CN217481616U - Noise eliminator, engine and vehicle - Google Patents

Abstract

The utility model belongs to the technical field of making an uproar falls in the noise elimination, a noise eliminator, engine and vehicle are disclosed, noise eliminator include outer tube, first inner tube and a plurality of first prewhirl flow distribution plate. Be provided with a plurality of first grooves of eliminating noise that encircle the outer tube along the circumference of outer tube on the outer tube inner wall, a plurality of first grooves of eliminating noise set up along the axial interval of outer tube, and the groove depth of each first groove of eliminating noise is all inequality. The first inner tube is sleeved in the outer tube, a plurality of second silencing grooves surrounding the first inner tube along the circumferential direction of the first inner tube are formed in the inner wall of the first inner tube, the plurality of second silencing grooves are arranged along the axial direction of the first inner tube at intervals, and the groove depths of the second silencing grooves are different. First prewhirl flow distribution plate extends to the other end of first inner tube by the one end of first inner tube, and the inner wall of outer tube and the outer wall of first inner tube are connected to first prewhirl flow distribution plate, and a plurality of first prewhirl flow distribution plate cooperations can drive the air current of flowing through between outer tube and the first inner tube and encircle the axis rotation of outer tube.

Description

Noise eliminator, engine and vehicle

Technical Field

The utility model relates to a noise elimination falls technical field, especially relates to a noise eliminator, engine and vehicle.

Background

The turbocharger is a standard configuration of an engine because the supercharger has obvious advantages in the aspects of improving power performance, fuel economy and the like, but the impeller of the supercharger rotates to drive gas to accelerate, pressure difference is generated in front of and behind the tongue tip of the impeller, BPF noise is caused by pressure pulsation, and meanwhile when the supercharger operates at a high pressure ratio and a low flow rate, disturbance is generated due to separation of gas flow at the inlet of a gas compressor, pressure fluctuation is generated, and whoosh noise is generated at the inlet of the supercharger. The BPF noise of the supercharger is characterized by narrow-frequency and high-frequency noise energy, the BPF noise is radiated to a cab through an air inlet of an air inlet system, the subjective feeling is metal scream, the subjective feeling of the Whoosh noise is that the "hissing" sound is generated at the air inlet of the supercharger, and the BPF noise and the Whoosh noise both seriously affect the comfort in a vehicle.

The existing silencer is generally designed according to a pipeline plane wave, the influence of a pipeline high-order mode (at a higher frequency, sound in the pipeline is not only transmitted in a plane wave form any more, but also the generation of the high-order sound mode is excited) is not considered, but the occurrence of high-order waves can greatly reduce the silencing performance of the silencer, the silencing frequency of the silencer cannot be further improved, the silencing frequency band of the silencer cannot be widened, and if the silencing is carried out in a wider frequency band and a higher frequency of up to ten thousand hertz, a pure reactance type silencer (a silencer which carries out silencing through a sudden change of a pipeline section or a bypass resonant cavity) in the prior art is difficult to obtain an ideal silencing effect. For the noise of the supercharger BPF, the rotating speed range of the supercharger BPF is large, the distribution range of the noise of the supercharger BPF is mainly concentrated in the range of 8000Hz-12000Hz, and meanwhile, due to the influence of high-order sound modes in a pipeline, a common noise eliminator can not eliminate the noise with high frequency, and does not have the noise elimination frequency band range with 4000Hz span. For the Whoosh noise, the Whoosh noise is broadband noise, the distribution range is mainly concentrated in 1000Hz-7000Hz, if the Woosh noise is eliminated by still adopting a silencer (a resonant cavity is installed), low-frequency silencing needs a large silencing space, and the space volume in engineering is difficult to meet the requirement.

Therefore, a muffler device, an engine and a vehicle are needed to solve the above problems.

SUMMERY OF THE UTILITY MODEL

An object of the utility model is to provide a noise eliminator, engine and vehicle restrain pipeline high-order acoustic mode's production, make noise eliminator have higher noise elimination effect at higher frequency to can obtain the noise elimination frequency band scope wideer of BPF noise, restrain the production of whoosh noise.

