# Artificial Engine Sound Synthesis Method for Modification of the Acoustic Characteristics of Electric Vehicles

Authors: Dongki Min; Buhm Park; Junhong Park
Journal: Shock and Vibration
 (2018)

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## Abstract

Sound radiation from electric motor-driven vehicles is negligibly small compared to sound radiation from internal combustion engine automobiles. When running on a local road, an artificial sound is required as a warning signal for the safety of pedestrians. In this study, an engine sound was synthesized by combining artificial mechanical and combustion sounds. The mechanical sounds were made by summing harmonic components representing sounds from rotating engine cranks. The harmonic components, including not only magnitude but also phase due to frequency, were obtained by the numerical integration method. The combustion noise was simulated by random sounds with similar spectral characteristics to the measured value and its amplitude was synchronized by the rotating speed. Important parameters essential for the synthesized sound to be evaluated as radiation from actual engines were proposed. This approach enabled playing of sounds for arbitrary engines. The synthesized engine sounds were evaluated for recognizability of vehicle approach and sound impression through auditory experiments.


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## Body

## 1. Introduction

With the increasing use of electric motor-driven vehicles due to their advantages such as environmental friendliness and fuel-efficient performance [1], it is necessary to generate artificial sounds to inform pedestrians and cyclists of the vehicle’s approach. In addition, drivers prefer sounds similar to internal combustion engines for auditory satisfaction, and the sounds should represent the current status (acceleration or deceleration) of the vehicle, for example, start-up or rapid acceleration and deceleration. A simple method of generating artificial engine sounds is to play recorded combustion engine sounds according to engine rotating speeds. However, this method exhibits limited performance for reproducing the complex conditions of a vehicle and requires an impractical number of recordings for generating artificial sounds for various vehicle statuses from a single machine. An artificial engine sound generator is considered the most effective solution. This sound generator should be designed to make a positive impression on people to minimize the possibility of noise pollution.Subjective evaluations of various engine sounds were performed in previous studies [2–5]. Amman and Das [6] proposed deterministic and stochastic components and used synchronous discrete Fourier transform and suboptimal multipulse excitation approaches to generate realistic engine sounds. Airplane engine sounds were generated by combining broadband and individual tonal contributions [7, 8] to determine the annoyance level and how to reduce it efficiently. Hastings [9] used deterministic and random variation in sound amplitude to regenerate diesel engine sounds. With amplitude variation following a rotating crank shaft, the random signals generated with impulse trains were used to generate artificial sounds for annoyance evaluation. Artificial engine sound generators mounted on low noise vehicles have used simple sounds for warning pedestrians outside the vehicle. The playing of sampled engine sounds for various rotating speeds was widely used in previous studies on artificial engine sound synthesis [10–18]. A system has been developed to warn pedestrians by using sine wave sweep signals [10–13], motor sounds [14], and future-oriented new sounds using instrument sounds [15]. The synthesizing method utilizing the premeasured actual engine sounds has the advantage of using less memory, but there is a limitation in creating a variety of sounds in relation to the vehicle speeds.Active noise control and active sound design techniques have been used to reduce low-frequency engine noise and synthesize harmonics to enhance existing engine sound quality [16]. The artificial complex sounds were required to minimize noise according to the driving conditions of the vehicle [17, 18]. Equalizers have been developed to allow setup of parameters adjusting the amplitude and range of the spectrum of basic sound building blocks.In this study, an artificial engine sound generator was developed using a sample-based algorithm. With the systematic data processing, engine sounds that are similar to the actual engine sound are generated. Artificial engine sound synthesis method was implemented by analyzing the actual engine sound generation mechanism. The numerical integration method allows construction of an optimal data set generating the engine sound. Synthesized artificial engine sounds according to the vehicle engine speed were generated by applying a sample-based algorithm.Many researches recorded and used the actual vehicle engine sound for sound synthesis. The artificial engine sound generator requires a CAN (controller area network) bus communication module and a sound module. This method is simple to use and implements actual engine sounds (or presynthesized beeps), but the types and scalability of sounds are limited and require a lot of memory. The auditory satisfaction of the user is also limited because it is difficult for the user to change the sound. To generate engine sounds, parameters related to engine characteristics such as number of cylinders, rotating speed, engine type, combustion pressure profile, timing, and amplitude modulation should be considered. For generation of engine sounds to be unique for each vehicle, important parameters that influence engine sound perception should be fully understood.In this study, a mathematical formulation to generate artificial engine sounds to meet consumer preferences is proposed. With this approach, flexible generation of engine sounds without playing sampled sounds is possible. To analyze the characteristics of engine sounds, gasoline and diesel engine sounds were recorded. After spectrum analysis, the mechanical and combustion engine sounds were separated. The mechanical sounds were synthesized using a summation of tonal sounds. The combustion sounds were generated using spectrum amplitude-modulated random sounds to exhibit a specific frequency envelope. The artificial engine sound was synthesized by combining these mechanical and combustion engine sounds. For illustration, several different engine sounds were generated and used in the evaluation of perception. Recognizability of vehicle approaches and perceived quality of the artificial engine sounds were evaluated by comparison to actual recorded engine sounds. This also provided information on the sound generation mechanism for actual engines and its perceived characteristics. Engine sound characteristics must be understood for both design of quiet vehicle engines and artificial engine sound-producing devices.


