WO2001047737A1

WO2001047737A1 - Exhaust pipe supporting device

Info

Publication number: WO2001047737A1
Application number: PCT/JP2000/008098
Authority: WO
Inventors: Naoki Yamaguchi; Kenji Murase
Original assignee: Toyo Tire & Rubber Co., Ltd.
Priority date: 1999-12-28
Filing date: 2000-11-16
Publication date: 2001-07-05
Also published as: JP3393294B2; JP2001180301A

Abstract

An exhaust pipe supporting device for vibration-proofingly supporting the exhaust pipe of an automobile on the car body, which is intended to reduce the dynamic absolute spring constant over a wide frequency domain and effectively prevent noise during the high speed rotation of the engine, so as to improve the quietness of the vehicle. As a means therefor, in a supporting device (A) integrally molded of elastic material and comprising a first holder (1) for a support member on the vehicle body side, a second holder (2) for a support member on the exhaust pipe side, a pair of side walls (3, 3) connecting these two holders with a spacing defined there between, and a central vibration control section (5) disposed in an intermediate position between the two holders and connected to the two side walls, respective portions between the two side walls of the first and second two holders are formed with cutout portion (6) or thin-walled portions (7) to moderately release vibrational load during vibration in the high frequency area.

Description

Description Exhaust pipe support device (Technical field)

The present invention relates to a muffler for an automobile, that is, an exhaust pipe support device for supporting an exhaust pipe to a vehicle body in a vibration-proof manner.

[Background technology]

Conventionally, as a support device for supporting an exhaust pipe to a vehicle body in a vibration-proof manner, a support device integrally formed of an elastic material such as rubber and having a through hole through which a support material on the vehicle body side is inserted. The holding part and the second holding part having a through hole into which the exhaust pipe-side support material is inserted are connected by left and right side walls so as to face each other at an interval vertically and as a whole. It is known that the ring member is formed in a substantially annular shape and the vibration is absorbed by an elastic material. Normally, this support device is arranged at a plurality of locations at predetermined intervals in the longitudinal direction of the exhaust pipe, and the exhaust pipe is supported on the vehicle body via these support devices.

Also, in order to extend the effect of suppressing vibration transmission to a high frequency range, the left and right side walls are connected at an intermediate position between the first and second holding portions to suppress lateral sway. There has been proposed an arrangement in which a central vibration damper is provided (for example, Japanese Patent No. 2558505).

In order to further improve the effect of suppressing vibration transmission in consideration of a rise in temperature during traveling, the present applicant also considers that the central portion of the central vibration damping portion is a mass portion, and both side portions extending from the mass portion. (See Japanese Patent No. 2863610). A support device is proposed in which a central vibration damping portion is formed, each of which is bifurcated and connected to both side walls.

FIG. 16 shows the supporting device proposed above, where 101 is the first holding unit, 1 Numeral 02 denotes a second holding portion, which has through holes 11 1 and 12 1 for inserting a support material, respectively. 103 and 103 are both side walls connecting the first and second holding parts 101 and 121, and 105 is a central damping part with the center being a mass part 105a. As shown in the figure, both sides are bifurcated to form a substantially X shape.

However, in the case of the support device provided with the above-mentioned central X-shaped vibration damper 105, the effect of suppressing vibration transmission particularly in the frequency range of 300 to 400 Hz is improved. In the high frequency range above 600 Hz, the dynamic absolute spring constant is high, the vehicle noise and vibration are high, and the noise prevention cannot be sufficiently satisfied. The effect was not sufficiently obtained.

The present invention has been made in view of the above, and as this type of exhaust pipe support device, the dynamic absolute not only in the frequency region of 600 Hz or less but also in the frequency region of 600 Hz or more. The spring constant can be reduced, and the dynamic absolute spring constant can be reduced over a wide frequency range, effectively preventing noise during high-speed engine rotation and contributing to improved vehicle quietness. It is like that.

[Disclosure of the invention]

A first exhaust pipe support device of the present invention is a first holding portion integrally formed of a material having elasticity and having a through hole into which a support material of a vehicle body is inserted, and a support material of an exhaust pipe side A second holding portion having a through hole into which the first and second holding portions are inserted, and a pair of side wall portions connecting the first holding portion and the second holding portion at both sides thereof with an interval therebetween, and between the first and second holding portions. An exhaust pipe support device having a central vibration-damping portion arranged at an intermediate position of and integrally connected to the both side wall portions, wherein the first holding portion and the second holding portion are each It is characterized in that it is cut off at one part between both side walls.

