Patent Application
20240183576
The present invention relates to a silencer for a ventilation passage that deadens sound in a ventilation passage.
Among ventilation passages, there is a ventilation passage that comprises a silencer for deadening sound (noise) passing through the ventilation passage. Examples of such a ventilation passage with a silencer include a duct disclosed in, for example, JP2016-133226A.
The duct disclosed in JP2016-133226A includes a resonator that includes an opening portion provided on a side surface of the duct, and a soundproof cover that covers the resonator. Further, a part of the duct, the resonator, and the soundproof cover form a sound deadening structure, and noise transmitted through the duct is deadened by this sound deadening structure.
Since it is necessary to ensure an installation space for the silencer in a configuration in which the silencer is disposed outside the ventilation passage as with the duct disclosed in JP2016-133226A, the structure of a portion of the ventilation passage on which the silencer is provided is increased in size. However, considering restrictions on an installation space and the like, the silencer provided on the ventilation passage is required to have a more compact structure.
Meanwhile, sound deadening performance against sound having a low frequency band tends to deteriorate in a small silencer. For this reason, it is important for the silencer for a ventilation passage to ensure sound deadening performance against sound having a low frequency band while having a compact structure. In addition, it is preferable that the silencer for a ventilation passage can effectively deaden sound having a high frequency band together with sound having a low frequency band.
The present invention has been made in consideration of the above-mentioned circumstances, and an object of the present invention is to provide a silencer for a ventilation passage that can solve the problems in the related art, and specifically, can effectively deaden sound having a broad frequency band while having a compact structure.
In order to achieve the above-mentioned object, the present invention has the following configurations.
The silencer for a ventilation passage according to an embodiment of the present invention deadens sound having a low frequency band via the vibration of the housing that forms a part of the ventilation passage. Further, sound having a high frequency band can be deadened by the sound absorbing member disposed in the housing. As a result, it is possible to provide a silencer for a ventilation passage that can deaden sound over a high frequency band from a low frequency band by a relative compact structure.
A silencer for a ventilation passage according to an embodiment of the present invention will be described in detail below with reference to a preferred embodiment shown in the accompanying drawings. An embodiment described below is merely an example for facilitating the understanding of the present invention, and does not limit the present invention. That is, the present invention may be modified or improved from the following embodiment without departing from the scope thereof. Further, the material, the shape, or the like of each member used to implement the present invention can be set in any manner in accordance with the purpose of use of the present invention and the technical level and the like at the time of implementation of the present invention. Furthermore, the present invention includes its equivalents.
In addition, in this specification, a numerical range represented using “to” means a range that includes numerical values written before and after “to” as a lower limit and an upper limit.
Further, in this specification, “orthogonal”, “perpendicular”, and “parallel” include a range of an error to be allowed in a technical field to which the present invention pertains. For example, “orthogonal”, “perpendicular”, and “parallel” in this specification mean that an angle is in a range including an error smaller than +10° from exact orthogonal, exact perpendicular, or exact parallel. An error from exact orthogonal or exact parallel is preferably 5° or less and more preferably 3° or less.
Furthermore, in this specification, the meanings of “the same”, “identical”, and “equal” may include the range of an error to be generally allowed in the technical field to which the present invention pertains.
In addition, in this specification, the meanings of “the entire”, “any”, and “all” may include the range of an error to be generally allowed in the technical field to which the present invention pertains, and may include the case of, for example, 99% or more, 95% or more, or 90% or more in addition to the case of 100%.
Further, “sound deadening” in the present invention is a concept including both of sound insulation and sound absorption. The sound insulation means blocking sound, in other words, preventing the transmission of sound. The sound absorption means reducing reflected sound and means absorbing sound (audio) in easy terms.
Furthermore, three directions orthogonal to each other will be referred to as “XYZ directions” in the following description. The X direction corresponds to a first direction of the present invention, the Z direction corresponds to a second direction of the present invention, and the Y direction corresponds to a third direction of the present invention.
In addition, in the following description, a side of a ventilation passage closer to an air outlet will be referred to as “downstream side” and a side opposite thereto, that is, a side of the ventilation passage closer to an air inlet will be referred to as “upstream side”.
A configuration of a silencer 10 for a ventilation passage according to an embodiment of the present invention (hereinafter, referred to as the present embodiment) will be described with reference to
The silencer 10 for a ventilation passage is disposed at an intermediate position on a ventilation passage provided in, for example, a device or a building. That is, the silencer 10 for a ventilation passage is installed in a state where the silencer 10 for a ventilation passage is interposed between an upstream ventilation passage Tu positioned on an upstream side of the silencer 10 for a ventilation passage and a downstream ventilation passage Td positioned on a downstream side of the silencer 10 for a ventilation passage as shown in
As shown in
The housing 12 is a box-shaped hollow body, and includes a wall 14 that surrounds the internal space of the housing 12 as shown in
The shape of the housing 12 will be described. The width (a length in the Z direction) of the housing 12 is larger than the height (a length in the Y direction) of the housing 12. Specifically, with regard to the contour line of a cross section of which a normal direction is the X direction among cross sections of the housing 12, a ratio of the length of the longest side of the contour line to the length of the shortest side of the contour line is 1.2 or more. Here, the shortest side corresponds to the height of the housing 12, and the length of the shortest side is equal to a length d1 shown in
Each portion of the wall 14 is a plate having a relatively small thickness, and forms both end portions of the housing 12 in the XYZ directions. A material of the wall 14 is not particularly limited, but, for example, a metal material, a resin material, a reinforced plastic material, a carbon fiber, and the like can be used as the material of the wall 14.
