阅读说明：本技术 汽车的腰线部隔音结构及汽车用门玻璃 (Car waist line part sound insulation structure and car door glass ) 是由 山田大介 于 2018-06-27 设计创作，主要内容包括：本发明提供一种汽车的腰线部隔音结构及用于该隔音结构的汽车用门玻璃,其通过抑制经由腰线部从车外侵入声音和因构成门玻璃的玻璃板的振动而产生声音,能将门玻璃关闭时的汽车内的隔音状态提高至高水平。汽车的腰线部隔音结构是沿着汽车的腰线将门板和门玻璃之间隔音的隔音结构,其特征在于,门板具有彼此相向的面板,门玻璃以能够升降的方式配置在面板之间并能自由开闭；门玻璃具有玻璃板和配置在其主面的下方部的粘弹性构件；在粘弹性构件表面测定的ASKER C硬度为10～80；当门玻璃关闭时,粘弹性构件受到玻璃板中的粘弹性构件的配置区域和相向的面板的表面的约束。(The invention provides a waist line part sound insulation structure of an automobile and an automobile door glass used for the sound insulation structure, which can improve the sound insulation state in the automobile when the door glass is closed to a high level by inhibiting the sound entering from the outside of the automobile through the waist line part and the sound generated by the vibration of a glass plate forming the door glass. The automotive belt line part sound insulation structure is a sound insulation structure for insulating sound between a door panel and a door glass along a belt line of an automobile, and is characterized in that the door panel is provided with panels which face each other, and the door glass is arranged between the panels in a lifting way and can be freely opened and closed; the door glass has a glass plate and a viscoelastic member disposed below a main surface thereof; the ASKER C hardness measured on the surface of the viscoelastic component is 10-80; when the door glass is closed, the viscoelastic member is constrained by the arrangement region of the viscoelastic member in the glass plate and the surface of the facing panel.)

1. A soundproof structure for a belt line portion of an automobile, which is a soundproof structure for insulating sound between a door panel and a door glass along a belt line of the automobile,

the door plate is provided with two panels which face each other, and the door glass is arranged between the two panels in a lifting manner;

the door glass has a glass plate and a viscoelastic member disposed below a main surface of one side of the glass plate;

the hardness measured on the surface of the viscoelastic member is 10-80 in terms of ASKER C hardness specified by SRIS 0101;

when the door glass is closed, the viscoelastic member is constrained by the arrangement region of the viscoelastic member in the glass plate and a part of the surface of the panel facing the one main surface.

2. The automotive belt line part acoustic insulation structure according to claim 1, wherein the viscoelastic member comprises a layer composed of a foam.

3. The automotive belt line sound insulation structure according to claim 2, wherein the surface layer portion of the viscoelastic member has a layer made of a non-foam material.

4. The automotive belt line part sound-insulating structure according to claim 2 or 3, wherein the foam has an open cell ratio of 80% or less.

5. The automotive belt line part sound-insulating structure according to any one of claims 2 to 4, wherein the foam has an airflow resistance value of 1.0 x 10 as measured according to ISO9053DC method⁴～1.0×10⁸N·s/m⁴。

6. The automotive belt line sound-insulating structure according to any one of claims 1 to 5, wherein the viscoelastic member has a cross section cut in the up-down direction in a wedge shape that gradually narrows toward an upper end thereof when the door glass is opened.

7. The automotive belt line sound-insulating structure according to claim 6, wherein the viscoelastic member has a cross section with an upper edge of 5 to 25mm and a lower edge of 10 to 30 mm.

8. The automotive belt line sound-insulating structure according to any one of claims 1 to 7, wherein the viscoelastic member has a drainage structure.

9. The automotive belt line part sound-insulating structure according to any one of claims 1 to 8, wherein the glass plate is formed of one glass plate.

10. The automotive belt line sound-insulating structure according to any one of claims 1 to 9,

the door glass further includes a viscoelastic member disposed below the other principal surface of the glass plate;

the hardness measured on the surface of the viscoelastic member disposed below the other main surface is 10 to 80 in terms of ASKER C hardness specified by SRIS 0101;

when the door glass is closed, the viscoelastic member disposed in the lower portion of the other main surface is constrained by the region in which the viscoelastic member is disposed on the other main surface of the glass plate and the surface of a portion of the panel facing the other main surface.

