EP2997240A1

EP2997240A1 - Exhaust system for an internal combustion engine and method for operating the exhaust system

Info

Publication number: EP2997240A1
Application number: EP14719766.9A
Authority: EP
Inventors: Rainer Drees; Christian Eichmüller
Original assignee: Bayerische Motoren Werke AG
Current assignee: Bayerische Motoren Werke AG
Priority date: 2013-05-15
Filing date: 2014-04-28
Publication date: 2016-03-23
Anticipated expiration: 2034-04-28
Also published as: DE102013208946A1; US20170198617A1; US9945276B2; CN105121796A; US9605580B2; CN105121796B; EP2997240B1; US20160053658A1; WO2014183978A1

Abstract

Exhaust system (1) for an internal combustion engine, having at least a first and a second cylinder, wherein the first cylinder is assigned a first exhaust gas manifold (2) and the second cylinder is assigned a second exhaust gas manifold (3), and wherein the first exhaust gas manifold (2) is assigned a first silencer (4), and the second exhaust gas manifold (3) is assigned a second silencer (5), characterised in that a first damping pipe (2') branches off from the first exhaust gas manifold (2) upstream of a first shut-off element (6), said damping pipe (2') firstly opening into a first reflection chamber (7) and being subsequently led through the first silencer (4) and opening into the second exhaust gas manifold (3) downstream of a second shut-off element (8), and wherein a second damping pipe (3') branches off from the second exhaust gas manifold (3) upstream of a second shut-off element (8), said second damping pipe (3') firstly opening into a second reflection chamber (9) and subsequently being led through the second silencer (5) and opening into the first exhaust gas manifold (2) downstream of the first shut-off element (6).

Description

Exhaust system for an internal combustion engine and method of operating «the exhaust system

description

The invention relates to an exhaust system for an internal combustion engine with the features of the preamble of patent claim 1 and method for operating the exhaust system according to the features of the claims 8 to 10.

From the German patent application DE 10 2009 032 213 A1, for example, an exhaust system of an internal combustion engine is known with a first cylinder group of the Brenrikraftmaschine associated first exhaust system and with a second cylinder group of the internal combustion engine associated second exhaust system. Each exhaust gas line has in each case an exhaust gas purification device and a first exhaust silencer arranged downstream of the respective exhaust gas purification device, as well as a second silencer downstream of the respective first silencer and an exhaust gas end pipe arranged downstream of the respective second silencer. A disadvantage of this known prior art is the fact that the damping resonator of the muffler is not variably adjustable in terms of sound.

Further mufflers for exhaust systems are generally known from the prior art, which operate on the absorption and / or reflection principle. The development of such a muffler usually means finding the best possible compromise between muzzle noise (volume after exhaust tailpipe), exhaust backpressure and required muffler volume. To circumvent such a compromise solution are often silencer with one or more movable closure elements or shut-off devices, such as an exhaust flap, executed to allow different flow paths in the exhaust pipe of the silencer system. In silencer systems for internal combustion engines, two, three or even four exhaust system tailpipes are often provided. In the case of the muffler designs known from the prior art, the arrangement of the closure elements leads disadvantageously to the fact that, depending on the position of the closure element, it is no longer possible to flow exhaust gas through all the exhaust system tailpipes or tailpipe branching elements.

However, this prior art has the following disadvantages:

Irritation at the customer, since exhaust gas does not escape from all exhaust tailpipes (visible at low outside temperature due to water vapor and at the different degree of contamination of the visible tailpipes);

High exhaust backpressure due to a bottleneck in the tailpipe tailpipe;

· *) · Audible flow noise through the bottleneck in the exhaust system tailpipe; Thermal stress between the cold and hot exhaust tailpipe runs the risk of cracking;

Elaborate management of the damping tubes at the silencer system;

· # * High weight of the silencer system;

-> high manufacturing costs of the silencer system;

Flaps are usually only partially separated or shifted in time, this leads to a significant increase in exhaust gas back pressure in an exhaust line.

Object of the present invention is to avoid the disadvantages mentioned above and at the same time introduce a variability in the acoustic damping properties of the silencer system.

This object is achieved by the device in the characterizing part of patent claim 1 and procedurally by the features of claims 8 to 10.

