JP2001246995A - Impact and vibration energy absorbing member - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a light-weight impact and vibration energy absorbing member capable of absorbing high impact energy caused when a collision occurs and simultaneously reducing the vibration generated in a vibration transmitting member. SOLUTION: This impact and vibration energy absorbing member consists of a housing 1 having one hollow part 1c therein and made of aluminum alloy and a highly rigid foaming elastic body 2 having a minute clearance between a wall face of the housing 1 and it and sealed into a hollow part 1c so as to loosely move. It has high impact energy absorbing capacity because an impact energy absorption amount by the highly rigid foaming elastic body 2 is greatly increased when the collision occurs and an impact is inputted. Moreover, when the vibration is transmitted from the vibration transmitting member and the housing 1 resonates, the foaming elastic body 2 sealed into the hollow part 1c so as to loosely move comes into contact with a wall face of the housing 1 to provide the damping property due to slide friction and energy loss by the collision and effectively suppress the vibration.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a shock and vibration energy absorbing member suitably used for, for example, a bumper of a vehicle, an impact beam of a door, or a panel board forming a passenger compartment.

[0002]

2. Description of the Related Art Conventionally, in a vehicle, various impact absorbing members and shock absorbers have been employed in a vehicle body frame, a panel board, and the like in order to protect the human body by absorbing an impact at the time of a collision. For example, bumper beams for absorbing impact energy at the time of a vehicle collision are attached to the front and rear portions of the body frame. Such a bumper beam is generally formed of a metal such as iron or an aluminum alloy, and has a hollow structure having a hollow portion therein to avoid an increase in weight.

[0003] In order to improve the impact energy absorbing ability of the bumper beam, techniques such as adding a reinforcing plate or increasing the thickness of a metal plate forming the bumper beam have been adopted. In recent years, there has been known a bumper beam in which a hollow portion of a bumper beam is filled with a foamed elastic body such as urethane foam.

On the other hand, in a vehicle equipped with an engine as a power source, vibration is generated by the operation of the engine, and vibration is input from a road surface during traveling. These vibrations are transmitted to the vehicle body through the engine mount bracket and the vehicle body frame that support the engine unit, or the suspension arms and subframes that are connected to the tire wheels. When this occurs, the transmission of vibration to the vehicle body is amplified, and the vehicle interior noise and the vehicle body vibration deteriorate.

Therefore, conventionally, a vibration damper, a dynamic damper, or the like is attached to these vibration transmitting members to suppress the vibration generated in the vibration transmitting members. The vibration damping material is formed in a single-layer or multi-layer sheet-like structure of asphalt, urethane, acrylic resin, metal plate, or the like, and is mainly attached to the surface of a panel-shaped vibration transmission member such as a roof panel or a floor panel. used. The vibration damping material is elastically deformed in accordance with the resonance of the vibration transmitting member, and attenuates the resonance by absorbing the vibration energy of the vibration transmitting member by the internal friction generated at that time.

Further, the dynamic damper has a mounting portion fixed to the vibration transmitting member, a mass (mass body) arranged at a distance from the mounting portion, and interposed between the mass and the mounting portion. This is a vibration absorbing device including a rubber elastic body (spring) that integrally connects the both. The dynamic damper is mounted by fixing the mounting portion to the vibration transmitting member, and the mass-rubber elastic body resonates when the vibration transmitting member resonates, thereby reducing the amplitude of the vibration transmitting member at the time of resonance. Attenuates the resonance.

The dynamic damper and the vibration damping material are not for absorbing impact energy at the time of collision or the like, unlike the bumper beam (impact absorbing member or shock absorber). Further, the bumper beam (shock absorbing member or shock absorber) is not for suppressing the vibration generated in the vibration transmitting member, unlike the dynamic damper and the vibration damping material.

[0008]

By the way, like the above-mentioned conventional bumper beam (impact absorbing member or shock absorber), a reinforcing plate is added or its thickness is increased in order to improve the impact energy absorbing ability. Thickening inevitably causes a significant increase in weight.

Further, since the foamed elastic body such as urethane foam filled in the hollow portion of the bumper beam is a low-density and low-rigidity material, it absorbs the initial impact energy at the time of a collision at a low speed to pedestrians. Although it has the effect of being able to reduce damage such as damage, it does not have high impact energy absorbing ability. Therefore, large impact energy at the time of a collision in high-speed running or the like cannot be sufficiently absorbed by the foamed elastic body, and the plastic deformation of the bumper beam is mainly absorbed. Therefore, in order to improve the impact energy absorbing ability, the thickness of the bumper beam must be increased, which also causes a significant increase in weight.

On the other hand, the vibration damping material used for suppressing the vibration generated in the vibration transmitting member needs to be adhered to a relatively large area of the vibration transmitting member, and a forming material having a relatively high specific gravity is used. Therefore, there is a problem that the weight increases. In addition, since the damping material has a temperature dependency in the damping action, there is a disadvantage that when tuned at room temperature, the damping effect is reduced at high or low temperatures.

In addition, since the resonance frequency of the dynamic damper is determined by the weight of the mass and the spring constant of the rubber elastic body, the dynamic damper exhibits a vibration damping effect only in one frequency region of resonance generated in the vibration transmitting member. can do. Therefore, it is not effective for a plurality of resonances. Further, since the weight of the mass and the spring constant of the rubber elastic body are set on the basis of the direction in which they act (vibration direction) from the positional relationship between the mass and the rubber elastic body, they have directionality. Therefore, it is difficult to simultaneously control vibrations in multiple directions with one dynamic damper. Further, a rubber elastic body used as a spring has a problem that the spring constant tends to change with temperature and is highly temperature-dependent, so that the vibration damping effect decreases at high or low temperatures.

The present invention has been devised in view of the above situation, and has a light impact and vibration that can simultaneously achieve high absorption of impact energy at the time of collision and reduction of vibration generated in the vibration transmitting member. It is an object to provide an energy absorbing member.

[0013]

According to a first aspect of the present invention, there is provided an impact and vibration energy absorbing member according to the first aspect of the present invention, comprising: a housing made of a rigid material having at least one hollow portion therein; And a high-rigidity foamed elastic body movably sealed in the hollow portion with a small gap between the wall and the wall forming the hollow portion.

In the shock and vibration energy absorbing member of the present invention, when a shock is applied to the member during a collision or the like, the housing is deformed while being elastically supported by the highly rigid foamed elastic body. Therefore, the amount of impact energy absorbed by the foamed elastic body is greatly increased, so that the amount of impact energy absorbed by the housing can be relatively reduced. This allows
By reducing the thickness of the housing or the like, a sufficient weight reduction can be realized, and a high impact energy absorbing ability at the time of a collision can be secured.

In the shock and vibration energy absorbing member of the present invention, when the vibration is transmitted from the vibration transmitting member and the housing resonates, the foamed elastic body movably sealed in the hollow portion of the housing comes into contact with the wall surface of the housing. (Abutment)
However, damping is exhibited by energy loss due to sliding friction and collision. Thereby, a large damping property is generated inside the housing, and vibration of the housing is effectively suppressed. As a result, the vibration of the vibration transmitting member is effectively suppressed.

