ACOUSTIC BARRIER SUPPORT STRUCTURE

专利摘要:
Structure for blocking acoustic wave energy, the structure comprising a support structure and at least one resonant membrane (110, 1110, 1600) covering a cell of the support structure, wherein the at least one resonant membrane (110, 1110, 1600) comprises at least one weight (113, 520, 620, 1112, 1121), and wherein the at least one resonant membrane (110, 1110, 1600) has an anti-resonant frequency.
公开号:FR3056812A1
申请号:FR1758583
申请日:2017-09-15
公开日:2018-03-30
发明作者:Geoffrey P. McKnight；Chia-Ming Chang；Tiffany A. Stewart；Joshua M. Montgomery；Janet M. Hogan；Thomas A. Zientek；Douglas R. Ludin
申请人:Boeing Co；
IPC主号:

专利说明:

Holder (s): THE BOEING COMPANY.
Agent (s): CABINET PLASSERAUD.
Pty ACOUSTIC BARRIER SUPPORT STRUCTURE.
_ Structure for blocking acoustic wave energy, the structure comprising a support structure and at least one resonant membrane (110, 1110, 1600) covering a cell of the support structure, in which the at least one membrane resonant (110, 1110, 1600) comprises at least one weight (113, 520, 620, 1112, 1121), and in which the at least one resonant membrane (110, 1110, 1600) has an anti-resonant frequency.
100FR 3,056 812 - A1
.110.-110
114,113
i
ACOUSTIC BARRIER SUPPORT STRUCTURE
The present invention generally relates to anti-resonant membranes, structures for supporting such membranes, and a hybrid reflective and absorbent housing defined by such anti-resonant membranes and support structures.
Noise can be harmful in a number of environments. Noise is generally recognized as being harmful and a source of pollution, such as noise, can be very penetrating and disruptive. Noise can cause negative effects in people, such as hearing loss, nausea, high blood pressure, increased stress, and the like. Sources of noise pollution can frequently be caused by machines, such as motor vehicles, aircraft, trains, generators, grinders, mixers, microwave ovens, drain pumps, and many other machines. Many of these machines can emit noise at relatively constant levels for long periods of time.
Various attempts have been made to provide noise reduction. Many soundproofing solutions are directly linked to the mass of a barrier. In general, noise transmission is governed by the law of mass density, which says that the acoustic transmission T through a barrier is inversely proportional to the product of wall thickness, mass density, and the frequency of sound. . Increasing the sound reduction characteristics of such a barrier may require increasing the thickness or mass density of the barrier, which increases the weight and size of the barrier, particularly in the low range. frequencies.
Other attempts have been made to improve noise reduction. For example, the published patent application US 2013/0087407 describes a tunable anti-resonant membrane, with a large bandwidth, with a weight disposed in a central part of the membrane. The published patent application US 2010/0212999 relates to conventional Helmholtz resonators with at least one membrane wall for the resonant housing. However, the resonance of the membrane wall (s) does not include any noise reflection capacity. US Patent No. 7,510,052 describes a noise canceling honeycomb based on a modified Helmholtz resonance effect.
However, the honeycomb solution in US Patent No. 7,510,052 does not include noise reflection capability. The published patent application US 2008/0099609 describes a tunable sound absorption system for an aircraft cabin which is tuned by selecting different materials and changing dimensions to obtain soundproofing for each specific position and aircraft. Although this application describes the details of integration of conventional barriers and absorbers, the structures described in this application US 2008/0099609 are heavy and bulky. US Patent No. 7,263,028 describes the incorporation of a plurality of particles with various characteristic acoustic impedances in a sandwich with other lightweight panels to improve sound insulation. Although this solution may be lighter or thinner than conventional solid soundproofing panels, it remains voluminous and its operating frequency for soundproofing is high, which makes it less effective for operation at low frequency. US Patent No. 7,249,653 describes sound-reducing materials which include an outer layer of stiff material which sandwiches other elastic flexible panels with an integrated mass positioned on the flexible panels. Using mechanical resonance, the panel passively absorbs the incident sound wave to reduce noise. The panel has a bandwidth of 100 Hz centered around 175 Hz and is not easily adapted to various environmental conditions. US Patents 4,149,612 and 4,325,461 describe silators. A silator is a vacuum-shaped lentiform element (biconvex lens shape) with a convex cap of sheet material. These silators include a flexible plate with an enclosed volume in which the pressure is lower than atmospheric pressure to form a vibratory system to reduce noise. To control the operating frequency, the pressure enclosed in the volume coupled to the structural configuration determines the noise blocking frequency. The fact that the operating frequency depends on the pressure in the enclosed volume means that the operating frequency depends on environmental changes, such as temperature. US Patent No. 5,851,626 describes an acoustic damping and decoupling system for a vehicle. This system includes a bubble wrap that can be filled with various damping liquids and air to allow for acoustic damping. It is an environmentally dependent passive damping system. US Patent No. 7,395,898 describes a networked anti-resonant cell panel based on flexible rubber membranes stretched over a rigid frame. However, the structures described in US Pat. No. 7,395,898 do not consider the effects of the vibration of the support frame which substantially affect the anti-resonance of each cell in terms of frequency and efficiency. In addition, the entire panel structure becomes an efficient sound transmission path, especially at resonant frequencies. The general effects due to the dynamics of both the cell and the frame could significantly affect the acoustic behavior of the panel and counter its soundproofing performance. This is particularly important in a large, lightweight and compact acoustic barrier design.
Illustrative embodiments of the present invention include, without limitation, methods, structures, and systems. In one aspect, a hybrid acoustic absorption and reflection resonator includes a rigid structure defining a cell, a membrane with at least one orifice and at least one weight attached to the rigid structure, and a back sheet attached to the rigid structure and covering the cell. The membrane is configured to reflect acoustic waves in a predetermined range of frequencies. The rigid structure, the membrane, and the back sheet define a Helmholtz cavity; the Helmholtz cavity is configured to absorb acoustic energy at a frequency within the predetermined frequency range.
In one embodiment, the membrane is configured to reflect acoustic waves at an anti-resonance frequency. In another embodiment, the membrane includes a plurality of holes. In one embodiment, the membrane has a plurality of holes. Any one of the holes may be covered by a plurality of perforations where each of the perforations has a smaller size than that of the orifice. In another embodiment, the back sheet may be a second membrane. The second membrane can be configured to reflect acoustic waves in the predetermined frequency range with or without added weight. In another embodiment, the back sheet may be a structural sheet or a plate.
In another embodiment, the membrane includes a weight. The weight can surround the hole and define a neck length of the hole. In one example, the weight may be a ring which has at least one circular opening. In other examples, the orifice may have the shape of a triangle, rectangle, square, or any other shape. The weight may have a tapered shape through its thickness. In another embodiment, the weight does not define the orifice and the neck length and the area of the orifice on the membrane is defined by a light tube which does not affect the frequency of tuning reflection of the membrane. For both embodiments, the weight added to the membrane with at least one orifice can be used to tune the absorption frequency of the Helmholtz resonator.
In another embodiment, the hybrid resonator may include at least one absorbent material positioned between the membrane and the back sheet. The absorbent material may include a porous and fibrous material. The absorbent material may also include at least one partition layer. The absorbent material can be positioned so that a small air space exists between the membrane and the absorbent material.
In another aspect, a network of hybrid resonators may include a rigid structure defining a network of cells and a plurality of hybrid resonators. Each of the plurality of hybrid resonators can be positioned in one of the cells. Each of the plurality of hybrid resonators may include a membrane attached to the rigid structure and a back sheet attached to the rigid structure and covering the cell. The membrane may include at least one orifice. The membrane with a fixed weight can be configured to reflect acoustic waves in a predetermined range of frequencies. The rigid structure, the membrane, and the back sheet can define a Helmholtz cavity. In one embodiment, the hybrid resonators in the plurality of hybrid resonators can be configured to reflect acoustic waves within the same predetermined frequency range. Some of the plurality of hybrid resonators can be configured to absorb acoustic energy at different frequencies within the predetermined frequency range. The Helmholtz cavities of some of the plurality of hybrid resonators may be substantially the same size, and some of the plurality of hybrid resonators may be configured to absorb acoustic energy at different frequencies. Absorption at different frequencies may occur depending on the positioning of an absorbent material in different locations within the Helmholtz cavities of some of the plurality of hybrid resonators.
Illustrative examples of the present invention include, without limitation, methods, structures, and systems for blocking acoustic wave energy. In one aspect, a structure includes a support structure defining a plurality of cells and at least one resonant membrane covering one of the plurality of cells. The at least one resonant membrane comprises at least one weight. The at least one resonant membrane has an antiresonant frequency and the support structure has a resonant frequency which exceeds the anti-resonant frequency of the at least one resonant membrane.
In one example, the support structure includes a plurality of horizontal structural members and a plurality of vertical structural members. The plurality of horizontal structural elements may include two exterior horizontal structural elements and at least one interior horizontal structural element, and the plurality of vertical structural elements may comprise two exterior vertical structural elements and at least one interior vertical structural element. The exterior structural elements can be twice as thick as the interior structural elements. The interior structural members may include one or more slots, and the slots may be positioned near the center of the interior structural members.
In one example, the support structure may include a plurality of horizontal or vertical structural stiffeners with a particular dimension. In another example, individual stiffeners of the structural stiffeners may have the shape of a solid beam, hollow beam, “I” beam, or “T” beam. In one example, the support structure comprises polymer composite materials. In another example, the support structure can be assembled using a high rigidity polymer adhesive. In another example, the support structure may include a metal alloy.
In another aspect, a structure may include a support structure defining a plurality of cells, at least one weight attached to the support structure near mode-form displacement ridges of the support structure, and at least one resonant membrane. covering one of the plurality of cells. The at least one resonant membrane can include at least one weight. The at least one resonant membrane can have an anti-resonant frequency and the support structure with the weight can have a resonant frequency which create a band gap of sufficient frequency between main odd resonance modes for the anti-resonant frequency of l '' at least one resonant membrane.
In one example, the weight attached to the support structure and the at least one weight of the at least one resonant membrane are selected so that primary odd resonance modes of the support structure and primary and secondary modes of the at least one resonant membrane is within a predetermined frequency range. In another example, the support structure may comprise a laminate of composite material, and the composite material may comprise a composite of carbon fiber.
In another example, the weight can be attached to the support structure in a location so that the weight does not protrude from planar surfaces of the support structure. In another example, the support structure includes a plurality of curved metal alloy strips, and some of the curved metal alloy strips are joined together. In another example, the membrane may include a polymeric material and the membrane may have a thickness within a range of from about 0.001 inch to about 0.005 inch. In another example, the support structure can define a face of the support structure, and the face can be non-planar. In another example, a plurality of vertical and horizontal stiffeners may protrude from the planar surface and divide the structure into sub-grids. In another example, the at least one resonant membrane can be attached to the support structure in a non-planar position.
