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Journal articles on the topic 'FRICTIONAL TORQUE'

Author: Grafiati
Published: 11 September 2023

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1

Xu, Zhujing, Zubin Jacob, and Tongcang Li. "Enhancement of rotational vacuum friction by surface photon tunneling." Nanophotonics 10, no. 1 (September 18, 2020): 537–43. http://dx.doi.org/10.1515/nanoph-2020-0391.

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AbstractWhen a neutral sphere is rotating near a surface in vacuum, it will experience a frictional torque due to quantum and thermal electromagnetic fluctuations. Such vacuum friction has attracted many interests but has been too weak to be observed. Here we investigate the vacuum frictional torque on a barium strontium titanate (BST) nanosphere near a BST surface. BST is a perovskite ferroelectric ceramic that can have large dielectric responses at GHz frequencies. At resonant rotating frequencies, the mechanical energy of motion can be converted to electromagnetic energy through resonant photon tunneling, leading to a large enhancement of the vacuum friction. The calculated vacuum frictional torques at resonances at sub-GHz and GHz frequencies are several orders larger than the minimum torque measured by an optically levitated nanorotor recently, and are thus promising to be observed experimentally. Moreover, we calculate the vacuum friction on a rotating sphere near a layered surface for the first time. By optimizing the thickness of the thin-film coating, the frictional torque can be further enhanced by several times.
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2

Wingertszahn, Patrick, Oliver Koch, Lorenzo Maccioni, Franco Concli, and Bernd Sauer. "Predicting Friction of Tapered Roller Bearings with Detailed Multi-Body Simulation Models." Lubricants 11, no. 9 (September 1, 2023): 369. http://dx.doi.org/10.3390/lubricants11090369.

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In the presented work, a parametric multibody simulation model is presented that is capable of predicting the friction torque and kinematics of tapered roller bearings. For a highly accurate prediction of bearing friction, consideration of solid and lubricant friction is mandatory. For tapered roller bearings in particular, the friction in the contact between the rolling element and raceway is of importance. Friction forces in the contact between the rolling element end face and inner ring rib as well as roller cage pocket contacts are also considered in the model. A large number of tests were carried out to validate the model in terms of the simulated frictional torque. Influencing variables such as speed, axial load, radial load, and temperature were investigated. The simulation results show good agreement with the measured friction torque, which confirms that the model is well suited to predict frictional torques and therefore the kinematics of tapered roller bearings.
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3

Chung, Michael, Robert J. Nikolai, Ki Beom Kim, and Donald R. Oliver. "Third-Order Torque and Self-Ligating Orthodontic Bracket–Type Effects on Sliding Friction." Angle Orthodontist 79, no. 3 (May 1, 2009): 551–57. http://dx.doi.org/10.2319/022608-114.1.

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Abstract Objective: To examine the influence of third-order torque on kinetic friction in sliding mechanics involving active and passive self-ligating brackets. Materials and Methods: Wire-slot frictional forces were quantified and compared across five sets of brackets and tubes within a simulated posterior dental segment with −15°, −10°, −5°, 0°, +5°, +10°, and +15° of torque placed in the second-premolar bracket; a working archwire was pulled through the slots. Results: Increasing the torque from 0° to ±15° produced significant increases in frictional resistance with all five sets of brackets and tubes. At 0° and ±5° of torque, generally less friction was created within the passive than within the active self-ligating bracket sets, and the conventional bracket sets with elastomeric ligation generated the most friction. At ±10° of torque, apparently with wire-slot clearance eliminated, all bracket-and-tube sets displayed similar resistances, with one exception at +10°. At ±15° of torque, one passive set and one active set produced significantly larger frictional resistances than the other three sets. Conclusions: Third-order torque in posterior dental segments can generate frictional resistance during anterior retraction with the archwire sliding through self-ligating bracket slots. With small torque angles, friction is less with passive than with active self-ligating brackets, but bracket design is a factor. Frictional forces are substantial, regardless of ligation if the wire-slot torque exceeds the third-order clearance.
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4

Trepte, M., and G. Prausner. "Measurement of frictional torque in friction welding." Welding International 5, no. 11 (January 1991): 914–15. http://dx.doi.org/10.1080/09507119109446816.

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5

Kinoshita, Hiroshi, Lars Bäckström, J. Randall Flanagan, and Roland S. Johansson. "Tangential Torque Effects on the Control of Grip Forces When Holding Objects With a Precision Grip." Journal of Neurophysiology 78, no. 3 (September 1, 1997): 1619–30. http://dx.doi.org/10.1152/jn.1997.78.3.1619.

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Kinoshita, Hiroshi, Lars Bäckström, J. Randall Flanagan, and Roland S. Johansson. Tangential torque effects on the control of grip forces when holding objects with a precision grip. J. Neurophysiol. 78: 1619–1630, 1997. When we manipulate small objects, our fingertips are generally subjected to tangential torques about the axis normal to the grasp surface in addition to linear forces tangential to the grasp surface. Tangential torques can arise because the normal force is distributed across the contact area rather than focused at a point. We investigated the effects of tangential torques and tangential forces on the minimum normal forces required to prevent slips (slip force) and on the normal forces actually employed by subjects to hold an object in a stationary position with the use of the tips of the index finger and thumb. By changing the location of the object's center of gravity in relation to the grasp surface, various levels of tangential torque (0–50 N⋅mm) were created while the subject counteracted object rotation. Tangential force (0–3.4 N) was varied by changing the weight of the object. The flat grasp surfaces were covered with rayon, suede, or sandpaper, providing differences in friction in relation to the skin. Under zero tangential force, both the employed normal force and the slip force increased in proportion to tangential torque with a slope that reflected the current frictional condition. Likewise, with pure tangential force, these forces increased in proportion to tangential force. The effects of combined tangential torques and tangential forces on the slip force were primarily additive, but there was a significant interaction of these variables. Specifically, the increase in slip force for a given increment in torque decreases as a function of tangential force. A mathematical model was developed that successfully predicted slip force from tangential torque, tangential force, and an estimate of coefficient of static friction in the digit-surface interface. The effects of combined tangential torques and forces on the employed normal force showed the same pattern as the effects on the slip force. The safety margin against frictional slips, measured as the difference between the employed normal force and the slip force, was relatively small and constant across all tangential force and torque levels except at small torques (<10 N⋅mm). There was no difference in safety margin between the digits. In conclusion, tangential torque strongly influences the normal force required for grasp stability. When controlling normal force, people take into account, in a precise fashion, the slip force reflecting both tangential force and tangential torque and their interaction as well as the current frictional condition in the object-digit interface.
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6

Henjes, Katja. "Frictional torque in ferrofluids." Journal of Magnetism and Magnetic Materials 117, no. 3 (December 1992): L311—L316. http://dx.doi.org/10.1016/0304-8853(92)90086-4.

