service life limited to ask
Topic, the present invention provide a kind of roller bearing, which is connect with raceway contact point as the edge of origin using logarithmic curve to using roller
The part progress correction of the flank shape that line length direction extends setting length is touched, extension is set except length using quadratic polynomial curve
Remainder carries out correction of the flank shape.
Further, in the correction of the flank shape of the bearing, the modification curve equation of logarithmic curve and quadratic polynomial curve combining
Are as follows:
Wherein, x is using roller and coordinate value of the raceway contact point as origin along contact line length direction, and y is abscissa value x
Corresponding radial coordinate value, LweFor roller contact effective length, L 'weFor logarithm correction of the flank shape effective length, that is, setting length,
R is roller chamfer radius, and P is to contact full load, γ1And γ2The respectively Poisson's ratio of contact element 1 and contact element 2, E1With
E2The respectively elasticity modulus of contact element 1 and contact element 2, a, b, c are respectively the parameter of quadratic polynomial equation.
Further, in the correction of the flank shape of the bearing, according to logarithmic curve equation and quadratic polynomial equation in unbalance loading stress
It is mutated coordinate points (x0,y0) the slope of curve it is identical with curve numerical value, the parameters relationship for obtaining quadratic polynomial equation is as follows:
Wherein,
Further, in the correction of the flank shape of the bearing, modification curve equation is converted by the optimization design problem of modification curve
The optimization of multiple parameters in formula obtains the variation of quadratic polynomial parameter Yu distribution of contact law curve by physical simulation
Relationship is obtained by comparison with by the corresponding optimal parameter of correction of the flank shape element, and the corresponding modification curve of the optimal parameter is as best
Modification curve.
Detailed description of the invention
Fig. 1 is that logarithm modification curve and logarithm add multinomial modification curve roller tendency with roller bus length variation tendency
Comparison diagram；
Fig. 2 be the non-correction of the flank shape of roller bus bearing at different roller position angles inner ring contact stress change with roller bus
Tendency chart；
Fig. 3 is that the bearing of the non-correction of the flank shape of roller bus changes in the outer ring different roller position Jiao Chu contact stress with roller bus
Tendency chart；
Fig. 4 be bearing after logarithm correction of the flank shape at different roller position angles inner ring contact stress with roller bus variation tendency
Figure；
Fig. 5 be bearing after logarithm correction of the flank shape in different roller position Jiao Chu outer ring contact stress with roller bus variation tendency
Figure；
Fig. 6 be logarithm add the bearing after multinomial correction of the flank shape at different roller position angles inner ring contact stress with roller bus
Trend chart；
Fig. 7 is that logarithm adds the bearing after multinomial correction of the flank shape in the outer ring different roller position Jiao Chu contact stress with roller bus
Trend chart.
Specific embodiment
The present invention will be further described in detail with reference to the accompanying drawing.
The present invention provides a kind of roller bearing, which obtains after carrying out correction of the flank shape by a kind of correction method, the party
Method is using logarithmic curve to using roller and raceway contact point as the part for extending setting length along contact line length direction of origin
Correction of the flank shape is carried out, carries out correction of the flank shape to the remainder set except length is extended using quadratic polynomial curve.
Firstly, the modification curve equation of building roller bearing, which includes logarithmic curve equation and secondary
Polynomial equation.
It is logarithm correction of the flank shape by middle part, and both ends are known as logarithm for polynomial profiling mode and add multinomial correction of the flank shape, wherein it should
Modification curve equation are as follows:
In formula, x is using roller and coordinate value of the raceway contact point as origin along contact line length direction, and y is abscissa value x
Corresponding radial coordinate value, LweFor roller contact effective length, L 'weIt is to set length, r for logarithm correction of the flank shape effective length
For roller chamfer radius, P is to contact full load, γ1And γ2The respectively Poisson's ratio of contact element 1 and contact element 2, E1And E2
The respectively elasticity modulus of contact element 1 and contact element 2, a, b, c are respectively the parameter of quadratic polynomial equation.Wherein, if
Measured length is origin to the length between gauche bearings stress mutation point.
