JP2004019837A - Engine mount - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To easily form a partially high strength part and an easily-breakable structure when an engine mount is requested to have the partially high strength part and the highly rigid and easily-breakable structure in an engine mount using the resin bracket. <P>SOLUTION: This engine mount 1 comprises a vibration isolation part 4 formed of an inner tube 2 and a vibration isolation rubber 3 and the resin bracket supporting the vibration isolation part 4. A part of the resin bracket is mounted, as a mounting flange 7, on a body F. In the bracket body part 6 of the resin bracket 5, the direction A side thereof through the vibration isolation rubber 3 is formed in the high strength part 18, and a metal stopper part 25 is inserted therein. The stopper part 25 is formed in a generally L-member formed integrally with a collar part 24, and the collar part 24 is inserted into a mount flange 7. The direction B side thereof from the vibration isolation rubber 3 is formed in the highly rigid and easily-breakable part 20, increased in rigidity by a rib 21, and formed easily-breakable by providing a weld line 22 and a slot hole 23 at the rib 21. <P>COPYRIGHT: (C)2004,JPO

Description

[0001]
TECHNICAL FIELD OF THE INVENTION
The present invention relates to an engine mount having a resin bracket, and more particularly to an engine mount capable of coping with a large displacement such as an impact. Here, large displacement means that when a large impact load is applied to the car body, the car body and the engine make an abnormally large relative displacement, and the displacement on the engine side cannot be stopped only by the elastic deformation of the vibration isolating rubber, A large displacement that must be received directly on the resin bracket side.
[0002]
[Prior art]
Engine mounts with resin brackets are known. Although the resin bracket can be reduced in weight, it must be added with reinforcing ribs and the like so that strength and rigidity are not insufficient, and the insert is integrated with the mounting seat so that bolts do not loosen at the joints with the vehicle body. ing.
[0003]
[Problems to be solved by the invention]
By the way, at the time of large displacement, the inner cylinder integral with the vibration isolating rubber is likely to strike the resin bracket and break it, so that a large-strength structure capable of preventing this is sometimes required. On the other hand, in normal use, the rigidity may be increased by ribs or the like in order to obtain sufficient support rigidity. When the large displacement occurs in such a high rigidity portion, it may be required to be easily broken. . In this case, a highly rigid and easily breakable structure is required.
Therefore, an object of the present invention is to form a highly rigid and easily breakable structure on a resin bracket.
[0004]
[Means for Solving the Problems]
In order to solve the above-mentioned problem, an engine mount according to the present invention provides an engine mount that supports an engine via a vibration-isolating rubber provided on a resin bracket, while providing the resin bracket with a highly rigid structure for increasing rigidity. A high-rigidity structure is provided with a weakened structure that becomes a crack starting point at the time of the large displacement on the engine side to form a high-rigidity easily cracked portion that is easily broken by the large displacement on the engine side.
[0005]
At this time, the high rigidity structure may be a rib for increasing rigidity, and the weakened structure may be a recess formed in the rib, a hole passing through the rib, or a weld line crossing the rib.
[0006]
【The invention's effect】
A high-rigid structure is formed on the resin bracket with ribs, and a weakened structure is provided in this high-rigid structure to serve as a crack starting point when a large displacement occurs. When it is necessary to break due to a large displacement, it can be easily broken starting from the weakened structure, and both high rigidity and susceptibility to a large displacement can be achieved. This weakened structure can be easily realized by a concave portion provided in the rib, a hole passing through the rib, or a weld line crossing the rib.
[0007]
BEST MODE FOR CARRYING OUT THE INVENTION
Hereinafter, an embodiment will be described with reference to the drawings. 1 is a plan view of the engine mount according to the present embodiment (a view from above in FIG. 2), FIG. 2 is a cross-sectional view taken along line 2-2 in FIG. 1, and FIG. 3 is a cross-sectional view taken along line 3-3 in FIG. 4 is a sectional view taken along line 4-4 in FIG. FIG. 5 is a perspective view of the stopper.
[0008]
In these figures, an engine mount 1 includes an inner cylinder 2 for connecting to a hanger H (FIG. 3) of an engine E, which is a vibration source, an anti-vibration rubber 3 for elastically supporting the inner cylinder 2, and an outer peripheral portion of the anti-vibration rubber 3. , Which is integrally formed with a bracket main body 6 on which the vibration isolating rubber 3 is provided and a mounting flange 7 for mounting to the vehicle body F (see FIG. 3). ).
[0009]
As shown in FIG. 3, the mounting flange 7 overlaps with a support portion of the vehicle body F on the vibration receiving side, and is fixed by bolts 8 and nuts 9. The bracket body 6 projects from the vehicle body F, and the hanger H of the engine E is fixed to the inner cylinder 2 supported by the bracket body 6 with bolts b and nuts n. The engine mount 1 is cantilevered by the vehicle body F and supports the engine E. The inner cylinder 2 forms a support for the engine E.