To achieve the purpose, the utility model adopts the following technical proposal:

a muffler assembly comprising:

the inner wall of the outer pipe is provided with a plurality of first silencing grooves surrounding the outer pipe along the circumferential direction of the outer pipe, the first silencing grooves are arranged at intervals along the axial direction of the outer pipe, and the groove depths of the first silencing grooves are different;

the first inner pipe is sleeved in the outer pipe, a plurality of second silencing grooves surrounding the first inner pipe along the circumferential direction of the first inner pipe are arranged on the inner wall of the first inner pipe, the plurality of second silencing grooves are arranged at intervals along the axial direction of the first inner pipe, and the groove depths of the second silencing grooves are different;

a plurality of first whirl flow distribution plates in advance, first whirl flow distribution plate by the one end of first inner tube extends to the other end of first inner tube, first whirl flow distribution plate is connected in advance the inner wall of outer tube with the outer wall of first inner tube, and is a plurality of first whirl flow distribution plate is followed the circumference interval of outer tube sets up, and is a plurality of first whirl flow distribution plate cooperation in advance can order about to flow through the outer tube with air current between the first inner tube encircles the axis of outer tube is rotatory.

Preferably, the muffler further comprises a second inner tube, the second inner tube is sleeved in the first inner tube, a plurality of third muffling grooves surrounding the second inner tube along the circumferential direction of the second inner tube are formed in the inner wall of the second inner tube, the plurality of third muffling grooves are arranged at intervals along the axial direction of the second inner tube, and the depths of the third muffling grooves are different;

a plurality of second is rotatory flow distribution plate in advance, the second in advance the rotatory flow distribution plate by the one end of second inner tube extends to the other end of second inner tube, the second is rotatory flow distribution plate in advance connect the inner wall of first inner tube with the outer wall of second inner tube is a plurality of the second is rotatory flow distribution plate in advance is followed the circumference interval of first inner tube sets up, and is a plurality of the second is rotatory flow distribution plate cooperation in advance can order about to flow through first inner tube with air current between the second inner tube encircles the axis of outer tube is rotatory.

Preferably, the inner wall of the outer pipe is provided with five first muffling grooves, the inner wall of the first inner pipe is provided with five second muffling grooves, and the inner wall of the second inner pipe is provided with three third muffling grooves.

Preferably, the outer tube, the first inner tube and the second inner tube are coaxially arranged.

Preferably, the distance between the inner wall of the outer tube and the outer wall of the first inner tube is equal to the distance between the inner wall of the first inner tube and the outer wall of the second inner tube.

Preferably, the method further comprises the following steps:

the inner diameter of the air inlet pipe is smaller than that of the outer pipe;

one end of the divergent pipe is communicated with the air inlet pipe, the other end of the divergent pipe is communicated with the outer pipe, and the diameter of the divergent pipe is gradually increased from one end communicated with the air inlet pipe to one end communicated with the outer pipe.

Preferably, the method further comprises the following steps:

the inner diameter of the air outlet pipe is smaller than that of the outer pipe;

and one end of the reducing pipe is communicated with the outer pipe, the other end of the reducing pipe is communicated with the air outlet pipe, and the diameter of the reducing pipe is gradually reduced from one end communicated with the outer pipe to one end communicated with the air outlet pipe.

Preferably, the inner diameter of the air inlet pipe is equal to the inner diameter of the air outlet pipe.

An engine comprising a muffler assembly as claimed in any one of the preceding claims.

A vehicle comprising a muffling apparatus of any of the above.