According to the exhaust pipe support device having the above configuration, the support member on the vehicle body side is inserted. When the first holding portion and the second holding portion into which the exhaust pipe-side support member is inserted vibrate relative to each other, for example, vibrate in the near and far directions, the first and second holding portions The rigidity of both side walls connecting the parts is appropriately increased by the central damping part, and the rigidity in the lateral direction is also increased. This is coupled with the resonance action of the central damping part, and Fluctuation, that is, vibration is effectively damped and suppressed.

In particular, since the first and second holding portions are partly separated, the vibrating load applied from the support material is appropriately released by the separated portion during vibration in a high frequency range. Therefore, the dynamic absolute spring constant is reduced over a wide frequency range as compared with the case of the conventional holding part which completely holds the entire circumference of the supporting material. In particular, the dynamic absolute spring constant decreases even in the high frequency range exceeding 600 Hz. This effectively prevents noise during high-speed rotation of the engine, and contributes to improving the quietness of the vehicle.

In the above-mentioned exhaust pipe support material, it is particularly preferable in terms of operation that the cut-off portion is formed so as to have a gap of 0.5 mm or more between the cut end faces. In other words, when the gap at the cut-off portion is less than 0.5 mm, the effect of releasing the vibration load is reduced, so that it is preferable to set as described above.

The second exhaust pipe support device of the present invention includes a support device having a common basic configuration with the first invention, that is, a first holding portion and a second holding portion similar to the above, a pair of side wall portions, and a central control portion. In the exhaust pipe supporting device provided with a vibrating part, the first holding part and the second holding part are formed to be thin at one part between the side wall parts instead of the cut-off part. The thin portion can be formed thin by providing a recess in a part of the holding portion. It is preferable that the concave portion forming the thin portion has a width of 0.5 mm or more in terms of an action of releasing a vibration load.

Also in the exhaust pipe support device of the present invention, the rigidity of the pair of side walls is moderate. The moderate damping by the central damping part and the resonance action of the central damping part not only effectively attenuate the fluctuations of the first and second holding parts, that is, the vibrations, In particular, since a part of the first and second holding parts is thin, when the vibration is generated in a high frequency range, the thin part appropriately releases the load caused by the vibration displacement of the support material. The dynamic absolute spring constant is reduced in a wide frequency range including a high frequency range exceeding 600 Hz. Therefore, also in the present invention, it is possible to effectively prevent noise during high-speed rotation of the engine, and to contribute to improvement in quietness of the vehicle.

In the exhaust pipe support device according to the first or second invention, the first holding portion and the second holding portion each include a support member inserted into a through-hole at a portion other than the cut-off portion or the thin portion. It is preferable to have at least one-half of the entire circumference. That is, it is not preferable that the portion other than the cut-out portion or the thin-walled portion is smaller than the above-described portion, because the effect of holding the support material is reduced and the dust is more likely to occur. In the exhaust pipe supporting device according to each of the inventions, the central vibration damping portion has a central portion formed as a mass portion, and both side portions extending from the mass portion, and the mass portion has both side portions. It is preferable that the mass is formed large, and the both side portions are each formed in a bifurcated shape and connected to the both side wall portions.

As a result, the rigidity of the central vibration damper in the diagonal direction increases, and when the ambient temperature of the support device rises and the elastic material such as rubber softens and the rigidity of the entire device decreases, As the side wall portion expands by its own weight such as the exhaust pipe, the bifurcated portion also expands, and the Young's modulus of the branched portion increases. Combined with the distribution, the vibration can be effectively attenuated by the resonance action of the central vibration suppression unit, and the frequency characteristics are prevented from shifting to the lower frequency side as the temperature rises. However, stable frequency characteristics can be maintained. Further, the present invention provides a support device having the same basic configuration as that of the first invention, that is, an exhaust pipe including a first holding portion and a second holding portion similar to the above, a pair of side wall portions, and a central vibration damping portion. In the support device, a cut-off portion or a thin-walled portion may be provided in a part of the central vibration damping portion.