Other features of the system and method of the invention are described below. The features, functions, and advantages can be obtained independently in various embodiments or can be combined in yet other embodiments, further details of which can be seen with reference to the following description and drawings.
Throughout the drawings, reference numbers can be reused to indicate a correspondence between referenced elements. The drawings are provided to illustrate the examples described herein and are not intended to limit the scope of the description.
Figure 1 illustrates an example of a network of resonant membranes attached to a frame.
Figure 2 illustrates a band eliminating filter effect for a single weight acoustic membrane.
FIG. 3 illustrates performances of various sizes of membrane network compared to a single membrane exhibiting a clear resonant behavior and a reduced transmission loss with an increasing network size.
FIG. 4 illustrates an example of a network comprising a grid structure and a number of integrated membranes.
Figures 5 and 6 illustrate examples of hierarchical designs with grids and structure weights added centrally.
FIG. 7 illustrates a graph of the speed spectrum at the center of the support structure with different central masses of structure added.
FIG. 8 illustrates a graph of the insertion loss of a large-scale 6 × 6 sound barrier with a dimension of 240 mm × 240 mm as a function of the frequency for various support structures with central weight.
Figures 9A to 9C illustrate examples of support structures with material removed from certain parts of the support structure.
Figures 10A to 10B illustrate examples of support structures with material removed from a grid support structure to create a non-planar membrane support structure.
Figure 11 illustrates an example of a hybrid membrane Helmholtz resonator that is capable of both reflecting and absorbing noise energy.
Figures 12A and 12B are graphs comparing the measurements of transmission loss and dissipation coefficient between a single antiresonance membrane and a hybrid membrane Helmholtz resonator.
FIG. 13A illustrates a test preparation for carrying out a test on various configurations of hybrid resonator. Figure 13B illustrates examples of membranes from a different angle. h Figure 13C illustrates test data graphs from various designs of two-membrane hybrid resonators.
FIGS. 14A to 14H illustrate various examples of possible configurations for hybrid membrane Helmholtz resonators.
Figure 15 illustrates an example of a support structure divided into a grid with sub-grid structures which increase the grid resonant frequency.
Figures 16A and 16B illustrate an example of a support structure formed from composite grids formed from thermoplastic. Figures 16C and 16D illustrate two examples of membrane sandwiching options and composite grids formed from thermoplastic.
Existing processes for noise reduction and control depend either on a mass to dampen the sound transmission by exchange of momentum or on active solutions which use energy and transducers to create cancellation waves out of phase with with respect to the incident energy. Foams and fibers, and acoustic blankets are traditionally used as sound absorbers, and acoustic blankets are traditionally used as acoustic barriers. For low frequency ranges, these materials may need to be extremely thick in order to reduce the sound, resulting in very heavy and bulky structures.
The sound attenuation qualities of the structure can be improved by adding mass to the entire structure. However, many noise environments do not allow heavy structures. Lightweight, compact, and variable-scale noise barriers could be beneficial in a wide range of environments. For example, commercial and military aircraft and rotorcraft could benefit from the damping or blocking of acoustic energy from engines, electronic devices, and other sources of noise with tonal noise, particularly on manned aircraft . Light barrier sound insulation could be used in aircraft, rotorcraft, and vehicle interiors for floors, ceilings, walls, toilets, cargo hold coverings, and many other situations .
Due to greater demands on fuel economy, carbon fiber composites are increasingly used as structural materials in vehicles due to their light weight and high stiffness. These materials are effective sound transmitters and reduce the background noise performance of vehicles. Previously, it was thought that ultralight structures, such as those in the range of 20 to 70 ounces per square yard, and rigid structures were too bad for the reduction of sound transmission because they are effective radiating elements.
In addition, conventional noise control depends on sound absorption or reflection to reduce the noise level. In absorbers, such as porous materials, sound propagation occurs in a network of mutually connected pores such that viscous and thermal effects result in the dissipation of acoustic energy. Energy dissipation requires air molecules to propagate through mutually connected tunnels; therefore, a thick wavelength absorbing material is usually necessary for effective absorption. As far as sound reflection barriers are concerned, noise blocking usually follows the prediction of the mass law which says that a greater reduction in noise occurs with an increasingly heavy mass and as and when as the frequency increases. However, low frequency noise with long wavelengths, which usually is very difficult to cancel with conventional methods, therefore becomes a problem for noise control engineering, particularly for lightweight vehicle design. modern low energy consumption. There is no classic solution for a light and compact approach with a combined absorption and reflection capacity for controlling low frequency noise.
Illustrated in FIG. 1 is an example of a network 100 of resonant membranes 110 fixed to a frame 120. Each of the resonant membranes 110 can have a first membrane 111 and a second membrane 112. A weight 113 can be attached to the second membrane 112. The weight can be fixed at or near the center of the second membrane 112. The membranes illustrated in FIG. 1 generally have a square shape, but other shapes are possible, such as circles, rectangles, triangles, hexagons, and the like. In one example, the first membrane 111 and the second membrane 112 comprise the same material (s) and / or have the same thickness. In another example, the first membrane 111 and the second membrane 112 comprise the same material (s). In another example, the first membrane 111 and the second membrane 112 can be fixed by means of a hinge 114. A hinge 114 can allow a designer to separate the response of the frame 120 from the system tension in membranes 111 and 112, and allow the use of stiff and creep-resistant materials for membranes 111 and 112.
In one example, the joint 114 is an elastic component, dominated by bending, built in the surface of the membranes 111 and 112, which creates a process for tuning the stiffness and therefore the resonant frequency of the membrane structure without using any voltage. The stiffness of the joint 114 is controlled by the parameters of length and thickness of the joint 114, which can be considered to be, for example, a curved plate. Thus, the stiffness is based on the modulus of elasticity, the Poisson ratio, and the thickness of the material (s) forming the joint 114. The thickness of the membrane can be between approximately 0.001 inch and approximately 0.005 thumb. In typical membranes, the tension component provides the entire flexural strength and thus defines the properties, regardless of the material selected. By adjusting the thickness and the aspect ratio of the joint 114, the stiffness of the resonant membranes 110 can be adjusted. With the ability to adjust the stiffness of the resonant membranes 110, the resonant membranes 110 can have a very low frequency response using stiff materials, such as thermoplastics and / or engineering thermorigides for membranes 111 and 112. These thermoplastics and thermorigides exhibit very low creep, which would change behavior and performance, and have high temperature stability, which is advantageous for many engineering applications. In some examples, the membranes 111 and 112 may include acrylonitrile butadiene styrene (ABS), polycarbonates (PC), polyamides (PA), polybutylene terephthalate (PBT), polyethylene terephthalate (PET), polyphenylene oxide (PPO), polysulfone (PSU), polyetherketone (PEK), polyetheretherketone (PEEK), polyphenylene sulfide (PPS) polyimides, polyoxymethylene plastic (POM), HDPE, LDPE , or nylon. It should be understood that other materials can also be used for membranes 111 and 112. Without implying any limitation, membranes 111 and 112 can also include metals, such as aluminum, brass and steel.
In some examples, the weights 113 may include iron alloys, brass alloys, aluminum, lead, ceramics, glass, stone, or other materials. In other examples, the weights 113 may be in the form of a cylinder, cube, or rectangular solid. To increase the size of the mass without influencing the length of the membrane, and without implying any limitation, the weights 113 can have the shape of a T, annular or irregular shapes according to the desired needs. The mass could couple to support structures with connecting materials, such as shape memory alloys or viscoelastic materials, to exploit the membrane properties, such as tension, damping, and local stiffness for adapt resonant dynamics, remove unwanted resonant modes and increase noise control performance.
In the example illustrated in Figure 1, the resonant membranes 110 are retained within a single network of membranes 100. The particular single network of membranes 100 illustrated in Figure 1 comprises four resonant membranes 110, each with membranes 111 and 112, weights 113, and joints 114. Many other variations of networks are possible, including variations in the overall shape of the network 100, variations in the shapes of the individual resonant membranes 110, variations in the number of resonant membranes 110, and the like.
Figure 2 illustrates a band eliminator filter effect for a single weighted acoustic membrane, such as network 100 shown in Figure 1, showing a significant reduction in transmission compared to a particular active band compared to conventional materials acoustic barrier with foam or rubber mat. When properly tuned by selection of tension, stiffness, and added weight, a membrane can create an effective barrier to acoustic energy through the principle of negative mass. In a resonant system, such as a weight membrane, there are two fundamental resonant ridges 201 and 202 for mass at maximum displacement and for the middle of the membrane, between added weight and fixed edges, at maximum displacement. Between these two fundamental resonant peaks 201 and 202, a negative mass regime 203 exists where the displacement of the membrane mode shape is a combination of these two modes. At an antinode 204 in the negative mass regime 203, the membrane acceleration becomes out of phase with respect to the pressure gradient on the membrane and, moreover, the combination of the two modes causes an almost zero displacement in the membrane. This difference in phase and effective constancy is analogous to a rigid wall and creates a significant loss of transmission through the membrane on a particular strip. As seen in FIG. 2, at the frequency of the antinode 204, the transmission loss can be more than 30 dB greater than that of a material such as an open cell foam of comparable mass thickness. This effect can be particularly useful at low frequencies where conventional barriers and absorbers are ineffective.
A single membrane can be assembled into networks of membranes in order to provide performance similar to that of the single membrane. This allows the scale of the membranes to be varied to cover large areas, which is desirable to protect user compartments in vehicles, such as cars, trucks, aircraft, and rotorcraft. Figure 3 illustrates the performance of various membrane networks, compared to a single membrane, with clear structural resonances and reduced transmission loss with increasing size. The only transmission peak is the result of a combined mode of multiple membranes, which can be controlled by design. The performances illustrated in FIG. 3 present the expected characteristics of an acoustic filter for stopping passage around a frequency of 1445 Hz. Although some of the networks - such as the lxl network, the 2x2 network, and the 3x3 network show a peak acoustic transmission loss around 1445 Hz, other networks - such as the 4x4 network, the 6x6 network, and the 8x8 network - exhibit much lower transmission loss around 1445 Hz. In particular, the network 4x4 divides the transmission loss peak into two sub-peaks. The resonances of the structure retaining the membranes in the networks degrade the transmission loss performance with increasing size.
FIG. 4 illustrates an example of a network 400 comprising a structure of a grid 410 and of a number of integrated membranes 420. In the example illustrated in FIG. 4, the grid 410 may include a number of structural elements horizontal 411 and a number of vertical structural members 412. The terms "vertical" structural members and "horizontal" structural members are used for convenience and clarity, although such structures may be aligned in any orientation. The grid 410 defines a number of cells for each of the membranes 420 intended to be positioned. In another example, the grid 410 can be made of carbon fiber composites. Each cell in the grid 410 can have at least one of the integrated membranes 420 positioned on the cell. The membranes may also include a central mass 421 to allow tuning and reduce the range of resonant frequencies. To control the dynamics and vibration of the integrated membranes 420, the width and height of the sides in an individual cell in the grid 410 can be less than 100 mm. To create barriers over large areas using smaller cells, an array or arrays of cells can be used. In one example, the external horizontal and vertical structural elements of the network 400 have a thickness which is at least twice the thickness of the internal horizontal and vertical structural elements.
