Precision Instrumentation for Rolling Element Bearing Characterization. Eric R. Marsh, Vincent C. Vigliano, Jeffrey R. Weiss, Alex W.
|
|
- Delilah Fleming
- 5 years ago
- Views:
Transcription
1 Precision Instrumentation for Rolling Element Bearing Characterization Eric R. Marsh, Vincent C. Vigliano, Jeffrey R. Weiss, Alex W. Moerlein Machine Dynamics Research Laboratory The Pennsylvania State University 331 Reber Building University Park, PA 16802, USA R. Ryan Vallance Precision Systems Laboratory The George Washington University 738 Phillips Hall nd St., N.W. Washington, DC, 20052, USA Abstract This article describes an instrument to measure the error motion of rolling element bearings. This challenge is met by simultaneously satisfying four requirements. First, an axial preload must be applied to seat the rolling elements in the bearing races. Second, one of the races must spin under the influence of an applied torque. Third, rotation of the remaining race must be prevented in a way that leaves the radial, axial/face, and tilt displacements free to move. Finally, the bearing must be fixtured and measured without introducing off-axis loading or other distorting influences. In the design presented here, an air bearing reference spindle with error motion of less than 10 nm rotates the inner race of the bearing under test. Non-influencing couplings are used to prevent rotation of the bearing outer race and apply an axial preload without distorting the bearing or influencing the measurement. Capacitive displacement sensors with 2 nm resolution target the nonrotating outer race. The error motion measurement repeatability is shown to be less than 25 nm. The paper closes with a discussion of how the instrument may be used to gather data with sufficient resolution to accurately estimate the contact angle of deep groove ball bearings. 1
2 1 Introduction Rolling element bearing performance improves over time as a result of ongoing metallurgical, tribological and manufacturing research and development. However, one of the remaining challenges in rolling element bearing applications is measurement of rotational accuracy. The instrument described in this article measures and characterizes the error motion of bearings intended for precision applications. Error motion is movement in the five rigid body degrees of freedom other than pure rotation. These five components of error motion are described with radial, tilt (angular), and axial measurements. However, most applications use at least two bearings to provide tilt stiffness. Accordingly, the radial and axial error motion components shown in Figure 1 are most relevant. Measurements made on the bearing under test reflect the combined contributions of errors in the bearing and the errors of the reference spindle. Figure 2 shows the decomposition of the measurement [4] separating these errors. The left-hand column of polar plots shows the synchronous and asynchronous components of a single radial measurement [15, 23]. The synchronous component is the repeatable path calculated by averaging several consecutive revolutions. Asynchronous error motion is the remaining error representing the revolution-byrevolution deviation from the synchronous component. The synchronous and asynchronous components have an intuitive interpretation in the frequency domain. Given some integer number of revolutions of data (greater than one), the synchronous component is contained in the frequency bins associated with integer multiples of the number of revolutions (or integer values of cycles per revolution or cpr). The asynchronous component appears in the remaining frequency bins, as illustrated in Figure 2. Rolling element bearings generally have proportionally greater asynchronous error motion because of the non-integer relationship between input shaft speed and rolling element rotation. For example, the cage rotation of a 6204 ball bearing is 38.5% of the inner race rotation. An error separation method may be applied to distinguish the synchronous error motion of the ball bearing under test from the reference air bearing spindle error. However, the synchronous error of the reference spindle is small compared to most rolling element bearings and is ignored in the results presented here. This is also true of the asynchronous component, 2
3 which is about 1 nm for the reference spindle while typically 100 nm for rolling element bearings. Asynchronous error motion presents an additional challenge to the metrologist in that not all of the apparent motion between the displacement sensor and target should be assigned to the bearing under test because of test stand vibration, environmental influences, and other instrumentation or sensor noise. One of the biggest challenges in accurately measuring ball bearings is minimizing the contribution of external effects so that a reliable reading of asynchronous error is achieved. The instrument presented here benefits from previous work in the techniques used to accurately quantify the performance of axes of rotation [10, 14, 16]. Precision engineering pioneers such as Tlusty and Donaldson inspired four decades of work to reduce axis of rotation measurement uncertainty through clever hardware and analytical developments [5, 6, 7, 22]. Sensors and data acquisition systems also advanced to the point where hardware design is often the largest remaining contributor to measurement uncertainty [8, 20, 18]. 2 Background Rolling element bearing measurement techniques may be broadly categorized by whether data are collected in situ or off-line on a dedicated instrument. In situ approaches have received the most interest for condition-based monitoring of mission-critical components. However, the interpretation of measurement results is complicated by the dynamic interaction of the bearing with its surrounding structure and environment [9, 11, 13, 21]. Off-line testing is the best way to reliably isolate a bearing from environmental and structural influences [10]. Properly designed instrumentation also offers a practical means of providing data for bearing model development. The last 30 years have seen several significant improvements in off-line bearing testing equipment and practice. One of the earliest commercially available instruments is the PDI Anderometer R, which characterizes bearing performance with three frequency ranges in units dubbed Anderons (1 Anderon is 1 micro-inch per radian of rotation). The low measurement range is from 1.67 to 10 times the shaft speed, medium is 10 to 60 times the shaft speed, and the high range is 60 to 300 times the shaft speed. A bearing is quantified in each of the three frequency ranges with a single number. 3
4 In unpublished work, Professional Instruments Co. began designing custom instrumentation for measuring bearing error motion in the early 1980 s in an effort led by Gene Dahl. The significant contribution of their work was the integration of high resolution capacitive displacement sensors with an ultra-precision air bearing spindle to enable accurate measurements with several khz bandwidth. This approach represented a significant departure from the Anderometer in both design and implementation; the PICo instruments allowed data collection over many revolutions and at thousands of data points per revolution, as triggered by optical encoders. Bouchard, Lau, and Talke measured asynchronous radial errors for both ball and fluid bearing spindles in the time and frequency domains using spindles mounted on a vibration isolation table [5]. They also used a capacitive displacement sensor to measure error motion. The asynchronous component was calculated by eliminating the repeatable signal from the timevarying displacement signal between the stationary probe and the rotating spindle. Statistical methods were used to calculate the asynchronous component in both the time and frequency domains. McFadden and Smith developed an experimental test rig to measure the vibration produced by a defect on the inner race of a ball bearing under a constant radial load [17]. Their instrument used an accelerometer to measure vibrations that were later correlated to the shaft rotation frequency. Noguchi et al. returned to the reference spindle-type instrument layout to measure the radial motion of the outer race of a bearing with the inner race rotated by an aerostatic spindle [20]. Load cells measured the axial load and torque while two orthogonal displacement sensors measured the radial error; a rotary encoder triggered data sampling. With the benefit of modern computing and data acquisition hardware, it is now practical to implement the PICo/Noguchi-style instrument with higher usable bandwidth and accuracy. Such a design improves resolution in both the time and frequency domains along with precisely controllable operating conditions to explore the effects of geometric and manufacturing problems such as misalignment and out-of-round components. Furthermore, issues such as bearing load, wear, and lubrication can be exhaustively studied in a controlled manner. 4
