JP4413228B2 - Strut mount - Google Patents

Description

  The present invention relates to a strut mount.

  The strut suspension generally includes a shock absorber for damping vertical vibrations. The tip of the shock absorber is usually located on the vehicle body side, and a structure in which the rod tip is supported on the vehicle body side via a vibration isolation base of a strut mount is conventionally known.

  For example, Japanese Patent Laid-Open No. 2001-171323 discloses a core material (inner cylinder) that is fixed to the tip of a shock absorber, a rubber elastic body (vibration-proof base) that is vulcanized and bonded to the core material, and its rubber elasticity. A strut mount is described that includes a pair of upper and lower bracket members that define a box portion (storage chamber) in which a body is stored.

  According to this strut mount, the pair of upper and lower bracket members, for example, one is formed in a substantially flat plate shape and the other is formed in a substantially cup shape, respectively. A substantially cylindrical storage chamber is defined. The vibration-proof base is stored in the storage chamber while being compressed between the pair of bracket members.

Moreover, a cup member having a substantially S-shaped cross section is attached to the bottom surface side (axle side surface) of the bracket member, and a bound bumper formed in a substantially cylindrical shape from urethane or the like is attached to the cup member. The proximal end portion is stored and held. When the compression allowance of the shock absorber exceeds a predetermined value, the bottom surface of the bracket member receives the upper end surface of the bound bumper, thereby exhibiting a stopper action.
JP 2001-171323 A (FIG. 1 etc.)

  By the way, in recent years, there has been a strong demand for lower fuel consumption in automobiles, and for this reason, demands for weight reduction of vehicle parts from automobile manufacturers are increasing every day. However, the conventional strut mount has a problem in that it cannot sufficiently meet the demand for weight reduction because an iron press product is used as the bracket member.

On the other hand, it is conceivable to replace as a means of lightening these bracket members from the iron aluminum alloy, in which case, when adopting the structure in steel bracket member directly to the bracket member made of aluminum alloy, bound bumpers and proof There was a problem that the strength was insufficient with respect to the load input to the bracket member via the vibration base.

  Further, in the strut mount, it is necessary to hold the bound bumper on the bottom surface side of the bracket member. For this reason, the cup member is attached to the bottom surface side to store and hold the base end portion of the bound bumper. However, in order to attach the cup member to the bottom surface side of the bracket member, caulking work or welding work is required. As a result, there was a problem that the assembly cost increased.

  The present invention has been made to solve the above-described problems, and an object of the present invention is to provide a strut mount capable of significantly reducing the weight while reducing the assembly cost.

In order to achieve this object, a strut mount according to a first aspect of the present invention includes an inner cylinder fixed to a rod tip of a shock absorber, a vibration-proof base made of a rubber-like elastic body vulcanized and bonded to the inner cylinder, and an anti-vibration base thereof. A pair of upper and lower upper and lower bracket members that define a storage portion in which a vibration base is stored, and a bound bumper holding member that holds a bound bumper that acts as a stopper when the shock absorber is compressed. The upper and lower bracket members are each made of an aluminum alloy, and the bound bumper holding member is integrally formed on the lower surface side of the lower bracket member, and the upper bracket member is the lower bracket member An upper bracket overlapping wall portion that is attached to the vehicle body side in a state of being overlapped with each other, and a lid wall of the storage portion. The lid is formed by compressing the anti-vibration base between the lower bracket member and having an opening at a substantially central portion thereof, and is interposed between the lid wall portion and the upper bracket overlapping wall portion. An inclined wall portion that is inclined in a taper shape that spreads upward in a sectional view in the axial direction, the lid wall portion and the inclined wall portion are formed thicker than the upper bracket overlapping wall portion, and the inclined wall portion is The taper slope angle θ1 formed by the upper surface formed in the taper shape extending upward in the direction section is made smaller than the taper inclination angle θ2 formed by the lower surface formed in the taper shape extending upward, and the thickness of the inclined wall portion is reduced. It is comprised so that it may increase gradually as it goes to the upper bracket overlapping wall part from the said lid wall part.

