JPS59145624A - Mounting structure for exhaust pipe system for car - Google Patents

Abstract

PURPOSE:To reduce the generation of vibration sound or echo sound by hunging one side part of an exhaust pipe system from a car body via an insulator plate faced upward and downward, while the other side part of the exhaust pipe system via an insulator plate faced to the side. CONSTITUTION:In a system where brackets 2 and 3 are fixed by welding on a lower part of a car body 1, hunging a muffler 6 via mounts 4 and 32, the mount 4 is formed to be fitted on the bracket 2 via the first insulator 8 made of rubber faced upward and downwared with its upper part by a bracket 7 and its lower part on one side part of the muffler 6 via bolts 11 and 13 respectively to be removable. While, the mount 32 is constructed to be fitted on the bracket 3 via the second insulator plate 34 made of rubber faced to the side with its one end via L-form bracket 33 and its other end on the other end part of the muffler 6 via bolts 19 and 21 respectively to be removable.

Description

DETAILED DESCRIPTION OF THE INVENTION The present invention relates to a mountain ink structure for an exhaust pipe system for an automobile, in which the exhaust pipe system for an automobile is suspended and supported by an insulator on the vehicle body. .

Some conventional FF type automobiles, that is, fluorocarbon 1-j<live type (front axle drive type) cars, have a horizontally mounted engine. In this type of vehicle, the engine vibrates in the roll direction (back and forth direction) due to its own vibration, and the transmission drive shirt 1
~・An excitation force is generated due to the torsional 1-lux reaction force of a drive system such as a tire. Here, if the vibration acting force due to the vibration displacement in the roll direction l\ is taken as the roll direction displacement input, and the vibration acting force due to the excitation force is taken as the power transmission system excitation input, then the vehicle It is caused to vibrate by the resultant vibration input due to the resultant force with the vibration input.

This vibration occurs when the vehicle is idling, under any conditions in the neural range or the drive range.

In this case, the human force for displacement in the roll direction is not only caused by the component caused by the deterioration of the engine mount system that supports the engine on the vehicle body, but also by the component caused by the rigidity of the exhaust pipe system connected to the engine system. There is a coupled component between the component contributing to resonance and the component resulting from the resonance characteristics of the exhaust pipe system itself. Then, these inputs are input to the car body from a part of the engine to the car body, causing the body to vibrate.

By the way, if the vibration of the vehicle body is too large, it will cause discomfort to the driver and passengers.

In particular, when the engine is linked, the low-frequency vibrations of the engine cause the exhaust pipe system to resonate greatly, and this resonance causes so-called muffled sounds and chattering noises in the cabin, which may cause damage to passengers, etc. give discomfort.

In order to avoid such discomfort, the specific 41i4 '1191 number of the υ1 tracheal system should be changed so that the exhaust pipe system does not resonate during idling, and the vibration will be improved, especially when the engine is idling. Should it be lower than the resonant frequency?

This 1j1. 1 (As a means of changing the natural frequency of the system, increase or decrease the stiffness and l/I of the tracheal system itself by 1). This is done by making changes.

rne1 Install a flexo-flu (1'q structure) in the exhaust pipe system to extremely lower the rigidity.

I: 3+ 1jl By having metal attached to the tracheal system 1
1: Locally change the quality of the tracheal system, thereby changing the vibration characteristics of the exhaust pipe system 6.

(g) Round 1 of the exhaust pipe system - Change the support rigidity depending on the method to change the vibration characteristics of the exhaust pipe system.

There are other methods.

In the method (3) above, it is necessary to change the resonance characteristics depending on the direction, and such changes are usually impossible or (
The 4j method is fully possible as long as the mounting method is selected. Based on this idea, a mounting structure for the exhaust pipe system as shown in Figure 1 has been considered. In Figure 1 (-), a muffler 6 is suspended from the brackets h2 and 3 welded to the lower part of the 111 body 1 via a mount 1-4.The mount 1-4 is omitted. Letter-shaped flake 1-7
and a first insulator plate 8 made of rubber, and the upper part of the flake 1-7 is made up of Pol 1-9 and Nano 1-1.
0, it can be detachably attached to bracket 2),
At the bottom of the bracket 1-7, there is a part of the insulator plate 8 facing downward that can be detached by bolts and nanos 1-12, and an exhaust pipe is installed at the bottom of the insufflator vj and 8. The side of the system muffler 6 goes to the port 13,
It is attached with detachable 1J capability by Nano 1-14.

