WO2009131074A1 - 加工用素材及びそれを用いる成型部材 - Google Patents
加工用素材及びそれを用いる成型部材 Download PDFInfo
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- WO2009131074A1 WO2009131074A1 PCT/JP2009/057786 JP2009057786W WO2009131074A1 WO 2009131074 A1 WO2009131074 A1 WO 2009131074A1 JP 2009057786 W JP2009057786 W JP 2009057786W WO 2009131074 A1 WO2009131074 A1 WO 2009131074A1
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- Prior art keywords
- vibration
- processing
- metal cover
- present
- hole
- Prior art date
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Images
Classifications
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- G—PHYSICS
- G10—MUSICAL INSTRUMENTS; ACOUSTICS
- G10K—SOUND-PRODUCING DEVICES; METHODS OR DEVICES FOR PROTECTING AGAINST, OR FOR DAMPING, NOISE OR OTHER ACOUSTIC WAVES IN GENERAL; ACOUSTICS NOT OTHERWISE PROVIDED FOR
- G10K11/00—Methods or devices for transmitting, conducting or directing sound in general; Methods or devices for protecting against, or for damping, noise or other acoustic waves in general
- G10K11/16—Methods or devices for protecting against, or for damping, noise or other acoustic waves in general
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B21—MECHANICAL METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
- B21D—WORKING OR PROCESSING OF SHEET METAL OR METAL TUBES, RODS OR PROFILES WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
- B21D47/00—Making rigid structural elements or units, e.g. honeycomb structures
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60R—VEHICLES, VEHICLE FITTINGS, OR VEHICLE PARTS, NOT OTHERWISE PROVIDED FOR
- B60R13/00—Elements for body-finishing, identifying, or decorating; Arrangements or adaptations for advertising purposes
- B60R13/08—Insulating elements, e.g. for sound insulation
- B60R13/0876—Insulating elements, e.g. for sound insulation for mounting around heat sources, e.g. exhaust pipes
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01N—GAS-FLOW SILENCERS OR EXHAUST APPARATUS FOR MACHINES OR ENGINES IN GENERAL; GAS-FLOW SILENCERS OR EXHAUST APPARATUS FOR INTERNAL COMBUSTION ENGINES
- F01N13/00—Exhaust or silencing apparatus characterised by constructional features ; Exhaust or silencing apparatus, or parts thereof, having pertinent characteristics not provided for in, or of interest apart from, groups F01N1/00 - F01N5/00, F01N9/00, F01N11/00
- F01N13/08—Other arrangements or adaptations of exhaust conduits
- F01N13/10—Other arrangements or adaptations of exhaust conduits of exhaust manifolds
- F01N13/102—Other arrangements or adaptations of exhaust conduits of exhaust manifolds having thermal insulation
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
- F02B77/00—Component parts, details or accessories, not otherwise provided for
- F02B77/11—Thermal or acoustic insulation
- F02B77/13—Acoustic insulation
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
- F16F15/00—Suppression of vibrations in systems; Means or arrangements for avoiding or reducing out-of-balance forces, e.g. due to motion
- F16F15/02—Suppression of vibrations of non-rotating, e.g. reciprocating systems; Suppression of vibrations of rotating systems by use of members not moving with the rotating systems
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01N—GAS-FLOW SILENCERS OR EXHAUST APPARATUS FOR MACHINES OR ENGINES IN GENERAL; GAS-FLOW SILENCERS OR EXHAUST APPARATUS FOR INTERNAL COMBUSTION ENGINES
- F01N13/00—Exhaust or silencing apparatus characterised by constructional features ; Exhaust or silencing apparatus, or parts thereof, having pertinent characteristics not provided for in, or of interest apart from, groups F01N1/00 - F01N5/00, F01N9/00, F01N11/00
- F01N13/14—Exhaust or silencing apparatus characterised by constructional features ; Exhaust or silencing apparatus, or parts thereof, having pertinent characteristics not provided for in, or of interest apart from, groups F01N1/00 - F01N5/00, F01N9/00, F01N11/00 having thermal insulation
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01N—GAS-FLOW SILENCERS OR EXHAUST APPARATUS FOR MACHINES OR ENGINES IN GENERAL; GAS-FLOW SILENCERS OR EXHAUST APPARATUS FOR INTERNAL COMBUSTION ENGINES
- F01N13/00—Exhaust or silencing apparatus characterised by constructional features ; Exhaust or silencing apparatus, or parts thereof, having pertinent characteristics not provided for in, or of interest apart from, groups F01N1/00 - F01N5/00, F01N9/00, F01N11/00
- F01N13/18—Construction facilitating manufacture, assembly, or disassembly
- F01N13/1838—Construction facilitating manufacture, assembly, or disassembly characterised by the type of connection between parts of exhaust or silencing apparatus, e.g. between housing and tubes, between tubes and baffles
- F01N13/1844—Mechanical joints
- F01N13/1855—Mechanical joints the connection being realised by using bolts, screws, rivets or the like
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01N—GAS-FLOW SILENCERS OR EXHAUST APPARATUS FOR MACHINES OR ENGINES IN GENERAL; GAS-FLOW SILENCERS OR EXHAUST APPARATUS FOR INTERNAL COMBUSTION ENGINES
- F01N2260/00—Exhaust treating devices having provisions not otherwise provided for
- F01N2260/20—Exhaust treating devices having provisions not otherwise provided for for heat or sound protection, e.g. using a shield or specially shaped outer surface of exhaust device
-
- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
- Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
- Y10T428/00—Stock material or miscellaneous articles
- Y10T428/24—Structurally defined web or sheet [e.g., overall dimension, etc.]
- Y10T428/24273—Structurally defined web or sheet [e.g., overall dimension, etc.] including aperture
Definitions
- the present invention is used for an object that generates vibration and noise as an example, and a processing material made of a single thin plate material that realizes a vibration damping action and a sound absorbing action on the object, and a molded member using the same It is about.
- An example of an object that generates such vibration is an internal combustion engine.