Examples of the metal material include aluminum, titanium, magnesium, tungsten, iron, steel, chromium, chromium molybdenum, nichrome-molybdenum, copper, steel galvanized cold commercial (SGCC), and alloys, such as stainless steel.
Examples of the resin material include an acrylic resin, polymethyl methacrylate, polycarbonate, polyamideimide, polyalylate, polyetherimide, polyacetal, polyetheretherketone, polyphenylene sulfide, polysulfone, polyethylene terephthalate, polybutylene terephthalate, polyimide, an ABS resin (a copolymer synthetic resin of acrylonitrile, a flame-retardant ABS resin, butadiene, and styrene), triacetylcellulose (TAC), polypropylene (PP), polyethylene (PE), polystyrene (PS), an acrylate styrene acrylonitrile (ASA) resin, a polyvinyl chloride (PVC) resin, and a polylactic acid (PLA) resin.
Examples of the reinforced plastic material include carbon fiber reinforced plastics (CFRP) and glass fiber reinforced plastics (GFRP).
Further, natural rubber, chloroprene rubber, butyl rubber, ethylene propylene diene rubber (EPDM), silicone rubber, and rubbers including a crosslinking structure thereof can be further used as the material of the wall 14.
For example, a plurality of (specifically, six) plates are disposed in a box shape and the plates adjacent to each other are joined to each other, so that the wall 14 is formed. Alternatively, in a case where the wall 14 is divided into two fragments to be fragmented, each fragment may be formed using injection molding or the like and the fragments may be combined with each other to form the wall 14. Further, each portion of the wall 14 forms a flat plate, and two portions of the wall 14 disposed at positions facing each other are arranged in parallel. Furthermore, the outer wall surfaces 12S (XZ planes), which are positioned at both ends of the housing 12 in the Y direction, among the outer wall surfaces 12S of the housing 12 formed of the outer surfaces of the wall 14 are surfaces having the largest area among the outer wall surfaces 12S, and will be referred to as largest outer wall surfaces in the following description. The outer wall surfaces 12S of the housing 12 include one or more portions that form a plane (more specifically, a flat surface), including the largest outer wall surfaces.
Furthermore, each portion of the wall 14 is made of the same material in the present embodiment. However, the present invention is not limited thereto, and a part of the wall 14 (for example, a vibration portion 20 to be described later) may be made of a material different from the material of a peripheral portion thereof. Alternatively, a part of the wall 14, for example, the vibration portion 20 may be made of the same material as the peripheral portion thereof, but may have a thickness different from the thickness of the peripheral portion thereof.
An inlet opening portion 16 is provided at one end portion of the wall 14 in the X direction, and an outlet opening portion 18 is provided at the other end portion thereof. That is, the internal space of the housing 12 forms a part of the ventilation passage, and air (wind) flowing into the housing 12 through the inlet opening portion 16 flows out of the housing 12 through the outlet opening portion 18. In this respect, the X direction corresponds to a direction in which air flows in the housing 12, that is, a ventilation direction.
The inlet opening portion 16 and the outlet opening portion 18 are holes penetrating the wall 14 in the X direction, and communicate with the internal space of the housing 12. Further, as shown in
Here, a boundary position between the inlet opening portion 16 and the internal space of the housing 12, that is, an inner opening end of the inlet opening portion 16 corresponds to an inlet opening 16A. As shown in
In the present embodiment, openings formed in the housing 12, more specifically, in the inner wall surface of the housing 12 are only the inlet opening 16A and the outlet opening 18A.
The shape (contour shape) of each of the inlet opening 16A and the outlet opening 18A is not particularly limited, but may be, for example, a circular shape, an elliptical shape, a polygonal shape, such as a triangular shape or a quadrangular shape, or an indefinite shape. Further, the size of each of the inlet opening 16A and the outlet opening 18A may be the same or different.
Furthermore, as shown in
A surface (edge surface), which is farthest from the inlet opening portion 16 and the outlet opening portion 18 in the Z direction, of the inner wall surface of the housing 12 will be referred to as “top surface” in the following description. Further, a surface (edge surface), which is opposite to the top surface in the Z direction, of the inner wall surface of the housing 12 will be referred to as “rear surface”.
Furthermore, in the present embodiment, as seen from
From the viewpoint of improving ventilation performance, it is preferable that the range in which the inlet opening 16A is present and the range in which the outlet opening 18A is present completely coincide with each other in a case where the inlet opening 16A and the outlet opening 18A have the same size. Further, in a case where the inlet opening 16A and the outlet opening 18A have different sizes, it is preferable that a range in which a smaller opening is present is within a range in which a larger opening is present as shown in
In addition, in the present embodiment, the housing 12 is provided with a vibration portion 20 that is adapted to vibrate in response to sound entering the housing 12. The vibration portion 20 is formed of a part of the wall 14, specifically, a portion of which an outer wall surface is a flat surface. In the present embodiment, a portion forming the largest outer wall surface forms the vibration portion 20. However, a portion of the housing 12 forming the vibration portion 20 may be a portion forming the outer wall surface 12S other than the largest outer wall surface.