## 2. Measurements of Acoustic Characteristics of Engine Sounds

Gasoline and diesel engine sounds were measured using the test engines in the laboratory [19, 20] for spectrum analysis. The measured engine noise was used to define the mechanical and combustion noise. Figure 1 shows the experimental setup to measure the engine sound. Figure 1 shows an overall schematic view of the laboratory chamber that has the controller adjusting operating conditions. The microphone used to measure sounds from each engine was located 1 meter from the engine. The engines used in the experiment were equipped with 4 cylinders. The engine room was surrounded by walls made of glass and porous panels. The sounds were measured for 10 seconds when the engine speed was 1000, 1500, 1800, and 2100 rpm, with idle conditions of 850 and 820 rpm for gasoline and diesel engines, respectively.Figure 1
Overall schematic view of the laboratory chamber.Figure2 compares the sound of the gasoline engine to that of the diesel engine at various rotation speeds. The measured results were focused on the spectrum characteristics of the mechanical sound and the combustion sound. The high-frequency component of the diesel engine combustion noise was higher than that of the gasoline engine.Figure 2
Spectral characteristics of (a) gasoline and (b) diesel engine sounds measured in the laboratory. The spectrum showed a decreasing level with increasing frequency, and the combustion noise at high frequencies over 1 kHz was larger for the diesel engine.
(a) (b)The combustion noise propagates into the air through the vibration of the various structures that make up the engine. The factors affecting the pressure profile include injection strategy, combustion chamber geometry, air-fuel mixture ratio, compression ratio, and amplitude changes due to explosion [20–24]. The resonance frequency of the crankcase and the cylinder block in the range of 200 to 1000 Hz, the timing gear, the rocker cover in the range of 1000 to 5000 Hz, and the cast aluminum cover and the thin cast iron in 5000 Hz were analyzed. The engine structures have different emission efficiencies. The frequency components were attenuated by more than 10 dB after 1 kHz for the diesel engines [25]. The contribution of the noise generated in the wide band over 1 kHz is relatively low compared to the mechanical sound of the tonal components. The sound level is reflected in frequencies and bands magnitude multiplied by artificial mechanical and combustion sounds. The low-frequency region of the measured sound was masked by the mechanical sound. The mechanical and the combustion sounds were separated with respect to the frequency of 1 kHz. This distinction provided a simple but accurate algorithm for generating artificial engine sounds.