In this shock and vibration energy absorbing member, damping is exerted based on sliding friction when the foamed elastic body contacts (contacts) the inner surface of the housing and energy loss due to collision. Therefore, effective damping can be obtained even for a plurality of resonances having different frequencies. Further, since the amount of energy loss due to sliding friction and collision as in the present invention is less affected by temperature, the vibration damping action has no temperature dependence.

Further, in this shock and vibration energy absorbing member, the gap formed between the wall surface of the housing and the foamed elastic body can be freely set in accordance with the vibration direction of the housing (the vibration direction of the vibration transmission member). In addition, it is possible to control the vibration of the housing in all directions.

When the housing is reduced in weight, when the input vibration is constant, the vibration of the housing increases due to the reduction of the inertial force. By arranging the foamed elastic body with a gap in the hollow part to attenuate the vibration, the weight of the housing can be reduced without causing deterioration of the vibration.

Therefore, according to the shock and vibration energy absorbing member of the present invention, it is possible to simultaneously absorb high shock energy at the time of collision and to reduce the vibration generated in the vibration transmitting member, and also realize a reduction in weight. can do.

The shock and vibration energy absorbing member of the present invention can be embodied by the following means.

The housing of the present invention is formed of a metal material such as an iron or aluminum alloy. As the iron-based material, for example, general materials such as carbon steel, alloy steel, cast steel, and cast iron can be used. Examples of aluminum alloy-based materials include Al-Mn-based materials and Al-
General materials such as Si-based, Al-Mg-based, and Al-Cu-Mn-based can be employed. In particular, strength and corrosion resistance,
From the viewpoint of specific gravity, workability, etc., for example, A6063 (JIS)
Al-Mg-Si based aluminum alloys such as A6061 (JIS) and the like are preferably used. Note that the housing can be formed of a synthetic resin material.

The housing may have any shape such as a cylindrical shape or a rectangular tube shape, and is not limited to a linear shape, but may be a curved shape or a bent shape. When the housing is cylindrical, a molded material formed by a simple method such as extrusion molding can be used.
This housing preferably has an elastic modulus of 5 × 10 ³ Mpa or more. If the elastic modulus is smaller than 5 × 10 ³ Mpa, the rigidity of the housing becomes insufficient, and the gap formed between the elastic body and the foamed elastic body sealed in the hollow portion becomes unstable.

Further, the hollow portion formed inside the housing does not necessarily have to be formed in a closed shape. The hollow portion of the housing can have a plurality of hollow portions by providing a partition wall in the internal space. As described above, by providing a plurality of hollow portions in which the foamed elastic body is sealed, the vibration damping effect can be improved. In addition, the provision of the partition wall increases the rigidity of the housing, which is advantageous in reducing the weight of the housing. Note that the thickness of the housing is preferably 2 mm or less. Thereby, the weight of the housing can be reliably reduced.

Incidentally, the housing of the present invention can be configured to have a bracket for fixing to the vibration transmitting member. In the case where the vibration transmitting member or the like to which the shock and vibration energy absorbing member of the present invention is to be attached has an appropriate hollow portion capable of enclosing the foamed elastic body, or if an appropriate hollow portion can be provided, A vibration transmitting member or the like can be used as a housing.

As the foamed elastic body of the present invention, those having high rigidity are employed in order to secure a sufficiently high impact energy absorbing ability, and those having a density of 0.2 to 0.5 g / cm ³ are suitably employed. Is done. When the density is less than 0.2 g / cm ³ ,
Sufficiently high rigidity of the foamed elastic body cannot be obtained, and it is difficult to secure a sufficiently high impact energy absorbing ability. Conversely, if the density exceeds 0.5 g / cm ³ , the rigidity of the foamed elastic body becomes too high, and a sufficiently large elastic deformation becomes impossible.

The foamed elastic body has a critical compression ratio of 60%.
Those capable of large elastic deformation as described above are suitably employed. If the critical compression ratio is less than 60%, large elastic deformation of the foamed elastic body becomes impossible, and the foamed elastic body is easily broken. Here, the critical compression ratio refers to a state where the foamed elastic body is elastically deformed without being broken when a foamed elastic body having a predetermined size (50 mm × 50 mm × 50 mm) is pressed from both sides and compressed. And a value obtained by [(amount of compression displacement of the foamed elastic body when the foamed elastic body is broken) / (distance in the compression direction of the foamed elastic body before compression) × 100]. It is.

The foamed elastic material preferably has an impact energy absorption of 400 kN · mm or more per 25 cm ² . The foamed elastic body preferably has a compression elastic modulus of about 150 MPa, and is preferably 100 to 300 MPa in view of the thickness and strength of the housing.
The compression elastic modulus can be appropriately set in the range of a.

The foamed elastic body of the present invention is sealed in the hollow part of the housing in a non-adhesive manner with a small gap between the elastic body and the wall surface forming the hollow part of the housing. That is, the foamed elastic body is arranged in a movable state in the hollow portion of the housing. In this case, the gap formed between the wall surface of the housing and the foamed elastic body is preferably 1 mm or less. If the gap exceeds 1 mm, the impact noise and abnormal noise generated when the foamed elastic body and the housing come into contact (contact) with each other increase.

The minimum gap ratio of the gap formed between the wall surface of the housing and the foamed elastic body is preferably 30% or less. When the minimum gap ratio exceeds 30%, when the housing vibrates with a particularly small amplitude, the foamed elastic body does not easily contact (contact) the inner surfaces on both sides in the vibration direction of the housing, and a good vibration suppression effect can be obtained. Because it is gone. In addition, the minimum gap ratio here means that, in a state where one surface of the foamed elastic body is in contact with the wall surface of the housing, the most protruding portion of the opposite surface of the foamed elastic body and the wall surface of the housing facing the same. It means the ratio obtained by dividing the distance dimension of the gap formed between them by the distance dimension between the wall surfaces of the housing.

The foamed elastic body of the present invention has a surface portion A
Shore D hardness of STM standard D2240 should be 80 or less
Is preferred. Further, the foamed elastic body has a compression elastic modulus of 1 to 1.
10 ^ThreeMpa, tan δ (loss tangent) is 10^-3Above, good
Preferably, those having characteristics of about 0.01 to 10 are preferred.
New

The foamed elastic body of the present invention can be formed by foaming a foamed elastic body forming material containing at least one of rubber and resin and a foaming agent as main components.
The expansion ratio in this case is 2 to 2 so that the density of the foamed elastic body after foaming is 0.2 to 0.5 g / cm ³ .
It is preferable to make it about five times. The foamed elastic body, which is singly formed in an appropriate size so that a gap is formed between the foamed elastic body and the wall surface of the housing, can be inserted into the hollow portion of the housing and arranged. Further, the foamed elastic body forming material may be arranged in the hollow portion by foaming the material in the hollow portion of the housing. In this case, a gap can be formed between the foamed elastic body foamed in the hollow portion of the housing and the wall surface of the housing by utilizing the heat shrinkage after foaming. Therefore, according to this method, since the foamed elastic body forming material can be foamed in the hollow portion of the housing and the foamed elastic body can be arranged in the hollow portion, the number of work steps can be reduced and simplified. .