In the wall 14, the vibration portion 20 is continuous with a peripheral portion of the vibration portion 20. The fact that the vibration portion 20 is continuous with the peripheral portion means that the vibration portion 20 and the peripheral portion are integrated with each other. A boundary between the vibration portion 20 and the peripheral portion may be provided with a scam or may have a seamless structure without a scam. However, in a case where there is no seam between the vibration portion 20 and the peripheral portion, higher strength and higher durability can be obtained in the housing 12 as compared to a case where there is a scam (that is, a welded portion or an adhesion portion).
From the viewpoint that the vibration portion 20 easily vibrates to increase an effect caused by natural vibration, a structure in which the peripheral portion of the vibration portion 20 can be regarded as a fixed end is preferable. Here, since corners (bent portions) of the housing 12 are regarded as portion not vibrating as fixed ends, a structure in which the entire surface surrounded by corners in the wall 14 of the housing 12 functions as the vibration portion 20 is desirable.
Further, the vibration portion 20 may have a thickness smaller than a thickness of the peripheral portion to be capable of easily vibrating. Specifically, it is preferable that the thickness of the vibration portion 20 is set to 0.01×t to 0.46×t in a case where the thickness of the peripheral portion is denoted by t. In a case where the vibration portion 20 is excessively thinner than the peripheral portion, the structural strength of the housing 12 is excessively low. For this reason, it is desirable that the thickness of the vibration portion 20 is set to about 1/100 even if the thickness of the vibration portion 20 is reduced.
Furthermore, in a case where the material of a plate is the same (exactly, young's modulus is the same), the stiffness of the plate is changed in proportion to the cube of a thickness. For this reason, in a case where the thickness of the vibration portion 20 is set to 0.46 or less times the thickness of the peripheral portion, the stiffness of the peripheral portion can be increased to about 10 times the stiffness of the vibration portion 20. As a result, natural vibration can be easily obtained.
In addition, the vibration portion 20 may be a portion forming at least one outer wall surface 12S of the six outer wall surfaces 12S of the housing 12, or the vibration portion 20 may be provided over two or more surfaces.
Further, the vibration portion 20 consists of a flat plate in the present embodiment, but the present invention is not limited thereto. The vibration portion 20 may be formed of a plate that is curved in an arch shape. However, since the curved vibration portion 20 is less likely to vibrate, the vibration portion 20 having a flat shape is more preferable.
Furthermore, a portion of the housing 12 forming the vibration portion 20 is one of portions forming the largest outer wall surfaces in the present embodiment, but the present invention is not limited thereto. The housing 12 may be provided with a plurality of vibration portions 20 (see
The vibration portion 20 is adapted to vibrate at a natural frequency thereof. The natural frequency of the vibration portion 20 is determined depending on the structure (the dimensions, the shape of an outer edge, and the like) and material of the vibration portion 20, the position of the vibration portion 20 in the housing 12, a method of fixing the vibration portion 20, a method of supporting the vibration portion 20, and the like. The natural frequency of the vibration portion 20 can be specified using publicly known natural frequency analysis or natural frequency calculation.
For example, vibration is applied using an impulse hammer, such as “GK-3100” manufactured by Ono Sokki Co., Ltd., and vibration is measured with an acceleration detector and is converted into a frequency using a fast fourier transform (FFT) analyzer, so that an actually measured value of a natural frequency can be obtained as a frequency response. In a case where a measurement is made at a plurality of points at this time, a vibration mode can also be analyzed using actual measurement. Further, a tester provided as a set, such as “natural frequency measurement system CAT-SA02 NF” manufactured by RION Co., Ltd., may be used. Many JIS standards for a procedure for actually measuring a natural frequency are also determined for each industry, and a natural frequency can be obtained according to, for example, JISG0602, JISB0908, and JISC60068-2-81, and the like.
Natural frequency calculation can be performed using general structural dynamics simulation. Specifically, in a case where the size of a material, physical properties (young's modulus, density, Poisson's ratio, and the like) of a material, and surrounding constraint conditions are input to various types of commercial software, such as COMSOL, ANSYS, and Abaqus, or self-made software, a natural frequency can be calculated.
Further, in a case where the lowest-order first natural frequency among natural frequencies of the vibration portion 20 is denoted by f1 (unit: Hz) in the present embodiment, the first natural frequency f1 satisfies the following expression (1).
f1<c/(2×L) Expression (1)
In Expression (1), c denotes a sound speed (unit: m/s). Further, L denotes a distance (unit: m) between the inlet opening 16A and the outlet opening 18A, specifically, a distance between the position of a geometric center of the inlet opening 16A and a position of a geometric center of the outlet opening 18A. In a case where each opening has the shape of a circle, the position of the geometric center of each opening is the position of the center of the circle. The distance L is a distance between the openings, in other words, a length of a path along which an air stream flows in the housing 12.