11. The automotive belt line sound-insulating structure according to claim 10, wherein the viscoelastic member disposed below the other main surface of the glass plate is the same as the viscoelastic member disposed below the one main surface of the glass plate according to any one of claims 2 to 8.

12. The door glass for an automobile, which is used for the beltline sound-insulating structure according to any one of claims 1 to 11, is composed of a glass plate with a viscoelastic member.

Technical Field

The present invention relates to a sound insulating structure for a belt line portion of an automobile and an automobile door glass used for the sound insulating structure.

Background

Conventionally, as one of methods for improving the sound insulation property in the vehicle interior, a method of providing a sound insulation structure along a belt line of the vehicle has been employed. As this sound insulation structure, for example, patent document 1 discloses a sound insulation structure in which a sound insulation material is provided on one of lower end portions of an outer seal portion and an inner seal portion attached to a door panel and a portion corresponding to a lower end portion of a door glass, and a protrusion that comes into contact with the sound insulation material is provided on the other.

In the sound insulation structure described in patent document 1, when the door glass is closed, the door panel, specifically, a gap between a sealing member provided in the door panel and the door glass is closed, so that intrusion of sound from outside the vehicle is prevented. However, the demand for quietness in the vehicle interior has increased year by year, and a high level of sound insulation performance that can meet the demand has not been obtained by the sound insulation structure of patent document 1.

Disclosure of Invention

Technical problem to be solved by the invention

The present invention has been made in view of the above-described circumstances, and an object thereof is to provide a beltline sound-insulating structure for an automobile, which can improve the sound-insulating state in the automobile when the door glass is closed to a high level by suppressing sound entering from the outside of the automobile through the beltline portion and sound generation due to vibration of the glass plate constituting the door glass, and a door glass for an automobile used for the sound-insulating structure.

Technical scheme for solving technical problem

The automotive belt line sound insulation structure of the present invention is a sound insulation structure that insulates sound between a door panel and a door glass along a belt line of an automobile, and is characterized in that the door panel has two panels facing each other, and the door glass is disposed between the two panels so as to be able to be lifted; the door glass has a glass plate and a viscoelastic member disposed below a main surface of one side of the glass plate; the hardness measured on the surface of the viscoelastic member is 10-80 in terms of ASKER C hardness specified by SRIS 0101; when the door glass is closed, the viscoelastic member is constrained by the arrangement region of the viscoelastic member in the glass plate and a part of the surface of the panel facing the one main surface.

The door glass for an automobile according to the present invention is characterized in that the beltline sound-insulating structure used in the present invention is formed of a glass plate with a viscoelastic member.

ADVANTAGEOUS EFFECTS OF INVENTION

The automotive beltline sound-insulating structure of the present invention has high sound-insulating performance for suppressing sound volume entering from the outside of the vehicle through the beltline part and suppressing sound generation due to vibration of a glass plate constituting a door glass. Further, the sound insulation of the waist portion hardly causes an increase in the sound volume entering the vehicle interior through other means. Thus, if the belt-line sound-insulating structure of an automobile according to the present invention is used, a high-level sound-insulating state can be achieved in the automobile when the door glass is closed.

The door glass for an automobile of the present invention can construct the belt-line sound-insulating structure for an automobile of the present invention, which can achieve a high-level sound-insulating state in the automobile when the door glass is closed when the door glass is assembled to the automobile.

Drawings

Fig. 1 is a side view of an automobile having a beltline portion acoustic insulation structure of the present invention.

Fig. 2 is a sectional view taken along line a-a' -a "in fig. 1 schematically showing a state of the door glass when it is closed and when it is opened, as an example of the beltline sound-insulating structure of the present invention.

Fig. 3 is a cross-sectional view schematically showing another example of the door glass for an automobile according to the present invention.