The strut mount according to claim 2 is the strut mount according to claim 1 , wherein the lower bracket member projects to a peripheral wall portion forming a peripheral wall of the storage portion and an inner peripheral surface side at one end side of the peripheral wall portion. A bottom wall portion that forms a bottom wall of the storage portion and has an opening for inserting the inner cylinder at a substantially central portion, and is interposed between the bottom wall portion and the peripheral wall portion and viewed in an axial sectional view. And at least the inner peripheral surface side of the peripheral wall portion is curved in an arc shape and the other end side of the peripheral wall portion projects to the outer peripheral surface side and is attached to the vehicle body side in a state of being overlapped with the upper bracket member. A lower bracket overlapping wall portion, the lower bracket overlapping wall portion is formed thinner than the peripheral wall portion, and the bottom wall portion is formed thicker than the peripheral wall portion, Of the first bending portion. Arc of radius of curvature located on the inner peripheral surface side of the peripheral wall portion in the cross section, compared the thickness of the peripheral wall portion is in a range of 2 times 3 times.

A strut mount according to a third aspect is the strut mount according to the second aspect , wherein the bound bumper holding member is integrally formed on an outer peripheral surface side of the first curved portion in the sectional view in the axial direction.

The strut mount according to claim 4 is the strut mount according to claim 2 or 3 , wherein the lower bracket member is interposed between the lower bracket overlapping wall portion and the peripheral wall portion and viewed in the axial sectional view. The second curved portion is curved in an arc shape, and the radius of curvature of the arc located on the outer peripheral surface side of the peripheral wall portion in the axial sectional view of the second curved portion is the axial direction of the first curved portion It is made smaller than the curvature radius of the circular arc located in the inner peripheral surface side of the said surrounding wall part in a cross sectional view.

The strut mount according to claim 5 is the strut mount according to any one of claims 1 to 4 , wherein the upper bracket member is interposed between the upper bracket overlapping wall and the inclined wall portion. A third bending portion that is curved in an arc shape when viewed, and a fourth bending portion that is interposed between the inclined wall portion and the lid wall portion and is curved in an arc shape when viewed in the axial direction. The radius of curvature of the arc located on the lower surface side of the upper bracket overlapping wall in the axial cross-sectional view of the curved portion is the largest among the arcs in the axial cross-section of the third curved portion and the fourth curved portion.

According to the strut mount of claim 1 , since the upper bracket member and the lower bracket member are made of an aluminum alloy, it is possible to achieve a significant weight reduction as compared with a conventional product made of iron. effective. In addition, since the bound bumper holding member is formed integrally with the lower bracket member, it is possible to simplify the assembly process by eliminating the need to join these members together (caulking work, welding work, etc.). There is an effect that the assembly cost can be greatly reduced.
Further, since the lid wall portion and the inclined wall portion are formed thicker than the upper bracket overlapping wall portion, there is an effect that it is possible to simultaneously achieve weight reduction and strength securing. That is, since the upper bracket overlapping wall portion is formed thinner, there is an effect that the weight of the entire strut mount can be reduced. On the other hand, since the lid wall portion and the inclined wall portion are formed thicker, there is an effect that a high strength can be ensured against a load input to the lid wall portion via the vibration isolating base.
In addition, such a thickness change cannot be imparted by a conventional iron press product, and can be imparted only by constituting an aluminum alloy as in the present invention. And securing strength can be achieved at the same time.
In addition, since the thickness of the inclined wall portion is configured to gradually increase from the lid wall portion toward the upper bracket overlapping wall portion, a higher strength can be obtained with respect to a load input to the lid wall portion via the vibration isolating base. There is an effect that it can be effectively secured.

According to the strut mount of the second aspect , in addition to the effect achieved by the strut mount of the first aspect , the lower bracket overlapping wall portion is formed thinner than the peripheral wall portion, so that the weight of the entire strut mount is reduced. There is an effect that can be. On the other hand, since the bottom wall portion is formed thicker than the peripheral wall portion, there is an effect that a high strength can be secured against a load input to the bottom wall portion via the bound bumper.

  Such thickness changes cannot be applied with conventional iron press products, and can only be applied with an aluminum alloy as in the present invention, thereby reducing weight. And securing strength can be achieved at the same time.

  In addition, since the radius of curvature of the arc located on the inner peripheral surface side of the peripheral wall portion in the axial section of the first curved portion is set in a range of about twice to about three times the plate thickness of the peripheral wall portion, it is lightweight. There is an effect that the strength of the bottom wall portion can be effectively ensured while achieving a reduction in size.

