Damping material

There is provided a vibration damping material capable of exhibiting excellent vibration damping performance and of reducing its own weight while having high rigidity. The vibration damping material of the present invention used so as to be installed on a panel of a vehicle includes a viscoelastic layer and a constraining layer provided on one surface of the viscoelastic layer, wherein a relationship between a strain εa and a strain εb is 0<εa/εb<1, the strain εa being a strain on a surface of the constraining layer on the opposite side to the viscoelastic layer, and the strain εb being a strain on a surface of the constraining layer on a side in contact with the viscoelastic layer.

CROSS-REFERENCE TO RELATED APPLICATIONS

The present application is a national phase entry under 35 U.S.C. § 371 of International Application No. PCT/JP2019/002329 filed Jan. 24, 2019, published in Japanese, which claims priority from Japanese Patent Application No. 2018-241305 filed Dec. 25, 2018, all of which are incorporated herein by reference.

TECHNICAL FIELD

The present invention relates to a vibration damping material, and more particularly, relates to a vibration damping material for vehicles.

BACKGROUND ART

Metal plates such as thin steel plates and aluminum plates are generally used as structural members in vehicles, electric appliances and the like. In order to reduce the vibration of a vehicle or electric appliance, it is possible to adhere a viscoelastic material on a surface of the metal plate to impart vibration attenuation performance (vibration damping performance) to a structural member. Such vibration damping structures are roughly classified into two types: a structure called a non-constraint type in which a viscoelastic material is simply adhered to one surface or both surfaces of a metal plate, and a structure called a “constraint type” in which a constraining plate such as a metal plate or a high polymeric material is further adhered to the surface of the viscoelastic material on the opposite side of the metal plate (Non-Patent Document 1).

In addition, as a constraint type vibration damping structure using a constraining plate made of a polymeric material, Patent Document 1 discloses a carbon fiber reinforced plastic molded body, including: a first carbon fiber reinforced plastic layer; a second carbon fiber reinforced plastic layer laminated on one surface of the first carbon fiber reinforced plastic layer; and a first vibration damping layer arranged between the first carbon fiber reinforced plastic layer and the second carbon fiber reinforced plastic layer, wherein: the thickness of the second carbon fiber reinforced plastic layer is thinner than the thickness of the first carbon fiber reinforced plastic layer; and the first vibration damping layer is provided with gaps extending in a direction intersecting the orientation direction of the carbon fibers contained in the second carbon fiber reinforced plastic layer. Patent Document 1 describes that: with this configuration such that the first carbon fiber reinforced plastic is made relatively thick and the second carbon fiber reinforced plastic layer is made relatively thin, the first vibration damping layer is arranged on the outer surface side with respect to the center of the carbon fiber reinforced plastic molded body; this prevents decrease in flexural modulus of the carbon fiber reinforced plastic molded body; furthermore, since the predetermined gaps are provided, the gaps relieve the stress caused by the expansion of the carbon fiber reinforced plastic layer and the contraction of the vibration damping layer; and as a result, even if the second carbon fiber reinforced plastic layer is configured to be thin, the surface of the second carbon fiber reinforced plastic layer is prevented from deformation generated when the carbon fiber reinforced plastic molded body is molded.

A typical structure of a vehicle has an engine compartment provided at the front, a trunk compartment provided at the rear, and a passenger compartment provided in the middle thereof. The passenger compartment is provided with seats such as a driver seat, a front passenger seat, and a rear seat. In addition, the passenger compartment has a dash insulator, a floor carpet, a floor spacer, a trunk trim, and a trunk floor installed so that they cover the outside of the vehicle interior. These components are formed in an uneven shape according to shapes of vehicle bodies or designs of components. Furthermore, the exterior under a vehicle body has a front fender liner, a rear fender liner, and an undercover that is formed in an uneven shape for controlling the air flow, installed thereon. For many of these components, a thermoplastic resin is used as a material, and each of the materials is heated and press-molded by a die having the shape of the component to be finished into an uneven-shaped component having a plurality of portions with different thicknesses.

As a recent trend of vehicle development, the quietness in the interior of a vehicle is emphasized. Noise transmitted to the interior of a vehicle includes noise from the windows, noise from the tires, noise from under the vehicle body, noise from engine sounds, and noise from motor sounds. Noise generated from a vehicle is transmitted to the vehicle interior via the vibration of air or via the vibration of an object. The noise transmitted mainly via the vibration of an object is blocked by the vibration damping structure described above. Accordingly, it is possible to exhibit sufficient acoustic performance against the noise generated in the vehicle. On the other hand, it is also important to reduce fuel consumption, and it is also required to reduce weight of interior and exterior components of vehicles.