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7

Ahmad, Mohamad Ali, Salmiah Kasolang, Rob Dwyer-Joyce, and Mimi Azlina Abu Bakar. "The Effects of Oil Groove Position on Torque and Frictional Force in Hydrodynamic Journal Bearing." Applied Mechanics and Materials 393 (September 2013): 907–12. http://dx.doi.org/10.4028/www.scientific.net/amm.393.907.

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Axial groove is a common supply method of distributing lubricant within a journal bearing. Lubricant is generally fed at a specific supply pressure to ensure that the journal and the bearing surface are separated. Shearing action between lubricant and bearing parts creates frictions which contribute to power loss in journal bearing. In the present study, an experimental work was conducted to determine the effect of oil groove location on torque and frictional force in hydrodynamic journal bearing. A journal diameter of 100mm with a 12 length-to-diameter ratio was used. The oil supply pressure was set at 0.20 to 0.25 MPa. The groove was positioned at 3 different locations namely 00, +150and +300. Measurements of torque and frictional force were obtained for speed values of 300, 500 and 800 RPM at different radial loads. It was observed that the change in oil groove location has affected the fluid frictional force and friction coefficient to some extent.
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8

Huang, Shan, Jiusheng Bao, Shirong Ge, Yan Yin, and Tonggang Liu. "Design of a frictional–electromagnetic compound disk brake for automotives." Proceedings of the Institution of Mechanical Engineers, Part D: Journal of Automobile Engineering 234, no. 4 (July 15, 2019): 1113–22. http://dx.doi.org/10.1177/0954407019864210.

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According to the disadvantages of serious wear and heat fade of friction pad in frequent and high speed braking of friction brakes, and the insufficient power of electromagnetic brakes in low speed braking, a novel frictional-electromagnetic compound disk brake which combines both of these two brake principles is proposed for automotives in this paper. The excitation coils are designed based on the Zhang Yicheng theory model, and the compound brake prototype is manufactured based on the self-made magnetic brake pads and existing automotive brakes. The magnetic field and dynamic of the brake are simulated by using COMSOL Multiphysics software. The frictional–electromagnetic compound brake tests are implemented on the reconstructive disk brake simulation test bench. The experimental results show that the friction braking torque accounts for more than 90% of the compound braking torque in the process of compound braking, and the trend of the change is the same as that of the compound braking torque. When the initial braking speed exceeds 75 km/h, the electromagnetic braking torque does not increase with the increase in speed, instead, it decreases slightly because of demagnetization. The designed frictional–electromagnetic compound disk brake has good braking performance.
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9

Wroblewski, B. M., P. D. Siney, and P. A. Fleming. "Charnley low-frictional torque arthroplasty." Journal of Bone and Joint Surgery. British volume 91-B, no. 4 (April 2009): 447–50. http://dx.doi.org/10.1302/0301-620x.91b4.21933.

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10

Chen, Wenjian, Jin Huang, and Yan Yang. "Research on the Transmission Performance of a High-Temperature Magnetorheological Fluid and Shape Memory Alloy Composite." Applied Sciences 12, no. 7 (March 22, 2022): 3228. http://dx.doi.org/10.3390/app12073228.

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To address the fact that the performance of magnetorheological fluid decreases with increasing temperature, a high-temperature magnetorheological fluid and shape memory alloy spring friction composite transmission method is proposed, and its transmission performance is shown to essentially maintain stability under high temperatures. We introduce a composite transmission method, performed a magnetic field finite element analysis, and present the equation of torque transmission of the composite. The results show that the amount of torque transferred by the magnetorheological fluid reached its maximum value at magnetic saturation, but decreased with increasing temperature, down to 33.41%, whereas the frictional torque generated by the shape memory alloy spring increased with increasing temperature. When the temperature reached 100 °C, the frictional torque effectively compensated for the decrease in the magnetorheological fluid’s performance.
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11

Pillai, Branesh M., and Jackrit Suthakorn. "Motion control applications: observer based DC motor parameters estimation for novices." International Journal of Power Electronics and Drive Systems (IJPEDS) 10, no. 1 (March 1, 2019): 195. http://dx.doi.org/10.11591/ijpeds.v10.i1.pp195-210.

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<span>Estimation of motor inertia and friction components is a complex and challenging task in motion control applications where small size DC motors (&lt;100W) are used for precise control. It is essential to estimate the accurate friction components and motor inertia, because the parameters provided by the manufacturer are not always accurate. This research proposes a Sensorless method of determining DC motor parameters, including moment of inertia, torque coefficient and frictional components using the Disturbance Observer (DOB) as a torque sensor. The constant velocity motion test and a novel Reverse Motion Acceleration test were conducted to estimate frictional components and moment of inertia of the motor. The validity of the proposed novel method was verified by experimental results and compared with conventional acceleration and deceleration motion tests. Experiments have been carried out to show the effectiveness and viability of the estimated parameters using a Reaction Torque Observer (RTOB) based friction compensation method.</span>
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12

Sarkar, Chiranjit, and Harish Hirani. "Experimental studies on magnetorheological brake containing plane, holed and slotted discs." Industrial Lubrication and Tribology 69, no. 2 (March 13, 2017): 116–22. http://dx.doi.org/10.1108/ilt-12-2015-0205.