In this case, the central vibration damping portion has a central portion formed as a mass portion, and both side portions extending from the mass portion, and the both side portions are each formed in a bifurcated shape to form the two side walls. It is preferable that the cut-off portion or the thin portion is formed on at least one of the bifurcated portions on at least one side of the both side portions.

In the case of the present invention, the peak of the dynamic absolute spring constant appears due to the resonance due to the bending of the central vibration damper, and the absolute spring constant is effectively reduced in the frequency range of 400 to 500 Hz. You can do it.

Further, the present invention provides a support device having a basic configuration common to the first invention, that is, an exhaust pipe support including a first holding portion and a second holding portion similar to those described above, a pair of side wall portions, and a central damping portion. In the device, a cut-off portion or a thin portion may be provided in a part of the side wall portion.

In the case of the present invention, the resonance of the side walls can be suppressed in the frequency range of 700 to 100 Hz due to the resonance of the side walls, and the rise of the dynamic absolute panel can be suppressed.

In any of the above cases, it is preferable to set the width of the gap between the cut-off portions or the width of the concave portion forming the thin portion to 0.5 mm or more from the viewpoint of releasing the vibration load. .

[Brief description of drawings]

FIG. 1 is a perspective view showing an exhaust pipe support device according to one embodiment of the first invention.

FIG. 2 is a front view of the supporting device. Fig. 3 is a cross-sectional side view taken along line X-X in the previous figure.

FIG. 4 is a cross-sectional view taken along the line YY.

FIG. 5 is a partial front view showing another embodiment of the above supporting device. FIG. 6 is a partial front view showing still another embodiment of the above supporting device.

FIG. 7 is a front view showing an exhaust pipe support device according to one embodiment of the second invention.

FIG. 8 is a sectional view taken along the line ZZ of FIG.

FIG. 9 is a front view showing still another embodiment of the exhaust pipe supporting device of the above.

Figure 10 is a graph showing the relationship between frequency and dynamic absolute spring constant. FIG. 11 is a front view showing still another embodiment of the exhaust pipe support device of the present invention.

FIG. 12 is a front view showing still another embodiment of the exhaust pipe support device of the present invention.

FIG. 13 is a front view showing still another embodiment of the exhaust pipe supporting device of the present invention.

FIG. 14 is a front view showing still another embodiment of the exhaust pipe supporting device of the present invention.

FIG. 15 is a front view showing still another embodiment of the exhaust pipe supporting device of the present invention.

FIG. 16 is a front view illustrating a conventional support device.

BEST MODE FOR CARRYING OUT THE INVENTION Hereinafter, a preferred embodiment of an exhaust pipe support device of the present invention will be described with reference to the drawings, but the present invention is not limited thereto.

FIGS. 1 to 4 and FIGS. 5 and 6 show a supporting device A according to the first embodiment of the invention. As shown in the figure, the overall shape is a substantially elliptical shape with the long axis as the vertical direction when viewed from the front, and is formed integrally by vulcanizing and molding an elastic material, that is, a rubber material. It is configured as follows.

In the upper part of the support device A, a first holding portion 1 having a through hole 11 in the front-rear direction (thickness direction) into which a support material (not shown) mainly for the vehicle body is inserted is formed. A support member (not shown) on the exhaust pipe side is inserted at a lower position facing the first holding part 1 at a required interval (usually 10 to 15 mm) (thickness direction). The second holding portion 2 having the through hole 21 is formed.

The first holding portion 1 and the second holding portion 2 are connected by arch-shaped left and right side walls 3, 3 having both ends connected to both left and right sides, respectively. It is formed in a substantially elliptical annular shape. In other words, when viewed from the front, it is formed in a substantially elliptical annular shape whose major axis is a line passing through both axes of the upper and lower first and second holding portions 1 and 2.

In addition, the side walls 3 have small gaps 4 between the first and second holding portions 1 and 2 between the first and second holding portions 1 and 2, respectively. And connected at both ends by a central vibration damper 5 connected to the inner surfaces of the side walls 3, 3.

The gaps 4, 4 between the central vibration damping part 5 and the two holding parts 1, 2 are such that the central part of the central vibration damping part 5 hits the inner surfaces of the two holding parts 1, 2 during large amplitude vibration. The intervals are set so that they can serve as stoppers for restricting excessive deformation by contact.