  That is, by defining the ratio between the radius of curvature and the plate thickness within the above range, stress concentration tends to occur while suppressing the plate thickness of the peripheral wall portion from being unnecessarily thick and reducing the weight. Stress can be distributed by making the base of the bottom wall part an arc with a sufficiently large radius of curvature, ensuring the strength against the load input to the bottom wall part through the bound bumper Can do.

According to the strut mount of the third aspect , in addition to the effect produced by the strut mount of the second aspect , the bound bumper holding member is integrally formed on the outer peripheral surface side of the peripheral wall portion in the axial section of the first bending portion. The thickness of the first curved portion can be increased, and as a result, there is an effect that the strength of the bottom wall portion can be efficiently ensured with a minimum increase in weight.

  That is, if the wall thickness is secured only to ensure strength, the achievement of weight reduction is impeded, and thus the role of holding the bound bumper by integrally forming the bound bumper holding member at a predetermined position, If it is configured to double the role of ensuring the thickness (that is, ensuring the strength), it is possible to efficiently achieve weight reduction as a whole while ensuring the strength at the predetermined position.

According to the strut mount of the fourth aspect , in addition to the effect exhibited by the strut mount of the second or third aspect, the radius of curvature of the arc positioned on the outer peripheral surface side of the peripheral wall portion in the axial section of the second curved portion is set. Since the radius of curvature of the arc located on the inner peripheral surface side of the peripheral wall portion in the axial cross section of the first curved portion is smaller than that, unnecessary thickening of the second curved portion or the second curved portion Unnecessary increase in diameter can be avoided, and as a result, there is an effect that weight reduction can be achieved effectively while ensuring the strength of the second bending portion.

According to the strut mount according to claim 5, in addition to the effects of the strut mount of the mounting serial to any one of claims 1 to 4, located on the lower surface of the upper bracket polymerization walls in axial section of the third curved portion Since the radius of curvature of the arc is the largest among the arcs in the axial cross section of the third and fourth curved portions, the lid wall is interposed via the vibration-proof base while reducing the overall weight. There is an effect that it is possible to effectively ensure a higher strength against the load input to the portion.

It is a front view of the strut mount in one embodiment of the present invention. It is sectional drawing of the strut mount in the II-II line | wire of FIG. It is a partial expanded sectional view of a lower bracket member. It is a partial expanded sectional view of an upper bracket member.

100 Strut mount 1 Inner cylinder 1a Flange (part of inner cylinder)
2 Anti-vibration base 3 Lower bracket member 3a Peripheral wall portion 3b Bottom wall portion 3c First curved portion 3d Lower bracket overlapping wall portion 3e Second curved portion 3f Bound bumper holding member 4 Upper bracket member 4a Upper bracket overlapping wall portion 4b Lid Wall part 4c Inclined wall part 4c1 3rd bending part 4c2 4th bending part 20 Rod (a part of shock absorber)
30 Bound bumper 40 Nut t1 Lower bracket overlap wall thickness t2 Perimeter wall thickness t3 Bottom wall thickness t4 Upper bracket overlap wall thickness t5 Lid wall thickness t6 Inclined wall thickness Thickness Ri1 Arc radius of curvature Ri3 located on the inner peripheral side of the peripheral wall portion of the first curved portion Ri3 Arc radius of curvature Ri5 located on the outer peripheral side of the peripheral wall portion of the second curved portion Located on the lower surface of the upper bracket overlapping wall of the third curved portion Arc curvature radii Ri5 to Ro8 Curvature radii θ1, θ2 of each arc of the third and fourth curved portions Tapered inclination angle

  DESCRIPTION OF EXEMPLARY EMBODIMENTS Hereinafter, preferred embodiments of the invention will be described with reference to the accompanying drawings. FIG. 1 is a front view of a strut mount 100 according to an embodiment of the present invention, and FIG. 2 is a cross-sectional view of the strut mount 100 taken along line II-II in FIG.

  In FIG. 2, the shock absorber rod 20, the bound bumper 30, and the nut 40 screwed to the tip of the rod 20 are virtually illustrated using a two-dot chain line.

