JP2012067673A - Muffler - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a muffler capable of reducing the pressure loss without causing the suction gas flow to be turbulent and widening the frequency band to be silenced.SOLUTION: An internal combustion engine includes a side branch 30 provided at a second suction pipe 15 through which the suction gas flows, and the internal space 31 of this side branch 30 is partitioned by walls 361, 362, 363, 364, 365, 366 extending in the axial direction of the second suction pipe 15 from the internal bottom surface 331 of the side branch 30, wherein the partitioned internal space 31 is put in communication with the second suction passage 151. This shortens the region where the section area of the second suction passage 151 enlarges, and the suction gas flow becomes unlikely to be turbulent, which reduces the pressure loss. Because one side branch 30 has a plurality of openings 391, 392, 393, 394, 395, 396, 397 having communication with the second suction passage 151, the one side branch can silence sounds of different frequencies, and it is possible to widen the frequency band to be silenced.

Description

  The present invention relates to a silencer provided in an intake pipe of an internal combustion engine.

  Conventionally, as a countermeasure for noise generated in an internal combustion engine, it is known to provide a silencer such as a side branch or a resonator in the middle of an intake passage formed by an intake pipe.

  Patent Document 1 discloses an intake pipe of a turbo mounted engine provided with a side branch and a resonator. In a turbo-mounted engine, a wide high frequency band of 2 to 3 kHz is generated by the rotation of a turbo compressor and the compression of air. On the other hand, by increasing the inner diameter of the side branch, the frequency that can be silenced by the side branch is set wider.

European Patent Application Publication No. 1548701

  However, by increasing the inner diameter of the side branch, a section in which the radial cross-sectional area of the intake passage is enlarged is formed in the intake pipe, and the flow of intake air is likely to be disturbed. When the air flow is disturbed, a large pressure loss occurs, and the pressure increased in the turbocharger is wasted. In addition, in the conventional side branch, the frequency to be muffled is one for each side branch. In order to mute the sound in a wide frequency band, a plurality of side branches having different frequencies to be muffled are used. It is necessary to align. As a result, the number of sections in which the radial cross-sectional area of the intake passage is larger than the radial cross-sectional area of the intake passage without the side branch increases, and the pressure loss increases.

  An object of the present invention is to provide a silencer capable of reducing pressure loss and expanding a frequency band that can be silenced without disturbing the flow of intake air.

  According to the first aspect of the present invention, the silencer includes an intake pipe, a side branch, and a wall body. The intake pipe forms an intake passage through which intake air taken into the combustion chamber of the internal combustion engine flows. The side branch is provided on the wall surface of the intake pipe, protrudes in the radially outward direction of the intake pipe, and has an internal space that communicates with the intake passage. The wall body rises from the inner bottom surface of the side branch in the radial direction of the intake pipe and partitions the internal space of the side branch into a plurality of communication spaces that communicate with the intake passage. By providing a wall that partitions the internal space of the side branch, the section in which the radial cross-sectional area of the intake passage is larger than the radial cross-sectional area of the intake passage without the side branch becomes intermittent and short. The flow is less disturbed. As a result, pressure loss is unlikely to occur, and the increased pressure can be used effectively.

  Further, in the side branch type silencer, the frequency that can be silenced is 1 based on the length of the side branch and the diameter of the virtual circle calculated when the area of the opening where the side branch communicates with the intake passage is replaced with the area of the circle. Will be determined. According to the first aspect of the present invention, a plurality of openings of the side branch are formed by partitioning the internal space of one side branch by the wall body. As a result, the side branch has a plurality of virtual circle diameters calculated when the area of the opening is replaced with the area of the circle, and sounds of a plurality of frequencies can be silenced by one side branch. That is, the frequency band that can be silenced can be expanded.

  According to the invention of claim 2, the wall body is installed so as to include a section in which the distance between one wall body and the other wall body adjacent to the one wall body or the side wall of the side branch is equal. ing. Thereby, the internal space of the side branch is composed of a plurality of communication spaces having different opening areas. Since one side branch has a plurality of different opening areas, one side branch has a diameter of a plurality of virtual circles, so that sounds of a plurality of frequencies can be silenced. Therefore, the frequency band that can be silenced by one side branch can be expanded.