The inventive design of the exhaust system, all the above problems are avoided. The exhaust system has a structure advantageous with respect to the exhaust backpressure. Due to the construction according to the invention, one or both shut-off valves can also be closed at the same time without a substantial increase in the exhaust backpressure. Compared with conventional exhaust systems exists with open shut-off devices, such. As exhaust valves, a minimum or hardly measurable throttling (increase in the exhaust backpressure), since the entire Abgasroh r and damping tube volume is used to the end of the exhaust system. By a slightly different structure, the shut-off valves can also be shifted in time to improve a subjective hearing impression during the switching phases. The staggered switching of the two shut-off devices can be reduced to conspicuous, acoustic level jumps in an advantageous manner. With regard to power and dynamics (response of the internal combustion engine), the very low exhaust back pressure of the exhaust system due to the inventive design has a very positive effect. For slight acoustic adjustments, the volumes of the first silencer and the second silencer can also be subsequently changed. In addition, one or more possibly necessary resonators can be easily integrated in the exhaust system while maintaining the symmetry in a simple manner. Due to the symmetrical design of the Abgasaniage this and beyond the muffler itself can be very cheap.

Many components of the exhaust system according to the invention can be manufactured or used as inexpensive common parts:

The silencer housing can be implemented, for example, as a cost-effective coil damper or shell construction. When implemented as a winding damper, the two side parts can be designed as a common part. In shell construction, the upper and lower shell can each be made of identical parts.

The exhaust pipes can also be manufactured and installed as the same components.

The Y-branch elements of the exhaust pipes to the damping tubes can be implemented, for example, as hydroforming (IHU). The damping tubes with perforation, which are guided through the silencer, are also implemented as equal parts. The same applies to the damping pipe from the Y pipe section to the reflection chamber.

Also for the production can be saved because of the common parts for the exhaust system assembly tools. Depending on how the production of a manufacturer or supplier is constructed, the pre-assembly of the Y- Branching elements and the shut-off devices for both sides of the exhaust system to be used the identical mounting device.

All of the above points lead to a significant reduction of the tool and manufacturing costs for the exhaust system according to the invention.

Due to the large proportion of identical parts and the reduction of individual part variants, it is also possible to realize a possibly desired lightweight construction much more easily.

Preferred developments of the exhaust system according to the invention for an internal combustion engine are described in the subclaims.

With the embodiments according to claims 2 and 3, several variants can be displayed in a simple manner.

With the embodiment according to claim 4, a further fine tuning of the exhaust system sound is possible.

The embodiment according to the claims 5 to 7 again reduces the production costs.

With the method for operating an exhaust system for an internal combustion engine according to claim 8, a minimum sound attenuation is achieved.

With the method for operating an exhaust system for an internal combustion engine according to claim 9, an average sound attenuation is achieved.

With the method for operating an exhaust system for an internal combustion engine according to claim 10 maximum sound attenuation is achieved. In the following, an exhaust system according to the invention and three methods for operating the exhaust system according to the invention are explained in more detail in four figures.

Fig. 1 shows schematically an exhaust system according to the invention.

Fig. 2 shows the exhaust system according to the invention with two closed shut-off devices.

Fig. 3 shows the exhaust system according to the invention with two open

Shutoff valves.

Fig. 4 shows the exhaust system according to the invention with a closed and an open obturator.

Fig. 1 shows an end portion of an exhaust system 1 according to the invention for an internal combustion engine, not shown, with at least a first and a second cylinder, also not shown. The first and the second cylinder are representative of cylinder groups of the internal combustion engine. For example, in a six-cylinder internal combustion engine, the cylinders 1 to 3 of the cylinder group 1 and the cylinders 4 to 6 correspond to the cylinder group 2. The first cylinder is a first exhaust pipe 2 and the second cylinder is associated with a second exhaust pipe 3. Further, the first exhaust pipe 2, a first muffler 4 and the second exhaust pipe 3, a second muffler 5 is assigned.