5 3 Bearing Analyzer The bearing analyzer instrument is shown in Figure 3 and Figure 4. Components chosen for the instrument allow testing at axial loads up to 100 N and speeds up to 10 krpm. An ultraprecision air bearing spindle (Professional Instruments BLOCK-HEAD spindle with Heidenhain ERO 1221 rotary encoder) spins the inner race of the bearing under test. The radial error motion of this spindle is less than 10 nm and the axial error motion is less than 5 nm. In most cases, it is reasonable to neglect the small contribution of this error to the bearing measurement. However, it is possible to accurately remove the reference spindle s contribution using an error separation technique such as Donaldson reversal [7]. Capacitive displacement sensors with 10 µm range and 2 nm resolution (Lion Precision C1- C capacitance probe with a DMT10 driver) measure the relative motion between the reference spindle s stator and the outer race. Capacitive sensors require that the target electrode be grounded. In this instrument configuration, the target electrode is the steel bearing retaining cup that does not rotate and is readily grounded. The inner race of the bearing under test is secured to the reference spindle on a lapped spherical carbide pilot sized with a light drive interference (FN) fit. The outer bearing race has a locational interference (LN) fit within the steel bearing retaining cup. The retaining cup also has a torque arm that prevents rotation of the outer race while enabling measurement of the torque. The torque arm prevents rotation but the remaining five degrees of freedom are unconstrained and free to move. This decoupling is achieved with a steel pin with lapped, carbide hemispherical ends that fit into lapped conical features. The axial preload is applied with a similar pin to minimize the transmission of off-axis loads to the bearing. The result is axial load and rotation constraint with the five remaining degrees of freedom almost completely unconstrained and uninfluenced by the test apparatus. A load cell is placed in line with the torsional restraint to allow torque measurement with repeatability of 1 mn-m using a piezoelectric sensor (Kistler 9303). Data acquisition and analysis is carried out using a National Instruments DAQ board (PCI- 6110E) and software written in LabWindows/CVI. Analog anti-alias filtering is done prior to digitization with a Krohn-Hite 3360 tunable filter. All error motion computations are made 5
6 in accordance with the procedures set by ANSI/AFBMA Standard , Rolling Bearing Vibration and Noise (Methods of Measuring) and ANSI/ASME B89.3.4M Axes of Rotation, Methods for Specifying and Testing [3, 4]. The software provides integrated motor control, thermal drift compensation, and data acquisition of the displacement and force sensors synchronized and triggered by the optical rotary encoder. 4 Results Sample measurement results are shown in Figure 5 from single-row, deep groove ABEC bearings. Table 1 lists the standardized 6204 bearing dimensions. Rolling element bearings exhibit significant asynchronous error motion because of the planetary-type kinematics of the inner race, outer race, and rotating balls that lead to noninteger relationships between shaft speed and the key rotational frequencies. Consecutive rotations will not yield identical error motion results even in the absence of measurement errors. However, a series of tests show similar overall characteristics, especially when averaged over multiple revolutions for the purpose of computing the error motion values specified in the ASME/ANSI B89.3.4M standard. The number of revolutions included in a test is chosen by the metrologist [4]. Experience shows that the shape of the synchronous error motion takes quite a few revolutions to emerge, especially for frequency components near, but not precisely equal to, integer multiples of the input (e.g., inner bearing race) speed. In general, averaging additional revolutions of data reduces the synchronous error motion and increases the asynchronous. In the results that follow, 512 revolutions were used in all computations. This number of revolutions was found to give stable results while providing sufficient frequency domain resolution within a reasonable amount of test time. 4.1 Measurement repeatability Table 2 shows data from consecutive measurements taken on a 6204 ball bearing at 1000 RPM for 512 revolutions under 100 N of axial preload. The tabulated motion and torque values have a standard deviation of approximately 15 to 20% of the mean. In the case of the 6204 bearing, 6
7 the repeatability is better than 100 nm for the overall magnitude of the radial error motion, and torque repeatability is better than 1 mn-m. The most significant (i.e., largest) frequency component in the data tabulated in Table 2 occurs at the cage rotation frequency at 38.5% of the shaft rotation frequency. This component is below the range included in the three frequency bands of the Anderometer. For this reason, the low-medium-high band results, which start at 1.67 times the shaft rotation speed, do not share the same general magnitude as the asynchronous component, which includes all noninteger multiples of the shaft rotation frequency down to zero Hz. The instrument repeatability is also apparent in the frequency domain. Figure 6 shows four FFT plots of the radial error motion calculated from 512 revolutions of data sampled 1024 times per revolution. As before, the results show little variation in consecutive tests. Furthermore, the frequency components associated with particular geometric defects of the ball bearing occur at identical frequencies and similar amplitudes for all tests, as summarized in Table 3. The high consistency in the frequency domain data suggests that the bearing frequency components combine in somewhat different patterns in the time domain because of the non-integer frequencies at which they occur. As a result, the FFTs are very similar while the polar plots show more variation. 4.2 Axial preload testing Testing was carried out to investigate the instrument performance with various axial loads applied to the bearing. Figure 7 shows the synchronous and asynchronous error motion values of a 6204 bearing at axial preload increasing in steps of 10 N. As before, these error motion values are computed from 512 revolutions of data taken at 1000 rpm. Axial loads above 30 N result in consistent values of synchronous error motion in the bearing. The asynchronous component also reaches a roughly constant value above 30 N until it jumps to a second plateau above 80 N. Table 4 shows additional information from the same testing. It is important that the axial load be sufficient to hold the bearing races in proper contact with the rotating rolling elements. The table shows an abrupt transition in error motion and bearing torque between 30 and 40 N. The bearing balls and races are loaded sufficiently to achieve proper contact above 7