As the rubber material forming the foamed elastic body,
For example, diene rubbers such as acrylonitrile-butadiene rubber (NBR) and styrene-butadiene rubber (SBR), natural rubber (NR), and the like can be suitably used.

Further, as the resin material, for example, a phenol type, an epoxy type, a urethane type or the like can be suitably used. Representative examples of particularly suitable urethanes include polyols having an average hydroxyl value (OHV) of 100 or more (polyethers, polyesters, caprolactones, polycarbonates, polyolefins, castor oils, etc.). One or a blend of two or more of them can be employed.

Examples of the foaming agent include inorganic foams such as sodium hydrogencarbonate, ammonium carbonate and ammonium hydrogencarbonate, and organic foams such as diazoamine derivatives, azonitrile derivatives, azodicarboxylic acid derivatives, and dinitrosopentamethylenetetramine. Can be mentioned.

In addition, the foamed elastic body forming material includes, in addition to the above-mentioned main components, a vulcanizing agent, a crosslinking agent, a plasticizer, a filler, a flame retardant, a hydrolysis inhibitor, a catalyst, and a foam stabilizer as required. Etc. can be added as appropriate.

[0036]

Embodiments of the present invention will be described below with reference to the drawings.

[Embodiment 1] FIG. 1 is a sectional view of an impact and vibration energy absorbing member according to the present embodiment, and FIG. 2 is a sectional view taken along line II-II of FIG.

The shock and vibration energy absorbing member of this embodiment is, as shown in FIGS. 1 and 2, between an aluminum alloy housing 1 having one hollow portion 1c therein and a wall surface of the housing 1. Highly rigid foamed elastic body 2 movably sealed in hollow portion 1c with minute gap S
And is composed of

The housing 1 comprises a main body 1a having a substantially constant thickness and formed in a rectangular cylindrical shape, and plug members 1b and 1b respectively joined to both ends of the main body 1a to seal the openings. A hollow portion 1c is formed inside. The main body 1a is made of an Al-Mg-Si based aluminum alloy (A6
063 (JIS)). The plug members 1b and 1b are formed of an aluminum alloy of the same material as the main body 1a. The housing 1 has an elastic modulus of 5 × 10 ⁴ Mpa or more.

The foamed elastic body 2 is made of urethane foam, and is a mixture of a polyol as a resin material, a foaming agent, a catalyst, a foam stabilizer, a flame retardant, a filler and the like in appropriate amounts. Is formed by reacting with isocyanate and foaming. This foamed elastic body 2 has a density of 0.36 g / cm ³ and a critical compressibility of 60%.
As described above, the compression elastic modulus is 171 MPa and the impact energy absorption is 733 kN · mm. The foamed elastic body 2 is formed in a prism shape having a size slightly smaller than the hollow portion 1c of the housing 1, and is sealed in the hollow portion 1c of the housing 1 in a non-adhesive manner. Thereby, the distance between the inner wall surface of the housing 1 and the foamed elastic body 2 is 0.3 mm.
A small gap S is formed, and the foamed elastic body 2 is arranged so as to be freely movable in the hollow portion 1c.

The shock and vibration energy absorbing member of the present embodiment configured as described above is used by being attached to a bumper beam 7 of a vehicle, as shown in FIGS.
The bumper beam 7 is formed of a long extruded material made of an aluminum alloy, and is curved in an arc shape by being entirely bent. On the front side where an impact is input at the time of collision of the bumper beam 7, three hollow portions 7 extending in the longitudinal direction and formed in a vertical direction are provided.
a, 7b and 7c are provided. The shock and vibration energy absorbing member of the present embodiment is formed so as to have a sectional shape slightly smaller than the sectional shape of the central hollow portion 7b, and the hollow portion is formed before the bumper beam 7 is bent. 7b, it is arranged at the center of the hollow portion 7b.

When a large impact is applied to the bumper beam 7 on which the impact and vibration energy absorbing member is attached by collision or the like, the foamed elastic body 2 is compressed while the housing 1 is plastically deformed together with the bumper beam 7. Due to the elastic deformation, the impact energy is effectively absorbed. At this time, since the foamed elastic body 2 has a density of 0.36 g / cm ³ and a critical compressibility of 60% or more, the rigidity is high and large elastic deformation is possible. A high impact energy absorbing ability is exhibited. Therefore, since the amount of impact energy absorbed by the housing 1 can be relatively reduced, the present embodiment uses the housing 1 having a sufficiently small thickness, thereby achieving a sufficient weight reduction. I have.

When the housing 1 resonates due to the vibration transmitted to the bumper beam 7 during running of the vehicle or the like, the foamed elastic body 2 comes into contact with (abuts) the inner wall surfaces on both sides in the vibration direction of the housing 1, causing sliding friction. Also, due to energy loss due to collision, attenuating properties are exhibited for a plurality of resonances having different frequencies. As a result, a large damping property is generated inside the housing 1 and the vibration of the housing 1 is effectively suppressed, so that the vibration of the bumper beam 7 is effectively suppressed.

In this shock and vibration energy absorbing member, a gap S is formed between the foamed elastic body 2 sealed in the hollow portion 1c of the housing 1 and the inner wall surface of the housing 1 in all directions. So that
Vibrations in all directions of the housing 1 (bumper beam 7) are effectively suppressed.

As described above, the shock and vibration energy absorbing member of the present embodiment has a small gap S between the highly rigid foamed elastic body 2 and the wall surface forming the hollow portion 1c of the housing 1.
, Which is movably sealed in the hollow portion 1c, so that it is possible to simultaneously absorb high impact energy and reduce vibration generated in the bumper beam 7 (vibration transmitting member) at the time of collision, and Lightening can also be achieved.

Embodiment 2 FIG. 5 is a sectional view of an impact and vibration energy absorbing member according to the present embodiment, and FIG. 6 is a sectional view taken along the line VI-VI of FIG.

As shown in FIGS. 5 and 6, the shock and vibration energy absorbing member according to the present embodiment includes a housing 11 made of an aluminum alloy having three hollow portions 11c, 11c, 11c therein, and a wall surface of the housing 11. And a high-rigidity foam elastic body 12 movably sealed in the hollow portion 11c with a small gap S therebetween.

The housing 11 is formed in an irregular cylindrical shape with a substantially constant thickness, and has three hollow portions 11c, 11c, 11c inside.
And a plug member 11b, 11b joined to both ends of the main body portion 11a and sealing the opening of one hollow portion 11c. The main body 11a is made of Al-
Mg-Si based aluminum alloy (A6063 (JI
It is formed of an extruded material made of S)).
The inner space of the main body 11a is divided into three hollow portions 11c, 11c, 1c extending in the extrusion direction by two partition walls 11f, 11f formed along the extrusion direction during extrusion molding.
1c. Also, plug members 11b, 11b
Is formed of an aluminum alloy of the same material as the main body 11a. This housing 11 has an elastic modulus of 5 ×
It is 10 ⁴ Mpa or more.

