EP3303793B1 - Abgassammler - Google Patents

Abgassammler Download PDF

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Publication number
EP3303793B1
EP3303793B1 EP16730039.1A EP16730039A EP3303793B1 EP 3303793 B1 EP3303793 B1 EP 3303793B1 EP 16730039 A EP16730039 A EP 16730039A EP 3303793 B1 EP3303793 B1 EP 3303793B1
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EP
European Patent Office
Prior art keywords
main passage
passage
cross sectional
inlet
sectional area
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EP16730039.1A
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English (en)
French (fr)
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EP3303793A1 (de
Inventor
Kim Petersson
Dennis KONSTANZER
Thomas Svensson
Jenny ANDERSSON
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Scania CV AB
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Scania CV AB
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Publication of EP3303793A1 publication Critical patent/EP3303793A1/de
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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01N—GAS-FLOW SILENCERS OR EXHAUST APPARATUS FOR MACHINES OR ENGINES IN GENERAL; GAS-FLOW SILENCERS OR EXHAUST APPARATUS FOR INTERNAL COMBUSTION ENGINES
    • F01N13/00—Exhaust or silencing apparatus characterised by constructional features ; Exhaust or silencing apparatus, or parts thereof, having pertinent characteristics not provided for in, or of interest apart from, groups F01N1/00 - F01N5/00, F01N9/00, F01N11/00
    • F01N13/08—Other arrangements or adaptations of exhaust conduits
    • F01N13/10—Other arrangements or adaptations of exhaust conduits of exhaust manifolds
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01N—GAS-FLOW SILENCERS OR EXHAUST APPARATUS FOR MACHINES OR ENGINES IN GENERAL; GAS-FLOW SILENCERS OR EXHAUST APPARATUS FOR INTERNAL COMBUSTION ENGINES
    • F01N2260/00—Exhaust treating devices having provisions not otherwise provided for
    • F01N2260/06—Exhaust treating devices having provisions not otherwise provided for for improving exhaust evacuation or circulation, or reducing back-pressure
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01N—GAS-FLOW SILENCERS OR EXHAUST APPARATUS FOR MACHINES OR ENGINES IN GENERAL; GAS-FLOW SILENCERS OR EXHAUST APPARATUS FOR INTERNAL COMBUSTION ENGINES
    • F01N2340/00—Dimensional characteristics of the exhaust system, e.g. length, diameter or volume of the apparatus; Spatial arrangements of exhaust apparatuses
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01N—GAS-FLOW SILENCERS OR EXHAUST APPARATUS FOR MACHINES OR ENGINES IN GENERAL; GAS-FLOW SILENCERS OR EXHAUST APPARATUS FOR INTERNAL COMBUSTION ENGINES
    • F01N2470/00—Structure or shape of gas passages, pipes or tubes
    • F01N2470/10—Tubes having non-circular cross section

Definitions

  • the present invention relates to an exhaust manifold for a four-stroke internal combustion engine.
  • An exhaust manifold of an internal combustion engine conducts exhaust gas from usually two or more cylinders towards a common exhaust conduit for the two or more cylinders.
  • the common conduit leads to further parts of an exhaust system, such as e.g. a turbocharger, an exhaust gas cleaning system, and/or a silencer. Since the exhaust manifold is connected to more than one cylinder of the combustion engine, it has to be ensured that the flows of exhaust gas from the respective cylinders are directed towards an outlet end of the exhaust manifold.
  • WO 97/04222 discloses a collector for the primary pipes of an exhaust manifold of an internal combustion engine.
  • the collector comprises a plurality of primary pipes, each leading from a cylinder of the combustion engine.
  • An outlet end of each of the primary pipes has a cross-sectional area which is less than the main cross-sectional area of the primary pipe.
  • Each outlet end of reduced cross-sectional area is in direct communication with a common cavity of the collector, at one end of the cavity.
  • the reduction in area is sufficient to provide a pulse conversion effect so that the pressure waves of one cylinder do not negatively affect the gas flows of other cylinders.
  • the area reduction is in the order of 5-10%.
  • US 5860278 discloses an exhaust manifold with several inlet ports and a combination of diffuser and nozzle portions associated with each inlet port for producing a high flow rate and a low pressure drop from entry to exit.