8 30 N for the 6204 deep groove bearing. 5 Discussion The previous section demonstrates the repeatability and resolution of the proposed bearing error motion instrument. This section introduces an application of the instrument to a problem of interest to end users of rolling element bearings as well as the bearing modeling community. An interesting facet of ball bearing analysis is the precise determination of the contact angle between the balls and the inner and outer races. The contact angle tends to vary somewhat with axial load because of the Hertzian contact deformation between the races and the rolling elements. In practice it is difficult to infer the contact angle from error motion data because of finite resolution in the frequency domain. The use of a single measured bearing defect frequency, such as the cage rotation frequency, can be less accurate than simply using the nominal contact angle calculated from the standardized bearing geometry. This is because bearing defect frequencies are not particularly sensitive to contact angle. Despite this challenge, the computation of the effective contact angle is critical in bearing modeling and troubleshooting applications. First, consider the measured cage rotation frequency as a means of estimating the effective contact angle of a ball bearing. The cage rotation frequency f cage is typically slightly less than half the inner race (shaft) rotational frequency f s and is a function of ball diameter b, pitch diameter p, and the contact angle α. f cage = f s 2 (1 bp cos α ) (1) Linearizing the cage rotation frequency with respect to the nominal value of the contact angle α 0 leads to an equation for the sensitivity of contact angle to small changes in cage frequency. or f cage = ( fs 2 ) b p sinα 0 α (2) ( ) 2p fcage α = (3) b sinα 0 f s 8
9 The sensitivity of the contact angle to the measured cage rotation frequency is limited by the number of revolutions captured in the data sample. For example, 512 revolutions of data yield a frequency resolution of 1/512 of the shaft speed f s. For the 6204 bearing, with a nominal contact angle of 15 degrees, the computed correction in contact angle is nearly two degrees over half the width of one frequency bin. This is insufficient for accurate estimation of the actual bearing contact angle. Therefore, we use several spectral peaks to improve the accuracy of the calculated contact angle. The bearing instrument is well suited for this because the measured spectral peaks may be relied upon to represent bearing harmonics and not other environmental influences. Furthermore, the peaks are sharp and easily identified because the data sampling is triggered by an optical encoder measuring shaft orientation angle, rather than relying on constant-speed rotation during testing. A number of spectral peaks appear in the FFT of the error motion and may be matched to integer combinations of the basic bearing defect frequencies. In addition to the cage rotation frequency, there is the cage rotation relative to the inner race f ci that is typically a little more than half the shaft rotation frequency. f ci = f s 2 (1 + bp cos α ) (4) The ball pass frequencies of the inner and outer races are computed from f c age and f ci using the number of rolling elements n. f bpo = nf cage (5) f bpi = nf ci (6) The rotational frequency of the rolling elements is given by ( f r = f ( ) ) 2 s p b 1 2 b p cos α (7) 9
10 Finally, a ball defect will appear at twice its rotational frequency f r because the defect will strike the inner and outer race once per revolution. f bp = 2f r (8) These frequencies may be calculated using standardized bearing geometry data with typical error of 0.2% or less, as demonstrated here for a 6204 bearing. To use a set of experimentallymeasured defect frequencies to improve our estimates of the bearing geometry, the defect frequency equations are linearized in terms of small deviations of ball diameter b, pitch diameter p and contact angle α. This yields a set of equations relating the predicted defect frequencies f (using the nominal geometry values b 0, p 0, and α 0, plus a small correction ˆf, to the measured defect frequencies f. f f + ˆf (9) where f = f cage f ci f r f bpo f bpi = f s b0 cos α0 p 0 b0 cos α0 p 0 p 0 b 0 b0 cos2 α 0 p 0 n n + b0n cos α0 p 0 b0 cos α0n p 0 (10) ˆf = ˆf cage ˆf ci ˆf r ˆf bpo ˆf bpi =. f i b.. f i p.. f i α. b p α = A x 10
11 = f s b 0 cos α 0 2p 0 1 b 0 1 p 0 tan α 0 1 b 0 1 p 0 tan α 0 cos α0 b 0 p2 0 cos α 0 b 3 0 cos α0 p 0 + p0 b 2 0 cos 2sin α 0 α0 n b 0 n p 0 ntan α 0 n b 0 n p 0 ntan α 0 b p α (11) These linearized equations may be used to compute the small deviation of the ball and pitch diameters along with the contact angle by matching the predicted and measured defect frequencies appearing in experimentally-gathered FFT spectra. Table 5 shows the measured and predicted error frequencies for a sample 6204 ball bearing measured under a 100 N axial load. The frequencies are listed as multiples of the shaft rotation speed f s. ˆf = f f = TA x (12) The matrix A is 5 3 and relates the frequency corrections to the geometry corrections. The matrix T is of dimension l 5 and contains the integer values relating the 5 bearing defect frequencies to the l spectral peaks identified in the experimental data and listed in the second column of Table 5. Sixteen spectral peaks were used to improve the estimate of bearing geometry under load. Matching 16 peaks allows better correction of the contact angle as well as the effective ball and pitch diameters, both of which are affected by the Hertzian-type contact of the bearing. T T = (13) The resulting system of equations is overconstrained and ill-conditioned, necessitating a singular value decomposition (SVD) solution. There are 16 equations and just three unknowns (the pitch diameter correction p, ball diameter correction d, and the contact angle correction 11
12 α). In this example, the singular values are 3.264, 0.491, and 0. The SVD solution eliminates the singularity and solves the problem with a numerically stable algorithm. The correction values are b = 4 µm, p = 1 µm, and α = 0.8 degrees for an effective contact angle of 14.2 degrees. 6 Conclusion This paper presents an instrument designed to measure error motions of precision rolling element bearings at various loads and speeds. The results are repeatable to the 100 nm level and may be used to identify bearing characteristics without the influence of the dynamics of a larger, compliant environment. Sample tests under varying axial load show that the error motion results are stable once sufficient load is applied to properly seat the rolling elements in the raceways. Additional testing of the effective contact angle shows that a significantly improved estimate of bearing geometry is obtained by comparing the predicted bearing fault frequencies with the measured values. This is important in contact angle calculations because without multiple spectral peaks to compare, the contact angle will be inaccurate. 12
13 References [1] Aini, R., Rahnejat, H., and Gohar, R. International Journal of Machine Tools & Manufacture 30, 1 (1990), [2] Aini, R., Rahnejat, H., and Gohar, R. Proceedings of the Institution of Mechanical Engineers, Part C: Journal of Mechanical Engineering Science 209, 2 (1995), [3] ANSI/AFBMA. Standard , rolling bearing vibration and noise, methods of measuring. Anti-Friction Bearing Manufacturers Association (1987). [4] ANSI/ASME. Standard B89.3.4M, axes of rotation; methods for specifying and testing. American Society of Mechanical Engineers (1985). [5] Bouchard, G., Lau, L., and Talke, F. E. IEEE Transactions on Magnetics MAG-23, 5 (1987), [6] Deeyiengyang, S., and Ono, K. Journal of Information Storage and Processing Systems 3, 1-2 (2001), [7] Donaldson, R. R. Annals of the CIRP 21, 1 (1972), [8] Grejda, R. D., Marsh, E. R., and Vallance, R. R. Precision Engineering 29, 1 (2005), [9] Gupta, P. Advanced dynamics of rolling elements. Springer-Verlag, New York, [10] Harris, T. A. Rolling bearing analysis, 4 ed. John Wiley and Sons, NY, [11] Houpert, L. Journal of Tribology 119 (1997), [12] Jones, A. American Society of Mechanical Engineers Transactions Journal of Basic Engineering Series D 82, 2 (1960), [13] Kahn, H. Evaluation Engineering 14, 5 (1975), [14] Lim, T., and Singh, R. Journal of Sound and Vibration 139, 2 (1990),