  In the present embodiment, a description will be given using a strut mount 1 used for a front suspension of an FR type automobile as an application target of the present invention. However, it is naturally possible to apply the present invention to a different strut mount.

  The strut mount 100 is for supporting the tip of a shock absorber (rod 20) on the side of a vehicle body (not shown). As shown in FIGS. 1 and 2, the inner cylinder 1, the vibration isolating base 2, The lower and upper bracket members 3 and 4 are mainly provided.

  As shown in FIG. 2, the inner cylinder 1 is a cylindrical body made of a steel material, and a rod 20 of a shock absorber (not shown) is inserted into the inner peripheral side of the cylindrical body. The rod 20 is fastened and fixed to the inner cylinder 1 by a nut 40 screwed to the tip thereof. At the upper end portion (upper side in FIG. 2) of the inner cylinder 1, a flange portion 1 a is formed so as to project in a radial shape in a flange shape.

  As shown in FIG. 2, the anti-vibration base 2 is configured from a rubber-like elastic body to a donut-like body, and is vulcanized and bonded to the flange portion 1 a of the inner cylinder 1. As will be described later, the vibration-isolating base 2 is housed in a compressed state in a housing portion defined by the lower and upper bracket members 3 and 4 and given a predetermined pre-compression.

  As shown in FIGS. 1 and 2, the lower and upper bracket members 3 and 4 are constructed as cold forged products made of aluminum alloy, and the above-mentioned vibration isolator is obtained by superimposing these bracket members 3 and 4 together. A storage portion for storing the base 2 is defined.

  Thus, in the strut mount 100 according to the present embodiment, since the lower and upper bracket members 3 and 4 are made of an aluminum alloy, the weight of the strut mount 100 is greatly reduced compared to a conventional product made of iron. be able to. Moreover, since it comprised as a cold forging product, compared with a hot forging product, a significant reduction in processing cost can be aimed at.

  Both bracket members 3 and 4 are fixed to a vehicle body (not shown) by a plurality of (three in the present embodiment) bolts 5. Further, as shown in FIG. 1, the bolts 5 are arranged at substantially equal intervals in the circumferential direction (approximately 120 degrees in the present embodiment).

  Further, as shown in FIG. 2, a bound bumper holding member 3 f for holding the bound bumper 30 is integrally formed on the lower surface side (the lower side in FIG. 2) of the lower bracket member 3. Therefore, it is not necessary to perform joining work (caulking work, welding work, etc.) of these two members (lower bracket member 3 and bound bumper holding member 3f) unlike the conventional product. As a result, the assembly process can be simplified, and as a result, the assembly cost can be greatly reduced.

  Here, the bound bumper 30 is formed in a substantially cylindrical shape from a rubber-like elastic body, high-quality urethane, or the like, and acts as a stopper when the shock absorber is compressed. That is, when the compression allowance of the shock absorber exceeds a predetermined value, the bound bumper 30 is compressed and deformed between the shock absorber body (not shown) and the bottom wall portion 3b of the lower bracket member 3. Demonstrates stopper action (buffer action) against large load input.

  As described above, the lower and upper bracket members 3, 4 compress the vibration-isolating base 2 in the vertical direction (the vertical direction in FIG. 2) by overlapping the members 3, 4, so In a state where compression is applied, it is bonded and fixed as shown in FIG.

  Here, in the present embodiment, a mechanical clinching is used as the joining and fixing means, in which the bracket members 3 and 4 are crushed and joined in the plate thickness direction. Thereby, compared with the conventional welding means, a large current for welding, cooling water, and the like are no longer necessary, and the energy used can be reduced, so that the joining cost can be greatly reduced.

  As shown in FIG. 2, the lower bracket member 3 includes a peripheral wall portion 3a, a bottom wall portion 3b, a first bending portion 3c, a lower bracket overlapping wall portion 3d, a second bending portion 3e, and a bound bumper. The holding member 3f is mainly provided, and is formed in a substantially deep dish shape as a whole. Moreover, as shown in FIG. 1, it is formed in a substantially triangular shape when viewed from above. The detailed configuration of the lower bracket member 3 will be described later (see FIG. 3).

  As shown in FIG. 2, the upper bracket member 4 mainly includes an upper bracket overlapping wall portion 4a, a lid wall portion 4b, and an inclined wall portion 4c, and is formed in a stepped plate shape as a whole. An opening 4b1 is formed through substantially the center, and a space for fastening the nut 40 is secured by the opening 4b1.