  • the diffuser and nozzle portions are arranged in series and designed into the manifold at each inlet port and slightly upstream of the next downstream positioned inlet port.
  • the diffuser portion decreases the velocity of exhaust gases as they enter the manifold and are then turned substantially ninety degrees into a longitudinal direction of the manifold. This diffuser action slows the velocity and reduces pressure losses as the turn of exhaust flow is accomplished.
  • the next in series nozzle portion increases the velocity of exhaust gases to cause the exhaust flow to accelerate past a neighboring downstream engine exhaust port.
  • US 2006/236687 discloses an exhaust manifold with deflector members positioned between downstream gas inlets from cylinders of an internal combustion engine and a main gas passage.
  • the deflector members redirect the flow of exhaust gas from the inlets into the general direction of the gas flowing in the main passage at an angle of less than 90 degrees as the exhaust gas enters the main passage.
  • the formed cross section area is no less than that of the inlet passage.
  • At the deflector member in the main passage at least the same cross section area as an upstream inlet passage is provided. As the upstream exhaust gas flow passes by the outside surface of the deflector member in the main passage, a low pressure area is created on the inlet passage side of the deflector.
  • DE 842 873 relates to an exhaust gas collector for supercharged internal combustion engines with downstream exhaust gas turbine.
  • JP 2000 104545 relates to an exhaust manifold connected to each cylinder of an engine and guiding exhaust gas from combustion chambers of these cylinders to a supercharger, a muffler or the like.
  • US 2008/302095 relates to an improved exhaust manifold for controlling combustion gases and more particularly to arrangements for reducing pneumatic interaction between cylinders and optimizing exhaust flow in an exhaust manifold.
  • the object is achieved by an exhaust manifold for a four-stroke internal combustion engine, the exhaust manifold forming at least two inlet passages and one main passage having an outlet end arranged downstream of the at least two inlet passages.
  • a first inlet passage of the at least two inlet passages connects to the main passage at a junction.
  • An intersecting wall portion between the first inlet passage and the main passage forms an upstream end portion of the junction.
  • a first portion of the first inlet passage at the intersecting wall portion has a first inlet passage cross sectional area, and the first inlet passage cross sectional area is smaller than a second inlet passage cross sectional area of a second portion of the first inlet passage located upstream of the first portion of the first inlet passage.
  • the first inlet passage is connected to the main passage downstream of a second inlet passage of the at least two inlet passages.
  • the main passage comprises a first main passage portion at the intersecting wall portion, the first main passage portion having a first main passage cross sectional area.
  • the first main passage cross sectional area is smaller than a second main passage cross sectional area of a second main passage portion of the main passage located upstream of the junction.
  • a charge of exhaust gas from a cylinder connected to the first inlet passage is accelerated past the junction by the smaller first inlet passage cross sectional area, compared to the second inlet passage cross sectional area.
  • the first main passage cross sectional area being smaller than the second main passage cross sectional area reduces the flow of exhaust gas in an upstream direction in the main passage towards the second inlet.
  • exhaust gas from the first inlet passage disturbing flow of exhaust gas from the second inlet passage is reduced compared to if the first main passage cross sectional area were not reduced.
  • the accelerated exhaust gas from the first inlet passage when entering the main passage, is further subjected to a comparatively high flow resistance in the upstream direction, promoting flow of exhaust gas from the first inlet passage in a downstream direction in the main passage.
  • the exhaust manifold is configured for conducting exhaust gas from each cylinder connected to the at least two inlet passages into the main passage.
  • the main passage forms a common exhaust conduit for the cylinders connected to the at least two inlet passages.
  • the main passage leads to further parts of an exhaust system.
  • the outlet end of the main passage may be connected to e.g. a turbocharger, and/or an exhaust gas cleaning system, and/or a silencer.
  • a main passage axis may extend centrally through the second main passage portion in a straight line past the junction and centrally through a third main passage portion of the main passage located downstream of the first main passage portion.
  • a centre axis of the first inlet passage at the first portion of the first inlet passage may extend at an acute angle to an upstream direction of the main passage axis. In this manner the exhaust gas emanating from a cylinder connected to the first inlet passage may be directed in a downstream direction in the main passage, towards the outlet end of the main passage.
