0
Research Papers: Applications

Rolling-Element Bearing Heat Transfer—Part III: Experimental Validation

[+] Author and Article Information
William M. Hannon

The Timken Company,
North Canton, OH 44720-5450
e-mail: william.hannon@timken.com

Todd A. Barr

The Timken Company,
North Canton, OH 44720-5450
e-mail: todd.barr@timken.com

Shawn T. Froelich

The Timken Company,
North Canton, OH 44720-5450
e-mail: shawn.froelich@timken.com

The Timken Bearing Syber Analysis Program calculated torque. This program calculates global and local deflection and bearing life, as well as the local rolling element contact stress, film thickness, torque, and power losses. The output of Syber is used in this work as an input to the heat transfer model.

Contributed by the Tribology Division of ASME for publication in the JOURNAL OF TRIBOLOGY. Manuscript received July 29, 2014; final manuscript received January 12, 2015; published online March 25, 2015. Assoc. Editor: Mihai Arghir.

J. Tribol 137(3), 031104 (Jul 01, 2015) (13 pages) Paper No: TRIB-14-1190; doi: 10.1115/1.4029734 History: Received July 29, 2014; Revised January 12, 2015; Online March 25, 2015

This paper concludes a series of papers outlining a new rolling-element bearing heat transfer model. Part I provided the model framework, Part II presented the partial differential equation (PDE) solutions, and Part III, this paper, presents full-scale test results for ball, cylindrical, spherical, and tapered rolling-element bearings. The results validate the heat partitioning equation and the predicted solid temperatures for circulating oil lubrication. In addition, sump lubrication was studied using an acrylic assembly. The results quantify what fraction of the bearing periphery is cooled by oil, as well as the flow of oil through a bearing. Finally, substantiation of the modeling assumptions is discussed.

Copyright © 2015 by ASME
Your Session has timed out. Please sign back in to continue.

References

Hannon, W. M., 2015, “Rolling-Element Bearing Heat Transfer—Part I: Analytic Model,” ASME J. Tribol.137(3), p. 031101. [CrossRef]
Hannon, W. M., 2015, “Rolling-Element Bearing Heat Transfer—Part II: Housing, Shaft, and Bearing Raceway Partial Differential Solutions,” ASME J. Tribol.137(3), p. 031102. [CrossRef]
Bates, S. J., Sienz, J., and Toropov, V. V., 2004, “Formulation of the Optimal Latin Hypercube Design of Experiments Using a Permutation Genetic Algorithm,” AIAA Paper No. 2004-2011, pp. 1–7. [CrossRef]
van Dam, E. R., 2008, “Two-Dimensional Minimax Latin Hypercube Designs,” CentER Discussion Paper, Tilburg University, Tilburg, The Netherlands, Vol. 156, pp. 3483–3493.
Jin, R., Chen, W., and Sudjianto, A., 2005, “An Efficient Algorithm for Constructing Optimal Design of Computer Experiments,” J. Stat. Plann. Inference, 134(1), pp. 268–287. [CrossRef]
Ye, K. Q., Li, W., and Sudjianto, A., 2000, “Algorithmic Construction of Optimal Symmetric Latin Hypercube Designs,” J. Stat. Plann. Inference, 90(1), pp. 145–159. [CrossRef]
Parker, R. J., 1984, “Comparison of Predicted and Experimental Thermal Performance of Angular Contact Ball Bearing,” NASA Technical Paper No. 2275.
Gupta, P. K., 2002, “Thermal Interactions in Rolling Bearing Dynamics,” U.S. Department of Commerce, Clifton Park, NY, Report No. ADA409914.
Pinel, S. I., Singer, H. R., and Zaretsky, E. V., 1998, “Design and Operating Characteristics of High-Speed, Small-Bore, Angular-Contact Ball Bearings,” Report No. NASA/TM 1988-206981.
Blok, H., 1937, “Theoretical Study of Temperature Rise at Surfaces of Actual Contact under Oiliness Lubrication Conditions,” Proceedings of the General Discussion on Lubrication, The Institution of Mechanical Engineers, London, Vol. 2, pp. 222–235.
Jaeger, J. C., 1942, “Moving Sources of Heat and the Temperature at Sliding Contacts,” J. Proc. R. Soc. N. S. W., 76(3), pp. 203–224.
Tian, X., and Kennedy, F. E., 1993, “Temperature Rise at the Sliding Contact Interface for a Coated Semi-Infinite Body,” ASME J. Tribol., 115(1), pp. 1–9. [CrossRef]
Tian, X., and Kennedy, F. E., 1994, “Maximum and Average Flash Temperatures in Sliding Contacts,” ASME J. Tribol., 116(1), pp. 167–174. [CrossRef]
Houpert, L., 1999, “Numerical and Analytical Calculations in Ball Bearings,” 8th European Space Mechanism and Tribology Symposium, Toulouse, France, Sept. 29, pp. 283–290.
Houpert, L., 2002, “Ball Bearing and Tapered Roller Bearing Torque: Analytical, Numerical and Experimental Results,” STLE Trib. Trans., 45(3), pp. 345–353. [CrossRef]
Biboulet, N., and Houpert, L., 2010, “Hydrodynamic Force and Moment in Pure Rolling Lubricated Contact: Part I: Line Contacts,” J. Eng. Tribol., 224(8), pp. 765–775.
Biboulet, N., and Houpert, L., 2010, “Hydrodynamic Force and Moment in Pure Rolling Lubricated Contact: Part II: Point Contacts,” J. Eng. Tribol., 224(8), pp. 777–787.
Harris, T., and Kotzalas, M. N., 2007, Advanced Concepts of Bearing Technology, 4th ed., Vol. 2, CRC Press, Boca Raton, FL, pp. 191–208.
Yovanovich, M. M., 1998, “Application of Thermal Contact Resistance Theory to Electronic Packages,” Advances in Thermal Modeling of Electronic Components and Systems, Vol. 1, A. D.Kraus, and A.Bar-Choen, eds., Hemisphere Publishing, New York, pp. 79–128.
Incropera, F. P., and Dewitt, D. P., 1985, Introduction to Heat Transfer. 3rd ed., Wiley, Jefferson City, MO.
Krieth, R., 1968, “Convection Heat Transfer in Rotating Systems,” Advances in Heat Transfer, Vol. 5, Elsevier, pp. 128–251.
Zaretsky, E. V., Singer, H. R., and Bamberger, E. N., 1974, “Operating Characteristics of 120 mm Bore Ball Bearings at 3 × 106 DN,” Report No. NASA TN D-7837.

