Acoustic Metamaterials for Architectural and Urban Noise Mitigations

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This entry is adapted from the peer-reviewed paper 10.3390/acoustics1030035

Owing to a steep rise in urban population, there has been a continuous growth in construction of buildings, public or private transport like cars, motorbikes, trains, and planes at a global level. Hence, urban noise has become a major issue affecting the health and quality of human life. In the current environmental scenario, architectural acoustics has been directed towards controlling and manipulating sound waves at a desired level. Structural engineers and designers are moving towards green technologies, which may help improve the overall comfort level of residents. A variety of conventional sound absorbing materials are being used to reduce noise, but attenuation of low-frequency noise still remains a challenge. Recently, acoustic metamaterials that enable low-frequency sound manipulation, mitigation, and control have been widely used for architectural acoustics and traffic noise mitigation.

room acoustics urban noise low-frequency noise indoor noise traffic noise acoustic metamaterials

1. Introduction

Noise is an integral part of the working environment and can be produced almost everywhere viz. rooms, industries, roads, airports, transportations, etc. In this 21st century, due to extreme exploitation of Mother Nature, noise pollution has become a major issue that affects the health and quality of life especially in the city. Noise was considered as a pollutant for the first time at the World Environment Congress held in Stockholm in 1972 and a recommendation was made for the development of standards for measuring and limiting of noise emissions ^[1]^[2]. However, the first modern noise legislation was the U.S. Noise Control Act (NCA) in 1972 ^[3]. Consequently, the World Health Organization (WHO) published several reports indicating the negative impact of noise on human beings. In 2011, WHO considered noise pollution as one of the most crucial factors having a direct adverse impact on the public health. In this regard, several guidelines have been recommended for safe levels of noise exposure originating from various sources. For example, <85 dB in bridge repainting (National Institute for Occupational Safety and Health NIOSH, 1999), the chemical plant (<82 dB, NIOSH, 1999) ^[4], railway noise (<54 dB) ^[5], aircraft noise (<82 dB), etc. More recently, in 2018, WHO set some environmental noise guidelines for public safety in the European region (Table 1). Long exposure to exceeding levels of noise can lead to several adverse human health issues such as, fatigue, stress, hearing loss, high blood pressure, sleeping disorder, psychological disorders, hypertension, obesity, cognitive impairment in children, coronary heart disease, diabetic type I and II, etc. ^[4]^[6]^[7]^[8]^[9], hence making it imperative to reduce the noise levels.

Table 1. Recommended safe noise levels for public health safety ^[5].

Source	Average Noise Exposure $(L_{d e n}) Limit$	Night Noise Exposure $(L_{n i g h t}) Limit$
Road traffic noise	<53 dB	<45 dB
Railway noise	<54 dB	<44 dB
Aircraft noise	<45 dB	<40 dB
Wind turbine noise	<45 dB	No recommendation
Leisure noise	<70 dB $L_{Aeq, 24 h}$

L_{d e n}

: Day–evening–night-weighted sound pressure level, over a whole day with a penalty of 10 dB(A) for night time noise (22.00–7.00) and an additional penalty of 5 dB(A) for evening noise (i.e., 19.00–23.00).

L_{n i g h t}

: Equivalent continuous sound pressure level when the reference time interval is the night (23.00–7.00).

A variety of traditional materials have been used to reduce noise such as, natural fibers (natural cotton, wool, and kenaf) ^[10], granular materials (porous concrete, asphalt, and granular clays) ^[11], synthetic cellular materials (inert glass wool, melamine foams, polyurethane, and polyester) ^[12]^[13], mass-loaded vinyl (MLV) ^[14], etc. These materials are efficient for development of sound absorption systems operating in the high frequency range (Figure 1). The typical sound absorption coefficients of other traditional materials can be found in several handbooks ^[15]^[16]^[17]. However, in case of low frequency noise (<200 Hz), these materials often fail to reduce noise effectively. This is because traditional materials follow the mass density law for sound shielding. According to the mass-density law, sound transmission through a substance is given by ^[18],

T = \frac{1}{ρ \times t \times f},

where

ρ

is density, t is thickness of the medium, and

f

is the sound wave frequency. Sound transmission loss (STL) is calculated as ^[19],

S T L = 10 \times \log_{10} [\frac{1}{T}] .