  According to the invention of claim 3, the wall body is installed so as to include a section in which the distance between one wall body and the other wall body adjacent to the one wall body or the side wall of the side branch is unequal. Has been. At this time, the side branch has a plurality of intervals between the wall bodies installed on the inner bottom surface of the side branch or between the wall body and the side wall of the side branch. The plurality of intervals may be different from each other, some may be installed at equal intervals, and the rest may be installed at intervals different from others. Thereby, the size of the plurality of openings formed in the side branch can be set according to the size of the frequency to be muffled and the frequency band, and the frequency band that can be muffled can be further expanded. .

  According to the fourth aspect of the present invention, the wall body is formed so as to be substantially orthogonal to the central axis of the intake pipe. Thereby, the length of the intake pipe in which the radial cross-sectional area of the intake passage is enlarged is shortened, and the flow of intake air is less likely to be disturbed. Therefore, pressure loss can be reduced.

  According to the invention which concerns on Claim 5, the wall body is formed in parallel with respect to the central axis of an intake pipe. As a result, the opposite end surface of the wall that does not contact the inner bottom surface of the side branch is along the flow direction of the intake air, so that the flow of intake air is not hindered. Therefore, the flow of intake air is less likely to be disturbed, and pressure loss can be reduced.

  According to the invention of claim 6, the wall body is formed such that its height decreases from the upstream side of the intake passage toward the center of the side branch and increases from the center of the side branch toward the downstream side of the intake passage. Yes. As described above, the frequency at which one side branch can mute is determined by the diameter of the virtual circle calculated from the length of the side branch and the opening area of the side branch. In the invention which concerns on Claim 6, the frequency which can be muffled can be set in multiple by changing the height of the wall body equivalent to the length of a side branch between wall bodies. Thereby, the frequency band which can be muffled by one side branch can be expanded.

  According to the invention which concerns on Claim 7, the wall body is formed so that the height may become lower than the height from the inner bottom face of a side branch to the wall surface of an intake pipe. As a result, the opposite end portion of the wall that is not in contact with the inner bottom surface of the side branch does not come into contact with the flow of intake air, so that the flow of intake air flowing through the intake passage is not disturbed. Therefore, the pressure loss of the intake air can be reduced.

  According to the eighth aspect of the invention, the side branch is provided in the intake pipe that connects the turbocharger and the intercooler. Thereby, the air immediately after being compressed by the turbocharger can be silenced with a small pressure loss.

It is a mimetic diagram of an air intake device to which a silencer of a 1st embodiment of the present invention is applied. BRIEF DESCRIPTION OF THE DRAWINGS It is sectional drawing of the silencer of 1st Embodiment of this invention, (a) Sectional drawing perpendicular | vertical with respect to the inner bottom face of a side branch, and including the central axis of an intake pipe, (b) (a) Section of IIb-IIb FIG. It is typical sectional drawing of the silencer of 2nd Embodiment of this invention, (a) Sectional drawing perpendicular | vertical with respect to the inner bottom face of a side branch, and including the central axis of an intake pipe, (b) (a) IIIb- It is sectional drawing of IIIb. It is typical sectional drawing of the silencer of 3rd Embodiment of this invention, (a) Sectional drawing perpendicular | vertical with respect to the inner bottom face of a side branch, and including the central axis of an intake pipe, (b) (a) IVb- It is sectional drawing of IVb. It is typical sectional drawing of the silencer of 4th Embodiment of this invention, (a) Sectional drawing perpendicular | vertical with respect to the inner bottom face of a side branch, and including the central axis of an intake pipe, (b) (a) Vb- It is sectional drawing of Vb. It is typical sectional drawing of the silencer of 5th Embodiment of this invention, (a) Sectional drawing perpendicular | vertical with respect to the inner bottom face of a side branch, and including the central axis of an intake pipe, (b) (a) VIb- It is sectional drawing of VIb. It is typical sectional drawing of the silencer of other embodiment of this invention, (a) Sectional drawing perpendicular | vertical with respect to the inner bottom face of a side branch, and including the central axis of an intake pipe, (b) (a) VIIb- It is sectional drawing of VIIb. It is typical sectional drawing of the silencer of other embodiment of this invention, (a) Sectional drawing perpendicular | vertical with respect to the inner bottom face of a side branch, and including the central axis of an intake pipe, (b) (a) VIIIb- It is sectional drawing of VIIIb. It is typical sectional drawing of the silencer of other embodiment of this invention, (a) Sectional drawing perpendicular | vertical with respect to the inner bottom face of a side branch, and including the central axis of an intake pipe, (b) (a) IXb- It is sectional drawing of IXb.