The inventor of the present invention has found that sound having a low frequency band can be efficiently deadened using the vibration of the vibration portion 20 in a case where Expression (1) is satisfied. Here, a right side of Expression (1), that is, a frequency corresponding to c/(2×L) is a frequency of sound of which a half of a wavelength λ (unit: m), that is, λ/2 corresponds to the distance L. Further, a frequency corresponding to c/(2×L) corresponds to a frequency of resonance in the housing 12 in the X direction (ventilation direction), and will also be referred to as a specific resonance frequency fr in the following description.
Furthermore, in a case where the first natural frequency f1 of the vibration portion 20 satisfies the following expression (2), sound having a frequency lower than a frequency of sound of which a quarter of a wavelength 2 (unit: m), that is, 24 corresponds to the distance L can be efficiently deadened.
f1<c/(4×L) Expression (2)
A frequency band of which sound can be deadened in a case where the vibration portion 20 vibrates at the first natural frequency f1 satisfying Expression (1) or (2) is 2400 Hz or less, specifically, 1700 Hz or less (see
As shown in
The sound absorbing member 30 is housed in the housing 12 as shown in
In addition to the examples described above, various sound absorbing materials, such as a sound absorbing material consisting of a material including a minute amount of air (specifically, a sound absorbing material consisting of glass wool, rock wool, and nanofiber-based fiber), can be used as the sound absorbing material as the sound absorbing member 30. Examples of the nanofiber-based fiber include silica nanofiber and acrylic nanofiber, such as XAI manufactured by Mitsubishi Chemical Corporation.
Moreover, a sound absorbing body that consists of a plate or a film in which innumerable through-holes having a diameter of about 100 μm are formed, such as a micro perforated plate, can be used as the sound absorbing member 30. In this case, sound can be absorbed by the sound absorbing body and a rear space formed on the rear side of the sound absorbing body. Examples of the micro perforated plate include a micro perforated plate made of aluminum, such as SUONO manufactured by DAIKEN CORPORATION, a micro perforated plate made of a vinyl chloride resin, such as DI-NOC manufactured by 3M Company, and the like. Further, another sound absorbing material may be disposed in the rear space, and a plurality of sound absorbing members 30 may be used in combination.
The sound absorbing member 30 can be considered in other cases. For example, the sound absorbing member 30 may be formed of a plate-like body or a film-like body that resonates in a case where sound having a frequency close to a resonance frequency is incident thereon, and may convert sound energy into thermal energy via the internal loss of the plate or the film to absorb sound. Further, the sound absorbing member 30 may be a resonator-type sound absorbing structure consisting of a perforated plate. In a case where sound having the same frequency as a resonance frequency collides with the sound absorbing member 30, air corresponding to hole portions may vibrate and the sound absorbing member 30 may convert sound energy into thermal energy via a viscosity loss at that time. Furthermore, the sound absorbing structure and another sound absorbing material may be disposed and a plurality of sound absorbing members 30 may be used in combination.
For the reason that ventilation performance in the housing 12 is to be ensured in the housing 12, the sound absorbing member 30 is disposed to avoid the range in which the inlet opening 16A is present and the range in which the outlet opening 18A is present in the Y direction and the Z direction. Simply, the sound absorbing member 30 is disposed at a position outside the range in which the inlet opening 16A is present and is disposed at a position outside the range in which the outlet opening 18A is present in the Y direction and the Z direction. Further, the sound absorbing member 30 may have a tubular shape. In that case, a space positioned in the sound absorbing member 30, that is, the inside of the tube may form a part of the ventilation passage.
Furthermore, in order to ensure ventilation performance in the housing 12 while maintaining sound absorption performance in a high frequency band, an occupancy ratio of the sound absorbing member 30 is preferably 80% or more, more preferably 90% or more, and particularly preferably 95%. The occupancy ratio of the sound absorbing member 30 is a ratio (volume ratio) of a region, which is occupied by the sound absorbing member 30, to the volume of a space, which excludes a flow channel portion 50 (see
In addition, in a case where a sound absorbing material is used as the sound absorbing member 30, it is preferable that a flow resistivity of the sound absorbing material is in a range of 1000 (Paxs/m2) to 100000 (Paxs/m2). Further, in a case where the structure of the sound absorbing member 30 is a structure in which a plurality of layers are laminated, the flow resistance of the entire structure can be measured and a flow resistivity can be calculated from the thickness of the entire structure.
The pair of connecting members 40 is disposed in the internal space of the housing 12 as shown in
Each of the upstream connecting member 42 and the downstream connecting member 44 is a cylindrical member, and specifically has the shape of a truncated cone (that is, a tapered shape) of which an outer diameter and an inner diameter are gradually changed like a horn.
The upstream connecting member 42 is mounted on the inner wall surface of the housing 12 in a state where an end, which has a smaller diameter, of the upstream connecting member 42 faces the inlet opening 16A. Likewise, the downstream connecting member 44 is mounted on the inner wall surface of the housing 12 in a state where an end, which has a smaller diameter, of the downstream connecting member 44 faces the outlet opening 18A. In other words, the area of a cross section (specifically, an area surrounded by the outer edge of the cross section) of each connecting member 40 of which a normal direction is the X direction is increased as a distance from the opening to which each connecting member 40 is connected in the X direction is increased.