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Purpose This study aims to design an ideal magnetorheological (MR) brake that exerts negligible frictional torque in the off-state condition and controllable frictional torque in the on-state condition. Design/methodology/approach Silicone-based MR fluid, containing 9 per cent volume carbonyl iron particles, has been synthesized and used. The synthesized MR fluid is advantageous in maintaining low friction losses in off-state conditions. A magneto-rheometer has been utilized to characterize the off-state viscosity of the MR fluid at variable shear rates and shear stress of MR fluids at various magnetic fields. A mechanism to enhance the braking torque in the on-state condition has been designed and developed. An experimental test rig has been developed to capture the torque characteristics of the developed MR brakes. Three different designs of MR discs have been experimented under a magnetic field varying from 0 to 375 kA/m. Experimental results of braking torque under shear and compression modes have been presented. Findings Slotted disc MR brake gives much better torque performance. Originality/value The braking torque results motivate to use the slotted disc MR brake for high torque application.
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13

Su, Zhu Yu. "A Study on Forming Mechanism of Braking Torque on the Friction Surface." Advanced Materials Research 850-851 (December 2013): 200–203. http://dx.doi.org/10.4028/www.scientific.net/amr.850-851.200.

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The process of vehicle brake, the influence of the temperature on brake friction directly determines the braking force and the frictional coefficient, and has a huge impact on the braking torque. Based on the characteristics of frictional material, combining with modeling and simulation tests, researching the basic theory of braking technology, contribute to the stability and enhancement of braking performance.
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14

Okamoto, N., N. Tanaka, and M. Nogami. "Finite Element and Experimental Studies of Creep at the Interface of Press Fitted Gears-Shafts Connections." Journal of Mechanical Design 118, no. 4 (December 1, 1996): 568–72. http://dx.doi.org/10.1115/1.2826930.

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It is shown experimentally that relative movement of shrink-fit connections occurs on mating surfaces even if the transmitting torque does not exceed the static frictional torque. However, there is a transmitting torque threshold below which no relative movement occurs. The experimental thresholds agree well with predictions from theoretical calculations of the slip model, which is based on the numerical results of shear stress variation along the interface and on Coulomb’s law of friction.
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15

Mungan, Carl E. "Frictional torque on a rotating disc." European Journal of Physics 33, no. 5 (June 28, 2012): 1119–23. http://dx.doi.org/10.1088/0143-0807/33/5/1119.

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16

Michalowski, Radoslaw L., and Andrzej Gawecki. "Limit Torque for a Frictional Joint*." Mechanics of Structures and Machines 24, no. 4 (January 1996): 499–512. http://dx.doi.org/10.1080/08905459608905275.

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17

Da˛browski, Leszek, and Michał Wasilczuk. "A Method of Friction Torque Measurement for a Hydrodynamic Thrust Bearing." Journal of Tribology 117, no. 4 (October 1, 1995): 674–78. http://dx.doi.org/10.1115/1.2831534.

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Measurements of thrust bearing friction torque are difficult because of the small values of the friction force in comparison with the axial load. Another problem of a thrust bearing test rig design is the necessity of accommodation of the axial load so that it does not interact with the frictional forces. Separation of fluid drag in the housing from torque in the bearing itself is also important. An analysis of a design in which the above-mentioned problems have been solved is presented. Theoretical analysis and calibration of the torque meter proved that the effect of axial load was successfully compensated for. Example of the results obtained due to the torque meter illustrate the application of the new design.
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18

Li, Tse Chang, Yu Wen Huang, and Jen Fin Lin. "Studies on Centrifugal Clutch of Frictional Lining Materials." Key Engineering Materials 642 (April 2015): 39–44. http://dx.doi.org/10.4028/www.scientific.net/kem.642.39.

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Using the Taguchi method, a 5-factorial, 3-level orthogonal array (L’18 (35)) was used as the experimental layout for 18 kinds of frictional lining specimen. These specimens were prepared in order to investigate their performance in establish a relationship between Ts/Td (Ts: static torque; Td: dynamic torque) and dμ/dνx (μ: friction coefficient; νx: relative velocity of frictional lining and clutch drum) parameters. The frictional torque and the rotational speeds of the driveline, clutch, and clutch drum as functions of contact time for 100 clutch cycles are experimentally obtained dμ/dνx and Ts/Td. In the study, a sharp rise in maximum contact pressure ratio occurred when the relative sliding velocity reached the critical velocity, Vc. This increase in maximum contact pressure ratio generally led to an increase of the (initially negative) dμ/dνx value. The mean values of dμ/dνx and Ts/Td for the clutching tests with 100 cycles can be roughly divided into three groups dependent on the fluctuation intensities of these two parameters, for each of which there is a linear relationship. The maximum contact pressure ratio significantly increases even increasing the mean value of dμ/dνx.
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19

Shinde, Anil B., and Prashant M. Pawar. "Effect of partial grooving on the performance of hydrodynamic journal bearing." Industrial Lubrication and Tribology 69, no. 4 (July 10, 2017): 574–84. http://dx.doi.org/10.1108/ilt-06-2016-0124.

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Purpose This study aims to improve the performance of hydrodynamic journal bearings through partial grooving on the bearing surface. Design/methodology/approach Bearing performance analysis is numerically carried out using the thin film flow physics of COMSOL Multiphysics 5.0 software. Initially, the static performance analysis is carried out for hydrodynamic journal bearing system with smooth surface, and the results of the same are validated with results from the literature. In the later part of the paper, the partial rectangular shape micro-textures are modeled on bearing surface. The effects of partial groove pattern on the bearing performance parameters, namely, fluid film pressure, load carrying capacity, frictional power loss and frictional torque, are studied in detail. Findings The numerical results show that the values of maximum fluid film pressure, load carrying capacity, frictional power loss and frictional torque are considerably improved due to deterministic micro-textures. Bearing surface with partial groove along 90°-180° region results in 81.9 per cent improvement in maximum fluid film pressure and 75.9 per cent improvement in load carrying capacity as compared with smooth surface of journal bearing, with no increase in frictional power loss and frictional torque. Maximum decrease in frictional power loss and frictional torque is observed for partially grooving along 90°-360° region. The simulations are supported by proof-of-concept experimentation. Originality/value This study is useful in the appropriate selection of groove parameters on bearing surface to the bearing performance characteristics.
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20

Hu, X. Q., R. J. K. Wood, A. Taylor, and M. A. Tuke. "The tribological behaviour of different clearance MOM hip joints with lubricants of physiological viscosities." Proceedings of the Institution of Mechanical Engineers, Part H: Journal of Engineering in Medicine 225, no. 11 (September 9, 2011): 1061–69. http://dx.doi.org/10.1177/0954411911419061.