Detailed Description

Embodiments of a beltline sound-insulating structure (hereinafter also simply referred to as "sound-insulating structure") and an automotive door glass (hereinafter also simply referred to as "door glass") according to the present invention will be described below with reference to the drawings. The present invention is not limited to these embodiments, and variations and modifications may be made to these embodiments without departing from the technical spirit and scope of the present invention.

Fig. 1 is a side view of an automobile having a beltline sound-insulating structure shown in fig. 2 as an example of the embodiment. In the automobile 10 shown in fig. 1, the front and rear side doors 3 are each composed of a door panel 2 and a door glass 1A disposed so as to be able to rise and fall on the door panel 2, and fig. 1 shows the automobile 10 in a state where the door glass 1 is closed.

In the side door 3, the door panel 2 has two panels (only the panel 22 on the vehicle outer side is shown in fig. 1) facing each other, and the door glass 1A is disposed between the two panels so as to be able to rise and fall. Thus, when the door glass 1A is closed, the window opening W is closed by the door glass 1A, and when the door glass 1A is opened, the window opening W is opened. In the present specification, a panel located on the vehicle interior side of two panels included in a door panel is referred to as an inner panel, and a panel located on the vehicle exterior side is referred to as an outer panel.

In the automobile 10, the belt line L is a line connecting the upper ends of the front and rear door panels 2. In the present invention, a region having a predetermined width from the upper end of the door panel 2 downward along the waist line L is referred to as a waist line portion, and is denoted by Ls in fig. 1. The side door 3 of the automobile 10 is configured to provide a sound insulating structure at the beltline portion Ls when the door glass 1A is closed.

Fig. 2 is a cross-sectional view taken along line a-a' -a "in fig. 1 schematically showing the side door 3 when the door glass 1A is closed and opened, as an example of the beltline sound-insulating structure of the present invention. Hereinafter, the time when the door glass 1A is closed and the time when the door glass 1A is opened are also simply referred to as "closed time" and "open time", respectively. The broken line shown in the door panel 2 of fig. 1 indicates the position of the lower end of the door glass 1A when the door glass 1A is lowered to the lowest position and the window opening W is fully opened. The door glass 1A when closed is lowered in the direction of arrow P1, and the fully lowered state is when opened. The door glass 1A when opened is raised in the direction of arrow P2, and the completely raised state is when closed. The sectional view of line a-a' -a "of fig. 1 shown when opened in fig. 2 includes a sectional view of the entire door glass 1A.

[ Sound insulation Structure ]

The sound insulating structure of the waist portion shown in fig. 2 will be explained. The door panel 2 includes an inner panel 21 and an outer panel 22 as two panels facing each other, and the door glass 1A is disposed between the inner panel 21 and the outer panel 22 so as to be able to be lifted and lowered. The inner panel 21 and the outer panel 22 have, as sealing members, an inner sealing member 41 and an outer sealing member 42 for sealing between the respective facing surfaces and the door glass 1A in a region along the beltline, that is, in the beltline portion. In the present specification, "inner" is a prefix of a member disposed on the vehicle interior side with respect to the door glass, and "outer" is a prefix of a member disposed on the vehicle exterior side with respect to the door glass.

The inner seal member 41 has upper and lower lips, i.e., an upper inner lip 411 and a lower inner lip 412, on the door glass 1A side, and the outer seal member 42 similarly has an upper outer lip 421 and a lower outer lip 422 on the door glass 1A side. The inner seal member 41 and the outer seal member 42 are formed of synthetic rubber such as ethylene-propylene rubber (EPDM rubber), thermoplastic elastomer such as polyolefin elastomer, or the like.

In the sound insulating structure according to the embodiment, the shapes of the inner seal member 41 and the outer seal member 42 are not limited to this. The sealing member in the sound insulating structure of the embodiment may be a sealing member having the same configuration as a sealing member commonly used in a belt line portion of an automobile. The conventional seal member may be formed with a lip, for example.

As shown in the entire cross-sectional view of the opened state of fig. 2, the door glass 1A has a glass plate 11A and a viscoelastic member 13A. The hardness measured on the surface of the viscoelastic member 13A is 10 to 80 in terms of ASKER C hardness specified by SRIS 0101 under the temperature condition of 23 ℃ +/-2 ℃. In the present specification, unless otherwise specified, "ASKER C hardness" refers to ASKER C hardness measured under the conditions.