  • the acceleration of the exhaust gas caused by the reduced first inlet passage portion cross sectional area may be utilised to ensure that the exhaust gas may reliably pass the junction in the downstream direction,
  • the centre axis of the first inlet passage, at the first portion of the first inlet passage may extend at an angle within a range of 30 - 45 degrees to the upstream direction of the main passage axis. In this manner it may be ensured that the exhaust gas from the cylinder connected to the first inlet passage is safely directed in the downstream direction in the main passage. Moreover, at an angle within such a range, the acceleration of the exhaust gas caused by the reduced first inlet passage portion cross sectional area may be utilised to ensure that the exhaust gas may reliably pass the junction in the downstream direction, which may reduce the amount of exhaust gases flowing in an upstream direction past the junction towards the second inlet passage.
  • the intersecting wall portion may form at least part of a deflector arranged between the first inlet passage and the main passage.
  • the deflector may extend towards the main passage axis. In this manner exhaust gas from the first inlet passage may be directed in a downstream direction in the main passage by the deflector.
  • exhaust gas in the main passage e.g. from the second inlet passage, may be directed away from the junction by the deflector.
  • the deflector may direct exhaust gas from both the first inlet passage and the second inlet passage.
  • the deflector may comprise a first wall portion forming a delimiting surface of the main passage.
  • the first wall portion may extend at an acute angle to the upstream direction of the main passage axis being smaller than the angle of the centre axis of the first portion of the first inlet passage to the upstream direction.
  • exhaust gas in the main passage e.g. from the second inlet passage
  • an angle of the first wall portion smaller than the angle of the centre axis of the first portion of the first inlet passage may be sufficient to reduce a tendency of the exhaust gas from the second inlet passage to flow into the first inlet passage.
  • the main passage comprises a widening section extending at least upstream of the first main passage portion, which widening section widens the main passage in a first direction.
  • the first direction extends in a first cross sectional plane, which first cross sectional plane extends through the first inlet passage, through at least a portion of the main passage, extends along the main passage axis, and includes the main passage axis.
  • the first direction is directed away from the first inlet passage. Since the widening section is arranged at least upstream of the junction in the main passage and widens in a direction away from the first inlet passage, exhaust gas from the first inlet passage flowing upstream in the main passage will flow into the widening section and form a circulating flow of exhaust gas therein.
  • the first fraction of a charge of exhaust gas from the first inlet passage will form a vortex in the widening section, which vortex reduces the effective flow area in the widening section for the remaining portion of the charge of exhaust gas from the first inlet passage.
  • the effective flow area reduced by the vortex prevents further partial amounts of the exhaust gas from the first inlet passage to flow in an upstream direction from the junction.
  • the widening section may form a bulging portion of the main passage, which bulging portion bulges in a direction away from the first inlet passage. Whereas the widening section widens the main passage in the first direction e.g. compared to the second main passage portion, the widening section, along a different cross-sectional direction, may have a smaller dimension than the second main passage portion.
  • an inner surface of the main passage, opposite to the first inlet passage, at a transition between the widening section and the second main passage portion may form an abrupt directional change, such that a vortex may be formed in exhaust gases during use of the exhaust manifold.
  • the abrupt directional change may assist in forming of the vortex in the widening section.
  • the inner surface may be provided with an abrupt directional change at a point of the inner surface, to which a vortex in the widening section extends.
  • the abrupt directional change may be provided opposite to the first inlet passage, seen in the first cross sectional plane.
  • the vortex in the widening section is formed by the first fraction of each charge of exhaust gas from the first inlet passage.
  • the widening section may extend upstream of an end point of the intersecting wall portion over a distance having a length within a range of 1,2 - 1,7 times a hydraulic diameter of the second main passage portion. In this manner a vortex may be formed in the widening section, which vortex reduces flow of exhaust gas upstream of the junction, but which vortex does not affect flow of exhaust gas in a downstream direction from the junction to any particular extent. Seen in the first cross sectional plane, the widening section may extend upstream of the end point of the intersecting wall portion to the abrupt directional change.
  • the widening section may extend downstream of the end point of the intersecting wall portion over a distance having a length within a range of 2 - 3 times a hydraulic diameter of the second main passage portion. In this manner the downstream end of the widening section does not promote flow of exhaust gas from the first inlet passage in the upstream direction in the main passage.