In the previous solutions, such as those described in US Pat. No. 7,395,898, the support structure is described as being acoustically transparent, implying that the support structure does not contribute to the acoustic behavior of the membrane. However, when looking at the performance results of the networks illustrated in Figure 3, it appears that the support structure actually actually contributes to the acoustic behavior of the membrane. Various examples of support structures are described herein for use as support structures with integrated tuned membranes which can create high performance acoustic barriers at minimum weight.
In one example, a support structure can be created with a fundamental resonant frequency at least 10% higher than a target isolation frequency range. In another example, a hierarchical support structure can be created with a fundamental high frequency with suitable solutions, such as a non-planar and stiffened structural grid with central slots which is subsequently tuned using a central mass to establish a band gap between odd resonance modes and controlling its vibration behavior over a prescribed range of frequencies. The central mass of the support structure and the membrane masses can be selected so that the odd resonance modes of the support structure and the odd resonance modes of the membranes are within a predetermined frequency range. These examples allow the sound transmission properties of the support structure to be similar to the sound transmission properties of individual cell membranes. When both the cell structure and membranes operate with similar sound transmission properties, the result is a general lightweight structure with very high sound insulation performance. These approaches significantly increase the performance of membranes with regard to the mass of the system and the total insertion loss that can be obtained. By optimizing the design of the system at multiple length scales, a light acoustic barrier with sound insulation greater than 50 dB can be obtained. In addition, the optimized support structure associated with the membrane network allows a number of configurations so that a broadband frequency can be covered.
The support structures can be made of various materials. For example, the support structures may be made of a composite polymer material of carbon fiber or glass. Other composites can be used depending on the thermal or chemical environmental conditions. These could include ceramic or metallic matrix composites. In one example, a composite support structure may include unidirectional fibers of construction 0-90-0 with 3 plies. Such a material can provide desired stiffness and mass properties with minimum mass. In one example, a desired range of thickness for the walls of the support structure is between about 0.01 inch and about 0.035 inch. To improve the bonding of the membrane as well as the lateral and torsional stability of the tile, the edges of the network can use additional plies of composite 0-90-0. In some examples, such additional layers may result in between 8 and 12 plies. The height of the structure can be specified so that the fundamental frequency under the applied boundary conditions (usually the set conditions) is at least 10% higher than that of the intended conditions of use. The determination of this dimension can be carried out using finite element modeling, a modified beam / plate theory, or any other method.
Support structures can be fabricated using a variety of methods. In one example, an interlocking grid approach is possible, where the individual members are cut into strips with corresponding slots allowing a type of wine box construction to form cells of particular shape. The cells of particular shape can be in the form of triangles, squares, rectangles, hexagons, and any other shape. Once in place, high stiffness adhesives, such as epoxy adhesives filled with ceramic or glass, can maintain stiffness between elements despite the slots in the frame elements. In another example, support structures can be constructed from strips of material that have been mold hardened to create a wavy pattern. These patterned plates can then be deburred and bonded using a secondary process to create cells of particular shape. Such cells of particular shape can have the shape of triangles, squares, rectangles, hexagons, and any other shape. These methods may allow better scalability in manufacturing since large assemblies can be created simultaneously and then cut, using a saw, to the desired thickness, thereby reducing the number of hardening and bonding steps. .
Although composite materials provide the highest performance by weight, the method described for hierarchical acoustic barriers is not limited to a support structure of composite material. Metal alloys can also be assembled with bending and joining operations. Joining operations could be based on adhesive or welding and soldering. In addition, although the support structures can be easily formed into square and rectangular cells, other shapes and configurations are possible. For example, a support structure may have the shape of a honeycomb to allow the use of hexagonal membranes.
In a particular example, an M40J Toray® carbon fiber prepreg material can be used due to its high fiber modulus and resulting high composite stiffness. The confection is hardened and its volume is reduced in a hot press according to specifications. A grid perimeter can be made with 13 plies of the same prepreg material. This can result in perimeter thickness to prevent uneven membrane tension as well as increase the overall resonant frequency of the grid by effectively increasing the overall stiffness of the support structure. Grids can be machined with slots, interlocked, and glued together with high strength epoxy. The height of the support structure can be determined by the resonant frequency of the structure, so that resonance occurs far from the target frequency. The resulting support structure is extremely light with high stiffness at a relatively low cost, which is not possible with conventional monolithic materials.
When the gate structure alone does not provide at least one mode resonant frequency (0.1) 10% higher than the target frequency to achieve acoustic transmission loss performance, a hierarchical structure can be created by adding mass concentrated in the light support structure. FIGS. 5 and 6 illustrate examples of hierarchical designs with grids and center structure weights added to create a frequency band gap between odd modes of structure and to remove the coupled modesmembrane. In the example illustrated in FIG. 5, a support structure 500 is illustrated with a grid 510 and an added weight 520. The grid 510 comprises a number of horizontal elements 511 and a number of vertical elements 512. The added weight 520 can be constructed of any material. Dense alloys, such as alloys which include one or more of steel, stainless steel, and tungsten, can provide sufficient weight without substantially increasing the size of the support structure 500 so that performance the highest of the added weight is near the mode shape peak amplitude.
The hierarchical design and subsequent improved acoustic response can be obtained by positioning the added weight 520 in the support structure. In this way, the added weight 520 performs a function similar to the weight added to the membranes in the individual cells. To obtain synergistic effects, it is necessary that the support structure 500 has odd mode resonance frequencies far from the desired frequency isolation frequency range of the individual cells. Even modes generally form acoustic dipoles which self-compensate for sound radiation and have a limited influence on noise isolation. The resident modal frequencies of the support structure 500 can be tuned by selecting an appropriate size of the added weight 520, an appropriate mass of the added weight 520, and / or a suitable location for the added weight 520 on the support structure 500. The added weight 520 can be positioned close to the maximum displacement of the odd resonant modes. For example, the added weight 520 in Figure 5 can be effective in establishing a band gap between modes (0.1) and (0.3) by moving mode (0.1) to a lower frequency and maintaining the mode frequency (0.3) relatively stable. In addition, mass inertia eliminates the membrane-coupled coupled modes while reducing the amplitude of vibration of mode shapes, which further improves the loss of transmission of the acoustic panel.
The added weight 520 itself can be incorporated into the grid 510 in a variety of methods. In one example, the size and shape of the added weight 520 can be selected to maintain a minimum profile for the support structure 500. The added weight 520 can be joined to the support grid structure 500 as an insert with a cross-shaped slot which mates with the support grid structure 500.
In the example illustrated in FIG. 6, a support structure 600 is illustrated with a grid 610 and added weights 620. The grid 610 comprises a number of horizontal elements 611 and a number of vertical elements 612. As is shown, multiple weights 620 can be added near the odd mode displacement peaks to create the hierarchical structure which has a band gap of sufficient frequency between odd modes and suppressed vibration near the target noise isolation frequency range . Each of the added weights can be joined to the grid 610 along one or more of the horizontal elements 611 and one or more of the vertical elements 612.
The effects of a support grid with a central added weight on the displacement of the fundamental resonance of the panel in association with the suppression of the vibration of the panel are shown in Figure 7. More specifically, Figure 7 illustrates a spectrum graph speed at the center of the support structure with uniform white noise acoustic excitation. Without added weight, the support structure undergoes a main resonance at around 1750 Hz. In this particular example, the desired frequency to block the noise transmission was a band centered on 1500 Hz. By adding increasing masses, the fundamental mode is forced under 1200 Hz and simultaneously its amplitude is reduced. This is caused by the significant increase in the moment of inertia of the fundamental mode. An anti-resonance peak appears above the fundamental mode, further reducing speed and increasing transmission loss. This approach is allowed by creating a very light, very stiff support structure which can then be dramatically tuned using small additions of weight in particular locations. For the results shown in Figure 7, the largest mass added to the support structure was approximately 33% of the mass of the support structure. Depending on the particular acoustic properties desired, the added mass can vary in a range between about 10% and about 50% of the mass of the support structure.
FIG. 8 illustrates a graph of the insertion loss of a support grid with a central added weight as a function of the frequency for various weight barrier acoustic support structures. As illustrated, a maximum insertion loss 801 of approximately 50 dB could be achieved with approximately a bandwidth of 1200 Hz 802 above the level of 30 dB. Due to the support structure adapted around a specified target frequency of 1500 Hz, a lightweight acoustic tile (64 ounces / square yard) was obtained with a maximum insertion loss of approximately 50 dB. At resonance, in the membrane or the support grid structure, the vibration is the highest. Increases in vibration cause increases in transmission over the barrier. By reducing the resonant frequency of the support structure to approximately that of the resonance membrane, the two resonances occur at about the same frequency and therefore the resonance effect on the noise transmission is at a minimum. This convergence of the support structure properties and the membrane properties creates a very high loss of acoustic transmission per unit of weight.
Contrary to popular belief, lightweight structural materials that house tuned membranes can also have satisfactory acoustic reduction characteristics if they are properly designed and tuned and to complement tuned membranes. When tuned, structures can provide very effective loss of transmission at specified frequency bands. In some examples, the resonance performance and vibration characteristics of a light and stiff structural support can be tuned using one or more central masses added to the structure. The matching of the membranes and the support structure can be optimized to produce a lightweight acoustic barrier support structure for noise reduction.
In an exemplary embodiment of a resonant membrane structure, resonant membranes may be designed to provide effective sound rejection at particular frequencies by tuning and selecting suitable materials. A support structure for the resonant membranes can be designed with a light grid and a central weight to copy the sound rejection of the resonant membranes at particular frequencies. Once designed, the support structure can be formed from a lightweight material, such as, for example, thin, snap-fit carbon fiber composite grids, which provide a lightweight solution with high stiffness. Resonant membranes can be formed and positioned in individual cells of the support structure. The entire resonant membrane structure, including the support structure and the resonant membranes, exhibits cooperative anti-resonant behavior to reject noise around particular frequencies. Such a resonant membrane structure can reject acoustic energy over a specified frequency range, at a quarter to a tenth of mass per unit area of conventional acoustic barrier solutions.