- Heat, noise, vibration, and the like are dissipated to the outside from an exhaust system such as an internal combustion engine body and an exhaust manifold (hereinafter referred to as “exhaust manifold”) connected to the internal combustion engine.
- exhaust manifold an exhaust manifold
- various covers such as an insulator are used for the vibration source in order to prevent a situation in which the vibration is radiated from the vibration source such as the internal combustion engine body or the exhaust system.
- FIG. 18 is a perspective view of a typical prior art exhaust manifold insulator (hereinafter referred to as “insulator”) 1 described in Patent Document 1 below.
- insulator a typical prior art exhaust manifold insulator 1 described in Patent Document 1 below.
- the insulator 1 will be described with reference to FIG.
- the insulator 1 is attached to the exhaust manifold of the internal combustion engine and covers the exhaust manifold.
- the insulator 1 has a substantially flat front surface portion 1a and a side wall portion 1b that is bent from the front surface portion 1a and extends toward the cylinder head of the internal combustion engine.
- the insulator 1 is formed by overlapping two steel plates 1A and 1B, and at one appropriate position of the edge of the slit 2, one of the two steel plates is folded at the folded portion with respect to the other steel plate. . By this folding, the bonding of the two steel plates 1A and 1B is strengthened.
- This prior art insulator 1 has a structure in which two steel plates 1A and 1B are overlapped, and the vibration of the frequency generated from the exhaust manifold through which high-temperature exhaust gas pulsating at a frequency of several thousand times per minute passes. , It acts so as not to be dissipated in the dark.
- JP-A-10-266850 (8th to 11th paragraphs and FIG. 1)
- Such a conventional insulator has a configuration in which the two steel plates 1A and 1B are overlapped as described above, and has a problem that it is relatively heavy.
- the insulator 1 when the insulator 1 generates surface vibration due to vibration propagated from the exhaust manifold and the vibration frequency matches the resonance frequency of the insulator 1, the insulator 1 itself becomes a noise source.
- the insulator is also required to be lighter and further improved in damping performance.
- the present invention has been made in order to solve the above-mentioned problems, and its purpose is to significantly improve the vibration damping performance, the sound insulation performance and the sound absorption performance, and to improve the weight reduction and the mechanical strength of the product.
- a processing material that can be processed and a molded member using the processing material are provided.
- the processing material according to the first aspect of the present invention is formed in a thin plate material that can be elastically deformed, in which a first corrugated shape in which trough portions and raised portions are alternately repeated is formed along the first direction, and the first direction.
- a second corrugated shape in which valleys and ridges are alternately repeated is formed in a row along a second direction intersecting with the first corrugated shape, and in the first corrugated shape, the ridges are a pair of side parts rising from the troughs, And the apex length along the first direction of the top part is defined longer than the opening length along the first direction of the base end part of the pair of side parts. .
- the processing material according to a second aspect of the present invention is the processing material according to the first aspect, wherein the thin plate material has a through hole.
- the processing material according to a third aspect of the present invention is the processing material according to the second aspect, wherein the through hole is provided at least at the top.
- a processing material according to a fourth aspect of the present invention is a molded member that uses a processing material obtained by processing a single thin plate material that can be elastically deformed into a three-dimensional shape, and includes a valley portion and a raised portion on the thin plate material. Are formed along the first direction, and valleys and ridges are alternately connected along the second direction intersecting the first direction.
- a repeated second corrugated shape is formed, and in the first corrugated shape, the raised portion includes a pair of side portions that rise from the valley portion and a top portion that is continuous between the side portions, and the first of the proximal end portions of the pair of side portions.
- the top length along the first direction of the top is determined to be longer than the length of the opening along the direction, and the processing material is configured, and either the first direction or the second direction of the processing material has a three-dimensional shape. It is characterized in that it is determined in a direction intersecting with.
- a molding member according to the fourth aspect wherein the molding member is preliminarily determined on the vibration generating member side with respect to the molding member main body to be attached to the vibration generating member. And a partition member provided at a distance, and the thin plate member constituting the molded member main body has a through hole.
- the molded member according to the fifth aspect wherein the through hole is provided at least at the top.
- the first corrugated shape and the second corrugated shape are formed along the first direction and the second direction, respectively, and in the first corrugated shape, the raised portion rises from the valley portion.
- the apex length along the first direction of the apex portion is determined to be longer than the opening length along the first direction of the base end portion of the pair of side portions including the side portion and the apex portion connected between the side portions. .
- the present invention when processing such a raw material for processing into a desired product shape, for example, by processing the thin plate material in which the corrugated shape is formed by expanding and contracting the corrugated shape.
- the margin of extension along the first direction is significantly larger than that of a flat plate-shaped thin plate material. This is ensured by the fact that the apex length along the first direction of the apex portion is longer than the opening length along the first direction of the base end portions of the pair of side portions in the first corrugated shape. .
- this top length is not longer than the opening length, it will not be possible to secure a sufficient amount of extension when pressing the processing material, resulting in reduced workability of the product and generation of cracks and product shape during processing. May not be fully realized. According to the present invention, the possibility of such a problem can be prevented and the workability of the processing material can be significantly improved.
- the degree of workability along the second direction is sufficiently improved. This is ensured by the fact that the second corrugated shape is formed in the thin plate material along the second direction.
- the first waveform shape and the second waveform shape are formed by alternately repeating the valley portions and the raised portions. That is, in the first waveform shape and the second waveform shape, the presence of a flat plate portion is excluded between the shapes of each period composed of the valley portion and the raised portion. Assuming the existence of the flat plate portion, it is assumed that the flat plate portion generates a large-amplitude surface vibration or that the mechanical strength is weak due to the flat plate portion.
- the present invention prevents the occurrence of such problems, the quality of products manufactured using processing materials can be significantly improved.
- the workability of the processing material of the present invention is remarkably improved as compared with a flat plate-shaped thin plate material.
- the present invention does not limit the material of the thin plate material at all, but the characteristic action and effect of the present invention is as a thin plate material, for example, a material having relatively large ductility and malleability such as iron and stainless steel. It is obvious that this can be realized remarkably when an aluminum alloy having relatively low ductility and malleability is used.