14 [15] Marsh, E., Couey, J., and Vallance, R. Journal of Manufacturing Science and Engineering, Transactions of the ASME 128, 1 (2006), [16] Martin, D. L., Tabenkin, A., and Parsons, F. International Journal of Machine Tool Manufacturers 35, 2 (1995), [17] McFadden, P. D., and Smith, J. D. Journal of Sound and Vibration 96, 1 (1984), [18] Noguchi, S., Hiruma, K., Kawa, H., and Kanada, T. Precision Engineering 29, 1 (2005), [19] Noguchi, S., and Ono, K. Precision Engineering 28, 4 (2004), [20] Noguchi, S., Tanaka, K., and Ono, K. IEEE Transactions on Magnetics 35, 2 (1999), [21] Tandon, N., and Choudhury, A. Journal of Sound and Vibration 205, 3 (1997), [22] Tlusty, J. Microtecnic 13, 4 (1959), [23] Vigliano, V. C. Computer control for precision bearing analysis. Master s thesis, The Pennsylvania State University, [24] Walford, T. L. H., and Stone, B. J. Proceedings of the Institution of Mechanical Engineers, Part C: Mechanical Engineering Science 197 (1983),
15 Bore diameter 20 mm Outer diameter 47 mm Ball diameter, b mm Pitch diameter, p 33.5 mm Ball count, n 8 Contact angle, α 15 Table 1: 6204 bearing parameters 15
16 Error motion (nm) RMS error motion (nm) RMS torque (mn-m) Synch Asynch Asynch Low Med High Low Med High Test P-V P-V 4σ mean σ Table 2: Repeatability results for radial error motion and torque. The low, medium, and high ranges are multiples of the input shaft speed, as reported in Anderometer-style measurements. 16
17 Error motion amplitude at bearing defect frequencies (nm) f c 2f c f bp f bpo f bpi Test (0.385f s) (0.771f s) (2.000f s) (3.084f s) (4.916f s) mean σ Table 3: Frequency and amplitude of bearing defect frequencies in consecutive measurements. 17
18 Total error motion (nm) RMS error motion (nm) RMS torque (mn-m) Synch Asynch Asynch Low Med High Low Med High Test P-V P-V 4σ Table 4: Radial error motion and bearing torque with varying axial preload. 18
19 Error Frequency Measured Predicted Corrected Predicted Corrected amplitude (nm) component frequency frequency frequency error (%) error (%) 58.5 f cage f cage f r 3f cage f bpo f r f cage f r + f cage f r + f cage f r f r + f cage f cage f r f bpo f r f cage f r f cage f r f cage f cage Table 5: 6204 bearing fault frequencies normalized by inner race speed. 19
20 Captions Figure 1. Axial (a) and radial (b) error motion associated with a rolling element bearing. The proposed instrument can also be used to measure the remaining rigid body motion (tilt) when appropriate. Figure 2. Separation of measurement data into synchronous and asynchronous components of rolling element bearing error motion and artifact form error (cpr is cycles per revolution; a two-lobe error will appear in the cpr = 2 frequency bin). Note that the 1 cpr bin (eccentricity) is always removed from radial measurements. Figure 3. Bearing analyzer with motorized air bearing reference spindle. Figure 4. Cross sectional view of the bearing error motion instrument. Figure 5. Sample polar plot and FFT results from a 6204 bearing. The synchronous error is quite small (33 nm) but the asynchronous error motion has a total excursion of 289 nm during the 512 revolutions of the test. However, 95% of the error motion values fall within a 160 nm band as suggested by the nearly normal distribution. The FFT allows identification of individual frequency components. Figure 6. Repeatability results from four consecutive tests on a single 6204 bearing. Figure 7. Radial error motion of a 6204 bearing as a function of axial preload. 20
21 Synchronous error (nm) Axial Load (N) Asynchronous error (nm)
22 Measurement locations Preload force Axial preload pin Bearing retainer cup Bearing Pilot Chuck adapter Spacer Spindle rotor A Torque arm Spindle stator Mounting flange Frameless motor Rotary encoder Section A-A Non-rotating components are hatched A
23 Axial load piston Bearing retaining cup with torque arm Radial error motion probe locations Bearing under test (inside cup) rot. Motorized air bearing master spindle with rotary encoder
24 Axial error motion Displacement indicator Radial error motion (a) (b) Non-rotating components are cross-hatched
25 0 1 2 cpr cpr f c 75 f c Radial error (nm) 2f c f bpo f bp 4-f c 4+f c Radial error (nm) 2f c f bpo f bp 4-f c 4+f c cpr cpr f c 75 f c Radial error (nm) 2f c f bp f bpo 4-f c 4+f c Radial error (nm) 2f c f bpo f bp 4-f c 4+f c
26 nm nm cpr cpr FFT FFT Error motion of ball bearing plus spindle: integer Fourier components Synchronous ball bearing error motion Raw probe data Initial processing Error separation (requires at least one additional measurement) Ball bearing Asynchronous: non-integer Fourier components Synchronous spindle error motion Reference spindle nm 80 FFT nm 80 FFT cpr cpr
27 125 nm f cage Synch 33 nm Asynch P-V 289 nm 4σ 160 nm -250 nm 250 2f cage f ballpass fouter cpr
Development of Measuring System for the Non-Repetitive Run-Out(NRRO) of Ball Bearing
Journal of Engineering Mechanics and Machinery (207) Vol. 2, Num. Clausius Scientific Press, Canada Development of Measuring System for the Non-Repetitive Run-Out(NRRO) of Ball Bearing Y. Chen,a,*, G.F.
More informationON NUMERICAL ANALYSIS AND EXPERIMENT VERIFICATION OF CHARACTERISTIC FREQUENCY OF ANGULAR CONTACT BALL-BEARING IN HIGH SPEED SPINDLE SYSTEM
ON NUMERICAL ANALYSIS AND EXPERIMENT VERIFICATION OF CHARACTERISTIC FREQUENCY OF ANGULAR CONTACT BALL-BEARING IN HIGH SPEED SPINDLE SYSTEM Tian-Yau Wu and Chun-Che Sun Department of Mechanical Engineering,
More informationObservation and analysis of the vibration and displacement signature of defective bearings due to various speeds and loads
Observation and analysis of the vibration and displacement signature of defective bearings due to various speeds and loads Alireza-Moazen ahmadi a) Carl Howard b) Department of Mechanical Engineering,
More informationNew Representation of Bearings in LS-DYNA
13 th International LS-DYNA Users Conference Session: Aerospace New Representation of Bearings in LS-DYNA Kelly S. Carney Samuel A. Howard NASA Glenn Research Center, Cleveland, OH 44135 Brad A. Miller
More informationKINEMATIC SPINDLES FOR PORTABLE ROUNDNESS INSTRUMENTS
KINEMATI SPINDLES FOR PORTALE ROUNDNESS INSTRUMENTS Eric Wolsing, King-Fu Hii, R Ryan Vallance Precision Systems Laboratory, University of Kentucky, Lexington, KY Abstract This paper describes the design
More informationA nonlinear dynamic vibration model of defective bearings: The importance of modelling the finite size of rolling elements
A nonlinear dynamic vibration model of defective bearings: The importance of modelling the finite size of rolling elements Alireza Moazenahmadi, Dick Petersen and Carl Howard School of Mechanical Engineering,
More informationNonlinear Rolling Element Bearings in MADYN 2000 Version 4.3
- 1 - Nonlinear Rolling Element Bearings in MADYN 2000 Version 4.3 In version 4.3 nonlinear rolling element bearings can be considered for transient analyses. The nonlinear forces are calculated with a
More informationAnalysis of dynamic characteristics of a HDD spindle system supported by ball bearing due to temperature variation
Analysis of dynamic characteristics of a HDD spindle system supported by ball bearing due to temperature variation G. H. Jang, D. K. Kim, J. H. Han, C. S. Kim Microsystem Technologies 9 (2003) 243 249
More informationVIBRATION TRANSMISSION THROUGH SELF-ALIGNING (SPHERICAL) ROLLING ELEMENT BEARINGS: THEORY AND EXPERIMENT
Journal of Sound and Vibration (1998) 215(5), 997 1014 Article No. sv981579 VIBRATION TRANSMISSION THROUGH SELF-ALIGNING (SPHERICAL) ROLLING ELEMENT BEARINGS: THEORY AND EXPERIMENT T. J. ROYSTON AND I.
More informationCHAPTER 4 FAULT DIAGNOSIS OF BEARINGS DUE TO SHAFT RUB
53 CHAPTER 4 FAULT DIAGNOSIS OF BEARINGS DUE TO SHAFT RUB 4.1 PHENOMENON OF SHAFT RUB Unwanted contact between the rotating and stationary parts of a rotating machine is more commonly referred to as rub.
More informationThe Influence of location of balls and ball diameter difference in rolling bearings on the nonrepetitive runout (NRRO) of retainer revolution
Precision Engineering 9 (005) 8 The Influence of location of balls and ball diameter difference in rolling bearings on the nonrepetitive runout (NRRO) of retainer revolution Shoji Noguchi a,, Kentaro Hiruma
More informationDesign, Modelling and Analysis of a Single Raw Four Point Angular Contact Split Ball Bearing to Increase its Life.
