JP3488006B2 - Anti-vibration mount bracket - Google Patents

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a bracket of an anti-vibration mount, such as an engine mount, which is interposed between a base body and a vibrating body to reduce vibration.

[0002]

2. Description of the Related Art FIGS. 3 (a) to 3 (c) show an example of a conventional engine mount bracket.
Has a bolt hole 42 for connecting to an unillustrated engine mount in the center of the left half portion of the rectangular flat plate portion 41, and has bolt holes 43, 44 at the upper and lower ends of the trapezoidal right half portion that follows the bolt hole 42. There is. Slightly below the middle portion of the bolt holes 43, 44, there is provided an implanting portion 45 having an internal thread on the inner circumference, and an implanting bolt 46 is screwed into the implanting portion 45, The stud bolt 46 and the bolt holes 43, 44 are connected to an unillustrated engine side bracket.

[0003]

By the way, in the above-mentioned conventional shape (FIG. 3A), the studs 46 are located near the outer peripheral edge of the flat plate portion 41 (shown as A portion in the figure). Therefore, the wall thickness between the stud bolt 46 and this portion A becomes thin, and when the stud bolt 46 is screwed into the stud portion 45 and is fastened to the engine side bracket, the above-mentioned A
Distortion tends to concentrate on the part. This is because when the above-mentioned studs 46 are used, the strain due to assembly is less likely to disperse, as compared to the normal bolts that are held and fixed at two places above and below, and therefore, the thin wall portion, especially the fastening surface side. Distortion will be concentrated. Also, the bracket of the engine mount is subject to large dynamic strain due to vibration input, and there is a concern that durability may deteriorate due to fatigue.

In such a case, a solution is usually taken such as changing the position of the implanting portion 45 to which the implanting bolt 46 is screwed, or increasing the distance between the implanting bolt 46 and the outer peripheral edge. However, there are some design restrictions due to reasons such as mounting with other parts or interference with parts arranged in the periphery, and it may be difficult to take the above measures.

SUMMARY OF THE INVENTION An object of the present invention, therefore, is to reduce the concentration of strain in the mounting bolt of an anti-vibration mount bracket having studs and improve the fatigue durability of the brackets.

[0006]

In order to solve such an object, in the constitution of claim 1 (see FIG. 1), the flat plate portion (31) is fixedly connected to an antivibration mount interposed between the base and the vibrating body. ) Implant bolt (36) near the outer peripheral edge (A part) of
In the anti-vibration mount bracket having the stud bolt (36) fastened to the base body or the vibrating body, the flat plate portion (31) has the stud bolt (3).
6) Centering the studs (36) on the fastening side end face
Then, at a position symmetrical with the outer peripheral edge (A portion), the plate thickness is set to 1
The recessed portion (3) for dispersing the assembling strain of the stud (36) by recessing at a depth of / 4 to 1/3.
7) is provided.

According to the above configuration, the stud (3)
6) Since the assembling strain concentrated in the surrounding thin portion is dispersed by the concave portion (37) provided at the symmetrical position, the fatigue durability of the bracket can be greatly improved.

The concave portion (37) has a thickness of 1/4 to
It is desirable to set the depth to 1/3, and the effect of strain reduction is effective.
Obtained . Specific examples of such an antivibration mount bracket include an engine mount bracket interposed between a vehicle body as the base body and a vehicle engine as the vibrating body (claim 2 ).

[0009]

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS An example in which the present invention is applied to an engine mount bracket will be described below with reference to the drawings. In FIG. 2, reference numeral 1 denotes a known liquid-filled type engine mount, which is a vibration-proof mount, and is configured to perform vibration damping by the action of a liquid filled in a liquid chamber having a vibration-proof rubber body as a chamber wall. The engine mount 1 is fixed on the vehicle frame 2 which is a base body by leg portions 11 and 12 extending downward from two left and right portions on the bottom surface side. The bracket 3 of the present invention is provided on the bottom surface of the engine mount 1.
Is fixed at one end, and the other end is connected to a bracket 5 on the engine side which is a vibrating body.