REFERENCE DOCUMENT LIST

Patent Document

Patent Document 1: JP 2012-162062 A

SUMMARY OF THE INVENTION

Problem to be Solved by the Invention

As described in Non-Patent Document 1, in non-constraint type vibration damping structure, the thicker the viscoelastic material, the higher the vibration damping performance Therefore, in order to obtain desired vibration damping performance, a problem is that the thickness of the viscoelastic material is too large to be practical. On the other hand, in a constraint type vibration damping structure, the vibration damping performance is maximized when the metal plate used as the constraining plate and the metal plate of the substrate have the same thickness. Therefore, in order to obtain desired vibration damping performance, another problem is that the weight of the constraining plate is large even though the rigidity is high, but weight reduction is difficult. In addition, when the carbon fiber reinforced plastic molded body described in Patent Document 1 is installed on a vehicle panel to be used for vibration damping of the panel, the molded body further need to be provided with a vibration damping layer (viscoelastic layer) also between the carbon fiber reinforced plastic molded body and the panel. Therefore, a plurality of carbon fiber reinforced plastic (CFRP) layers and a plurality of viscoelastic layers are laminated on the panel, and there also is a problem of difficulty in weight reduction.

Therefore, an object of the present invention is to provide a vibration damping material capable of exhibiting excellent vibration damping performance and reducing its own weight.

Means for Solving the Problem

In order to achieve the object, the present invention provides a vibration damping material, including a viscoelastic layer and a constraining layer provided on one surface of the viscoelastic layer, wherein a relationship between a strain εa and a strain εb is 0<εa/εb<1, the strain εa being a strain on a surface of the constraining layer on the opposite side to the viscoelastic layer, and the strain εb being a strain on a surface of the constraining layer on a side in contact with the viscoelastic layer.

The constraining layer may have a multilayer structure including at least a core layer in which tubular cells are arranged in a plurality of rows. The tubular cell may have a polygonal tubular shape such as a substantially quadrangular tubular shape or a substantially hexagonal tubular shape, or may have a curved tubular shape such as a substantially circular tubular shape or a substantially elliptical tubular shape. It is preferable that each of the cells in the core layer have a closed surface at one end and an open end at another end; the open ends of the cells each allow an internal space of the cell to be in communication with an outside; and the open ends of the cells be arranged on both sides of the core layer such that rows of the open ends of the cells are in every other row. The open end, the one-side closed surface, and the other-side closed surface may have a polygonal shape such as a substantially quadrangular shape or a substantially hexagonal shape, or may have a curved shape such as a substantially circular shape or a substantially elliptical shape, according to the shape of the cell. The constraining layer may further include film layers provided on both sides of the core layer. Each of the film layers may have a plurality of apertures penetrating the film layer.

The viscoelastic layer may have a thickness of 0.5 to 2 mm. The constraining layer may be formed to match a panel shape so that a thickness of the viscoelastic layer is uniform. That is, the constraining layer is not limited to a flat shape, and may have a shape such as a curved shape or a corrugated shape corresponding to the shape of the panel. The relationship between the strain εa and the strain εb is preferably 0.2<εa/εb<0.7.

The viscoelastic layer may be partially provided on a surface of the constraining layer on the side in contact with the viscoelastic layer. In addition, the constraining layer may have a multilayer structure including a fiber layer on the constraining layer on the side in contact with the viscoelastic layer. The constraining layer may have a multilayer structure including a metal layer on the constraining layer on a side opposite to the side in contact with the viscoelastic layer.

Effects of the Invention

The vibration damping material of the present invention has a configuration such that the strain ratio εa/εb satisfies the expression 0<εa/εb<1, where: the strain εa is the strain on the surface of the constraining layer, which is provided on the viscoelastic layer, on the opposite side of the viscoelastic layer; and the strain εb is the strain on the surface thereof on the side in contact with the viscoelastic layer. This moves the bending central axis of the constraining layer in the direction opposite to the viscoelastic layer with respect to the center position of the thickness of the constraining layer. This configuration allows the vibration damping material to improve in the vibration damping performance Therefore, the constraining layer configured with a resin material, instead of a thick metal plate, can exhibit excellent vibration damping performance, and can reduce its own weight while having high rigidity.

In particular, a configuration, such as one in which the constraining layer has a multilayer structure including at least a core layer in which tubular cells are arranged in a plurality of rows, can exhibit excellent vibration damping performance, and enables weight reduction while having high rigidity.