Design, Modelling and Analysis of a Single Raw Four Point Angular Contact Split Ball Bearing to Increase its Life. Pranav B. Bhatt #1, Prof. N. L. Mehta *2 #1 M. E. Mechanical (CAD/CAM) Student, Department
More informationROLLING FRICTION TORQUE IN MICROSYSTEMS
Proceedings of VAREHD 15, Suceava, May 6-8, 010 170 ROLLING FRICTION TORQUE IN MICROSYSTEMS D. N. Olaru, C. Stamate, A. Dumitrascu, Gh. Prisacaru Department of Machine Elements and Mechatronics,Technical
More informationTribology Prof. Dr. Harish Hirani Department of Mechanical Engineering Indian Institute of Technology, Delhi
Tribology Prof. Dr. Harish Hirani Department of Mechanical Engineering Indian Institute of Technology, Delhi Lecture No. # 29 Rolling Element Bearings (Contd.) Welcome to 29 th lecture of video course
More informationDESIGN AND MODELING OF A KINEMATICALLY-CONSTRAINED TRACTION-DRIVE SPINDLE FOR MICRO MACHINING
DESIGN AND MODELING OF A KINEMATICALLY-CONSTRAINED TRACTION-DRIVE SPINDLE FOR MICRO MACHINING Christopher J. Morgan 1, R. Ryan Vallance, Eric R. Marsh 3, 1 Mechanical Engineering, University of Kentucky
More informationPARAMETER ESTIMATION IN IMBALANCED NON-LINEAR ROTOR-BEARING SYSTEMS FROM RANDOM RESPONSE
Journal of Sound and Vibration (1997) 208(1), 1 14 PARAMETER ESTIMATION IN IMBALANCED NON-LINEAR ROTOR-BEARING SYSTEMS FROM RANDOM RESPONSE Department of Mechanical Engineering, Indian Institute of Technology,
More informationBall Bearing Model Performance on Various Sized Rotors with and without Centrifugal and Gyroscopic Forces
Ball Bearing Model Performance on Various Sized Rotors with and without Centrifugal and Gyroscopic Forces Emil Kurvinen a,, Jussi Sopanen a, Aki Mikkola a a Lappeenranta University of Technology, Department
More informationKey words: Polymeric Composite Bearing, Clearance, FEM
A study on the effect of the clearance on the contact stresses and kinematics of polymeric composite journal bearings under reciprocating sliding conditions Abstract The effect of the clearance on the
More informationNON-LINEAR BEARING STIFFNESS PARAMETER EXTRACTION FROM RANDOM RESPONSE IN FLEXIBLE ROTOR-BEARING SYSTEMS
Journal of Sound and Vibration (1997) 3(3), 389 48 NON-LINEAR BEARING STIFFNESS PARAMETER EXTRACTION FROM RANDOM RESPONSE IN FLEXIBLE ROTOR-BEARING SYSTEMS Department of Mechanical Engineering, Indian
More informationBearing Internal Clearance and Preload
. Bearing Internal Clearance and Preload. Bearing internal clearance Bearing internal clearance is the amount of internal free movement before mounting. As shown in Fig.., when either the inner ring or
More informationUSING ROTOR KIT BENTLY NEVADA FOR EXPERIMENTS WITH AEROSTATIC BEARINGS
USING ROTOR KIT BENTLY NEVADA FOR EXPERIMENTS WITH AEROSTATIC BEARINGS ŠIMEK, J. 1, KOZÁNEK, J., STEINBAUER, P., NEUSSER, Z. 3 1 TECHLAB Ltd., Prague, Institute of Thermomechanics AS CR 3 CTU in Prague,
More informationComparison of Models for Rolling Bearing Dynamic Capacity and Life
2013 STLE Annual Meeting & Exhibition May 5-9, 2013 Detroit Marriott at the Renaissance Center Detroit, Michigan, USA Comparison of Models for Rolling Bearing Dynamic Capacity and Life Rolling-Element
More informationPrecision Ball Screw/Spline
58-2E Models BNS-A, BNS, NS-A and NS Seal Outer ring Shim plate Seal Spline nut Seal Collar Shim plate Seal End cap Ball Outer ring Ball screw nut Outer ring Ball Retainer Retainer Outer ring Point of
More informationLeast square curve fitting technique for processing time sampled high speed spindle data. S. Denis Ashok and G.L. Samuel*
256 Int. J. Manufacturing Research, Vol. 6, No. 3, 2011 Least square curve fitting technique for processing time sampled high speed spindle data S. Denis Asho and G.L. Samuel* Department of Mechanical
More information( ) 5. Bearing internal load distribution and displacement. 5.1 Bearing internal load distribution
5. internal load distribution and displacement 5. internal load distribution This section will begin by examing the effect of a radial load F r and an axial load F a applied on a single-row bearing with
More informationNoise and Vibration of Electrical Machines
Noise and Vibration of Electrical Machines P. L. TIMÄR A. FAZEKAS J. KISS A. MIKLOS S. J. YANG Edited by P. L. Timär ш Akademiai Kiadö, Budapest 1989 CONTENTS Foreword xiii List of symbols xiv Introduction
More informationModeling Method Analysis of the Friction Torque for High Speed Spindle Bearing
MATEC Web of Conferences 75, 0308 (08) https://doi.org/0.05/matecconf/08750308 IFCAE-IOT 08 Modeling Method Analysis of the Friction Torque for High Speed Spindle Bearing Songsheng Li,, HuihangChen,, Haibing
More informationAPVC2009. Forced Vibration Analysis of the Flexible Spinning Disk-spindle System Represented by Asymmetric Finite Element Equations
Forced Vibration Analysis of the Flexible Spinning Disk-spindle System Represented by Asymmetric Finite Element Equations Kiyong Park, Gunhee Jang* and Chanhee Seo Department of Mechanical Engineering,
More informationValidation of a physics-based model for rolling element bearings with diagnosis purposes
8th European Workshop On Structural Health Monitoring (EWSHM 2016), 5-8 July 2016, Spain, Bilbao www.ndt.net/app.ewshm2016 Validation of a physics-based model for rolling element bearings with diagnosis
More informationStability Analysis and Research of Permanent Magnet Synchronous Linear Motor
Stability Analysis and Research of Permanent Magnet Synchronous Linear Motor Abstract Rudong Du a, Huan Liu b School of Mechanical and Electronic Engineering, Shandong University of Science and Technology,
More informationACCELEROMETER BASED IN SITU RUNOUT MEASUREMENT OF ROTORS
7th International DAAAM Baltic Conference "INDUSTRIAL ENGINEERING" 22-24 April 21, Tallinn, Estonia ACCELEROMETER BASED IN SITU RUNOUT MEASUREMENT OF ROTORS Kiviluoma, P., Porkka, E., Pirttiniemi, J. &
More informationROLLER BEARING FAILURES IN REDUCTION GEAR CAUSED BY INADEQUATE DAMPING BY ELASTIC COUPLINGS FOR LOW ORDER EXCITATIONS
ROLLER BEARIG FAILURES I REDUCTIO GEAR CAUSED BY IADEQUATE DAMPIG BY ELASTIC COUPLIGS FOR LOW ORDER EXCITATIOS ~by Herbert Roeser, Trans Marine Propulsion Systems, Inc. Seattle Flexible couplings provide
More informationJournal of Physics: Conference Series. Related content. Recent citations PAPER OPEN ACCESS
Journal of Physics: Conference Series PAPER OPEN ACCESS Ball's motion, sliding friction, and internal load distribution in a high-speed ball bearing subjected to a combined radial, thrust, and moment load,
More informationChapter 3. Experimentation and Data Acquisition
48 Chapter 3 Experimentation and Data Acquisition In order to achieve the objectives set by the present investigation as mentioned in the Section 2.5, an experimental set-up has been fabricated by mounting
More informationA methodology for fault detection in rolling element bearings using singular spectrum analysis
A methodology for fault detection in rolling element bearings using singular spectrum analysis Hussein Al Bugharbee,1, and Irina Trendafilova 2 1 Department of Mechanical engineering, the University of
More informationRobust shaft design to compensate deformation in the hub press fitting and disk clamping process of 2.5 HDDs
DOI 10.1007/s00542-016-2850-2 TECHNICAL PAPER Robust shaft design to compensate deformation in the hub press fitting and disk clamping process of 2.5 HDDs Bumcho Kim 1,2 Minho Lee 3 Gunhee Jang 3 Received:
More informationScattered Energy of Vibration a novel parameter for rotating shaft vibration assessment
5 th Australasian Congress on Applied Mechanics, ACAM 007 10-1 December 007, Brisbane, Australia Scattered Energy of Vibration a novel parameter for rotating shaft vibration assessment Abdul Md Mazid Department
More informationParametrically Excited Vibration in Rolling Element Bearings
Parametrically Ecited Vibration in Rolling Element Bearings R. Srinath ; A. Sarkar ; A. S. Sekhar 3,,3 Indian Institute of Technology Madras, India, 636 ABSTRACT A defect-free rolling element bearing has
More informationThe basic dynamic load rating C is a statistical number and it is based on 90% of the bearings surviving 50 km of travel carrying the full load.
