DE102015221249A1 - Intake air duct for an internal combustion engine - Google Patents

Abstract

The invention relates to an intake air guide for an internal combustion engine for air conduction and sound attenuation, with a channel (14) through which a sucked air stream (12) is passed, wherein the channel (14) has at least one channel outer wall (16) having a channel interior (18 ), wherein the channel (14) in at least three channel segments (20) is divided, wherein the channel segments (20) in a damping position (22) for the air flow (12) are connected in series and wherein the channel segments (20) in a power position (24) for the air flow (12) are connected in parallel, with at least two flaps (26), each of which at least two of the channel segments (20) can open and close one side. In order to reduce the space requirement, it is proposed that the channel segments (20) are arranged adjacent to one another in the circumferential direction.

Description

The invention relates to an intake air duct for an internal combustion engine for air ducting and soundproofing with a channel through which a sucked air flow is passed, wherein the channel has at least one channel outer wall which radially delimits a channel interior, wherein the channel is divided into at least three channel segments, wherein the Channel segments are connected in series in an attenuation position for the air flow and wherein the channel segments are connected in parallel in a power position for the air flow, with at least two flaps, which open and close at least two of the channel segments one side. Furthermore, the invention relates to an internal combustion engine with such an intake air guide.

On the one hand, such intake air ducts have the task of sucking in fresh air from outside the engine compartment and supplying it to the internal combustion engine. To accomplish this as efficiently and with low pressure drop, it is advantageous to form large flow cross sections in the intake ducts. Low pressure loss is particularly necessary to reduce fuel consumption and thus CO ₂ emissions. On the other hand, intake air ducts must best dampen the sound produced in the engine. In order to reduce the muzzle sound effectively, small flow cross sections are particularly advantageous. Thus, these two tasks are in conflict with each other. Therefore, intake air ducts are known, which can switch between a damping position and a power position depending on the requirements of the internal combustion engine.

For example, is from the JP 61255216 A a generic Ansaugluftführung known. In this, the channel segments are arranged side by side and thus require a relatively large amount of space.

Modern motor vehicles are equipped with many different units, so that the space within the engine compartment must be used as best as possible.

The invention has for its object to provide an improved or at least other embodiment of an intake air duct or an internal combustion engine, which is characterized in particular by a smaller footprint and improved sound attenuation.

This object is achieved by the subjects of the independent claims. Advantageous developments are the subject of the dependent claims.

The invention is based on the general idea to arrange the channel segments in the circumferential direction adjacent to each other. This means that the channel segments are distributed in the circumferential direction and each adjacent to two adjacent channel segments. As a result, the available space can be optimally utilized. For example, the channel segments may be arranged circumferentially around a channel longitudinal axis. This would be a simple structural arrangement of the individual channel segments. Viewed in cross section of the channel so are the focal points of the cross sections of the individual channel segments such that they span a surface. In addition, the expansion in a single lateral direction is reduced since the channel segments need not be juxtaposed.

In the specification and the appended claims, the terms "radial", "axial" and "circumferentially" refer to a longitudinal central axis of the channel.

A favorable solution provides that the air flow is deflected in the damping position at the flaps at least twice. The deflection takes place approximately 180 °. Due to the double deflection, on the one hand, the path that the air flow has to take in the channel is lengthened, whereby a damping effect is achieved. On the other hand, an additional damping effect is achieved solely by deflecting the flaps.

In order to improve the damping effect in the deflection at the flaps, it is advantageous if a structured surface is formed on the inner sides of the flaps, which in particular breaks the sound transported by the air flow. Consequently, the sound attenuation can be further improved.

Another favorable possibility provides that the channel segments are formed by a separating element which is arranged in the channel and which has at least three partitions which extend from a base of the separating element in the channel to the channel outer wall. That is, the partitions do not extend from the channel outer wall to the channel outer wall. A diagonal wall would correspond to two partitions. As a result of the formation of at least three partitions, at least three channel segments can be formed, which are arranged adjacent one another in the circumferential direction. The at least three partitions and thus at least three channel segments allow both in the damping position and in the power position, an inlet side and an outlet side of the channel are arranged at longitudinally opposite ends. It is not necessary that when switching between the damping position and the power position outside the channel flow paths must be switched.