Then, in the supporting device A having the above-described configuration, the first and second holding portions 1, 2 are respectively inserted into the through-holes 11, 21 at a portion between the side walls 3, 3. It is separated so as to have a gap that has almost no effect on the vibration characteristics in the low-frequency range by a dividing line that is substantially parallel to the axis of the shaft. The cut-off portion 6 is pressed so as to have a gap of 0.5 mm or more between the cut end faces. It is preferable that the cut portion 6 is cut and formed. For example, as shown in FIG. 5, the cut portion 6 may be cut so as to open substantially a half circumference of the through hole. In this case, it becomes easy to insert the support material into the through holes.

However, if the gap of the cut-off portion 6 is too large, the vibration characteristics in the low frequency range will be affected, and the effect of holding the support material inserted into the through holes 11 and 21 will be small. Therefore, it is preferable that the support member be formed so as to hold at least 1/2 of the entire circumference of the support member by the other portion except the cutoff portion 6.

The cut-off portion 6 is provided, as shown in FIGS. 2 and 5, on the side opposite to the center vibration damping portion 5 and, as shown in FIG. (The part 2 side is not shown).

FIGS. 7 and 8 show one embodiment of the second invention.

The supporting device A of this embodiment has basically the same configuration as that of the above-described embodiment, that is, the first holding portion 1 and the second holding portion 2, the pair of side wall portions 3, 3 and the central vibration damping portion 5. Is provided as a basic configuration. In the case of this support device, the first holding portion 1 and the second holding portion 2 are replaced with the first holding portion 1 and the second holding portion 2, each portion between the side wall portions 3, 3, for example, a central vibration damping portion. 5 is formed to be thin at the part on the opposite side with respect to it, and the rigidity of the holding part is weakened at this part. 7 shows the thin part.

Also in this embodiment, as in the case of the above-mentioned cut-off portion 6, the thin-walled portion 7 is formed in a part of the holding portions 1 and 2 by 0.5 mm in the circumferential direction of the through holes 11 and 21. By providing the concave portion 8 having the above width, it is preferable to form the portion of the concave portion 8 to be thin, and to be inserted into the through holes 11, 21 in other portions except the thin portion 7. It should be formed so that it can hold at least 1/2 of the entire circumference of the supporting material. The thickness of the thin portion 7 can be appropriately set so as to be suitable for releasing a vibration load against high-frequency vibration. Further, the thin portion 7 is connected to the first and second holding portions 1 and 2 on the side thereof. It is also possible to provide in a part.

In each of the above examples, the elastic material used had a rubber hardness of 50 degrees (based on the measurement method of the rubber hardness test specified in JISK-6301A of Japanese Industrial Standard). As described above, it is particularly preferable to use a rubber material of 55 to 70 degrees so that the required strength and static spring constant can be secured.

The supporting device A of the present invention configured as described above inserts and fixes the support material on the vehicle body side into the through hole 11 of the upper first holding portion 1 and fixes the lower second holding portion 2 A support material on the exhaust pipe side is inserted into the through hole 21 and fixed. In this way, the exhaust pipe is supported and used at a plurality of locations at a required interval in the longitudinal direction of the exhaust pipe.

In this use state, the vibration transmitted from the exhaust pipe side by the engine drive and the vibration transmitted from the vehicle body side are absorbed by the support device, and the noise and vibration in the vehicle interior are prevented from being deteriorated.

In the case of the present invention, the first and second holding portions 1 are provided by the central vibration damping portion 5 connecting the left and right side walls 3, 3 between the first and second holding portions 1, 2. The rigidity of both side walls 3 and 3 connecting, 2 is appropriately increased, and the lateral stiffness is higher than that without the central damping part. Therefore, when the first holding portion 1 and the second holding portion 2 relatively vibrate, for example, vibrate and displace in the perspective direction, the rigidity is increased, so that the central vibration damping portion 5 has a high rigidity. Combined with the resonance action, the fluctuation, that is, the vibration of the two holding portions 1 and 2 can be effectively attenuated and suppressed.

Furthermore, since the first and second holding portions 1 and 2 are provided with the cut-off portion 6 or the thin portion 7, when the vibration in a high frequency range, the holding portions 1 and 2 are cut off. The separated portion 6 or the thinned portion 7 acts so as to appropriately release the load due to the vibration displacement of the support material. As a result, the dynamic absolute dynamics over a wider frequency range than in the case of the conventional holder that embraces the entire circumference of the support material The spring constant will be reduced. In particular, the dynamic absolute spring constant decreases even in the high frequency range exceeding 600 Hz or 800 Hz. As a result, noise can be effectively prevented when the engine rotates at a high speed, and the quietness of the vehicle can be improved.