  Further, as shown in FIG. 1, the upper bracket member 4 is formed in a substantially triangular shape slightly smaller than the lower bracket member 3 described above, and a circumferential position (a top position of the triangle) is formed. They are overlaid in a consistent state. The detailed configuration of the upper bracket member 4 will be described later (see FIG. 4).

  Next, a detailed configuration of the lower bracket member 3 will be described with reference to FIG. FIG. 3 is a partially enlarged cross-sectional view of the lower bracket member 3. 3 corresponds to a sectional view taken along line II-II in FIG. 1, that is, an axial sectional view.

  Here, as described above, when the compression amount of the shock absorber exceeds a predetermined amount and the stopper action by the bound bumper is exhibited, the upper end surface of the bound bumper 30 is the bottom wall portion 3b of the lower bracket member 3. Is pushed upward (upper side in FIG. 2), an extremely large load (for example, about 4.5 t) acts on the bottom wall portion 3b (see FIG. 2).

  Therefore, simply replacing the structure of the iron bracket member (conventional product) with an aluminum alloy as it is cannot secure the strength and durability against such a load. Therefore, as will be described later, the lower bracket member 3 in the present embodiment is configured so that the strength of the bottom wall portion 3b can be effectively ensured while reducing the overall weight. .

  The peripheral wall portion 3a is a portion that forms the peripheral wall of the storage portion for storing the above-described vibration isolating base 2 (see FIG. 2), and as shown in FIG. A bottom wall portion 3b is formed on the lower right side, and a lower bracket overlapping wall portion 3d is formed to protrude in the radial direction on the outer peripheral surface side (upper left side in FIG. 3).

  The bottom wall portion 3b is a portion for forming the bottom wall of the storage portion described above (see FIG. 2), and as shown in FIG. 3, the inner cylinder 1 (see FIG. 2) is provided at a substantially central portion thereof. An opening 3b1 for insertion is formed. On the other hand, the lower bracket overlapping wall portion 3d is a portion that is attached to the vehicle body side in a state of being overlapped with the upper bracket overlapping wall portion 4a (see FIG. 2) of the upper bracket member 4, and the bolt 5 is fixed thereto. (See FIG. 2).

  Here, the plate thickness t1 of the lower bracket overlap wall portion 3d is formed to be thinner than the plate thickness t2 of the peripheral wall portion 3a (t1 <t2), and the plate thickness t3 of the bottom wall portion 3b is equal to that of the peripheral wall portion. It is formed thicker than the plate thickness t2 (t2 <t3). In this embodiment, t1 = 3 mm, t2 = 4 mm, and t3 = 6.5 mm.

Thus, since the lower bracket overlapping wall portion 3d is formed thinner than the peripheral wall portion 3a, the weight of the entire strut mount 100 can be reduced. On the other hand, since the bottom wall portion 3b is formed thicker than the peripheral wall portion, it is possible to ensure high strength against a load input to the bottom wall portion 3b via the bound bumper 30 (see FIG. 2).

  In addition, such a thickness change cannot be imparted by a conventional iron press product, and can be imparted for the first time only by constituting an aluminum alloy as in the present invention. And securing strength can be achieved at the same time.

  As shown in FIG. 3, the first curved portion 3 c is interposed between the peripheral wall portion 3 a and the bottom wall portion 3 b, and the inner peripheral surface side (the right side in FIG. 3) of the peripheral wall portion 3 a in the axial cross-sectional view has a radius of curvature. Ri1 is curved in an arc shape. In the present embodiment, the outside of the first bending portion 3c (the outer peripheral surface side of the peripheral wall portion 3a) is also curved in an arc shape, and the radius of curvature is Ro2.

  Here, the radius of curvature Ri1 of the arc on the inner side of the first curved portion 3c (the arc positioned on the inner peripheral surface side of the peripheral wall portion 3a) is approximately twice to approximately three times the plate thickness t2 of the peripheral wall portion 3a. It is within the range (2 × t2 ≦ Ri1 ≦ 3 × t2). Thereby, the intensity | strength of the bottom wall part 3b input via the bound bumper 30 with respect to a load can be ensured effectively.

