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Looney tunes silicone bakare molds

Looney tunes silicone bakare molds

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Looney tunes silicone bakare molds

Looney tunes silicone bakare molds

Looney tunes silicone bakare molds

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To browse Academia. Skip to main content. You're using an out-of-date version of Internet Explorer. By using our site, you agree to our collection of information through the use of cookies. Log In Sign Up. The Ijes The Ijes. The aim of this paper is to apply ANSYS software to determine the natural vibration modes and forced harmonic frequency response for gearbox casing.

The important elements in vibration analysis are the modelling of the bolted connections between the upper and lower casing and the modelling of the fixture to the support. This analysis is to find the natural frequency and harmonic frequency response of gearbox casing in order to prevent resonance for gearbox casing. From the result, this analysis can show the range of the frequency that is suitable for gearbox casing which can prevent maximum amplitude.

From the movement of the gear it will produce the vibration to the gearbox casing. Figure 1. A gearbox casing Reference [4] show that the study of natural frequency,consider a beam fixed at one end and having a mass attachedto the other, this would be a single degree of freedom SDoF oscillator. Once set into motion it will oscillate at it s naturalfrequency.

For a single degree of freedom oscillator, a systemin which the motion can be described by a single coordinate,the natural frequency depends on two system properties; massand stiffness. Without first finding thecircular natural frequency, the natural frequency can be founddirectly using: www.

A force of this type could, for example, begenerated by a rotating imbalance. The frequency response of the system www. In a lightly damped system when the forcingfrequency nears the natural frequency the amplitudeof the vibration can get extremely high.

This phenomenon iscalled resonance subsequently the natural frequency of asystem is often referred to as the resonant frequency. In rotorbearing systems any rotational speed that excites a resonantfrequency is referred to as a critical speed. If resonance occurs in a mechanical system it can be veryharmful — leading to eventual failure of the system.

Consequently, one of the major reasons for vibration analysisis to predict when this type of resonance may occur and thento determine what steps to take to prevent it from occurring. As the amplitude plot shows, adding damping cansignificantly reduce the magnitude of the vibration.

Also, themagnitude can be reduced if the natural frequency can beshifted away from the forcing frequency by changing thestiffness or mass of the system. If the system cannot bechanged, perhaps the forcing frequency can be shifted forexample, changing the speed of the machine generating theforce.

The following are some other points in regards to the forcedvibration shown in the frequency response plots. Therefore the mass—spring—damper systemis isolating the harmonic force from the mountingbase — referred to as vibration isolation. This analysis is to find the natural frequency and harmonicfrequency response of gearbox casing in order to preventresonance for gearbox casing. From the result, this analysiscan show the range of the frequency that is suitable forgearbox casing which can prevent maximum amplitude.

Figure 3: Bolts connecting gearbox halves B. An appropriate esh is selected to make sure thismeshing can solve in 1 hour duration. This mesh is applied towhole object as one body meshing. Table : Details of meshing strategy www.

Natural Vibration Analysis A modal analysis is performed with number of modes is The details of the support is in Table Figure 8: Actual fixed support on bottom created circle surface Harmonic Frequency Response Analysis In the harmonic frequency response analysis, the fixedsupport is exactly same condition in Figure 8.

In this analysis, 1MPa pressures is applied to the upper halfof the bearings on one side of the gearbox and to the lowerhalf of the other side for a frequency range from zero to 1. This 1MPa pressure is applied normal to the surfaceaccording to the Table and Figure 9. From these result, 10 lowest vibration frequencies are: Table lowest frequencies for natural vibration analysis Result of Harmonic Frequency Response Analysis In this harmonic frequency response analysis, frequencyrange need to be set up from zero to 1.

In Table 4, tenth vibration mode is This point isselected because this point is the maximum total displacementin the Figure Figure Details of Y-axis result for normal stress Figure Details of Y-axis result for directional deformation. X-axis result. Figure Details of X-axis result for normal stress www. Diagnosis requires a skill in identifying machine's condition from symptoms. The term diagnosis isunderstood here similarly as in medicine. It isgenerally thought that vibration is a symptom of agearbox condition.

Vibration generated by gearboxesis complicated in its structure but gives a lot ofinformation. We may say that vibration is a signal ofa gearbox condition. In order to detect and diagnosis an impending failure, a goodunderstanding of the evidence relating to the failuremode and methods of collecting and quantifying theevidenc e is needed. Although many faults may beeasily detectable by physical examination of a component, using techniques such as microscopy, Xray,dye penetrates, magnetic rubber, etc.