The utility model has the advantages that:

the utility model discloses a noise eliminator, engine and vehicle, the cross-section of outer tube is radially cut apart along the outer tube to first inner tube, the cross-section of outer tube is cut apart along the circumference of outer tube to a plurality of first whirl flow distribution plates in advance, the first whirl flow distribution plate of first inner tube cooperation is cut apart into a plurality of small cross-section passageways with the outer tube, the channel cross-section is less, the excitation frequency of pipeline high-order acoustics mode is higher, consequently, cut apart into a plurality of small cross-section passageways with the outer tube and can restrain the production of pipeline high-order acoustics mode, make noise eliminator have better noise elimination effect at higher frequency. Be provided with a plurality of first muffling grooves on the inner wall of outer tube, the groove depth of each first muffling groove is all inequality, and the first muffling groove of different groove depths corresponds the BPF noise of eliminating different frequencies respectively, is provided with a plurality of second muffling grooves on the inner wall of first inner tube, and the groove depth of each second muffling groove is all inequality, and the second muffling groove of different groove depths corresponds the BPF noise of eliminating different frequencies respectively to obtain the more wideer muffling frequency band scope to the BPF noise. The cooperation of a plurality of first prewhirl flow distribution plates can drive the air current that flows through between outer tube and the first inner tube and encircle the axis rotation of outer tube to make the air current rotatory after passing through noise eliminator, restrain the air current separation of booster air inlet, restrain the production of whoosh noise in the source. The noise reduction requirements of the engine turbocharger on BPF noise and whoosh noise are met.

Drawings

Fig. 1 is a schematic structural view of a muffler device provided by an embodiment of the present invention;

fig. 2 is a cross-sectional view of a muffler assembly according to an embodiment of the present invention;

fig. 3 is a sectional view of a part of the structure of a muffler device according to an embodiment of the present invention;

fig. 4 is a schematic view of a part of the structure of a muffler device according to an embodiment of the present invention;

fig. 5 is a cross-sectional view of a first inner tube of a muffler assembly according to an embodiment of the present invention;

FIG. 6 is a schematic view of a part of the muffler device according to the embodiment of the present invention;

fig. 7 is a cross-sectional view of a second inner tube of a muffler assembly according to an embodiment of the present invention;

fig. 8 is a schematic structural view of the muffler device according to the embodiment of the present invention when mounted on a supercharger.

In the figure:

100. a supercharger; 200. a turbine end;

1. an outer tube; 11. a first muffling slot;

2. a first inner tube; 21. a second muffling slot;

3. a first pre-rotation splitter plate;

4. a second inner tube; 41. a third muffling slot;

5. a second pre-rotation flow distribution plate;

6. an air inlet pipe;

7. a divergent pipe;

8. an air outlet pipe;

9. and (4) reducing the pipe.

Detailed Description

The present invention will be described in further detail with reference to the accompanying drawings and examples. It is to be understood that the specific embodiments described herein are merely illustrative of the invention and are not limiting of the invention. It should be further noted that, for the convenience of description, only some of the structures associated with the present invention are shown in the drawings, not all of them.

In the description of the present invention, unless otherwise explicitly specified or limited, the terms "connected", "connected" and "fixed" are to be construed broadly, e.g., as being fixedly connected, detachably connected, or integrated; can be mechanically or electrically connected; either directly or indirectly through intervening media, either internally or in any other relationship. The specific meaning of the above terms in the present invention can be understood as a specific case by those skilled in the art.

In the present application, unless expressly stated or limited otherwise, the recitation of a first feature "on" or "under" a second feature may include the recitation of the first and second features being in direct contact, and may also include the recitation of the first and second features not being in direct contact, but being in contact with another feature between them. Also, the first feature being "on," "above" and "over" the second feature includes the first feature being directly on and obliquely above the second feature, or merely indicating that the first feature is at a higher level than the second feature. A first feature being "under," "below," and "beneath" a second feature includes the first feature being directly under and obliquely below the second feature, or simply meaning that the first feature is at a lesser elevation than the second feature.

In the description of the present embodiment, the terms "upper", "lower", "right", and the like are used in the orientation or positional relationship shown in the drawings only for convenience of description and simplicity of operation, and do not indicate or imply that the device or element referred to must have a specific orientation, be constructed in a specific orientation, and be operated, and thus should not be construed as limiting the present invention. Furthermore, the terms "first" and "second" are used only for descriptive purposes and are not intended to be limiting.