- the working material of the present invention can realize these functions and effects with a configuration made of a single thin plate material, the configuration can be simplified and reduced in weight, and the cost can be greatly reduced. it can.
- the thin plate material constituting the processing material has a through hole.
- the processing material of the present invention has a through hole in itself.
- the processing material vibrates, when air passes through the through hole, energy is attenuated due to friction between the end surface constituting the through hole of the processing material and the air. For this reason, the energy of the sound wave which is vibration of air is converted into thermal energy, and the sound absorbing performance is exhibited.
- the frequency band in which the sound absorbing performance is exhibited is determined based on the dimensional shape such as the equivalent hole diameter, aperture ratio, and plate thickness of the through hole.
- the thin plate material is easy to move in the same phase because of the rib reinforcing effect by the raised portion and the valley portion.
- the acoustic radiation efficiency which is the energy conversion efficiency from vibration to sound of the processing material, is reduced by providing the through-hole in the thin plate material compared to the case without the through-hole. ing.
- the processing material of the present invention vibrates, it is possible to realize a sound absorbing effect on the sound radiated from the processing material.
- the processing material of the present invention since the through hole is provided at least at the top portion, the processing material of the present invention has the above-described effect described in relation to claim 1. In addition, the following sound absorbing action and vibration radiation sound reducing action are realized.
- the acoustic resonance mechanism is configured with an air layer having a thickness determined by the distance between the upper surface of the raised portion and the bottom surface of the valley, Sound absorption performance is realized. Moreover, the sound absorption performance by the energy attenuation by the friction mentioned above regarding the air which passes through the through-hole provided in the top part of the protruding part is also implement
- Such a synergistic sound absorbing effect can reduce the vibration and noise generated by the processing material itself by absorbing the sound after the generation.
- the molded member when the molded member is vibrated by vibration from the outside with respect to the molded member formed from the processing material, such vibration is caused by valleys and raised portions in the corrugated shape. Is converted into elastic deformation of the thin plate material. Thereby, a considerable part of the vibration applied from the outside is converted into thermal energy by elastic deformation of the thin plate material itself. Thereby, the vibration of the molding member due to the vibration received by the processing material is suppressed.
- the processing material when used for the vibration source and used as a molding member that should realize noise suppression, the molding member using the processing material is transmitted by vibration from the vibration source. Vibrate.
- the molded member vibrates, it is assumed that the product part vibrates so that the product parts on both sides of the ridge part which is a bent part of the product shape flutter. When such vibration is generated, a portion near the ridge portion of the product is likely to be cracked due to metal fatigue due to repeated bending.
- the processing material to be processed into a product is formed with corrugated shapes along the first direction and the second direction, respectively.
- the first direction corresponds to the ridge portion of the product. Therefore, the corrugated shape realizes the action of the rib against the vibration centered on the ridge. Thereby, the vibration of the product can be suppressed, the occurrence of cracks in the product can be prevented, and the quality of the product can be significantly improved.
- the working material of the present invention can achieve these functions and effects with a single thin plate material, the structure of the molded member can be simplified and lightened, and the cost can be greatly reduced. Can be planned.
- the molded member of the present invention is formed by processing a corrugated shape on a thin plate material, when the molded member has a bent shape, when one surface of the molded member is convex, the other surface is concave. At this time, the interval between the corrugated ridges widens on the convex shape side, and the interval between the corrugated ridges narrows on the other surface side.
- a member having fine irregularities or a member having a relatively soft surface property (hereinafter referred to as a base material) is brought into contact with one surface of the processing material of the present invention and the processing material is bent together with the base material.
- the processing material and the substrate mesh with each other and are fixed to each other. Will be. Therefore, mounting of the processing material to the base material can be realized without taking special measures such as an adhesive.
- the configuration of the molded part of the present invention can be simplified and downsized.
- the shape and structure of the molded member are determined by the shape when the processing material is processed into the molded member. Therefore, in the present invention, the shape and structure of the processing material in the stage before being processed into the molded member are arbitrary in the present invention. Thus, the present invention is applicable to a wide variety of processing materials as long as the shape and structure of the thin plate material when processed into a molded member satisfy the third aspect.
- the molding member includes a molding member main body mounted on the vibration generating member, and a partition member provided at a predetermined distance on the vibration generating member side with respect to the molding member main body.
- the thin plate material constituting the molded member has a through hole.
- the first sound absorbing structure is formed by the air layer formed between the molded member main body in which the through hole is formed and the partition member, and exhibits a sound absorbing action.
- An acoustic resonance mechanism is formed by a large number of through holes formed in the molded member main body and a back air layer between the molded member main body and the partition wall member, and the first sound absorbing structure is configured.
- the first sound absorption frequency band in which such a sound absorbing effect is exhibited is the back air determined by the dimension shape such as the equivalent hole diameter, aperture ratio, plate thickness and the like of the through hole and the distance between the molded member body and the partition member. Determined by factors such as layer thickness.
- the noise generated by the molded member itself when the molded member is attached to the vibration source can be reduced by absorbing the noise by the molded member itself after generation.
- the thin plate material is easy to move in the same phase because of the rib reinforcing effect by the raised portion and the valley portion.
- the acoustic radiation efficiency which is the energy conversion efficiency from vibration to sound of the processing material, can be reduced compared to the case where there is no gas flow part. confirmed. Thereby, even when the processing material of the present invention vibrates, the amplitude of the sound radiated from the processing material can be reduced.
- the vibration radiation noise reduction effect by providing the gas flow part in the thin plate material, if the surface vibration of the thin plate material partially differs in amplitude or / and phase, that is, if vibration distribution occurs on the surface of the processing material, vibration It is known that the effect of the radiation noise reduction action is reduced.
- the vibration distribution can be reduced and the effect of reducing vibration radiation sound is remarkable. can do. Therefore, the noise generated by the processing material itself can be reduced by the vibration radiation noise reduction effect.
- the molded member of the present invention has the above-described effects described in relation to claims 4 and 5.