Support structures can be improved by reducing material from certain parts of the support structure. As shown in Figure 9A, material can be removed from the central portion of a grid structure 900 by including slots 910 in portions of the grid. In the particular example shown in Figure 9A, the slots 910 are limited to the central 2x2 cell region of the grid structure 900. The inclusion of the slots 910 in the grid structure 900 may increase the resonant frequency of the structure 900 grid alone while simultaneously reducing the total mass of the 900 grid structure. Positioning slots in other parts of the 900 grid structure (i.e., outside of the central area) could adversely affect the acoustic performance and structural integrity of the grid structure 900. Even when the slots 910 are included in the grid structure 900, proper tuning of the acoustic properties of the grid structure 900 could include fixing a central mass to the grid structure. Adding a central mass to the grid structure 900, while also including the slots 910 in the grid structure to remove a mass from the grid structure, may seem counterproductive; however, the slots 910 and the added center mass can result in much higher performance for acoustic loss per unit mass.
Slits cut in the sides of a grid structure can take a number of forms. In Figure 9A, the slots 910 in the grid structure 900 are rectangular in shape. Figure 9B illustrates triangular slots 920 which could also be used in a grid structure. Figure 9C illustrates circular slots 930 which could also be used. Any other form of the slots could also be used to reduce the mass of the grid structure. In Figure 9A, the illustrated rectangular cutout section was selected because it exhibited an increase in fundamental resonant frequency of about 20%.
In other examples, a mass can be removed from a grid support structure to create a non-planar membrane support structure. FIG. 10A illustrates a grid structure 1000 with a flat face on the bottom the grid structure 1000 and a curved face (ie, not planar) 1010 on the top of the grid structure 1000. Resonant membranes can be fixed to the flat bottom of the grid structure 1000 while the non-planar face 1010 on top of the grid structure 1000 removes a mass from the overall grid structure 1000. The non-planar face 1010 can remove more of the mass from the center of the grid structure 1000 as edges of the grid structure 1000, as illustrated in Figure 10A. FIG. 10B illustrates an area 1020 of a grid structure 1030 from which it may be advantageous to remove a mass. It may be advantageous to leave the parts of the grid structure 1030 outside the area 1020 intact to guarantee the structural integrity of the grid structure 1030.
In additional examples, it may be advantageous to create acoustic barrier panels which have one or more curved faces. Such a barrier may be useful in certain environments, such as aircraft engines, aircraft fuselages, and the like, which may have curvature in one or more directions. Attaching resonant membranes to support structures in non-planar positions (e.g., to curved surfaces of support structures) can be difficult. However, vacuum assisted manufacturing techniques can be used to fix membranes in non-planar positions where the degree of curvature is limited to a single axis.
Other manufacturing techniques can assist and be used to attach membranes to curved surfaces where the degree of curvature includes one or more axes.
An acoustic barrier solution created on the basis of a membrane can also combine reflection and noise absorption. Such noise control results in a semi-active or active toughness approach for noise control frequency targets.
FIG. 11 illustrates an example of a hybrid membrane resonator 1100 which is capable of acoustic absorption and reflection capacities. The hybrid resonator 1100 includes two anti-resonant reflective membranes 1110 and 1120 with a small orifice 1111 in the membrane 1110. The membranes 1110 and 1120 may also be referred to as a "layer" herein. For example, first membranes, such as membrane 1110, can be considered to be a "front layer", and second membranes, such as membrane 1120, can be considered to be a "back layer". The membranes 1110 and 1120 can be connected to sides 1101 and 1102 of a support structure, such as a rigid support grid structure defining grid cells. The membrane 1110 can have a fixed weight 1112, and the membrane 1120 can have a fixed weight 1121. The weight 1112 on the membrane 1110 can be in the form of a ring (for example, a washer) in order to allow at least one passage of air. through the hole 1111. The weight 1121 on the membrane 1120 can be in the form of a disc, a ring, or any other form. The size and mass of the weights 1112 and 1121 can be determined according to a desired anti-resonant effect of the membranes 1110 and 1120, according to a desired Helmholtz resonator effect of the hybrid resonator 1100, or a combination both.
Optionally, one or more absorbers 1130 can be used in conjunction with the orifice to optimize the properties of flow resistance and sound absorption. Figure 11 shows that the absorber 1130 can be a porous material and positioned between the two membranes 1110 and 1120 with a small air space to allow vibrations of the membranes 1110 and 1120. Other absorbers include at least one partition layer which includes a thin layer with semi-porous properties. A plurality of partition layers positioned in specific locations within an air cavity can create multiple absorption ridges. The air trapped between the membranes behaves like a spring because sound waves excite trapped air. In conjunction with the air mass near the opening, the air-mass spring system resonates and dissipates the incident acoustic energy.
Although in conventional Helmholtz absorbers, the front and rear faces are assumed to be an acoustically rigid wall and not used for acoustic purposes, in the example shown in Figure 11, each of the membranes 1110 and 1120 has its own effect d antiresonance which reflects and dissipates incident sound waves 1140 (also called "acoustic waves") respectively at their antiresonance frequency. Therefore, this membrane resonator design simultaneously has adjustable absorption and reflection functionality and provides satisfactory noise reduction with a light and compact configuration. However, other configurations of two-layer Helmholtz resonators are possible. The front layer of a Helmholtz resonator can be configured to provide noise absorption, but does not necessarily have to have the shape of the membrane 1110 illustrated in Figure 11. The front layer can be configured to provide noise absorption without weight use. For example, the first layer can be configured to match a target frequency and optimize the absorption amplitude as a function of one or more of the thickness of the first layer, the diameter of an orifice in the first layer, the spacing between multiple holes in the first layer, and / or the distance between the first and second layers can also be selected. In addition, an opening in the first layer is not necessary to provide the noise absorption function of the first layer.
Figures 12A and 12B are graphs which compare measurements of transmission loss and dissipation between a single antiresonance membrane and a hybrid membrane Helmholtz resonator comprising two tuned stacked membranes. FIG. 12A represents a transmission loss as a function of the noise frequency and FIG. 12B represents a dissipation coefficient as a function of the noise frequency. For the single antiresonance membrane, first and second resonances of transmission loss drops were found to be around 470 Hz and 3500 Hz, and the anti-resonance peak was found to be around 700 Hz, as shown in Figure 12A. For the Helmholtz membrane hybrid resonator, two dissipation peaks were around frequencies corresponding to resonant frequencies (470 Hz and 3500 Hz), as shown in Figure 12B. For the hybrid membrane Helmholtz resonator, the transmission loss curve represents two groups of double first and second resonances due to a slight difference between two membranes, as shown in Figure 12A. Also, two anti-resonances were observed between the first and second groups of resonances, as shown in Figure 12B. Higher general and wideband transmission loss was achieved using the hybrid Helmholtz membrane resonator. In addition, a peak of additional dissipation coefficient near 1 indicated the combined reflectance and absorption capacity factor of the hybrid Helmholtz membrane resonator.
FIG. 13A illustrates a test preparation 1300 for carrying out a test on various configurations of hybrid resonator. Test preparation 1300 comprises a first membrane 1310 and a second membrane 1320. The first membrane can comprise one or more orifices 1311 and one or more weights 1312. The second membrane 1320 can also include one or more weights 1321. At one end of the test preparation 1300, a noise source 1330 is positioned to emit an incident noise 1331 towards the first membrane 1310. At the other end of the test preparation 1300, an anechoic barrier is positioned to absorb any noise and prevent noise from returning to the second membrane 1320. Figure 13B illustrates examples of membranes 1310 and 1320 from another angle. As shown, the first membrane 1310 may have an annular weight 1312 which surrounds an orifice 1311. The membrane 1320 may also include one or more weights 1321 in the form of discoid weights and have no orifices.
A number of variables can be used to exploit the performance of the hybrid membrane Helmholtz resonator function of the two membranes 1310 and 1320. For example, the material of the membranes 1310 and 1320, the thickness of the membranes 1310 and 1320, the voltage membranes 1310 and 1320, the distance between the membranes 1310 and 1320, the size and shape of the weights 1312 and 1321, the thickness of the weight 1312 which defines the length of the resonator neck of
Helmholtz, any material positioned between membranes 1310 and 1320, and any other number of factors, individually and / or in combination, can all have an effect on the performance of the Helmholtz resonator function with a hybrid membrane of the two membranes 1310 and 1320 .
Figure 13C illustrates test data graphs from various designs of a two-membrane hybrid resonator. By changing the mass to weight on each membrane, the anti-resonance of each membrane is tuned to achieve a loss of broadband transmission while exhibiting high absorption at the target frequency. The long dashed line indicates a design with two discoid weights and an annular weight. In this case, the transmission loss graph represents two peaks and a high dissipation coefficient is represented near 1500 Hz. However, at the same frequency, the transmission loss graph represents a relatively small transmission loss due to the Helmholtz resonance. The thin dashed line indicates a design with 1.5 discoid weight and an annular weight. In this case, the first transmission loss peak moves to a higher frequency without changing the absorption peak near 1500 Hz. The dash-dots-dots-dashes line indicates a design with 1.5 discoid weights and two ring weights. The two ring weights have the effect of increasing the neck size of the orifice in the Helmholtz resonator. In this case, there is a strong absorption peak at a lower frequency. At this frequency, the transmission loss graph represents a higher level of transmission loss, above 30 dB. By adjusting the parameters in Test Preparation 1300, the hybrid resonator can be tuned to create unwanted transmission loss over a wide frequency band and absorption over a targeted moderate frequency band. The parameters can be further adjusted, for example by adjusting the masses of the weights, the size of the weights, using materials with different densities, and the like, many different behaviors can be created to match the requirements for transmission loss and absorption of a specific application. In addition, adding absorbent materials, such as foam / acoustic fibers, into the cavity can effectively improve both the transmission loss and the absorption of hybrid membrane Helmholtz resonators.
There are several material options for constructing membrane resonators. The resonator can be transparent if transparent membranes are used. In the enclosure with heat generated components, the thermal conductivity of the membrane may be desirable to increase heat dissipation. For example, for thermal insulation required in applications such as commercial aircraft cabins or helicopter fuselages, the membrane can be coated with a heat reflecting layer to reflect heat energy. Heat insulating fibers can also be integrated between membranes to provide both acoustic and thermal insulation.