Thus, for a particular frequency, doubling the thickness of the sound insulator would result in an increment of only 6 dB STL. Therefore, a thicker porous material is required for shielding of low frequency noise. This is valid only if the sound source is in “free-field”. Moreover, low frequency sound absorbers work using resonance whereas porous absorbers are dissipative media (sound is converted into heat).

Figure 1. Sound absorption coefficients of various traditional materials. Data are retrieved from the published articles ^[20]^[21]^[22]^[23]^[24].

Low frequency noise arises from several human-made sources such as compressors, turbines, boilers, automobile engines, aircraft engines, music systems, loudspeakers, etc. Low frequency noise has a very high penetrative power as its dissipative power is quadratic in rate ^[25]^[26]. Even a thick concrete wall fails to attenuate low levels of low frequency noise. Researchers have reported several hazardous impacts of low-frequency noise on human health such as annoyance, headache, city-fatigue ^[27], etc. To attenuate low frequency sound, many composite structures have been demonstrated such as gradient index materials ^[28], double walls with cladding, perforated plate ^[29], acoustic mufflers, etc. These composite structures exhibit a group of sound absorbing properties from its constituent or parent materials and are capable of attenuating noise in the mid-to-high frequency range. These are widely used in many application areas such as rooms, auditoriums, offices, and airports. However, sound attenuation at low frequencies remains to be a challenging task because of the inherently weak intrinsic dissipation of traditional homogeneous materials, which usually fail to achieve broadband attenuation in this regime ^[30].

Owing to the need of low frequency sound absorption, it is desired to develop a new generation of absorbers with deep-subwavelength thickness that can be tailored for a desired frequency spectrum. In the late 1990s, a different kind of functional material known as “metamaterial” was realized, which had the capability of breaking the threshold of inherent properties of tradition sound barriers. Acoustic metamaterials are often made of artificially engineered periodic structures that give rise to unique acoustic wave characteristics, which are not found in nature ^[31]. Their unusual acoustic properties stem from their geometry and structure rather than the material composition from which they are fabricated. These properties can then be used to control acoustic wave propagation in unprecedented ways. The advent of acoustic metamaterials has revolutionized the concept of sound attenuation in more innovative and effective ways. It offers an entirely different route to further enrich the capability of researchers to design acoustic noise barriers as per specific requirements. By adjusting the geometrical size and shape of structures, acoustic metamaterials can be used for noise attenuation purpose over a specific pre-designed and tunable frequency range. The fundamental concept of acoustic metamaterials is extensively discussed in previously published review articles ^[31]^[32]^[33]^[34]^[35]^[36]^[37]^[38]^[39]^[40]^[41].

2. Applications of Acoustic Metamaterials

Noise can be reduced or obstructed by installing different kinds of acoustic metamaterials such as acoustic meta-absorbers, meta-diffusers, sonic crystals, etc. The selection of these noise barriers solely depends on the target requirement. In the following subsection, we discuss the various acoustic metamaterials, which are suitable for low-to-mid frequency noise attenuation.