According to the invention, a first damping pipe 2 'branches off from the first exhaust pipe 2 upstream of a first shut-off element 6. This first flows into a first reflection chamber 7 and is then passed through the first muffler 4 and opens again into the second exhaust pipe 3 downstream of a second obturator 8. In addition, branches from the second exhaust pipe 3 upstream of a second obturator 8, a second Damping tube 3 'from which first opens into a second reflection chamber 9 and then passed through the second muffler 5 and opens into the first exhaust pipe 2 downstream of the first obturator 6. Flow directions of the exhaust gases, which are represented by arrows are shown in FIGS. 2 to 4 can be removed.

As is known from the prior art, the first damping tube 2 'and the second damping tube 3' in the volume of the first muffler 4 and in the region of the second muffler 5 on a perforation, for emitting sound emissions in the muffler 4, 5 for frequency-selective Attenuation of the sound pressure level. The damping effect is shown symbolically in FIGS. 2 to 4 by dashed lines in the region of the perforation.

In the present embodiment, the first and the second obturator 6, 8 is an exhaust valve, in other embodiments, it may for example be rollers.

Next to the first exhaust pipe 2 downstream of the first obturator 6, a third reflection chamber 10 and the second exhaust pipe 3 downstream of the second obturator 8, a fourth reflection chamber 11 assigned. In another embodiment, a reflection chamber 10, 11 omitted.

Preferably, the first exhaust pipe 2 is connected via a perforation 12 exhaust gas leading to the third reflection chamber 10 and / or the second exhaust pipe 3 via a perforation 12 exhaust gas connected to the fourth Refiexionskammer 11. In a further embodiment, the first and the third reflection chamber 7, 10 and / or the second and the fourth Refiexionskammer 9, 11 may be connected to each other exhaust-conducting, for example by a further perforation. By this measure, a further acoustic optimization is possible. Particularly preferably, the first and the second muffler 4, 5 are arranged in a common housing 13, whereby manufacturing costs are saved.

In yet another particularly preferred embodiment, the first and the second reflection chamber 7, 9 are arranged in the housing 13. The greatest cost saving is achieved if even the third and the fourth reflection chamber 10, 11 are arranged in the housing 13.

In yet another embodiment, the first and second reflection chambers 7, 9 can also be designed as resonator chambers.

Again, in another embodiment, the third and the fourth reflection chamber 10, 11 may be designed as absorption chambers. The particular embodiment of a reflection chamber, a resonator chamber, or absorption chamber will not be described in detail, since this is sufficiently defined in standard textbooks.

Due to the symmetrical design of the entire exhaust system 1 can be reduced in particular the production costs, since the common parts principle can be applied in a wide range. For example, the Y-branch pipes (transition region from the exhaust pipe to the damping pipe), the damping pipes 2 ', 3', the shut-off elements 6, 8, the tail pipe branches, the reflection chambers 7, 9, 10, 11, the mufflers 4, 5 and the exhaust pipes 2, 3 are designed as equal parts. In a particularly advantageous manner, the muffler 4, 5, the reflection chambers 7, 9, 10, 11 accommodate cost in a single common housing 13. Also for the production can be 1 assembly tools save due to the common parts for the exhaust system. This also leads to a significant reduction in tooling costs.

In FIGS. 2 to 4, in which the same reference numerals apply to the same components as in FIG. 1, the same exhaust system 1 is shown again as in FIG. 1, but for three different operating states. Exhaust gas flow directions are, as already stated above, each schematically represented by Pfeiie.

FIG. 2 shows the exhaust system 1 according to the invention with a setting for a first operating method, the first and the second shut-off elements 6, 8 being closed. By this setting, a maximum sound attenuation for the exhaust system 1 is achieved.

Fig. 3 shows the exhaust system 1 according to the invention with a setting for a second operating method, wherein the first and the second obturator 6, 8 are opened. By this setting a minimum sound attenuation for the exhaust system 1 is achieved.

Fig. 4 shows the exhaust system 1 according to the invention with a setting for a third operating method, wherein the first obturator 6 is closed and the second obturator 8 is opened. By this setting, an average sound attenuation for the exhaust system 1 is achieved.