As shown in fig. 1 to 8, the present embodiment provides a muffler device including an outer pipe 1, a first inner pipe 2, and a plurality of first pre-swirl flow distribution plates 3. Be provided with a plurality of first grooves 11 that eliminate noise that encircle outer tube 1 along the circumference of outer tube 1 on the outer tube 1 inner wall, a plurality of first grooves 11 that eliminate noise set up along the axial interval of outer tube 1, and the groove depth of each first groove 11 that eliminates noise is all inequality. The first inner tube 2 is sleeved in the outer tube 1, a plurality of second silencing grooves 21 which surround the first inner tube 2 along the circumferential direction of the first inner tube 2 are arranged on the inner wall of the first inner tube 2, the plurality of second silencing grooves 21 are arranged along the axial direction of the first inner tube 2 at intervals, and the groove depths of the second silencing grooves 21 are different. First whirl flow distribution plate 3 extends to the other end of first inner tube 2 by the one end of first inner tube 2 in advance, and the inner wall of outer tube 1 and the outer wall of first inner tube 2 are connected to first whirl flow distribution plate 3 in advance, and a plurality of first whirl flow distribution plates 3 set up along the circumference interval of outer tube 1 in advance, and a plurality of first whirl flow distribution plates 3 cooperation can order about the air current between outer tube 1 and the first inner tube 2 of flowing through and encircle the axis rotation of outer tube 1 in advance.

According to the silencer provided by the embodiment, the first inner pipe 2 divides the cross section of the outer pipe 1 along the radial direction of the outer pipe 1, the plurality of first pre-rotation flow distribution plates 3 divide the cross section of the outer pipe 1 along the circumferential direction of the outer pipe 1, the first inner pipe 2 is matched with the first pre-rotation flow distribution plates 3 to divide the outer pipe 1 into the plurality of small-section channels, the smaller the channel cross section is, the higher the excitation frequency of a high-order acoustic mode of a pipeline is, so that the generation of the high-order acoustic mode of the pipeline can be inhibited by dividing the outer pipe 1 into the plurality of small-section channels, and the silencer has a better silencing effect at a higher frequency. The inner wall of the outer pipe 1 is provided with a plurality of first silencing grooves 11, the depth of each first silencing groove 11 is different, the first silencing grooves 11 with different depths of grooves correspondingly eliminate BPF (noise reduction) noises with different frequencies respectively, the inner wall of the first inner pipe 2 is provided with a plurality of second silencing grooves 21, the depth of each second silencing groove 21 is different, and the second silencing grooves 21 with different depths of grooves correspondingly eliminate the BPF noises with different frequencies respectively, so that a wider silencing frequency band range for the BPF noises is obtained, and the BPF noise reduction requirement of the engine supercharger 100 is met. The first prewhirl splitter plates 3 are matched to drive the airflow flowing between the outer pipe 1 and the first inner pipe 2 to rotate around the axis of the outer pipe 1, so that the airflow rotates after passing through the silencer, the airflow separation of the air inlet of the supercharger 100 is inhibited, and the whoosh noise is inhibited from being generated at the source. Meeting the noise reduction requirements of the engine turbocharger 100 for BPF noise and whoosh noise.