MODE FOR CARRYING OUT THE INVENTION

An embodiment of a vibration damping material according to the present invention is described below with reference to the accompanying drawings. Note that, although respective embodiments describe cases in each of which a vibration damping material is used for a vehicle, the present invention is not limited to these, and can be used for electric appliances and the like. In addition, the drawings are not intended to be drawn to scale unless otherwise specified.

First Embodiment

As shown inFIG.1A, a vibration damping material of a first embodiment includes a constraining layer100and a viscoelastic layer200provided on one surface thereof. Note that the vibration damping material of the present invention is used so that the viscoelastic layer200side is located on a noise source side, that is, the vibration damping material of the present invention is provided on the vehicle interior side such that the viscoelastic layer200is installed on the side of a panel300of the vehicle body.

In the constraining layer100, a ratio εa/εb satisfies an expression 0<εa/εb<1, where: εa is the strain of a surface100aon the side opposite to the viscoelastic layer200; and εb is the strain of a surface100bon the side in contact with the viscoelastic layer200. The configuration, such that the constraining layer100has a strain ratio εa/εb that satisfies the expression, moves the bending central axis NA of the constraining layer100in the direction opposite to the viscoelastic layer200with respect to the center position of the thickness of the constraining layer100, as shown inFIG.1B, when the vibration damping material installed on the panel300is bent (that is, when subjected to vibration). This allows the vibration damping material to have improved vibration damping performance.

The constraining layer100is not particularly limited if the strain ratio εa/εb satisfies the expression, but may be, for example, a multilayered structure having two or more layers. For each layer of the multilayered structure, for example, a material such as a metal material, a synthetic resin material, or a fiber-reinforced resin material may be used, or these materials may be configured to be, for example, a solid film layer, a hollow core layer, a nonwoven fabric layer, and/or a foam layer. All layers may be made of the same material or different materials. In addition, all the layers may have the same configuration or different configurations. For example, the constraining layer100can have different material in each layer, and different configuration and/or thickness in each layer, and can be surface-treated to allow the strain ratio εa/εb to satisfy the expression. The lower limit of εa/εb is preferably 0.1 or more, more preferably 0.15 or more, and still more preferably 0.2 or more. In addition, the upper limit of εa/εb is preferably 0.95 or less, more preferably 0.7 or less, and still more preferably 0.5 or less.

The viscoelastic layer200is not particularly limited if it is a material generally used for the viscoelastic layer in the vibration damping material, but for example, a rubber material, an elastomer material, or the like may be used. Examples of the rubber material include butyl rubber, acrylic rubber, chloroprene rubber and the like. Examples of the elastomer material include olefin-based elastomers, isobutylene-based elastomers and the like. The constraining layer100and the viscoelastic layer200can be adhered to each other by the viscosity of the viscoelastic layer200.

From the viewpoint of panel followability, the lower limit of the thickness of the viscoelastic layer200is, for example, preferably 0.5 mm or more, more preferably 1 mm or more, still more preferably 2 mm or more. In addition, from the viewpoint of mass efficiency, the upper limit of the thickness of the viscoelastic layer200is, for example, preferably 5 mm or less, more preferably 4 mm or less, still more preferably 3 mm or less, and most preferably 2 mm or less.

According to the first embodiment, the viscoelastic layer200is provided with a constraining layer100having a strain ratio εa/εb satisfying the expression 0<εa/εb<1. This can improve the vibration damping performance, can block noise transmitted mainly via vibration of an object, and can exhibit sufficient sound insulation performance.

Second Embodiment

As shown inFIGS.2and3, a vibration damping material of a second embodiment includes a core layer10having a hollow structure, a first film layer40provided on one surface of the core layer10, a second film layer50provided on another surface of the core layer10, and a viscoelastic layer200in contact with the second film layer50. The multilayered structure of the core layer10, and the first and second film layers40and50serves as a constraining layer100of the first embodiment described above. That is, the ratio εa/εb satisfies an expression 0<εa/εb<1, where: εa is the strain of the surface of the constraining layer100on the first film layer40side; and εb is the strain of the surface on the second film layer50side. Note that the same configurations as those in the first embodiment are referred to by the same reference signs, and detailed descriptions thereof are omitted here.

The core layer10is not particularly limited if it is a core layer generally used for a soundproofing material or a sound absorbing material, such as a core layer in which tubular cells are arranged in a plurality of rows. However, it is preferable to use a core layer having a structure as described below.