[0010]
As shown in FIG. 1, the mounting flange 7 is provided with three mounting seats reinforced by metal inserts 10, 11, and 12. Of these, the insert 10 has an integrated stopper described later, and the inserts 11 and 12 have a general collar structure.
[0011]
The anti-vibration rubber 3 is made of a known rubber material, and connects the inner cylinder 2 and the outer peripheral portion 13 of the anti-vibration rubber 3 with a pair of rubber feet 4 extending to the opposite side across the inner cylinder 2. In the following description, the rubber foot 4 has a substantially V-shape, and a straight line C1 passing through each rubber foot 4, 4 and the center of the inner cylinder 2 is a Y-axis. Is a X-axis, and a central axis of the inner cylinder 2 orthogonal to these is a Z-axis. The plane defined by the X and Y axes is parallel to the support surface of the engine E in the bracket body 6, and the X axis direction is also the direction of movement of the engine support during large displacement.
[0012]
The outer peripheral portion 13 is substantially rectangular, and is formed integrally with the peripheral portion of the substantially rectangular mounting hole 14 formed in the bracket main body 6 and is formed so as to protrude at the edge portion. Protrusions 15 and 16 protruding toward the inner cylinder 2 are formed on the sides A and B of the outer peripheral part 13, and a thick part 17 formed around the inner cylinder 2 as a part of the vibration-proof rubber 3 is provided. A predetermined gap is formed.
[0013]
Since there is no rubber foot 4 on the X axis, the inner cylinder 2 can be relatively moved relatively in the opposite A and B directions on the X axis. When the inner cylinder 2 moves relative to the resin bracket 5 in the directions A and B on the X axis, the elastic deformation of the rubber feet 4 or 4 or the thick portion 17 abuts on the protruding portion 15 or 16 and the elastic members are separated from each other. When the movement can be stopped by the contact of the object, such movement is referred to as normal vibration. A movement that cannot be stopped only by the elasticity of these elastic members and is directly received by the bracket body 6 is referred to as a large displacement. The movement in the Y-axis and Z-axis directions is set to be stopped by the elastic deformation of the rubber feet 4.
[0014]
The resin bracket 5 is made of a suitable resin material such as nylon, and is formed by a known method such as injection molding. As shown in FIG. 1, the X-axis direction is formed to be longer than the Y-axis direction. The left half side, which is also the A direction side, forms a high strength portion 18 that withstands the large displacement of the inner cylinder 2, and the right half side, which is the B direction side, forms a highly rigid easily cracked portion 20. Note that due to layout restrictions, the large strength portion 18 is formed in a smaller area than the high rigidity easily cracked portion 20 side.
[0015]
The high rigidity easily cracked portion 20 is integrally formed with a rib 21, and has a high rigidity structure in which a partially thick structure is provided to obtain high rigidity sufficient to support the engine E. Further, a weld line 22 is formed so as to cross the rib 21, and a slot hole 23 penetrating the rib 21 in the Z-axis direction is formed. The slot hole 23 has an elongated hole shape whose opening is long in the Y-axis direction. Each of the weld line 22 and the slot hole 23 has a weakened structure as an easily breakable structure, and serves as a starting point of a crack at the time of the large displacement to easily break the high rigidity easily cracked portion 20.
[0016]
The slot hole 23 has an asymmetric shape with the weld line 22 interposed therebetween. In this embodiment, the mounting flange 7 side has a relatively small opening than the weld line 22, and the opposite side has an enlarged opening. In this case, the large opening side is further weakened, so that the crack can be guided to that side. Therefore, the crack direction can be freely set by adjusting the size and shape of the opening. The slot hole 23 has a round shape as a whole, and is curved so that the intermediate portion is convex toward the side opposite to the rubber cushion 3 as shown in FIG.
[0017]
The weld line 22 is formed at a place where the resin diverted and sneak around in the mold in the injection molding or the like meets, and the strength of the molded product is reduced, and the weld line 22 becomes a weak portion serving as a starting point of a crack at the time of large displacement. The position of the weld line 22 can be formed at an arbitrary position by setting an injection port or the like. In this embodiment, the weld line 22 is formed to be long from the edge of the mounting hole 14 to the end in the B direction.
[0018]
As shown in FIG. 5, the insert 10 is a substantially L-shaped member made of a suitable metal such as iron or light alloy in which a collar portion 24 and a stopper portion 25 extending therefrom are integrated at one end. Formed by forging or the like, the section modulus and the like of each part are designed to provide strength sufficient to withstand large displacements and engine support loads.
