CN104965946A - Finite element calculation method for steady temperature field of high-speed railway bearing - Google Patents
Finite element calculation method for steady temperature field of high-speed railway bearing Download PDFInfo
- Publication number
- CN104965946A CN104965946A CN201510366935.6A CN201510366935A CN104965946A CN 104965946 A CN104965946 A CN 104965946A CN 201510366935 A CN201510366935 A CN 201510366935A CN 104965946 A CN104965946 A CN 104965946A
- Authority
- CN
- China
- Prior art keywords
- bearing
- finite element
- heat
- high ferro
- steady
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Pending
Links
Landscapes
- Rolling Contact Bearings (AREA)
Abstract
The present invention discloses a finite element calculation method for a steady temperature field of a high-speed railway bearing. The method comprises: first, selecting a two-rowed conical roller bearing for a high-speed railway as a study object, and establishing a two-dimensional model in solidwork software; second, establishing a bearing system heat transfer model and replacing the heat dissipation of a bearing seat, a bearing and a shaft with heat flow quantity according to a work condition and a bearing system parameter of the high-speed railway bearing; loading a convection heat dissipation coefficient of the bearing seat, the bearing and the shaft relative to the bearing on a work surface, and furthermore, converting a study on a temperature field of a bearing system into a study on the temperature field of a bearing assembly; then, calculating a heating amount of the bearing according to a bearing friction torque; then calculating an air convection heat transfer coefficient, convection coefficients of the shaft and the bearing, a lubricant convection coefficient and a convection heat transfer coefficient of the outer surface of the bearing seat; then calculating external heat dissipating quantity; and finally, establishing a finite element model of the high-speed railway bearing and allocating heat sources.
Description
Technical field
The present invention relates to high ferro bearing computing method field, specifically a kind of finite element method of high ferro bearing Steady-State Thermal Field.
Background technology
Bullet train axle box bearing is the important foundation parts of high-speed railway.Compared with other industrial bearings, bullet train axle box bearing more emphasizes the research of security technique.Under the operating mode of high speed, heavy duty, temperature rise and temperature distribution state directly affect serviceability, the serviceable life of main shaft-bearing system, and even the safe operation of full car.
Along with the development of bearing material, under high temperature, the inefficacy of lubricant has become the bottleneck in restriction bearing serviceable life and stability.Thermoanalytical status highlights day by day, but correlative study both at home and abroad can not show a candle to quiet, dynamics research is ripe.Thus the design and R&D important in inhibiting of temperature field for high ferro bearing of high ferro bearing is analyzed.
Heat of friction under bearing runs up and Temperature Distribution calculate very complicated, and the Heating mechanism coming from bearing is on the one hand very complicated, and the heat transfer and the radiation processes that come from bearing are on the other hand uncertain.Pertinent literature both domestic and external is less, in general often uses hot-fluid network technique or finite element method.The hot-fluid network technique such as Pouly and Nicolas analyzes the distribution of bearing steady temperature, but hot-fluid network technique needs to solve a large amount of equations, and can only obtain the discrete data of bearing temperature.Finite element method have dividing elements flexibly, finite element model and the feature such as structural model is unified, and the distribution of part bulk temperature can be solved.If but consider that oil film is on the impact of bearing, finite element analysis is carried out again after then first must simulating the kinetic characteristic of lubricant in fluid analysis software is as FLUENT, the stress and strain model of oil film very easily causes oil film to penetrate, and huge calculated amount adds the working time again undoubtedly.In addition, utilizing finite element method to carry out in the process of numerical simulation to bearing temperature field, thermal source solve the definition etc. with allocation scheme, edge-restraint condition, be several key issues that researchist needs deep understanding and resolves.
Summary of the invention
The object of this invention is to provide a kind of finite element method of high ferro bearing Steady-State Thermal Field, to solve prior art Problems existing.