FIG.4is a perspective view showing a manufacturing process of a core material to be the core layer10. Note that the manufacturing method of this core material is described in detail in WO 2006/053407 A, which is incorporated herein by reference.

As shown inFIG.4, a flat material sheet is thermoformed by a roller (not shown) having a predetermined die to be plastically deformed substantially without cutting of the sheet, so that a core material1in the figure is formed. The materials of the core material1to be used can include, for example, a thermoplastic resin such as polypropylene (PP), polyethylene (PE), polyethylene terephthalate (PET), a composite material with fibers, paper, and metal, but it is not limited to these. In particular, a thermoplastic resin is preferable. In this embodiment, a case in which a thermoplastic resin is used is described below. The thickness of the material sheet is preferably in the range of 0.05 mm to 0.50 mm, for example, but it is not limited to this, and the thickness of the core material1after thermoforming is substantially the same.

The core material1has a three-dimensional structure in which ridge portions11and valley portions12are alternately arranged in a width direction X orthogonal to a manufacturing direction Y. The ridge portion11is configured with two side surfaces13and a top surface17between them, and the valley portion12is configured with two side surfaces13shared with the adjacent ridge portions11and a bottom surface14between them. Note that, in this embodiment, a case is described in which the shape of the ridge portion11is a trapezoid as shown inFIG.4, but the present invention is not limited to this, and in addition to polygons such as triangles or rectangles, shapes may be curved shapes such as sine curves or bow shapes.

The core material1includes the three-dimensional structure continuously in the manufacturing direction Y. That is, as shown inFIG.4, a plurality of ridge portions11a,11b,11c, and11dare continuously formed in the manufacturing direction Y. The valley portions12are also formed continuously. The connection between the ridge portions11and the connection between the valley portions12are made by alternately repeating two types of connection methods.

The first connection method is such that, as shown inFIG.4, on a first folding line X1in the width direction, top surfaces17band17cof two adjacent ridge portions11band11care connected, via trapezoidal-shaped ridge portion connecting surfaces15band15c, respectively. The ridge portion connecting surface15is formed at a right angle to the top surface17. On the first folding line X1in the width direction, bottom surfaces14band14cof two adjacent valley portions are directly connected. The second connection method is such that, as shown inFIG.4, on a second folding line X2in the width direction, bottom surfaces14aand14b(or14cand14d) of two adjacent valley portions are connected, via trapezoidal-shaped valley portion connecting surfaces16aand16b(or16cand16d), respectively. A valley portion connecting surface16is formed at a right angle to the bottom surface14. On the second folding line X2in the width direction, top surfaces12aand12b(or12cand12d) of two adjacent ridge portions are directly connected.

Thus, the core material1has a plurality of three-dimensional structures (the ridge portions11and the valley portions12) connected via the connection regions (the ridge portion connecting surfaces15and the valley portion connecting surfaces16), and has the connection region folded to form a core layer of the vibration damping material of the present invention. Specifically, the core material1is mountain-folded along the first folding line X1such that the bottom surfaces14band14cof two adjacent valley portions contact back-to-back with each other, and the angle formed by the ridge portion connecting surfaces15band15cof two adjacent ridge portions increases to 180 degrees. In addition, the core material1is valley-folded along the second folding line X2such that top surfaces17aand17b(or17cand17d) of two adjacent ridge portions contact face to face with each other, and the angle between the valley portion connecting surfaces16aand16b(or16cand16d) of two adjacent valley portions decreases to 180 degrees. A core layer10of the vibration damping material of the present invention obtained by folding the core material1in this manner is shown inFIGS.5and6.

As shown inFIGS.5and6, the core layer10includes substantially hexagonal tubular cells20arranged in a plurality of rows, and has cells20A,20C and20E formed out of two adjacent ridge portions and cells20B and20D formed out of two adjacent valley portions, each arranged in every other row. A broken line18inFIG.6is the surface that has been the back surface of the core material, and generally indicates the inner wall of the cell20having the substantially hexagonal tubular shape.

The cells20A,20C, and20E formed from the ridge portions each include six cell side walls forming the substantially hexagonal tubular shape. These cell side walls are formed out of the two top surfaces17and the four side surfaces13of the cell material. Furthermore, these cells20A,20C, and20E include substantially hexagonal tubular-shaped closed surfaces21A,21C, and21E, respectively, to close the cell ends at the cell ends on one surface10a(front surface inFIG.5) of the core layer10. Each of these closed surfaces21on one side is formed out of two trapezoidal ridge portion connecting surfaces15in the cell material. Furthermore, these cells20A,20C, and20E include open ends22A,22C, and22E that are opened in the substantially hexagonal shape at the cell ends on the other surface10bwhich is at the opposite side of the core layer10. The open ends22A,22C, and22E allow the respective internal spaces of the cells20A,20C, and20E to be in communication with the outside.