A connecting member-side opening portion 46 connected to the inlet opening 16A is provided on an inner side of the upstream connecting member 40 as shown in
It is preferable that an opening of the upstream connecting member 42 facing the inlet opening 16A has the same shape as the inlet opening 16A and has substantially the same opening area as the inlet opening 16A. It is preferable that an opening of the downstream connecting member 44 facing the outlet opening 18A has the same shape as the outlet opening 18A and has substantially the same opening area as the outlet opening 18A.
Each connecting member 40 may be made of the same material as the wall 14 of the housing 12, or may be made of the same material as the upstream ventilation passage Tu and the downstream ventilation passage Td. Further, a method of mounting each connecting member 40 is not particularly limited. For example, an edge surface of each connecting member 40 may be joined to the inner wall surface of the housing 12 and fixed by an adhesive or fasteners, such as screws. Alternatively, each connecting member 40 may be connected to the upstream ventilation passage Tu or the downstream ventilation passage Td.
The shape of each connecting member 40 may be a shape in which a peripheral wall is curved in a convex shape toward a central axis of the connecting member 40 as shown in
Further, each connecting member 40 may comprise a same-diameter portion 40a which is provided at an intermediate portion of the connecting member 40 in a direction of a central axis of the connecting member 40 (X direction) and of which a diameter is constant without being changed as shown in
Moreover, the connecting members 40 are connected to both the inlet opening 16A and the outlet opening 18A in the present embodiment, but the present invention is not limited thereto. The connecting member 40 may be connected to only any one of the inlet opening 16A or the outlet opening 18A. Further, both the inlet opening 16A and the outlet opening 18A may not be provided with the connecting members 40.
The silencer 10 for a ventilation passage deadens sound in the ventilation passage via the vibration of the vibration portion 20, acoustic resonance in the housing 12, resonance in the rear space of the connecting members 40, and the absorption of sound caused by the sound absorbing member 30.
Specifically, in a case where (2n+1)×λ/4 (n is a natural number) coincides with a distance between the inner wall surface of the housing 12 and the opening (specifically, the inlet opening 16A or the outlet opening 18A) in the silencer 10 for a ventilation passage, acoustic resonance occurs in the housing 12 at a frequency of the wavelength λ. For convenience, this resonance will be referred to as “λ/4 resonance”. The λ/4 resonance is, for example, resonance in the Z direction in
In the present embodiment, the inlet opening portion 16 and the outlet opening portion 18 are present at positions close to an end of the housing 12 in the longitudinal direction of the housing 12 (the Z direction) and are farther from the top surface of the inner wall surface of the housing 12. Since the inlet opening portion 16 and the outlet opening portion 18 are away from the top surface as described above, a resonance frequency in λ/4 resonance can be lowered.
Further, in the silencer 10 for a ventilation passage, the vibration portion 20 vibrates at the first natural frequency f1 satisfying Expression (1) described above. Accordingly, sound having a frequency lower than the frequency of sound of which λ/4 corresponds to the distance L is emitted to the outside of the housing 12 due to resonance. As a result, low-frequency sound can be deadened as shown in
Furthermore, the rear space of the connecting members 40 (specifically, the upstream connecting member 42) acts as a type of resonator in the silencer 10 for a ventilation passage, so that sound resonates in the rear space H. The rear space H is a space formed between the rear surface, which is close to the connecting members 40, of the inner wall surface of the housing 12 and the connecting members 40, and is reduced in size toward a middle position of the housing 12 in the X direction (see
Moreover, in the silencer 10 for a ventilation passage, sound is absorbed by the sound absorbing member 30 provided in the housing 12. Accordingly, as shown in
Meanwhile, as the general silencer 10 for a ventilation passage is reduced in size, it is difficult for the general silencer 10 for a ventilation passage to deaden sound having a low frequency band. On the other hand, in a case where the distance L is lengthened, the frequency band of sound to be deadened can be lowered. However, in a case where the distance L is lengthened, the housing 12 is increased in size. For this reason, it is necessary to ensure a larger installation space for the silencer 10 for a ventilation passage. On the other hand, in the silencer 10 for a ventilation passage according to the present embodiment, the frequency band of sound to be deadened can be lowered without a change in the distance L using the deadening of sound via the vibration of the vibration portion 20.
As described above, according to the silencer 10 for a ventilation passage of the present embodiment, it is possible to deaden sound over a wide range from sound having a low frequency band to sound having a high frequency band even though the size of the housing 12 is relatively compact. That is, since a resonance mode not depending on the size of the internal space of the housing 12 is used in the present embodiment, broad sound deadening can be obtained using the deadening of sound caused by the housing 12 and the absorption of sound caused by the sound absorbing member 30 together.