2.1. Acoustic Metamaterials as Sound Absorbers

In the past few years, researchers have demonstrated the efficacy of several hybrid metasurface absorbers, combining the traditional perforated plate with subwavelength-sized metastructures. These acoustic absorbers are based on the concept of impedance-matching of surfaces with hybrid resonance ^[42]^[43]. When the acoustic impedance of a hybrid metasurface matches with that of the incoming sound wave, the metasurface neither reflects nor transmits the incoming sound wave; it almost perfectly absorbs the incoming sound energy. Cai et al. ^[44] reported a space coiling-based sound absorbing meta-panel with subwavelength thickness. The structure consists of a coplanar spiral resonant tube embedded in a traditional perforated panel backed by a rigid cavity. Figure 2a illustrates the design of a unit cell. The designed structure is capable of almost perfectly absorbing the incident sound energy at low frequencies where the impedance of overall structure matches with the incoming sound wave. In a physical sense, when the incoming sound wave enters the perforated hole, some portion of the sound wave is absorbed because of three prominent phenomena viz., Helmholtz resonance effect, energy loss due to viscous friction and heat transfer ^[45]. The remaining sound wave further slows down through the space coiled metastructures inside the air cavity. The space coiling approach is further utilized in designing various other acoustic metamaterials. Li and Assouar ^[46] proposed an ultrathin acoustic metastructure for perfect sound absorption in the low frequency range. The metastructure consists of a thin perforated plate with centered holes placed on top of a squared rigid air cavity, while a coiled space chamber is sandwiched between them. Figure 2b shows the schematic of the proposed ultrathin acoustic metastructure. Perfect sound absorption is achieved through the proposed metastructure at a frequency of 125 Hz. Jiménez et al. ^[47] reported a quasi-omnidirectional acoustic meta-absorber with a thickness of deep subwavelength regime (

< λ / 88

). The structure consists of an array of square cross-sectional Helmholtz resonators (HRs) covered with a thin top panel perforated with periodic slits. The incoming acoustic wave enters the cavities of HRs through the slits resulting in an effective sound wave attenuation in a low frequency regime. Figure 2c shows the conceptual view of the thin panel placed on a rigid wall with an array of Helmholtz resonators. The proposed metastructure was also fabricated for experimental measurements. As shown in Figure 2c; right, almost perfect absorption (α = 0.97) is achieved experimentally at 338.75 Hz. This metastructure is highly tunable, and its local resonance can be tuned by adjusting the geometrical variables. Recently, Tang et al. ^[48] presented a honeycomb-corrugation hybrid core (H-C hybrid core) acoustic metamaterial for sound absorption in the low-frequency regime. The metastructure consists of two face sheets, a lightweight perforated top plate and a rigid panel as bottom face sheet while, a sandwich perforated honeycomb-corrugation hybrid core is sandwiched between two sheets. Figure 2d shows the schematic of the proposed metastructure. The proposed metamaterial exhibits a broadband sound absorption and also possess high mechanical stiffness/strength.

Figure 2. (a) Schematic of space coiled metamaterials (left) and sound absorption plot (right), Inset shows the 3D printed unit cell. Reprinted with permission from Cai et al. ^[44], © 2014 AIP Publishing LLC; (b) schematic diagrams of the metasurface composed of a traditional perforated plate (transparent gray region) with a hole and a coiled air chamber (left). Simulated sound absorption coefficient results (right) of the proposed metasurface. Reprinted with permission from Li and Assouar ^[46], © 2016 AIP Publishing LLC; (c) schematic presentation of ultra-thin acoustic metamaterials (left), photograph of installed fabricated structure for experimentation (center) and measured absorption coefficient of the system (right). Reprinted with permission from Jiménez et al. ^[47], © 2016 AIP Publishing LLC; (d) schematic diagrams of proposed hybrid acoustic metamaterials, comprising of a perforated plate and AMs (left), sound absorption coefficient of hybrid acoustic metamaterials compared with competing structures (right). Reprinted with permission from Tang et al. ^[48], licensed under a Creative Commons Attribution 4.0 International License.