  Hereinafter, embodiments of the present invention will be described with reference to the drawings. Hereinafter, an embodiment in which the present invention is applied to an intake device equipped with a turbocharger that supplies compressed air to a vehicle engine will be described.

(First embodiment)
FIG. 1 shows an intake device for an internal combustion engine according to a first embodiment of the present invention. The intake device 10 includes an air intake port 111, an air cleaner 11, a turbocharger 14, a side branch 30, an intercooler 16, a throttle valve 18, an intake manifold 19, and the like.

  The first intake pipe 13, the second intake pipe 15, and the third intake pipe 17 as intake pipes installed in the intake device 10 are all formed in a substantially cylindrical shape, and are respectively a first intake passage 131 and a second intake passage. 151, a third intake passage 171 is formed. The first intake pipe 13, the second intake pipe 15, and the third intake pipe 17 correspond to the “intake pipe” recited in the claims, and include the first intake passage 131, the second intake passage 151, and the third intake passage. Reference numeral 171 corresponds to an “intake passage” recited in the claims. The first intake pipe 13 connects the air cleaner 11 and the turbocharger 14. The air cleaner 11 has a box shape, and an air intake 111 for taking in outside air is formed on the upstream side. The downstream side of the air cleaner 11 is connected to the first intake pipe 13, and the air from which foreign matter has been removed by the air cleaner 11 is sent to the turbocharger 14 through the first intake passage 131.

  An aero flow meter 12 is installed in the middle of the first intake pipe 13. The aero flow meter 12 measures the flow rate of the air that has passed through the air cleaner 11.

  The turbocharger 14 connected to the first intake pipe 13 compresses the air sent from the first intake passage 131 by the rotation of the turbo compressor 141, and the second intake passage 151 formed by the second intake pipe 15. Send to.

  The second intake pipe 15 connects the turbocharger 14 and the intercooler 16. The second intake pipe 15 sends the air compressed by the turbocharger 14 to the intercooler 16. A side branch 30 is installed on a pipe wall 155 that forms the second intake pipe 15. Details of the side branch 30 will be described later.

The air whose temperature has risen due to compression in the turbocharger 14 is cooled by passing through the intercooler 16 and is sent to the third intake passage 171 formed by the third intake pipe 17. The third intake pipe 17 connects the intercooler 16 and the intake manifold 19, and a throttle valve 18 is installed on the downstream side of the third intake pipe 17. The throttle valve 18 adjusts the amount of air supplied to the engine, and the adjusted air is sent to the intake manifold 19.
The air introduced into the intake manifold 19 is branched for each cylinder of the engine 195 and supplied to the engine 195.

Next, the side branch 30 will be described with reference to FIG.
The side branch 30 has a bottomed concave shape and is installed so as to protrude from the tube wall 155 of the second intake pipe 15. The bottom wall 33 of the side branch 30 is substantially circular and is installed substantially parallel to the central axis Z of the second intake pipe 15. The side wall 32 of the side branch 30 has a substantially tubular shape, and one end not connected to the bottom wall 33 is connected to the tube wall 155 of the second intake pipe 15. The internal space 31 formed by the bottom wall 33 and the side wall 32 communicates with the second intake passage 151 formed by the second intake pipe 15.