An internal structure of the silencer for a ventilation passage according to the embodiment of the present invention is not limited to the example shown in
In the internal structure shown in
Further, in the internal structure shown in
Further, the partition member 62 extends straight in the X direction from an upstream edge surface of the inner wall surface of the housing 12, and a distal end thereof is separated from a downstream edge surface of the inner wall surface of the housing 12. That is, a relatively wide gap is formed between the distal end of the partition member 62 and the inner wall surface (specifically, the downstream edge surface) of the housing 12. This gap corresponds to a communication portion 60c that allows the first space 60a and the second space 60b to communicate with each other.
Further, the first space 60a, which has a smaller volume, of the two spaces partitioned by the partition member 62 forms a resonance space that absorbs sound via resonance. Specifically, the first space 60a functions as an air-column resonator since a standing wave is generated in a space including the communication portion 60c (gap). The air-column resonator can match the resonance frequency thereof to the frequency of sound to be deadened to absorb the sound having the frequency.
In the silencer 10X for a ventilation passage having the internal configuration described above, portions of the housing 12 adjacent to the rear space 60 in the X and Y directions form vibration portions as shown in
In
The range in which the inlet opening 16A is present and the range in which the outlet opening 18A is present in the Y direction and the Z direction overlap with each other in the configuration shown in
In a silencer 10Y for a ventilation passage shown in
Further, even in the silencer 10Y for a ventilation passage shown in
In the silencer 10Y for a ventilation passage having the internal configuration described above, as shown in
Hereinafter, the present invention will be more specifically described with reference to examples. Materials, the amounts and proportions of the materials to be used, details and procedures of treatments, and the like described in the following examples can be changed as appropriate without departing from the scope of the present invention. Accordingly, the scope of the present invention should not be interpreted to be limited by the following examples.
In addition, “parts” is on a mass basis unless otherwise specified.
A housing made of an acrylonitrile butadiene styrene (ABS) resin was produced using a 3D printer. The housing had a rectangular parallelepiped shape and included a wall having a thickness of 2 mm, and a total length, a height, and a width (lengths in the respective XYZ directions) of the housing are 110 mm, 50 mm, and 130 mm, respectively. That is, with regard to the contour line of a cross section of the housing of which a normal direction was the X direction, a ratio of the length of the longest side to the length of the shortest side was set to 2.6:1.
Further, the housing included an inlet opening portion and an outlet opening portion, and a ventilation passage consisting of a hose having an inner diameter of 28 mm was connected to each of the opening portions. The inlet opening portion and the outlet opening portion were provided at positions shifted from a middle position of the housing in the Z direction by 28 mm.
Furthermore, QonPET (manufactured by Bridgestone KBG Co., Ltd.) as a sound absorbing member was disposed in an internal space of the housing at a position avoiding each of the regions in which the inlet opening and the outlet opening were present. The flow resistivity of this sound absorbing member was about 8000 Rayls/m.
Further, a plate-like portion forming one surface of the housing, specifically, the largest outer wall surface (a surface having a size of 130 mm×110 mm) was adapted to be capable of vibrating as a vibration portion. Natural vibration calculation was performed for this vibration portion using COMSOL Multiphysics. The fact that the periphery of the plate-like portion as the vibration portion is fixed and restrained was used as a precondition in the calculation. As a result of analysis, it was found that a first natural frequency f1 (resonance frequency) of the vibration portion is 358 Hz.
In Comparative Example 1, the thickness of a wall of the housing was set to 20 mm and vibration in the housing was suppressed. In terms of other points, the configuration of Comparative Example 1 was the same as that of Example 1.
As result of the above-mentioned natural vibration analysis that was performed for a plate-like portion of the housing of Comparative Example 1 forming the largest outer wall surface (a surface having a size of 130 mm×110 mm), the first natural frequency f1 of the plate-like portion was 2799 Hz.
A sound source was disposed on an upstream side of a silencer for a ventilation passage produced in each of Example 1 and Comparative Example 1, sound generated from the sound source was incident on the silencer for a ventilation passage, and the transmittance and reflectivity of sound incident on the silencer for a ventilation passage were measured. Measurement was performed according to a publicly known acoustic tube measurement method (specifically, ASTM E2611) with a microphone 4-terminal method using an acoustic tube having a diameter of 28 mm.
(1−transmittance-reflectivity) was defined as an absorbance and a sound absorption coefficient was obtained as an index that indicates the amount of sound deadened in the silencer for a ventilation passage. Further, a value of 10×log10(1/transmittance) was obtained as a transmission loss. Measurement results of the transmission loss are shown in
In Example 1, as seen from
On the other hand, in Comparative Example 1, as seen from
In Example 2, the width (a length in the Z direction) of the housing was set to 90 mm. That is, with regard to the contour line of a cross section of which a normal direction was the X direction among the cross sections of the housing of Example 2, a ratio of the length of the longest side to the length of the shortest side was set to 1.8:1. Further, positions where the inlet opening portion and the outlet opening portion were provided in the housing were shifted from the middle position of the housing in the Z direction by 18 mm. In terms of other points, the configuration of Example 2 was the same as that of Example 1.