Technical data Load Rating & Life Under normal conditions, the linear rail system can be damaged by metal fatigue as the result of repeated stress. The repeated stress causes flaking of the raceways and
More informationModeling and simulation of multi-disk auto-balancing rotor
IJCSI International Journal of Computer Science Issues, Volume, Issue 6, November 6 ISSN (Print): 69-8 ISSN (Online): 69-78 www.ijcsi.org https://doi.org/.9/66.8897 88 Modeling and simulation of multi-disk
More informationCS491/691: Introduction to Aerial Robotics
CS491/691: Introduction to Aerial Robotics Topic: Midterm Preparation Dr. Kostas Alexis (CSE) Areas of Focus Coordinate system transformations (CST) MAV Dynamics (MAVD) Navigation Sensors (NS) State Estimation
More informationISO INTERNATIONAL STANDARD. Test code for machine tools Part 7: Geometric accuracy of axes of rotation
INTERNATIONAL STANDARD ISO 230-7 First edition 2006-11-15 Test code for machine tools Part 7: Geometric accuracy of axes of rotation Code d'essai des machines-outils Partie 7: Exactitude géométrique des
More informationDispersion of critical rotational speeds of gearbox: effect of bearings stiffnesses
Dispersion of critical rotational speeds of gearbox: effect of bearings stiffnesses F. Mayeux, E. Rigaud, J. Perret-Liaudet Ecole Centrale de Lyon Laboratoire de Tribologie et Dynamique des Systèmes Batiment
More informationMisalignment Fault Detection in Dual-rotor System Based on Time Frequency Techniques
Misalignment Fault Detection in Dual-rotor System Based on Time Frequency Techniques Nan-fei Wang, Dong-xiang Jiang *, Te Han State Key Laboratory of Control and Simulation of Power System and Generation
More informationEffect of an hourglass shaped sleeve on the performance of the fluid dynamic bearings of a HDD spindle motor
DOI 10.1007/s00542-014-2136-5 Technical Paper Effect of an hourglass shaped sleeve on the performance of the fluid dynamic bearings of a HDD spindle motor Jihoon Lee Minho Lee Gunhee Jang Received: 14
More informationApplication of a self-calibratable rotary encoder
Application of a self-calibratable rotary encoder Tsukasa Watanabe, Hiroyuki Fujimoto National Metrology Institute of Japan(NMIJ) National Institute of Advanced Industrial Science and Technology (AIST)
More informationNew Way Porous Gas Bearings as Seals. Bearings Seals
New Way Porous Gas Bearings as Seals Bearings Seals 1 New Way Overview Founded January 1994. Aston, Pa. 15 miles south of Philadelphia 54 employees 35,000 sq ft facility, Environmentally Controlled Precision
More informationExperiment Two (2) Torsional testing of Circular Shafts
Experiment Two (2) Torsional testing of Circular Shafts Introduction: Torsion occurs when any shaft is subjected to a torque. This is true whether the shaft is rotating (such as drive shafts on engines,
More informationElectromagnetic Vibration Analysis of High Speed Motorized Spindle Considering Length Reduction of Air Gap
Electromagnetic Vibration Analysis of High Speed Motorized Spindle Considering Length Reduction of Air Gap Te Li1, 2*, Jian Wu1 1 Changshu Institute of Technology, School of Mechanical Engineering, Changshu,
More informationTowards Rotordynamic Analysis with COMSOL Multiphysics
Towards Rotordynamic Analysis with COMSOL Multiphysics Martin Karlsson *1, and Jean-Claude Luneno 1 1 ÅF Sound & Vibration *Corresponding author: SE-169 99 Stockholm, martin.r.karlsson@afconsult.com Abstract:
More informationMitigation of Diesel Generator Vibrations in Nuclear Applications Antti Kangasperko. FSD3020xxx-x_01-00
Mitigation of Diesel Generator Vibrations in Nuclear Applications Antti Kangasperko FSD3020xxx-x_01-00 1 Content Introduction Vibration problems in EDGs Sources of excitation 2 Introduction Goal of this
More informationCHAPTER 6 FAULT DIAGNOSIS OF UNBALANCED CNC MACHINE SPINDLE USING VIBRATION SIGNATURES-A CASE STUDY
81 CHAPTER 6 FAULT DIAGNOSIS OF UNBALANCED CNC MACHINE SPINDLE USING VIBRATION SIGNATURES-A CASE STUDY 6.1 INTRODUCTION For obtaining products of good quality in the manufacturing industry, it is absolutely
More informationOpen Access Repository eprint
Open Access Repository eprint Terms and Conditions: Users may access, download, store, search and print a hard copy of the article. Copying must be limited to making a single printed copy or electronic
More informationThe SKF model for calculating the frictional moment
The SKF model for calculating the frictional moment The SKF model for calculating the frictional moment Bearing friction is not constant and depends on certain tribological phenomena that occur in the
More informationOperating Conditions of Floating Ring Annular Seals
Operating Conditions of Floating Ring Annular Seals Mihai ARGHIR Institut PPRIME, UPR CNRS 3346, Université de Poitiers, ISAE ENSMA, France Antoine MARIOT Safran Aircraft Engines, France Authors Bio Mihai
More informationInduction Motor Bearing Fault Detection with Non-stationary Signal Analysis
Proceedings of International Conference on Mechatronics Kumamoto Japan, 8-1 May 7 ThA1-C-1 Induction Motor Bearing Fault Detection with Non-stationary Signal Analysis D.-M. Yang Department of Mechanical
More informationDetection of bearing faults in high speed rotor systems
Detection of bearing faults in high speed rotor systems Jens Strackeljan, Stefan Goreczka, Tahsin Doguer Otto-von-Guericke-Universität Magdeburg, Fakultät für Maschinenbau Institut für Mechanik, Universitätsplatz
More informationT20WN. Data Sheet. Torque transducers. Special features. Installation example with bellows couplings. B en
T20WN Torque transducers Data Sheet Special features - Nominal (rated) torques 0.1 N m, 0.2 N m, 0. N m, 1 N m, 2 N m, N m, 10 N m, 20 N m, 0 N m, 100 N m, 200 N m - Accuracy class: 0.2 - Contactless transmission
More informationAnalysis of High Speed Spindle with a Double Helical Cooling Channel R.Sathiya Moorthy, V. Prabhu Raja, R.Lakshmipathi
International Journal of Scientific & Engineering Research Volume 3, Issue 5, May-2012 1 Analysis of High Speed Spindle with a Double Helical Cooling Channel R.Sathiya Moorthy, V. Prabhu Raja, R.Lakshmipathi
More informationExpedient Modeling of Ball Screw Feed Drives
S. Frey a A. Dadalau a A. Verl a Expedient Modeling of Ball Screw Feed Drives Stuttgart, February 2011 a Institute for Control Engineering of Machine Tools and Manufacturing Units (ISW), University of
More informationPERIOD-N BIFURCATIONS IN MILLING: NUMERICAL AND EXPERIMENTAL VERIFICATION
PERIOD-N BIFURCATIONS IN MILLING: NUMERICAL AND EXPERIMENTAL VERIFICATION Andrew Honeycutt and Tony L. Schmitz Department of Mechanical Engineering and Engineering Science University of North Carolina
More informationBall bearing skidding under radial and axial loads
Mechanism and Machine Theory 37 2002) 91±113 www.elsevier.com/locate/mechmt Ball bearing skidding under radial and axial loads Neng Tung Liao a, Jen Fin Lin b,* a Department of Mechanical Engineering,
More informationCharacterization of Fixture-Workpiece Static Friction
Characterization of Fixture-Workpiece Static Friction By Jose F. Hurtado Shreyes N. Melkote Precision Manufacturing Research Consortium Georgia Institute of Technology Sponsors: NSF, GM R&D Center Background
More informationDepartment of Mechanical FTC College of Engineering & Research, Sangola (Maharashtra), India.