It is understood that the base of the separating element, from which the partitions extend outwardly to the channel outer wall, may be formed in different ways. In the simplest case, the base is the intersection of partitions. Furthermore, the base may run on or near the longitudinal central axis of the channel. Alternatively or additionally, the base may also be hollow, in particular tubular, or formed as a wall. In such a case, the partitions do not extend from the same line, for example, the channel longitudinal axis, but each of lines, which are different from the channel longitudinal axis, outwardly to the channel outer wall.

A particularly favorable possibility provides that the partitions sealingly bear against the channel outer wall and / or are connected to the channel outer wall. This allows the partitions together with the channel outer wall to form the channel segments.

A particularly favorable possibility provides that each dividing wall runs between two channel segments. As a result, each partition actually separates two channel segments from each other. Consequently, the partitions can be optimally utilized.

An advantageous solution provides that the partitions extend radially outward from a channel longitudinal axis. Such a configuration causes the partitions in the radial direction have the same length. Thus, a simple way is given to provide each channel segment a same flow cross-section available.

A further advantageous solution provides that the separating element is integrally formed. For example, the separating element may be made of plastic, in particular by a plastic injection molding process. As a result, a very simple production of the separating element is given. Further, by integrally forming the partition member, the assembly of the intake air duct is facilitated since the number of parts is reduced.

A particularly advantageous solution provides that at least two of the partitions each have an end flow opening between two adjacent channel segments, which is flowed through in the damping position of the air flow and preferably is not flowed through in the power position. The end flow openings thus form the connection between two channel segments, which allow the series connection of the channel segments for the air flow. In the power position, the flow openings must not be flowed through, since the channel segments are flowed through in parallel in the power position of the air flow. Preferably, at least one end-side flow opening is provided on both longitudinally spaced end regions. Thus, in each end region, there is a flow connection between two channel segments, so that in the damping position the air flow must at least once reverse the flow direction and thus have to flow back to an inflow end of the channel. In this way, the flow path through the channel in the damping position is tripled.

A favorable variant provides that the channel has more than three channel segments, and that at least one of the channel segments in the damping position is not flowed through by the air flow. Three channel segments are needed for the series connection of the channel segments. The additional channel segment must therefore not be flowed through in the damping position. However, the additional channel segment can be flowed through in the power position by the air flow and thereby cause an even larger flow cross-section in the power position, so that the pressure difference in the power position can be further reduced.

A particularly favorable variant provides that the at least one channel segment, which is not flowed through by the air flow in the damping position, is connected via a connection opening to a channel segment through which the air flow flows in the damping position. As a result, the at least one channel segment, which is not flowed through by the air flow in the damping position, can act as a resonance tube, in particular as a λ / 4 resonator. As a result, an additional sound attenuation can be achieved by the at least one channel segment through which the air flow does not flow in the damping position. Thus, the flow resistance of the channel in the power position can be reduced as well as the sound damping effect can be improved in the damping position by the formation of a non-flowed through the air flow channel segment in the damping position.

Another particularly favorable variant provides that the flaps are each rotatably mounted in the channel about an axis of rotation, and that the axes of rotation of the flaps extend substantially parallel to one another in a plane extending substantially parallel to a channel longitudinal axis. As a result, the flaps can be driven in a particularly favorable synchronous manner by a common actuator.

In the specification and the appended claims, "substantially parallel" means at an angle to each other which is less than 5 °, preferably less than 2 °, and more preferably less than 1 °.

Another favorable variant provides that the flaps each have a recess which corresponds in each case to the cross section of one of the channel segments.

As a result, one channel segment can always remain open on each side of the channel, so that an inflow and outflow of the air flow into the channel segments is made possible both in the power position and in the damping position.

An advantageous possibility provides that an inlet-side flap has an inlet recess. Through the inlet recess, the air flow can flow into the corresponding channel segment and thus into the channel.

A further advantageous possibility provides that an outlet-side flap has an outlet recess. Through the Auslassaussparung the air flow from the respective channel segment and thus flow out of the channel.