  The partition walls 361, 362, 363, 364, 365, and 366 as “wall bodies” are formed integrally with the bottom wall 33 and the side wall 32, for example, by resin, and are formed with respect to the central axis Z of the second intake pipe 15. It is installed almost vertically. The sectional shape of the surface perpendicular to the central axis Z of the partition walls 361, 362, 363, 364, 365, 366 is the tube wall 155 of the second intake pipe 15 at the upper end of the partition walls 361, 362, 363, 364, 365, 366. It is the flat plate made into the circular arc shape along the shape. The communication space 311 is formed by the partition wall 361, the side wall 32, and the bottom wall 33. The communication space 312 is formed by the partition wall 361, the partition wall 362, the side wall 32, and the bottom wall 33. The communication space 313 is formed by the partition wall 362, the partition wall 363, the side wall 32, and the bottom wall 33. The communication space 314 is formed by the partition wall 363, the partition wall 364, the side wall 32, and the bottom wall 33. The communication space 315 is formed by the partition wall 364, the partition wall 365, the side wall 32, and the bottom wall 33. The communication space 316 is formed by a partition wall 365, a partition wall 366, a side wall 32, and a bottom wall 33. The communication space 317 is formed by the partition wall 366, the side wall 32, and the bottom wall 33.

The partition walls 361, 362, 363, 364, 365, and 366 are installed at equal intervals. Specifically, as shown in FIG. 3B, the distance between the inner side surface 32 and the upstream side surface 371 of the partition wall 361 from the upstream side of the second intake passage 151 along the central axis Z is L ₃₁ . The distance between the downstream side surface 381 of the wall 361 and the upstream side surface 372 of the partition wall 362 is L ₃₂ , the distance between the downstream side surface 382 of the partition wall 362 and the upstream side surface 373 of the partition wall 363 is L ₃₃ , and the partition wall 363. The distance between the downstream side surface 383 of the partition wall 364 and the upstream side surface 374 of the partition wall 364 is L ₃₄ , the distance between the downstream side surface 384 of the partition wall 364 and the upstream side surface 375 of the partition wall 365 is L ₃₅ , and the downstream of the partition wall 365. The distance between the side surface 385 and the upstream side surface 376 of the partition wall 366 is L ₃₆ , and the distance between the downstream side surface 386 and the inner surface 32 of the partition wall 366 is L ₃₇ . At this _{time, L 31 = L 32 = L} 33 = L 34 = L 35 = L 36 = partition wall 361,362,363,364,365,366 as L becomes ₃₇ are installed.

The communication spaces 311, 312, 313, 314, 315, 316, and 317 have openings 391, 392, 393, 394, 395, 396, 397 that communicate with the second intake passage 151. The respective opening areas S ₃₁ , S ₃₂ , S ₃₃ , S ₃₄ , S ₃₅ , S ₃₆ , S _{37 have} a size relationship of S ₃₄ > S ₃₃ = S ₃₅ > S ₃₂ = S ₃₆ > S ₃₁ = S ₃₇ . is there.

As shown in FIG. 2, the partition wall 361 extending from the inner bottom surface 331 from the lower end surfaces 341, 342, 343, 345, 346 where the partition walls 361, 362, 363, 364, 365, 366 and the inner bottom surface 331 are connected. , 362, 363, 364, 365, 366, heights H ₃₁ , H ₃₂ , H ₃₃ , H ₃₄ , H ₃₅ , H ₃₆ up to upper end surfaces 351, 352, 353, 354, 355, 356 The relationship is H ₃₁ = H ₃₂ = H ₃₃ = H ₃₄ = H ₃₅ = H ₃₆ , and the height H from the inner bottom surface 331 of the inner side surface 321 to the outer side surface 156 of the pipe wall 155 of the second intake passage 15 is It is the same height.

(Function)
During operation of the engine 195, air taken in from the air intake port 111 passes through the air cleaner 11 and is sent to the turbocharger 14. In the turbocharger 14, air is compressed by the rotation of the turbo compressor 141, and at this time, a sound in a wide high frequency band is generated.

  The air compressed by the turbo compressor 141 goes to the intercooler 16 through the second intake passage 151. At this time, the air flowing through the second intake passage 151 in the communication spaces 311, 312, 313, 314, 315, 316, and 317 formed in the side branch 30 installed on the pipe wall 155 of the second intake passage 151. Sound is generated due to changes in density. The sound detouring the communication spaces 311, 312, 313, 314, 315, 316 and 317 interferes with the sound of the air flowing through the second intake passage 151, and the sound generated by the turbo compressor 141 is muted. .

(effect)
Next, the effect of the side branch 30 according to the first embodiment of the present invention will be described in comparison with a comparative example having no wall body.