FIG. 1A is a view of the bracket 3 of the present invention seen from the back side, and FIG. 1B is a side view of the bracket 3. The bracket 3 is flat and made of aluminum or the like.
In the figure, the flat plate portion 31 of the bracket 3 has a bolt hole 32 at the center of the left half of the rectangle, and is connected and fixed to the bottom surface of the engine mount 1 of FIG. 2 by a bolt inserted into the bolt hole 32. The right half portion of the flat plate portion 31 has a substantially trapezoidal shape and has bolt holes 33 and 34 at the upper and lower ends of the wide right end portion,
A planting portion 35, which is internally threaded, is provided slightly below the intermediate portion of the bolt holes 33, 34. A stud bolt 36 is screwed to the stud portion 35, and the stud bolt 36 and a bolt inserted into the bolt holes 33 and 34 are connected to the bracket 5 on the engine side in FIG. .

The outer peripheral edge of the flat plate portion 31 extending from the left half portion to the lower half portion of the right half portion is inwardly arcuate in order to avoid interference with peripheral parts, and the stud bolt 36 is in the arcuate shape. Is located in the vicinity of the outer peripheral edge (shown as part A in FIG. 1A). Therefore, the stud 36 and the A
The wall thickness between the portions is thin, and the strain due to the assembly of the stud bolt 36 is easily concentrated on the thin wall portion.

Therefore, according to the present invention,
A concave portion 37 is formed at a position symmetrical with the portion A with the stud 36 as a center. The concave portion 37 has a substantially triangular shape and is formed at a predetermined depth on the back surface side of the flat plate portion 31 as shown in FIG. 1C, and has a function of dispersing strain generated around the stud bolt 36 by assembly. Have.

The formation position of the recessed portion 37 is on the back surface side where the strain is large and is axially symmetrical to the portion A with respect to the implant bolt 36, that is, opposite to the portion A with respect to the implant bolt 36. It is desirable that they are formed at the same distance on the side, but they may be slightly displaced from that position.

The depth of the concave portion 37 is about ¼ of the plate thickness or more, and the same strain reducing effect as when it is penetrated can be obtained. Even if the depth is increased to more than 1/4 of the plate thickness of the bracket flat plate portion 31, there is no great difference in the effect, and conversely the strength tends to decrease. It is preferably about / 4 to 1/3.
Here, in FIG. 1 (c), when the diameter of the implant bolt 36 is 10 mm, the plate thickness of the flat plate portion 31 is 20 mm, and the distance d1 from the center of the implant bolt 36 to the portion A is 10 mm, the implant The distance d2 from the center of the bolt 36 to the recess 37 is 10 mm, the width d3 of the recess 37 is 5 mm,
The depth d4 of the recess 37 is 5 mm.

The shape of the recess 37 is not limited to the shape shown in the drawing, but may be a groove, for example. In this case, an arc-shaped groove may be formed along the circle centered on the stud bolt 36 and having a radius between the stud bolt 36 and the portion A.

By forming the recessed portion 37 in this manner, it is possible to disperse the strain generated by the implantation of the stud bolt 36 into the bracket and the fastening to the bracket 5 on the engine side which is a mating component. it can. Therefore, even when there is a design constraint on the position of the stud 36, the shape of the flat plate portion, or the like, it is possible to prevent the strain from being concentrated on the thin portion A and reducing the strength of the bracket, and to prevent breakage or the like. It can be prevented from occurring and its durability can be greatly improved.

Next, a test was conducted to confirm the effect of the present invention. First, a bracket having a conventional structure without the recess 37 is manufactured (see FIG. 3), and the stud 46 is inserted.
When the strain applied to the above-mentioned section A was investigated by implanting it into the bracket and assembling with the bracket on the engine side, Table 1
Was like. At this time, portions B to D of the table are shown in FIG.
The lower end portion (B portion) and the intermediate portion (C) of the bracket 4 shown in
Part) and the upper end part (D part), and it can be seen that the strain is concentrated in the B part on the fastening surface side.