[0019]
A through hole 26 for the bolt 8 is formed in the collar portion 24, and the left seat surface 27 of the left and right seat surfaces 27, 28 in FIG. Inner surface). The substantially seat surface 28 protrudes from the opposite side surface (hereinafter referred to as an outer surface) of the mounting flange 7 by a small amount h toward the vehicle body to prevent the resin from settling at the time of fastening. The collar portion 24 is substantially circular when viewed from the direction of the stop axis of the through hole 27, and the outer diameter of the collar portion 24 is larger than the width of the intermediate portion 30.
[0020]
The stopper portion 25 becomes thinner from the intermediate portion 30 to form a square cross section or the like (FIG. 2), extends in the Y-axis direction along the A side of the outer peripheral portion 13, and has a tip longer than the inner cylinder 2 in the Y-axis direction. Extending to However, the length of the outer peripheral portion 13 is slightly shorter than the length of the side in the direction A. Assuming that the distance D from the mounting surface of the mounting flange 7 to the tip of the stopper 25 with respect to the vehicle-body-side mounting surface and the distance from the inner cylinder 2 to the outer periphery of the inner cylinder 2 on the side opposite to the mounting flange 7 are d, D> d.
[0021]
The intermediate portion 30 and the stopper portion 25 are connected by an arc portion 31 to reduce stress concentration. The insert 10 has a substantially L-shape when viewed from above in FIG. Further, the stopper portion 25 is provided with through holes 32, 32, and the resin passes through the through holes 32, 33 and continuously connects the front and rear of the stopper portion 25 at the time of resin molding. It has a connection strengthening structure that strengthens integration.
[0022]
The stopper portion 25 is inserted into the large strength portion 18, the intermediate portion 30 is inserted into the large strength portion 18 and the mounting flange 7, and the collar portion 24 is inserted into the mounting flange 7. Therefore, the insert 10 is inserted in a substantially L-shape from the large strength portion 18 of the bracket main body 6 to the mounting flange 7 as shown in FIG.
[0023]
As shown in FIG. 4, the ribs 21 are formed integrally in an arcuate shape from the lower surface side of the bracket main body 6 in the illustrated state to the side surface of the mounting flange 7 on the bracket main body side. The insert 11 is a collar made of metal or the like in which a through hole 34 for a bolt is formed, and the left and right seating surfaces 35 and 36 are made smaller in diameter than the intermediate portion 37 to prevent them from falling off. Non-circular and detented.
[0024]
The left seat surface 35 in the figure is flush with the inner surface of the mounting flange 7, and the right seat surface 36 is slightly protruded from the outer surface of the mounting flange 7. The same is true. In addition, since the insert 10 is a deformed member having a substantially different shape from a normal insert collar configured as a single body, for example, the entire shape of the insert is substantially L-shaped. Not required. The insert 12 has the same structure as the insert 11.
[0025]
As shown in FIG. 5, a positioning recess 35 is formed on a side surface of the intermediate portion 30. The positioning recess 35 forms a positioning structure at the time of resin molding, and is filled with resin. In addition, it functions similarly as a convex part instead of the concave part 38. Also, when the insert 10 is viewed as a collar, it is an L-shaped deformed member as compared with a general cylindrical member, and this shape itself also forms a positioning structure.
[0026]
Next, the operation of the present embodiment will be described. In FIG. 1, general vibration in the X-axis direction is absorbed by elastically deforming the vibration isolating rubber 3, and slightly larger vibration is absorbed by the elastic deformation of the thick portion 17 colliding with the protrusion 15 or 16. I do.
[0027]
When a large impact force is applied to the vehicle body and the inner cylinder 2 moves relatively largely with respect to the resin bracket 5 to make a large displacement that destroys the bracket body 6, when the large displacement in the A direction occurs, The cylinder 2 strongly contacts the edge of the mounting hole 14, and a stopper 25 is inserted near this edge to form a large strength portion 18 reinforced to sufficiently withstand such an impact. Therefore, it is possible to avoid destruction due to such a large displacement.
[0028]
In addition, since the stopper portion 25 is integrated with the collar portion 24 and attached to the vehicle body with the collar portion 24, the strength of the insert 10 itself is increased, and the collar portion 24 and the stopper portion 25 can be used together. Thus, the number of parts can be reduced. In addition, it is possible to obtain a sufficiently large strength in spite of the location where the layout is restricted in order to provide the rib, and it is possible to form the high-strength portion. Therefore, the resin bracket 5 does not need to be so thick, and the weight can be reduced.
[0029]
Conversely, when a large displacement is made in the opposite direction B, the inner cylinder 2 crushes the protruding portion 16 and hits the mounting hole 14. At this time, since the high-rigidity easily cracked portion 20 has a structure with high rigidity and easy cracking, the large-rigidity portion is cracked with the weakened structure portion including the weld line 22 and the slot hole 23 as a starting point.