The foamed elastic body 12 is made of foamed urethane formed by foam molding in the same manner as in the first embodiment. This foamed elastic body 12 has a density of 0.36
g / cm ³ , the critical compression rate is 60% or more, and the compression modulus is 1
It has a characteristic of 71 MPa and an impact energy absorption of 733 kN · mm. The foamed elastic body 12 is formed in a block shape having a size slightly smaller than the hollow portion 11c of the housing 11, and
It is sealed in non-adhesively in c. Thereby, the distance between the inner wall surface of the housing 11 and the foamed elastic body 12 is 0.3 mm.
A small gap S is formed, and the foamed elastic body 12 is arranged so as to be freely movable in the hollow portion 11c.

As shown in FIGS. 3 and 7, the shock and vibration energy absorbing members of the present embodiment configured as described above are attached to the left and right ends of the bumper beam 7 used in the first embodiment, respectively. Used as a crash box. In this shock and vibration energy absorbing member, the hollow portion 11c in which the foamed elastic body 12 is sealed is located on the center side of the bumper beam 7, and the hollow portions 11c, 11c, 11c
Are fixed to the rear surface of the bumper beam 7 so as to extend in the vertical direction.

When a large impact is applied to the bumper beam 7 on which the shock and vibration energy absorbing member is attached by collision or the like, the foamed elastic body 12 is compressed while the housing 11 is plastically deformed together with the bumper beam 7. Due to the elastic deformation, the impact energy is effectively absorbed. At this time, since the foamed elastic body 12 has a density of 0.36 g / cm ³ and a critical compression ratio of 60% or more, the rigidity is high and large elastic deformation is possible. A high impact energy absorbing ability is exhibited. For this reason, the amount of impact energy absorbed by the housing 11 can be relatively reduced. Therefore, in the present embodiment, the housing 11 having a sufficiently small thickness is used, thereby achieving a sufficient weight reduction. I have.

When the housing 11 resonates due to the vibration transmitted to the bumper beam 7 during running of the vehicle or the like, the foamed elastic body 12 comes into contact with (abuts) the inner surfaces on both sides of the housing 11 in the vibration direction, and the sliding friction and Due to the energy loss due to the collision, a damping property is exhibited for a plurality of resonances having different frequencies. Thereby, a large damping property is generated inside the housing 11 and the vibration of the housing 11 is effectively suppressed, so that the vibration of the bumper beam 7 is effectively suppressed.

In this shock and vibration energy absorbing member, a gap S is formed between the foamed elastic body 12 sealed in the hollow portion 11c of the housing 11 and the inner wall surface of the housing 11 in all directions. As a result, the vibration of the housing 11 (bumper beam 7) in all directions is effectively suppressed.

As described above, the shock and vibration energy absorbing member of the present embodiment has the minute gap S between the highly rigid foamed elastic body 12 and the wall surface forming the hollow portion 11c of the housing 11. Since it is movably sealed in the hollow portion 11c, it is possible to simultaneously absorb high impact energy and reduce vibration generated in the bumper beam 7 (vibration transmitting member) at the time of collision, and to reduce the weight. Can be realized.

[Embodiment 3] FIG. 8 is a cross-sectional view of a shock and vibration energy absorbing member according to the present embodiment.
FIG. 9 is a sectional view taken along line II-VIII, and FIG. 9 is a plan view of the shock and vibration energy absorbing member.

As shown in FIGS. 8 and 9, the shock and vibration energy absorbing member of this embodiment includes an iron housing 21 having one hollow portion 21c therein, and a housing 2 having a hollow portion 21c.
And a highly rigid foamed elastic body 22 movably sealed in a hollow portion 21c with a small gap S between itself and the first wall surface.

The housing 21 has a first member 23 comprising a concave portion 23a extending in the longitudinal direction and having a U-shaped cross section, and a pair of flat portions 23b, 23b extending outward at right angles from both ends of the concave portion 23a. A flat plate-shaped second member 24 joined to both flat portions 23b, 23b by forming a hollow portion 21c between the recessed portion 23a of the first member 23 and a recessed portion 2 of the first member 23
Plug members 25, 25 respectively joined to both ends of 3a and sealing the opening of the hollow portion 21c. The first member 23 and the second member 24 are made of an iron plate (SPCE (J
IS)). This housing 21
Has an elastic modulus of 5 × 10 ⁴ Mpa or more.

The foamed elastic body 22 is made of foamed urethane formed by foam molding in the same manner as in the first embodiment. This foamed elastic body 22 has a density of 0.36.
g / cm ³ , the critical compression rate is 60% or more, and the compression modulus is 1
It has a characteristic of 71 MPa and an impact energy absorption of 733 kN · mm. The foamed elastic body 22 is formed in the shape of a prism having a size slightly smaller than the hollow portion 21 c of the housing 21, and is sealed in the hollow portion 21 c of the housing 21 without adhesion. Thereby, the housing 21
A gap S of about 0.3 mm is formed between the inner wall surface of the elastic member 22 and the foamed elastic body 22, and the foamed elastic body 22 is
It is arranged so as to be able to move inside c.

As shown in FIG. 10, the shock and vibration energy absorbing member of the present embodiment constructed as described above has a concave portion 8a having a U-shaped cross section extending in the longitudinal direction and a right angle outward from both ends of the concave portion 8a. A pair of flat portions 8b, 8 extending in the direction
b. In this case, the shock and vibration energy absorbing member is configured such that the recesses 23a of the housing 21 are fitted into the recesses 8a of the front frame 8, and the two flat portions 23b, 23b of the housing 21 and the two flat portions 8b of the front frame 8,
8b by welding.

When a large impact is applied to the front frame 8 on which the shock and vibration energy absorbing member is attached in this manner, due to a collision or the like, the housing 21 is plastically deformed together with the front frame 8 and the foamed elastic body 2 is formed.
2 is elastically deformed while being compressed, so that its impact energy is effectively absorbed. At this time, the foamed elastic body 2
No. 2 has a density of 0.36 g / cm ³ and a critical compressibility of 60% or more, so that it has high rigidity and is capable of large elastic deformation. Is exhibited. Therefore, the housing 2
In this embodiment, the housing 21 having a sufficiently small thickness is used because the amount of impact energy absorbed by 1 can be relatively reduced, thereby achieving a sufficient reduction in weight.

When the housing 21 resonates due to the vibration transmitted to the front frame 8 during running of the vehicle or the like, the foamed elastic body 22 comes into contact with (abuts) the inner surfaces on both sides of the housing 21 in the vibration direction, and the sliding friction occurs. Also, due to energy loss due to collision, attenuating properties are exhibited for a plurality of resonances having different frequencies. As a result, a large damping property is generated inside the housing 21 and the vibration of the housing 21 is effectively suppressed, so that the vibration of the front frame 8 is effectively suppressed.

In this shock and vibration energy absorbing member, a gap S is formed between the foamed elastic body 22 sealed in the hollow portion 21c of the housing 21 and the inner wall surface of the housing 21 in all directions. As a result, the vibration of the housing 21 (the front frame 8) in all directions is effectively suppressed.