A particularly advantageous possibility provides that the flaps are driven synchronously by a common actuator. Thus, it can be avoided that the flaps move independently and thus assume an undefined and possibly ineffective intermediate position.

Another particularly advantageous possibility provides that the actuator has a control rod which is coupled to the flaps and adjusts the flaps synchronously. The fact that the flaps are controlled by a common control rod, the actuator can be very easily formed. As a result, costs and space can be saved.

A favorable solution provides that the flaps extend in the damping position transverse to a channel longitudinal axis. Because the flaps are transverse to the channel longitudinal axis, the flaps block a majority of the air flow flow area. Thus, the flaps can force the air flow through the channel segments such that the air flow flows through at least three of the channel segments in series.

In the specification and the appended claims, "transverse" means an angle of 90 ° with a deviation of 5 °, preferably with a deviation of 2 °, more preferably with a deviation of 1 ° ".

Another favorable solution provides that the flaps in the damping position at least partially rest against the separating elements. Due to the fact that the flaps lie at least partially against the separating element in the damping position, the flaps can rest sealingly against the individual dividing walls. Thus, the flaps can close the channel segments airtight.

A particularly favorable solution provides that the flaps in the damping position each cover at least two channel segments on one side, axially. Thus, the air flow can not flow axially into or out of the covered channel segments. This allows the flaps to force the air flow to flow through the channel segments in series.

Another particularly favorable solution provides that the flaps in a power position each form an extension of at least one of the partitions. As a result, turbulence on the partitions can be avoided. Furthermore, the flaps are thus arranged particularly favorable in terms of flow, since they are at least partially at least partially in the lee of the respective partition or partition in question at least partially in the lee of the flap.

An advantageous variant provides that the at least one partition, which is extended in the power position, has an end connection opening or flow opening between two adjacent channel segments, which is open in the damping position and is preferably closed in the power position by the flap. Thus, turbulence at the connection opening or flow opening in the power position can be avoided. In the damping position, either the air flow can flow through the flow opening or be formed through the connection opening a connection to a non-flow channel segment, whereby the damping is improved in the damping position.

A further advantageous variant provides that the partition, which is extended in the power position, extends substantially parallel to the axis of rotation of the respective flap. As a result, the flap can extend the respective partition particularly favorable.

A further particularly advantageous variant provides that at least one of the channel segments is subdivided into at least two subsegments, which are parallel both in the power position and in the damping position for the air flow connected to each other. So it does not matter in how many subsegments the individual channel segments are subdivided. As long as the subchannel segments are switched together either between a parallel flow and a serial flow with the other channel segments or between a parallel flow with the other channel segments and a closed position, the subchannel segments are to be regarded as a channel segment.

Further, the invention is based on the general idea of equipping an internal combustion engine with such an intake air guide, wherein combustion air is passed through the intake air to combustion chambers of the internal combustion engine, and wherein a control device is provided, which depends on a load request of the internal combustion engine, the intake air between a damping position and a Performance adjusted. Thus, the advantages of the intake air guide can be optimally transferred to the internal combustion engine, to the above description of which reference is made.

It is favorable that the internal combustion engine has a charging device, wherein the intake air guide is arranged upstream of the charging device. As a result, on the one hand, the intake air guide can also dampen the noises generated by the charging device. On the other hand, the intake air duct does not have to withstand the boost pressure of the charging device.

Other important features and advantages of the invention will become apparent from the dependent claims, from the drawings and from the associated figure description with reference to the drawings.

It is understood that the features mentioned above and those yet to be explained below can be used not only in the particular combination given, but also in other combinations or in isolation, without departing from the scope of the present invention.

Preferred embodiments of the invention are illustrated in the drawings and will be described in more detail in the following description, wherein like reference numerals refer to the same or similar or functionally identical components.

It show, each schematically

1 a perspective view of an intake air guide, wherein the intake air guide is in a damping position and a channel outer wall is hidden,

2 a view in the axial direction of a flap of the suction device, which is in the damping position,

3 a perspective view of the suction device 1 wherein the intake air duct is in a power position,

4 a view in the axial direction of a flap, which is in the power position,

5 a perspective view of the intake air duct 1 in an attenuation position, wherein an air flow is indicated by arrows,

6 a perspective view of the intake air duct 1 from another angle, so that other channel segments are recognizable,

7 a perspective view of an intake air duct according to a second embodiment, wherein a channel outer wall is hidden and the intake air duct is in a damping position,

8th a view along an axial direction of an inlet-side flap of the intake air guide according to 7 .