### 2.1. Spectral Characteristics of Engine Sounds

The frequency components of the measured engine sounds are shown in Figure2. The measured sound was divided into mechanical and combustion sounds to produce artificial engine sound. The mechanical sound clearly shows the frequency shift in accordance with the engine speed in the low-frequency range. The combustion noise was defined for spectral components higher than 1 kHz, where the increase in the noise level of the broadband noise is noticeable depending on the engine speed. Although the combustion sound also affects the low-frequency range according to the cylinder internal pressure conditions [23, 24], the variation of the combustion sound level by the mechanical sounds was negligibly small. At frequencies below 1000 Hz, the engine sound level showed minimal dependence on the engine speed but showed a significant influence from the first engine order defined as(1)f0=N·n2·60,where N is the engine speed which is represented in revolutions per minute (rpm) and n is the number of cylinders. The harmonic components at multiples of the first engine order had a significant influence at low-frequency bands, below 600 Hz, and are known as mechanical sounds [3, 21, 22, 25, 26]. The combustion sounds measured for the diesel engine at frequencies between 1 and 10 kHz were much higher compared to those of the gasoline engine. The high in-cylinder pressure of the diesel engine for autoignition caused this increased level of the combustion sound [26, 27]. The basic spectrum envelope of the frequency response between combustion and acoustic pressure remains the same for most diesel engines [4, 25]. The combustion sound level is proportional to the engine speed in the fixed injection strategy and idle state.


### 2.2. Transient Variation in Engine Sounds

One important characteristic of diesel engine sounds is the temporal variation [3, 15]. Direct injection diesel engines are often short-circuited to the cylinder prior to the top dead center (TDC), often expressed as zero degrees of crank. Ignition occurs at 10 degrees prior to the combustion [28]. The first peak of the combustion pressure is due to the mechanical action of compressing the air in the second stroke. The second peak is caused by the sudden change in the sound pressure during the combustion process. For further investigation of combustion sound, a single-cylinder diesel engine [29, 30] was used for recording. To prevent reflection of engine sounds, an absorbing chamber was installed around the engine system. The engine sounds were recorded using a microphone which was located in front of the engine at a height of 1 m. The in-cylinder pressure was measured at the same time.Since the measured engine sound shown in Figure3 included noise from various components of the test engine, the measured engine sound was bandpass-filtered from 1.1 to 2.9 kHz and from 1.9 to 2.1 kHz. The temporal variation in filtered sound due to the combustion cycle is clearly demonstrated in Figure 3. Comparing the temporal variation to the time history of the in-cylinder pressure shows that combustion sound is boosted periodically with the in-cylinder pressure change. The first maximum in the in-cylinder pressure was from the piston’s mechanical movement during the compression stroke; the second maximum is from the combustion during the explosion stroke. Therefore, it is apparent that a combustion sound has a certain frequency envelope above 1 kHz and it is amplitude-modulated in accordance with the mechanical cycling motion of the cylinder.Figure 3
Comparison between (a) in-cylinder static pressure and (b) acoustic pressure for a single-cylinder diesel engine. For the acoustic pressure, the gray and black lines show measured and filtered (from 1.1 to 2.9 kHz and 1.9 to 2.1 kHz) acoustic pressures to minimize influence from the dynamometer used in the experiments.
(a) (b)