Optionally, as shown in fig. 2, 6 and 7, the muffler device provided by the present embodiment further includes a second inner pipe 4 and a plurality of second pre-swirl flow distribution plates 5. The second inner tube 4 is sleeved in the first inner tube 2, a plurality of third silencing grooves 41 which surround the second inner tube 4 along the circumferential direction of the second inner tube 4 are arranged on the inner wall of the second inner tube 4, the third silencing grooves 41 are arranged along the axial direction of the second inner tube 4 at intervals, and the depth of each third silencing groove 41 is different. Second is rotatory flow distribution plate 5 in advance extends to the other end of second inner tube 4 by the one end of second inner tube 4, and the inner wall of first inner tube 2 and the outer wall of second inner tube 4 are connected to second is rotatory flow distribution plate 5 in advance, and a plurality of second is rotatory flow distribution plate 5 in advance sets up along the circumference interval of first inner tube 2, and a plurality of second are rotatory flow distribution plate 5 cooperation in advance can order to order about the air current of flowing through between first inner tube 2 and the second inner tube 4 and encircle the axis rotation of outer tube 1. The sectional size of the divided channel can be further reduced by arranging the second inner pipe 4 and the plurality of second pre-rotation flow distribution plates 5, so that the generation of high-order acoustic modes of the pipeline can be better inhibited. The second pre-rotation flow distribution plates 5 can drive the airflow entering between the second inner tube 4 and the first inner tube 2 to rotate, so that the airflow can be kept rotating more stably after passing through the silencer, the airflow separation of the air inlet of the supercharger 100 is further inhibited, and the generation of whoosh noise is further inhibited.

The utility model discloses mainly adopt slit noise elimination unit to eliminate the BPF noise, slit noise cancelling structure is 1/4 wavelength noise elimination unit actually, and the degree of depth of slit has decided the noise elimination frequency of this structure, noise elimination frequencyfThe calculation formula of (a) is as follows:

wherein,fin order to achieve a sound-damping frequency,cis the speed of propagation of the sound,l _e the equivalent acoustic length of the slit depth. Since the frequency spectrum of the BPF noise is mainly distributed within 8000-.

Specifically, as shown in fig. 3, 5 and 7, in the present embodiment, five first muffling grooves 11 are provided on the inner wall of the outer pipe 1, five second muffling grooves 21 are also provided on the first inner pipe 2, and the groove depths of the five first muffling grooves 11 are equal to the groove depths of the five second muffling grooves 21 in one-to-one correspondence, that is, the largest one of the five first muffling grooves 11 is equal to the largest one of the five second muffling grooves 21, the smallest one of the five first muffling grooves 11 is equal to the smallest one of the five second muffling grooves 21, and the groove depths of the middle three first muffling grooves 11 and the middle three second muffling grooves 21 are also equal to each other. The five first muffling grooves 11 are mainly used for eliminating the BPF noise in the range of 8000Hz to 12000Hz respectively, for example, the first muffling groove 11 with the largest groove depth is mainly used for eliminating the BPF noise near 8000Hz, the first muffling groove 11 with the second largest groove depth is mainly used for eliminating the BPF noise near 9000Hz, the first muffling groove 11 with the third largest groove depth is mainly used for eliminating the BPF noise near 10000Hz, the first muffling groove 11 with the fourth largest groove depth is mainly used for eliminating the BPF noise near 11000Hz, and the first muffling groove 11 with the smallest groove depth is mainly used for eliminating the BPF noise near 12000 Hz. The correspondence relationship between the five second muffling grooves 21 and the BPF noise frequency is the same as that between the five first muffling grooves 11. In other embodiments, a different number of first muffling slots 11 and second muffling slots 21 may be employed. The inner wall of the second inner tube 4 is provided with three third muffling grooves 41, the largest one of the three third muffling grooves 41 is equal to the largest one of the five first muffling grooves 11, the smallest one of the three third muffling grooves 41 is equal to the smallest one of the five first muffling grooves 11, and the middle one of the three third muffling grooves 41 is equal to the middle one of the five first muffling grooves 11. Because the inner diameter of the second inner tube 4 is smaller, the second inner tube 4 can have a better noise reduction effect on the BPF noise of 8000Hz-12000Hz only by arranging the three third noise reduction grooves 41.

Alternatively, as shown in fig. 2, the outer tube 1, the first inner tube 2, and the second inner tube 4 are coaxially arranged, so as to ensure the guiding and rotating effect of the first pre-swirl flow distribution plate 3 and the second pre-swirl flow distribution plate 5 on the airflow.

Alternatively, as shown in fig. 2, the distance between the inner wall of the outer tube 1 and the outer wall of the first inner tube 2 is equal to the distance between the inner wall of the first inner tube 2 and the outer wall of the second inner tube 4.