Further, the mount 5 is made up of a flat bracket 1-15 and a second insulator plate 16 made of rubber. The upper parts of brackets 1 to 15 are removably attached to bracket 3 using poles 1-17 and nuts 18, and
~15, the upper part of the insulator plate J6 facing the tote direction is ↑ due to Pol 1-19 and Nano 1-20.
1 removable f = j, ゛insulator provisional 16
The other side 81) of the muffler 6 is attached to the upper part of the muffler 6 with 21 to the port 1 and 22 to the nano 1 so that it can be attached and detached.

Due to the mounting structure of the JJI tracheal system, 1
11 (Idle link by changing the natural vibration t!L+ number of the tracheal system; 1, which can reduce the crackling sound and muffled sound that occurs in the tracheal system) 17 In vehicles with this system, the 91r has a crank part that bends laterally in the exhaust pipe system in order to avoid the shift 1 lever of the 1-rance transmission, so the exhaust pipe system has a crank part. In the 1?P system vehicle, the Y direction of the transverse engine, that is, the roll direction (vehicle iiIM r+
X for 4bi 4rJJ of js backbu 51+'j1)
The vibration component in the horizontal direction (transverse direction) is 10 times higher. Moreover, the double mounting structure j1 is XIIL: l: Insulator 'tk 8 + Ib is 1 - downward direction
Direction) Since it is provided, ``2]: Direction swing 1
The vibration force in the lateral direction (X direction) was applied (three rows of N soil 7 yi number ko 1 孭?)). Accordingly, the exhaust pipe system is equipped with a crank part 1, which is a p + r system σ)) 1 (which lowers the vibration of the pipe system in the Z direction to some extent). However, the vibration M of the exhaust pipe system in the X direction is
Kk is something that cannot be touched, and the second is -1.
As a result, it was not possible to sufficiently reduce the vibrations of +lX and 7 (A and (X:I problems).

During this time, the method of determining M is to increase the spring tension of the insulators 8 and 16])-1 or increase the length of the insulator plate 8.16 in the direction of the upper blade'Q)-
4- However, in the former method, the insulator I'Jj
8. The thickness of 1.6 must be made extremely thick, and the insulator is temporary. ] If 6 becomes quite heavy, another problem arises. Further, according to the latter method, there is a problem that the height of the muffler 6 changes when the muffler 6 is picked up, causing the muffler 6 to interfere with the air L1 of the vehicle body 1 or the ground.

Secondly, the present invention solves the above problems by sufficiently changing the resonance characteristics of the exhaust pipe system in the lateral direction (X direction) to reduce the vibration of the vehicle body in a specific part of the engine operating range or in general. The purpose of the present invention is to provide a mounting structure for an automatic small exhaust pipe system that can suppress the generation of crackling noise, muffled noise, etc. of the IT body. At the beginning of the month, this invention
111 The side part of the 111 tracheal system of the engine should be suspended from the car body via the first insulator plate facing in the 1-F direction, and the other side part of the 111 tracheal system should be oriented laterally. The feature 1, ν is that the mount 71' of the automobile II tracheal system is suspended and supported on the vehicle body through the second insulator plate facing toward the vehicle body.

Hereinafter, this invention will be explained according to FIGS. 2 to 181:zl. Note that the same parts as in FIG. 1 are given the same reference numerals and their explanations will be omitted.

In FIG. 2, 23 is an engine, and 24 is an engine 23.
This is the exhaust pipe system. This 24-piece exhaust pipe system includes an exhaust tube 25, a freon 1 to tube 26 bent laterally in a crank shape, a sub-muffler 27, a center tube 28,
The main muffler 29 and the tail tube 3 (1) are connected in this order.The main muffler 29 is
It is suspended and supported at a position not shown in the vehicle body 1 of FIG. 3 via a mount 1-31. Also, one side of the sub-muffler 27 is supported on the vehicle body 1 side via the mount 1-4, and the other side of the sub-muffler 27 is supported on the vehicle body 1 via the mount I-32 as shown in FIG. Suspended and supported, 11. Deil 1
, in this embodiment, the mount l-4 is the same as in Fig. 1.
There is a structure, Maun 1-32 is abbreviated as I, and Warakeno 1 is shaped like a letter.
~33 and the second insulator made by IX (λ, j3
/l (see Figure 4), and one end of the vertical part of the fuukenoto 3:) is removably attached to the fuukenoto 3 by means of the port 1-17 and ten nod 18. j is also AI, one end of the second insulator plate 3/I facing in the lateral direction (horizontal direction) is removably attached to the horizontal part of the bracket 1 to 33 by the pole 1 to 19 and the Nara 1-20, The other side of the sub-muffler 27 is removably attached to the other end of the second insulator plate 34 by means of a bolt 2 and a napht 22.