2.2. Acoustic Metamaterials as Sound Barriers

In recent years, several types of acoustic metamaterials have been reported for environmental noise mitigation showing the potential for scale-up. In early stages, membrane type metamaterials were popular for low frequency noise attenuation and showed tremendous potential for several applications like indoor noise, aircraft cabin noise mitigation ^[49]^[50]^[51]^[52]. Kumar et al. ^[53]^[54] demonstrated a membrane type double negative acoustic metamaterial for low frequency noise attenuation. The structure consists of periodically arranged unit cells, with each unit cell comprising two hexagonal cavities interconnected with a cylindrical hollow neck and an elastic membrane stacked on both ends. Figure 3a illustrates the geometrical design of the proposed metastructure. A wide band gap was achieved due to a strong coupling between the membranes and the hexagonal Helmholtz resonators. An average sound transmission loss of 45 dB(A) was attained for frequencies below 500 Hz, which satisfactorily agree with the NIOSH standards. Figure 3b shows the transmission loss spectra obtained from the double negative acoustic metastructure. Membrane type metamaterials are associated with some limitations like variation of membrane properties in environmental conditions, requirement of external equipment for membrane holding, air leakage due to poor adhesion between membrane and metastructures, manufacturing challenges in large size membrane production, etc. Recently researchers have tried to address these challenges by replacing the elastic membrane with a stiff thin polymeric plate ^[55]^[56]^[57]. Ang et al. ^[58] reported a large-scale plate type acoustic metamaterial for low-frequency noise control. The structure consists of two Mylar thin plate sheets and an internal tonraum resonator, assembled with two rigid outer frames. The incoming sound enters the metastructure through a small orifice provided onto the plate. Figure 3c depicts the schematics of the proposed unit cell. The acoustic performance of the proposed metamaterial is superior to existing commercial noise barriers. Furthermore, the plate type metamaterial is relatively simple to scale up for real applications.

Figure 3. (a) Schematics of double negative acoustic metamaterial; (b) measured and simulated sound transmission loss of the proposed metamaterials. a and b are reprinted with permission from Kumar et al. ^[53], © 2018 AIP Publishing LLC; (c) schematic of plate-type acoustic metamaterial (left) and reverberation room setup for transmission loss measurement of the large size metamaterial (right). Adapted with permission from Ang et al. ^[59], © 2019 Elsevier Ltd.

Another type of sound barriers, sonic crystals, have been widely used for the outdoor noise mitigation. The basic idea of sonic crystals conceived from the concept of photonic crystal-a refraction index-modulated periodic structures, used for manipulation of an optical wave. Sonic crystals are non-homogeneous composite structures comprising of a regular distribution of wave scatterers distributed in 3D space, whose material properties like elasticity and density differ from those of the host medium ^[60]^[61]. The size of a sonic crystal is on a deep subwavelength scale so that at specific frequencies (mid-gap frequencies), the band gap structure obstructs the incoming acoustic waves while, at frequencies away from the resonances, the composite structure allows acoustic waves to pass through it displaying weak wave scattering ^[62]. Some critical parameters mostly influencing the size of the band gap are the density ratio—the ratio between the densities of scatterer′s material and that of host medium, the filling factor—the volume fraction occupied by the scatterers and the lattice designs ^[63], so the band structure of a sonic crystal can be engineered and tuned by adjusting the above parameters. A variety of shapes such as spherical ^[62], cylindrical ^[64], square ^[65], triangular ^[66], rectangular ^[67] and honeycomb ^[68] are used to make these lattice scatterers. The spacing between two consecutive scatterers is chosen such that the periodic structures interact with the incident wave efficiently. The Bragg′s law governs the distance between two adjacent scatterers (

