Friction Moment of Radial Ball Bearing under Thrust Load

Kakuta, Kazuo

doi:10.1299/kikai1938.27.945

Cited by 16 publications

(10 citation statements)

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“…Based on Kakuta's study, 16,17 when considering the sign of the friction force in the forward process (V > 0) and the return process (V < 0) in the experiment (see ''Experimental method'' section), the friction force F 0 Dij due to differential slip between the jth ball in the ith row and a rail raceway groove can be written as…”

Section: Friction Forcesmentioning

confidence: 99%

“…3 In addition, they studied the relationship between the friction variation and rolling surface waviness. 4 Kasai et al 5 applied the friction calculation method for rotary type ball bearings by Kakuta 16,17 to estimate the friction force of linear guideway type ball bearings (shown in Figure 1(b)). They pointed out that the total friction force of linear guideway type ball bearings in low-speed operation was the sum of the friction forces due to the differential slip and elastic hysteresis.…”

Section: Introductionmentioning

confidence: 99%

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Effects of misaligned rails on the friction force–displacement curves of a linear ball bearing system in low-speed operation

Ohta

Sato

Ueki³

2015

Proceedings of the Institution of Mechanical Engineers, Part J:

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This paper investigates the effects of misaligned rails on the friction force-displacement curves of a linear ball bearing system (which consists of two sets of deep groove type non-recirculating linear ball bearings, a table and a bed). Experiments showed that the measured friction force-displacement curves, of the linear ball bearing system, with aligned rails were rectangular-shaped hysteresis loops, while the corresponding curves with misaligned rails were trapezoidalshaped hysteresis loops. In addition, the hysteresis loop area increased as the distance between table side rails decreased. Next, calculations for the total friction force expression due to differential slip and elastic hysteresis loss, including the effects of the misaligned rails, are presented. It was confirmed that the calculated total friction force-displacement curves closely matched the measured friction force-displacement curves for both the aligned and misaligned rail cases.

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Section: Friction Forcesmentioning

confidence: 99%

Section: Introductionmentioning

confidence: 99%

Effects of misaligned rails on the friction force–displacement curves of a linear ball bearing system in low-speed operation

Ohta

Sato

Ueki³

2015

Proceedings of the Institution of Mechanical Engineers, Part J:

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“…The torque produced by elastic hysteresis is found as proposed by Kakuta in a study of friction moments in ball bearings [14]:…”

Section: Consideration Of Elastic Hysteresismentioning

confidence: 99%

“…When the balls in a bearing roll on the race surface under a load, the energy of elastic deformation is dissipated as heat, thus causing an elastic hysteresis loss, which is added to the bearing torque. The torque produced by elastic hysteresis is found as proposed by Kakuta in a study of friction moments in ball bearings [14]:…”

Section: Consideration Of Elastic Hysteresismentioning

confidence: 99%

Bearing Resistance of Wind Turbine Generator System

Aso

Aida

Seki³

2015

Electrical Engineering Japan

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SUMMARY The vertical axis wind turbine generator is mainly used for small size wind turbine applications, and is independent of wind direction. Its rotating part (shaft unit) should be rotated by an extremely small torque so as to increase the generation efficiency. However, commercially available bearings are not necessarily suitable for the shaft unit because their static and dynamic load ratings are frequently larger than those required for the vertical axis wind turbine. As a result, the frictional force and the rotating torque of commercially available bearings are too large for the shaft unit to rotate lightly. In this study, through an experiment with an actual vertical axis wind turbine, the bearings used for the shaft unit are reviewed in accordance with IEC61400‐2. Design of a shaft unit with the bearings having the most suitable load rating and frictional force for the vertical axis wind turbine is attempted. The newly designed shaft unit will be applied to the vertical axis wind turbine and will be tested.

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“…The formula of the friction moment given by equation 8seems to be unreasonable from the standpoint of the author's work [4]. 6 Especially under radial load, it must be considered another cause of friction that is the differential slip friction loss, at the same time including the dissipating mechanisms of (a), (ft), and (c), from which a reasonable explanation for Prof. Reichenbach's question may be led.…”

Section: Author's Closurementioning

confidence: 99%

Discussion: “The Effects of Misalignment on the Forces Acting on the Retainer of Ball Bearings” (Kakuta, K., 1964, ASME J. Basic Eng., 86, pp. 449–454)

Reichenbach

1964

Journal of Basic Engineering

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zero. Hence the retainer rotates concentricalty with the bearing axia and does not contact the races. But as shown in Fig. 18, on the sides of the retainer, the repeated compressive and tensile stresses due to the ball-to-retainer forces must occur, and from the cause of those stresses the fatigue rupture in the retainer may appear. This phenomenon was confirmed by the many endurance tests under pure moment load for radial ball bearings having two piece pressed retainers. In the tests, after the total revolutions of the shaft reached over about 10 6 , the retainers failed in rupture and the fractured surfaces produced were the brittle ones as in fatigue ruptures.

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Friction Moment of Radial Ball Bearing under Thrust Load

Cited by 16 publications

References 0 publications

Effects of misaligned rails on the friction force–displacement curves of a linear ball bearing system in low-speed operation

Effects of misaligned rails on the friction force–displacement curves of a linear ball bearing system in low-speed operation

Bearing Resistance of Wind Turbine Generator System

Discussion: “The Effects of Misalignment on the Forces Acting on the Retainer of Ball Bearings” (Kakuta, K., 1964, ASME J. Basic Eng., 86, pp. 449–454)

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