- the following sound absorbing action and vibration radiation sound reducing action are realized.
- the ridges A second sound absorbing structure is formed, which is determined by the air layer thickness determined by the distance between the top surface of the part and the bottom of the valley part, and the dimensional shape such as the equivalent pore diameter, aperture ratio, and plate thickness of the gas flow part on the surface of the raised part.
- the sound absorbing action is exhibited in the vicinity of the acoustic resonance frequency band, which is the second sound absorbing frequency band determined by the above dimensions and the like.
- the first sound absorption frequency band and the second sound absorption frequency band are different from each other in size, shape, and the like described above that define these frequency bands.
- a conventional combination structure of a flat plate and an air layer, or a gentle concavo-convex shape that is, a concavo-convex structure in which the top length of the convex portion is shorter than the opening length of the concave portion, only sound absorption characteristics around a single frequency band are exhibited. Is done.
- the present invention as described above, even with a single molded member main body, the sound absorbing action is exhibited before and after different frequency bands, so that an extremely broad sound absorbing characteristic can be obtained with a simple configuration. Can be realized.
- the noise generated by the molded member itself when the molded member is attached to the vibration source can be reduced by absorbing the noise by the molded member itself after generation.
- vibration and noise generated by the processing material itself can be reduced by absorbing the sound after the generation.
- FIG. 2 is a cross-sectional view taken along section line X2-X2 in FIG. 1 is an enlarged front view of a metal cover 1.
- FIG. 4 is a cross-sectional view taken along section line X4-X4 in FIG. 3.
- FIG. 4 is a cross-sectional view taken along section line X5-X5 in FIG. 3.
- FIG. 4 is a cross-sectional view taken along section line X6-X6 in FIG.
- FIG. 2 is a simplified cross-sectional view seen from a section line X7-X7 in FIG. It is a perspective view explaining the characteristic of a present Example.
- FIG. 3 is a cross-sectional view for explaining the expansion and contraction action of the metal cover 1.
- FIG. 4 is a graph for explaining a vibration damping action of the metal cover 1.
- 4 is a graph showing a loss factor of the metal cover 1.
- 4 is a graph showing a temperature change of a loss coefficient of the metal cover 1.
- It is a perspective view of the metal plate 6 of Example 2 of this invention. 6 is a simplified cross-sectional view of a cover 1a of Example 2.
- FIG. 6 is a graph illustrating sound absorption characteristics of Example 2. It is a conceptual diagram which shows the structure of the investigation apparatus 21 based on Example 2.
- FIG. It is a graph explaining the investigation result by the investigation apparatus 21 regarding a sound absorption characteristic. It is a perspective view of a prior art.
- the present invention is implemented as an exhaust manifold cover or the like that is mounted in an exhaust manifold (hereinafter referred to as “exhaust manifold”) of an internal combustion engine so that vibrations and noises are not radiated from the exhaust manifold. be able to.
- exhaust manifold an exhaust manifold of an internal combustion engine
- Embodiment 1 of the present invention will be described with reference to FIGS.
- FIG. 1 is a front view showing a state in which the metal cover 1 of the present embodiment is mounted on the exhaust manifold 3
- FIG. 2 is a cross-sectional view taken along the section line X2-X2 of FIG. 1
- FIG. 4 is an enlarged front view of FIG. 1
- FIG. 4 is a cross-sectional view taken along section line X4-X4 of FIG. 3
- FIG. 5 is a cross-sectional view taken along section line X5-X5 of FIG.
- FIG. 7 is a cross-sectional view taken along the cutting plane line X6-X6 of FIG. 3
- FIG. 7 is a simplified cross-sectional view taken along the cutting plane line X7-X7 of FIG. 1, and FIG. FIG.
- FIG. 9 is a sectional view for explaining the operation of the present embodiment
- FIG. 10 is a graph for explaining the vibration damping performance of the present embodiment
- FIG. 11 is a graph of the present embodiment and the existing technology.
- FIG. 12 is a graph showing the damping performance
- FIG. 12 is a graph showing the temperature change of the loss coefficient.
- the exhaust manifold 3 of an internal combustion engine such as an automobile engine 2 passes through the combustion chamber of the internal combustion engine, for example, combustion exhaust gas pulsating at a frequency of several thousand cycles per minute at a high temperature of 600 to 700 ° C.
- a certain exhaust manifold 3 itself becomes a heat source that generates high-temperature heat radiation, and a vibration source that dissipates noise caused by the explosion of fuel in the engine 2 and the movement of combustion exhaust gas in the exhaust manifold 3 to the outside. It becomes.
- a metal cover 1 that is a molding member having a configuration described later is installed in a manner covering the exhaust manifold 3.
- the metal cover 1 of the present embodiment is composed of a metal plate 4 made of an aluminum alloy having a specific gravity of about 2.7, which is a thin plate material having a plate thickness of 0.3 mm. 2 and FIG. 7, it is formed in a three-dimensional shape along the appearance shape of the exhaust manifold 3.
- the metal cover 1 includes a side wall T1 and a top T2 that connects the entire periphery of the end of the side wall T1.
- the side wall T1 and the top part T2 are connected at an obtuse angle ⁇ .
- the metal plate 4 is not limited in its kind as long as it is a material that can be elastically deformed.
- Aluminum foil or aluminum alloy foil, aluminum or its alloy, stainless steel, engineering A thin plate material made of synthetic resin such as plastic is included as a modified example.
- a thin plate material made of synthetic resin such as aluminum, an alloy thereof, or engineering plastic is preferable.
- the metal plate 4 used in the cover 1 of the present embodiment is formed from a single aluminum alloy thin plate.
- the metal plate 4 has a plurality of first corrugated shapes in which the raised portions 7 and the valley portions 8 are alternately connected to each other along the first direction A1.
- the ridge 7a and the valley 8a are connected to each other along the second direction A2 that is the direction intersecting the first direction A1, and preferably the direction orthogonal to the first direction A1, and the second waveform is the same.
- a corrugated shape 9a is formed.