δ

) for destructive interference of a wave, which is as follows,

f = c / 2 δ \sin θ,

where f is the center frequency of the bandgap, c is the speed of sound and

θ

is the incident angle of incoming sound wave relative to the front plane of the array of scatterers. Therefore, the band gap frequency can also be tuned by varying the distance between the scatterers. In the past few decades, researchers have reported several innovative metamaterials based on sonic crystals for sound insulation purposes. Among these, some of the structures have shown great potential for indoor noise attenuation as well as outdoor noise. Morandi et al. ^[69] developed a real-sized sonic crystal and successfully installed it as a noise barrier in the Acoustic Laboratory of the University of Bologna. The structure is made of hollow PVC cylinders periodically arranged in a square lattice. Figure 4a shows the photograph of a fabricated sonic crystal for experimental measurements. Each vertical cylinder has a length of 3 m, the outer radius of 0.08 m and annular thickness of 3.2 mm. The width of the proposed sonic crystal noise barrier is 3 m wide, and its depth varies as per the number of rows of cylinders. They performed several acoustical measurements of the sonic crystal with different depths. Figure 4 (a, bottom) shows the measured sound insulation index at varying number of rows of cylinders. As the traffic noise spectrum is centered around 1000 Hz, the proposed structure is suitable for outdoor noise mitigation. Recently, Lee et al. ^[70] designed and developed a new kind of structure for both indoor and outdoor noise attenuation in the low-to-mid frequency range. The structure is comprised of an array of rectangular sonic crystals. Figure 4b shows the basic design of the sonic crystals. They performed several acoustical experiments in different environmental settings such as indoors, windows, outdoors, etc. for calculation of sound insertion loss of the proposed structure and validated their potential applicability. Following this work, their group designed several variants of sonic crystals such as the serrated trailing edge of ceiling fan blades ^[71], sonic crystal window ^[72] and ventilated plenum window ^[73]. More recently, Cavalieri et al. ^[74] presented a 3D locally resonant sonic crystal for broadband noise attenuation. The metastructure is made of square shaped scatterers containing periodically arranged two different kinds of resonators namely, quarter wavelength resonators and Helmholtz resonators. Figure 4c shows the schematic diagrams of both the resonators and three-dimensional unit cell. The hybrid resonators yield multiple coupled resonant frequencies and the Bragg bandgaps exhibiting a sound insertion loss of about 16.8 dB in a wide band gap ranging from 350 to 5000 Hz (Figure 4d). The structure is suitable for railway noise mitigation.

Figure 4. (a) Experimental setup for the measurement of sound insulation index (left) and sound reduction index (right) of the sonic crystal. The sample was arranged in the main hall (volume 5000 m³) of the laboratory. Measured values of sound insulation index of the sonic crystals (bottom). The central microphones were placed such that the microphone array faces the center of a cylinder. Reprinted with permission from Morandi et al. ^[69], ©2016 Elsevier Ltd; (b) photograph of rectangular sonic crystals employed as a ventilated window. The unit cell of sonic crystal window with dimensions (bottom); (c) schematic diagram of the unit cell: Local resonators (quarter wavelength and Helmholtz resonator) and a three-dimensional unit cell; (d) layout of insertion loss measurement (left) and the measured insertion loss plot (right) in the real railway noise environment. Reprinted with permission from Cavalieri et al. ^[74], ©2019 Elsevier Ltd.

Recently, acoustic metadiffusers are reported for noise shielding purposes. The acoustic metadiffusers are based on a classic design “Schroeder diffuser” used for desired sound reflection in a diffuse field. Since its first discovery in the late 1970s ^[75]^[76], the Schroeder diffuser (SD) has been used for controlling the acoustic energy level in many indoor applications like rooms, concert halls, large auditoriums, opera houses, etc. where substantial loss of sound energy is undesirable. These traditional diffusers are generally composed of a series of wells of different depths designed for the desired sound scattering. The depth of wells is based on the number sequence theories ^[75], and the overall thickness is selected according to a specific sound frequency. Figure 5a shows the basic representation of well design, so Schroeder diffusers are bulky in size, especially for low-frequency sounds such as traffic noise or human voices, the thickness of a diffuser could reach an exceptional value of 69 cm at 250 Hz, which limit their installation in real settings. In recent times, researchers have redesigned the diffusers by incorporating the concept of acoustic metamaterials with existing SDs. Zhu et al. ^[77] presented an ultrathin acoustic metadiffuser whose performance is almost similar to the conventional diffuser but with a 1/10th of thickness. The metadiffuser consists of a two-dimensional array of locally resonant wells with a single Helmholtz resonator like structure at the bottom (Figure 5b). The diffusion coefficient spectra of the proposed structure are presented in Figure 5c.