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Clearance is one of the most influential parameters on the tribological performance of metal-on-metal (MOM) hip joints and its selection is a subject of considerable debate. The objective of this paper is to study the lubrication behaviour of different clearances for MOM hip joints within the range of human physiological and pathological fluid viscosities. The frictional torques developed by MOM hip joints with a 50 mm diameter were measured for both virgin surfaces and during a wear simulator test. Joints were manufactured with three different diametral clearances: 20, 100, and 200 µm. The fluid used for the friction measurements which contained different ratios of 25 per cent newborn calf serum and carboxymethyl cellulose (CMC) with the obtained viscosities values ranging from 0.001 to 0.71 Pa s. The obtained results indicate that the frictional torque for the 20 µm clearance joint remains high over the whole range of the viscosity values. The frictional torque of the 100 µm clearance joint was low for the very low viscosity (0.001 Pa s) lubricant, but increased with increasing viscosity value. The frictional torque of the 200 µm clearance joint was high at very low viscosity levels, however, it reduced with increasing viscosity. It is concluded that a smaller clearance level can enhance the formation of an elastohydrodynamic lubrication (EHL) film, but this is at the cost of preventing fluid recovery between the bearing surfaces during the unloaded phase of walking. Larger clearance bearings allow a better recovery of lubricant during the unloaded phase, which is necessary for higher viscosity lubricants. The selection of the clearance value should therefore consider both the formation of the EHL film and the fluid recovery as a function of the physiological viscosity in order to get an optimal tribological performance for MOM hip joints. The application of either 25 per cent bovine serum or water in existing in vitro tribological study should also be revised to consider the relevance of clinic synovial fluid viscosities and to avoid possible misleading results.
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21

Han, Lin, Wentie Niu, Dawei Zhang, and Fujun Wang. "An Improved Algorithm for Calculating Friction Force and Torque in Involute Helical Gears." Mathematical Problems in Engineering 2013 (2013): 1–13. http://dx.doi.org/10.1155/2013/575302.

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Time varying frictional force and torque are one of the main exciting sources of vibration in helical gears. This paper presents an approach to determine the friction force and torque in involute helical gears considering nonuniform load distribution along contact lines. An analytical load distribution model is employed and extended to obtain the load per unit of length along contact lines. Friction force and torque models under nonuniform assumption are derived. Comparisons of the determined friction force and torque with the results from uniform assumption are made. In addition, the differences between constant friction coefficient and varying coefficient are revealed. Moreover, two typical design cases of helical gears are studied. Results show that the fluctuations of friction force and torque under uniform assumption are more significant than those under nonuniform assumption in sample I for a single tooth, but less significant for the sum of those of the three teeth, while in sample II, the fluctuations under uniform assumption are less significant than those under nonuniform assumption. The friction coefficient induced difference is negligible compared with the difference induced by load distribution assumptions.
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22

Vidyasagar, K. E. Ch, R. K. Pandey, and Dinesh Kalyanasundaram. "An exploration of frictional and vibrational behaviors of textured deep groove ball bearing in the vicinity of requisite minimum load." Friction 9, no. 6 (March 17, 2021): 1749–65. http://dx.doi.org/10.1007/s40544-021-0495-3.

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AbstractIn case of lightly loaded radial ball bearings, failure mechanisms other than fatigue such as smearing of raceways due to increased frictional torque and vibrations often prevail. Hence, attempts have been made herein for reducing the frictional torque and minimizing the vibrations of a radial deep groove ball bearing employing surface textures at the inner race. Nanosecond pulsed laser was used to create texture (involving micro-dimples having different dimple area density) on the inner race of test bearings. Using an in-house developed test rig, frictional torque and vibrational parameters were measured at different speeds and light loads (i.e. in vicinity of 0.01C, where C is dynamic load capacity of radial ball bearing). Significant reduction in frictional torque and overall vibrations were found in the presence of micro-dimples on inner race at light loads irrespective of operating speeds. Even without satisfying the minimum load needed criteria for the satisfactory operation, substantial reduction in smearing marks was found on the races of textured ball bearings in comparison to conventional cases.
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23

Ahmad, Mohamad Ali, Salmiah Kasolang, and Rob Dwyer-Joyce. "Experimental Study of Oil Supply Pressure Effects on Bearing Friction in Hydrodynamic Lubrication." Applied Mechanics and Materials 315 (April 2013): 977–81. http://dx.doi.org/10.4028/www.scientific.net/amm.315.977.

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Journal bearing is widely applied in most of rotating machineries for transmission of large loads at mean speed of rotation. Friction caused by the shearing condition between journal, bearing and lubricant contribute to power loses in journal bearing system. In the present study, an experimental work was conducted to determine the effect of oil supply pressure on frictional force, friction coefficient and torque of a journal bearing. A journal diameter of 100 mm with a ½ length-to-diameter ratio was used. The oil supply pressure was set at three different values (0.3, 0.5, 0.7 MPa). Frictional force and friction coefficient results for 400, 600 and 800 RPM at different radial loads were obtained. It was observed that the change in oil supply pressure has affected the fluid frictional force and friction coefficient to some extent.
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24

Wilkie, Jack, Paul D. Docherty, and Knut Möller. "Developments in Modelling Bone Screwing." Current Directions in Biomedical Engineering 6, no. 3 (September 1, 2020): 111–14. http://dx.doi.org/10.1515/cdbme-2020-3029.