As described above, the shock and vibration energy absorbing member of the present embodiment has the minute gap S between the highly rigid foamed elastic body 22 and the wall surface forming the hollow portion 21c of the housing 21. Since it is movably sealed in the hollow portion 21c, it is possible to simultaneously absorb high impact energy at the time of collision and reduce vibration generated in the front frame 8 (vibration transmitting member), and to reduce the weight. Can also be realized.

[Embodiment 4] FIG. 11 is a plan view showing a part of a shock and vibration energy absorbing member according to this embodiment in a cutaway section, and FIG. 12 is a sectional view taken along line XII-XII in FIG. FIG. 13 is a sectional view taken along the line XIII-XIII in FIG.
It is sectional drawing cut | disconnected along the line.

As shown in FIGS. 11 to 13, the shock and vibration energy absorbing member of the present embodiment is a housing 31 made of an aluminum alloy having one hollow portion 31c therein.
And a highly rigid foamed elastic body 32 movably sealed in a hollow portion 31c with a small gap S between the wall surface of the housing 31.

The housing 31 is formed in a cylindrical shape with a substantially constant thickness and has a main body portion 31a having a hollow portion 31c therein.
And a hollow portion 3 joined to both ends of the main body portion 31a.
It comprises plug members 31b, 31b for sealing the opening of 1c, and a pair of flat plate-like bracket portions 31d, 31d extending in opposite directions on the same plane from the outer periphery of the main body portion 31a. Main body 31a and brackets 31d, 31
d is an Al-Mg-Si based aluminum alloy (A60
63 (JIS)). The plug members 31b, 31b are formed of an aluminum alloy of the same material as the main body 31a. In addition, through holes 33 into which mounting bolts and the like are inserted are provided at both ends of each bracket portion 31d. The housing 31 has an elastic modulus of 5 × 10
More than ⁴ Mpa.

The foamed elastic body 32 is made of urethane foam formed by foam molding in the same manner as in the first embodiment. This foamed elastic body 32 has a density of 0.36
g / cm ³ , the critical compression rate is 60% or more, and the compression modulus is 1
It has a characteristic of 71 MPa and an impact energy absorption of 733 kN · mm. The foamed elastic body 32 is formed in a block shape having a size slightly smaller than the hollow portion 31c of the housing 31, and the hollow portion 31 of the housing 31 is formed.
It is sealed in non-adhesively in c. Thereby, the distance between the inner wall surface of the housing 31 and the foamed elastic body 32 is 0.3 mm.
A small gap S is formed, and the foamed elastic body 32 is arranged so as to be freely movable in the hollow portion 31c.

The shock and vibration energy absorbing member of the present embodiment configured as described above is mounted on the center pillar (not shown) constituting the body frame of the vehicle by each bracket 3.
1d and 31d are attached and used by fixing them with bolts or the like.

When a large impact is input to the center pillar on which the impact and vibration energy absorbing member is attached in this manner, the impact is applied to the housing 3 together with the center pillar.
The foamed elastic body 32 is elastically deformed while being compressed with the plastic deformation of 1, so that its impact energy is effectively absorbed. At this time, since the foamed elastic body 32 has a density of 0.36 g / cm ³ and a critical compressibility of 60% or more, the rigidity is high and large elastic deformation is possible. A high impact energy absorbing ability is exhibited. Therefore, since the amount of impact energy absorbed by the housing 31 can be relatively reduced, the present embodiment uses the housing 31 with a sufficiently small wall thickness, thereby achieving a sufficient weight reduction. I have.

When the housing 31 resonates due to the vibration transmitted to the center pillar when the vehicle is running or the like, the foamed elastic body 32 contacts (contacts) the inner surfaces on both sides of the housing 31 in the vibration direction, and the sliding friction and Due to the energy loss due to the collision, a damping property is exhibited for a plurality of resonances having different frequencies. Thereby, a large damping property is generated inside the housing 31 and the vibration of the housing 31 is effectively suppressed, so that the vibration of the center pillar is effectively suppressed.

In this shock and vibration energy absorbing member, a gap S is formed between the foamed elastic body 32 sealed in the hollow portion 31c of the housing 31 and the inner wall surface of the housing 31 in all directions. As a result, the vibration of the housing 31 (center pillar) in all directions is effectively suppressed.

As described above, the shock and vibration energy absorbing member of the present embodiment has the minute gap S between the highly rigid foamed elastic body 32 and the wall surface forming the hollow portion 31c of the housing 31. Since it is movably sealed in the hollow portion 31c, it is possible to simultaneously absorb high impact energy and reduce vibration generated in the center pillar (vibration transmitting member) at the time of collision, and to reduce the weight. Can be realized.

[Embodiment 5] FIG. 14 is a plan view showing a part of a shock and vibration energy absorbing member according to the present embodiment in a cutaway section, and FIG. 15 is cut along the line XV-XV in FIG. FIG.

As shown in FIGS. 14 and 15, the shock and vibration energy absorbing member of this embodiment comprises a housing 41 made of an aluminum alloy having a large number of hollow portions 41c,. Are formed in the respective hollow portions 41c,... With a small gap S therebetween, and are slidably sealed in the respective hollow portions 41c,.

The housing 41 is formed in a plate shape with a substantially constant thickness and has a plurality of hollow portions 41c,... Inside thereof, and a main body portion 41a which is joined to both ends of the main body portion 41a to form respective hollow portions 11c. Plug members 41b, 41b for sealing the openings
Consists of The main body 41a is formed of an extruded material made of an Al-Mg-Si-based aluminum alloy (A6063 (JIS)). The interior space of the main body 41a is divided into a large number of hollow portions 41c extending in the extrusion direction by a plurality of partition walls 41f formed along the extrusion direction during extrusion molding. Further, the plug members 41b, 41b are formed of an aluminum alloy of the same material as the main body 41a. This housing 41
Has an elastic modulus of 5 × 10 ⁴ Mpa or more.

The foamed elastic members 42,...
And urethane foam formed by foam molding. The foamed elastic bodies 42 have a density of 0.36 g / cm ³ , a critical compressibility of 60% or more, a compressive elasticity of 171 MPa, and an impact energy absorption of 733.
It has a characteristic of kN · mm. The foamed elastic bodies 42 are formed in a flat plate shape having a size slightly smaller than the hollow portions 41c of the housing 41, and are sealed in the hollow portions 41c of the housing 41 without adhesion. Have been. Thus, a gap S of about 0.3 mm is formed between the inner wall surface of the housing 41 and each foamed elastic body 42,..., And each foamed elastic body 42,. It is arranged so as to be able to move inside.

The shock and vibration energy absorbing member of the present embodiment configured as described above is used as a body panel for forming a compartment such as a dash panel, a roof panel, and a floor panel of a vehicle. In this case, although the housing 41 of the present embodiment is formed in a flat plate shape, a bending process or the like is appropriately performed so as to conform to a panel shape of a part to be used.