Next, the mounting 4i of the exhaust pipe system having such a configuration will be explained.
The functions of the '6 model will be explained based on Figures 5 to 5 and 14.

FIG. 5 shows the mounting structure of the exhaust pipe system of the type according to the present invention, and the spring constants of the first and second insulator plates 8, 34 are as shown in Table 19.
FIG. 6 shows an example of a pond of the type of exhaust pipe system shown in FIG. 1 having a non-tain structure. The Hane constants of ++ are shown in Table 1.

In Fig. 6, the flaket 15 is young: the head of the ``bent, por h13,2'' is insulated by the insulator tJi8.
．． Four parts 8 yen formed in 16.

16a is inserted into the first one. .

Person 1--I' Schley Kusaka Momahachi passed away ~ 4 Table 1 in the text
The sound pressure level of the noise when conducting an experiment using a mounting design with the specifications of 1 - above the floor (above the front seats)
41, and the front floor at this time is -
1- As a result of measuring the magnitude of the downward vibration acceleration JAM width, the measurement results for four houses were <Sノ, as shown in Figs. 7 to 11. In the figure, the broken line is shown in FIG. 5 and represents the characteristic curve △ of the type of the invention, and the solid line is shown in FIG. 1. Figure 7 shows the relationship between the engine speed and the high pressure level of noise at high speed.As is clear from this figure, the noise of the type of this invention is higher than that of the type of Figure 6. (However, within the normally used engine speed range of 7-7, the maximum noise value of the type of this invention was lower than that of the type shown in Figure 6.) Further, FIG. 8 shows the relationship between the number of engine revolutions tljii during deceleration 116 and the magnitude of the vibration acceleration amplitude of the freon 1-floor. As is clear from this figure, the steady-state running range, which is commonly used, is about 60 Km/h, or the engine speed is 2. O
In the OOrpm part, the amplitude of the vibration acceleration in the 1-degree direction of the fluorocarbon 1-floor can be made much smaller than that of the type of this invention or the type shown in FIG. The amplitude of the vibration acceleration in the 1-dimension direction of the area could also be made lower on average than that of the type of the present invention or the type of Figure 6. In addition,
Engine speed is 4, I:1OOrp+n or higher! 1) The acceleration amplitude becomes extremely large, but 4,
000 rput or more1. This region is hardly used, so it does not pose a problem.Figure 9 shows the relationship between the engine speed and the sound pressure level of noise during acceleration. As shown in Figure 6, the noise during acceleration (1''f) could be made sufficiently lower overall than that of the type of this invention or the type shown in Fig. 6.

Furthermore, Figure 10 shows the relationship between the engine speed and the vibration acceleration amplitude of the front floor at 1 speed. At a speed of about 60 Km/h, that is, at an engine speed of 2.00 rpm, the type of the present invention has a lower vibration acceleration amplitude in the direction of 1 to the floor than the type shown in Figure 3. Fig. 11 shows the relationship between the engine speed in the idle link range and the sound pressure level of the noise when the automatic transmission J1. is stopped and the gear shift position is set to the drive range. It is shown in this figure.
As is clear from the above, the average idle link position is 71-)
In the range of engine rotational speed from 75 rpm to 800 rpm, the type of the present invention was able to sufficiently reduce [3,I/,Ff] compared to the type shown in Fig. 6.

Next, in the type of this invention shown in FIG.
The relationship between the engine speed and the amplitude of the noise or floor vibration when the lateral length L and vertical spring constant of the second insulator plate 371 are changed as shown in Table 2 is shown in FIGS. This will be explained according to FIG.

Figure 12 shows the noise that affects the front seats 1-1 in relation to the engine speed, and Figure 13 shows the noise that affects the front seats 1-1 in relation to the engine speed. Figure 14 shows the amplitude of the fluorocarbon (in the 1-do direction of the -floor) in relation to the number of engine simultaneous conversations. Characteristics when using l1 mouth!ib
, D is the 'characteristic curve when using the medium-sized one in Table 2.

① is the characteristic curve when the "short" one in Table 2 is used. As is clear from the diagrams above, noise and fluorocarbons
- the amplitude of the vibration of the floor is determined by the second insulator plate 34;
It was found that changing the length of the spring and the spring constant of the spring made almost no significant difference. If the lateral length (2) of the second insulator plate 34 becomes longer, the insulator plate 34 will have a slight step as shown in FIG. Figures 12 to 15 or 1) are also clear.