- the raised portions 7 are alternately arranged with the first raised portions 10 and the second raised portions 11 rising from the valley portions 8 along the longitudinal direction thereof.
- the valley 8 has flat portions 12 and recesses 13 arranged alternately.
- the first upright portion 10 includes a pair of side walls 14 and 15 that rise from the valley portion 8 in a substantially trapezoidal shape, and a relatively flat top portion 18 that is formed by connecting the tips of the side walls 14 and 15 to each other. A one-cycle shape is formed.
- the first upright portion 10 is bent inwardly, and the apex length L2 along the first direction A1 of the apex portion 18 is longer than the opening length L10 along the first direction A1 of the base end portion of the first upright portion 10. It is determined to be.
- the second upright portion 11 is formed by crushing the first upright portion 10 to a predetermined extent in the width direction, and a pair of side walls 19, 20 rising from the flat portion 12, and the side walls 19, 20. The distal ends are connected to each other, and a concave recess 23 is formed on the lower side of FIG.
- Each of the second upright portions 11 and the concave portions 13 is intermittently connected along a second direction A2 that is a direction substantially orthogonal to the first direction A1 that is a direction in which the plurality of waveform shapes 9 extend. Formed as follows.
- the 2nd standing part 11 is curving inside, and the top part length L11 along the 1st direction A1 of the recessed part 13 rather than the opening part length L11 along the 1st direction A1 of the base end part of the 2nd standing part 11 is. Is determined to be long.
- the side walls 14 and 15 and the side walls 19 and 20 have a corrugated shape 9 along at least one of the first direction A1 and the second direction A2, and the metal plate 4 is folded over the metal plate 4 itself. A folded stack 45 is formed.
- the length L1 of one cycle of the waveform shape 9 along the first direction A1 the first upright part 10
- the length L2 of the top portion 18 and the length L3 of the concave portion 23 of the second upright portion 11 are selected to be 11 mm, 7 mm, and 5 mm, respectively. Accordingly, the opening length L10 is selected to be smaller than 7 mm, and the opening length L11 is selected to be smaller than 5 mm.
- the metal cover 1 has such a shape, and is formed by pressing the metal plate 4 into a three-dimensional shape along the outer shape of the exhaust manifold 3.
- the metal cover 1 of the present embodiment Since the metal cover 1 of the present embodiment is formed in a three-dimensional shape that conforms to the three-dimensional appearance of the exhaust manifold 3 as described above, the metal cover 1 has a bent metal plate 4 as shown in FIG. One or a plurality of ridge line equivalent parts 30 that are parts and ridges are formed.
- the metal plate 4 is arranged such that the first direction A1 which is the longitudinal direction of the corrugated shape 9 is a direction intersecting a main ridge line equivalent portion 30 described later among the plurality of ridge line equivalent portions 30. 5 is pressed into a three-dimensional shape.
- the main ridge line equivalent portion 30 is a bent portion where a relatively large curvature characterizing the overall shape of the metal cover 1 continues. That is, among the various large and small bent portions formed on the metal cover 1, the bent portion extending over a relatively long length that substantially determines the external shape of the metal cover 1 is indicated.
- the metal cover 1 When the metal cover 1 is attached to the exhaust manifold 3, the metal cover 1 is also vibrated by transmission of vibration from the exhaust manifold 3. When the metal cover 1 vibrates due to this vibration, the metal cover 1 vibrates so that the portions of the metal cover 1 on both sides of the main ridge line corresponding portion 30 flutter. If such vibration is left unattended, a portion near the ridge line corresponding portion 30 of the metal cover 1 is subject to metal fatigue due to repeated bending, and cracks are likely to occur.
- the second upright portion 11 is also capable of realizing a rib function and suppressing vibration.
- the flange 28 is formed on at least a part of the outer peripheral portion of the metal cover 1.
- the metal cover 1 is formed by forming the metal plate 4 in a three-dimensional shape, and the plurality of corrugated shapes 9 formed on the metal plate 4 are raised.
- a portion 7 and a valley portion 8 are formed continuously along the first direction A1, and the height of each raised portion 7 is periodically changed along the longitudinal direction, that is, the first direction A1.
- the first direction A1 is set in a direction orthogonal to the main ridge line corresponding portion 30 of the metal cover 1 constituting a three-dimensional shape.
- the corrugated shape 9 realizes the action of the rib against the vibrations on both sides of the main ridge line equivalent part 30.
- the vibration from the exhaust manifold 3 prevents the metal cover 1 from vibrating such that the portions of the metal cover 1 on both sides of the main ridge line corresponding portion 30 flutter, and the metal cover 1 This prevents a situation in which the portion near the ridge line corresponding portion 30 is prone to metal fatigue due to repeated bending and is likely to generate cracks.
- the vibration of the metal cover 1 of this embodiment can be suppressed, the occurrence of cracks in the metal cover 1 can be prevented, and the quality of the metal cover 1 can be significantly improved.
- the metal cover 1 is a direction in which the first direction A1 having a plurality of corrugated shapes formed on the metal cover 1 intersects the bent portion 30 of the product shape of the metal cover 1, preferably, Since it is determined in the orthogonal direction, the wave shape realizes the action of the rib against the vibration centered on the bent portion 30. Thereby, the vibration of the metal cover 1 can be suppressed, the occurrence of cracks in the metal cover 1 can be prevented, and the quality of the metal cover 1 can be significantly improved.
- FIG. 9 is a simplified cross-sectional view showing the operation of the metal cover 1 of the present embodiment.
- the laminated portion 45 is formed on the metal plate 4 that is an elastically deformable material having the corrugated shape 9 formed on substantially the entire surface.
- the width of the recess 46 at the extension portion becomes a width L5 at the time of extension larger than the width L4, and the width of the recess 46 at the compression portion. Stretching deformation is generated in each part over the entire surface of the metal cover 1 so that the width becomes a compression width L6 smaller than the width L4.
- the vibration applied from the outside due to the expansion / contraction deformation of each part of the corrugated shape 9 is converted into thermal energy by the elastic deformation of the metal plate 4 itself. Thereby, the vibration of the metal cover 1 can be suppressed.