As result of natural vibration analysis that was performed for a plate-like portion of the housing forming the largest outer wall surface (a surface having a size of 90 mm×110 mm), that is, a vibration portion, the first natural frequency f1 (resonance frequency) of the plate-like portion was 521 Hz. In addition, the fact that the periphery of the plate-like portion as the vibration portion is fixed and restrained was used as a precondition in the natural vibration analysis.
In Comparative Example 2, the thickness of the wall of the housing was set to 20 mm and vibration in the housing was suppressed. In terms of other points, the configuration of Comparative Example 2 was the same as that of Example 2.
As result of the natural vibration analysis that was performed for a plate-like portion of the housing of Comparative Example 2 forming the largest outer wall surface (a surface having a size of 90 mm×110 mm), the first natural frequency f1 of the plate-like portion was 3760 Hz.
In Example 2 and Comparative Example 2, in the same manner as in Example 1 and Comparative Example 1, the transmittance and reflectivity of sound incident on the silencer for a ventilation passage were measured and a transmission loss was measured. Measurement results of the transmission loss are shown in
In Example 2, as seen from
On the other hand, in Comparative Example 2, as seen from
In Example 3, positions where the inlet opening portion and the outlet opening portion were provided in the housing were set to the middle position of the housing in the Z direction. In terms of other points, the configuration of Example 3 was the same as that of Example 2. For this reason, the first natural frequency f1 of the plate-like portion forming the vibration portion in the housing had the same value (=521 Hz) as that of Example 2.
Further, in Example 3, in the same manner as in Example 1, the transmittance and reflectivity of sound incident on the silencer for a ventilation passage were measured and a transmission loss was measured. Measurement results of the transmission loss are shown in
In Example 3, as seen from
The above-mentioned points will be described in detail. In the silencers (that is, the silencers for a ventilation passage according to embodiments of the present invention) of Examples 2 and 3, λ/4 resonance occurs in the housing within a range of a distance between the inlet opening portion and the top surface of the inner wall surface of the housing. Since the sound absorbing member is disposed in the silencer, large sound absorption occurs around a frequency of λ/4 resonance, which causes a transmission loss to increase. In Example 3, the resonance frequency of λ/4 resonance was 2766 Hz in response to a distance between the center of the inlet opening and the top surface that was 31 mm. On the other hand, since the position where the inlet opening portion was provided (that is, a position where the hose was connected) was shifted from the middle position of the housing in Example 2, a distance between the center of the inlet opening and the top surface was longer than 49 mm. Further, the resonance frequency of λ/4 resonance in Example 2 was a frequency corresponding to the distance, and was specifically 1750 Hz. As a result, sound deadening performance was improved around a frequency of 1700 Hz in the silencer of Example 2, which was consistent with the fact that a transmission loss exceeding the transmission loss of the silencer of Example 3 was obtained in a low frequency band. From the above description, it is possible to adjust a frequency (resonance frequency) at which sound can be deadened by λ/4 resonance in the housing in a case where the inlet opening portion was provided at a position close to an end without being provided at the middle position of the housing in the Z direction. As a result, it is possible to obtain a high transmission loss in a low frequency band in which it is more difficult to deaden sound.
In Example 4, the width (a length in the Z direction) of the housing was set to 60 mm. That is, with regard to the contour line of a cross section of which a normal direction was the X direction among the cross sections of the housing of Example 4, a ratio of the length of the longest side to the length of the shortest side was set to 1.2:1. Further, positions where the inlet opening portion and the outlet opening portion were provided in the housing were set to the middle position of the housing in the Z direction. In terms of other points, the configuration of Example 4 was the same as that of Example 1.
As result of natural vibration analysis that was performed for a plate-like portion of the housing forming the largest outer wall surface (a surface having a size of 60 mm×110 mm), that is, a vibration portion, the first natural frequency f1 (resonance frequency) of the plate-like portion was 956 Hz. In addition, the fact that the periphery of the plate-like portion as the vibration portion is fixed and restrained was used as a precondition in the natural vibration analysis.
In Comparative Example 3, the thickness of a wall of a housing was set to 20 mm and vibration in the housing was suppressed. In terms of other points, the configuration of Comparative Example 3 was the same as that of Example 4. As result of the above-mentioned natural vibration analysis that was performed for a plate-like portion of the housing of Comparative Example 3 forming the largest outer wall surface (a surface having a size of 60 mm×110 mm), the first natural frequency f1 of the plate-like portion was 5834 Hz.
In Example 4 and Comparative Example 3, in the same manner as in Example 1 and Comparative Example 1, the transmittance and reflectivity of sound incident on the silencer for a ventilation passage were measured and a transmission loss was measured. Measurement results of the transmission loss are shown in
In Example 4, as seen from
On the other hand, as seen from
In Example 5, a connecting member was fixed to each of the inlet opening and the outlet opening on the inner wall surface of the housing. The connecting member used in Example 5 had a length of 30 mm in the X direction, and a proximal end thereof was fixed to an edge portion of each opening. Further, an opening portion (connecting member-side opening portion) of the connecting member was widened toward a distal end of the connecting member, and had a maximum opening width of 40 mm.
In terms of other points, the configuration of Example 5 was the same as that of Example 2.