Figures

Grahic Jump Location
Fig. 2

Test rig schematic

Grahic Jump Location
Fig. 3

Tapered bearing space filling design for load and speed

Grahic Jump Location
Fig. 4

Lubricant distribution by lubricant method

Grahic Jump Location
Fig. 5

Sump flow acrylic housing

Grahic Jump Location
Fig. 6

Ball bearing oil outlet temperature—predicted versus experiment

Grahic Jump Location
Fig. 7

Ball bearing oil outlet percent error—predicted versus experiment

Grahic Jump Location
Fig. 8

Cylindrical bearing oil outlet temperature—predicted versus Experiment

Grahic Jump Location
Fig. 9

Cylindrical bearing oil outlet percent error—predicted versus experiment

Grahic Jump Location
Fig. 10

Spherical bearing oil outlet temperature—predicted versus experiment

Grahic Jump Location
Fig. 11

Spherical bearing oil outlet percent error—predicted versus experiment

Grahic Jump Location
Fig. 12

Tapered bearing oil outlet temperature—predicted versus experiment

Grahic Jump Location
Fig. 13

Tapered bearing oil outlet percent error—predicted versus experiment

Grahic Jump Location
Fig. 14

Bearing raceway radial boundary condition

Grahic Jump Location
Fig. 15

Predicted results for the first row of the first spherical bearing (refer Fig. 2). Predicted outer raceway temperature: (a) at r = R3 and (b) in the load zone. (c) Predicted inner raceway temperature at r = R2 and (d) predicted inner raceway temperature.

Grahic Jump Location
Fig. 16

Predicted results for the first row of the third spherical bearing (refer Fig. 2). Predicted outer raceway temperature: (a) at r = R3 and (b) in the load zone. (c) Predicted inner raceway temperature at r = R2 and (d) predicted inner raceway temperature.

Grahic Jump Location
Fig. 17

Thermal model—actual by predicted results

Grahic Jump Location
Fig. 18

Bearing convection-coefficient

Grahic Jump Location
Fig. 19

Fluorescent lubricant illumination within the bearing, under rotation. (Rotation is bottom-up or counterclockwise when viewed from the left end of the shaft.) (a) 0 rpm, (b) 100 rpm, (c) 250 rpm, and (d) 500 rpm.

Grahic Jump Location
Fig. 20

High-speed photograph of sump-driven flow

Grahic Jump Location
Fig. 21

Oil height along the bearing periphery. Static percent fill: (a) 12.5%–160 cSt, (b) 25%–160 cSt, and (c) 50%–160 cSt.

Grahic Jump Location
Fig. 22

Dye injection into sump oil at 250 rpm. Images (a)–(d) were obtained when the static-assembly sump was 25% full of 160 cSt oil. (a) t = 0 s, (b) t = 2 s, (c) t = 4 s, and (a) t = 6 s. (a) Images (e)–(h) were obtained when the static-assembly sump was 12.5% full of 10 cSt oil. (e) t = 0 s, (f) t = 2 s, (g) t = 4 s, and (h) t = 6 s.

Grahic Jump Location
Fig. 23

Acrylic housing with grease; rotation speed of 250 rpm

Grahic Jump Location
Fig. 24

In-rotation cylindrical bearing percent fill

Tables

Errata

Discussions

Related

Some tools below are only available to our subscribers or users with an online account.

Related Content

Customize your page view by dragging and repositioning the boxes below.

Related Journal Articles
Related eBook Content
Topic Collections

Sorry! You do not have access to this content. For assistance or to subscribe, please contact us:

  • TELEPHONE: 1-800-843-2763 (Toll-free in the USA)
  • EMAIL: asmedigitalcollection@asme.org
Sign In