VALIDATION OF VIBRATION ANALYSIS OF ROTATING SHAFT WITH LONGITUDINAL CRACK 1 S. A. Todkar, 2 M. D. Patil, 3 S. K. Narale, 4 K. P. Patil 1,2,3,4 Department of Mechanical FTC College of Engineering & Research,
More informationMECTROL CORPORATION 9 NORTHWESTERN DRIVE, SALEM, NH PHONE FAX TIMING BELT THEORY
MECTRO CORPORATION 9 NORTHWESTERN DRIVE, SAEM, NH 03079 PHONE 603-890-55 FAX 603-890-66 TIMING BET THEORY Copyright 997, 999, 00 Mectrol Corporation. All rights reserved. April 00 Timing Belt Theory Introduction
More informationComputational and Experimental Approach for Fault Detection of Gears
Columbia International Publishing Journal of Vibration Analysis, Measurement, and Control (2014) Vol. 2 No. 1 pp. 16-29 doi:10.7726/jvamc.2014.1002 Research Article Computational and Experimental Approach
More informationOrbit Analysis. Jaafar Alsalaet College of Engineering-University of Basrah
Orbit Analysis Jaafar Alsalaet College of Engineering-University of Basrah 1. Introduction Orbits are Lissajous patterns of time domain signals that are simultaneously plotted in the X Y coordinate plane
More informationDYNAMIC ISSUES AND PROCEDURE TO OBTAIN USEFUL DOMAIN OF DYNAMOMETERS USED IN MACHINE TOOL RESEARCH ARIA
7 th INTERNATIONAL MULTIDISCIPLINARY CONFERENCE Baia Mare, Romania, May 17-18, 2007 ISSN -1224-3264 DYNAMIC ISSUES AND PROCEDURE TO OBTAIN USEFUL DOMAIN OF DYNAMOMETERS USED IN MACHINE TOOL RESEARCH ARIA
More information1541. A fast and reliable numerical method for analyzing loaded rolling element bearing displacements and stiffness
1541. A fast and reliable numerical method for analyzing loaded rolling element bearing displacements and stiffness Yu Zhang 1 Guohua Sun 2 Teik C. Lim 3 Liyang Xie 4 1 4 School of Mechanical Engineering
More informationOrder of Authors: DUMITRU N OLARU, Professor; CIPRIAN STAMATE, Dr.; ALINA DUMITRASCU, Doctoral student; GHEORGHE PRISACARU, Ass.
Editorial Manager(tm) for Tribology Letters Manuscript Draft Manuscript Number: TRIL Title: NEW MICRO TRIBOMETER FOR ROLLING FRICTION Article Type: Tribology Methods Keywords: Rolling friction, Friction
More informationExperimental Assessment of Unbalanced Magnetic Force according to Rotor Eccentricity in Permanent Magnet Machine
Journal of Magnetics 23(1), 68-73 (218) ISSN (Print) 1226-175 ISSN (Online) 2233-6656 https://doi.org/1.4283/jmag.218.23.1.68 Experimental Assessment of Unbalanced Magnetic Force according to Rotor Eccentricity
More informationNew concept of a 3D-probing system for micro-components
Research Collection Journal Article New concept of a 3D-probing system for micro-components Author(s): Liebrich, Thomas; Kanpp, W. Publication Date: 2010 Permanent Link: https://doi.org/10.3929/ethz-a-006071031
More informationWORK SHEET FOR MEP311
EXPERIMENT II-1A STUDY OF PRESSURE DISTRIBUTIONS IN LUBRICATING OIL FILMS USING MICHELL TILTING PAD APPARATUS OBJECTIVE To study generation of pressure profile along and across the thick fluid film (converging,
More informationNot all thin-section bearings are created equal. KAYDON new capacity calculations. Robert Roos, Scott Hansen
Not all thin-section bearings are created equal KAYDON new capacity calculations Robert Roos, Scott Hansen A white paper from KAYDON Bearings Division Table of Contents Abstract... pg. Introduction...