9 a perspective view of the intake air duct 7 , wherein the intake air guide is in a power position, and

10 a view in the axial direction of the inlet-side flap 9 ,

One in the 1 to 6 illustrated first embodiment of the intake air duct 10 is used for air guidance and noise reduction in an internal combustion engine. The intake air duct 10 guides an airflow 12 to the internal combustion engine, so that the air flow 12 Combustion chambers of the internal combustion engine can be supplied. The intake air duct 10 has a channel 14 on, with a canal exterior wall 16 which has a channel interior 18 of the canal 14 limited. The channel interior 18 of the canal 14 is in at least three channel segments 20 , for example, four channel segments 20 , divided. The channel segments 20 are in a damping position 22 for the airflow 12 connected in series and in a power position 24 for the airflow 12 connected in parallel. To between the damping position 22 and the achievement status 24 to switch, has the intake air 10 two flaps 26 on. An inlet-side flap 28 is in an inlet-side end region 30 of the canal 14 arranged. An outlet-side flap 32 is in an outlet end area 34 of the canal 14 arranged.

The channel 14 points along a channel longitudinal axis 36 a substantially constant cross section 38 on. In the description and the appended claims, the terms "axial", "radial" and "circumferential direction" refer to this channel longitudinal axis 36 ,

The cross section 38 of the canal 14 is through the channel outer wall 16 certainly. For example, encloses the channel outer wall 16 a square section with rounded corners. Other cross-sectional shapes that are oval, angular or circular are also conceivable. The canal exterior wall 16 thus limits the channel interior 18 radial.

In the channel interior 18 of the canal 14 is a separator 40 arranged, which at least three, for example four, partitions 42 having. The partitions 42 each extend from a base 44 of the separating element 40 to the canal exterior wall 16 , Preferably, the partitions extend 42 from the base 44 out radially to the outside. Deviations from the radial direction are possible. For example, the partitions 42 bent. Furthermore, the base 44 next to the channel longitudinal axis 36 lie so that the partitions 42 extend obliquely to the radial direction.

Preferably, the partitions lie 42 sealing on the canal outer wall 16 at. The partitions 42 can be connected to the channel outer wall. For example, by form or material bond.

In the axial direction, the partitions extend 42 continuous between the two flaps 26 , At least two of the partitions 42 have end recesses 46 on.

Through the partitions 42 is the channel interior 18 of the canal 14 into the channel segments 20 divided. The end-side recesses 46 in the partitions 42 form either flow openings 48 , which in the damping position 22 from the airflow 12 are flowed through and in the power position 24 are not flowed through. It is understood that even in the performance position 24 a part of the airflow 12 through the flow openings 48 can flow. However, the main flow direction of the air flow runs 12 in the power position at the flow openings 48 over and not through them. By the flow past the flow openings 48 However, due to turbulence currents can flow through the flow openings 48 occur.

Furthermore, at least one of the end-side recess 46 a connection opening 50 between two channel segments 20 form, which both in the performance position 24 as well as in the damping position 22 not from the airflow 12 be flowed through. Small, especially oscillating, partial flows of the air flow 12 can still through the connection opening 50 stream.

The flow openings 48 connect two adjacent channel segments 20 together. Preferably, both in the inlet-side end region 30 as well as in the outlet end region 34 in each case at least one flow opening 48 intended. The at least one connection opening 50 may be in both the inlet-side end region and the outlet-side end region 34 be provided.

The base 44 of the separating element 40 from which the partitions 42 out to the outside of the canal 16 extend, may be formed in different ways. In the simplest case is the base 44 the intersection of partitions 42 , Alternatively or additionally, the basis 44 also hollow, in particular tubular, or be formed as a wall. In such a case, the partitions extend 42 not from the same line, such as the channel longitudinal axis 36 but each of lines, which of the channel longitudinal axis 36 are different, outward to the canal outer wall 16 ,

The separating element is preferably formed from plastic. Particularly preferably, the separating element is integrally formed, for example by a plastic injection molding process.