The cells20B and20D formed from the valley portions each also includes six cell side walls forming the substantially hexagonal tubular shape. These cell side walls are formed from two bottom surfaces14and four side surfaces13of the cell material. Furthermore, these cells20B and20D include open ends22B and22D that are opened in the substantially hexagonal shape at the cell ends on the one surface10aof the core layer10. The open ends22B and22D allow the respective internal spaces of the cells20B and20D to be in communication with the outside. Furthermore, these cells20B and20D include substantially hexagonal tubular-shaped closed surfaces21B and21D that close the cell ends, respectively, at the cell ends on the other surface10b, which is at the opposite side of the core layer10. Each of these closed surfaces21on the other side is formed out of the two trapezoidal valley portion connecting surfaces16in the cell material.

In this way, the core layer10has the one-side closed surfaces21A,21C, and21E formed out of the ridge portions of the cell material in every other row at the cell end on one surface10a, and has the other-side closed surfaces21B and21D formed out of valley portions of the cell material in the different cell rows from the above at the cell ends on the other surface10b. However, unless otherwise stated, both the closed surface21on one side and the closed surface21on the other side perform substantially the same function.

The thickness of the entire core layer10varies depending on which component of the vehicle a vibration damping material is used for, so it is not limited to the following. However, from the viewpoint of sound absorption performance of the core layer10itself, and strength and weight of the core layer10, it is preferably in the range of 3 mm to 50 mm, and is more preferably in the range of 5 mm to 30 mm.

The basis weight (weight per unit area) of the core layer10varies depending on which component of the vehicle the vibration damping material is used for, so it is not limited to the following. However, it is preferably in the range of 400 g/m2to 4,000 g/m2, and is more preferably in the range of 500 g/m2to 3,000 g/m2. As the thickness of the core layer10is greater and the basis weight is greater, the strength of the core layer10generally tends to be higher.

The basis weight of the core layer10can be adjusted by the type of material of the core layer10, the thickness of the entire core layer10or the wall thickness of the cell20(thickness of the material sheet) as well as the pitches Pcx and Pcy between the cells20of the core layer10(distance between the central axes of the cells). In order to set the basis weight of the core layer10within the above range, for example, it is preferable that the pitch Pcy between the cells20be in the range of 2 mm to 20 mm in the direction in which the cells20are adjacent to each other to form a row, which is the core manufacturing direction Y, it is more preferable that the pitch Pcy be in the range of 3 mm to 15 mm, and it is still more preferable that the pitch Pcy be in the range of 4 mm to 10 mm.

When the core layer10is used as the constraining layer100, the materials, thickness, Young's modulus, or the like of the first and second film layers40and50are changed so that the constraining layer100has a strain ratio εa/εb satisfying the expression of 0<εa/εb<1.

The material of the first and second film layers40, and50to be used may be, for example, resin films such as polypropylene (PP), polyethylene (PE), polyethylene terephthalate (PET), and polyamide (PA), but it is not limited to these. For the first film layer40and the second film layer50, the same material may be used or different materials may be used, so that the strain ratio εa/εb satisfies the above expression.

The thicknesses of the first and second film layers40and50are not particularly limited, but for example, the lower limit thereof is preferably 0.03 mm or more, more preferably 0.04 mm or more, still more preferably 0.05 mm or more. In addition, the upper limit of the thickness is preferably 0.5 mm or less, more preferably 0.4 mm or less, and still more preferably 0.3 mm or less. The first film layer40and the second film layer50may have the same thickness or may have different thicknesses, so that the strain ratio εa/εb satisfies the above expression.

The first and second film layers40and50may be adhered to the core layer10by heat-welding, or may be adhered thereto via an adhesive (not shown). The adhesive to be used is not particularly limited, but for example, it may be an epoxy-based or acrylic-based adhesive. In addition, the first and second film layers40and50each may have a three-layer structure including a central layer and two adhesive layers located on both side surfaces thereof. In this case, the material of the adhesive layer is a material having a melting point lower than the melting point of the material used for the central layer. For example, polyamide having a melting point of 190° C. to 220° C. is used for the central layer, and polyethylene having a melting point of 90° C. to 130° C. is used for the adhesive layer. Then, the temperature at the time of heating when the first and second film layers40and50are adhered to the core layer10or the viscoelastic layer200, and the temperature for thermoforming into a predetermined shape of the vibration damping material are set to about 150° C. to 160° C. This configuration and process melts only the adhesive layer without melting the central layer to enable the central layer to firmly adhere to the core layer10. A resin having a melting point higher than that of polyethylene for the adhesive layer is polypropylene as well as polyamide.