In order to achieve the above object, the technical solution adopted in the present invention is:
A finite element method for high ferro bearing Steady-State Thermal Field, is characterized in that: comprise the following steps:
(1), with double-row conical bearing used for high-speed railway for research object, in solidwork software, two dimensional model is set up;
(2) bearing arrangement heat transfer model, is set up, according to operating mode and the bearing arrangement parameter of high ferro bearing, the heat radiation of bearing seat, bearing, axle is replaced by heat flux, bearing seat, axle and oil film are loaded on working surface relative to the heat loss through convection coefficient of bearing, and then the Study on Temperature Field of bearing arrangement is converted into the Study on Temperature Field to bearing assembly;
(3), calculation bearing thermal value is carried out according to bearing frictional torque;
(4), the cross-ventilation coefficient of heat transfer is calculated, the convection coefficient of axle and bearing, lubricant convection coefficient, the convection transfer rate of bearing seat outside surface;
(5), extraneous heat dissipation capacity is calculated;
(6), set up the finite element model of high ferro bearing, and distribute thermal source and solve, obtain the Numerical Simulation Results of Steady-State Thermal Field.
The finite element method of described a kind of high ferro bearing Steady-State Thermal Field, it is characterized in that: in step (2), the heat transfer model of bearing arrangement is the heat transfer model of bearing seat, outer ring, taper roller, inner ring, tubular shaft, air, oil film.
The finite element method of described a kind of high ferro bearing Steady-State Thermal Field, is characterized in that: in step (3), bearing heating amount is calculated as:
H
tot＝1.047×10
-4nM，
Wherein, n is rotating speed, M=M
r+ M
a+ M
v,
M
rfor only having the moment of friction of radial load, computing formula is:
M
r＝3.35×10
-6G(nν
0)
1/2(f
tF
r/K)
1/3，
M
afor the moment of friction of axial load, computing formula is:
M
a＝3.35×10
-6G(nν
0)
1/3F
a 1/3，
M
vfor the viscous friction moment that lubricant causes, computing formula is:
Wherein, G is sliding friction variable, and n is rotating speed, ν
0for lubricant kinematic viscosity under working temperature, f
rfor friction factor, F
rfor radial load size, K is bearing type constant, F
afor axial load size, f
0for friction factor, d
mfor the mean diameter of bearing;
The finite element method of described a kind of high ferro bearing Steady-State Thermal Field, it is characterized in that: in step (5), extraneous heat dissipation capacity computing formula is:
Q＝2πλlΔt/In(d
2/d
1)，
Wherein, λ is the thermal conductivity of material, and l is bearing seat length, and Δ t is temperature variation, d
2for bearing seat external diameter; d
1for warp in bearing seat.
The finite element method of described a kind of high ferro bearing Steady-State Thermal Field, it is characterized in that: in step (6), the finite element model of high ferro bearing adopts free mesh, contact area local refinement between roller and Internal and external cycle, heating part between roller and Internal and external cycle adopts face load, boundary condition is thermal convection, and Internal and external cycle heat radiation adopts negative heat flux.
The finite element method of described a kind of high ferro bearing Steady-State Thermal Field, it is characterized in that: in step (6), thermal source allocation scheme is: with roller and Internal and external cycle for thermal source but the different load mode of temperature, but uneven for heat is allocated in bearing roller and Internal and external cycle, and the heat of two place's contact areas is higher than the region do not contacted.
The present invention, compared with traditional hot-fluid network technique, avoids a large amount of equation solutions, and can obtain monolithic stability distribution situation, for the optimal design of high ferro bearing provides foundation.
Accompanying drawing explanation
Fig. 1 is double-row conical bearing two dimensional model used for high-speed railway.
Fig. 2 is bearing arrangement heat transfer model.
Embodiment
A finite element method for high ferro bearing Steady-State Thermal Field, embodiment comprises the following steps:
(1), with double-row conical bearing used for high-speed railway for research object, in solidwork software, two dimensional model is set up, as shown in Figure 1.
(2) bearing arrangement heat transfer model, is set up, as shown in Figure 2, mainly comprise bearing seat, outer ring, taper roller, inner ring, tubular shaft, air, oil film etc., according to operating mode and the bearing arrangement parameter of high ferro bearing, the heat radiation of bearing seat, bearing, axle is replaced by heat flux, bearing seat, axle and oil film are loaded on working surface relative to the heat loss through convection coefficient of bearing, and then the Study on Temperature Field of bearing arrangement is converted into the Study on Temperature Field to bearing assembly.