The channel segments 20 are through the partitions 42 separated from each other and thereby arranged adjacent to each other. Furthermore, the channel segments lie 20 in the circumferential direction adjacent to each other. This allows the channel interior 18 of the canal 14 optimal with channel segments 20 fill out.

Through the end-side recesses 46 in the partitions 42 can the channel segments 20 with an adjacent channel segment 20 be connected. It is understood that the channel segments 20 to two adjacent channel segments 20 each may have at least one connection, but it is also possible that a channel segment 20 to no adjacent channel segment 20 has a connection.

The connection between the channel segments 20 can either through a flow opening 48 done by an end recess 46 in one of the partitions 42 is formed. These flow openings 48 serve to the channel segments 20 in the damping position to connect such that the air flow 12 several of the channel segments 20 must flow through one behind the other. Furthermore, at least one channel segment 20 a connection opening 50 to an adjacent channel segment 20 exhibit. The connection opening 50 does not serve to guide the flow of air 12 but for the acoustic coupling of the two channel segments 20 to achieve improved soundproofing.

To achieve the series connection for the air flow, has a first channel segment 52 the channel segments 20 in the outlet end area 34 a flow opening 48 to a second channel segment 54 on, adjacent to the first channel segment 52 is arranged. Accordingly, the second channel segment in the outlet-side end region 34 same flow opening 48 to the first channel segment 52 on. In the inlet end area 30 has the second channel segment 54 another flow opening 48 on that the second channel segment 54 with a third channel segment 56 which is adjacent to the second channel segment 54 is arranged. This indicates the third channel segment 56 corresponding to the inlet-side end region 30 a flow opening 48 to the second channel segment 54 on.

This allows the airflow 12 , the inlet side in the first channel segment 52 flows in, at the outlet end portion 34 of the canal 14 in the second channel segment 54 stream. There is the air flow 12 on the outlet side flap 32 deflected and flows along the second channel segment 54 back to the inlet end area 30 where the airflow 12 on the inlet side flap 28 is deflected and through the further flow opening 48 in the third channel segment 56 can flow in. In the third channel segment 56 Finally, the air flow 12 again in the direction of the outlet end area 34 stream and out of the canal 14 flow out.

Consequently, the flow openings allow 48 a series connection of the first channel segment 52 , the second channel segment 54 and the third channel segment 56 for the airflow 12 ,

A fourth channel segment 58 which is between the first channel segment 52 and the third channel segment 56 is arranged, has a connection opening 50 to the third channel segment 56 on.

The flaps 26 have a cross section that is the cross section 38 of the canal 14 equivalent. Thus, the flaps 26 the channel 14 close. However, the flaps point 26 one recess each 60 on which a cross section 62 one of the channel segments 20 equivalent. As a result, one channel segment remains on the inlet side and on the outlet side 20 open.

In the inlet-side flap 28 forms the recess 60 an inlet-side recess 61 that the cross section 62 of the first channel segment 52 equivalent. In the outlet side flap 32 forms the recess 60 an outlet-side recess 63 that the cross section 62 of the third channel segment 56 equivalent.

In the damping position 22 are the flaps 26 arranged such that the channel segments 20 closed at the end. However, each inlet side and outlet side through the recesses 60 one of the channel segments 20 open. In the performance position 24 are the flaps 26 arranged such that all channel segments are open.

At the inlet-side flap 28 lies the inlet-side recess 61 such that the first channel segment 52 not through the inlet-side flap 28 is closed. At the outlet side flap 32 is the outlet-side recess 63 in alignment with the third channel segment 56 so that the third channel segment 56 not closed on the outlet side.

Thus, in the damping position 22 inlet side, the first channel segment 52 open and the remaining channel segments 20 closed and outlet side is the third channel segment 56 open and the remaining channel segments 20 locked. This allows the airflow 12 inlet side in the first channel segment 52 inflow, the outlet side in the second channel segment 54 overflow, in the second channel segment 54 back to the inlet side and there into the third channel segment 56 overflow. From the third channel segment 56 out can the airflow 12 outlet side again from the channel 14 escape. As a result, the air flow flows 12 zigzagged and must complete a long flow path, which causes a good sound attenuation.