- the width of the recess 46 in the extended portion 7 is a width L5 when extended, which is larger than the width L4, compared to the width L4 of the recess 46 of the standard raised portion 7 where the raised portion 7 is not deformed.
- the width of the recess 46 is a compression width L6 smaller than the width L4.
- the inventors of the present invention follow the bending of the waveform shape 9.
- the length of one cycle (hereinafter referred to as the perimeter) was measured.
- the peripheral length L0 is about 17 mm, and an extension allowance of about 55% can be realized with respect to the length L1 of one cycle of the waveform shape 9 (11 mm in this example).
- an aluminum material is used as the metal plate 4, but the aluminum material has lower ductility and malleability compared to iron materials and stainless steel, and cracks etc. when performing press working, particularly deep drawing. The problem may occur.
- the metal plate 4 is equivalent to having about 55% ductility and malleability, press working including deep drawing is remarkably facilitated. Thereby, light metals, such as aluminum, can be used as a material of the metal cover 1, and weight reduction of the metal cover 1 can be achieved. Moreover, workability is also greatly improved.
- the laminated portion 45 is expanded and contracted as shown in FIG.
- the extension allowance in the processing of the plate 4 is significantly larger than that of a flat metal plate. Thereby, processing becomes much easier as compared with a flat metal plate. This effect is remarkably realized when an aluminum alloy having relatively low ductility is used as the metal plate, for example, iron or stainless steel.
- the plate of the metal plate 4 constituting the metal cover 1 is achieved in order to achieve this.
- the necessity of increasing the rigidity of the metal cover 1 or increasing the support location for the exhaust manifold 2 of the metal cover 1 by increasing the thickness or adding a reinforcing member is eliminated. This increases the possibility of cracking in the vicinity of the support location due to the increase in the weight of the metal cover 1 assumed when the rigidity of the metal cover 1 is increased, and increases the support location of the metal cover 1. It is possible to prevent the occurrence of cracks due to thermal strain assumed when In these respects, the reliability of the metal cover 1 is significantly improved.
- FIG. 10 is a graph for explaining the vibration control action of the metal cover 1.
- the vibration damping action of the metal cover 1 will be described with reference to FIG.
- the present inventor applied vibration to the steel plate, stainless steel plate, FRP plate, sandwich steel plate, and the metal cover 1 of the present embodiment. The damping coefficient of vibration was measured. The result is shown in the graph of FIG.
- the vibration attenuation coefficient of the metal cover 1 of the present embodiment shown by the region P in FIG. 10 is larger than that of the steel plate and the stainless steel plate, and smaller than that of the FRP (fiber reinforced plastic) plate and the sandwich steel plate. Confirmed to belong to. Therefore, although the damping coefficient is smaller than that of a sandwich steel plate having a laminated structure of different materials or FRP containing inorganic fibers therein, it is larger than a steel plate or stainless steel plate that is often used as a material for covers of internal combustion engines. It has a vibration damping coefficient, and it has been confirmed that the vibration control performance is significantly improved over the prior art.
- FIG. 11 shows a sandwich steel plate using a single-layer aluminum-plated steel plate having a thickness of 0.5 mm, a single-layer aluminum plate having a thickness of 0.5 mm, and a metal, in order to confirm the vibration damping performance of the metal cover 1 of this embodiment. It is a graph which shows the result of having measured each loss factor (eta) of the laminated aluminum board of the sheet-made cover 1 and the plate
- the vibration control performance of the metal cover 1 of the present embodiment is lower than the sandwich steel plate and 0.5 mm thick aluminum plate, but higher than the laminated aluminum plate.
- FIG. 12 is a graph showing the results of measuring the temperature change of the loss coefficient ⁇ related to the vibration of various materials in relation to the metal cover 1 of this example.
- the measurement temperature range is between room temperature and about 250 ° C.
- the measurement result of the metal cover 1 is indicated by a curve g1
- the measurement result of an aluminum-plated steel plate having a thickness of 0.5 mm is indicated by a curve g2.
- the loss factor of the metal cover 1 of this embodiment is lower than the loss factor of the aluminum-plated steel sheet in the temperature range below about 100 ° C., but in the temperature range exceeding about 100 ° C. It was confirmed that the loss coefficient of the aluminum-plated steel sheet was significantly improved.
- the metal cover 1 when used for a vibration source that generates heat, such as an automobile engine, for example, it has been confirmed that it exhibits good vibration damping properties when the engine is in operation.
- the corrugated shape 9 formed on the metal plates 4 and 5 is not limited to the shape of the above embodiment, and even when an arbitrary corrugated shape is formed, It is clear that the waveform-shaped expansion / contraction operation accompanying the vibration can be realized, and the vibration control action by this expansion / contraction operation can be realized.
- the waveform shapes 9, 9a are formed continuously along the first direction A1 and the second direction A2, respectively. Therefore, regarding the metal cover 1 formed from the metal plates 4 and 5, when the cover 1 generates vibration due to external vibration, such vibration is caused by the valley portions 8 and 8a in the waveform shapes 9 and 9a and It is converted into elastic deformation of the metal plate 4 in the raised portions 7 and 7a. Thereby, a considerable part of the vibration applied from the outside is converted into thermal energy by the elastic deformation of the metal plate 4 itself. Thereby, the vibration of the cover 1 by the vibration which the metal plate 4 receives can be suppressed.
- the product formed from the processing material vibrates by transmission of vibration from the vibration source.
- the product vibrates, it vibrates so that the product parts on both sides of the product shape flutter around the bent part of the product shape.
- vibration is generated, a portion near the bent portion of the product is subject to metal fatigue due to repeated bending, and cracks are likely to occur.
- the processing material to be processed into a product is formed with corrugated shapes along the first direction and the second direction, respectively.
- the first direction corresponds to the bent portion of the product.
- the corrugated shapes 9 and 9a are expanded and contracted to expand and contract the corrugated shapes 9 and 9a.