Then, the node coordinate for obtaining roller bearing unbalance loading stress mutation, according to logarithmic curve equation at node coordinate
The equal relationship of numerical value and slope at node coordinate of numerical value and slope and quadratic polynomial equation, be calculated secondary more
Each parameters relationship of item formula equation.
If two curves are in node coordinate (x0,y0) at link up smoothly, need to guarantee that two slopes of curve are identical and two curve numbers
It is worth equal, it may be assumed that
It is as follows that simultaneous obtains each parameters relationship:
Wherein,
It can be converted the optimization design problem of modification curve to two in modification curve equation by obtaining each parameters relationship
The multiple parameters optimization problem of order polynomial.
The optimal parameter that simulation calculation determines quadratic polynomial equation is carried out to roller bearing by physical simulation, according to institute
It states optimal parameter corresponding modification curve equation and correction of the flank shape is carried out to bearing.
By the regularity of distribution curve graph for the contact stress that Applied Physics emulation mode obtains, then by multiple groups modification curve side
The calculating analysis of journey and the comparison of distribution of contact law curve figure, optimize each parameter in modification curve equation, to obtain
It is loaded and by the corresponding best modification curve of correction of the flank shape component geometries with institute.
By taking the modification design of double row tapered roller bearing as an example, the basic parameter of the bearing are as follows: bearing radial load
92.5KN, axial load 16.8KN, bearing inner ring interior diameter 130mm, outer ring outer diameter 240mm, the wide 80mm of single-row inner ring, single-row outer ring
Wide 165mm, single-row roller number 19, roller outside diameter 27.11mm, 2 ° 27 ' of roller taper angle, roller length 53mm, effectively
Contact length 49.371mm.
The best ginseng that logarithm adds quadratic polynomial equation in multinomial correction of the flank shape is obtained by RomaxDesigner pad optimization
Number, corresponding logarithm correction of the flank shape equation are as follows:
With logarithm plus multinomial correction of the flank shape equation are as follows:
As shown in Figure 1, be two modification curve roller tendencies with roller bus length variation tendency comparison diagram, it can be with from figure
Find out that logarithm adds multinomial modification curve both ends curvature to be significantly less than logarithmic curve both ends slope.
Add multinomial correction of the flank shape equation to obtain according to above-mentioned actual logarithm correction of the flank shape equation and logarithm, is illustrated in figure 2 roller
The bearing of the non-correction of the flank shape of bus inner ring contact stress at different roller position angles is illustrated in figure 3 with roller bus variation tendency
The bearing of the non-correction of the flank shape of roller bus is in different roller position Jiao Chu outer ring contact stress with roller bus variation tendency；Such as Fig. 4 institute
Inner ring contact stress is with roller bus variation tendency at different roller position angles for bearing after being shown as logarithm correction of the flank shape, such as Fig. 5 institute
Bearing after being shown as logarithm correction of the flank shape is in different roller position Jiao Chu outer ring contact stress with roller bus variation tendency；Such as Fig. 6 institute
Be shown as logarithm add the bearing after multinomial correction of the flank shape at different roller position angles inner ring contact stress with roller bus variation tendency,
Being illustrated in figure 7 logarithm adds the bearing after multinomial correction of the flank shape to become in the outer ring different roller position Jiao Chu contact stress with roller bus
Change trend.
Fig. 2 to Fig. 7 is that the Internal and external cycle raceway at bearing difference roller position angle becomes with roller contact stress with roller bus
Change trend, wherein roller position angle is using bearing centre as polar origin, and roller is with Internal and external cycle raceway Max.contact stress
Polar axis, polar axis correspond to the direction that angle is zero, and bearing counterclockwise demarcates each roller position angle, position in Fig. 2 to Fig. 7
Angle is the roller and raceway contact stress maximum at 94.737 °.
