JPH038817Y2 - - Google Patents

Description

[Detailed Description of the Invention] (Industrial Application Field) The present invention relates to a fluid-filled mount used when a vibration source such as an engine or a shock absorber is coupled to a fixed member such as a vehicle body.

(Prior Art) When a vibration source such as an engine is directly attached to a vehicle body, vibrations are directly transmitted to the vehicle body, so conventionally, the vibration source is attached via a mount. The simplest type of mount is a block mount using only rubber or the like, but since it cannot exhibit sufficient vibration absorption and damping effects, a fluid-filled mount as shown in FIG. 3 may be used.

In such a fluid-filled mount, the top of an elastic member 100 having a generally truncated conical shape on both the inner and outer surfaces is baked onto a mounting member 101 that connects to a vibration source, and the bottom is baked onto a base member 102 that is fixed to a fixed member. , a diaphragm 103 is attached to this base member 102.
Attach the diaphragm 103 and the elastic member 100.
The space formed by the inner peripheral surface is the orifice 104a.
Two fluid chambers 1 are formed by an orifice plate 104 formed with
05 and 106, the load from the vibration source is received by the elastic member 100, and a damping force is generated at the orifice 104a.

In the case of such a fluid-filled mount, since the elastic member 100 is thinner than that of a block mount, it is likely to buckle against large displacements, resulting in a high static spring constant and, as a result, a high dynamic spring constant. There is a disadvantage. For this reason, a reinforcing interring 107 is embedded in the elastic member 100 in the center of the elastic member 100, similar to the suspension bushing.

(Problem to be solved by the invention) By the way, the interring 107 is connected to the elastic member 1.
00, and this interring 107 connects the elastic member 100 to the inner part 100a and the outer part 10.
0b, unless the surface curvature of the elastic member 100 is considered, the likelihood of buckling of the inner portion 100a is determined by the thickness T ₁ of the inner portion 100a and the inner portion 1
00a to the length L ₁ (T ₁ /L ₁ ), and the ease of buckling of the outer portion 100b is similarly determined by the ratio (T ₂ /L 1 ) of the thickness T ₂ to the length L ₂ L ₂ ), and the smaller (T ₁ /L ₁ ) and (T ₂ /L ₂ ), the more likely buckling occurs.

On the other hand, since the inner portion 100a has a smaller diameter than the outer portion 100b, it is necessary to receive a load larger than that per circumference.
The thickness T ₁ of a is greater than the thickness T ₂ of the outer portion.

However, in the conventional fluid-filled mount, since the interring 107 is embedded in the center of the elastic member 100, L ₁ =L ₂ , and as a result, buckling is likely to occur in the outer portion 100b.

(Means for Solving the Problems) In order to solve the above problems, the present invention makes the inner part of the elastic member thicker than the outer part of the interring, and also makes the interring closer to the bottom of the elastic member. By embedding it in the outer portion, the radial distance between the interring and the mounting member is larger than the radial distance between the interring and the base member.

(Function) By making the radial distance between the interring and the mounting member larger than the radial distance between the interring and the base member, the length of the inner part of the elastic member bordering on the interring is equal to that of the outer part. It is larger than the length, and an equal buckling load acts on the inner and outer parts.

(Example) An example of the present invention will be described below with reference to FIG. 1, which is a longitudinal cross-sectional view, and FIG. 2, which is an explanatory diagram of the dimensional relationship.

The fluid-filled mount 1 has an elastic member 2 whose top part is fixed to a mounting member 3 and its bottom part is fixed to a base member 4 by baking. Here, the elastic member 2 is made of a material such as natural rubber, butadiene rubber, isoprene rubber, butyl rubber, ethylene propylene rubber, chloroprene rubber, etc., and its shape is approximately a truncated conical shape with an inner circumferential surface and an outer circumferential surface. , including a truncated pyramid shape), and a recess 5 into which the base of the mounting member 3 is fitted is formed at the top thereof, and the thickness in the axial direction thereof gradually increases from the bottom to the top. Approximately equal loads are applied to both.

In addition, bulges 6 and 7 are formed on the outer and inner peripheral surfaces of the elastic member 2 at portions slightly closer to the bottom, and within the elastic member 2 is an interring 8 of equal thickness formed by press-forming a steel plate or the like. This inter ring 8
The elastic member 2 is attached to the inner part 2a and the outer part 2b.
It is divided into Further, the outer end of the interring 8 projects outward from the bulge 6 , and the inner end of the interring 8 is located within the bulge 7 . Specifically, the inner end of the interring 8 protrudes inward from the virtual inner peripheral surface (indicated by a dotted line) when the bulge 7 is not formed.