Optionally, as shown in fig. 1 to 3, the muffler device provided by the present embodiment further includes an air inlet pipe 6 and a divergent pipe 7. The inner diameter of the air inlet pipe 6 is smaller than that of the outer pipe 1. One end of the divergent pipe 7 is communicated with the air inlet pipe 6, the other end is communicated with the outer pipe 1, and the diameter of the divergent pipe 7 is gradually increased from the end communicated with the air inlet pipe 6 to the end communicated with the outer pipe 1. Because the first inner tube 2 and the second inner tube 4 are arranged in the outer tube 1, the cross section of the channel in the outer tube 1 is reduced, so that the inner diameter of the air inlet tube 6 needs to be smaller than the inner diameter of the outer tube 1, the flow cross section area of the outer tube 1 can be the same as that of the outer tube 1, and the generation of overhigh back pressure at the outer diameter 1 is avoided.

Optionally, as shown in fig. 1-3, the muffler device of the present embodiment further includes a wind outlet pipe 8 and a reducer pipe 9. The inner diameter of the air outlet pipe 8 is smaller than that of the outer pipe 1. One end of the reducing pipe 9 is communicated with the outer pipe 1, the other end is communicated with the air outlet pipe 8, and the diameter of the reducing pipe 9 is gradually reduced from the end communicated with the outer pipe 1 to the end communicated with the air outlet pipe 8. After passing through the outer pipe 1, the air outlet pipe 8 is connected through the reducer 9, so that the diameter of the air outlet pipe 8 is reduced, and the air outlet pipe 8 is convenient to be connected with subsequent parts of an engine.

Alternatively, as shown in fig. 2 and 3, the inner diameter of the air inlet pipe 6 is equal to the inner diameter of the air outlet pipe 8, so as to keep the flow cross-sectional area of the air inlet pipe 6 equal to the flow cross-sectional area of the air outlet pipe 8, thereby ensuring the quality of inlet air.

Alternatively, as shown in fig. 2, 4 and 6, each of the first pre-swirl flow distribution plates 3 and each of the second pre-swirl flow distribution plates 5 are biased in a clockwise direction or a counterclockwise direction in the axial direction of the outer tube 1. Specifically, in the present embodiment, each of the first pre-swirl flow distribution plates 3 and each of the second pre-swirl flow distribution plates 5 are biased clockwise from the end of the outer pipe 1 close to the air inlet pipe 6 toward the end of the outer pipe 1 far from the air inlet pipe 6.

The silencing performance is evaluated by transmission loss TL, and is defined as the difference between the incident sound power level of an acoustic inlet and the transmission sound power level of an acoustic outlet, and the corresponding calculation formula is as follows:

wherein,

incident sound power is the acoustic inlet of the silencing device;

transmitting acoustic power to the acoustic outlet of the muffling apparatus.

Through calculation, the transmission loss of the silencer is above 10dBA within a frequency band of 8000Hz-12000Hz in which the 100BPF noise is mainly concentrated, and the silencing capability is good.

The embodiment also provides an engine, as shown in fig. 8, including the above noise eliminator, further including a supercharger 100 and a turbine end 200, where the supercharger 100 is connected to the turbine end 200, and an air outlet pipe 8 of the noise eliminator is connected to an air inlet of the supercharger 100.

The embodiment also provides a vehicle comprising the muffler device.

It is to be understood that the above-described embodiments of the present invention are merely examples for clearly illustrating the present invention and are not intended to limit the embodiments of the present invention. Numerous obvious variations, rearrangements and substitutions will now occur to those skilled in the art without departing from the scope of the invention. And are neither required nor exhaustive of all embodiments. Any modification, equivalent replacement, and improvement made within the spirit and principle of the present invention should be included in the protection scope of the claims of the present invention.