The glass plate 11A of the door glass 1A is not particularly limited as long as it is a transparent plate-like body generally used as a window of a vehicle. Examples of the shape include a flat plate shape and a curved shape. The shape of the main surface is matched with the shape of a window opening of a vehicle to be mounted. The glass plate 11A may be a general-purpose plate glass, tempered glass, or wired glass. The thickness of the glass plate 11A is about 2.8 to 5.0mm depending on the type of vehicle. The glass plate 11A may be a single glass plate, so-called single-layer glass, a laminated glass in which a plurality of glass plates are laminated with an intermediate layer interposed therebetween, or a multi-layer glass in which a plurality of glass plates are laminated so as to have an air layer due to the presence of a spacer. Even if the glass plate 11A is a single glass plate, by combining the glass plate 11A with the viscoelastic member 13A, excellent sound-insulating properties can be obtained at low cost without using a laminated glass having sound-insulating properties.

The glass used as the glass plate 11A may, for example, be transparent inorganic glass or organic glass (resin). Specific examples of the inorganic glass include ordinary soda-lime glass, borosilicate glass, alkali-free glass, and quartz glass. As the glass, glass absorbing ultraviolet rays and infrared rays may be used. Further, the resin may, for example, be an acrylic resin such as polymethyl methacrylate, an aromatic polycarbonate resin such as polyphenylene carbonate, or a polystyrene resin.

The viscoelastic member 13A is disposed below the main surface Sa of the glass plate 11A on the vehicle interior side. Then, as shown in fig. 2, when the door glass 1A is closed, the viscoelastic member 13A is restrained by the arrangement region of the viscoelastic member 13A in the glass plate 11A and a part of the surface of the inner panel 21 on the door glass 1A side. The lower portion of the glass plate 11A refers to a region where the viscoelastic member 13A can be restrained by the glass plate 11A and a part of the surface of the inner panel 21 on the door glass 1A side when the door glass 1A is closed.

In the sound insulation structure according to the embodiment, the viscoelastic member may be configured such that at least a part thereof is constrained by the glass plate of the door glass and a part of the surface of the panel on the door glass side when the door glass is closed. For example, as shown in the closed state of fig. 2, the upper portion of the viscoelastic member 13A may be sandwiched between the inner seal member 41 and the glass plate 11A, and the lower portion of the viscoelastic member 13A may be restrained by the glass plate 11A and a portion of the surface of the inner panel 21 on the door glass 1A side.

With the sound insulation structure shown in fig. 2, the viscoelastic member 13A having an ASKER C hardness of 10 to 80 can be brought into close contact with the space between the glass plate 11A and the inner panel 21 and the space between the glass plate 11A and the lower portion of the inner seal member 41, thereby sealing the vehicle interior. Therefore, the sound volume entering the vehicle interior through the belt line portion when the door glass is closed can be sufficiently suppressed. Further, the viscoelastic member 13A forms a constraint type vibration damping structure by being constrained between the glass plate 11A and the inner plate 21.

Here, "constraint" means a state in which the viscoelastic member 13A is sandwiched between the glass plate 11A and the inner plate 21 and the movement of the viscoelastic member 13A is restricted. Therefore, the vibration of the glass plate 11A can be sufficiently suppressed, and a high sound insulation effect in the vehicle interior when the door glass is closed can be achieved. Further, as the cause of the vibration of the glass plate in the door glass, there are, for example, propagation of road noise from the door panel to the glass plate of the door glass, propagation of engine noise, and the like. The inventive waist line part sound insulation structure can sufficiently restrain the vibration of the glass plate in the door glass caused by any reason.

Further, the viscoelastic member 13A can also form a constraining structure in the case where it is sandwiched between the glass plate 11A and the upper and lower inner lips 411, 412. In this case, in order to obtain sufficient vibration damping properties for the glass plate, the ASKER C hardness of the portion of the inner seal member that contacts the viscoelastic member is preferably greater than the ASKER C hardness of the viscoelastic member, and is preferably greater than the ASKER C hardness of the viscoelastic member by 5 or more, more preferably greater than 10 or more, and still more preferably greater than 15 or more.