(3), calculation bearing thermal value is carried out according to bearing frictional torque; Bearing heating amount is calculated as:
H
tot＝1.047×10
-4nM，
Wherein, n is rotating speed, M=M
r+ M
a+ M
v,
M
rfor only having the moment of friction of radial load, computing formula is:
M
r＝3.35×10
-6G(nν
0)
1/2(f
tF
r/K)
1/3，
M
afor the moment of friction of axial load, computing formula is:
M
a＝3.35×10
-6G(nν
0)
1/3F
a 1/3，
M
vfor the viscous friction moment that lubricant causes, computing formula is:
Wherein, G is sliding friction variable, and n is rotating speed, ν
0for lubricant kinematic viscosity under working temperature, f
rfor friction factor, F
rfor radial load size, K is bearing type constant, F
afor axial load size, f
0for friction factor, d
mfor the mean diameter of bearing;
(4), the cross-ventilation coefficient of heat transfer is calculated, the convection coefficient of axle and bearing, lubricant convection coefficient, the convection transfer rate of bearing seat outside surface;
(5), calculate extraneous heat dissipation capacity, computing formula is:
Q=2 π λ l Δ t/In (d
2/ d
1)
,wherein, λ is the thermal conductivity of material, and l is bearing seat length, and Δ t is temperature variation, d
2for bearing seat external diameter; d
1for warp in bearing seat.
(6), set up the finite element model of high ferro bearing, and distribute thermal source and solve, obtain the Numerical Simulation Results of Steady-State Thermal Field.
Wherein, the finite element model of high ferro bearing adopts free mesh, the contact area local refinement between roller and Internal and external cycle, and the heating part between roller and Internal and external cycle adopts face load, and boundary condition is thermal convection, and Internal and external cycle heat radiation adopts negative heat flux;
Thermal source allocation scheme is: with roller and Internal and external cycle for thermal source but the different load mode of temperature, but uneven for heat is allocated in bearing roller and Internal and external cycle, and the heat of two place's contact areas is higher than the region do not contacted.
Claims (6)
1. a finite element method for high ferro bearing Steady-State Thermal Field, is characterized in that: comprise the following steps:
(1), with double-row conical bearing used for high-speed railway for research object, in solidwork software, two dimensional model is set up;
(2) bearing arrangement heat transfer model, is set up, according to operating mode and the bearing arrangement parameter of high ferro bearing, the heat radiation of bearing seat, bearing, axle is replaced by heat flux, bearing seat, axle and oil film are loaded on working surface relative to the heat loss through convection coefficient of bearing, and then the Study on Temperature Field of bearing arrangement is converted into the Study on Temperature Field to bearing assembly;
(3), calculation bearing thermal value is carried out according to bearing frictional torque;
(4), the cross-ventilation coefficient of heat transfer is calculated, the convection coefficient of axle and bearing, lubricant convection coefficient, the convection transfer rate of bearing seat outside surface;
(5), extraneous heat dissipation capacity is calculated;
(6), set up the finite element model of high ferro bearing, and distribute thermal source and solve, obtain the Numerical Simulation Results of Steady-State Thermal Field.
2. the finite element method of a kind of high ferro bearing Steady-State Thermal Field according to claim 1, it is characterized in that: in step (2), the heat transfer model of bearing arrangement is the heat transfer model of bearing seat, outer ring, taper roller, inner ring, tubular shaft, air, oil film.
3. the finite element method of a kind of high ferro bearing Steady-State Thermal Field according to claim 1, is characterized in that: in step (3), bearing heating amount is calculated as:
H
tot＝1.047×10
-4nM，
Wherein, n is rotating speed, M=M
r+ M
a+ M
v, M
rfor only having the moment of friction of radial load, M
afor the moment of friction of axial load, M
vfor the viscous friction moment that lubricant causes.
4. the finite element method of a kind of high ferro bearing Steady-State Thermal Field according to claim 1, it is characterized in that: in step (5), extraneous heat dissipation capacity computing formula is:
Q＝2πλlΔt/In(d
2/d
1)，
Wherein, λ is the thermal conductivity of material, and l is bearing seat length, and Δ t is temperature variation, d
2for bearing seat external diameter; d
1for warp in bearing seat.
5. the finite element method of a kind of high ferro bearing Steady-State Thermal Field according to claim 1, it is characterized in that: in step (6), the finite element model of high ferro bearing adopts free mesh, contact area local refinement between roller and Internal and external cycle, heating part between roller and Internal and external cycle adopts face load, boundary condition is thermal convection, and Internal and external cycle heat radiation adopts negative heat flux.