Logarithm adds multinomial profiling mode to reduce edge stress compared to logarithm profiling mode as can be seen from Table 1, mentions
High bearing life.
Table 1
Specific embodiment of the present invention is presented above, but the present invention is not limited to described embodiment.
Under the thinking that the present invention provides, to the skill in above-described embodiment by the way of being readily apparent that those skilled in the art
Art means are converted, are replaced, are modified, and play the role of with the present invention in relevant art means it is essentially identical, realize
Goal of the invention it is also essentially identical, the technical solution formed in this way is to be finely adjusted to be formed to above-described embodiment, this technology
Scheme is still fallen in protection scope of the present invention.
Claims (8)
1. a kind of correction method of tapered roller bearing, which is characterized in that using logarithmic curve to roller and raceway contact point
Correction of the flank shape is carried out for the part for extending setting length along contact line length direction of origin, extension is set using quadratic polynomial curve
Remainder except measured length carries out correction of the flank shape.
2. the correction method of tapered roller bearing according to claim 1, which is characterized in that logarithmic curve and secondary multinomial
The modification curve equation of formula curve combining are as follows:
Wherein, x is using roller and coordinate value of the raceway contact point as origin along contact line length direction, and y is that abscissa value x institute is right
The radial coordinate value answered, LweFor roller contact effective length, L 'weFor logarithm correction of the flank shape effective length, that is, setting length, r is
Roller chamfer radius, P are to contact full load, γ1And γ2The respectively Poisson's ratio of contact element 1 and contact element 2, E1And E2Point
Not Wei contact element 1 and contact element 2 elasticity modulus, a, b, c are respectively the parameter of quadratic polynomial equation.
3. the correction method of tapered roller bearing according to claim 2, which is characterized in that according to logarithmic curve equation with
Quadratic polynomial equation is in unbalance loading stress mutation coordinate points (x0,y0) the slope of curve it is identical with curve numerical value, obtain secondary multinomial
The parameters relationship of formula equation is as follows:
Wherein,
4. the correction method of tapered roller bearing according to claim 3, which is characterized in that obtain two by physical simulation
The variation relation of order polynomial parameter and distribution of contact law curve obtains corresponding most with by correction of the flank shape element by comparison
Good parameter, the corresponding modification curve of the optimal parameter are best modification curve.
5. a kind of roller bearing, which is characterized in that the bearing is using logarithmic curve to using roller and raceway contact point as origin
Along contact line length direction extend setting length part carry out correction of the flank shape, using quadratic polynomial curve to extend setting length it
Outer remainder carries out correction of the flank shape.
6. roller bearing according to claim 5, which is characterized in that logarithmic curve and quadratic polynomial curve combining are repaired
Shape curvilinear equation are as follows:
Wherein, x is using roller and coordinate value of the raceway contact point as origin along contact line length direction, and y is that abscissa value x institute is right
The radial coordinate value answered, LweFor roller contact effective length, L 'weFor logarithm correction of the flank shape effective length, that is, setting length, r is
Roller chamfer radius, P are to contact full load, γ1And γ2The respectively Poisson's ratio of contact element 1 and contact element 2, E1And E2Point
Not Wei contact element 1 and contact element 2 elasticity modulus, a, b, c are respectively the parameter of quadratic polynomial equation.
7. roller bearing according to claim 6, which is characterized in that according to logarithmic curve equation and quadratic polynomial equation
In unbalance loading stress mutation coordinate points (x0,y0) the slope of curve it is identical with curve numerical value, obtain quadratic polynomial equation parameter close
It is as follows:
Wherein,
8. roller bearing according to claim 7, which is characterized in that by physical simulation obtain quadratic polynomial parameter with
The variation relation of distribution of contact law curve is obtained by comparison with by the corresponding optimal parameter of correction of the flank shape element, this is best
The corresponding modification curve of parameter is best modification curve.