The first and second film layers40and50each may be breathable with a plurality of apertures penetrating the film layer, or each may be non-breathable without such apertures. Providing the apertures can increase the strain E of the surface on the film layer side having the apertures provided, and can readily control the strain ratio εa/εb described above. When there are apertures, the holes are provided in advance before the first film layer40or the second film layer50is adhered to the core layer10, for example, by a hot needle or punching (punching using a male die and a female die). In order to prevent the holes from being closed, it is preferable to have a hole shape in which burrs of the holes are minimized. The aperture pattern does not have any particular limitation, but it is preferably arranged in a staggered arrangement or a lattice arrangement. The aperture rate of the first film layer40, or the second film layer50is not particularly limited, but it is preferably in the range of 0.2% to 5%. The diameter of the aperture is preferably in the range of 0.25 mm to 2.5 mm, and more preferably in the range of 0.3 mm to 2.0 mm Note that the pitch of the apertures of the first film layer40or the second film layer50does not necessarily need to be the same as the pitches Pcx and Pcy of the cells20of the core layer10shown inFIG.5, and the apertures and the cells20do not necessarily need to be aligned when the first film layer40, or the second film layer50is adhered to the core layer10. This is because the positions of the apertures of the first film layer40or the second film layer50, and the open ends22of the cells20of the core layer10randomly overlap each other to allow appropriate communication between the inside and outside. It is preferable that the pitch of the apertures of the first film layer40or the second film layer50be smaller than the pitch of the cells20of the core layer10, at least in either an X direction or a Y direction.

According to the second embodiment, the constraining layer100is configured such that the first and second film layers40and50are provided on both sides of the core layer10on which the open ends and the closed surfaces are arranged in every other row. This makes it possible to provide a vibration damping material which can obtain the same effect as that of the first embodiment and can achieve weight reduction together with high rigidity.

Third Embodiment

In the first and second embodiments, cases are described in which the surface of the viscoelastic layer200in contact with the constraining layer100has the same area as the surface of the constraining layer100on the viscoelastic layer200side, but the present invention is not limited to this. As shown in each example ofFIGS.7A to7C, a vibration damping material of a third embodiment has a viscoelastic layer200partially provided on the surface100bof the constraining layer100on the side in contact with the viscoelastic layer. Note that the same configurations as those in the first and second embodiments are referred to by the same reference signs, and detailed descriptions thereof are omitted here.

For example, as shown inFIG.7A, a plurality of linear viscoelastic layers200A may be arranged in parallel on the surface100bof the constraining layer100on the side in contact with the viscoelastic layer. In addition, as shown inFIG.7B, a curved viscoelastic layer200B having an S-shape or the like may be provided on the surface100bof the constraining layer100on the side in contact with the viscoelastic layer. Furthermore, as shown inFIG.7C, a plurality of rectangular viscoelastic layers200C may be arranged in a lattice pattern or in a staggered pattern, on the surface100bof the constraining layer100on the side in contact with the viscoelastic layer. In this way, for example, the area of the surface of the viscoelastic layer200in contact with the constraining layer100is preferably in the range of 5% to 50% of the area of the surface of the constraining layer100on the viscoelastic layer200side, and more preferably in the range of 10% to 20%.

According to the third embodiment, the viscoelastic layer200is partially provided on the surface100bof the constraining layer100on the side in contact with the viscoelastic layer. This makes it possible to obtain the same effect as that of the first and second embodiments while the amount of the viscoelastic layer200to be used is reduced.

Fourth Embodiment

As shown inFIGS.8and9, a vibration damping material of a fourth embodiment includes a core layer10, a first film layer40provided on one surface of the core layer10, a second film layer50and a fiber layer60provided in order on the other surface of the core layer10, and a viscoelastic layer200in contact with the fiber layer60. The multilayered structure of the core layer10, the first and second film layers40and50, and the fiber layer60serves as a constraining layer100of the first embodiment described above. That is, the ratio εa/εb satisfies the expression 0<εa/εb<1, where: εa is the strain on the surface of the constraining layer100on the first film layer40side; and εb is the strain on the surface on the fiber layer60side. Note that the same configurations as those in the first to third embodiments are referred to by the same reference signs, and detailed descriptions thereof are omitted here.