- the extension allowance in processing of the metal plate 4 on which the metal plate 4 is formed becomes significantly larger than that of the flat plate-shaped metal plate 4.
- workability is remarkably improved compared with a flat metal plate.
- This function and effect is remarkably realized when, for example, an aluminum alloy having relatively low ductility and malleability is used as the metal plate 4 rather than a material having relatively high ductility and malleability such as iron and stainless steel.
- the cover 1 is formed by processing the corrugated shapes 9 and 9a on the metal plate 4, so that when the cover 1 has a bent shape, one surface of the cover 1 has a convex shape.
- the other surface has a concave shape.
- the interval between the raised portions 7 and 7a of the waveform shapes 9 and 9a is widened on the convex shape side, and the interval between the raised portions 7 and 7a of the waveform shapes 9 and 9a is narrowed on the other surface side.
- a base material a member having a relatively soft surface property
- the mounting of the metal plate 4 on the base material can be realized without taking special measures such as an adhesive. Also in this respect, the structure of the cover 1 of the present embodiment can be simplified and downsized.
- the shape and structure of the cover 1 are determined by the shape when the metal plate 4 is processed into the cover 1. Therefore, in this embodiment, the shape and structure of the metal plate 4 at the stage before being processed into the cover 1 are arbitrary. As a result, this embodiment is applicable to a wide variety of processing materials as long as the shape and structure of the metal plate 4 when processed into the cover 1 satisfy the conditions defined in this embodiment. is there.
- FIG. 13 is a perspective view of the metal plate 6 that is the material of the metal cover 1a of this embodiment
- FIG. 14 is a simplified cross-sectional view of the metal cover 1a that is a molding member of this embodiment
- FIG. FIG. 16 is a conceptual diagram illustrating the configuration of the investigation device 21 based on the present embodiment
- FIG. 17 is a graph illustrating the investigation result by the investigation device 21 regarding the sound absorption characteristics. is there.
- the metal cover 1a of the present embodiment is similar to that of the first embodiment, and corresponding parts are denoted by the same reference numerals.
- One of the features of the present embodiment is that a large number of through holes 22 are formed in the metal plate 6 that is a thin plate material made of a flat plate aluminum plate having a plate thickness t0 constituting the cover 1a.
- the through hole 22 is formed so that air can move in the thickness direction (vertical direction in FIG. 13) of the metal plate 6.
- the through-hole 22 has a cylindrical cross-sectional shape shown in FIG. 13 as an example, but is not limited thereto, and may have a rectangular slit shape or other irregular shapes.
- the plate thickness t0 is selected to be 0.15 mm
- the opening diameter D1 of the through-hole 22 is such that the sound input to the metal cover 1a passes through the through-hole 22 as an air dense wave, and the peripheral portion of the through-hole 22 It has a great influence on the conversion action of the vibration energy of the air due to the friction between the air and the heat into the heat energy and the attenuation action of the energy due to the pressure loss of the air flow.
- the opening diameter D1 capable of realizing the energy attenuating action due to the pressure loss in the air passing through the through hole 22 is preferably 3 mm or less. This is because, when the opening diameter D1 is larger than 3 mm, the pressure loss during the passage of air is greatly reduced, and it is confirmed that the threshold value regarding the normal incident sound absorption coefficient with respect to the metal plate 6 is significantly lower than 0.3. . Further, it has been confirmed that if the opening diameter D1 of the through hole 22 is 1 mm or less, a viscous action can be reliably generated in the air flow passing through the through hole 22.
- the metal plate 6 having a large number of such through holes 22 is described above along the first direction A1 and the second direction A2.
- Each of these corrugations is applied.
- the processing material 24 shown in FIG. 14 obtained by performing such corrugation processing, and a back plate 25 which is a partition member provided by separating the air layer 26 at a predetermined distance L21 from the processing material 24 are included.
- the metal cover 1a which is a molding member of the present embodiment is configured.
- FIG. 15 is a graph showing the frequency vs. normal incidence sound absorption coefficient of the measurement result.
- Curves g10, g11, g12, and g13 show changes in the normal incident sound absorption coefficient when the distance L21 is 0 mm, 2 mm, 4 mm, and 8 mm, respectively.
- the normal incidence sound absorption coefficient of the present embodiment has two peak frequency bands, a first frequency band f1 (1 to 2 kHz) and a second frequency band f2 (3 to 4 kHz).
- the first frequency band f1 which is the lower peak frequency band is resonance by the air layer determined by the distance L22 between the raised portion 7 and the back plate 25 and the through hole 22 formed in the raised portion 7 portion.
- the second frequency band which is the higher peak frequency band, is a frequency band resulting from the resonance frequency of the air layer determined by the distance L23 between the raised portion 7 and the valley portion 8 and the through hole 22 formed in the raised portion 7. It is.
- the inventor of the present invention investigated the metal plate 6 having the configuration shown in FIG. 13 with the investigation device 21 shown in FIG. 16 with respect to the metal cover 1a of this example.
- the investigation device 21 includes a vibration exciter 33 and a mounting jig 34.
- the metal plate 6 is attached to the vibrator 33 with the mounting jig 34, and the metal cover is covered with the sound pressure detecting means 35 such as a microphone installed in the vicinity of the metal plate 6 on the opposite side of the vibrator 33.
- the sound pressure level of the sound from 1a was measured.
- the measurement results are shown in the graph of FIG.
- a curve g15 is a case of the metal cover 1a of the present embodiment having a large number of through holes 22, and a curve g16 is a case of the metal cover 1 in which the through holes 22 are not formed.
- the metal cover 1a of the present example having the through hole 22 is at a level reduced from the curve g16 in each of the frequency bands around 630 Hz, around 1250 Hz, and 2500 Hz. It was confirmed that the noise reduction effect by the through-hole 22 was seen.
- Such a metal cover 1a of the present embodiment can realize the following sound absorbing action and vibration radiation sound reducing action.
- the metal cover 1a of the present embodiment is provided with a through hole 22 in itself. Therefore, when the metal cover 1a vibrates, when the air passes through the through hole 22 in the direction of the arrow e1, energy of friction is generated between the end surface 32 constituting the through hole 22 of the processing material 24 and the air. Attenuation occurs.