The viscoelastic member 13A effectively blocks sound entering the vehicle interior through the belt line portion by setting the ASKER C hardness to 10 to 80. The details are described below.

The sound entering the vehicle interior through the belt line portion is actually sound entering the vehicle interior from the door panel 2 through the belt line portion. Here, it is considered that if sound is reflected by the viscoelastic member 13A into the door panel 2, the sound volume entering the vehicle interior via the belt line portion decreases, but the reflected sound (reflected sound) enters the vehicle interior through a portion of the inner door panel below the belt line portion.

The viscoelastic member 13A preferably has sound absorption and sound insulation properties in a good balance. Thus, the sound insulation effect can reduce the sound entering the vehicle from the door panel through the waist portion. Further, the viscoelastic member 13A has sound absorption properties, and particularly when it includes a layer made of a foam, sound intrusion into the vehicle interior can be reduced by the sound absorption effect of the bubble structure.

(Properties of the viscoelastic Member 13A)

The viscoelastic member 13A is made of a material having viscoelasticity (hereinafter also referred to as "viscoelastic material"), and has an ASKER C hardness of 10 to 80. By providing the viscoelastic member 13A with such characteristics, the sound insulating property and the vibration damping property when the door glass is closed can be achieved in the sound insulating structure of the embodiment.

If the hardness of ASKER C is within the range of 10 to 80, the viscoelastic member 13A has a desired sound insulating property (both of sound absorbing property and sound blocking property), whereby the volume of sound entering the vehicle can be reduced. If the asker c hardness is 10 or more, the sound volume passing through the viscoelastic member 13A can be effectively reduced, and therefore the sound volume intruding into the vehicle interior via the belt line portion can be greatly reduced. If the hardness of ASKER C is 80 or less, the amount of sound absorbed by the viscoelastic member 13A increases, the sound volume penetrating the inner door panel into the vehicle decreases, and the sound volume penetrating the vehicle interior can be greatly reduced. Further, if the ASKER C hardness of the viscoelastic member 13A is within the range of 10 to 80, the viscoelastic member 13A has appropriate shape following properties, and when the door glass is closed, the viscoelastic member 13A deforms when the viscoelastic member 13A is sandwiched between the glass plate 11A and the inner plate 21, and the surface can adhere to the inner plate 21 and the inner side sealing member 41 with good sealing properties, and both sound insulation properties and vibration damping properties are excellent.

The ASKER C hardness of the viscoelastic member 13A is preferably 10 to 78, more preferably 15 to 60, and further preferably 28 to 40. The ASKER C hardness of the viscoelastic member 13A is a hardness measured on the surface of the viscoelastic member 13A. The viscoelastic member 13A may be formed of a single viscoelastic material, or may be formed of a plurality of viscoelastic materials.

When the viscoelastic member 13A is made of a single viscoelastic material, the ASKER C hardness of the viscoelastic material is 10 to 80. When the viscoelastic member 13A is made of a plurality of viscoelastic materials, the ASKER C hardness of each viscoelastic material is not necessarily within a range of 10 to 80. The ASKER C hardness of the viscoelastic member 13A obtained by using a plurality of viscoelastic materials is within a range of 10 to 80. The ASKER C hardness is measured on the surface of the middle portion of the viscoelastic member 13A excluding the end portions (indicated by "ms" in fig. 2), and is measured on the surface on the inner panel 21 side of the viscoelastic member 13A, for example, on the surface on the inner side 12mm or more from the end portions.

As the viscoelastic material satisfying the ASKER C hardness of 10 to 80, specifically, a viscoelastic material composed of synthetic rubber such as EPDM rubber, thermoplastic elastomer resin such as polyolefin elastomer and polystyrene elastomer, urethane resin, polyvinyl chloride resin, epoxy resin, silicone gel, polynorbornene, or the like is adjusted to have an ASKER C hardness of 10 to 80, and other properties are optimized.