In the damping position 22 are three of the four channel segments 20 closed at the end. Through three of the channel segments 20 runs a flow path of the air flow 12 zigzag. The fourth channel segment 58 is not from the airflow 12 flows through. However, it is in fluid communication with the third channel segment 56 , This affects the fourth channel segment 58 as a resonator, in particular as a λ / 4 resonator and can thereby cause a reduction of the sound.

Alternatively or additionally, a plurality of non-flow channel segments 20 be provided so that several tuned to different frequencies λ / 4 resonator can be formed.

The flaps 26 are each about a rotation axis 65 rotatably mounted to the flaps 26 between the damping position 22 and the achievement status 24 to be able to pivot. Preferably, the axes of rotation run 65 the flaps 26 substantially parallel to each other and in a plane substantially parallel to the channel longitudinal axis 36 runs. This allows the flaps 26 through a common actuator 67 be adjusted synchronously.

Substantially parallel in the specification and the appended claims includes a departure from the parallels of less than 5 °, preferably less than 2 °, and more preferably less than 1 °.

The axes of rotation 65 and with it the flaps 26 are in the axial direction flush with the axially located ends of the separating element 40 arranged. This leaves the flaps 26 at front ends 68 the partitions, when the flaps 26 across the channel 14 lie. Thus, the channel segments 20 through the flaps 26 be closed. When the flaps 26 longitudinally in the channel 14 lie, are the channel segments 20 open. To the rotation of the flaps 26 in the performance position 24 to enable, is the recess 60 the respective flap 26 formed such that one of the partitions 42 in the recess 60 can engage, allowing the rotation of the flaps 26 not through the partition 42 is blocked.

On one side of the rotary axes 65 swing the flaps 26 in the axial direction away from the separator 40 , On the other side of the rotary axes 65 swing the flaps 26 in the direction of the separating element 40 , On this page need the recesses 60 be provided so that the flaps 26 into the corresponding channel segment 20 can swing in.

It can be provided the flaps 26 when swinging at least partially in the end-side recess 46 one of the partitions 42 engages, and thus the flow opening 48 or the connection opening 50 closes. Thus, the flap forms 26 an extension of the relevant partition 42 ,

The flaps 26 are preferably made of plastic, more preferably by means of a plastic injection molding process.

Alternatively or additionally, it can be provided that one of the channel segments 20 is subdivided into further subchannel segments, which together with the respective channel segment 20 between the achievement position 24 and the damping position 22 be switched. This is indicated for example by a dashed partition shown in FIG 4 shown. Subchannel segments thus formed become together as a single channel segment 20 considered in the context of the invention

The actuator 67 has a control rod 70 on which over lever 72 the flaps 26 drives. By doing that the flaps 26 via a common control rod 70 are driven, the flaps move synchronously. Furthermore, in this way a very space-saving actuator 67 be formed.

One in the 7 to 10 illustrated second embodiment of the intake air duct 10 is different from the one in the 1 to 6 shown first embodiment of the intake air 10 in that the channel 14 exactly three channel segments 20 having. The channel 14 thus has no non-flow channel segment 20 on. Further, the channel shows 14 in the example a circular or circular cross-section 38 , Again, there are other cross sections 38 conceivable, eg oval or rectangular.

Incidentally, the right in the 7 to 10 illustrated second embodiment of the intake air duct 10 in terms of structure and function with in the 1 to 6 shown first embodiment of the intake air 10 to the above description of which reference is made.

QUOTES INCLUDE IN THE DESCRIPTION

This list of the documents listed by the applicant has been generated automatically and is included solely for the better information of the reader. The list is not part of the German patent or utility model application. The DPMA assumes no liability for any errors or omissions.