When a large shock is applied to the shock and vibration energy absorbing member mounted as the body panel due to a collision or the like, the foamed elastic bodies 42 are compressed while the housing 41 is plastically deformed. Due to the elastic deformation, the impact energy is effectively absorbed. At this time, the foamed elastic bodies 42,.
6 g / cm ³ and a critical compression ratio of 60% or more, so that the rigidity is high and large elastic deformation is possible, so that the foamed elastic bodies 42,. . For this reason, the amount of impact energy absorbed by the housing 41 can be relatively reduced. In this embodiment, the housing 41 having a sufficiently small thickness is used, and thus a sufficient weight reduction is realized. I have.

When the housing 41 resonates due to the vibration transmitted to the body panel during running of the vehicle or the like, the foamed elastic bodies 42 contact the inner surfaces on both sides of the housing 41 in the vibration direction. In addition, a damping property is exhibited for a plurality of resonances having different frequencies due to energy loss due to sliding friction and collision. Thereby, the housing 41
Of the housing 41 is effectively suppressed, and the vibration of the center pillar is effectively suppressed.

In this shock and vibration energy absorbing member, the foamed elastic bodies 42,... Enclosed in the hollow portions 41c,. Are arranged so as to form the gap S, so that vibrations of the housing 41 (body panel) in all directions are effectively suppressed.

As described above, the shock and vibration energy absorbing member of the present embodiment is characterized in that the highly rigid foamed elastic bodies 42 are minutely arranged between the housing 41 and the wall surface forming the hollow portions 41c. Since each of the hollow portions 41c has a gap S and is movably sealed in the hollow portions 41c, it simultaneously achieves high absorption of impact energy and reduction of vibration generated in the body panel (vibration transmitting member) at the time of collision. And lightening can be realized.

[Test 1] A test was conducted to confirm that the shock and vibration energy absorbing member of the present invention had excellent shock energy absorbing ability.

As Embodiment 1, as shown in FIGS. 16 and 17, three hollow portions 51c, 51c having both ends opened,
Aluminum alloy housing 51 having 51c
An impact-absorbing member composed of a foamed elastic body 52 filled in a hollow portion 51c at the center of the housing 51 was prepared. The housing 51 is entirely formed with a thickness of about 1.2 mm, and has a length (L1): 60 mm and a width (W1):
115 mm, thickness (T1): 60 mm.
The width (W2) of the central hollow portion 51c is 45.4 m.
m, the width (W3) of the hollow portions 51c on both sides is 3
2.4 mm. Note that no gap is formed between the foamed elastic body 52 disposed in the hollow portion 51c and the inner wall surface of the housing 51.

As comparative examples, three types of shock absorbing members (Comparative Examples 1 to 3) were prepared which consisted only of an aluminum alloy housing which was not filled with a foamed elastic body and had variously changed thicknesses of the housing. In Comparative Examples 1 to 3, the same material as the housing 1 of Example 1 was formed in the same rectangular tube shape. Comparative Example 1 has a wall thickness of 1.8 mm and a total weight of 1.4 N (0.14 kg). Comparative Example 2 has a thickness of 2.5 mm and a total weight of 2.0 N (0.20 kg). Comparative Example 3 had a thickness of 3.0 mm and a total weight of 2.3 N.
(0.23 kg). In Example 1, the thickness was 1.2 mm and the total weight was 1.5 N (0.15 kg).

In order to examine the compression characteristics of Example 1 and Comparative Examples 1 to 3,
When a compressive load was applied in the thickness direction and the displacement (mm) and the load (kN) at that time were measured, the results shown in FIG. 18 were obtained. In FIG. 18, the amount of impact energy absorption in each of Example 1 and Comparative Examples 1 to 3 corresponds to the area of a region surrounded by each characteristic curve and the horizontal axis indicating the amount of displacement.

As is clear from FIG. 18, in Comparative Examples 1 to 3 in which the foamed elastic body is not filled, the larger the thickness of the housing, the larger the amount of impact energy absorption. . On the other hand, it can be seen that Example 1 in which the foamed elastic body is filled has a larger amount of impact energy absorption than Comparative Example 3 among Comparative Examples 1 to 3, which has the largest amount of impact energy absorption. Thus, it can be understood that a higher impact energy absorbing ability can be secured by filling the inside of the housing with the foamed elastic body than by increasing the thickness of the housing.

In Comparative Examples 1 to 3, in the initial stage of the input of the compressive load, the load value suddenly increased and then decreased rapidly, indicating that the buckling occurred at those peaks. ing. In this case, the thicker the housing, the larger the buckling load. The buckling load of the thickest comparative example 3 (about 52 kN) is the buckling load of the thinnest comparative example 1. (About 22 kN). That is, it can be seen that Comparative Example 3 has higher buckling strength and higher impact energy absorbing ability than Comparative Examples 1 and 2.

On the other hand, in the case of the first embodiment, the sudden increase in the load value in the initial stage of the input of the compression load
After the load value increased to approximately the same value as that of Comparative Example 1 (about 22 kN), the displacement amount was 2
Until it is close to 0 mm, it keeps almost the same value without descending. This is because the housing is deformed while being elastically supported by the foamed elastic body and is not buckled because the foamed elastic body having high rigidity and large deformation is filled in the hollow portion of the housing.

Further, thereafter, the load value of the first embodiment gradually rises, rapidly rises from the vicinity where the displacement amount is 35 mm, reaches a peak when the displacement amount exceeds 40 mm,
Immediately after that, the compression deformation of the first embodiment is completed by suddenly descending. That is, the load value of the first embodiment is such that the displacement amount is about 7 to 4
In the range of 0 mm, the load value is always higher than the load value of Comparative Example 3, and the difference gradually increases as the displacement amount increases. Thus, the first embodiment
Large impact energy absorption capacity is secured.

The load value of Comparative Example 3 was about
From around 8 mm, it rises sharply and the displacement is 4
The peak reaches around 5 mm, and immediately after that, the pressure rapidly drops and the compression deformation of Comparative Example 3 is completed. Therefore, in the case of Comparative Example 3, a large impact energy absorption amount can be obtained in the range where the displacement amount is about 38 to 45 mm. However, the total impact energy absorption amount of Comparative Example 3 is the total impact energy absorption amount of Example 1. Energy absorption has not been exceeded.

As described above, the first embodiment in which the foamed elastic body is filled in the hollow portion of the housing is the same as the comparative example 1.
It can be seen that despite having a thinner housing than 肉 3, it has a high impact energy absorbing capacity. Therefore, in Example 1 in which the foamed elastic body is filled and arranged, compared with Comparative Examples 1 to 3 having no foamed elastic body, it is possible to significantly improve the impact energy absorbing capacity without increasing the weight so much. it can. As in Comparative Example 3, even if the thickness of the housing is increased so that the total weight exceeds that of Example 1, it is not possible to obtain a high impact energy absorbing ability as in Example 1.