- the sound absorbing performance due to such energy attenuation is exhibited by converting sound wave energy, which is vibration of air, into thermal energy.
- the sound absorption performance in the lower peak frequency band f1 is determined by the air layer determined by the distance L22 between the raised portion 7 and the back plate 25 and the air determined by the distance L21 between the valley portion 8 and the back plate 25. Due to resonance by layers.
- the resonance is caused by an air layer having a thickness L23 between the upper surface of the raised portions 7 and the bottom surface of the valley 8. Sound absorption performance in the vicinity of the acoustic resonance frequency band.
- vibration and noise generated by the processing material 24 itself can be reduced by absorbing the sound after the generation.
- the metal plate 6 is easy to move in the same phase due to the rib reinforcing effect by the raised portion 7 and the valley portion 8.
- the acoustic radiation efficiency which is the energy conversion efficiency from vibration to sound of the processing material 24
- the amplitude of sound radiated from the processing material 24 can be reduced.
- the vibration radiation noise reduction effect by providing the through hole 22 in the metal plate 6, when the surface vibration of the metal plate 6 is partially different in amplitude or / and phase, that is, vibration distribution is generated on the surface of the processing material 24.
- the effect of the vibration radiation sound reducing action is reduced.
- the vibration distribution can be reduced and the vibration radiated sound can be reduced. The effect can be made remarkable. Therefore, the noise generated by the processing material 24 itself can be reduced by this vibration radiation sound reduction effect.
- the cover 1a when the cover 1a generates vibration due to external vibration with respect to the metal cover 1a formed from the processing material 24, such vibration is caused by the trough 8 in the waveform shape 9 and It is converted into elastic deformation of the metal plate 6 in the raised portion 7. Thereby, a considerable part of the vibration applied from the outside is converted into thermal energy by the elastic deformation of the metal plate 6 itself. Thereby, the vibration of the cover 1a by the vibration which the raw material 24 for processing receives can be suppressed.
- the aperture diameter D1, the aperture ratio, the plate thickness t0, and the distance between the raised portion 7 and the back plate 25 or the valley portion 8 are appropriately adjusted to match the frequency band to be reduced. It is possible to adjust so as to obtain an effect of reducing vibration radiation sound.
- the material of the metal plate 6 constituting the metal cover 1a of the present embodiment and the hole shape of the through hole 22 are not limited to the above embodiments, and the present invention can be used when other materials are used. include.
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Abstract
Description
3 エキマニ
4、5、6 金属板
7、7a 隆起部
8、8a 谷部
9、9a、9b 波形形状
12 平坦部
13 凹部
18 頂部
21 調査装置
22 貫通孔
23 凹部
24 加工用素材
26 空気層
32 端面
45 積層部
46 凹所
A1 第1方向
A2 第2方向
D1 開口径
板や板厚0.5mmのアルミ板よりも低いものの、前記積層アルミ板よりも高いことが確認された。
Claims (6)
- 弾性変形可能な単一の薄板材に、谷部と隆起部とが相互に連なって交互に繰り返される第1波形形状が第1方向に沿って形成され、該第1方向と交差する第2方向に沿って、谷部と隆起部とが相互に連なって交互に繰り返される第2波形形状が形成され、
該第1波形形状において、該隆起部は該谷部から立ち上がる一対の側部と、該側部間に連なる頂部とを含み、一対の側部の基端部の第1方向に沿う開口部長さよりも、頂部の第1方向に沿う頂部長さが長く定められている、
ことを特徴とする加工用素材。 - 前記薄板材は、貫通孔を有する、
ことを特徴とする請求項1記載の加工用素材。 - 前記貫通孔は、少なくとも前記頂部に設けられている
ことを特徴とする請求項2記載の加工用素材。 - 弾性変形可能な単一の薄板材を立体形状に加工して得られる加工用素材を用いる成型部材であって、
該薄板材に、谷部と隆起部とが相互に連なって交互に繰り返される第1波形形状が第1方向に沿って形成され、該第1方向と交差する第2方向に沿って、谷部と隆起部とが相互に連なって交互に繰り返される第2波形形状が形成され、
該第1波形形状において、該隆起部は該谷部から立ち上がる一対の側部と、該側部間に連なる頂部とを含み、一対の側部の基端部の第1方向に沿う開口部長さよりも、頂部の第1方向に沿う頂部長さが長く定められて加工用素材が構成され、
該加工用素材の第1方向及び第2方向のいずれかが該立体形状の稜部と交差する方向に定められている、
ことを特徴とする成型部材。 - 前記成型部材は、振動発生部材に対して装着される成型部材本体と、該成型部材本体よりも振動発生部材側に予め定める距離を隔てて設けられる隔壁部材とを含み、
該成型部材本体を構成する前記薄板材は貫通孔を有する、
ことを特徴とする請求項4記載の成型部材。 - 前記貫通孔は、少なくとも前記頂部に設けられている
ことを特徴とする請求項5記載の成型部材。
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EP09736005.1A EP2302185B1 (en) | 2008-04-21 | 2009-04-17 | Material for processing and molding member using material for processing |
KR1020107025701A KR101057422B1 (ko) | 2008-04-21 | 2009-04-17 | 가공용 소재 및 그것을 이용한 성형 부재 |
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Also Published As
Publication number | Publication date |
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JP4601707B2 (ja) | 2010-12-22 |
EP2302185A4 (en) | 2014-07-09 |
CN102007281A (zh) | 2011-04-06 |
MY177430A (en) | 2020-09-15 |
CN102007281B (zh) | 2012-10-10 |
KR101057422B1 (ko) | 2011-08-19 |
EP2302185B1 (en) | 2016-07-20 |
EP2302185A1 (en) | 2011-03-30 |
US20110094824A1 (en) | 2011-04-28 |
KR20100133017A (ko) | 2010-12-20 |
US8042648B2 (en) | 2011-10-25 |
JP2009281379A (ja) | 2009-12-03 |
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