  • charge of exhaust gas refers to the exhaust gas discharged from one combustion cycle of one cylinder. Since fuel combusts in the different cylinders of the combustion engine at different angles of a crankshaft of the engine, charges of exhaust gas flow through different inlet passages of an exhaust manifold at different points in time.
  • downstream relates to the flow direction in an exhaust manifold from a respective cylinder to an outlet end of the exhaust manifold.
  • upstream relates to the opposite flow direction in the exhaust manifold.
  • hydraulic diameter will be used for the purpose of comparing cross sectional sizes and distances of various portions and sections of an exhaust manifold.
  • the hydraulic diameter is a commonly used term when calculating flow related parameters in noncircular passages, such as tubes or channels.
  • parameters of a passage may be calculated in the same manner as for a circular passage.
  • a cross section of a passage portion extends perpendicularly to a centre line of the relevant passage portion.
  • Fig. 1 illustrates a cross section through an exhaust manifold 2 according to exemplary embodiments adapted for use with a four-stroke internal combustion engine.
  • the exhaust manifold 2 is adapted to be attached to three cylinders of the internal combustion engine (not shown).
  • the internal combustion engine may be e.g. of a type having three or more cylinders arranged in a straight line, or of a type having cylinders arranged in a V configuration, such as in a V-6 or V-8 engine.
  • the exhaust manifold 2 forms a plurality of exhaust gas inlet branches 4 arranged in series and connected to a main branch 6.
  • the exhaust manifold 2 comprises three exhaust gas inlet branches 4.
  • an exhaust gas manifold may comprise only two exhaust gas inlet branches, or more than three inlet branches, depending inter alia on the cylinder configuration of a relevant internal combustion engine.
  • Each exhaust gas inlet branch 4 defines an inlet passage 8, 10, 14.
  • the inlet passages 8, 10, 14 each receive a charge of exhaust gas from an associated exhaust opening (not shown) of a cylinder head of the internal combustion engine.
  • the main branch 6 defines a main passage 12.
  • the exhaust manifold 2 comprises walls having inner surfaces. The inner surfaces delimit the inlet passages 8, 10, 14 and the main passage 12. Cross sectional areas of the passages 8, 10, 14, 12 are delimited by the inner surfaces.
  • the exhaust manifold 2 forms at least two inlet passages 8, 10, 14 and one main passage 12.
  • the main passage 12 has an outlet end 16 arranged downstream of the at least two inlet passages 8, 10, 14.
  • the exhaust manifold 2 generally extends longitudinally with a closed forward end portion and the open outlet end 16. When attached to the associated engine cylinder head, the manifold 2 is secured so as to align its inlet passages 8, 10, 14, with exhaust gas outlet openings of the cylinder head. As each exhaust valve opens for an associated cylinder, a charge of exhaust gas flows from the cylinder head into the associated inlet passage 8, 10, 14, and from the inlet passage into the main passage 12.
  • the outlet end 16 of the main passage 12 may be connected to e.g. a turbocharger of the internal combustion engine.
  • the exhaust manifold 2 may be provided with non-shown flanges for connecting the exhaust manifold 2 to the cylinder head, exhaust conduits, etc.
  • a first inlet passage 8 of the at least two inlet passages connects to the main passage 12 at a junction 18.
  • the at least two inlet passages 8, 10, 14 are connected in series to the main passage 12.
  • the first inlet passage 8 is connected to the main passage 12 downstream of a second inlet passage 10 of the at least two inlet passages 8, 10, 14.
  • a third inlet passage 14 of the at least two inlet passages 8, 10, 14 is connected to the main passage 12 downstream of the first inlet passage 8.
  • the third inlet passage 14 and its connection to the main passage 12 are substantially identical to the first inlet passage 8 and its connection to the main passage 12.
  • the difference between the second inlet passage 10, and the first and third inlet passages 8, 14 is that the second inlet passage 10 does not have any inlet passage arranged upstream thereof along the main passage 12. Accordingly, a charge of exhaust gas flowing from the second inlet passage 10 into the main passage 12 is subjected to different flow conditions than charges of exhaust gas flowing from the first or third inlet passage 8, 14 into the main passage 12.