The viscoelastic material constituting the viscoelastic member 13A may contain a filler such as an organic filler or a mineral filler. As the organic filler, for example, resin particles made of a resin such as crosslinked polyester, polystyrene, styrene-acrylic copolymer resin, or urea resin, synthetic fibers, or natural fibers can be used.

Examples of the mineral filler include calcium carbonate, calcium oxide, magnesium hydroxide, magnesium oxide, magnesium carbonate, aluminum hydroxide, barium sulfate, barium oxide, titanium oxide, iron oxide, zinc carbonate, agalmatolite clay, kaolinite clay, clay such as calcined clay, and inorganic fillers such as mica, diatomaceous earth, carbon black, silica, glass fibers, carbon fibers, fibrous fillers, and hollow glass microparticles. As described above, by containing the filler, the ASKER C hardness, the young's modulus, and the loss factor of the viscoelastic member 13A can be adjusted to desired values.

In order to achieve the ASKER C hardness of 10 to 80, the viscoelastic member 13A is preferably made of a foam. When the viscoelastic member 13A is formed of a foam, the viscoelastic member 13A is preferably a polymer foam having an ASKER C hardness of 10 to 80, which is formed by foaming the above viscoelastic material or a polymer material such as a resin other than the above viscoelastic material by a conventional method. Examples of the polymer material constituting the skeleton of the polymer foam include the viscoelastic materials mentioned above, polystyrene, polyolefin (polyethylene, polypropylene, etc.), phenol resin, polyvinyl chloride, urea resin, silicone, polyimide, melamine resin, ethylene-vinyl acetate copolymer (EVA), and the like.

The foam is composed of a skeleton and cells (voids). The material constituting the foam skeleton is preferably the above-mentioned polymer material, and among the above-mentioned polymer materials, polyurethane resin, EPDM rubber, polyethylene, polypropylene, polystyrene, EVA, and the like are preferable, and polyurethane resin is particularly preferable. These materials have excellent resilience to compression.

The porosity of the foam is preferably 63 to 80%, more preferably 71 to 77%. The porosity was determined by using an apparent density (density of the entire sample including the skeleton and voids) and a true density (density of a material constituting the skeleton) and "porosity [% ], 1- (apparent density/true density) × 100". If the porosity of the foam is within the above range, both the sound absorbing effect and the sound insulating effect can be expected at the same time, which is preferable.

The average cell diameter of the foam is preferably 0.10 to 0.56mm, more preferably 0.21 to 0.33 mm. The average cell diameter can be determined by taking a scanning electron micrograph of a cross section of the foam according to the test method of ASTM D2842-69, for example, as an average of diameters of 20 cells. The diameter of the bubble is, for example, averaged between the maximum diameter and the minimum diameter. If the average cell diameter of the foam is within the above range, both the sound absorbing effect and the sound insulating effect can be expected at the same time, which is preferable.

The foam is classified into an open-cell foam, and a semi-open-cell foam according to the form of cells. In the closed-cell foam, cells are independently present in the foam. In an open-cell foam, cells are continuously formed, and when a cross section of the foam is observed, for example, voids are continuously formed from one end of the foam to the other end. In the semi-closed cell foam, although a portion where cells are connected together is present in the foam, the ratio thereof is smaller than that in the open cell foam.

In an open cell foam, sound can propagate through the foam in the voids. However, the sound collides with the frame during its propagation in the gap to generate echo, and the energy is attenuated accordingly. Further, in the vicinity of the boundary between the gap and the skeleton, the energy of sound is attenuated by friction. That is, the open cell foam has sound absorption properties that absorb sound passing therethrough. On the other hand, in the open cell foam, sound can propagate through the voids, and therefore, the sound insulation effect by blocking the intrusion of sound itself is poor.

In the case of the closed cell foam, since sound does not propagate through the air gap as in the open cell foam, the effect of absorbing sound by energy attenuation due to echo and friction is poor, but the sound insulation effect by blocking the passage of sound is better than that of the open cell foam.

In the case of a semi-closed cell foam, the foam has both a sound-insulating effect of absorbing sound by energy attenuation due to echo and friction and a sound-insulating effect of blocking the passage of sound.