FIGS. 14A to 14F illustrate various examples of possible configurations for hybrid membrane Helmholtz resonators. Figure 14A illustrates a hybrid resonator design with a first membrane 1401 and a second membrane 1402 retained between a first wall 1403 of a support structure and a second wall 1404 of the support structure. The first membrane 1401 includes an opening 1405 and a first weight 1406. The first weight 1406 can have the shape of a ring to define a neck for the Helmholtz chamber. The second membrane 1402 can comprise a second weight 1407. The absorption frequency of the hybrid resonator can be varied by modifying one or more among the air cavity formed between the two membranes 1401 and 1402 and the walls 1403 and 1404, the length neck of the orifice 1405 which is defined by the thickness of the first weight 1406, and the size of the orifice 1405. The reflection performance of the hybrid resonator can be varied by modifying one or more among the tension of the two membranes 1401 and 1402, the material properties of the two membranes 1401 and 1402, the size of the two membranes 1401 and 1402, the stiffening pattern on the two membranes 1401 and 1402, the added materials of shape memory alloy or viscoelastics on both membranes, the thickness of the two membranes 1401 and 1402, the material of the two membranes 1401 and 1402, the masses of the weights 1406 and 1407, the sizes of the weights 1406 and 1407, and the locations nts of weights 1406 and 1407. The shape of hole 1405 need not necessarily be a circle, and may be any other shape, such as a triangle, a square, a rectangle, and the like. It is also possible that shaping the 1405 hole through its depth may provide additional control over the absorption properties.
Figure 14B illustrates a hybrid resonator design with a first membrane 1411 and a second membrane 1412 retained between a first wall 1413 of a support structure and a second wall 1414 of the support structure. The first membrane 1411 comprises an orifice 1415 and a first weight 1416. The first weight 1416 may have the shape of a ring to define a neck for the Helmholtz chamber. The second membrane 1412 can comprise a second weight 1417. Unlike the example illustrated in FIG. 14A, the example illustrated in FIG. 14B also comprises an absorber 1418. The absorber 1418 can be porous or fibrous, for example a foam with open cells or fiberglass materials. The amplitude of absorption and the bandwidth of the Helmholtz cavity can be optimized by using specific absorbent materials. The absorber 1418 can also affect the flow of sound waves through the Helmholtz cavity and the resistivity to the flow of the absorber 1418 can be optimized by selecting certain absorbent materials. To prevent contact between the absorber 1418 and the membranes 1411 and 1412, an air space can be maintained between the absorber 1418 and each of the membranes 1411 and 1412. The air space can be minimized, for example a air space in the range of about 1 mm to about 2 mm, to allow the size of the absorber 1418 to be maximized between the membranes 1411 and 1412.
FIG. 14C illustrates a design of a hybrid resonator with a membrane 1421 and a rear layer produced in the form of a rear wall 1422 retained between a first wall 1423 of a support structure and a second wall 1424 of the support structure. The membrane 1421 includes an orifice 1425 and a weight 1426. The weight 1426 can have the shape of a ring to define a neck for the Helmholtz chamber. The rear wall 1422 may be a thin sheet or plate. The rear wall 1422 can provide other functions, such as structural or thermal load protection, and can be part of the system, such as an enclosure and a device protective sheet. Although such a rear wall 1422 may not provide a membrane acoustic reflection, the Helmholtz chamber is formed by the membrane 1421 and the rear wall 1422. A minimum stiffness may be required to maintain sufficient stiffness for the Helmholtz chamber .
Figure 14D illustrates a hybrid resonator design with a first membrane 1431 and a second membrane 1432 retained between a first wall 1433 of a support structure and a second wall 1434 of the support structure. The first membrane 1431 includes an orifice 1435 and a first weight 1436. The first weight 1436 can have the shape of a ring to define a neck for the Helmholtz chamber. The second membrane 1432 can comprise a second weight 1437. Unlike the example illustrated in FIG. 14A, the example illustrated in FIG. 14D also comprises a partition layer 1438 which can increase the absorption of energy. The partition layer 1438 can be of a resistivity to the flow or of an acoustic impedance prescribed according to the requirements of the application. The location of the bulkhead layer 1438 in the depth direction of the cell can be used to create a multi-cavity effect inside a single enclosed Helmholtz chamber. Such a multi-cavity effect can be effective in broadening the absorption of the resonator.
Figure 14E illustrates a hybrid resonator design with a first membrane 1441 and a second membrane 1442 retained between a first wall 1443 of a support structure and a second wall 1444 of the support structure. The first membrane 1441 includes an orifice 1445 and a first weight 1446. The first weight 1446 can have a shape of a ring to define a neck for the Helmholtz chamber. The second membrane 1442 may include a second weight 1447. Unlike the example illustrated in Figure 14A, in the example illustrated in Figure 14E, the first membrane 1441 may include multiple perforations 1448 and 1449. A multiple perforation design can affect the absorption frequency and the absorption performance of the Helmholtz chamber due to the changes in air mass around the perforations on the first membrane 1441. By changing the aspect ratio of the orifice 1445 and the perforations 1448 and 1449 while simultaneously controlling the mass and area fraction of the first weight 1446, different absorption and reflection peaks can be created. The size and length of the neck of the perforations can be the same, to increase the absorption for a single frequency absorption, or different, to cover a wider frequency range for various applications. In case an added neck length and / or the definition of an orifice size is desirable without adding significant weight, a light tube can be used to define the orifice size and / or increase the neck length orifice without adding significant weight. In other examples, a weight may have a frustoconical shape, such as, for example, a frustoconical ring. A tapered ring may have a larger inside diameter on the side of the ring away from the membrane and a smaller inside diameter on the side of the ring near the membrane. The frustoconical shape may have an effect on the absorption of Helmholtz by the Helmholtz cavity.
Figure 14F illustrates a hybrid resonator design with a first membrane 1451 and a second membrane 1452 retained between a first wall 1453 of a support structure and a second wall 1454 of the support structure. The first membrane 1451 includes an orifice 1455 and a first weight 1456. The first weight 1456 can have a ring shape to define a neck for the Helmholtz chamber. The second membrane 1452 can comprise a second weight 1457. Unlike the example illustrated in FIG. 14A, in the example illustrated in FIG. 14F, the first membrane 1451 can comprise multiple perforations 1458 and 1459. In addition, unlike the example illustrated in FIG. 14E, in the example illustrated in FIG. 14F, each of the orifice 1455 and of the perforations 1458 and 1459 comprises a micro-perforated cover. The holes in the micro-perforated covers on port 1455 and the perforations 1458 and 1459 are smaller than the sizes of the port 1455 and the perforations 1458 and 1459. These micro-perforations can provide additional energy dissipation in compact space.
Any of the hybrid resonators described herein can be used as a single cell or in a network of cells. For example, in the example illustrated in FIG. 4, the individual integrated membranes 420 in the network can be hybrid resonators. In a flat network configuration, large areas could be covered while maintaining the properties obtained by a single hybrid resonator. In general, each of the membranes integrated 420 into a network will have the same design of anti-resonant membrane. In a larger network, if the same reflection characteristics of a cell were significantly different, the network would have a "hole" (ie, the different cell) through which noise could be transmitted and cause loss important insulation performance. On the other hand, the absorption properties have more options because not all cells need to be uniform. If all cells were configured to absorb sound within a single frequency range, absorption would be maximized at that frequency range. If cells in a network were configured to absorb sound in a different frequency range, the network could provide a bandwidth of frequency absorption. It may be desirable to keep the cell volume uniform, preventing tuning by changing the cell volume. However, the absorption frequency of each cell can always be changed by changing the length and area of the orifice. Cell uptake frequencies can also be varied by incorporating bulkheads to partially divide cells into sub-volumes. By positioning partition layers in different locations in different cells, the volume of the resonant cavities of the cells can be varied, creating an absorption range among a network of cells.
Figure 14G illustrates a design of a series of hybrid resonators. A support structure includes a number of structural members 1461 which define cell walls. The cells can have rear layers 1462. The rear layers 1462 can comprise masses 1463. Cells can also have front layers 1464. The front layers 1464 can comprise masses; however, as shown in Figure 14G, weights are not required on the front layers 1464. In addition, the front layers 1464 may include one or more holes, although holes are also not required. It may be advantageous to have front and rear layers which do not have any openings since having front and rear layers without any orifices may contain any of the masses 1463 which undo the rear layers 1462 and may reduce or eliminate the risk of foreign contaminants entering the cells. The front layers 1464 can be configured at a target frequency so that the absorption amplitude at the target frequency is within a predetermined range. The configuration of the front layers 1464 can be based on one or more of a thickness of the front layers 1464, a diameter of a hole in the front layers 1464, a spacing of holes between holes in the front layers 1646, and distances between the front layers 1464 and the rear layers 1462.
Figure 14H illustrates a design of a series of hybrid resonators. A support structure includes a number of exterior structural elements 1471 and interior structural elements 1472 which define cell walls. As shown in Figure 14H, the interior structural members 1472 may not extend as far forward (i.e., on the left in Figure 14H) as the exterior structural members 1471. Cells may have layers rear 1473. The rear layers 1473 can comprise masses 1474. The cells can also comprise a single front layer 1475 which is connected to the external structural elements 1471. Although the internal structural elements 1472 do not extend sufficiently forwards come into contact with the front layer 1475, the front layer 1475 can still provide sufficient noise absorption for the performance of hybrid resonators. The front layer 1475 can be configured at a target frequency so that the absorption amplitude at the target frequency is within a predetermined range. The configuration of the front layer 1475 can be based on one or more of a thickness of the front layer 1475, a diameter of an orifice in the front layer 1475, a spacing of holes between orifices in the front layer 1475, and distances between the front layer 1475 and the rear layer 1473.
Figure 15 illustrates an example of a support structure 1500 divided into a grid with sub-grid structures which increase the grid resonant frequency. The support structure 1500 comprises a number of vertical structural elements 1501 and a number of horizontal structural elements 1502. A subset of the horizontal structural elements 1502 has been replaced with stiffeners 1503 and 1504. The stiffeners 1503 and 1504 may have greater flexural stiffness than that of the horizontal structural members 1502 for bringing modes of the support structure 1500 within a predetermined frequency range. The stiffeners 1503 and 1504 may have fixed support ends 1505 and 1506, respectively. Although the illustration represented in FIG. 15 represents stiffeners 1503 and 1504 used in place of a subset of horizontal structural elements 1502, other stiffeners could also be used in place of a subset vertical structural members 1501.
Figures 16A and 16B illustrate an example of a support structure 1600 formed from composite grids formed from thermoplastic. FIG. 16A illustrates a top view of the support structure 1600 which includes exterior vertical support elements 1601 and 1602 and interior vertical support elements 1603, 1604, 1605, and 1606. The support structure 1600 also includes elements horizontal exterior and interior support. Parts of an interior horizontal support member 1607, 1608, 1609, 1610, and 1611 are also marked. The horizontal and vertical support elements can be made of composite materials formed from thermoplastic. Figure 16B illustrates a cross-sectional view of the support structure 1600, including a cross-sectional view of the outer vertical support members 1601 and 1602 and the inner vertical support members 1603, 1604, 1605, and 1606, and views front of the parts of the inner horizontal support member 1607, 1608, 1609, 1610, and 1611. Although the examples here have been described with respect to composites formed from thermoplastic, other materials may be used, such as '' a thermorigide material and composite resin.
FIGS. 16C and 16D illustrate two examples of sandwich arrangements 1620 and 1630 of composite membrane and grids formed from thermoplastic. In the arrangement 1620 illustrated in FIG. 16C, an upper grid 1621 is positioned on a lower grid 1622 and a membrane 1623 is positioned on the upper grid 1621. Cut parts 1624 of the upper and lower grids 1621 and 1622 are also shown. The cut parts 1624 can be cut to form cells of a support structure. In the arrangement 1630 illustrated in FIG. 16D, an upper grid 1631 is positioned on a lower grid 1632 and a membrane 1633 is positioned between the upper grid 1631 and the lower grid 1632. Cut-out parts 1634 of the upper and lower grids 1631 and 1632 are also represented. The cut parts 1634 can be cut to form cells of a support structure.