Claims (10)

1. A muffler assembly, comprising:

the inner wall of the outer pipe (1) is provided with a plurality of first silencing grooves (11) which surround the outer pipe (1) along the circumferential direction of the outer pipe (1), the first silencing grooves (11) are arranged at intervals along the axial direction of the outer pipe (1), and the groove depths of the first silencing grooves (11) are different;

the inner pipe (2) is sleeved in the outer pipe (1), a plurality of second silencing grooves (21) which surround the first inner pipe (2) along the circumferential direction of the first inner pipe (2) are formed in the inner wall of the first inner pipe (2), the second silencing grooves (21) are arranged at intervals along the axial direction of the first inner pipe (2), and the groove depths of the second silencing grooves (21) are different;

a plurality of first whirl flow distribution plates (3) in advance, first whirl flow distribution plates (3) by the one end of first inner tube (2) extends to the other end of first inner tube (2), first whirl flow distribution plates (3) are connected in advance the inner wall of outer tube (1) with the outer wall of first inner tube (2), and is a plurality of first whirl flow distribution plates (3) are followed the circumference interval setting of outer tube (1) is a plurality of first whirl flow distribution plates (3) cooperation can order about to flow through outer tube (1) with air current between first inner tube (2) encircles the axis of outer tube (1) is rotatory.

2. A muffler device according to claim 1, further comprising a second inner pipe (4), wherein the second inner pipe (4) is sleeved in the first inner pipe (2), the inner wall of the second inner pipe (4) is provided with a plurality of third muffling grooves (41) which surround the second inner pipe (4) along the circumferential direction of the second inner pipe (4), the plurality of third muffling grooves (41) are arranged at intervals along the axial direction of the second inner pipe (4), and the depth of each third muffling groove (41) is different;

a plurality of second is whirl flow distribution plate (5) in advance, second whirl flow distribution plate (5) in advance by the one end of second inner tube (4) extends to the other end of second inner tube (4), second whirl flow distribution plate (5) are connected in advance the inner wall of first inner tube (2) with the outer wall of second inner tube (4), and are a plurality of second whirl flow distribution plate (5) are followed in advance the circumference interval setting of first inner tube (2), and are a plurality of second whirl flow distribution plate (5) cooperation can be ordered about to flow through first inner tube (2) with air current between second inner tube (4) encircles the axis of outer tube (1) is rotatory.

3. A sound-damping arrangement according to claim 2, characterised in that five first damping grooves (11) are provided in the inner wall of the outer pipe (1), five second damping grooves (21) are provided in the inner wall of the first inner pipe (2), and three third damping grooves (41) are provided in the inner wall of the second inner pipe (4).

4. A sound-damping arrangement according to claim 2, characterised in that the outer pipe (1), the first inner pipe (2) and the second inner pipe (4) are arranged coaxially.

5. A sound-damping arrangement according to claim 4, characterised in that the distance between the inner wall of the outer pipe (1) and the outer wall of the first inner pipe (2) is equal to the distance between the inner wall of the first inner pipe (2) and the outer wall of the second inner pipe (4).

6. The muffling device of claim 1, further comprising:

an air inlet pipe (6) having an inner diameter smaller than the inner diameter of the outer pipe (1);

one end of the divergent pipe (7) is communicated with the air inlet pipe (6), the other end of the divergent pipe is communicated with the outer pipe (1), and the diameter of the divergent pipe (7) is gradually increased from the end communicated with the air inlet pipe (6) to the end communicated with the outer pipe (1).

7. The muffling device of claim 6, further comprising:

the inner diameter of the air outlet pipe (8) is smaller than that of the outer pipe (1);

one end of the reducing pipe (9) is communicated with the outer pipe (1), the other end of the reducing pipe is communicated with the air outlet pipe (8), and the diameter of the reducing pipe (9) is gradually reduced from the end communicated with the outer pipe (1) to the end communicated with the air outlet pipe (8).

8. A sound-damping arrangement according to claim 7, characterised in that the inner diameter of the inlet duct (6) is equal to the inner diameter of the outlet duct (8).

9. An engine comprising the muffler device defined in any one of claims 1 to 8.

10. A vehicle comprising a muffler assembly according to any one of claims 1 to 8.

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