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| Application Number | Priority Date | Filing Date | Title |
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| CN201810475193.4A CN110502765B (en) | 2018-05-17 | 2018-05-17 | Tapered roller bearing and shape modification method thereof |
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| CN201810475193.4A CN110502765B (en) | 2018-05-17 | 2018-05-17 | Tapered roller bearing and shape modification method thereof |
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| CN110502765B CN110502765B (en) | 2023-04-07 |
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Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN111291455A (en) * | 2020-03-10 | 2020-06-16 | 洛阳Lyc轴承有限公司 | Shape modification design method of self-aligning bearing roller for wind power equipment |
| CN111475895A (en) * | 2020-04-10 | 2020-07-31 | 洛阳Lyc轴承有限公司 | End arc shape-modifying method of spherical roller |
| CN115139158A (en) * | 2022-06-22 | 2022-10-04 | 洛阳理工学院 | Roller shaping method for double-row self-aligning spherical roller bearing |
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| EP1249623A1 (en) * | 2001-04-12 | 2002-10-16 | NSK Ltd., | Tapered roller bearing |
| CN103810354A (en) * | 2014-03-11 | 2014-05-21 | 大连交通大学 | Optimal design method for logarithm shaping curve of cylindrical roller bearing |
| CN104636596A (en) * | 2014-12-26 | 2015-05-20 | 中国北方车辆研究所 | Cylindrical roller bearing asymmetric shape correction method under specific loads |
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2018
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| EP1249623A1 (en) * | 2001-04-12 | 2002-10-16 | NSK Ltd., | Tapered roller bearing |
| CN103810354A (en) * | 2014-03-11 | 2014-05-21 | 大连交通大学 | Optimal design method for logarithm shaping curve of cylindrical roller bearing |
| CN104636596A (en) * | 2014-12-26 | 2015-05-20 | 中国北方车辆研究所 | Cylindrical roller bearing asymmetric shape correction method under specific loads |
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Cited By (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN111291455A (en) * | 2020-03-10 | 2020-06-16 | 洛阳Lyc轴承有限公司 | Shape modification design method of self-aligning bearing roller for wind power equipment |
| CN111291455B (en) * | 2020-03-10 | 2024-04-26 | 洛阳轴承集团股份有限公司 | Shape modification design method of self-aligning bearing roller for wind power equipment |
| CN111475895A (en) * | 2020-04-10 | 2020-07-31 | 洛阳Lyc轴承有限公司 | End arc shape-modifying method of spherical roller |
| CN111475895B (en) * | 2020-04-10 | 2023-03-24 | 洛阳Lyc轴承有限公司 | End arc shape-modifying method for spherical roller |
| CN115139158A (en) * | 2022-06-22 | 2022-10-04 | 洛阳理工学院 | Roller shaping method for double-row self-aligning spherical roller bearing |
| CN115139158B (en) * | 2022-06-22 | 2023-10-10 | 洛阳理工学院 | Roller repairing method for double-row aligning spherical roller bearing |
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Inventor after: Qiu Ming Inventor after: Niu Zhenhua Inventor after: Zhang Bin Inventor after: Wang Xinying Inventor after: Zhang Rui Inventor after: Pang Xiaoxu Inventor after: Du Hui Inventor after: Li Yingchun Inventor before: Qiu Ming Inventor before: Niu Zhenhua Inventor before: Zhang Rui Inventor before: Pang Xiaoxu Inventor before: Du Hui Inventor before: Li Yingchun |
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Effective date of registration: 20240227 Address after: No.263, Kaiyuan Avenue, Luolong District, Luoyang City, Henan Province Patentee after: HENAN University OF SCIENCE AND TECHNOLOGY Country or region after: China Patentee after: METALS & CHEMISTRY RESEARCH INSTITUTE OF CHINA ACADEMY OF RAILWAY SCIENCES Corp.,Ltd. Patentee after: Luoyang Bearing Group Co.,Ltd. Address before: 471003 No. 48, Xiyuan Road, Jianxi District, Henan, Luoyang Patentee before: HENAN University OF SCIENCE AND TECHNOLOGY Country or region before: China |