In any of the embodiments of the invention described above, the central vibration damping portion 5 includes a columnar central portion formed as a mass portion 5a, and both side portions 5b, 5b extending from the mass portion 5a. The mass portion 5a is formed to have a larger mass than both side portions 5b, 5b. Further, both side portions 5b, 5b are bifurcated to form a branch, and these branch portions 5c, 5c, 5c, 5c are connected to the side wall portions 3, 3, respectively, and are substantially X-shaped. Has made.

With this configuration, the rigidity of the central vibration damper 5 in the diagonal direction is increased, and the ambient temperature of the support device A is increased, and the elastic material such as rubber is softened and the rigidity of the entire device is increased. When the side wall portions 3, 3 extend under their own weight of the exhaust pipe or the like, the bifurcated branch portions 5 c, 5 c also extend and the branch portions 5 c, 5 c The Young's modulus of c increases, and this, coupled with the mass distribution due to the central part being mass part 5a, can effectively attenuate vibrations by the resonance action of the central vibration suppression part, and increase with temperature. It is possible to suppress the frequency characteristics from shifting to the lower frequency side, and to maintain stable frequency characteristics against temperature changes.

The mass part 5a of the central vibration damping part 5 is formed in a quadrangular prism shape by increasing the thickness in the vertical direction as shown in the figure, and the largest dimension in the front-rear direction of other parts excluding the mass part 5a That is, it is also possible to extend the first and second holding parts 1 and 2 longer than the front-rear dimension and have a larger mass. By appropriately setting the length and the position of the center of gravity, the mass in accordance with the purpose can be provided, and the frequency range in which the absolute spring constant can be reduced is further widened. It is also possible to embed a metal having a large specific gravity, such as iron, in the mass part 5a to have a large mass. Also, the branch legs 5c, 5c on both sides of the central vibration damping unit 5 are designed so that the combined thickness of both legs does not become larger than the vertical thickness of the mass unit 5a. It is formed into a thin plate shape, but its branch angle is 30 ° to 60 °, and the ratio (t / L) of its thickness t to length L is in the range of 0.1 to 0.5. It is preferable to set such that the vibration suppressing effect is obtained.

In addition, as shown in FIG. 9, the present invention is also applicable to a structure in which the central vibration damping portion 5 is stretched across the side wall portions 3 in a single horizontal character, as described above. Portions (not shown) can be formed and implemented. In this case as well, the dynamic absolute spring constant can be reduced in a wide frequency range, for example, even in a high frequency range exceeding 600 Hz or 800 Hz.

In order to confirm the effect of the above-described support device of the present invention, the first and second holding portions are each provided with a cut-out portion 6 in the form shown in FIGS. Example 1 (Example 1) having a diameter of 1.5 mm, an example (Example 2) shown in FIG. 5 having a cut-out portion 6 obtained by cutting a substantially half circumference of a through hole, and FIG. The relationship between the vibration frequency and the dynamic spring constant was measured and compared with the comparative example product (comparative example) of the conventional structure shown in 16. Figure 10 shows the results.

In each of the examples and comparative examples, the total length H in the vertical direction (longitudinal direction) is 65 mm, the width W is 55 mm, and the dimension T in the thickness direction of the first holding portion 1 is 25 mm. The dimension T1 in the thickness direction of the side wall 3 is 20 mm, the dimension W1 in the same width direction is 10 mm, the rubber hardness is 55 degrees, and the branch angle of the branch legs 5c, 5c is determined. 40 °, and the ratio of the thickness to the length was 0.3.

The above-mentioned dynamic absolute spring constant was measured using a dynamic characteristic determination tester (KC-V type) manufactured by Sagimiya Seisakusho using a rod-shaped support fitting inserted into the first and second holders of the support device. It is fixed to the jig of the dynamic characteristic tester, statically applies a predetermined load (5 kgf), and applies a predetermined vibration (acceleration 5 G-constant) by a vibrator. Given, 100 Hz-: Dynamic load when swept to LOOOH z. Measure the dynamic displacement (deflection) and its phase angle, and calculate the absolute spring constant by a predetermined calculation method. Performed by The absolute spring constant referred to in the present invention is an average value of values obtained by dividing a dynamic displacement generated by an excitation frequency by a dynamic load in the above-mentioned measuring method.