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AbstractINTRODUCTION: A torque-rotation model of the bone-screwing process has been proposed. Identification of model parameters using recorded data could potentially be used to determine the material properties of bone. These properties can then be used to recommend tightening torques to avoid over or under-tightening of bone screws. This paper improves an existing model to formulate it in terms of material properties and remove some assumptions. METHOD: The modelling methodology considers a critical torque, which is required to overcome friction and advance the screw into the bone. Below this torque the screw may rotate with elastic deformation of the bone tissue, and above this the screw moves relative to the bone, and the speed is governed by a speed-torque model of the operator’s hand. The model is formulated in terms of elastic modulus, ultimite tensile strength, and frictional coefficient of the bone and the geometry of the screw and hole. RESULTS: The model output shows the speed decreasing and torque increasing as the screw advances into the bone, due to increasing resistance. The general shape of the torque and speed follow the input effort. Compared with the existing model, this model removes the assumption of viscous friction, models the increase in friction as the screw advances into the bone, and is directly in terms of the bone material properties. CONCLUSION: The model presented makes significant improvements on the existing model. However it is intended for use in parameter identification, which was not evaluated here. Further simulation and experimental validation is required to establish the accuracy and fitness of this model for identifying bone material properties.
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25

Yin, Yan, Jiusheng Bao, Jinge Liu, Chaoxun Guo, Tonggang Liu, and Yangyang Ji. "Braking performance of a novel frictional-magnetic compound disc brake for automobiles." Proceedings of the Institution of Mechanical Engineers, Part D: Journal of Automobile Engineering 233, no. 10 (August 3, 2018): 2443–54. http://dx.doi.org/10.1177/0954407018791056.

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Disc brakes have been applied in various automobiles widely and their braking performance has vitally important effects on the safe operation of automobiles. Although numerous researches have been conducted to find out the influential law and mechanism of working condition parameters like braking pressure, initial braking speed, and interface temperature on braking performance of disc brakes, the influence of magnetic field is seldom taken into consideration. In this paper, based on the novel automotive frictional-magnetic compound disc brake, the influential law of magnetic field on braking performance was investigated deeply. First, braking simulation tests of disc brakes were carried out, and then dynamic variation laws and mechanisms of braking torque and interface temperature were discussed. Furthermore, some parameters including average braking torque, trend coefficient and fluctuation coefficient of braking torque, average temperature, maximum temperature rise, and the time corresponding to the maximum temperature rise were extracted to characterize the braking performance of disc brakes. Finally, the influential law and mechanism of excitation voltage on braking performance were analyzed through braking simulation tests and surface topography analysis of friction material. It is concluded that the performance of frictional-magnetic compound disc brake is prior to common brake. Magnetic field is greatly beneficial for improving the braking performance of frictional-magnetic compound disc brake.
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26

Nam, Yoonsu, and Sung Kyung Hong. "Active stick control using frictional torque compensation." Sensors and Actuators A: Physical 117, no. 2 (January 2005): 194–202. http://dx.doi.org/10.1016/j.sna.2004.06.018.

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27

Wroblewski, B. M., Paul D. Siney, and Patricia A. Fleming. "Charnley low frictional torque arthroplasty: clinical developments." Orthopedic Clinics of North America 36, no. 1 (January 2005): 11–16. http://dx.doi.org/10.1016/j.ocl.2004.06.013.

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28

Hatazawa, T., and T. Kawaguchi. "Frictional Torque of Needle Roller Thrust Bearings." Tribology Transactions 52, no. 1 (December 22, 2008): 127–32. http://dx.doi.org/10.1080/10402000802561384.

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29

Henein, Naeim A., Shengqiang Huang, and Walter Bryzik. "A New Approach to Determine Lubrication Regimes of Piston-Ring Assemblies." Journal of Tribology 119, no. 4 (October 1, 1997): 808–16. http://dx.doi.org/10.1115/1.2833889.

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A new approach is developed to determine piston-ring assembly lubrication regimes from the instantaneous frictional torque measured for the whole engine. This is based on the variation of the friction coefficient with the duty parameter in the Stribeck diagram over the mixed and hydrodynamic lubrication regimes. The derived equation determines the lubrication regimes from the slope of the line in the Stribeck diagram. A single cylinder spark ignition engine was instrumented to determine the total instantaneous frictional torque of the engine. Experiments were conducted under different loads at a constant speed. Results show that the regime is mixed lubrication near the top dead center (TDC) and shifts to the hydrodynamic lubrication regime as the piston moves away from TDC. The extent of the mixed lubrication regime depends on engine load and speed.
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30

Tang, Yan Li, Rong Di Han, and Jia Bin Ju. "Theoretical and Experimental Research on Tapping of GH4169 and TC4 with Modified-Tooth Taps." Key Engineering Materials 375-376 (March 2008): 221–25. http://dx.doi.org/10.4028/www.scientific.net/kem.375-376.221.

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Based on the theoretical principle of tapping formation and simulation with modified-tooth tap, the relationship among the different geometric parameters of the tap was further analyzed. A series of modified-tooth taps and standard ones with a cutting cone angle of 7°30´and a outer diameter of M6, which were made from high-speed steel W9, were taken to do the comparative tapping test on nickel-based high-temperature alloy GH4169, titanium alloy TC4 and 45 steel. The test results indicated that the leading cause of difficult tapping in GH4169 and TC4 was the largeness of their friction torques which were about 35 % and 62 % of tapping torque respectively, where the frictional wear was a fundamental reason for tough tapping GH4169 and the spring back of machined surface for TC4.The obvious decreases of friction torque with the modified-tooth tap approximately 70% and 50% respectively for GH4169 and TC4 were attributed to its unique tapping formation principle of generating broaching but no remarkable effects on 45 steel in comparison with standard tap.
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31

Elhami, M. R., and D. J. Brookfield. "Identification of Coulomb and Viscous Friction in Robot Drives: An Experimental Comparison of Methods." Proceedings of the Institution of Mechanical Engineers, Part C: Journal of Mechanical Engineering Science 210, no. 6 (November 1996): 529–40. http://dx.doi.org/10.1243/pime_proc_1996_210_228_02.