6. the finite element method of a kind of high ferro bearing Steady-State Thermal Field according to claim 1, it is characterized in that: in step (6), thermal source allocation scheme is: with roller and Internal and external cycle for thermal source but the different load mode of temperature, but uneven for heat is allocated in bearing roller and Internal and external cycle, and the heat of two place's contact areas is higher than the region do not contacted.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201510366935.6A CN104965946A (en) | 2015-06-26 | 2015-06-26 | Finite element calculation method for steady temperature field of high-speed railway bearing |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201510366935.6A CN104965946A (en) | 2015-06-26 | 2015-06-26 | Finite element calculation method for steady temperature field of high-speed railway bearing |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN104965946A true CN104965946A (en) | 2015-10-07 |
Family
ID=54219983
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201510366935.6A Pending CN104965946A (en) | 2015-06-26 | 2015-06-26 | Finite element calculation method for steady temperature field of high-speed railway bearing |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN104965946A (en) |
Cited By (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN108038268A (en) * | 2017-11-18 | 2018-05-15 | 西安交通大学 | GIL running temperature appraisal procedures in a kind of corridor pipe |
| CN110321602A (en) * | 2019-06-17 | 2019-10-11 | 大连理工大学 | A kind of mining magnetic coupler whole audience temperature computation method |
| CN110726495A (en) * | 2019-10-25 | 2020-01-24 | 中铁工程服务有限公司 | System and method for testing temperature field of shield main bearing |
| CN110781629A (en) * | 2019-11-20 | 2020-02-11 | 桂林理工大学 | Method and system for determining convection heat dissipation coefficient |
| CN112287482A (en) * | 2020-10-28 | 2021-01-29 | 南京航空航天大学 | Method and system for calculating convection heat transfer coefficient of ball bearing |
| CN113312728A (en) * | 2021-06-24 | 2021-08-27 | 南京航空航天大学 | Flow field simulation method and system in oil loss process of double-row tapered roller bearing |
| CN113392559A (en) * | 2021-06-24 | 2021-09-14 | 南京航空航天大学 | Method and system for calculating temperature field of double-row tapered roller bearing in oil loss process |
Citations (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN102867088A (en) * | 2012-09-12 | 2013-01-09 | 西安交通大学 | Thermal network modeling method applied to electric spindle steady temperature field |
| CN103366050A (en) * | 2013-06-25 | 2013-10-23 | 华中科技大学 | High-speed electric spindle power-heat coupling modeling method |
-
2015
- 2015-06-26 CN CN201510366935.6A patent/CN104965946A/en active Pending
Patent Citations (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN102867088A (en) * | 2012-09-12 | 2013-01-09 | 西安交通大学 | Thermal network modeling method applied to electric spindle steady temperature field |
| CN103366050A (en) * | 2013-06-25 | 2013-10-23 | 华中科技大学 | High-speed electric spindle power-heat coupling modeling method |
Non-Patent Citations (3)
| Title |
|---|
| 冯军: "《高铁轴承试验机陪试轴承散热分析》", 《中国优秀硕士学位论文全文数据库 工程科技II辑》 * |
| 李凌鑫: "《高铁轴承试验台陪试轴承温度场特性及散热方法研究》", 《中国优秀硕士学位论文全文数据库 工程科技II辑》 * |
| 邢喆: "《列车轴箱轴承的可靠性稳健设计》", 《中国优秀硕士学位论文全文数据库 工程科技II辑》 * |
Cited By (12)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN108038268A (en) * | 2017-11-18 | 2018-05-15 | 西安交通大学 | GIL running temperature appraisal procedures in a kind of corridor pipe |
| CN108038268B (en) * | 2017-11-18 | 2020-06-02 | 西安交通大学 | Method for evaluating GIL (general in-lane) running temperature in corridor |
| CN110321602A (en) * | 2019-06-17 | 2019-10-11 | 大连理工大学 | A kind of mining magnetic coupler whole audience temperature computation method |
| CN110321602B (en) * | 2019-06-17 | 2020-12-11 | 大连理工大学 | Full-field temperature calculation method for mine magnetic coupler |
| CN110726495A (en) * | 2019-10-25 | 2020-01-24 | 中铁工程服务有限公司 | System and method for testing temperature field of shield main bearing |
| CN110781629A (en) * | 2019-11-20 | 2020-02-11 | 桂林理工大学 | Method and system for determining convection heat dissipation coefficient |
| CN112287482A (en) * | 2020-10-28 | 2021-01-29 | 南京航空航天大学 | Method and system for calculating convection heat transfer coefficient of ball bearing |