  • the exhaust manifold 2 may be manufactured e.g. by sand casting. Different parts of the exhaust manifold 2 may be cast separately and thereafter joined to form the exhaust manifold.
  • Figs. 2 and 3 illustrate cross sections through part of the exhaust manifold 2 of Fig. 1 . More specifically, the cross sections of Figs. 2 and 3 illustrate a portion of the main passage 12 and the first inlet passage 8 connecting thereto.
  • An intersecting wall portion 20 between the first inlet passage 8 and the main passage 12 forms an upstream end portion of the junction 18.
  • a first portion 22 of the first inlet passage 8 at the intersecting wall portion 20 has a first inlet passage cross sectional area 24.
  • a second portion 26 of the first inlet passage 8 arranged upstream of the first portion 22 of the first inlet passage 8 has a second inlet passage cross sectional area 28.
  • the second portion 26 of the first inlet passage 8 is in these embodiments arranged at an inlet 29 of the first inlet passage 8.
  • the first inlet passage cross sectional area 24 is smaller than the second inlet passage cross sectional area 28.
  • the hydraulic diameter of the first inlet passage cross sectional area 24 is smaller than the hydraulic diameter of the second inlet passage cross sectional area 28.
  • the main passage 12 comprises a first main passage portion 30 at the intersecting wall portion 20.
  • the first main passage portion 30 has a first main passage cross sectional area 32.
  • the main passage 12 comprises a second main passage portion 40 upstream of the junction 18.
  • the second main passage portion 40 has a second main passage cross sectional area 48.
  • the first main passage cross sectional area 32 is smaller than the second main passage cross sectional area 48.
  • the hydraulic diameter of the first main passage cross sectional area 32 is smaller than the hydraulic diameter of the second main passage cross sectional area 48.
  • the first portion 22 of the first inlet passage 8 may be positioned at an end portion 37 of the intersecting wall portion 20. Also the first main passage portion 30 may be positioned at the end portion 37 of the intersecting wall portion 20.
  • a main passage axis 38 extends centrally through the second main passage portion 40 in a straight line past the junction 18 and centrally through a third main passage portion 34 downstream of the first main passage portion 30.
  • the first main passage cross sectional area 32 extends perpendicularly to the main passage axis 38.
  • a centre axis 42 of the first inlet passage 8 at the first portion 22 of the first inlet passage 8 extends at an acute angle ⁇ to an upstream direction 44 of the main passage axis 38.
  • the angle ⁇ may be within a range of 30 - 45 degrees.
  • a charge of exhaust gas flowing through the first inlet passage 8 is directed in a downstream direction 46 in the main passage 12. Due to the reduction of the cross sectional area of the first inlet passage 8 from the second portion 26 of the first inlet passage 8 to the first portion 22 of the first inlet passage 8, the charge of exhaust gas is accelerated past the junction 18, in the downstream direction 46 of the main passage 12.
  • the acute angle ⁇ to the upstream direction 44 of the main passage axis 38 entails that the acute angle ⁇ points in the downstream direction 46 of the main passage axis 38.
  • the smaller first main passage cross sectional area 32 compared to the second main passage cross sectional area 48 reduces the portion of a charge of exhaust gas from the first inlet passage 8 flowing in the upstream direction 44 in the main passage 12.
  • the first inlet passage cross sectional area 24 may have a hydraulic diameter within a range of 0,65 - 0,85 times a hydraulic diameter of the second inlet passage cross sectional area 28.
  • the first inlet passage cross sectional area 24 may have a hydraulic diameter within a range of 0,68 - 0,75 times the hydraulic diameter of the second inlet passage cross sectional area 28.
  • the first main passage cross sectional area 32 may have a hydraulic diameter within a range of 0,8 - 0,99 times a hydraulic diameter of the second main passage cross sectional area 48.
  • the first main passage cross sectional area 32 may have a hydraulic diameter within a range of 0,92 - 0,98 times the hydraulic diameter of the second main passage cross sectional area 48.
  • the second inlet passage cross sectional area 28 and a third main passage cross sectional area 36 of the third main passage portion 34 may have hydraulic diameters of substantially the same size. In this manner exhaust gas pressure and flow from the first inlet passage 8 may remain consistent downstream of the junction 18 with those at the inlet 29 of the first inlet passage 8 thus, providing consistent exhaust gas properties towards the outlet end of the exhaust manifold 2.