Cited patent literature

• JP 61255216 A [0003]

Claims (15)

Intake air duct for an internal combustion engine for air ducting and soundproofing, - with one duct ( 14 ), through which a sucked air flow ( 12 ), the channel ( 14 ) at least one channel outer wall ( 16 ) having a channel interior ( 18 ) radially limited, - wherein the channel ( 14 ) in at least three channel segments ( 20 ), the channel segments ( 20 ) in a damping position ( 22 ) for the air flow ( 12 ) are connected in series and - wherein the channel segments ( 20 ) in a capacity ( 24 ) for the air flow ( 12 ) are connected in parallel, - with at least two flaps ( 26 ), each of at least two of the channel segments ( 20 ) can open and close on one side, characterized in that the channel segments ( 20 ) are arranged adjacent to each other in a circumferential direction. Intake air duct according to claim 1, characterized in that the duct segments ( 20 ) by a separating element ( 40 ) formed in the channel ( 14 ) is arranged and the at least three partitions ( 42 ) extending from a base ( 44 ) of the separating element ( 40 ) starting in the channel ( 14 ) to the channel outer wall ( 16 ). Intake air duct according to claim 2, characterized in that at least two of the partitions ( 42 ) each have an end-side flow opening ( 48 ) between two adjacent channel segments ( 20 ), which in the damping position ( 22 ) from the airflow ( 12 ) is flowed through and preferably in the power position ( 24 ) is not flowed through. Intake air duct according to one of claims 1 to 3, characterized in that the duct ( 14 ) more than three channel segments ( 20 ), and that at least one of the channel segments ( 20 . 58 ) in the damping position ( 22 ) not from the airflow ( 12 ) is flowed through. Intake air duct according to claim 4, characterized in that the at least one in the damping position ( 22 ) not from the airflow ( 12 ) channel segment ( 20 . 58 ) via a connection opening ( 50 ) to a in the damping position ( 22 ) from the airflow ( 12 ) channel segment ( 20 . 56 ) connected. Intake air duct according to one of claims 1 to 5, characterized in that - the flaps ( 26 ) each about a rotation axis ( 65 ) in the channel ( 14 ) are rotatably mounted, and - that the axes of rotation ( 65 ) of the flaps ( 26 ) substantially parallel to each other and in a substantially parallel to a channel longitudinal axis ( 36 ) extending level. Intake air duct according to one of claims 1 to 6, characterized in that the flaps ( 26 ) each have a recess ( 60 ) each having the cross-section ( 62 ) one of the channel segments ( 20 ) corresponds. Intake air duct according to one of claims 1 to 7, characterized in that the flaps ( 26 ) by a common actuator ( 67 ) are driven synchronously. Intake air duct according to claim 8, characterized in that the actuator ( 67 ) a control rod ( 70 ), which with the flaps ( 26 ) and the flaps ( 26 ) adjusted synchronously. Intake air duct according to one of claims 1 to 9, characterized in that the flaps ( 26 ) in the damping position ( 22 ) transversely to a channel longitudinal axis ( 36 ). Intake air duct according to one of claims 1 to 10, characterized in that - the flaps ( 26 ) in the damping position ( 22 ) at least partially on the separating element ( 40 ) and / or - that the flaps ( 26 ) in the damping position ( 22 ) at least two channel segments ( 20 ) on one side, axially cover. Intake air duct according to one of claims 1 to 11, characterized in that the flaps ( 26 ) in a capacity ( 24 ) each an extension of at least one of the partitions ( 42 ) form. Intake air duct according to claim 12, characterized in that the at least one partition wall ( 42 ), which are in the position of 24 ), an end connection opening ( 50 ) or flow opening ( 48 ) between two adjacent channel segments ( 20 ), which in the damping position ( 22 ) is open and preferably in the performance position ( 24 ) through the flap ( 26 ) closed is. Intake air duct according to one of claims 1 to 13, characterized in that at least one of the channel segments ( 20 ) is subdivided into at least two subchannel segments that are both in the power position ( 24 ) as well as in the Damping position ( 22 ) are connected in parallel to each other for the air flow. Internal combustion engine with an intake air guide according to one of claims 1 to 14, wherein combustion air through the intake air guide ( 10 ) is guided to combustion chambers of the internal combustion engine, and wherein a control device is provided, which depends on a load request of the internal combustion engine, the intake air ( 10 ) between the damping position ( 22 ) and the benefit status ( 24 ) adjusted.

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