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This paper presents an experimental comparison of five methods of identifying friction in robot drives. The methods considered are direct plotting of velocity versus armature voltage, plotting velocity versus armature current, third harmonic estimation, batch least squares and sequential least squares. These methods were implemented on a d.c. servo motor robot drive system to identify Coulomb and viscous friction parameters. It is shown that an asymmetric Coulomb and viscous model properly identifies the frictional torque due to the combined sliding and rolling friction in the motor. Furthermore, although each of the identification methods is shown to be capable of giving reasonable estimates of the frictional coefficients, the plotting of velocity versus armature current is shown to be most suitable for off-line frictional identification and the sequential least-squares method most suitable for on-line identification, particularly when coefficients may change with time.
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32

Harada, M., and J. Tsukazaki. "The Steady-State Characteristics of a Hydrostatic Thrust Bearing With a Floating Disk." Journal of Tribology 111, no. 2 (April 1, 1989): 352–57. http://dx.doi.org/10.1115/1.3261921.

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To reduce the frictional power loss of hydrostatic thrust bearings, the hydrostatic thrust bearing with a floating disk shaped in a simplified configuration is proposed. And the load capacity and the frictional torque are experimentally investigated in laminar and superlaminar regimes. Following results can be obtained: (1) The disk floats at a certain stable position for given shaft rotational speed and rotates at nearly half rotational speed of the shaft. (2) The frictional torque of this type of the bearing is less than half of a conventional hydrostatic thrust bearing with the same surface configuration as the floating disk.
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33

Zhou, R. S., and M. R. Hoeprich. "Torque of Tapered Roller Bearings." Journal of Tribology 113, no. 3 (July 1, 1991): 590–97. http://dx.doi.org/10.1115/1.2920664.

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An analytic tapered roller bearing torque model is presented along with laboratory test data. Initial results of this proposed model are favorable. An accurate general purpose torque prediction tool could be obtained by extending the concepts presented in conjunction with a more comprehensive analysis of actual bearing operating conditions. By using EHL (Elastohydrodynamic Lubrication) theory and micro-macro contact analysis, the bearing torque can be determined by predicting each torque component for each roller due to raceway rolling, raceway moments due to EHL pressure distribution, and frictional force of rib-roller end contact. The roughness effect of contact surfaces, effect of EHL film thickness parameter (the ratio of film thickness to composite surface roughness), and thermal EHL effects are also included. A bearing torque test rig, which can measure the torque of cup race, cone race, and rib separately, was built and used to provide test data. Good agreement between the experimentally measured bearing torques and the predictions of the new torque model has been obtained. This torque model will provide a greater fundamental understanding and is more versatile over a wide range of operating conditions.
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34

Hu, Xiu Chi, Jian Zhong Zhang, Jun Hai Zhang, and Lan Xia Zheng. "Tribometer Design of Slide Bearings under Micro-Load." Advanced Materials Research 219-220 (March 2011): 446–52. http://dx.doi.org/10.4028/www.scientific.net/amr.219-220.446.

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A type of tribometer for experimental study of tribological performance of journal bearings under micro-load was developed, which utilizes the method of load counterpoise to obtain mechanics equilibrium state of the test rig so as to apply load from zero. A laser device and a PSD sensor were used to measure the displacement and friction force with high precision without contact. The friction coefficient is obtained from the frictional angle of the cantilever and displacement of PSD sensor. Two methods were used for the measurement of friction coefficient, friction angle and frictional torque equilibrium. The former measures the angle resulting from friction, and the latter utilizes the exterior torque to poise the rig mechanics state under the rotating condition. The zero location on PSD is at the tail end of test process. Through reaching one side weight limitation with pulley at the static state, calibration of load was completed. The tribometer can measure friction, stick-slip of journal bearings under micro-load. Furthermore, measurements of wider range of load and /or friction coefficient were achieved by setting the structure parameters of the tribometer. With data sampling and processing capability, bearing bulk temperature and friction coefficient can be obtained continuously with adjustable load or/and speed.
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35

Zhang, Ming Zhu, Hong Tao Li, and Hai Tao Zhao. "Test and Analysis of Friction Torque for Wind Turbine Pitch Bearing." Advanced Materials Research 189-193 (February 2011): 2601–4. http://dx.doi.org/10.4028/www.scientific.net/amr.189-193.2601.

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In this paper, we introduce a new test method for friction performance of wind turbine pitch bearing. Four loading devices are used to put on load on the pitch bearing from different directions through load board. It can accurately simulate the axial force, radial force and overturning moment of wind turbine pitch bearing. The data acquisition device can measure the value of speed, torque and actual output load of loading hydraulic cylinder. After analysis and calculation, the influence of additional friction torque produced by loading device can be obviated, the friction torque of wind turbine pitch bearing under different loads can be test accurately in the laboratory. The research shows that the structure of test bed is compact, mechanical rigidity is good, the replacement of bearing model is expedient. It puts on load easily and can measure the frictional torque of wind turbine pitch bearing under different loads more accurately. It can provide data for performance analysis of wind turbine pitch bearing and ensure the pitch bearing satisfying the application requirements.
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36

Wang, Yanzhong, Kai Yang, and Xiangyu Wu. "Structural Design and Friction Performance Test of a New Conical Groove Friction Disks in Wet Clutch." Applied Sciences 11, no. 16 (August 5, 2021): 7231. http://dx.doi.org/10.3390/app11167231.