(1) When a comparative example having no wall is applied to a turbo-equipped vehicle, the frequency that requires silencing is as wide as 2 to 3 kHz, so the opening area of the side branch is compared to the radial cross-sectional area of the intake passage. It needs to be bigger. At this time, the radial cross-sectional area of the intake passage in the section where the side branch is installed is larger than the radial cross-sectional area of the intake passage in the section where there is no side branch. Further, since the section where the radial cross-sectional area of the intake passage is large is continuously long, the air flow is likely to be disturbed and a large pressure loss is likely to occur. Therefore, the pressure boosted by the turbocharger is wasted.
In the first embodiment of the present invention, the internal space 31 of the side branch 30 is divided by partition walls 361, 362, 363, 364, 365, and 366. As a result, in the second intake pipe 15, the section in which the radial cross-sectional area of the second intake passage 151 is increased is shortened, and the section in which the cross-sectional area is increased continues intermittently, so that the air flow is less likely to be disturbed. Therefore, the pressure loss is reduced, and the pressure increased by the turbocharger can be used effectively.

(2) In the comparative example having no wall body, the diameter L and the height H of the opening of the side branch are each one, and therefore the frequency aimed at silencing with one side branch is limited to one.
On the other hand, in the first embodiment of the present invention, the internal space 31 of the side branch 30 is divided into seven spaces by partition walls 361, 362, 363, 364, 365, and 366. Accordingly, since the side branch 30 has seven openings, the diameter of the virtual circle calculated when each of the opening areas is converted into a circle area is seven. Therefore, the side branch has seven silencing frequencies, and the frequency that can be silenced can be expanded by one side branch.

(Second Embodiment)
A silencer according to a second embodiment of the present invention is shown in FIG. The second embodiment differs from the first embodiment in the arrangement direction of the partition walls. In addition, the same code | symbol is attached | subjected to the component substantially the same as 1st Embodiment.
In the second embodiment, as shown in FIG. 3, the partition walls 461, 462, 463, 464, 465, 466 of the side branch 40 are arranged in parallel with the central axis Z of the second intake pipe 15. At this time, the sections of the partition walls 461, 462, 463, 464, 465, and 466 are substantially rectangular in cross section on a plane perpendicular to the bottom surface 43 and parallel to the central axis Z. Thereby, since the upper end surfaces 451, 452, 453, 454, 455, and 456 of the partition walls 461, 462, 463, 464, 465, and 466 are along the air flow direction, it is difficult to disturb the air flow. . Therefore, in addition to the effects (1) and (2) of the first embodiment, the pressure loss can be further reduced.

(Third embodiment)
A silencer according to a third embodiment of the present invention is shown in FIG. The third embodiment differs from the first embodiment in the arrangement interval of the partition walls. In addition, the same code | symbol is attached | subjected to the component substantially the same as 1st Embodiment.
In the third embodiment, the partition walls 561, 562, 563, 564, 565, and 566 that partition the internal space 51 of the side branch 50 are arranged at different intervals. Specifically, the relationship between the distances L ₅₁ , L ₅₂ , L ₅₃ , L ₅₄ , L ₅₅ , L ₅₆ , and L ₅₇ representing the interval between the partition walls is L ₅₄ > L ₅₃ = L ₅₅ > L ₅₂ = L ₅₆ > L ₅₁ = L ₅₇ Further, compared to the first embodiment, the distance L ₅₄ representing the interval between the section walls is longer than the distance L ₃₄ in the first embodiment. The distances L ₅₁ and L ₅₇ are shorter than the distances L ₃₁ and L ₃₇ in the first embodiment. Accordingly, the opening area S ₅₄ of the opening 594 is larger than the opening area S ₃₄ of the opening 394 in the first embodiment. Further, the opening areas S ₅₁ and S ₅₇ of the openings 591 and 597 are smaller than the opening areas S ₃₁ and S ₃₇ of the openings 391 and 397 of the first embodiment. That is, the difference between the maximum value and the minimum value of the diameter of the virtual circle calculated from the opening area is larger than that in the first embodiment. Thereby, the frequency which can be muffled can be expanded. Therefore, in addition to the effects (1) and (2) of the first embodiment, it is possible to further expand the muffleable frequency band.