Whilst physical examinationtechniques still play a critical role duringmanufacture, assembly and overhaul, they ar eimpractical in an operational large transmissionsystem and other non-intrusive fault detectionmethods need to be employed for routine monitoringpurposes. The increment in the numberand amplitude of such sidebands may indicate a faultcondition. J [2], has proposed two new detectiontechniques. The time synchronous averaging conceptwas extended from revolution-based to toothengagement based.

The detection techniques arebased on statistical comparisons among the averages for the individual teeth. These techniques wereapplied to a series of three seeded fault crack propagation tests. Polyshchuk V.

V et al [3],has presents the development of a novel method ingear damage detection using a new gear faultdetection parameter based on the energy change inthe joint time- frequency analysis of the vibrationanalysis of the vibration signal. Choy F. K et al, [4], demonstrates the use of vibrationsignature analysis procedures for health monitoringand diagnostics of a gear transmission system. Lin J. J [5], has introduced an adaptivewavelet filter based on Morlet Wavelet, theparameters in the Morlet wavelet function areoptimized based on the kurtosis maximizationprinciple.

The wavelet used is adaptive because theparameters are not fixed. The adaptive wavelet filteris found to be very effective in detection ofsymptoms from vibration signals of a gearbox withearly fatigue tooth crack.

Designerrors may be due to causes like improper geargeometry, use of wrong materials, quality, lubricationand other confiscations. Application errors can bedue to problems like vibration, mounting andinstallation, cooling and maintenance whilemanufacturing errors can be in the form of mistakesin machining or problems in heat treating.

Summaryof safety critical failure modes Table , severalresearchers worked on the subject of gearbox defectdetection and diagnosis through vibration analysis. Time domain, frequency domain, time frequencydomain based on short time Fourier transform STFT and wavelet transform and advanced signalprocessing techniques have been implemented andtested. Table Safety critical failure modes Time Domain Analysis: The time domainmethods try to analyze the amplitude and phaseinformation of the vibration time signal to detect thefault of gear-rotor-bearing system.

The time domainis a perceptive that feels natural, and providesphysical insight into the vibration [6]. It isparticularly useful in analyzing impulsive signalsfrom bearing and gear defects with non-steady andshort transient impulses [7]. However, diagnosis of faults was a difficult task; relatinga change to a particular component requiredthe manual calculation of the repetition frequencybased on the time difference observed betweenfeature points.

Waveform analysis can also be usefulin identify vibrations that are non-synchronous withshaft speed. In machine cost down analysis waveformcan indicate the occurrence of resonance. A typical vibration waveform is shown in figure This waveform shows the anomalousbehavior of the gear after certain intervals with largemagnitude. The peak level, RMS, level, and the crestfactor are often used to quantify the time signal.

Indices: Indices have also been used invibration analysis [8, 6]. The peak value, RMS leveland their ratio crest factor are often used to quantifythe time signal. The peak level is not a statistical Quantity and hence may not be reliable in detectingdamage continuously operating systems. The crest factor, defined as the ratio ofthe peak value to RMS level, has been proposed as atrending parameter as it includes both parameters. Crest factors are reliable only in the presence of Significant impulsiveness.

Crest Factor: The crest factor is defined as the ratio of the peak value to the RMS of the signal: Statistical Methods: Statistical analysis canalso be carried out on time domain data. Kurtosis: Kurtosis is the normalized fourth statisticalmoment of the signal [8]. The kurtosis level of a signal is used in a similarfashion to the crest factor that is to provide a measureof the impulsive nature of the signal.

Raising thesignal to the fourth power effectively amplifiesisolated peaks in the signal. A distributionof data set is symmetric if it looks the same to the left www. A distribution of data set is symmetric if it looks the same to the leftand right of the centre point.

Equation 3. Any real world signal can be brokendown into a combination of unique sine waves. Everysine wave separated from the signal appears as avertical line in the frequency domain. Its heightrepresents its amplitude and its position representsthe frequency.

The frequency domain representationof the signal is called the signal. The frequencydomain completely defines the vibration. Frequencydomain analysis not only detects the faults in rotating Machinery but also indicates the cause of the defect[6]. Theoretically, time domain can be converted intofrequency domain using the Fourier Transforms andvice versa.

Then change the sum to an integral, and the equations become Here, equation 3. Fast Fourier Transformation: The FastFourier Transform FFT is simply a class of specialalgorithms which implement the discrete Fouriertransform with considerable savings in computationaltime.

Looney tunes silicone bakare molds

Looney tunes silicone bakare molds

Looney tunes silicone bakare molds