Figure 5. (a) Schematic representation of one dimensional Schroeder diffuser with seven wells. The well depth (

h_{n}

) nth well is calculated from the above-mentioned formula. Where

; is the sequence number for the nth well. Here, modulo indicates the least non-negative remainder and

N

is the number of wells per period.

λ_{0}

is the wavelength; (b) schematics of a 2D Schroeder diffuser (SD; left) and the proposed metasurface-based SD (MSD) with their unit cells; (c) simulated and measured diffusion coefficient (d_n) spectra for normal incidence (left) and 45° incidence (right) in the x–z plane versus frequency for the broadband MSD (BMSD) and the conventional SD, respectively. Figure a, b and c are reprinted with permission from ^[77], published by the American Physical Society under the terms of the Creative Commons Attribution 4.0 International license; (d) scheme of metadiffuser composed of seven slits, containing three Helmholtz resonators in each of the slits. Reprinted with permission from ^[78], published by the Springer Nature under the terms of the Creative Commons Attribution 4.0 International License.

Jiménez et al. ^[78] designed and fabricated the metadiffusers with deep-subwavelength thickness in a range of 1/46th to 1/20th times the designed wavelength. The modified diffusers were designed for frequencies ranging from 250 Hz to 2 kHz, and composed of seven sub-wavelength slits, each of them consisting of three Helmholtz resonators (Figure 5d). The Helmholtz resonators display a strong dispersion, reducing the speed of sound inside the cavities, and hence each slit behaves like a deep-subwavelength resonator. By tuning the geometries of the metadiffusers, broadband reflections in a desired frequency range can be achieved. Following these works, several metamaterial-based diffusers have also been reported ^[79]. These structures have a potential for commercialization and can be an alternative solution to the existing bulky and ineffective noise barriers.

2.3. Acoustic Metamaterials as Soundproof Ventilated Windows

A ventilated window is generally used for circulation of fresh air from the external environment into a room, but at the same time, unwanted outdoor noise travels through these vents. At times, the noise may amplify due to the architectural structure of the vents. Several traditional approaches like installation of noise barrier mats in front of the window, and use of sound absorbing materials for the fabrication of the entire window are used to reduce the noise levels. However, the problem persists, because these techniques are not adequate for low-frequency noise mitigation. Addition of auxiliary materials also result in a bulky structure, occupying substantial spaces, and restricting the air flow, which is extremely undesirable for small buildings. In the past few years, researchers have come up with unique designs of metamaterial-based windows for mitigation of outside noise in a wide band gap. The metastructures exhibit several desirable characteristics like lightweight, deep subwavelength thickness, highly tunable and can be easily fabricated using 3D printing.