[Test 2] Test Examples 1 to 6 were prepared by changing the density of the foamed elastic body (urethane foam) used in Example 1 in various ways, and a test for examining their static compression characteristics was performed. went. Test Examples 1 to 6 were 5
It is formed in a block shape having a size of 0 mm × 50 mm × 50 mm, and the foaming elastic bodies to be formed each have a predetermined density by changing the foaming ratio at the time of foam molding. The density of Test Examples 1 to 6 is
It is as described in Table 1.

For each of Test Examples 1 to 6, a test was performed by pressing both surfaces to compress the plate until the displacement amount became 30 mm (compression rate 60%), and the compression elastic modulus, critical compression rate, and absorbed energy (60 % Compression) and the results are shown in Table 1. The critical compression ratio shown in Table 1 indicates the compression ratio when the foamed elastic body breaks, but when the displacement amount is 30 mm (compression ratio is 60%), it is not broken. Is described as “60 ≦”. Also,
The load-displacement curves of Test Examples 1 to 5 during the compression test are shown in FIG. 19, and the load-displacement curves of Test Example 6 are shown in FIG.

[0094]

[Table 1]

As is clear from Table 1, as for the compressive elastic modulus, the higher the density, the higher the value. Naturally, Test Example 1 with the lowest density shows the lowest value (30.7 MPa). Test example 6 with the highest density
Showed the largest value (1421.0 MPa). The compression modulus of Test Example 6 is about 5 times that of Test Example 5, which shows the closest value, and is dramatically increased. Therefore, it is understood that Test Example 6 has extremely high rigidity.

Further, as to the critical elastic modulus, Test Examples 1 to
5 was 60% or more in each case, and only Test Example 6 was 55%.
Met. Therefore, Test Example 6 has a narrower range in which elastic deformation is allowed than Test Examples 1 to 5.

Table 1 shows the amount of energy absorbed in Test Examples 1 to 6. Test Examples 1 to 1 shown in Table 1
5, the amount of absorbed energy is 30 m in FIG.
m, and corresponds to the area of a region surrounded by each characteristic curve extending to m and the horizontal axis indicating the amount of displacement. In the case of Test Example 6, as shown in FIG. 20, measurement was impossible because the sample was broken when the displacement amount was 30 mm (compression rate: 60%).

As is clear from Table 1, Test Examples 1 to 5
The higher the density, the larger the value of the absorbed energy. The absorbed energy amount of Test Example 1 having the lowest density is 8
3.1 kN · mm, which is extremely small. The absorbed energy amount of Test Example 2 having the second lowest density was 191.3 kN.
・ Mm, 400 kN ・ m which is a reference as a necessary amount
still less than m. And the next low density test example 3
Had an absorbed energy of 627.9 kN · mm. The amount of absorbed energy in Test Example 3 was significantly over 400 kN · mm, which is a sufficiently satisfactory value. Further, in Test Examples 4 and 5, which have a larger amount of absorbed energy than in Test Example 3, the amount of absorbed energy significantly exceeds 400 kN · mm.

From the above, the density is 0.2 g / cm.^Three
Test Examples 1 and 2 less than
Not enough rigidity, enough absorption energy
It turns out that a giant amount cannot be obtained. The density is 0.5g
/ Cm^ThreeIn Test Example 6 above, the compression modulus was large and the rigidity was high.
Is too high and the critical elastic modulus is less than 60%.
It turns out that it is a thing. In contrast, the density
0.2-0.5 g / cm ^ThreeTest Examples 3, 4, and 5
Elastic modulus of 60% or more, enough absorbed energy
[Test 3] Impact of the present invention
And excellent vibration reduction effect of vibration energy absorbing member
In order for the foam to be filled in the hollow part of the housing
Test sun with various changes in the material and size of the elastic body
Prepare pulls 1 to 5 and perform a hammering test,
The respective vibration damping characteristics were investigated.

The housing has an outer diameter of 27 mm, an inner diameter of 20.4 mm, a thickness of 3.3 mm, and a total length of 470 m.
m, weight: 310 g of an aluminum alloy pipe was used. The material of the foamed elastic body, the outer diameter of the foamed elastic body, the gap ratio, the adhesion state, and the weight of the foamed elastic body of Test Samples 1 to 5 are as described in Table 1.

The high-damping foam rubber as the foamed elastic material is composed of 5 to 25 parts by weight of sulfur, 5 to 200 parts by weight of phenol resin and 5 parts by weight of NBR per 100 parts by weight.
A foam obtained by heating and foaming a foamable rubber composition containing up to 40 parts by weight of a foaming agent, and having a density of 0.
3 g / cm ³ , compression modulus: 80 MPa, tan δ:
0.25. The high-rigidity foamed rubber is obtained by heating and foaming a foamable rubber composition comprising 10 to 50 parts by weight of sulfur and 5 to 40 parts by weight of a foaming agent with respect to 100 parts by weight of the diene rubber. Consisting of the foam obtained
Density: 0.3 g / cm ³ , compression modulus: 170 Mpa,
tan δ: 0.04.

[0102]

[Table 2]

The hammering of the test samples 1 to 9 was carried out in a freely supported state by hanging the test samples 1 to 9 with rubber strings. Fig. 2
As shown in FIG. 1, 10 mm inward from both ends of the housing
Are P1, P5, and P2, P3, and P4 are the four equally spaced positions between P1 and P5. These are two positions 10 mm outward from P2 and P4.
Further, the hammering points are set to five points P1 to P5 for the test sample 1, and
Was set at one position of P3.

As described above, test samples 1 to 9
Was subjected to a hammering test. Then, the inertance (dB (g / N)) in a predetermined frequency region was measured, and the results of the obtained vibration damping characteristics were shown in FIGS.
Shown in The vibration damping characteristics of the test sample 1 without the filler were compared with those of the other test samples 2 to 9 as shown in FIG.
29 are respectively shown by chain lines, and the vibration damping characteristics of Test Samples 2 to 9 are shown by solid lines in FIG. 22 to FIG.

(Evaluation) (1) Reduction Effect of Peak Level (Primary Bending Resonance Near 650 Hz) As is clear from FIGS. 22 and 26, the filler material is different and the filler is filled in an adhesive state. In the case of test samples 2 and 6, both show substantially similar vibration damping characteristics,
The peak level is 4 to 6 dB compared to the test sample 1.
To some extent.

Further, as is apparent from FIGS. 23 and 27, in the case of test samples 3 and 7 in which the filler material is different and the filler is filled in a non-adhered state at substantially the same void ratio, both are substantially the same. The peak level is reduced by about 23 to 25 dB as compared with the test sample 1.

As is apparent from FIGS. 24 and 28, in the case of test samples 4 and 8 in which the filler material is different and the filler is filled in a non-adhered state at substantially the same void ratio, both are substantially the same. The peak level is reduced by about 10 to 11 dB as compared with the test sample 1.

As is apparent from FIGS. 25 and 29, in the case of test samples 5 and 9 in which the filler material is different and the filler is filled in a non-adhered state at substantially the same void ratio, both are substantially the same. The peak level is reduced by about 7 to 8 dB as compared with the test sample 1.