## 2.1. Spectral Characteristics of Engine Sounds

The frequency components of the measured engine sounds are shown in Figure2. The measured sound was divided into mechanical and combustion sounds to produce artificial engine sound. The mechanical sound clearly shows the frequency shift in accordance with the engine speed in the low-frequency range. The combustion noise was defined for spectral components higher than 1 kHz, where the increase in the noise level of the broadband noise is noticeable depending on the engine speed. Although the combustion sound also affects the low-frequency range according to the cylinder internal pressure conditions [23, 24], the variation of the combustion sound level by the mechanical sounds was negligibly small. At frequencies below 1000 Hz, the engine sound level showed minimal dependence on the engine speed but showed a significant influence from the first engine order defined as(1)f0=N·n2·60,where N is the engine speed which is represented in revolutions per minute (rpm) and n is the number of cylinders. The harmonic components at multiples of the first engine order had a significant influence at low-frequency bands, below 600 Hz, and are known as mechanical sounds [3, 21, 22, 25, 26]. The combustion sounds measured for the diesel engine at frequencies between 1 and 10 kHz were much higher compared to those of the gasoline engine. The high in-cylinder pressure of the diesel engine for autoignition caused this increased level of the combustion sound [26, 27]. The basic spectrum envelope of the frequency response between combustion and acoustic pressure remains the same for most diesel engines [4, 25]. The combustion sound level is proportional to the engine speed in the fixed injection strategy and idle state.


## 2.2. Transient Variation in Engine Sounds

One important characteristic of diesel engine sounds is the temporal variation [3, 15]. Direct injection diesel engines are often short-circuited to the cylinder prior to the top dead center (TDC), often expressed as zero degrees of crank. Ignition occurs at 10 degrees prior to the combustion [28]. The first peak of the combustion pressure is due to the mechanical action of compressing the air in the second stroke. The second peak is caused by the sudden change in the sound pressure during the combustion process. For further investigation of combustion sound, a single-cylinder diesel engine [29, 30] was used for recording. To prevent reflection of engine sounds, an absorbing chamber was installed around the engine system. The engine sounds were recorded using a microphone which was located in front of the engine at a height of 1 m. The in-cylinder pressure was measured at the same time.Since the measured engine sound shown in Figure3 included noise from various components of the test engine, the measured engine sound was bandpass-filtered from 1.1 to 2.9 kHz and from 1.9 to 2.1 kHz. The temporal variation in filtered sound due to the combustion cycle is clearly demonstrated in Figure 3. Comparing the temporal variation to the time history of the in-cylinder pressure shows that combustion sound is boosted periodically with the in-cylinder pressure change. The first maximum in the in-cylinder pressure was from the piston’s mechanical movement during the compression stroke; the second maximum is from the combustion during the explosion stroke. Therefore, it is apparent that a combustion sound has a certain frequency envelope above 1 kHz and it is amplitude-modulated in accordance with the mechanical cycling motion of the cylinder.Figure 3
Comparison between (a) in-cylinder static pressure and (b) acoustic pressure for a single-cylinder diesel engine. For the acoustic pressure, the gray and black lines show measured and filtered (from 1.1 to 2.9 kHz and 1.9 to 2.1 kHz) acoustic pressures to minimize influence from the dynamometer used in the experiments.
(a) (b)


## 3. Development of a Synthesis Method for Artificial Engine Sound

Based on the measured spectral characteristics of engine sound, mechanical sound below 1 kHz was especially dominant for the gasoline engine. The combustion sound above 1 kHz had significant influence on the diesel engine sound. According to this measured variation, an artificial engine sound was synthesized by summing synthesized mechanical and combustion sounds.