More informationChapter 11. Bearing Types. Bearing Load. The Reliability Goal. Selection of Tapered Roller Bearings
Chapter 11 Rolling Contact Bearing Bearing Types Bearing Life Bearing Load Bearing Survival The Reliability Goal Selection of Ball and Straight Roller Bearings Selection of Tapered Roller Bearings 1 Introduction
More informationDevelopment of a diagnosis technique for failures of V-belts by a cross-spectrum method and a discriminant function approach
Journal of Intelligent Manufacturing (1996) 7, 85 93 Development of a diagnosis technique for failures of V-belts by a cross-spectrum method and a discriminant function approach HAJIME YAMASHINA, 1 SUSUMU
More informationExperimental test of static and dynamic characteristics of tilting-pad thrust bearings
Special Issue Article Experimental test of static and dynamic characteristics of tilting-pad thrust bearings Advances in Mechanical Engineering 2015, Vol. 7(7) 1 8 Ó The Author(s) 2015 DOI: 10.1177/1687814015593878
More informationDynamic Tests on Ring Shear Apparatus
, July 1-3, 2015, London, U.K. Dynamic Tests on Ring Shear Apparatus G. Di Massa Member IAENG, S. Pagano, M. Ramondini Abstract Ring shear apparatus are used to determine the ultimate shear strength of
More informationStability of Water-Lubricated, Hydrostatic, Conical Bearings With Spiral Grooves for High-Speed Spindles
S. Yoshimoto Professor Science University of Tokyo, Department of Mechanical Engineering, 1-3 Kagurazaka Shinjuku-ku, Tokyo 16-8601 Japan S. Oshima Graduate Student Science University of Tokyo, Department
More informationFEDSM99 S-291 AXIAL ROTOR OSCILLATIONS IN CRYOGENIC FLUID MACHINERY
Proceedings of the 3 rd ASME/JSME Joint Fluids Engineering Conference 1999 ASME Fluids Engineering Division Summer Meeting July 18-23 1999, San Francisco, California FEDSM99 S-291 AXIAL ROTOR OSCILLATIONS
More informationTMSI High Speed Uniformity Machine
TMSI High Speed Uniformity Machine Presenter: Greg Meine TMSI LLC gmeine@mesnac.us www.tmsi-usa.com TMSI Introduction Tire Uniformity and DFMS 2 TMSI Introduction Founded in 1991 by Dr. Jerry Potts Headquartered
More informationVIBRATION ANALYSIS OF ROTARY DRIER
Engineering MECHANICS, Vol. 14, 2007, No. 4, p. 259 268 259 VIBRATION ANALYSIS OF ROTARY DRIER František Palčák*, Martin Vančo* In this paper the transfer of vibration from motor to the bottom group of
More informationLecture 20. Measuring Pressure and Temperature (Chapter 9) Measuring Pressure Measuring Temperature MECH 373. Instrumentation and Measurements
MECH 373 Instrumentation and Measurements Lecture 20 Measuring Pressure and Temperature (Chapter 9) Measuring Pressure Measuring Temperature 1 Measuring Acceleration and Vibration Accelerometers using
More informationMassachusetts Institute of Technology Department of Electrical Engineering and Computer Science Electric Machines
Massachusetts Institute of Technology Department of Electrical Engineering and Computer Science 6.685 Electric Machines Problem Set 10 Issued November 11, 2013 Due November 20, 2013 Problem 1: Permanent
More informationAccurate Joule Loss Estimation for Rotating Machines: An Engineering Approach
Accurate Joule Loss Estimation for Rotating Machines: An Engineering Approach Adeeb Ahmed Department of Electrical and Computer Engineering North Carolina State University Raleigh, NC, USA aahmed4@ncsu.edu
More informationDynamic Analysis of Rotor-Ball Bearing System of Air Conditioning Motor of Electric Vehicle
International Journal of Mechanical Engineering and Applications 2015; 3(3-1): 22-28 Published online February 13, 2015 (http://www.sciencepublishinggroup.com/j/ijmea) doi: 10.11648/j.ijmea.s.2015030301.14
More informationEXPERIMENTAL DETERMINATION OF DYNAMIC CHARACTERISTICS OF STRUCTURES
EXPERIMENTAL DETERMINATION OF DYNAMIC CHARACTERISTICS OF STRUCTURES RADU CRUCIAT, Assistant Professor, Technical University of Civil Engineering, Faculty of Railways, Roads and Bridges, e-mail: rcruciat@utcb.ro
More informationA novel fluid-structure interaction model for lubricating gaps of piston machines
Fluid Structure Interaction V 13 A novel fluid-structure interaction model for lubricating gaps of piston machines M. Pelosi & M. Ivantysynova Department of Agricultural and Biological Engineering and
More informationFlux-O-Meter. Making luminous flux measurements more accessible. Andrew Bierman, Martin Overington
Flux-O-Meter Making luminous flux measurements more accessible Andrew Bierman, Martin Overington Funded by EPA National Lighting Product Information Program (NLPIP) Sponsors Alliance for Solid-State Illumination
More informationAN EXAMINATION OF SURFACE LOCATION ERROR AND SURFACE ROUGHNESS FOR PERIOD-2 INSTABILITY IN MILLING
AN EXAMINATION OF SURFACE LOCATION ERROR AND SURFACE ROUGHNESS FOR PERIOD-2 INSTABILITY IN MILLING Andrew Honeycutt and Tony L. Schmitz Mechanical Engineering and Engineering Science University of North
More informationANALYSIS AND IDENTIFICATION IN ROTOR-BEARING SYSTEMS
ANALYSIS AND IDENTIFICATION IN ROTOR-BEARING SYSTEMS A Lecture Notes Developed under the Curriculum Development Scheme of Quality Improvement Programme at IIT Guwahati Sponsored by All India Council of
More informationJournal bearing performance and metrology issues
of Achievements in Materials and Manufacturing Engineering VOLUME 3 ISSUE 1 January 009 Journal bearing performance and metrology issues S. Sharma a, *, D. Hargreaves b, W. Scott b a School of Engineering
More informationDEVELOPMENT OF DROP WEIGHT IMPACT TEST MACHINE
CHAPTER-8 DEVELOPMENT OF DROP WEIGHT IMPACT TEST MACHINE 8.1 Introduction The behavior of materials is different when they are subjected to dynamic loading [9]. The testing of materials under dynamic conditions
More informationNoise Reduction of an Electrical Motor by Using a Numerical Model
Noise Reduction of an Electrical Motor by Using a Numerical Model Ahmet Ali Uslu Arcelik A.S. R&D Department, Vibration & Acoustic Technologies Laboratory, Istanbul, Turkey. Summary Electrical motor is
More informationEFFECT OF HYDRODYNAMIC THRUST BEARINGS ON ROTORDYNAMICS
The 12th International Symposium on Transport Phenomena and Dynamics of Rotating Machinery Honolulu, Hawaii, February 17-22, 2008 ISROMAC12-2008-20076 EFFECT OF HYDRODYNAMIC THRUST BEARINGS ON ROTORDYNAMICS
More informationEXPERIMENTAL INVESTIGATION OF THE EFFECTS OF TORSIONAL EXCITATION OF VARIABLE INERTIA EFFECTS IN A MULTI-CYLINDER RECIPROCATING ENGINE
International Journal of Mechanical Engineering and Technology (IJMET) Volume 6, Issue 8, Aug 2015, pp. 59-69, Article ID: IJMET_06_08_006 Available online at http://www.iaeme.com/ijmet/issues.asp?jtypeijmet&vtype=6&itype=8
More informationEffects of Ball Groupings on Ball Passage Vibrations of a Linear Guideway Type Ball Bearing Pitching and Yawing Ball Passage Vibrations
Hiroyuki Ohta 1 Department of Mechanical Engineering, Nagaoka University of Technology, 1603-1 Kamitomioka, Nagaoka, Niigata, Japan e-mail: ohta@mech.nagaokaut.ac.jp Yoshiki Kitajima LG Technology Department,
More informationInfluence of electromagnetic stiffness on coupled micro vibrations generated by solar array drive assembly
Influence of electromagnetic stiffness on coupled micro vibrations generated by solar array drive assembly Mariyam Sattar 1, Cheng Wei 2, Awais Jalali 3 1, 2 Beihang University of Aeronautics and Astronautics,
More informationDynamic Analysis for Needle Roller Bearings Under Planetary Motion
NTN TECHNICAL REVIEW No.75 2007 Technical Paper Dynamic Analysis for Needle Roller Bearings Under Planetary Motion Tomoya SAKAGUCHI A dynamic analysis tool for needle roller bearings in planetary gear
More informationA 3D-ball bearing model for simulation of axial load variations
A 3D-ball bearing model for simulation of axial load variations Petro Tkachuk and Jens Strackeljan Otto-von-Guericke-Universität Magdeburg, Fakultät für Maschinenbau Institut für Mechanik Universitätsplatz
More information