  That is, by defining the ratio between the radius of curvature Ri1 and the plate thickness t2 within the above range, the plate thickness (t2) of the peripheral wall portion 3a is prevented from becoming unnecessarily thick, and the weight is reduced. By making the base of the bottom wall portion 3b where stress concentration is likely to occur an arc having a sufficiently large radius of curvature (Ri1), the stress can be dispersed, and the bottom wall portion 3b with respect to the load input via the bound bumper 30 The strength of the can be further secured.

  In the present embodiment, the radius of curvature of each arc of the first bending portion 3c is Ri1 = 10 mm and Ro2 = 20 mm.

  As shown in FIG. 3, the bound bumper holding member 3f is integrally formed on the outer peripheral surface side of the first curved portion 3c. More specifically, the bound bumper holding member 3f is formed to project downward (downward in FIG. 3) at the connecting portion between the outer peripheral surface of the first curved portion 3c and the lower surface of the bottom wall portion 3b.

  As a result, the thickness of the first curved portion 3c can be increased, and the strength of the bottom wall portion 3b can be effectively ensured. That is, if the thickness of the first curved portion 3c is increased only for securing the strength, the achievement of weight reduction is hindered. In this way, the bound bumper 30 is held and fixed to the bound bumper holding member 3f. By combining the role of and the role of ensuring the strength, it is possible to efficiently achieve the strength of the bottom wall portion 3b while reducing the overall weight.

  As shown in FIG. 3, a second curved portion 3 e that is curved in an arc shape when viewed in the axial direction is interposed between the peripheral wall portion 3 a and the lower bracket overlapping wall portion 3 d. The second curved portion 3e has a radius of curvature of an arc located on the inner side (the outer peripheral surface side of the peripheral wall portion 3a) as Ri3 and a radius of curvature of an arc located on the outer side (the inner peripheral side of the peripheral wall portion 3a). Ro4.

  Here, since the radius of curvature Ri3 of the arc inside the second curved portion 3e is smaller than the radius of curvature Ri1 of the arc inside the first curved portion 3c (Ri3 <Ri1), the radius of curvature of the second curved portion 3e Avoiding a reduction in weight due to unnecessary thickening, or a decrease in strength in the vicinity of the second bending portion 3e due to an unnecessary increase in diameter of the second bending portion 3e. it can.

  In the present embodiment, the radius of curvature of each arc of the second bending portion 3e is Ri3 = 7 mm and Ro4 = 11 mm.

  Next, a detailed configuration of the upper bracket member 4 will be described with reference to FIG. FIG. 4 is a partial enlarged cross-sectional view of the upper bracket member 4. 4 corresponds to a cross-sectional view taken along the line II-II in FIG. 1, that is, an axial cross-sectional view.

  Here, at the time of compression deformation of the shock absorber, a load corresponding to the damping action acts on the lid wall portion 4b of the upper bracket member 4 from the flange portion 1a of the inner cylinder 1 through the vibration isolation base 2, thereby preventing vibration. Since the upper end surface of the base body 2 pushes up the lid wall portion 4b of the upper bracket member 4 upward (upper side in FIG. 2), an extremely large load (for example, about 1 t) always acts on the lid wall portion 4b (see FIG. 2).

  Therefore, simply replacing the structure of the iron bracket member (conventional product) with an aluminum alloy as it is cannot secure the strength and durability against such a load. Therefore, as will be described later, the upper bracket member 4 in the present embodiment is configured such that the strength of the lid wall portion 4b can be effectively ensured while reducing the overall weight.

  The upper bracket overlapping wall portion 4a is a portion that is attached to the vehicle body side in a state of being overlapped with the lower bracket overlapping wall portion 3d of the lower bracket member 3, and a bolt 5 is fixed (see FIG. 2). .

  On the other hand, the lid wall portion 4b is a part for forming the lid wall of the housing portion for housing the above-described vibration isolating base body 2 (see FIG. 2), and the vibration isolating base body 2 is attached to the bottom of the lower bracket member 3. It compresses between the wall parts 3b. Further, as described above, the opening 4b1 is formed in the substantially central portion.