Conditional language used herein, for example, inter alia, "may", "could", "for example", and the like, unless specifically noted otherwise, or other interpretation within the context as used, is generally intended to express that certain examples include, while other examples do not include, certain characteristics, certain elements, and / or certain steps. Thus, such a conditional language is generally not intended to imply that features, elements and / or steps are in any way required for one or more examples or that one or more examples necessarily include logic for decide, with or without the author's contribution or incentive, whether these characteristics, elements and / or steps are included or must be achieved in any particular example. The terms "including", "comprising", "comprising" and the like are synonymous and are used inclusive, openly, and do not exclude elements, features, actions, additional operations, and so on. Likewise, the term "or" is used in its inclusive sense (and not in its exclusive sense) so that, when used, for example, to link a list of items, the term "or" means a, some, or all of the items in the list.
In general, the various features and methods described above can be used independently of each other, or can be combined in different ways. All possible associations and sub-associations are intended to be within the scope of this description. In addition, certain process or process blocks may be omitted in some implementations. The methods and processes described herein are also not limited to any particular sequence, and the blocks or states relating thereto can be performed in other sequences that are appropriate. For example, described blocks or states can be made in an order other than that specifically described, or multiple blocks or states can be associated in a single block or state. Illustrative blocks or states can be done in series, in parallel, or in some other way. The blocks or states can be added to or removed from the illustrative examples described. The illustrative systems and components described herein may be configured differently from what is described. For example, elements may be added to the illustrative examples described, removed therefrom, or rearranged therefrom.
Although certain examples or illustrative examples have been described, these examples have been presented by way of example only, and are not intended to limit the scope of the inventions described herein. Indeed, the new methods and systems described herein can be realized in a variety of other forms. The appended claims and their equivalents are intended to cover forms or modifications such as those that would be within the scope and spirit of some of the inventions described herein.
In addition, the description includes embodiments according to the following clauses:
Clause 1. A hybrid resonator with acoustic absorption and reflection capacities, comprising:
a rigid structure defining a cell;
a front layer fixed to the rigid structure; and a rear layer fixed to the rigid structure and in the cell;
wherein the front layer is configured to reflect acoustic waves in a predetermined range of frequencies;
wherein the rigid structure, the front layer, and the rear layer define a Helmholtz cavity, and wherein the Helmholtz cavity is configured to absorb acoustic energy at a frequency within the predetermined frequency range.
Clause 2. The hybrid resonator according to clause 1, in which the front layer is configured to reflect acoustic waves at an anti-resonance frequency.
Clause 3. The hybrid resonator according to clause 1 or 2, in which the front layer comprises a plurality of holes.
Clause 4. The hybrid resonator according to any one of clauses 1 to 3, wherein the front layer comprises at least one orifice having a plurality of perforations, in which one size of each of the plurality of perforations is smaller than a size of at least one orifice.
Clause 5. The hybrid resonator according to any one of clauses 1 to 4, in which at least one of the front layer and the rear layer is a membrane.
Clause 6. The hybrid resonator according to any one of clauses 1 to 5, wherein the back layer comprises a weight and is configured to reflect acoustic waves in the predetermined frequency range.
Clause 7. The hybrid resonator according to any of clauses 1 to 6, wherein the back layer comprises one or more of a structural sheet and a plate.
Clause 8. The hybrid resonator according to any one of clauses 1 to 7, in which the front layer comprises a weight.
Clause 9. The hybrid resonator according to clause 8, in which the weight surrounds an orifice on the front layer and defines a neck length of the orifice.
Clause 10. The hybrid resonator according to clause 9, in which the weight includes a ring and in which the orifice has the shape of a circle.
Clause 11. The hybrid resonator according to any one of clauses 8 to 10, wherein the orifice has the shape of one of the group consisting of a triangle, a square, and a rectangle.
Clause 12. The hybrid resonator according to any one of clauses 8 to 11, in which a thickness of the weight has a tapered thickness.
Clause 13. The hybrid resonator according to any one of clauses 1 to 12, further comprising an absorbent material positioned between the membrane and the back sheet.
Clause 14. The hybrid resonator according to clause 13, wherein the absorbent material comprises a porous material.
Clause 15. The hybrid resonator according to clause 13 or 14, in which the absorbent material is positioned so that an air space exists between the membrane and the absorbent material.
Clause 16. The hybrid resonator according to clause 13 or 15, in which the absorbent material comprises at least one partition layer.
Clause 17. The hybrid resonator according to any one of clauses 1 to 16, in which the front layer comprises at least one orifice and at least one tube defining a size and a length of the neck of the orifice.
Clause 18. A network of hybrid resonators, including:
a rigid structure defining a network of cells; and a plurality of hybrid resonators, each of the plurality of hybrid resonators being positioned in a cell of the cell network, in which each of the plurality of hybrid resonators comprises:
a membrane attached to the rigid structure, the membrane comprising at least one orifice, in which the membrane is configured to reflect acoustic waves in a predetermined range of frequencies, and a back sheet attached to the rigid structure and in the cell, in which the rigid structure, the membrane, and the back sheet define a Helmholtz cavity.
Clause 19. The network of hybrid resonators according to clause 18, wherein the hybrid resonators in the plurality of hybrid resonators are configured to reflect acoustic waves within the predetermined frequency range.
Clause 20. The network of hybrid resonators according to clause 19, wherein some of the plurality of hybrid resonators are configured to absorb acoustic energy at different frequencies within the predetermined frequency range.
Clause 21. The network of hybrid resonators according to clause 20, in which the Helmholtz cavities of some of the plurality of hybrid resonators have substantially similar sizes, and in which the some of the plurality of hybrid resonators are configured to absorb energy at different frequencies based on one or more of a location of the at least one orifice on the membrane, different dimensions of some of the at least one orifice on the membrane, a size of the at least one orifice on the membrane, a neck length of the at least one orifice on the membrane, an added weight on the membrane, and an absorbent material being positioned in different locations within the Helmholtz cavities of some among the plurality of hybrid resonators.
Clause 22. A structure for blocking acoustic wave energy, the structure comprising:
a support structure defining a plurality of cells; and at least one resonant membrane covering one of the plurality of cells, in which the at least one resonant membrane comprises at least one weight, and in which the at least one resonant membrane comprises an antiresonant frequency;
wherein the support structure has main odd resonant frequencies which exceed the anti-resonant frequency of the at least one resonant membrane.
Clause 23. The structure according to clause 22, in which the support structure comprises fibrous composite materials.
Clause 24. The structure according to clause 22 or 23, wherein the support structure comprises a plurality of horizontal structural elements and a plurality of vertical structural elements.
Clause 25. The structure according to clause 24, wherein the plurality of horizontal structural elements includes two exterior horizontal structural elements and at least one interior horizontal structural element, and wherein the plurality of vertical structural elements comprises two exterior vertical structural elements and at least one interior vertical structural element.
Clause 26. The structure according to clause 25, in which a thickness of the two exterior horizontal structural elements is at least twice as great as a thickness of the at least interior horizontal structural element, and in which a thickness of the two structural elements vertical vertical is at least twice as large as a thickness of the at least one internal vertical structural element.
Clause 27. The structure according to clause 25 or 26, in which a height of a first of the at least one interior vertical structural element is greater than a height of a second of the at least one vertical structural element interior, and in which a height of a first of the at least interior horizontal structural element is greater than a height of a second of the at least interior horizontal structural element.
Clause 28. The structure according to any of clauses 25 to 27, wherein the at least one interior horizontal structural member includes at least one slot, and wherein the at least one slot is positioned near a central portion of the at least interior horizontal structural element.
Clause 29. The structure according to any of clauses 25 to 28, wherein the at least one interior vertical structural member comprises at least one slot, and wherein the at least one slot is positioned near a central portion of the '' at least one interior vertical structural element.
Clause 30. The structure according to any of clauses 22 to 29, in which the support structure is assembled using a high stiff polymeric adhesive.
Clause 31. The structure according to any of clauses 22 to 29, wherein the support structure comprises a metal alloy.
Clause 32. The structure according to any of clauses 22 to 31, in which the main odd frequencies exceed the anti-resonant frequency of the at least one resonant membrane.
Clause 33. The structure of any of clauses 22 to 32, wherein the support structure includes a weight attached to the support structure near odds of displacement of odd resonant modes of the support structure.
Clause 34. The structure according to any of clauses 22 to 33, in which at least part of a structural element of the support structure is removed.
Clause 35. A structure to block the acoustic wave energy comprising:
a support structure defining a plurality of cells;
a weight attached to the support structure near peaks of displacement of odd resonant modes of the support structure; and at least one resonant membrane covering one of the plurality of cells, in which the at least one resonant membrane comprises at least one weight, and in which the at least one resonant membrane has an antiresonant frequency;
wherein the support structure with the weight has a resonant frequency which includes a frequency band which includes the anti-resonant frequency of the at least one resonant membrane.
Clause 36. The structure according to clause 35, in which the weight attached to the support structure and the at least one weight of the at least one resonant membrane are selected so that odd resonance modes of the support structure and odd resonance modes of the at least one resonant membrane are within a predetermined frequency range.
Clause 37. The structure according to clause 35 or 36, in which the support structure comprises a laminate of composite material.
Clause 38. The structure according to clause 37, in which the composite material laminate comprises a carbon fiber composite.
Clause 39. The structure according to any of clauses 35 to 38, wherein the weight is attached to the support structure in a location so that the weight does not protrude from the edges of the support structure.
Clause 40. The structure according to any of clauses 35 to 39, wherein the support structure comprises a plurality of composite grids formed of thermoplastic, and wherein the composite grids formed of thermoplastic are fixed together and with at least one membrane.
Clause 41. The structure according to any of clauses 35 to 39, wherein the support structure comprises a plurality of curved metal alloy strips, and wherein some of the plurality of curved metal alloy strips are joined to each other. other.
Clause 42. The structure according to any of clauses 35 to 41, wherein the at least one resonant membrane comprises a polymeric material and wherein the at least one resonant membrane has a thickness within a range of about 0.001 inch to about 0.005 inch.
Clause 43. The structure according to any of clauses 35 to 42, in which the support structure defines a face of the support structure, and in which the face of the support structure is not planar.
Clause 44. The structure according to any of clauses 35 to 43, wherein the at least one resonant membrane is attached to the support structure in a non-planar position.