In the fourth embodiment, the fiber layer60is provided between the second film layer50and the viscoelastic layer200. The fiber layer60is not particularly limited if it maintains the strain ratio εa/εb described above within a predetermined range. However, for example, it is preferable to use various nonwoven fabrics such as spunbonded, spunlaced, or needle punched nonwoven fabrics, using resin fibers such as polyethylene terephthalate (PET), polypropylene (PP), or polyethylene (PE). The basis weight of the fiber layer60is not particularly limited if the strain ratio εa/εb described above is maintained within a predetermined range. However, for example, it is preferably in the range of 10 g/m2to 600 g/m2, more preferably in the range of 20 g/m2to 500 g/m2, and still more preferably in the range of 30 g/m2to 300 g/m2.

The fiber layer60and the second film layer50can be adhered to each other by utilizing the heat-welding property of the second film layer50or by using an adhesive. The fiber layer60and the viscoelastic layer200can be adhered to each other by utilizing the viscosity of the viscoelastic layer200.

According to the fourth embodiment, the constraining layer100is provided so that the fiber layer60is in contact with the viscoelastic layer200. This enables obtaining the same effect as that of the first embodiment, and as shown inFIG.9, sinks fibers62in the fiber layer60of the constraining layer100into the inside of the viscoelastic layer200to adhere the fibers62thereto. This configuration such that the fibers are mixed in the viscoelastic layer200enables obtaining an effect such that the vibration damping effect is improved and the adhesive strength between the constraining layer100and the viscoelastic layer200is also improved.

Fifth Embodiment

As shown inFIG.13, a vibration damping material of a fifth embodiment includes a core layer10, a first film layer40and a metal layer70provided in order on one surface of the core layer10, a second film layer50provided on the other surface of the core layer10, and a viscoelastic layer200in contact with the second film layer50. The multilayered structure of the core layer10, the first and second film layers40and50, and the metal layer70serves as a constraining layer100of the first embodiment described above. That is, the ratio εa/εb satisfies the expression 0<εa/εb<1, where: εa is the strain on the surface of the constraining layer100on the metal layer70side; and εb is the strain on the surface on the second film layer50side. Note that the same configurations as those in the first to third embodiments are referred to by the same reference signs, and detailed descriptions thereof are omitted here.

In the fifth embodiment, the metal layer70is provided on the outer surface side of the first film layer40. The metal layer70is not particularly limited if it maintains the strain ratio εa/εb described above within a predetermined range, but for example, it is preferable to use a metal thin film such as a steel plate, an aluminum foil, or a copper foil. The thickness of the metal layer70is not particularly limited if the strain ratio εa/εb described above is maintained within a predetermined range, but for example, the lower limit is preferably 5 μm or more, more preferably 7 μm or more, and still more preferably 10 μm or more. Furthermore, the upper limit is preferably 1 mm or less, more preferably 0.5 mm or less, still more preferably 0.1 mm or less. The metal layer70and the first film layer40can be adhered to each other by utilizing the heat-welding property of the first film layer40or by using an adhesive.

According to the fifth embodiment, the metal layer70is provided on the surface of the constraining layer100opposite to the viscoelastic layer200. This makes it possible to obtain the same effect as that of the first embodiment, and to significantly reduce the strain εa on the surface of the constraining layer100on the opposite side to the viscoelastic layer200to facilitate control of the strain ratio εa/εb.

Sixth Embodiment

As shown inFIG.14, a vibration damping material of a sixth embodiment has a structure such that a constraining layer100R is molded to match the shape of a panel300R of the roof of a vehicle so that the thickness of a viscoelastic layer200R is uniform. Note that the same configurations as those in the first embodiment are referred to by the same reference signs, and detailed descriptions thereof are omitted here.

In the case of the vibration damping material molded in this way, as shown inFIG.14B, the strain ratio εa/εb described above satisfies the expression 0<εa/εb<1, where: εa is the strain on the surface of the constraining layer100R after molding on the side opposite to the viscoelastic layer200R; and εb is the strain on the surface thereof on the side in contact with the viscoelastic layer200R.

According to the sixth embodiment, the constraining layer100R of the vibration damping material has a shape such as a curved shape or a corrugated shape corresponding to the shape of the panel300R, instead of a flat shape. However, if the thickness of the viscoelastic layer200R is uniform, the constraining layer100R having a strain ratio εa/εb satisfying the above expression can improve the vibration damping performance as in the first embodiment, can block noise transmitted mainly via vibration of an object, and can exhibit sufficient sound insulation performance. Note that, althoughFIG.14shows a vibration damping material provided on the roof panel of a vehicle, the present invention is not limited to this, and the same effect also can be obtained on panels having various shapes, which are not flat, such as dash panels, floor panels, and door panels of vehicles.