Further, in Example 5, in the same manner as in Example 1, the transmittance and reflectivity of sound incident on the silencer for a ventilation passage were measured and a transmission loss was measured. Measurement results of the transmission loss are shown in
In Example 5, as seen from
In Examples 6 and 7, a weight made of an ABS resin was mounted on a central portion of the largest outer wall surface (that is, the vibration portion) of the housing and other points were the same as in Example 2. In Example 6, the radius of the weight was set to 20 mm and the height of the weight was set to 10 mm. In Example 7, the radius of the weight was set to 20 mm and the height of the weight was set to 20 mm. In the structure of each of Examples 6 and 7, the housing and the weight were collectively formed by a 3D printer.
Further, in each of Examples 6 and 7, in the same manner as in Example 1, the transmittance and reflectivity of sound incident on the silencer for a ventilation passage were measured and a transmission loss was measured. Measurement results of the transmission loss are shown in
It is possible to control a frequency at which a transmission loss is increased by providing the weight on the vibration portion as described above.
In Example 8, a silencer 10 having a structure different from that of Examples described above was produced using a 3D printer. The silencer 10 of Example 8 had a structure in which the shapes of both end portions of a wall 14 of a housing 12 in the Y direction were different from each other as shown in
The respective dimensions j1 to j6 shown in
Further, the specific resonance frequency fr (=c/(2×L)) in the housing 12 of the silencer 10 was 1234 Hz, and fr/2 (=c/(4×L)) was 617 Hz. Furthermore, the first natural frequencies of the first vibration portion 24, the second vibration portion 26, and the third vibration portion 28 were 286 Hz, 1078 Hz, and 1283 Hz, respectively. The first natural frequency of the first vibration portion 24 was sufficiently lower than fr/2 (=c/(4×L)).
In addition, QonPET as a sound absorbing member was disposed in the entire internal space of the housing 12 except for a space (that is, a flow channel portion) connecting the inlet opening and the outlet opening.
In Example 9, the thickness of the first vibration portion 24 was set to 2 mm and the thickness of each of the second vibration portion 26, the third vibration portion 28, and the bent part disposed between the second vibration portion 26 and the third vibration portion 28 was set to 20 mm. In Example 9, for the purpose of verifying an effect of the vibration of the vibration portion, the second vibration portion 26 and the third vibration portion 28 were made to be stiffer than those of Example 8 so that the second vibration portion 26 and the third vibration portion 28 were less likely to oscillate. The first natural frequency of the second vibration portion 26 in this case was 6264 Hz, and the first natural frequency of the third vibration portion 28 was 7046 Hz. In terms of other points, the configuration of Example 9 was the same as that of Example 8.
Further, in Examples 8 and 9, in the same manner as in Example 1, the transmittance and reflectivity of sound incident on the silencer for a ventilation passage were measured and a transmission loss was measured. Measurement results of the transmission loss are shown in
As shown in
In a case where a plurality of vibration portions of which first natural frequencies are changed with a change in surface size or the like as in Example 8 are provided as described above, a peak of a transmission loss based on the first natural frequency of each vibration portion can be expressed for the plurality of frequencies.
All of Examples 1 to 9 described above are within the scope of the present invention, and the effects of the present invention are apparent from the measurement results of a transmission loss in each of Examples.
In a case where wind flows in the housing of the silencer according to the embodiment of the present invention and the sound absorbing member is disposed in the housing, the path of the ventilation passage (specifically, a flow channel portion in the housing) is changed. As a result, wind noise is also changed. With regard to this point, a relationship between the volume of the sound absorbing member to be installed and the amount of wind noise was obtained from fluid calculation.
Specifically, fluid calculation was performed using a computer fluid dynamics (CFD) module of COMSOL, and the sound pressure of wind noise generated in the silencer was obtained using a Proudman analogy method. The silencer as a calculation target had the same structure as in Example 2. Here, in a case where a sound absorbing member is installed even in a hose part connected to each of the inlet opening and the outlet opening of the housing or in a flow channel portion in the housing and fills the hose part, ventilation performance is lost. Accordingly, in the fluid calculation, a state in which a ventilation portion between an inlet-side hose part and an outlet-side hose part in the internal space of the housing is opened (that is, a state in which a ventilation portion surrounded by the sound absorbing member is provided). Then, while a ratio of a space, which is occupied by the sound absorbing member, to a space, which excludes the ventilation portion, of the internal space of the housing is changed, wind noise under each ratio was obtained. Calculation results are shown in
As shown in
| Number | Date | Country | Kind |
|---|---|---|---|
| 2021-139628 | Aug 2021 | JP | national |
| 2022-118691 | Jul 2022 | JP | national |
This application is a Continuation of PCT International Application No. PCT/JP2022/030476 filed on Aug. 9, 2022, which claims priority under 35 U.S.C. § 119(a) to Japanese Patent Application No. 2021-139628 filed on Aug. 30, 2021 and Japanese Patent Application No. 2022-118691 filed on Jul. 26, 2022. The above applications are hereby expressly incorporated by reference, in their entirety, into the present application.
| Number | Date | Country | |
|---|---|---|---|
| Parent | PCT/JP2022/030476 | Aug 2022 | WO |
| Child | 18442971 | US |