In the embodiment described above, the poles 1- passing through the insulator plate 8°34 are fixed to the brackets h2, 3 and the sub-muffler 27, but the invention is not necessarily limited to this. For example, as in No. 1151M+, a collection side plate 35 is provided on one side of a part of the first insulator plate 8 and on the other side of the lower part. '36 was burnt and fixed name, Tori f=J
Temporary 35.36 Pol 1-] 1, Nala 1-12 and Pol I
~13, When attaching nuts 14 to the sides of bracket 1-7 and sub-muffler 27, no.
, the second insulator plate 3.1σ is attached to the tenth surface on one side and the lower surface on the other side, respectively: '17. :38, 4 hard? :f and take it] Board 37.38 Pol 1-19,
The nut 1-20 and the nut 22 may be mounted on the other side of the bracket 15 and the sub-muffler 27, respectively.

Furthermore, in the embodiment described above, the portion of the sub-muffler 27 which is the antinode of vibration is mounted toward the vehicle body 1, but the angle is not necessarily limited to 11 degrees.

For example, as shown in Fig. 17, the parts other than the muffler of the antinode of the vibration of the exhaust pipe system during idling [? may be suspended and supported by the mounting structure according to the present invention.

Furthermore, even if the sub-muffler 27 was moved slightly back and forth as shown in FIG. 18, there was no significant difference in effectiveness.

As explained above, the present invention is based on the first insulator plate that connects the - side part of the exhaust pipe system of the engine to the -J- downward direction. The other side of the exhaust pipe system is suspended and supported on the vehicle body via a second insulator plate with the other side of the exhaust pipe system oriented laterally. In vehicles where the exhaust pipe system is equipped with a clamper section to avoid the gear shift lever of the transmission, etc., 1.
j1: Even if vibration occurs in the tracheal system (
1), the part where the engine speed is 2.000rρ111 (see FIG. 10)], or the entire engine speed (see FIG. 8).

As a result, it is possible to sufficiently suppress the occurrence of chatter noise, muffled noise, etc. of the vehicle body.

In addition, when the exhaust pipe system resonates due to engine vibrations during idling, if the antinode of vibration of the exhaust pipe system is suspended from the vehicle body via an insulator plate, The resonance of the exhaust pipe system caused by engine vibration can be suppressed more effectively.

[Brief explanation of drawings]

FIG. 1 is a cross-sectional view showing an example of a mounting structure for an automobile exhaust pipe system, FIG. 3 is a sectional view of the mounting structure shown in FIG. 2, FIG. 4 is a perspective view of the second insulator plate shown in FIG. 3, and FIG. 5 shows a part of the mounting structure of the present invention modified by a number R1. A sectional view, FIG. 6 is a sectional view showing a modification of the mounting structure of the type shown in FIG. 1, and FIG.
Figures 9, 11 to 14 are characteristic curve diagrams showing the relationship between engine speed and sound pressure level of noise, and Figures 8 and 10 are characteristic curve diagrams showing the relationship between engine speed and vibration acceleration amplitude. Fig. 16 (a sectional view showing other embodiments of Makoto's invention, Fig. 17, Fig. 16) Fig. 18 is a west control system diagram showing still another embodiment of the present invention. 1. Car body, 2, 3... To bracket 1, 4, 5. Magnon 1-18... No. 1 insulator plate, 11.
・・・Bolt, 12...Narah-13-・Bolt,]4
... Nando, 23... Engine, 24... Exhaust pipe system,
25...11'' air tube, 26...front tube, 27...sub muffler, 28...center tube, 29...main muffler, 30...tail tube, 3], 32...mount 1~. 33...Bracket 1-
134...Second insulator plate, 35°3G,
37, 38... Take a; 1 board. Figure 3 1 4 Figure 5

Claims (2)

[Claims] (1) One side of the exhaust pipe system of the engine is suspended and supported on the vehicle body via a first insulator plate with the exhaust pipe system oriented vertically, and a second insulator plate with the other side of the exhaust pipe system oriented laterally. A mountain ink structure 5 for an automobile exhaust pipe system, characterized in that it is suspended and supported on the vehicle body via an insulator plate. (2) Engine vibration when the exhaust pipe system is ringing
Claim 1, characterized in that, when the exhaust pipe system is shaken more, the portion that becomes the antinode of vibration (7) of the exhaust pipe system is suspended and supported on the vehicle body via an insulator. 1
Automotive exhaust 1' ax system mounting 111 described in
η construction,