权利要求:
Claims (25)
[1" id="c-fr-0001]
1. Structure for blocking acoustic wave energy, the structure comprising:
a support structure (500, 1500, 1600); and at least one resonant membrane (110, 1110, 1600) covering a cell of the support structure (500, 1500, 1600), wherein the at least one resonant membrane (110, 1110, 1600) comprises at least one weight (113 , 520, 620, 1112, 1121), and in which T at least one resonant membrane (110, 1110, 1600) has an anti-resonant frequency.
[2" id="c-fr-0002]
2. Structure according to claim 1, in which the support structure (500, 1500, 1600) has main odd resonant frequencies which exceed the anti-resonant frequency of Tau at least one resonant membrane.
[3" id="c-fr-0003]
3. Structure according to claim 1 or 2, wherein the support structure (500, 1500, 1600) comprises fibrous composite materials.
[4" id="c-fr-0004]
4. Structure according to claim 2 or 3, wherein the support structure (500, 1500, 1600) comprises a plurality of horizontal structural elements and a plurality of vertical structural elements.
[5" id="c-fr-0005]
5. The structure as claimed in claim 4, in which the plurality of horizontal structural elements comprises two external horizontal structural elements and at least one internal horizontal structural element, and in which the plurality of vertical structural elements comprises two external vertical structural elements and at minus an interior vertical structural element.
[6" id="c-fr-0006]
6. Structure according to claim 5, in which a thickness of the two external horizontal structural elements is at least twice as great as a thickness of Tau at least an internal horizontal structural element, and in which a thickness of the two external vertical structural elements is at at least twice as large as a thickness of T at least one interior vertical structural element.
[7" id="c-fr-0007]
7. Structure according to claim 5 or 6, in which a height of a first of Tau at least one interior vertical structural element is greater than a height of a second of Tau at least one interior vertical structural element, and in which a height of a first of the at least interior horizontal structural element is greater than a height of a second of the at least interior horizontal structural element.
[8" id="c-fr-0008]
8. Structure according to any one of claims 5 to 7, in which the at least internal horizontal structural element comprises at least one slot, and in which the at least one slot is positioned near a central part of the at least interior horizontal structural element.
[9" id="c-fr-0009]
9. Structure according to any one of claims 5 to 8, in which the at least one internal vertical structural element comprises at least one slot, and in which the at least one slot is positioned near a central part of the minus an interior vertical structural element.
[10" id="c-fr-0010]
10. Structure according to any one of claims 2 to 9, in which the support structure (500, 1500, 1600) is assembled using a high-stiffness polymer adhesive.
[11" id="c-fr-0011]
11. Structure according to any one of claims 2 to 9, in which the support structure (500, 1500, 1600) comprises a metal alloy.
[12" id="c-fr-0012]
12. Structure according to any one of claims 2 to 11, in which the main odd frequencies exceed the anti-resonant frequency of the at least one resonant membrane (110, 1110, 1600).
[13" id="c-fr-0013]
13. Structure according to any one of claims 2 to 12, in which the support structure (500, 1500, 1600) comprises a weight (113, 520, 620, 1112, 1121) fixed to the support structure (500, 1500, 1600) near odds of displacement of odd resonant modes of the support structure (500, 1500, 1600).
[14" id="c-fr-0014]
14. Structure according to any one of claims 2 to 13, in which at least part of a structural element of the support structure (500, 1500, 1600) is removed.
[15" id="c-fr-0015]
15. Structure according to claim 1 comprising:
a weight (113, 520, 620, 1112, 1121) attached to the support structure (500, 1500, 1600) near odds of displacement of odd resonant modes of the support structure (500, 1500, 1600); and in which the support structure (500, 1500, 1600) with the weight (113,
520, 620, 1112, 1121) has a resonant frequency which includes a frequency band which includes the anti-resonant frequency of the at least one resonant membrane (110, 1110, 1600).
[16" id="c-fr-0016]
16. The structure as claimed in claim 15, in which the weight (113, 520, 620, 1112, 1121) fixed to the support structure (500, 1500, 1600) and the at least one weight (113, 520, 620, 1112, 1121) of the at least one resonant membrane (110, 1110, 1600) are selected so that odd resonance modes of the support structure (500, 1500, 1600) and odd resonance modes of the at least one resonant membrane (110, 1110, 1600) is within a predetermined frequency range.
[17" id="c-fr-0017]
17. The structure of claim 15 or 16, wherein the support structure (500, 1500, 1600) comprises a laminate of composite material.
[18" id="c-fr-0018]
18. The structure of claim 17, wherein the composite material laminate comprises a carbon fiber composite.
[19" id="c-fr-0019]
19. Structure according to any one of claims 15 to 18, in which the weight (113, 520, 620, 1112, 1121) is fixed to the support structure (500, 1500, 1600) in a location so that the weight ( 113, 520, 620, 1112, 1121) does not protrude from the edges of the support structure (500, 1500, 1600).
[20" id="c-fr-0020]
20. Structure according to any one of claims 15 to 19, in which the support structure (500, 1500, 1600) comprises a plurality of composite grids formed of thermoplastic, and in which the composite grids formed of thermoplastic are fixed together and with at minus a membrane.
[21" id="c-fr-0021]
21. Structure according to any one of claims 15 to 19, in which the support structure (500, 1500, 1600) comprises a plurality of curved metal alloy strips, and in which some of the plurality of curved metal alloy strips are attached to each other.
[22" id="c-fr-0022]
22. Structure according to any one of claims 15 to 21, in which the at least one resonant membrane (110, 1110, 1600) comprises a polymer material and in which the at least one resonant membrane (110, 1110, 1600) comprises a thickness within a range of from about 0.001 inch to about 0.005 inch.
[23" id="c-fr-0023]
23. Structure according to any one of claims 15 to 22, in which the support structure (500, 1500, 1600) defines a face of the support structure (500, 1500, 1600), and in which the face of the support structure support (500, 1500, 1600) is not flat.
[24" id="c-fr-0024]
24. Structure according to any one of claims 15 to 23, wherein the at least one resonant membrane (110, 1110, 1600) is fixed to the support structure (500, 1500, 1600) in a non-planar position.
[25" id="c-fr-0025]
25. Structure according to any one of claims 15 to 23, in which 5 support structure (500, 1500, 1600) defining a plurality of cells.
100
1/17
114,113