Here, the thickness T ₁ of the inner portion 2a of the elastic member 2
is larger than the thickness T ₂ of the outer portion 2b, and the length L ₁ of the inner portion 2a is larger than the length L ₂ of the outer portion 2b, specifically, T ₁ /L ₁ and T ₂ /L ₂ are made to be approximately equal. Also, as L ₁ > L ₂ , the result is
Radial distance between interring 8 and mounting member 3
D ₁ is larger than the radial distance D ₂ between the interring 8 and the base member 4 (D ₁ >D ₂ ).

The reason why the bulge 7 is provided on the inner circumferential surface of the elastic member 2 is to prevent stress from concentrating in this part, which becomes the starting point for cracks and reduces durability. In particular, the reason why the interring 8 is covered with the bulge 7 is that the fluid sealed inside the elastic member 2 comes into contact with the adhesive between the elastic member 2 and the interring 8, and the adhesive force is increased. This is to prevent this from causing a decline.

Further, the mounting member 3 has a bolt 9 projecting thereon for connecting to a vibration source such as an engine, and the base member 4 has a mounting hole 1 for mounting to a vehicle body frame or the like.
0 is formed.

The lower end of the base member 4 has an annular holding part, and the orifice plate 11 having the orifice 11a, the diaphragm 12, and the cap-shaped cover 13 are held together in this annular holding part, with the orifice plate 11 on top, the diaphragm 12 in the middle, and the cover 13 in the middle. It is held so that it is facing downwards. Then, the fluid 14 is sealed in the space formed between the diaphragm 12 and the inner peripheral surface of the elastic member 3, and this space is filled with the orifice plate 11.
The fluid chamber 15 is divided into an upper main fluid chamber 15 and a lower sub-fluid chamber 16, and these fluid chambers 15 and 16 are communicated through an orifice 11a.

In the above, the load from the vibration source is applied to the mounting member 3.
When the fluid is transmitted to the elastic member 2 through the fluid, the elastic member 2 is deformed, and as a result of this deformation, the fluid flows between the main fluid chamber 15 and the auxiliary fluid chamber 16 through the orifice 11a, and the fluid flows in the orifice 11a. Damping force is generated due to resistance. The vibrations are absorbed and alleviated by the deformation and damping force of the elastic member 2.

(Effects of the invention) As explained above, according to the invention, in a fluid-filled mount in which an elastic member is baked and fixed between a mounting member and a base member, the position of the interring buried in the elastic member is closer to the bottom, and the Since the radial distance between the ring and the mounting member is larger than the radial distance between the interring and the base member, the buckling load acting on the elastic member inside and outside the interring is reduced. Thus, the mount as a whole can be made more compact and less prone to buckling.

[Brief explanation of the drawing]

FIG. 1 is a longitudinal cross-sectional view of a fluid-filled mount according to the present invention, and FIG. 2 is a diagram showing the dimensional relationship of the mount.
FIG. 3 is a longitudinal sectional view of a conventional fluid-filled mount. In the drawings, 1 is a fluid-filled mount, 2 is an elastic member, 2a is an inner part, 2b is an outer part, 3 is a mounting member, 4 is a base member, 6 and 7 are bulging parts, 8 is an interring, and 11 is a An orifice plate, 12 a diaphragm, 14 a fluid, 15 and 16 a fluid chamber,
T ₁ and T ₂ are the thicknesses of the elastic members, L ₁ and L ₂ are the lengths of the elastic members, and D ₁ and D ₂ are the radial distances between the interring, the mounting member, and the base member.

Claims (1)

[Scope of utility model registration request] The top part of the elastic member, which has a substantially truncated pyramid shape on both the outer and inner peripheral surfaces, is fixed to the mounting member connected to the vibration source, and the bottom part is fixed to the base member by baking or the like, and an orifice plate is attached to the inside of the elastic member. In a fluid-filled mount which forms a defined fluid chamber and has a reinforcing interring embedded within an elastic member, a portion of the elastic member that is inner than the interring is thicker than an outer portion; A fluid-filled mount characterized in that a radial distance between the interring and the mounting member is greater than a radial distance between the interring and the base member.