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Wet clutch transmits its power by the friction torque between friction and separate disks. Conical groove friction disk is a new attempt in Wet clutch. Its configurations allow significant enhancement of torque delivery performances, compared with the traditional plane friction disk. In order to study the frictional performances of the conical groove friction configuration, the friction coefficient calculation model of conical groove friction disk was established, and experimental investigation was used to measure the friction coefficient under sliding velocity conditions. The influence of configuration parameters: cone heights and angles on friction coefficients were evaluated in a typical variable speed test. The results indicated that configuration parameters can affect friction performance in a constant speed period. The equivalent radius can directly describe the friction region of a conical groove friction disk. The constant speed test can be a useful method.
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37

Schanner, Jonathan, Roman Funke, Andreas Schubert, and Alexander Hasse. "Investigating the Friction Behavior of Turn-Milled High Friction Surface Microstructures under Different Tribological Influence Factors." Journal of Manufacturing and Materials Processing 6, no. 6 (November 15, 2022): 143. http://dx.doi.org/10.3390/jmmp6060143.

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The coefficient of friction (COF) is an important parameter for mechanical engineers to consider when designing frictional connections. Previous work has shown that a surface microstructuring of the harder friction partner leads to a significant increase in the COF. However, the impact of the changes in the tribological system on the COF are not known in detail. In this study, the tribological influence factors such as the nominal surface pressure, the material pairing, lubrication, and the surface properties of the counterbody are investigated. Microstructuring is applied by turn-milling of an annular contact surface of cylindrical specimens. A torsional test bench is used to measure the torque depending on the displacement of the two specimens, thus enabling the determination of the COF. All tests with the microstructured specimens result in higher COF than the reference test with unstructured samples. The manufacturing process of the counterbody surface, the nominal surface pressure, and the materials in contact have a significant influence on the COF. While lubrication reduces friction in the case of unstructured specimens, the COF does not change significantly for microstructured samples. This proves that the deformative friction component dominates over the adhesive. Microstructuring the harder friction partner increases the transmittable torque in frictional connections and reduces the sensitivity towards possible contamination with lubricants.
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38

Shapovalov, Vladimir, Petr Shcherbak, Pavel Kharlamov, Tatiana Sajamova, and Denis Ryabysh. "Improving the energy efficiency of power transmissions of a rolling stock on the basis of dynamic anisotropy of frictional contact." E3S Web of Conferences 104 (2019): 01002. http://dx.doi.org/10.1051/e3sconf/201910401002.

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The analysis showed the following tendencies of development and energy efficiency of designs of gearboxes for track machines: provision of a maximum level of efficiency, removal of rupture of a stream of the passed capacity, provision of a high level of reliability, decrease of power input on gearbox work, provision of convenience, simplicity of service and steering, engine braking maintenance, and also maintenance of a relatively low cost. The above-mentioned tasks are performed by including clutch pinion gears with the built in frictional amplifier elements in an automatic gearbox, and also during the effect of dynamic anisotropy of frictional bonds. Besides a torque transfer, the clutch gear carries out a safety clutch function. That means that there is sliding at a high rotational power. Factor of strengthening of the given link is Кstr → ∞ due to occurence of dynamic anisotropy of frictional bonds. Physical and mechanical characteristics of contacting surfaces are formed in the course of dynamic interaction of roughnesses in friction units at modes of dry and boundary friction. Essential-nonlinear friction processes, interconnected with dynamic processes on the contact area, define values of target characteristics of frictional system. They can fluctuate in a very wide range. The friction factor fmp for the same friction units at preservation of constant conditions and friction parameters can vary from zero to infinity that is an essence of dynamic anisotropy of frictional bonds.
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39

DENG, Sier. "Frictional Torque Characteristic of Angular Contact Ball Bearings." Journal of Mechanical Engineering 47, no. 05 (2011): 114. http://dx.doi.org/10.3901/jme.2011.05.114.

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40

HOSOKAWA, Shuji, and Takasi TAKAHASI. "H04 Frictional Torque by Tightening of Threaded Fasteners." Proceedings of Conference of Kyushu Branch 2006.59 (2006): 195–96. http://dx.doi.org/10.1299/jsmekyushu.2006.59.195.

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41

Lim, C. T., and W. J. Stronge. "Frictional torque and compliance in collinear elastic collisions." International Journal of Mechanical Sciences 36, no. 10 (October 1994): 911–30. http://dx.doi.org/10.1016/0020-7403(94)90054-x.

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42

Wroblewski, B. M., P. A. Fleming, and P. D. Siney. "Charnley low-frictional torque arthroplasty of the hip." Journal of Bone and Joint Surgery. British volume 81-B, no. 3 (May 1999): 427–30. http://dx.doi.org/10.1302/0301-620x.81b3.0810427.

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43

HOSOKAWA, Shuji. "2933 Frictional Torque of Bolt Head at Tightening." Proceedings of the JSME annual meeting 2007.4 (2007): 51–52. http://dx.doi.org/10.1299/jsmemecjo.2007.4.0_51.

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44

Sun, Jing, Guojing Xing, Xudong Liu, Xiaoling Fu, and Chenghui Zhang. "A Novel Torque Coordination Control Strategy of a Single-Shaft Parallel Hybrid Electric Vehicle Based on Model Predictive Control." Mathematical Problems in Engineering 2015 (2015): 1–12. http://dx.doi.org/10.1155/2015/960678.

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The torque coordination control during mode transition is a very important task for hybrid electric vehicle (HEV) with a clutch serving as the key enabling actuator element. Poor coordination will deteriorate the drivability of the driver and lead to excessive wearing to the clutch friction plates. In this paper, a novel torque coordination control strategy for a single-shaft parallel hybrid electric vehicle is presented to coordinate the motor torque, engine torque, and clutch torque so that the seamless mode switching can be achieved. Different to the existing model predictive control (MPC) methods, only one model predictive controller is needed and the clutch torque is taken as an optimized variable rather than a known parameter. Furthermore, the successful idea of model reference control (MRC) is also used for reference to generate the set-point signal required by MPC. The parameter sensitivity is studied for better performance of the proposed model predictive controller. The simulation results validate that the proposed novel torque coordination control strategy has less vehicle jerk, less torque interruption, and smaller clutch frictional losses, compared with the baseline method. In addition, the sensitivity and adaptiveness of the proposed novel torque coordination control strategy are evaluated.
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45

Miwa, Reo, Norifumi Miyanaga, and Jun Tomioka. "Appearance of Hysteresis Phenomena on Hydrodynamic Lubrication in a Seal-Type Thrust Bearing with Dimples." Materials 14, no. 18 (September 10, 2021): 5222. http://dx.doi.org/10.3390/ma14185222.