类似技术:

---

公开号 | 公开日 | 专利标题

---

FR3056812A1|2018-03-30|ACOUSTIC BARRIER SUPPORT STRUCTURE

---

US8752667B2|2014-06-17|High bandwidth antiresonant membrane

---

US9284727B2|2016-03-15|Acoustic barrier support structure

---

US9270253B2|2016-02-23|Hybrid acoustic barrier and absorber

---

CA2720841C|2017-01-17|Acoustic insulation panel

---

WO2013050694A1|2013-04-11|Structural acoustic attenuation panel

---

Nguyen et al.2021|A broadband acoustic panel based on double-layer membrane-type metamaterials

---

EP2210783A1|2010-07-28|Acoustic screen

---

WO2017137455A1|2017-08-17|Acoustic absorber, acoustic wall and method for design and production

---

FR3013629A1|2015-05-29|SOUND CONTROL PANEL AND AIRCRAFT

---

FR2971233A1|2012-08-10|Multilayer substrate for dampening panel structure of e.g. telecommunication satellite, has skins separated by honeycomb type structure comprising tubular cells, where one of cells is provided with damping element occupying interior of cell

---

EP3043347B1|2020-03-04|Soundproofing trim panel, and aircraft

---

FR2526985A1|1983-11-18|ANTISONIC ELEMENT WITH RESONATORS

---

FR3047599A1|2017-08-11|LOW THICK PERFORATED MILLE-SHEET ACOUSTIC RESONATOR FOR VERY LOW FREQUENCY ABSORPTION OR ACOUSTIC RADIATION

---

WO2020128103A1|2020-06-25|Acoustically insulating panel

---

WO2016091708A1|2016-06-16|Vibrating device comprising embedded mechanical reflectors for defining an active plate mode propagation area and mobile apparatus comprising the device

---

EP3868602A1|2021-08-25|Headrest comprising at least one speaker system

---

FR2818421A1|2002-06-21|Acoustic sandwich panel with several degrees of freedom has two or more cellular layers of different dimensions with porous separators

---

FR3111927A1|2021-12-31|Phonic spacer

---

FR3055306A1|2018-03-02|WALL WITH EXTERNAL SKIN SUBDIVIDIZED IN MESH SPACES BY REAR STAYS AND AND FLYING OBJECT

---

WO2010112747A1|2010-10-07|Acoustic panel for receiving, emitting or absorbing sounds

---

FR2715244A1|1995-07-21|Method of absorbing acoustic waves for noise suppression

同族专利:

---

公开号 | 公开日

---

CN104347064B|2021-02-09|

---

FR3009122B1|2017-12-15|

---

FR3009122A1|2015-01-30|

---

CN104347064A|2015-02-11|

---

FR3056812B1|2021-08-27|

引用文献:

---

公开号 | 申请日 | 公开日 | 申请人 | 专利标题

---

IT201900002569A1|2019-02-22|2020-08-22|Phononic Vibes S R L|Acoustic attenuation device for sound propagated through surfaces|US2541159A|1946-01-22|1951-02-13|Paul H Geiger|Sound deadener for vibratory bodies|

---

US4667768A|1986-05-01|1987-05-26|Lockheed Corporation|Sound absorbing panel|

---

US5119427A|1988-03-14|1992-06-02|Hersh Alan S|Extended frequency range Helmholtz resonators|

---

JPH02282795A|1989-04-25|1990-11-20|Matsushita Electric Works Ltd|Sound absorbing device|

---

DE4011658C2|1990-04-11|1993-02-11|Deutsche Aerospace Ag, 8000 Muenchen, De|

---

JP3062378B2|1993-09-24|2000-07-10|松下電器産業株式会社|Sound absorbing device|

---

JP3323329B2|1994-06-17|2002-09-09|エヌ・オー・ケー・ビブラコースティック株式会社|Sound absorbing material|

---

DE19826745A1|1998-06-16|1999-12-30|Continental Ag|Damping element|

---

US6244378B1|1998-12-11|2001-06-12|Owens Corning Fiberglas Technology, Inc.|Dual sonic character acoustic panel and systems for use thereof|

---

US7395898B2|2004-03-05|2008-07-08|Rsm Technologies Limited|Sound attenuating structures|

---

JP4215790B2|2006-08-29|2009-01-28|Ｎｅｃディスプレイソリューションズ株式会社|Silencer, electronic device, and method for controlling silencing characteristics|

---

EP2232482B1|2007-12-21|2014-03-19|3M Innovative Properties Company|Sound barrier for audible acoustic frequency management|

---

CN102482965B|2009-08-28|2014-01-29|丰田自动车株式会社|Exhaust device for internal combustion engine|

---

JP5866751B2|2009-11-30|2016-02-17|ヤマハ株式会社|Acoustic resonator and acoustic chamber|

---

US9124968B2|2010-10-21|2015-09-01|Acoustic 3D Holdings Limited|Acoustic diffusion generator with wells and fluted fins|

---

CN102568466A|2010-12-14|2012-07-11|西北工业大学|Tunable negative elastic modulus acoustic metamaterial|

---

WO2013052702A1|2011-10-06|2013-04-11|Hrl Laboratories, Llc|High bandwidth antiresonant membrane|

---

IN2014CN02653A|2011-10-20|2015-06-26|Koninkl Philips Nv|EP3340236B1|2015-08-20|2020-04-08|FUJIFILM Corporation|Soundproof structure, louver, and soundproof wall|

---

CN105118496B|2015-09-11|2019-09-13|黄礼范|Acoustic metamaterial basic structural unit and its composite construction and assembly method|

---

FR3080392B1|2018-04-18|2020-12-04|Saint Gobain Placo|DYNAMIC ABSORBER WALL|

---

CN108847211B|2018-05-18|2020-09-11|上海超颖声学科技有限公司|Acoustic structure and design method thereof|

---

CN110588683A|2019-08-16|2019-12-20|哈工大机电工程研究院|Composite board for low-frequency broadband noise reduction of compartment structure|

---

CN111071431A|2019-12-24|2020-04-28|重庆再升科技股份有限公司|Low-frequency sound-absorbing noise-reducing device for aircraft cabin|

法律状态:
2018-05-14| PLFP| Fee payment|Year of fee payment: 2 |

---

2018-05-25| PLFP| Fee payment|Year of fee payment: 5 |

---

2019-05-27| PLFP| Fee payment|Year of fee payment: 6 |

---

2020-05-25| PLFP| Fee payment|Year of fee payment: 7 |

---

2021-05-25| PLFP| Fee payment|Year of fee payment: 8 |

优先权:

---

申请号 | 申请日 | 专利标题

---

US13953155|2013-07-29|

---

US13/953,155|US8857563B1|2013-07-29|2013-07-29|Hybrid acoustic barrier and absorber|

---

US13/952,995|US8869933B1|2013-07-29|2013-07-29|Acoustic barrier support structure|

---

FR1454278A|FR3009122B1|2013-07-29|2014-05-14|HYBRID ACOUSTIC BARRIER AND ABSORBER|

---