### 3.1. Mechanical Sound Synthesis

Mechanical engine sound below 1 kHz was synthesized by summing the harmonic components according to first engine order as(2)pmt=∑k=1Kakcos⁡2πkf0tNm+bksin⁡2πkf0tNm,where pm is the mechanical sound and Nm is the resolution for obtaining spectral components lower than the first engine order (Nm=n2). The magnitude of each frequency component, ak, and phase, ϕk (the Fourier coefficients of the cosine and sine terms, ak and bk), was obtained from spectrum analysis of the actual engine sounds measured for 10 s. Because a typical spectrum analysis such as fast Fourier transform provides information only about the magnitude without phase, an integration method was applied to obtain both of them in this study as(3)ak=1M∑m=1M1T∫0Tpt+m-1Tcos⁡2πktTdtbk=1M∑m=1M1T∫0Tpt+m-1Tsin⁡2πktTdt,where dt is the discrete-time interval of the recorded engine sound p(t), T is the integration period considering resolution for obtaining spectral components, and M is the number of samples of time averaging as recording time over T. Note that the summation of (3) means a time averaging. To solve the above integration numerically, Simpson’s 1/3 rule was applied. Using the integration and time averaging, random noise components including the combustion noise become negligible. Therefore, only the mechanical sound components can be obtained. The magnitude of each frequency component Ak and phase ϕk was expressed for convenience of calculation of the mechanical sound synthesis.(4)Ak=ak2+bk2ϕk=tan-1bkak.Figure4(a) shows the measured mechanical sounds and Figure 4(b) shows the synthesized engine sound under idle conditions. Note the low-frequency envelope of 8 Hz (repeating every 0.15 s) in the signal. This low-frequency envelope originated from the cyclic motion of the engine piston and differences in the firing process between the cylinders and significantly influenced the development of realistic engine sounds. This low-frequency component is crucial for making specific engine sounds. In addition, by changing the frequency components and their magnitude and phase in (2), the synthesized engine sound changed as shown in Figure 4(c).Figure 4
Comparison between (a) measured engine sound and (b) synthesized engine sound. The mechanical sound was varied by adjusting the amplitude (the amplitudes at frequencies 2f0 and 10f0 were amplified 2 and 10 times and are shown in (c)).
(a) (b) (c)


### 3.2. Combustion Sound Synthesis

Combustion sound has a specific frequency envelope above 1 kHz and is amplitude-modulated with piston movements. Considering the fixed aspects of the changes in the amplitudes and the time characteristics of the mechanical sounds and the random signal characteristics of the broadband frequencies of the combustion noise, it is shown that they can produce sounds similar to those of real diesel engines [9]. The coefficients to adjust the total noise level and to change the fixed time characteristic of the mechanical sound as shown in (5) were used. It was possible to produce noise that is similar to the actual combustion noise. According to the spectrum characteristics of the combustion sound, the artificial spectrum, pe, was generated using white noise sampled with 1/3-octave bands and the magnitude of each band was adjusted for generating an arbitrary combustion engine as shown in Figure 5. After inverse Fourier transform, the combustion sound was made as (5)pct=C·Mf·pet·pmt+Cr·Mf,where pc and Mf are the combustion sound and the magnitude of the first engine order component, respectively. The magnitude coefficient, C, is a ratio of Mf and was determined to be between 0.005 and 0.05, based on measured typical diesel engine-driven vehicle noises at low and high rotation speeds. The broadband noise component considering reverberation effects by resonance in the combustion chamber and repetitive explosive excitations was considered to be a constant Cr. The reverberation coefficient Cr was determined to be between 2 and 4 at low and high rotation speeds. Consequently, the combustion sound was synchronized in magnitude with the mechanical sound. Figure 6 shows an example of synchronized engine sound in Figure 4(a) under constant rotation of the engine. Total engine sound was generated by summing the mechanical and combustion engine sounds.Figure 5
Typical combustion sound spectrum, which is composed of magnitude-adjusted noise bands from sampled white noise with 1/3-octave band.Figure 6
Acoustic pressure fluctuations of the measured and synthesized combustion sounds.