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This paper described unique hysteresis phenomena that appear in the hydrodynamic lubrication properties of dimpled thrust bearings. A seal-type thrust bearing specimen was textured with dimples. The load-carrying capacity and frictional torque were measured with a constant film thickness and compared to those of a dimple-free specimen. For examining the size of cavitation bubbles that occurred in various conditions, the lubricating area was observed during experiments. The used dimpled specimen produced the load-carrying capacity, and it exhibited an interesting hysteresis phenomenon, the difference in the values in the increasing and decreasing processes of rotational speed. The visualization test results revealed that the size of cavitation bubbles occurring within the dimples strongly affected this phenomenon. In addition, the dimpled specimen was able to reduce the frictional torque compared to the dimple-free specimen. However, the frictional torque did not show the hysteresis loop similar to that shown in the load-carrying capacity.
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46

Oliva, E., G. Berselli, and F. Pini. "Dynamic Identification of Industrial Robots from Low-Sampled Data." Applied Mechanics and Materials 328 (June 2013): 644–50. http://dx.doi.org/10.4028/www.scientific.net/amm.328.644.

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This paper proposes a fast and on-site method for the dynamic identification of industrial robots from low-sampled position and torque data. Owing to the basic architecture of the employed controller, only trapezoidal-velocity trajectories can be enforced for identification purposes. Differently from previous literature, where this kind of trajectories were performed with limited joint velocities and range of motions, the procedure proposed hereafter is characterized by fast movements performed on wide angular ranges. Furthermore, in order to identify the influence of friction without deriving complex friction models, a novel method is outlined that decouples frictional torques from gravitational, centrifugal and inertial ones. Finally, although multiple experiments of different kinds have been performed, inertial parameters are determined in one singular step, thus avoiding possible error increase due to sequential identification algorithms.
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47

Coleman, Simon G. S. "The Effect of Different Calculation Methods of Flywheel Parameters on the Wingate Anaerobic Test." Canadian Journal of Applied Physiology 23, no. 4 (August 1, 1998): 409–17. http://dx.doi.org/10.1139/h98-025.

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Researchers compared different methods of calculating kinetic parameters of friction-braked cycle ergometers, and the subsequent effects on calculating power outputs in the Wingate Anaerobic Test (WAnT). Three methods of determining flywheel moment of inertia and frictional torque were investigated, requiring "run-down" tests and segmental geometry. Parameters were used to calculate corrected power outputs from 10 males in a 30-s WAnT against a load related to body mass (0.075 kg•kg−1). Wingate Indices of maximum (5 s) power, work, and fatigue index were also compared. Significant differences were found between uncorrected and corrected power outputs and between correction methods (p < .05). The same finding was evident for all Wingate Indices (p < .05). Results suggest that WAnT must be corrected to give true power outputs and that choosing an appropriate correction calculation is important. Determining flywheel moment of inertia and frictional torque using unloaded run-down tests is recommended. Key words: sprint ergometry, power output, moment of inertia
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48

Kumai, Katsuya, Hiroki Fukushige, and Yoshimasa Takayama. "Modelling and Analysis of High Strain Rate Deformation at Elevated Temperature in Friction Stirring of Aluminum Alloys." Materials Science Forum 838-839 (January 2016): 110–15. http://dx.doi.org/10.4028/www.scientific.net/msf.838-839.110.

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Friction stirring is a fundamental process in the friction stir welding (FSW), and moreover, high strain rate deformation in elevated temperature to lead to extremely high ductility and fine grain size. In the present study, friction stirring process has been successfully modelled as a high temperature deformation depending on strain rate and temperature, assuming shear deformation of material in stir zone and generation of frictional heat by rotating tool. Axial load and torque during the process were estimated based on the model, and compared with the experimental data at two kinds of combination ratio in FSW of aluminum and Al-Mg alloy. It was, consequently, confirmed that the model could evaluate flow stress and strain rate from the experimental load and torque.
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49

Tzou, Gow-Yi, Yeong-Maw Hwang, and Sai-Chih Pan. "ANALYTICAL APPROACH TO ROTATING COMPRESSION OF A POROUS CYLINDER CONSIDERING CONSTANT SHEAR FRICTION." Transactions of the Canadian Society for Mechanical Engineering 41, no. 4 (November 2017): 571–80. http://dx.doi.org/10.1139/tcsme-2017-1040.

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The volume of the porous material in forming cannot be constant. However, the mass of the porous material remains constant; thereby making the derivations more complicated. A plastic mechanics analytical model with constant shear friction based on the slab method in this study is to explore the characteristics of the rotating compression of a porous cylinder. The effects of the frictional factor and frictional angle on the vertical stress, radial stress, average pressure, compression force, and rotating torque are systematically studied. The analytical results could be advantageous to the industries related to the forging of porous materials.
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50

Shi, Jun, Ren He, and Xiao Dan Gu. "Study and Design of Integrated System of Electromagnetic and Frictional Brake of Car." Advanced Materials Research 779-780 (September 2013): 739–46. http://dx.doi.org/10.4028/www.scientific.net/amr.779-780.739.

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To solve the brake thermal recession of traditional brake, an integrated brake of double-disc frictional and electromagnetic was proposed. For a certain car, the integrated brake of double-disc frictional with electromagnetic was designed. Through simulation and bench test, torque characteristic of the integrated brake was studied. Results showed that the theoretical designing curve agreed well with the experimental curve. The electromagnetic brake device of the integrated brake can provide a braking torque for 180-202N.m, thus it can effectively improve the brake thermal recession.
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