  • the hydraulic diameters of the second inlet passage cross sectional area 28 and the third main passage cross sectional area 36 may differ within the range of 1 - 3 %.
  • the second main passage cross sectional area 48 may have a same hydraulic diameter as the third main passage cross sectional area 36. In this manner exhaust gas pressure and flow from the second inlet passage upstream of the first inlet passage 8 may remain consistent downstream of the junction 18 with those upstream of the junction 18 thus, providing consistent exhaust gas properties towards the outlet end of the exhaust manifold 2.
  • a hydraulic diameter of a cross sectional area of the outlet end 16 of the exhaust manifold 2 may have substantially a same hydraulic diameter as those of the second and third main passage cross sectional areas 48, 36.
  • consistent exhaust gas properties may be maintained along portions of the main passage 12 and towards the outlet end 16 of the exhaust manifold 2.
  • the second and third cross sectional areas 48, 36 of the exhaust manifold 2 may have hydraulic diameters of 42 mm, for a V8 diesel engine having a total displacement of 16 litres.
  • the intersecting wall portion 20 forms at least part of a deflector 50 arranged between the first inlet passage 8 and the main passage 12.
  • the deflector 50 extends into the main passage 12. That is, the deflector 50 extends towards the main passage axis 38.
  • the deflector 50 comprises a first wall portion 52 forming a delimiting surface of the main passage 12.
  • the first wall portion 52 extends at an acute angle ⁇ to the upstream direction 44 of the main passage axis 38 smaller than the angle ⁇ of the centre axis 42 of the first portion 22 of the first inlet passage 8 to the upstream direction 44.
  • the first wall portion 52 is slightly curved, e.g.
  • this feature entails that a general outline of the first wall portion 52 extends at an acute angle ⁇ to the upstream direction 44 of the main passage axis 38 smaller than the angle ⁇ .
  • a tangent of such a slightly curved wall portion may extend at an acute angle ⁇ to the upstream direction 44 of the main passage axis 38 smaller than the angle ⁇ .
  • the angle ⁇ may be at least 1 degree.
  • the acute angle ⁇ to the upstream direction 44 of the main passage axis 38 entails that the acute angle ⁇ points in the downstream direction 46 of the main passage axis 38.
  • the main passage 12 comprises a widening section 54 extending at least upstream of the first main passage portion 30.
  • the widening section 54 widens the main passage 12 in a first direction 56.
  • the first direction 56 is directed away from the first inlet passage 8 in a first cross sectional plane.
  • the first cross sectional plane extends through the first inlet passage 8, through at least a portion of the main passage 12, extends along the main passage axis 38, and includes the main passage axis 38.
  • the first cross sectional plane also includes the centre axis 42 of the first inlet passage 8. That is, the cross sections of Figs. 2 and 3 are placed in the first cross sectional plane.
  • the widening section 54 also extends downstream of the first main passage portion 30.
  • the widening section 54 may extend between the second and third main passage portions 40, 34.
  • a portion of a charge of exhaust gas from the first inlet passage 8 will flow upstream in the main passage 12, despite the first main passage portion 30 having a smaller cross sectional area than the second main passage portion 40.
  • the widening section 54 will cause the exhaust gas to form a vortex 58 in the main passage 12, upstream of the first passage portion 30.
  • the vortex 58 reduces the effective flow area 60 of the main passage 12.
  • the vortex 58 reduces the flow of exhaust gas in a direction upstream of the first main passage portion 30.
  • An inner surface 61 of the main passage 12, opposite to the first inlet passage 8 seen in the first cross sectional plane, at a transition between the widening section 54 and the second main passage portion 40 forms an abrupt directional change 63, such that a vortex is formed in exhaust gases during use of the exhaust manifold 2.
  • the vortex in the widening section is formed by the first fraction of each charge of exhaust gas from the first inlet passage 8.
  • the inner surface 61 is an inner surface of a second wall portion 62 extending along the widening section 54 and the second main passage portion 40.
  • the widening section 54 extends upstream of an end point 64 of the intersecting wall portion 20 over a distance having a length within a range of 1,2 - 1,7 times a hydraulic diameter of the second main passage portion 40.
  • the widening section 54 may extend upstream of the end point 64 to the abrupt directional change 63.