## 3.1. Mechanical Sound Synthesis

Mechanical engine sound below 1 kHz was synthesized by summing the harmonic components according to first engine order as(2)pmt=∑k=1Kakcos⁡2πkf0tNm+bksin⁡2πkf0tNm,where pm is the mechanical sound and Nm is the resolution for obtaining spectral components lower than the first engine order (Nm=n2). The magnitude of each frequency component, ak, and phase, ϕk (the Fourier coefficients of the cosine and sine terms, ak and bk), was obtained from spectrum analysis of the actual engine sounds measured for 10 s. Because a typical spectrum analysis such as fast Fourier transform provides information only about the magnitude without phase, an integration method was applied to obtain both of them in this study as(3)ak=1M∑m=1M1T∫0Tpt+m-1Tcos⁡2πktTdtbk=1M∑m=1M1T∫0Tpt+m-1Tsin⁡2πktTdt,where dt is the discrete-time interval of the recorded engine sound p(t), T is the integration period considering resolution for obtaining spectral components, and M is the number of samples of time averaging as recording time over T. Note that the summation of (3) means a time averaging. To solve the above integration numerically, Simpson’s 1/3 rule was applied. Using the integration and time averaging, random noise components including the combustion noise become negligible. Therefore, only the mechanical sound components can be obtained. The magnitude of each frequency component Ak and phase ϕk was expressed for convenience of calculation of the mechanical sound synthesis.(4)Ak=ak2+bk2ϕk=tan-1bkak.Figure4(a) shows the measured mechanical sounds and Figure 4(b) shows the synthesized engine sound under idle conditions. Note the low-frequency envelope of 8 Hz (repeating every 0.15 s) in the signal. This low-frequency envelope originated from the cyclic motion of the engine piston and differences in the firing process between the cylinders and significantly influenced the development of realistic engine sounds. This low-frequency component is crucial for making specific engine sounds. In addition, by changing the frequency components and their magnitude and phase in (2), the synthesized engine sound changed as shown in Figure 4(c).Figure 4
Comparison between (a) measured engine sound and (b) synthesized engine sound. The mechanical sound was varied by adjusting the amplitude (the amplitudes at frequencies 2f0 and 10f0 were amplified 2 and 10 times and are shown in (c)).
(a) (b) (c)


## 3.2. Combustion Sound Synthesis

Combustion sound has a specific frequency envelope above 1 kHz and is amplitude-modulated with piston movements. Considering the fixed aspects of the changes in the amplitudes and the time characteristics of the mechanical sounds and the random signal characteristics of the broadband frequencies of the combustion noise, it is shown that they can produce sounds similar to those of real diesel engines [9]. The coefficients to adjust the total noise level and to change the fixed time characteristic of the mechanical sound as shown in (5) were used. It was possible to produce noise that is similar to the actual combustion noise. According to the spectrum characteristics of the combustion sound, the artificial spectrum, pe, was generated using white noise sampled with 1/3-octave bands and the magnitude of each band was adjusted for generating an arbitrary combustion engine as shown in Figure 5. After inverse Fourier transform, the combustion sound was made as (5)pct=C·Mf·pet·pmt+Cr·Mf,where pc and Mf are the combustion sound and the magnitude of the first engine order component, respectively. The magnitude coefficient, C, is a ratio of Mf and was determined to be between 0.005 and 0.05, based on measured typical diesel engine-driven vehicle noises at low and high rotation speeds. The broadband noise component considering reverberation effects by resonance in the combustion chamber and repetitive explosive excitations was considered to be a constant Cr. The reverberation coefficient Cr was determined to be between 2 and 4 at low and high rotation speeds. Consequently, the combustion sound was synchronized in magnitude with the mechanical sound. Figure 6 shows an example of synchronized engine sound in Figure 4(a) under constant rotation of the engine. Total engine sound was generated by summing the mechanical and combustion engine sounds.Figure 5
Typical combustion sound spectrum, which is composed of magnitude-adjusted noise bands from sampled white noise with 1/3-octave band.Figure 6
Acoustic pressure fluctuations of the measured and synthesized combustion sounds.