As is evident from Fig. 10, the comparative example, which is a conventional product, shows that the absolute spring constant gradually increases in the high frequency range where the frequency exceeds 600 Hz, reducing vibration and noise during high-speed rotation of the engine. Although the effect is small, in the case of the example product of the present invention, in the frequency range of 600 Hz or more, the absolute spring constant is significantly reduced as compared with the comparative example product, and the vibration transmission is suppressed and the noise is reduced. It turned out to be even more effective in prevention.

FIG. 11 shows an embodiment of the third invention.

The supporting device A of this embodiment has basically the same configuration as that of the above-described embodiment, that is, a basic configuration including a first holding portion 1 and a second holding portion 2, a pair of side wall portions 3, 3 and a central vibration damping portion 5. It is prepared for. In addition, in the case of the support device A, a cut-out portion 61 is provided in a part of the central vibration damper 5.

As shown in the figure, the cut-off portion 61 has a central portion formed as the central vibration-suppressing portion 5 and a mass portion 5a, and both side portions 5b and 5 extending from the mass portion 5a. b, the two side portions 5b and 5b are bifurcated, and the branch portions 5c, 5c, 5c, 5c are respectively connected to the both side wall portions 3, 3. In the case of an approximately X-shape, it is formed on at least one of the bifurcated branch portions 5c, 5c on at least one side (both sides in the figure) of the both sides 5b, 5b. Is good.

That is, in the case of the supporting device having the above-described substantially X-shaped central vibration damper 5, the second peak of the dynamic absolute panel constant is determined by resonance of the central vibration damper 5 due to bending. Appears in the vicinity of the frequency range of 50 to 500 Hz, but by providing the cut-off portion 61 in a part of the central vibration damper 5 as described above, The lowering of the second peak due to the resonance can be suppressed, and the absolute panel constant can be effectively reduced even in the frequency range of 400 to 500 Hz. In particular, if this is implemented in conjunction with the first or second invention described above, the effect will be greater.

It should be noted that a thin portion formed by a concave portion may be provided in a part of the central vibration damping portion 5 instead of the cut-off portion (not shown). In this case, the same effect as described above can be obtained. Further, not only the support device having the substantially X-shaped central vibration damper, but also the support device having the horizontal character-shaped central vibration damper, for example, is provided with the same separated portion and thin portion as described above. And the second peak of the second absolute panel constant in the frequency range of 400 to 500 Hz can be reduced.

In this embodiment, the width of the concave portion forming the gap or the thin portion of the cut-off portion 61 is preferably 0.5 mm or more, and particularly preferably 1. ◦ mm or more.

FIGS. 12 to 15 each show an embodiment of the exhaust pipe supporting device of the fourth invention.

Also in the support device A of the present invention, the configuration is basically the same as that of each of the above embodiments, that is, the first holding portion 1 and the second holding portion 2, the pair of side wall portions 3 and 3, and the central vibration As a basic configuration.

Further, in such a supporting device A, in the embodiment of FIG. 12, a cut-off portion 62 is provided in a part of the side walls 3, 3. In the case of FIG. 13, a concave portion 82 is provided on one or both of the inner and outer surfaces instead of the cut-off portion 62 on one of the side walls 3, 3. A thin portion 72 is formed, and the rigidity of the side wall portion is reduced at this portion.

When the cut-off portion 62 and the thin portion 72 are provided on the side wall portion 3 as described above, the central vibration-damping portion 5 has a mass portion 5 as shown in FIGS. 12 and 13. a, and both side portions 5 b, 5 b extending from the mass portion 5 a, and the both side portions 5 b, 5 b are bifurcated into branch portions 5 c, 5 b This can be particularly suitably implemented for those which are connected to the both side walls 3 and 3 and have a substantially X shape.

In other words, in the case of a support device having a substantially X-shaped central vibration damper 5, in the case of the conventional structure, the absolute panel due to the resonance of the side walls 3, 3 in the frequency range of 700 to 100 mm. An increase in the constant is observed, but by providing the cut-out portion 62 or the thin portion 72 on the side wall portion 3 as described above, the above-described resonance can be suppressed, and an increase in the absolute panel constant can be suppressed. it can. In particular, if this is implemented in conjunction with the first or second invention described above, the effect will be greater.