From the above, it can be seen that there is almost no difference in the effect of reducing the peak level due to the difference in the filler material. When the filler is filled in a non-adhered state (test samples 2 and 6), when the filler is filled in an adhered state (test samples 3, 4, 5, and 5).
7, 8, 9), the effect of reducing the peak level is greater,
In addition, it can be seen that the effect of reducing the peak level increases as the gap ratio decreases. In particular, in the case of Test Samples 3 and 7, which have the smallest gap ratio, the peak level is reduced to approximately half that of Test Sample 1, and it can be seen that the vibration can be suppressed very well by the filler. (2) Movement of peak frequency As is clear from FIGS. 22 and 26, in the case of Test Samples 2 and 6 in which the filler is filled in an adhesive state, the weight increases due to the filler. , The peak frequency is shifted to the lower frequency side. Normally, when the weight of the arm body increases and the rigidity increases, the peak frequency shifts to the high frequency side. However, in the case of Test Samples 2 and 6, the dynamic rigidity increasing effect due to the filling of the arm body with the filler is provided. It turns out that is not seen.

As is clear from FIGS. 23 and 27, in the case of test samples 3 and 7 in which the filler is filled in a non-adhered state, although the peak frequency is shifted to the lower frequency side, The shift amount is small compared to the weight increase due to the filler.

In particular, in the case of test samples 3, 5, 8, and 9 in which the filler with a small weight is filled in a non-adhesive state, there is almost no shift in the peak frequency, and the influence of the filling with the filler is small. We understand that we do not receive.

[Brief description of the drawings]

FIG. 1 is a sectional view of an impact and vibration energy absorbing member according to Embodiment 1 of the present invention.

FIG. 2 is a sectional view taken along the line II-II of FIG.

FIG. 3 is a plan view of a bumper beam to which shock and vibration energy absorbing members according to Embodiments 1 and 2 of the present invention are attached.

FIG. 4 is a sectional view taken along the line IV-IV in FIG. 3;

FIG. 5 is a sectional view of an impact and vibration energy absorbing member according to Embodiment 2 of the present invention.

6 is a sectional view taken along the line VI-VI of FIG.

FIG. 7 is a sectional view taken along the line VII-VII of FIG. 3;

8 is a cross-sectional view of the shock and vibration energy absorbing member according to the third embodiment of the present invention, which is a cross-sectional view taken along line VIII-VIII of FIG.

FIG. 9 is a plan view of a shock and vibration energy absorbing member according to Embodiment 3 of the present invention.

FIG. 10 is a sectional perspective view of a front frame to which an impact and vibration energy absorbing member according to Embodiment 3 of the present invention is mounted.

FIG. 11 is a plan view showing a part of a shock and vibration energy absorbing member according to a fourth embodiment of the present invention in a cutaway cross section.

12 is a sectional view taken along the line XII-XII of FIG.

FIG. 13 is a sectional view taken along line XIII-XIII of FIG. 11;

FIG. 14 is a plan view showing a part of a shock and vibration energy absorbing member according to a fifth embodiment of the present invention in a cutaway cross section.

FIG. 15 is a sectional view taken along the line XV-XV in FIG. 14;

FIG. 16 is a cross-sectional view of the shock and vibration energy absorbing member according to Example 1 in Test 1, and is a sectional view taken along XVII-XVII in FIG.
It is sectional drawing cut | disconnected along the line.

FIG. 17 is a plan view of the shock and vibration energy absorbing member according to Example 1 in Test 1.

FIG. 18 is a graph showing load-displacement curves of Example 1 and Comparative Examples 1 to 3 in Test 1.

19 is a graph showing load-displacement curves of Test Examples 1 to 5 in Test 2. FIG.

FIG. 20 is a graph showing a load-displacement curve of Test Example 6 in Test 2.

FIG. 21 is an explanatory diagram showing hammering positions of test samples in test 3.

FIG. 22 is a graph showing the vibration damping characteristics of Test Samples 1 and 2 in Test 3.

FIG. 23 is a graph showing the vibration damping characteristics of Test Samples 1 and 3 in Test 3.

FIG. 24 is a graph showing the vibration damping characteristics of Test Samples 1 and 4 in Test 3.

FIG. 25 is a graph showing the vibration damping characteristics of Test Samples 1 and 5 in Test 3.

FIG. 26 is a graph showing the vibration damping characteristics of Test Samples 1 and 6 in Test 3.

FIG. 27 is a graph showing the vibration damping characteristics of Test Samples 1 and 7 in Test 3.

FIG. 28 is a graph showing the vibration damping characteristics of Test Samples 1 and 8 in Test 3.

FIG. 29 is a graph showing the vibration damping characteristics of Test Samples 1 and 9 in Test 3.

[Explanation of symbols]

1, 11, 21, 31, 41, 51 ... housing 1a, 11a, 31a, 41a ... main body 1b, 11b, 31b, 41b ... plug member 1c, 11c, 21c, 31c, 41c, 51c ... hollow portion 11f, 41f ... Partition walls 2, 12, 22, 32, 42, 52 ... Foam elastic body 23 ... First member 23a ... Depression 23b ... Plane part 24 ... Second member 25 ... Plug member 31d ... Bracket part 33 ... Through hole 7 ... Bumper beam 7a, 7
b, 7c: hollow portion 8: front frame 8a: concave portion 8b: flat portion S: gap

Continued on the front page (51) Int.Cl. ⁷ Identification symbol FI Theme coat II (Reference) B60R 21/02 B60R 21/02 M F16F 7/00 F16F 7/00 K 15/02 15/02 QC 15/08 15 / 08 D (72) Inventor Yoshinori Yasumoto 3-1, Higashi 3-chome, Komaki City, Aichi Prefecture Tokai Rubber Industries Co., Ltd. F term (reference) 3J048 AA01 AC01 AD08 AD16 BA24 BD02 DA04 EA36 3J066 AA02 BA01 BB01 BC03 BD05 BD07 BE06

Claims (7)

[Claims] 1. A housing made of a rigid material having at least one hollow portion therein, and a small gap between a wall forming the hollow portion of the housing and being movably sealed in the hollow portion. A shock and vibration energy absorbing member, comprising: a high-rigidity foamed elastic body; 2. The shock and vibration energy absorbing member according to claim 1, wherein said housing has a partition wall for partitioning an internal space of said housing into a plurality of hollow portions. 3. The foamed elastic body has a density of 0.2 to 0.1.
2. The shock and vibration energy absorbing member according to claim 1, wherein the impact and vibration energy absorbing member is 5 g / cm ³ . 4. The foamed elastic body has a critical compressibility of 60%.
The shock and vibration energy absorbing member according to claim 1, wherein: 5. The shock and vibration energy absorbing member according to claim 1, wherein said foamed elastic body has a surface portion having a Shore D hardness of 80 or less. 6. The impact according to claim 1, wherein the foamed elastic body is formed by foaming a foamed elastic body forming material mainly composed of at least one of rubber and resin and a foaming agent. And a vibration energy absorbing member. 7. The shock and vibration energy absorbing member according to claim 1, wherein a gap formed between the wall surface of the housing and the foamed elastic body is 1 mm or less.