Simulation of vibrations and noise in the car's gearbox

In its work, the gearbox used to transfer energy from the engine to the wheels is quite noisy. The first reason for this undesirable effect is that the transverse and axial forces resulting from the transfer of energy from one shaft to another using gear, have an undesirable mechanical effect on the bearings and the housing. The second reason is the flexibility of the various components of the gearbox, including the bearings and housing, which can also lead to vibration. The variable stiffness of the gear clutch in the gearbox causes a constant vibration transmitted to the body, which, in turn, also vibrates and transmits the energy of the surrounding fluid, for example, transmission oil, as a result of which acoustic waves are excited.

To effectively reduce the noise level in such complex dynamic systems in the early stages of design, development engineers often resort to numerical simulation. Under the cut on the example of a 5-speed manual synchronized gearbox, we describe and show the methodology of such a study in COMSOL Multiphysics ® , which includes strength analysis of the mechanical contact of the gearing, analysis of the dynamics of the multibody gearbox system and acoustic analysis of the noise generated by the working box in the surrounding space.

Visualization of sound generated by a working gearbox

Step 1. Calculation of mechanical contact in gearing

The gearing, which we will consider elastic, is a source of constant vibration. For this reason, it is necessary to evaluate the stiffness of the gears in different positions. The teeth are deformed during operation, and a series of stationary strength calculations for various angles of rotation are performed to determine how the stiffness changes during a gear coupling operation cycle . For the calculation, the penalty method is applied to the contact, and constraints are defined to take into account the twisting of the gears, as a result of which contact forces arise.

The characteristic results at the output of such an analysis, in the form of a von Mises stress distribution in a gear pair, show high stresses at the contact points and at the bases of the teeth (Fig. 1, left). In addition, the calculation made allows us to observe and analyze the change in the rigidity of the gear coupling as the shaft rotates (Fig. 1, right).

Fig. 1. Left: von Mises stress distribution in a gear pair. Right: change in stiffness of the toothed clutch as the shaft rotates.

Step 2. Analysis of the multibody system of shafts, gears and casing

Analysis of multibody systems is performed in the time domain for one full rotation of the drive shaft, taking into account the rigidity of the gear coupling, predicted when calculating the contact in the first step. This analysis is necessary to calculate the dynamics of the gears and the values ​​of the resulting vibrations transmitted to the body. In this example, the analysis is performed at an engine speed of 5000 rpm and an output torque of 2000 N ∙ m. The calculation is carried out under the assumption that the shafts and gears are ideally rigid, with the exception of the gear coupling, the rigidity of which is taken from the previous study of mechanical contact. A body made of structural steel is regarded as an elastic body.

The distribution of von Mises stress in the housing under the action of forces transmitted by the drive and intermediate shafts, as well as the normal acceleration of the vibrating housing, which is the cause of the noise radiation, are shown in Fig. 2

Fig. 2. Left: von Mises stress distribution in the housing. Right: normal acceleration received on the surface of the body.

In fig. 3 shows a time diagram of the normal acceleration in one of the points on the upper part of the body and its frequency spectrum. The frequencies at which the housing vibrates with the greatest amplitude are in the range between 1500 and 2000 Hz.

Fig. 3. Normal acceleration at a point on the surface of the body. Left: Timeline. Right: Her frequency spectrum.

Step 3. Acoustic calculation of noise radiation from the body

Normal acceleration of the hull, obtained as a result of analysis of the dynamics of multibody systems, can then be used in acoustic research as a source of noise. With the help of research in the frequency domain, you can predict the sound pressure level outside the gearbox. Since the values ​​of the normal acceleration are obtained in the time domain, the direct fast Fourier transform (FFT) is used to transform them into the frequency domain. To calculate the acoustic pressure, the gearbox should be surrounded by an air region, and in order to reduce the size of the computational domain without reducing the accuracy of the results, a radiation condition of the Sommerfeld type is applied to the outer edges of the air region. for spherical wavefronts so that outgoing acoustic waves can leave the simulation area with minimal reflection.

The calculation makes it possible to obtain data on the sound pressure level on the surface of the body and in the near zone (Fig. 4), and from the graphs of the far zone in different planes and at a distance of 1 m, one can find out the prevailing direction of noise radiation at the selected frequency (Fig. 5).

Fig. 4. Sound pressure levels on the housing surface (left) and in the near zone (right) for the frequency of 1500 Hz.

Fig. 5. The sound pressure level (dB) in the far zone in the xy, xz and yz planes, respectively, at a distance of 1 m for a frequency of 1500 Hz.

Conclusion

In this note, we examined the method of modeling the noise from the gearbox using a combination of mechanical static analysis of a gear coupling, dynamic study of a multibody system, and subsequent acoustic calculation.

The actual functionality of the COMSOL Multiphysics ® package will even allow you to record and reproduce in the audio format the noise of the gearbox under study , which brings the simulation closer to a real physical experiment.

This technique can be used before the start of the production process to create less noisy gearboxes in the working speed range, as well as in the complex modeling of other operating mechanisms in industrial and musical equipment.

This material is based on the following articles:

A detailed video tutorial in Russian about assembling models of this class for joint vibration and acoustic analysis of a working gearbox can be found here . You can also request a demo version of COMSOL in the comments or on our website and independently familiarize yourself with the model described in this note and with step-by-step instructions for assembling it .

More examples of the use of COMSOL ® in acoustic calculations by research teams from B & K, Knowles, ABB, HARMAN and NASA can be found in the issue of COMSOL NEWS 2017: Acoustics in Russian.

COMSOL NEWS 2017 Summary: Special Edition Acoustics
• Виртуальная настройка автомобильной аудиосистемы. HARMAN, Франция
• Разработка промышленных и измерительных микрофонов. Bruel&Kjaer, Дания
• Расчёт акустических характеристик осреднённого течения в ракетных системах. NASA, США
• Снижение уровня шума мотоциклов. Mahindra Two Wheelers, Индия
• Исследование магнитострикционных эффектов и шума в силовых трансформаторах. ABB, Швеция
• Вибрационный анализ шума, создаваемого коробкой передач автомобиля. COMSOL, США/Швеция
• Передовые акустические исследования метаматериалов. Университет Дьюка (Duke), США
• Воздействие вибраций на здания вблизи аэропортов. NGI, Норвегия
• Разработка слуховых аппаратов. Knowles, США
• Неразрушающий акустический контроль в водопроводных магистралях. Echologics, Канада
• Новая конструкция электростатических наушников. XI Engineering и WAT, Великобритания

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