Kim and Lee ^[80] presented an air transparent (air ventilation) soundproof window for the low-to-mid frequency noise mitigation. The structure consisted of a three-dimensional array of resonators with a centered hole in each resonator (Figure 6a). The air hole and rooms were separated by an automotive air filter made of sound dissipative material. The cylindrical hole allowed air circulation while resonator dampened the incoming sound wave in a particular frequency range. The sound attenuation of the structure is based on the theory of wave diffraction and the concept of “impedance matching”. A large size window of 1.2 m × 1 m is fabricated to measure the transmission loss in an anechoic chamber. The result shows a significant transmission loss of 20–35 dB in the range of 700–2200 Hz (Figure 6a). Yu et al. ^[81] demonstrated the sound transmission capabilities of a periodic acoustic metamaterial grating of finite size. Figure 6b shows the schematic of a single layer periodic acoustic metamaterial grating. Each metamaterial unit cell consists of an open duct patterned with the coiled resonators. The sound transmission behavior of the structure is mainly governed by the acoustic stop-band, the edge diffraction and the radiation interference behind the acoustic grating. A maximum transmission loss of 40 dB is achieved through the structure signifying its potential for future applications. Jung et al. ^[82] presented a muffler type acoustic metamaterial panel for ventilated sound attenuation. As shown in Figure 6c, each unit cell of the metapanel consisted of one circular duct enclosed by an array of annular cavities. The air duct allows for the air passage while the incoming sound wave is attenuated due to the acoustic impedance mismatch at the intersection between the circular duct and the annular cavity. Wu et al. ^[83] designed and fabricated a ventilated metamaterial absorber with an operating frequency of <500 Hz. The structure is composed of periodically arranged multiple unit cells. Each unit cell consists of two identical but oppositely oriented split tube resonators (Figure 6d). The gap between two adjacent unit cells allows air to flow through the structure. The high absorption of the sound wave has resulted from the weak coupling of two split tube resonators. A 3D printed sample is fabricated from polylactide (PLA) plastic for the experimental measurements (Figure 6d). The experimental result shows the maximum sound absorption of 82.1% at 342 Hz and no significant change in absorption under the oblique incidence (up to 60°). Shen et al. ^[84] presented the two-dimensional ventilated acoustic metacages with a subwavelength thickness (Figure 6e). A ring-shaped structure is created by the radial arrangement of the metacages, and each metacage is composed of several shunted Helmholtz resonators with increasing heights along the radial direction. The structure is capable of shielding the noise coming from all directions while allowing substantial airflow through a gap between two adjacent metacage. An omnidirectional acoustic shielding is realized by the fabricated structure. Li et al. ^[85] demonstrated a broadband compact acoustic absorber for the low-to-mid frequency noise absorption while ensuring high ventilation for air passage. The structure is constructed by attaching the eight unit cells to the outer periphery of the square-shaped hollow tube. Each unit cell consists of a double-layered metastructure with micro-perforated holes on opposite sides. Figure 6f shows the schematics of the proposed absorbers. The perforated unit cells serve for the sound attenuation while the hollow tube provides the passage for air ventilation (70% cross-section open). They experimentally showed the high absorption (>0.5) in the frequency range of 850–1000 Hz.

Figure 6. (a) Schematics of the air transparent soundproof window (left top), consisting of three different unit cells, namely, one, two, and four rooms (left bottom). Fabricated window installed near a highway (right top), and measured transmission loss of windows with different dimensions (right bottom). Reprinted with permission from ^[80], ©2014 Author(s); (b) schematic of a single layer periodic acoustic metamaterial grating. Reprinted with permission from ^[81], © 2019 Elsevier Ltd; (c) schematic representation of the proposed acoustic metamaterial panel, comprising of an array of unit cells, the unit cell of which consists of a circular duct (i.e., a circular hole) and an annular cavity. Reprinted with permission from ^[82], © 2018 Author(s); (d) geometrical illustration of the designed ventilated metamaterial absorber (left). Experimental setup for the transmission loss and absorption coefficient measurements of the fabricated sample (right top). Reprinted with permission from ^[83], © 2018 Author(s); (e) schematic of the metacage (left bottom) with the geometry of each unit cell. Experiment set-up of the flow rate measurement (right). Reprinted with permission from ^[84], © 2018 Author(s); (f) 3D schematic diagram of the proposed broadband compact absorber. Reprinted with permission from ^[85], © 2018 Author(s); (g) Schematics of ultra-open acoustic metamaterial silencer and a 3D printed circular unit cell; (h) acoustic transmittance and sound transmission plot of the proposed metastructure. Figure f and g are reprinted with permission from ^[86], ©2019 American Physical Society.