[0018]

[Table 1]

Next, the recess 37 shown in FIG.
The bracket of the present invention having (the plate thickness of the flat plate portion 31 is 20 m
m) was actually manufactured, the above-mentioned stud bolt 36 was implanted into the bracket, and the engine side bracket 5 was assembled. Then, the strain applied to the fastening side end of the above-mentioned section A was measured.
Further, for comparison, the bracket of FIG. 3 having no recessed portion and the bracket having a large distance between the stud 36 and the portion A (thickness increased by 30%) were manufactured, and the bracket A was similarly prepared. The strain applied to the part (fastening side end) was measured. The results are shown in Table 2.

[0020]

[Table 2]

As is clear from Table 2, by forming the concave portion 37, the same effect as when the wall thickness is increased by 30% is obtained, and the distortion is reduced without increasing the size and weight of the product. I know that I can do it.

In order to investigate the relationship between the depth of the recess 37 and the effect of reducing strain, in the bracket of the present invention shown in FIG. 1, the depth of the recess 37 is set to 3 mm, 5 mm and 20 mm.
The value was changed to mm (penetration), and the strain applied to the fastening side end of the above-mentioned section A was measured in the same manner and shown in Table 3.

[0023]

[Table 3]

From Table 3, the depth of 5 mm or more has almost the same effect as the penetration, and in order to secure the strength and reduce the strain at the same time, the depth is 1 / th of the plate thickness. It turns out that it is good to set it to about 4.

[Brief description of drawings]

FIG. 1 (a) is an overall cross-sectional view of an engine mount bracket showing an embodiment of the present invention, as viewed from the direction of arrow a in FIG. 1 (b),
(B) is the whole side view, (c) is the IC-IC sectional view taken on the line of (a).

FIG. 2 is a view showing an assembled state of the engine mount bracket and the engine mount and the engine side bracket of FIG.

3A is an overall cross-sectional view showing the configuration of a conventional engine mount bracket, FIG. 3B is an arrow view of FIG. 3B, FIG. 3B is an overall side view, and FIG. 3C is III-III of FIG. It is a C line sectional view.

[Explanation of symbols]

DESCRIPTION OF SYMBOLS 1 Engine mount (anti-vibration mount) 11, 12 Leg part 2 Vehicle frame (base) 3 Engine mount bracket (anti-vibration mount bracket) 31 Flat plate parts 32, 33, 34 Bolt hole 35 Embedded part 36 Embedded bolt 37 Recessed part 5 Engine side bracket

Front page continued (72) Inventor Norihiro Yamada No. 1 Nagahata Ochiai, Kasuga-cho, Nishikasugai-gun, Aichi Toyoda Gosei Co., Ltd. In-house (56) References JP-A-61-228140 (JP, A) (58) Fields investigated (Int.Cl. ⁷ , DB name) B60K 5/12 F16F 1/36 F16F 15/08

Claims (2)

(57) [Claims] 1. A bracket, which is connected and fixed to a vibration-proof mount interposed between a base and a vibrating body, has a stud bolt near the outer peripheral edge of the flat plate portion, and the stud is used for the base body. Alternatively, in the vibration-proof mount bracket fastened to the vibrating body, the flat plate portion has the outer peripheral edge of the fastening-side end surface of the stud bolt around the stud bolt.
Concave the position that is symmetric with the depth of 1/4 to 1/3 of the plate thickness.
An anti-vibration mount bracket, characterized in that a recess is provided to disperse the assembling strain of the stud, when the mounting bolt is depressed . 2. The anti-vibration mount bracket according to claim 1, wherein the base body is a vehicle body, and the vibrating body is a vehicle engine.