  As shown in FIG. 4, the inclined wall portion 4 c is interposed between the upper bracket overlapping wall portion 4 a and the lid wall portion 4 b, and has a tapered shape (inverted C shape, FIG. 2). Thus, the upper bracket member 4 is formed in a stepped plate shape.

  As shown in FIG. 4, the inclined wall portion 4c has a taper-like inclination angle on the upper surface side of θ1, a taper-like inclination angle on the lower surface side of θ2, and both angles satisfy θ1 <θ2. It is configured as follows. In this embodiment, θ1 = 106 ° and θ2 = 116 °.

  Here, the plate thickness t5 of the lid wall portion 4b and the plate thickness t6 of the inclined wall portion 4c are formed thicker than the plate thickness t4 of the upper bracket overlap wall portion 4a (t4 <t5, t4 <t6). . Thus, weight reduction and securing of strength can be achieved at the same time by defining the plate thicknesses t4 to t6 of the members 4a to 4c.

  That is, by forming the plate thickness t4 of the upper bracket overlapping wall portion 4a to be thinner than the lid wall portion 4b and the inclined wall portion 4c, the weight of the entire strut mount 100 can be reduced accordingly. On the other hand, by forming the plate thickness t5, t6 of the lid wall portion 4b and the inclined wall portion 4c to be thicker than the upper bracket overlapping wall portion 4a, the load input to the lid wall portion 4b via the vibration isolating base 2 High strength can be secured.

  In addition, like the case of the lower bracket member 3 described above, such a thickness change cannot be imparted by a conventional iron press product, and is not made until it is made of an aluminum alloy as in the present invention. Thus, weight reduction and securing of strength can be achieved at the same time.

  Here, as described above, the inclined wall portion 4c has the tapered inclination angle θ1 on the upper surface side (upper side surface in FIG. 4) smaller than the tapered inclination angle θ2 on the lower surface side (θ1 <θ2). The thickness t6 of the inclined wall portion 4c gradually increases from the lid wall portion 4b side toward the upper bracket overlapping wall portion 4a side (t6a <t6b).

  Thereby, the intensity | strength of the cover wall part 4b (and inclined wall part 4c) with respect to the load input via the vibration proof base 2 can be ensured more effectively, aiming at weight reduction as a whole. Moreover, since the area of the upper surface side of the upper bracket overlapping wall portion 4a is increased, the contact area with the vehicle body (not shown) can be increased correspondingly, and the mounting state of the strut mount 100 can be stabilized. it can.

  In the present embodiment, the plate thickness of the upper bracket overlapping wall portion 4a is t4 = 3 mm, and the plate thickness of the lid wall portion 4b is t5 = 3.5 mm. Further, the plate thickness t6 of the inclined wall portion 4c is defined by the tapered inclination angles θ1 and θ2 described above.

  Between the upper bracket overlapping wall 4a and the inclined wall portion 4c, as shown in FIG. 4, a third curved portion 4c1 that is curved in an arc shape in the axial sectional view is interposed, and the inclined wall portion 4c and Between the lid wall portion 4b, a fourth curved portion 4c2 that is curved in an arc shape in an axial sectional view is interposed.

  The third curved portion 4c1 has a radius of curvature Ri5 on the inner side (the lower surface side of the upper bracket overlapping wall 4a, the lower side in FIG. 4), and the outer side (the upper surface side of the upper bracket overlapping wall 4a, the upper side in FIG. 4). The radius of curvature of the arc located at) is Ro6.

  On the other hand, the fourth bending portion 4c2 has a radius of curvature Ri7 on the inner side (the upper surface side of the lid wall portion 4b, the upper side in FIG. 4), and the outer side (lower surface side of the lid wall portion 4b, the lower side in FIG. 4). The radius of curvature of the arc located at) is Ro8.

  Of these curvature radii Ri5 to Ro8, the curvature radius Ri5 of the arc inside the third bending portion 4c1 is the largest (Ro6, Ri7, Ro8 <Ri5). Thereby, the intensity | strength of the cover wall part 4b (and inclined wall part 4c) with respect to the load input via the vibration proof base 2 can be ensured still more effectively, aiming at weight reduction as a whole.

  In the present embodiment, the curvature radii of the arcs of the third and fourth curved portions 4c1 and 4c2 are Ri5 = 10 mm and Ro6 = Ri7 = Ro8 = 5 mm.