(Fourth embodiment)
A silencer according to a fourth embodiment of the present invention is shown in FIG. The fourth embodiment differs from the third embodiment in the height of the partition wall. In addition, the same code | symbol is attached | subjected to the component substantially the same as 3rd Embodiment.
In the fourth embodiment, the partition walls 661, 662, 663, 664, 665, 666 that partition the internal space 61 of the side branch 60 are formed at different heights. Specifically, the height H of the side branch 60 and the lower end surfaces 641, 642, 643, 644, 645, 645, 646 of the partition walls 661, 662, 663, 664, 665, 666 are changed to the upper end surfaces 651, 652, 653. , 654, 655, 655, 656, the height relationship between the heights H ₆₁ , H ₆₂ , H ₆₃ , H ₆₄ , H ₆₅ , H ₆₆ is as follows: H = H ₆₁ = H ₆₆ > H ₆₂ = H ₆₅ > H and it has a ₆₃ = H _64. That is, the communication spaces 612, 613, 614, 615, and 616 partitioned by the partition walls 662, 663, 664, and 665 have a height that determines the silencing frequency as a side branch type silencer and the height H of the side branch 60. Low compared. Thereby, in addition to the effect of 3rd Embodiment, the frequency muffled by communication space 612, 613, 614, 615, 616 can be further expanded compared with 3rd Embodiment.

(Fifth embodiment)
A silencer according to a fifth embodiment of the present invention is shown in FIG. The fifth embodiment differs from the third embodiment in the height of the partition wall. In addition, the same code | symbol is attached | subjected to the component substantially the same as 3rd Embodiment.
In the fifth embodiment, the partition walls 761, 762, 763, 764, 765, and 766 that partition the internal space 71 of the side branch 70 are formed at a height different from the height H of the side branch 70. . Specifically, the height H of the side branch 70 and the lower end surfaces 741, 742, 743, 744, 745, 745, and 746 of the partition walls 761, 762, 763, 764, 765, and 766 to the upper end surfaces 751, 752, and 753. , 754, 755, 755, and 756, the magnitude relationship with the heights H ₇₁ , H ₇₂ , H ₇₃ , H ₇₄ , H ₇₅ , H ₇₆ is as follows: H> H ₇₁ = H ₇₂ = H ₇₃ = H ₇₄ = H a ₇₅ = H _76. As a result, the upper end surfaces 751, 752, 753, 754, 755, 755, and 756 of the partition walls 761, 762, 763, 764, 765, and 766 do not come into contact with the air flowing through the second intake passage 151. (2) The air flow in the intake passage 151 is not disturbed. Therefore, in addition to the effects of the third embodiment, the pressure loss can be further reduced.

(Other embodiments)
(A) In the first embodiment and the third to fifth embodiments, the installation direction of the partition wall of the side branch is perpendicular to the central axis of the intake pipe. However, the installation direction of the partition wall is not limited to this. It may be parallel to the central axis of the intake pipe as in the second embodiment. For example, FIG. 7 shows a side branch 80 in an embodiment corresponding to the third embodiment of FIG. For example, FIG. 8 shows the side branch 90 in an embodiment corresponding to the fourth embodiment of FIG. For example, FIG. 9 shows the side branch 100 in an embodiment corresponding to the fifth embodiment of FIG. Further, the installation direction of the partition wall of the side branch may be oblique to the central axis of the intake pipe. By installing the partition wall obliquely with respect to the fluid flow direction, the fluid flow direction can be controlled.

  (A) In the above embodiment, the partition wall of the side branch is installed perpendicular to the inner bottom surface of the side branch. However, the installation angle on the inner bottom surface of the partition wall is not limited to this.

  (C) In the above embodiment, six partition walls of the side branch are installed. However, the number of partition walls is not limited to this. It is preferable to install more partition walls as the volume of the internal space of the side branch is larger.

  (D) In the first embodiment and the second embodiment described above, the partition walls are all set at equal intervals. Moreover, in said 3rd Embodiment-5th Embodiment, the installation space | interval of a partition wall was narrowed toward the upstream and downstream direction of the flow of intake air from the center of the side branch, and it was set as the contrast with respect to the center of the side branch. However, the interval between the partition walls is not limited to this. All the installation intervals may be different distances, some of the plurality of intervals may be equal intervals, and the rest may be different intervals.