## 4. Validation of Synthesized Engine Sound through an Auditory Experiment

To compare the performance of actual and artificial engine sounds, auditory experiments were performed using the magnitude estimation method [31]. Seven sound samples were used in the experiments. Figure 7 shows the acoustic pressure profile of the stimuli during idle condition for various recorded and synthesized engine sounds in Table 1. The engine rotating speed was increased gradually from 800 rpm and reached a maximum rpm of 3000 rpm and decreased to the idle condition again. The maximum sound level of each stimulus was adjusted to be 70 dBA. Figure 8 shows an example of acoustic pressure variation for the sound sample shown in Figure 7(a) during playback.Table 1
Stimuli used in the auditory experiments.
Type Number Description  Synthesized engine sound (a) Mechanical sound of a gasoline engine (b) Mechanical sound of a diesel engine (c) Mechanical and combustion sound of a diesel engine  Recorded real engine sound (d) Gasoline engine, 2000 cc displacement (reference stimulus) (e) Diesel engine, 2000 cc displacement (f) Sports car engine, 6000 cc displacement (g) Sports car engine, 4000 cc displacementFigure 7
Acoustic pressure profiles of stimuli used in the auditory experiment. The sounds from (a) to (c) are the synthesized sounds and the sounds from (d) to (g) are the measured sounds. Thex-axis of each layer indicates time in seconds of 0–0.5, respectively.
(a) (b) (c) (d) (e) (f) (g)Figure 8
Acoustic pressure variation due to rpm change of stimuli used in the auditory experiment.The stimuli were presented to 23 participants with normal hearing using loudspeakers in a soundproof room in which the sound level was lower than 38 dBA. Participants were asked to evaluate the recognizability of the vehicle approach and a preference for engine sounds when a stimulus was given. A typical gasoline engine sound (Figure7(d)) was played three times as a reference stimulus that was set to four points for participants who were not used to evaluating using a seven-point scale method. Note that points 1 and 7 mean “extremely poor” and “extremely good,” respectively.The results of auditory experiments are summarized in Figure9. Participants’ consistency analysis was performed for subjective evaluation. Because stimulus (d), which was given as a reference, has an average of 4.48 and the standard deviation was small at 0.8, the reliability of the result was verified. A synthesized diesel engine (stimulus c) shows the highest performance for achieving a recognizable vehicle approach. Compared to synthesized mechanical sounds only (stimuli a and b), the inclusion of the combustion sounds significantly increased the recognizability of engine sounds. The recorded sounds of sports cars (stimuli f and g) showed high performance, but not higher than that of stimulus c.Figure 9
Results of the auditory experiments to evaluate the recognizability of vehicle approach and preference for engine sound.Synthesized gasoline engine sounds (stimuli a and b) exhibited better performance than that of the diesel engine (stimulus c). This suggested that a more annoying sound made pedestrians clearly recognize a vehicle approach. The sports car engine sound (stimulus g) has better engine sound preference than the other sounds (stimuli c, d, e, and f). The strongly fluctuating sounds of the sports vehicles were one reason for this large variation.


## 5. Conclusions

In this study, the transient and spectrum variation of recorded sounds from the test engines in a lab was analyzed to investigate the effects of piston cyclic motion on the radiation of mechanical and combustion engine sounds and their correlation to frequency components. Artificial engine mechanical sound was synthesized using summation of sinusoidal waves representing mechanical sounds. Due to small differences in the frequency of sounds radiating from each cylinder, a modulated mechanical sound was generated. For representing mechanical sounds with harmonic sums without influence of the combustion noise, the Fourier series was used with the fundamental frequency smaller than the first engine order. After considering these frequency components less than the rotating speeds, the synthesized mechanical sounds exhibited similar characteristics to actual gasoline engine sounds. The combustion sound was synthesized using a spectrum-enveloped random signal. The engine sound was generated by combining these mechanical and combustion sounds. This approach enables generation of arbitrary engine sounds to customer preference for their own vehicles. From the results of the auditory experiments, recognizability of vehicle approach and preference for engine sound were compared to actual engine sounds. The synthesized sounds, especially for the diesel engine, showed excellent performance for informing participants of vehicle operation. The proposed algorithm utilizes variations in frequency components with rotating speeds and allows the use of various sound sources from musical instruments. Consequently, pleasant sounds may inform pedestrians of a vehicle approach.



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