In the case where the cut-out portion 62 and the thin portion 72 are provided on the side wall portion 3, the center damping portion 5 is not limited to the above-described substantially X-shaped portion, and is shown in FIGS. 14 and 15. As illustrated, the same effect can be obtained in a device having a central damping portion of another structure, such as one formed in a horizontal single character and connected to both side walls 3, 3. Play.

In any of the above cases, it is preferable that the gap between the cut-off portions 62 or the width of the concave portion 82 forming the thin portion 72 is set to 0.5 mm or more.

[Industrial feasibility]

As described above, according to the exhaust pipe support device of the present invention, the absolute repulsion constant can be set to be low not only in the frequency region of 600 Hz or less but also in the frequency region of 600 Hz or more, and extremely wide range. In this frequency range, the absolute spring constant can be reduced, effectively preventing noise when the engine is rotating at high speed, and contributing to improved vehicle quietness. It can be suitably used as a device for supporting an automobile muffler, that is, an exhaust pipe on a vehicle body in a vibration-proof manner.

Claims

Scope of the request: a first holding portion integrally formed of a material having elasticity and having a through hole into which a support material on the vehicle body side is inserted, and a through hole into which a support material on the exhaust pipe side is inserted. A second holding portion, a pair of side wall portions connecting the first holding portion and the second holding portion at both sides thereof at an interval, and an intermediate position between the first and second holding portions; An exhaust pipe support device having a central vibration damping part integrally connected to both side walls,

The exhaust pipe support device, wherein the first holding portion and the second holding portion are separated from each other at a portion between the side wall portions.

2. The exhaust pipe supporting device according to claim 1, wherein the cut-off portion is formed so as to have a gap of 0.5 mm or more between cut end faces.

The first holding portion and the second holding portion are formed so as to hold at least one half of the entire circumference of the support material inserted into the through hole in the other portion except the cut-off portion. The exhaust pipe support device according to claim 1. A first holding portion integrally formed of a material having elasticity and having a through hole into which the support material on the vehicle body side is inserted, and a second holding portion having a through hole into which the support material on the exhaust pipe side is inserted. And a pair of side wall portions connecting the first holding portion and the second holding portion at both sides thereof at an interval, the exhaust pipe supporting device comprising:

The exhaust pipe support device, wherein the first holding portion and the second holding portion are formed to be thin at portions between the side wall portions.

5. The exhaust pipe support according to claim 4, wherein the thin portion is formed to be thin by forming a concave portion having a width of 0.5 mm or more in a part of a holding portion. The part and the second holding part hold at least one-half of the entire circumference of the support material inserted into the through hole in the other part except the thin part. 6. The exhaust pipe support device according to claim 4, wherein the exhaust pipe support device is formed as follows. The central vibration damping portion has a central portion formed as a mass portion, and both side portions extending from the mass portion, and the mass portion is formed to have a larger mass than that of both side portions. 5. The exhaust pipe support device according to claim 1, wherein the both side portions are each formed in a bifurcated shape and connected to the both side wall portions.

A first holding portion integrally formed of an elastic material and having a through hole into which the support material on the vehicle body side is inserted, and a second holding portion having a through hole into which the support material on the exhaust pipe side is inserted. A pair of side wall portions connecting the first holding portion and the second holding portion on both sides thereof at an interval, and the both side wall portions disposed at an intermediate position between the first and second holding portions. An exhaust pipe support device having a central vibration damping part integrally connected to the exhaust pipe,

A support device for an exhaust pipe, wherein a cut-off portion or a thin portion is provided in a part of the central vibration damping portion.

A first holding portion formed integrally with an elastic material and having a through hole into which the support material on the vehicle body side is inserted, and a second holding portion having a through hole into which the support material on the exhaust pipe side is inserted. A pair of side wall portions connecting the first holding portion and the second holding portion at both sides thereof at an interval, and a pair of side wall portions arranged at an intermediate position between the first and second holding portions and provided on the both side wall portions. An exhaust pipe support device having a central vibration damping unit integrally connected,

A supporting device for an exhaust pipe, wherein a cut-off portion or a thin portion is provided in a part of the side wall portion.