| CN112287482B (en) * | 2020-10-28 | 2024-05-14 | 南京航空航天大学 | Method and system for calculating convection heat exchange coefficient of ball bearing |
| CN113312728A (en) * | 2021-06-24 | 2021-08-27 | 南京航空航天大学 | Flow field simulation method and system in oil loss process of double-row tapered roller bearing |
| CN113392559A (en) * | 2021-06-24 | 2021-09-14 | 南京航空航天大学 | Method and system for calculating temperature field of double-row tapered roller bearing in oil loss process |
| CN113392559B (en) * | 2021-06-24 | 2024-05-28 | 南京航空航天大学 | Calculation method and system for temperature field of double-row tapered roller bearing in oil loss process |
| CN113312728B (en) * | 2021-06-24 | 2024-06-11 | 南京航空航天大学 | Flow field simulation method and system in oil loss process of double-row tapered roller bearing |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| CN104965946A (en) | Finite element calculation method for steady temperature field of high-speed railway bearing | |
| Brown et al. | ‘Melt welt’mechanism of extreme weakening of gabbro at seismic slip rates | |
| Patil et al. | Dynamic structural and thermal characteristics analysis of oil-lubricated multi-speed transmission gearbox: Variation of load, rotational speed and convection heat transfer | |
| CN110096784A (en) | A kind of quick calculating and design method of the bush(ing) bearing with axial pressure difference | |
| Kyrkou et al. | Simulation of thermo-hydrodynamic behavior of journal bearings, lubricating with commercial oils of different performance | |
| Iqbal et al. | Frictional power loss in solid‐grease‐lubricated needle roller bearing | |
| Hao et al. | Thermal-fluid-solid coupling in thermal characteristics analysis of rolling bearing system under oil lubrication | |
| Xie et al. | Thermal behavior of multidisk friction pairs in hydroviscous drive considering inertia item | |
| Wang et al. | Impact of brake pad structure on temperature and stress fields of brake disc | |
| Chen et al. | Prediction and optimization of lubrication performance for a transfer case based on computational fluid dynamics | |
| Yu et al. | Thermodynamic differences of different friction pairs in a multidisc clutch caused by spline friction: Numerical simulation and experimental verification | |
| Zhang et al. | Effect on friction performance of mining wet brake under different working conditions | |
| Gao et al. | Analysis and experimental research on the fluid–solid coupled heat transfer of high-speed motorized spindle bearing under oil–air lubrication | |
| Koranteng et al. | Effect of contact geometry on temperature field distribution and thermal buckling of an in-wheel disc brake system | |
| Wang et al. | Wet multi-disc friction components heat dissipation capability and optimal oil supply under continuous braking condition | |
| Xu et al. | Calculation and finite element analysis of the temperature field for high-speed rail bearing based on vibrational characteristics | |
| CN106289782A (en) | A kind of Thrust Bearing Test Rig hydraulic loading device | |
| Flouros | The impact of oil and sealing air flow, chamber pressure, rotor speed, and axial load on the power consumption in an aeroengine bearing chamber | |
| Wang et al. | Simulation and experimental study on the influence of oil groove structure on the drag torque of the wet clutch | |
| Zhu et al. | Influence of lubricant supply on thermal and efficient performances of a gear reducer for electric vehicles | |
| Dotsenko et al. | Experimental Determination of Power Losses in Steel and Hybrid Rolling Bearings | |
| Sun et al. | Comparing of temperatures of rolling bearing under the oil-air lubrication to the spray lubrication | |
| Czaban | CFD analysis of non-Newtonian and non-isothermal lubrication of hydrodynamic conical bearing | |
| Liu et al. | Application of computerized numerical modeling in multi-state wet wheel hub heat simulations | |
| CN206111704U (en) | Thrust bearing test bench hydraulic loading device |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| C06 | Publication | ||
| PB01 | Publication | ||
| C10 | Entry into substantive examination | ||
| SE01 | Entry into force of request for substantive examination | ||
| RJ01 | Rejection of invention patent application after publication |
Application publication date: 20151007 |
|
| RJ01 | Rejection of invention patent application after publication |