  The present invention has been described above based on the embodiments, but the present invention is not limited to the above embodiments, and various improvements and modifications can be made without departing from the spirit of the present invention. It can be easily guessed.

  For example, the numerical values raised in the present embodiment are merely examples, and other numerical values can naturally be used.

  In the present embodiment, the case where the lower and upper bracket members 3 and 4 are joined by mechanical clinching has been described. However, the present invention is not necessarily limited to this, and is joined by other means (for example, welding or the like). Of course it is possible.

  ADVANTAGE OF THE INVENTION According to this invention, it can contribute to the weight reduction of a strut mount, and the reduction of assembly cost.

Claims (5)

A pair of upper and lower upper sides that define an inner cylinder fixed to the rod end of the shock absorber, a vibration-proof base vulcanized and bonded to the inner cylinder, and a storage section for storing the vibration-proof base And a strut mount comprising a lower bracket member and a bound bumper holding member for holding a bound bumper that acts as a stopper when the shock absorber is compressed,
The upper and lower bracket members are each made of an aluminum alloy, and the bound bumper holding member is integrally formed on the lower surface side of the lower bracket member,
The upper bracket member is
An upper bracket overlapping wall portion attached to the vehicle body in a state of being superimposed on the lower bracket member;
A lid wall portion that forms a lid wall of the storage portion and compresses the vibration-proof base between the lower bracket member and has an opening at a substantially central portion thereof;
An inclined wall portion that is interposed between the lid wall portion and the upper bracket overlapping wall portion and is inclined in a taper shape spreading upward in the axial cross-sectional view,
The lid wall portion and the inclined wall portion are formed to be thicker than the upper bracket overlapping wall portion,
The inclined wall portion has a tapered inclination angle θ1 formed by an upper surface formed in an upwardly tapered shape in an axial section smaller than a tapered inclination angle θ2 formed by a lower surface formed in an upwardly extending tapered shape, A strut mount, characterized in that the thickness of the inclined wall portion is gradually increased from the lid wall portion toward the upper bracket overlapping wall portion. The lower bracket member is
A peripheral wall portion forming a peripheral wall of the storage portion;
A bottom wall portion that has an opening at a substantially central portion that extends to the inner peripheral surface side at one end side of the peripheral wall portion to form the bottom wall of the storage portion and through which the inner cylinder is inserted;
A first curved portion that is interposed between the bottom wall portion and the peripheral wall portion, and at least an inner peripheral surface side of the peripheral wall portion is curved in an arc shape in an axial sectional view;
A lower bracket overlapping wall portion that is attached to the vehicle body in a state of being overlaid with the upper bracket member and projecting to the outer peripheral surface side at the other end side of the peripheral wall portion,
The lower bracket overlapping wall part is formed thinner than the peripheral wall part, and the bottom wall part is formed thicker than the peripheral wall part,
The radius of curvature of the arc located on the inner peripheral surface side of the peripheral wall portion in the axial section of the first curved portion is in a range of 2 to 3 times the plate thickness of the peripheral wall portion. 2. The strut mount according to claim 1, wherein The strut mount according to claim 2, wherein the bound bumper holding member is integrally formed on an outer peripheral surface side of the first bending portion in the axial sectional view. The lower bracket member includes a second bending portion that is interposed between the lower bracket overlapping wall portion and the peripheral wall portion and is curved in an arc shape in the axial sectional view,
The radius of curvature of the arc located on the outer peripheral surface side of the peripheral wall portion in the axial sectional view of the second curved portion is located on the inner peripheral surface side of the peripheral wall portion in the axial sectional view of the first curved portion. The strut mount according to claim 2 or 3, wherein the strut mount is smaller than a radius of curvature of the arc. The upper bracket member is
A third curved portion interposed between the upper bracket overlapping wall and the inclined wall portion and curved in an arc shape in the axial cross-sectional view;
A fourth curved portion interposed between the inclined wall portion and the lid wall portion and curved in an arc shape in the axial cross-sectional view;
The radius of curvature of the arc located on the lower surface side of the upper bracket overlapping wall in the axial sectional view of the third curved portion is the largest of the arcs in the axial sectional view of the third curved portion and the fourth curved portion. The strut mount according to any one of claims 1 to 4, wherein the strut mount is provided.

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