If the form of the cells and the sound insulating characteristics thereof described above are to be examined, as the foam constituting the viscoelastic member, a closed cell foam or a semi-closed cell foam is preferable. In the present specification, a semi-closed cell foam is a foam having an open cell content of about 30% to 80%, a foam having an open cell content of less than 30% is referred to as a closed cell foam, and a foam having an open cell content of more than 80% is referred to as an open cell foam. The open cell content can be measured according to ASTM D-2856-87.

Further, as an index for characterizing sound absorption property of absorbing sound by energy attenuation caused by echo and friction when sound propagates in the voids of the foam body, there is an air flow resistance value. It is found that when the viscoelastic member 13A is composed of a foam, or includes a layer composed of a foam, or has an air flow resistance value within a specific rangeNext, excellent sound insulation can be exhibited by a synergistic effect with the beltline sound insulation structure of the automobile of the present invention. The foam preferably has an airflow resistance value of 1.0 × 10 measured at 23 ℃ + -2 ℃ by ISO9053DC method⁴～1.0×10⁸(N·s/m⁴). The air flow resistance of the foam is a value measured when the door glass is opened. Similarly, in the present specification, all of the physical property values of the viscoelastic member are values measured when the door glass is opened.

If the air flow resistance value of the foam is within the above range, the viscoelastic member 13A is sandwiched between the glass plate 11A and the inner panel 21 when the door glass is closed, and in this case, sound is not reflected on the surface of the viscoelastic member 13A and is absorbed, so that the sound insulating property is very good. The air flow resistance value is more preferably 1.0 × 10⁵～1.0×10⁷(N·s/m⁴). The air flow resistance value can be measured, for example, by using an AirReSys (standard ISO9053 DC) flow resistance measurement system manufactured by japan acoustic engineering (japan impact membrane エンジニアリング).

Young's modulus E (N/m) at 20 ℃ of the viscoelastic member 13A²) And a loss coefficient tan. delta. at 20 ℃ and a frequency of 4000Hz preferably satisfies the following formula (1). In the present specification, unless otherwise specified, the Young's modulus represents a value at 20 ℃ and the loss factor represents a value at 20 ℃ and a frequency of 4000 Hz.

[ mathematical formula 1]

Hereinbefore, the young's modulus E is an index representing the hardness of the viscoelastic member 13A, and the loss coefficient tan δ is an index representing the viscosity of the viscoelastic member 13A. When the young's modulus E and the loss coefficient tan δ fall within the range satisfying the above formula (1), the viscoelastic member 13A can exert the effect of preventing sound intrusion and the vibration damping effect on the glass plate 11A with good balance, and has an excellent sound insulating effect.

When the viscoelastic member 13A is made of a single viscoelastic material, the relationship between the young's modulus and the loss absorption of the viscoelastic material preferably satisfies the above expression (1). When the viscoelastic member 13A is made of a plurality of viscoelastic materials, the relationship between the young's modulus and the loss coefficient of each viscoelastic material does not necessarily satisfy the above formula (1), and it is preferable that the relationship between the young's modulus and the loss coefficient of the viscoelastic member 13A made of a plurality of viscoelastic materials satisfies the above formula (1).

The young's modulus E and the loss coefficient tan δ of the viscoelastic member 13A more preferably satisfy the following formula (2), and still more preferably satisfy the following formula (3).

[ mathematical formula 2]

(shape of viscoelastic Member)

The shape of the viscoelastic member 13A is preferably a wedge shape in which the shape of a cross section of the viscoelastic member 13A cut in the up-down direction is tapered toward the upper end thereof when the door glass 1A is opened. In the viscoelastic member 13A shown in fig. 2, the cross-sectional shape is a substantially trapezoidal shape having an upper side smaller than a lower side. The viscoelastic member 13A has a shape different from the cross-sectional shape when the door glass 1A is closed and is sandwiched between the glass plate 11A and the inner panel 21 from the lower portion of the inner seal member 41 to the opening. In this manner, the viscoelastic member 13A forms a constraint-type vibration damping structure that is constrained between the glass plate 11A and the inner plate 21 when the door glass 1A is closed.