[0030]
However, since the high-rigidity easily cracked portion 20 is reinforced by the ribs 21 to provide high rigidity, except for such a large displacement, the rigidity of the resin bracket 5 is increased to contribute to the stable support of the heavy engine E. are doing. In addition, by forming the ribs 21, it is possible to avoid increasing the thickness of the high-rigidity easily cracked portion 20 as a whole and to contribute to a reduction in the overall weight.
[0031]
Although the weakened structure does not need to have both the weld line 22 and the slot hole 23 at the same time, depending on the degree of the high rigidity structure provided by the ribs 21, it is possible to make the high rigidity portion easily crack by only one of them. it can. Further, by forming the substantially L-shaped insert 10 between the large strength portion 18 and the mounting flange 7 and the rib 21 over the high rigidity easily cracked portion 20 and the mounting flange 7, respectively, as shown in FIG. When the main body 6 receives a load in the Z-axis direction, despite the fact that the resin bracket 5 is cantilevered by the mounting flange 7, sufficient support rigidity can be given to the load in this direction. The joint 7 can be used as a fulcrum, and can sufficiently withstand a swinging motion with the inner cylinder 2 as a point of action.
[0032]
As described above, with respect to one resin bracket 5, the high strength portion 18 can be formed by the insert 10 on the A direction side and the high rigidity easily cracked portion 20 can be formed on the B direction side by sandwiching the vibration isolating rubber 3. It is not necessary to provide the large-strength portion 18 together with the high-rigidity easily cracked portion 20 on one resin bracket 5, and this may be omitted depending on the purpose specification. Further, the resin bracket 5 does not necessarily have to be L-shaped, and may be a flat shape in which the bracket body 6 and the mounting flange 7 are on the same plane.
[0033]
In addition, a large-strength portion 18 is provided on one side of the resin bracket 5 with the anti-vibration rubber 3 therebetween, and a high-rigidity portion 20 reinforced with a rib is provided on the other side, and the high-rigidity portion 20 is provided. The large-strength portion 18 is provided in a portion smaller than the existing area, so that sufficient strength is given to a small-area portion where sufficient rib shape reinforcement cannot be obtained to obtain the required strength due to layout restrictions. Can be.
[0034]
Further, a substantially L-shaped insert 10 in which a stopper 25 and a collar 24 forming a mounting seat are integrated is embedded and integrated into a substantially L-shaped resin bracket 5 in which the bracket body 6 and the mounting flange 7 are integrated. As a result, sufficient support rigidity can be provided despite the cantilever support of the engine, and it is sufficient for swinging motion with the mounting portion of the mounting flange 7 as a fulcrum and the engine connecting portion of the bracket body 6 as an operation point. Can withstand.
[0035]
In addition, since the insert 10 has its own L-shaped irregular shape and concave portion 38 as a positioning structure at the time of resin molding, when used as an engine mount after resin molding, the positioning function can effectively exert a stopper function.
[0036]
In addition, since the insert 10 has a structure for strengthening the connection with the resin formed of the through holes 32 and 33, the insert 10 and the resin are firmly bonded and integrated at the time of resin molding, and the strength and rigidity can be increased.
[0037]
Further, the weakened structure with respect to the high rigidity structure by the rib 21 does not necessarily have to be a slot hole that penetrates, but may be a concave part with a bottom. In short, any material having a weakened structure serving as a crack starting point at the time of large displacement may be used. The high-rigidity structure is not limited to the ribs, but may be a thick-walled structure that is simply thicker than the others.
[Brief description of the drawings]
FIG. 1 is a plan view of an engine mount. FIG. 2 is a cross-sectional view taken along line 2-2 of FIG. 1. FIG. 3 is a cross-sectional view taken along line 3-3 of FIG. 1. FIG. 5) Perspective view of stopper [Explanation of reference numerals]
1: engine mount, 2: inner cylinder, 3: anti-vibration rubber, 4: rubber feet, 5: resin bracket, 6: bracket body, 7: mounting flange, 10: insert, 13: outer peripheral, 14: mounting hole , 15: projecting portion, 16: projecting portion, 17: thick portion, 18: large strength portion, 20: high rigidity easily cracked portion, 21: rib, 22: weld line, 23: slot hole

Claims (3)

In an engine mount that supports an engine via a vibration-isolating rubber provided on a resin bracket, a high-rigidity structure for increasing rigidity is provided on the resin bracket, and the high-rigidity structure has a crack origin at a large displacement on the engine side. An engine mount characterized by having a weakened structure to form a high-rigidity easily cracked portion that is highly rigid and easily cracked by large displacement on the engine side. The engine mount according to claim 1, wherein the high-rigidity structure is a rib for increasing rigidity, and the weakened structure is a recess formed in the rib or a hole passing through the rib. The engine mount according to claim 1, wherein the high-rigidity structure is a rib for increasing rigidity, and the weakened structure is a weld line crossing the rib.

Images