  (E) In the fourth embodiment, the height of the partition wall is increased from the center of the side branch toward the upstream / downstream direction of the fluid flow. However, the change in the height of the partition wall is not limited to this. It may be lowered from the center of the side branch toward the upstream / downstream direction of the fluid flow, or may be lowered from the center of the side branch toward the inner surface of the side branch and then increased.

  (F) In the above embodiment, the upper end shape of the partition wall is an arc shape along the shape of the pipe wall of the intake pipe. However, the shape of the partition wall is not limited to this. For example, the partition wall may be a substantially rectangular flat plate.

  (G) In the above embodiment, the side branch has a substantially cylindrical shape with a bottom. However, the shape of the side branch is not limited to this.

  (H) In the above embodiment, the radial cross-sectional shape of the intake pipe is substantially tubular. However, the radial cross-sectional shape of the intake pipe is not limited to this.

  As mentioned above, although the embodiment which applied the silencer of the present invention to the intake pipe of a turbo loading car was described, the present invention is not limited to such an embodiment, and it is various forms in the range which does not deviate from the gist. Can be implemented.

10: Intake device,
13 ... 1st intake pipe (intake pipe),
131 ・ ・ ・ first intake passage (intake passage),
15 ・ ・ ・ Second intake pipe (intake pipe),
151... Second intake passage (intake passage),
17 ... third intake pipe (intake pipe),
171... Third intake passage (intake passage),
30, 40, 50, 60, 70, 80, 90, 100 ... side branch,
31, 51, 61, 71 ... internal space,
311, 312, 313, 314, 315, 316, 511, 512, 513, 514, 515, 516, 611, 612, 613, 614, 615, 616, 711, 712, 713, 714, 715, 716 ... Communication space,
33, 43, 53, 63, 73 ... bottom wall,
331, 431, 531, 631, 731 ... inner bottom surface,
361, 362, 363, 364, 365, 366, 461, 462, 463, 464, 465, 466, 561, 562, 563, 564, 565, 566, 661, 662, 663, 664, 665, 666, 761, 762, 763, 764, 765, 766 ... partition walls (wall bodies),
_{L, L 31, L 32,} L 33, L 34, L 35, L 36, L 37, L 51, L 52, L 53, L 54, L 55, L 56, L 57 ··· distance (interval) ,
_{H, H 31, H 32,} H 33, H 34, H 35, H 36, H 61, H 62, H 63, H 64, H 65, H 66, H 71, H 72, H 73, H 74, H ₇₅ , H ₇₆ ... height,
Z: central axis.

Claims (8)

An intake pipe that forms an intake passage through which intake air drawn into the combustion chamber of the internal combustion engine flows;
A side branch provided on a wall surface of the intake pipe, protruding in a radially outward direction of the intake pipe, and having an internal space communicating with the intake passage;
One or more walls that rise from the inner bottom surface of the side branch in the radial direction of the intake pipe and partition the internal space into a plurality of communication spaces that communicate with the intake passage;
A silencing device comprising:   The wall body is installed so as to include a section in which the distance between one wall body and another wall body adjacent to the one wall body or the side wall of the side branch is equal. The muffler according to claim 1.   The wall body is installed so as to include a section in which the distance between one wall body and another wall body adjacent to the one wall body or the side wall of the side branch is unequal. The muffler according to claim 1 or 2.   The silencer according to any one of claims 1 to 3, wherein the wall body is installed so as to be substantially orthogonal to a central axis of the intake pipe.   The silencer according to any one of claims 1 to 3, wherein the wall body is installed substantially parallel to a central axis of the intake pipe.   The height of the wall body from the inner bottom surface decreases from the upstream of the intake passage toward the center of the inner bottom surface, and increases from the center of the inner bottom surface toward the downstream of the intake passage. The muffler according to any one of claims 1 to 5.   The silencing device according to any one of claims 1 to 6, wherein a height of the wall body from the inner bottom surface is lower than a height from the inner bottom surface to the wall surface of the intake pipe.   The silencer according to any one of claims 1 to 7, wherein the side branch is provided in an intake pipe that connects the turbocharger and the intercooler.

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