EXAMPLES

Examples and a Comparative Example of the present invention are described below.

As Example 1, a vibration damping material including the constraining layer and the viscoelastic layer shown inFIG.2was produced. First, to produce a constraining layer, the first film layer (material: polypropylene (PP) film, thickness: 350 μm) was adhered to one surface of the core layer having the structures shown inFIGS.5and6(material: polypropylene (PP) resin, pitch between cells Pcy: 8 mm, core layer thickness: 10 mm), and the second film layer (material: polypropylene (PP) film, thickness: 300 μm) was adhered to the other surface. Then, this constraining layer was subjected to three-point bending using a universal material testing machine (model 5900, manufactured by Instron), and the strain was measured. The size of the test piece was 60 mm×200 mm. As shown inFIG.10, a test piece100S was supported by two fulcrums102located at an interval of 100 mm, and a load was applied to the center position thereof with an indenter104so that the indenter104moved down by 0.5 mm. For strain measurement, a strain measuring instrument (PCD-400A, manufactured by Kyowa Electronic Instruments Co., Ltd.) was used. Each of the strains εa and εb on both sides of the constraining layer was measured. As a result, the strain ratio εa/εb was 0.91.

Next, a viscoelastic layer (material: butyl rubber, thickness: 1 mm sheet) was adhered to the second film layer side of the constraining layer to produce a vibration damping material. Furthermore, a panel (material: steel plate, thickness: 0.5 mm) was adhered to the viscoelastic layer side of this vibration damping material. Then, the loss coefficient was measured with the vibration damping material adhered to this panel. As the test piece, as shown inFIG.11A, the constraining layer100S and the viscoelastic layer200S each had a size of 60 mm×180 mm, and a panel300S had a size of 60 mm×200 mm. The protruding, 20 mm length portion of the panel was fixed to a fixing device112to support the test piece on one side. Then, the FFT analyzer116(DS-3200, manufactured by Ono Sokki Co., Ltd.) was placed on the panel300S of the test piece 40 mm away from the fixing device112, and the free end side of the test piece was loaded with a hand-held electromagnetic exciter114(Type 5961, manufactured by B & K Co., Ltd. The loss coefficient was calculated from the obtained measurement results of the resonance characteristics by a half-value width method. As shown inFIG.11B, a frequency graph with respect to the amplitude of the test piece is created. The loss coefficient was calculated from an expression of η=(f2−f1)/f0, where: f0was the frequency at the maximum amplitude; and f1and f2were frequencies between which the amplitudes ranging over 3 dB from the maximum amplitude were contained. The result is shown in Table 1 andFIG.12.

Note that a vibration damping material in Comparative Example 1 for comparison was produced in the same manner as in Example 1 except that only a PP film (thickness: 300 μm) was used as the constraining layer. In Comparative Example 1, the strain and the loss coefficient were measured in the same manner as in Example 1. The result is shown in Table 1 andFIG.12.

In addition, vibration damping materials in Examples 2 to 6, as shown in Table 1, were produced in the same manner as in Example 1, except that the film layers had different thicknesses on the viscoelastic layer side and the opposite side, of the constraining layer, and some film layers further had a metal layer (material: steel plate, thickness: 0.5 mm; or material: aluminum foil, thickness: 30 μm) provided thereon. Then, the strains and loss coefficients were measured in Examples 2 to 6. These results are shown in Table 1 and FIG.12.

As shown in Table 1 andFIG.12, the vibration damping materials in Examples 1 to 6 had the strain ratio εa/εb smaller than 1, where: εa was the strain on the surface of the constraining layer on the opposite side to the viscoelastic layer; and εb was the strain on the surface thereof on the side in contact with the viscoelastic layer, and the vibration damping materials in Examples 1 to 6 improved loss coefficients significantly as compared with that in Comparative Example 1 having a strain ratio εa/εb of 1.

INDUSTRIAL APPLICABILITY

According to the vibration damping material of the present invention can achieve high rigidity and weight reduction while exhibiting excellent vibration damping performance (sound insulation performance). Therefore, the vibration damping material of the present invention is specifically useful for, for example, a component that attenuates panel vibration between a vehicle interior and a noise source such as a dash panel, floor panel, door panel, roof, wheel house, and fender panels.

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