Design of Spur Gears Using Profile Modification

Sachidananda, H. K.; Raghunandana, K; Gonsalvis, Joseph

doi:10.1080/10402004.2015.1010762

Cited by 17 publications

(8 citation statements)

References 16 publications

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“…The scanning electron microphotographs are taken at pitch circle area. The morphological results of points B (LPSTC) and D (HPSTC) were studied and published earlier by the authors . According to that, as per the consideration of only contact stress, points B (LPSTC) and D (HPSTC) are critical.…”

Section: Methodsmentioning

confidence: 99%

“…In this context, the authors have shown the shifting of maximum contact stresses along the length of contact for various profile shifts [19][20][21] for a tooth sum of 100 (altered by ±4% with a standard centre distance and gear ratio of 1 : 1), but the effect of sliding velocity has not been taken into consideration in previous studies. In view of this research gap, the (σ V s ) factor has been analysed in this investigation for tooth sum for various profile shifts mentioned in the preceding texts.…”

Section: Estimation Of Contact Stressmentioning

confidence: 99%

“…The morphological results of points B (LPSTC) and D (HPSTC) were studied and published earlier by the authors. 21 According to that, as per the consideration of only contact stress, points B (LPSTC) and D (HPSTC) are critical. At these points, it was also found that the negative-altered tooth-sum gear was better as compared with standard and positive-altered tooth-sum gears.…”

Section: Morphological Investigation Of Tested Gear Tooth Surfacementioning

confidence: 99%

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Sliding velocity in profile‐corrected gears

Sachidananda

Raghunandana

Gonsalvis³

2016

Lubrication Science

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The effects of sliding velocity in a spur gear for a tooth sum of 100 (altered by ±4%) with constant centre distance have been studied. The product of contact stress and sliding velocity (σ Vs) factor is calculated for varied profile shift. The effect of Hertzian compression, bending and shear deflection on sliding velocity at points along length of the path of contact has been computed. The scanning electron micrographs at pitch point C show that negative alteration in tooth‐sum gears is better compared with standard and positive alterations in tooth sum. Copyright © 2016 John Wiley & Sons, Ltd.

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Section: Methodsmentioning

confidence: 99%

Section: Estimation Of Contact Stressmentioning

confidence: 99%

Section: Morphological Investigation Of Tested Gear Tooth Surfacementioning

confidence: 99%

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Sliding velocity in profile‐corrected gears

Sachidananda

Raghunandana

Gonsalvis³

2016

Lubrication Science

Self Cite

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“…1 In order to improve the quality of gear meshing, tooth surfaces with different orders of transmission errors are obtained by gear profile modification technique. [2][3][4] Experimentation and practice show that gear transmission system with higher order polynomial function of transmission error (H-TE) has lower vibration, better noise performance, and more reliable stability compared to the second-order parabolic function of transmission error (2-TE) system. Due to the interference in the machining process when tooth surface with higher order transmission error than sixth-order polynomial function of transmission error (6H-TE), tooth surface with 6H-TE was selected as the study object.…”

Section: Introductionmentioning

confidence: 99%

Design and analysis of herringbone gear with sixth-order transmission error based on meshing vibration optimization

Wang

Fang

et al. 2017

Advances in Mechanical Engineering

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To reduce the herringbone gear transmission vibration and noise, an optimization design method about the meshing vibration of herringbone gear is provided with a controllable sixth-order polynomial function of transmission error. First, the polynomial coefficients of sixth-order polynomial function of transmission error curves can be determined by optimizing the aim at minimum root mean square value of herringbone gear meshing vibration acceleration based on loaded tooth contact analysis method and herringbone gear vibration model. Second, because of the existence of second-order frequency factors in the amplitude of loaded transmission error, the root mean square value of meshing vibration acceleration under the optimization of amplitude of loaded transmission error is worse than the value under the optimization of meshing vibration acceleration in resonant frequency. Third, a numerical simulation of example based on herringbone gear with different order transmission errors is performed, which proves that the herringbone gear train with sixthorder polynomial function of transmission error has the lowest root mean square value of meshing vibration acceleration in the design loads' range. This study provides evidence that the proposed herringbone gear train with sixth-order polynomial function of transmission error has the significantly better performances in vibration reduction and smooth transmission than that with fourth-order polynomial function of transmission error and second-order parabolic function of transmission error.

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“…Thus, conducting simulations and evaluating the performance of the gear pair with tooth profile modification are difficult. Sachidananda et al [14] proposed a method to calculate the contact stress of the modified gear pair. However, this method is not suitable for calculating the bending stress.…”

Section: State Of the Artmentioning

confidence: 99%

Tooth Profile Modification and Simulation Analysis of Involute Spur Gear

Li¹,

Wang²,

Lv³

2016

Int. j. simul. model.

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The spur gear mechanism with the standard involute profile may generate noise and shock because of tooth structure and transmission principle, resulting in substantial transmission errors. These limitations can be effectively resolved through tooth profile modification. To address the defects and deficiencies of existing tooth profile modification methods in terms of the modification principle and effect assessment, this study proposes an adaptive method of tooth profile modification with alterable tooth profile for spur gear mechanism. A corresponding simulation method for evaluating the modification performance of the gear transmission was introduced in detail. The final shape parameters of the modification profile were determined by orthogonal experiments. Simulation results show that tooth profile modification for involute spur gear does not affect bending and contact stresses. The process can also effectively improve the stability of transmission. The impact and noise of gear pair with tooth profile modification significantly decreased during meshing. The proposed method exhibits stronger adaptability compared with other existing methods of tooth profile modification. Moreover, the proposed method can adaptively determine the optimal modification parameters based on different conditions and obtain the ideal modification effect.

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Design of Spur Gears Using Profile Modification

Cited by 17 publications

References 16 publications

Sliding velocity in profile‐corrected gears

Sliding velocity in profile‐corrected gears

Design and analysis of herringbone gear with sixth-order transmission error based on meshing vibration optimization

Tooth Profile Modification and Simulation Analysis of Involute Spur Gear

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