The exhaust system 1 according to the invention has a construction which is very advantageous with regard to the exhaust backpressure. As a result of the design according to the invention, one or both shut-off elements 6, 8 can also be closed at the same time without a substantial increase in the exhaust backpressure. Compared with conventional exhaust systems with open shut-off valves 6, 8, such. As exhaust valves, a minimum or hardly measurable throttling (increase in the exhaust backpressure), since the entire exhaust - from Dämp- exhaust pipe volume to the end of the exhaust system 1 - is used. By a slightly different construction, the shut-off devices 6, 8 can also be switched over in time to improve a subjective hearing impression during the switching phase. By staggered switching of the two shut-off valves 6, 8 can be reduced to conspicuous acoustic level jumps in an advantageous manner.

With regard to power and dynamics (response of the internal combustion engine), the very low exhaust backpressure of the exhaust system 1 due to the embodiment according to the invention has a very positive effect. For slight acoustic adjustments, the volumes of the first muffler 4 and the second muffler 5 can also be subsequently changed. In addition, one or more possibly necessary resonator chambers 10, 11, which are also designed as reflection chambers, can be integrated in the exhaust system 1 in a simple manner without great expense, while maintaining the symmetry.

Due to the arrangement of the first and the second adjusting element 6, 8 in the first and in the second exhaust pipe 2, 3 in the flow direction of the exhaust gas in front of the Abgasend a switching operation of outsiders is virtually impossible to hear.

LIST OF REFERENCES:

1st exhaust system

2, first exhaust pipe

2 ¹ first damping tube

3rd second exhaust pipe

3 'second damping tube

4. first silencer

5. second silencer

6. first shut-off device

7. first reflection chamber (resonator chamber)

8. second obturator

9. second reflection chamber (resonator chamber)

10. third reflection chamber (absorption chamber)

11. fourth reflection chamber (absorption chamber)

12. perforation

13. Housing

Claims

Exhaust system for an internal combustion engine and method for operating the Abgaeanlage claims

1. exhaust system (1) for an internal combustion engine, with at least a first and a second cylinder, wherein the first cylinder a first exhaust pipe (2) and the second cylinder, a second exhaust pipe (3) is associated and wherein the first exhaust pipe (2) a first muffler (4) and the second exhaust pipe (3) is associated with a second muffler (5),

characterized in that from the first exhaust pipe (2) upstream of a first obturator (6) branches off a first damping tube (2 '), which first in a first reflection chamber (7) opens and then passed through the first muffler (4) and in the second exhaust pipe (3) downstream of a second obturator (8) opens and that from the second exhaust pipe (3) upstream of a second obturator (8) branches off a second damping pipe (3 '), which first opens into a second reflection chamber (9) and is then passed through the second muffler (5) and in the first exhaust pipe (2) downstream of the first obturator (6) opens.

2. Exhaust system according to claim 1,

characterized in that the first exhaust pipe (2) downstream of the first obturator (6) has a third reflection chamber (10) and / or the second exhaust pipe (3) downstream of the second obturator (8) is associated with a fourth reflection chamber (11).

3. Exhaust system according to claim 2,

characterized in that the first exhaust pipe (2) via a perforation (12) exhaust leading to the third reflection chamber (10) and / or the second exhaust pipe (3) via a perforation (12) leading exhaust connected to the fourth reflection chamber (11) is.

4. Exhaust system according to claim 2 or 3,

characterized in that the first and the third reflection chamber (7, 10) and / or the second and the fourth reflection chamber (9, 1) exhaust leading are interconnected.

5. Exhaust system according to one of the claims 1 to 4,

characterized in that the first and the second silencer (4, 5) in a common housing (13) are arranged.

6. Exhaust system according to claim 5,

characterized in that the first and second reflection chambers (7, 9) are arranged in the housing (13).

7. Exhaust system according to claim 5 or 6,

characterized in that the third and the fourth reflection chamber (10, 11) are arranged in the housing (13).

8. A method for operating an exhaust system according to one of the claims 1 to 7,

characterized by the following process:

Opening the first and the second shut-off device (6, 8) for a minimum sound attenuation.

9. A method for operating an exhaust system according to one of the claims 1 to 7,

characterized by the following process step:

Opening the first obturator (6) and closing the second obturator (8) for a mean sound attenuation.

10. A method for operating an exhaust system according to one of the claims 1 to 7,

characterized by the following process step:

Closing the first and second shut-off means (6, 8) for maximum sound attenuation.