Recently, Ghaffarivardavagh et al. ^[86] demonstrated a prototype of ring-like ultra-open acoustic metamaterial with capabilities of silencing the incoming sound as well as allowing the air to pass through it. Figure 6g shows a 3D printed ring-like acoustic barrier. The design is based on Fano-like interference for effective sound attenuation at a desirable frequency. As shown in Figure 6h, the metastructure almost reflects the incoming sound (94%) to the environment. Their unique design has great potential for real applications like window frame for rooms, where both effective sound attenuation and proper air ventilation are required.

More recently, researchers have demonstrated asymmetric acoustic metamaterials possessing unique characteristics like unidirectional sound wave propagation. These kinds of structures allow air circulation inside the building, and at the same time, restrict outside (omnidirectional) noises. Zhang et al. ^[87] proposed an omnidirectional ventilated acoustic barrier with a planer profile and a subwavelength thickness (Figure 7a). The barrier is composed of multiple arrays of unit cells with two different structures, a hollow pipe and a labyrinthine (coiled unit). The hollow unit cell allows the uninterrupted transmission of fluid and other entities like light, while the labyrinthine unit cell blocks the omnidirectional noise. Figure 7b shows the sound transmission spectra of both unit cells. As shown, hollow pipe unit cell allows constant sound transmission (unity) over the frequency range, and on the other hand, a coiled unit cell has a transmission peak at the resonant frequency of 5600 Hz, and after that, it decreases. The acoustic barrier is capable of obstructing sound with random incident angles (ranging from normal incidence to grazing incidence) while providing high ventilation (63% ventilation rate). Ge et al. ^[88] presented an open window structure exhibiting the unidirectional acoustic insulation properties. The open window is constructed by assembling the multiple blades attached with a unique metasurface. Each metasurface is composed of a periodic array of hook-like meta-atoms (Figure 7c). During the sound wave propagation through the open window, the lateral momentum of acoustic wave changes due to the hook-like meta-atoms, which leads to an acoustic blind region. Figure 7d shows the schematic configuration of the assembled window with wave directions. As shown in figure, in the frequency range of 2.89–3.51 kHz (shadow region), the sound transmission coefficient (simulated) is less than 0.2 for the right-side incidence (RI) while for left-side incidence (LI) is higher than 0.9. For the experimental realization of these unusual properties, metastructure was fabricated using 3D printing techniques, and the sound transmission was measured for LI and RI. The experimental results show a good agreement with simulation results (Figure 7e). Following this work, they demonstrated the switchable omnidirectional acoustic insulation capabilities of the same metastructures ^[89]. The sound propagation direction of the open window structure can be switch by merely changing the configuration of the meta-atoms array. Sound insulation can also be switched “on” or “off” by adjusting the distance between two adjacent blades, i.e., tunnel gap. These studies indicate that sound transmission can be flexibly tuned as per the requirements and has great potential for future applications.

Figure 7. (a) Schematic of the omnidirectional ventilated acoustic barrier, consisting of two unit cells with different structural outlines. The wind signal represents the wind, and the “note” represents the acoustic wave in both sides of the planer surface. Photograph of a 3D printed fabricated acoustic barrier; (b) transmission spectra of the coiled structure, hollow pipe and phase delay of the resonant unit versus frequency. Figure a and b are reprinted with permission from ^[87], © 2017 Author(s); (c) schematic of an acoustic metasurface with hook-like meta-atoms; (d) schematic of unidirectional acoustic insulation (UAI) window composed of six blades and transmittance spectra for left-side incidence (LI) and right-side incidence (RI); (e) photograph of unidirectional acoustic insulation window (top) with simulated and measured transmission spectra (bottom). Figure c, d and e are reprinted with permission from ^[88]^[89] © 2018 Author(s), and ©2019 American Physical Society, respectively.

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