  • the widening section 54 extends downstream of the end point 64 of the intersecting wall portion 20 over a distance having a length within a range of 2 - 3 times a hydraulic diameter of the second main passage portion 40.
  • a transition between the widening section 54 and the third main passage portion 34 is gradual.
  • the gradual transition between the widening section 54 and the third main passage portion 34 promotes a laminar flow of exhaust gas in the downstream direction 46.
  • no vortex is formed at the gradual transition, as opposed to at the abrupt directional change 63 at the upstream end of the widening section 54 where a vortex is formed.
  • the end portion 37 of the intersecting wall portion 20 comprises the end point 64 in the first cross sectional plane.
  • Fig. 3 outlines 66 of three inner perimeters of the main passage 12 according to an embodiment are illustrated.

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  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Exhaust Silencers (AREA)

Claims (12)

  1. Abgaskrümmer (2) für einen Viertaktverbrennungsmotor, wobei der Abgaskrümmer (2) zumindest zwei Einlasskanäle und einen Hauptkanal (12) mit einem Auslassende (16) bildet, das stromabwärts der zumindest zwei Einlasskanäle angeordnet ist,
    wobei ein erster Einlasskanal (8) der zumindest zwei Einlasskanäle an einer Anschlussstelle (18) mit dem Hauptkanal (12) in Verbindung steht,
    wobei ein kreuzender Wandabschnitt (20) zwischen dem ersten Einlasskanal (8) und dem Hauptkanal (12) einen stromaufwärtigen Endabschnitt der Anschlussstelle (18) bildet,
    wobei ein erster Abschnitt (22) des ersten Einlasskanals (8) an dem kreuzenden Wandabschnitt (20) eine erste Einlasskanalquerschnittsfläche (24) hat,
    wobei die erste Einlasskanalquerschnittsfläche (24) kleiner ist als eine zweite Einlasskanalquerschnittsfläche (28) eines zweiten Abschnitts (26) des ersten Einlasskanals (8), der stromaufwärts des ersten Abschnitts (22) des ersten Einlasskanals (8) angeordnet ist, und
    wobei die Querschnittsfläche eines Kanalabschnitts basierend auf dem hydraulischen Durchmesser der betreffenden Querschnittsfläche berechnet ist,
    wobei
    der erste Einlasskanal (8) stromabwärts eines zweiten Einlasskanals (10) der zumindest zwei Einlasskanäle mit dem Hauptkanal (12) verbunden ist,
    wobei der Hauptkanal (12) einen ersten Hauptkanalabschnitt (30) an dem kreuzenden Wandabschnitt (20) aufweist, wobei der erste Hauptkanalabschnitt (30) eine erste Hauptkanalquerschnittsfläche (32) hat, und
    wobei die erste Hauptkanalquerschnittsfläche (32) kleiner ist als eine zweite Hauptkanalquerschnittsfläche (48) eines zweiten Hauptkanalabschnitts (40) des Hauptkanals (12), der stromaufwärts der Anschlussstelle (18) angeordnet ist,
    dadurch gekennzeichnet, dass
    der Hauptkanal (12) einen Verbreiterungsabschnitt (54) aufweist, der zumindest stromaufwärts des ersten Hauptkanalabschnitts (30) verläuft, wobei der Verbreiterungsabschnitt (54) den Hauptkanal (12) in einer ersten Richtung (56) verbreitert, wobei die erste Richtung (56) in einer ersten Querschnittsebene verläuft, die sich durch den ersten Einlasskanal (8) erstreckt, durch zumindest einen Teil des Hauptkanals (12), sich längs der Hauptkanalachse (38) erstreckt und die Hauptkanalachse (38) einschließt, und wobei die erste Richtung (56) von dem ersten Einlasskanal (8) weggerichtet ist.
  2. Abgaskrümmer (2) nach Anspruch 1, wobei eine Hauptkanalachse (38) sich mittig durch den zweiten Hauptkanalabschnitt (40) in einer geraden Linie an der Anschlussstelle (18) vorbei und mittig durch einen dritten Hauptkanalabschnitt (34) des Hauptkanals (12) erstreckt, der stromabwärts des ersten Hauptkanalabschnitts (30) angeordnet ist.
  3. Abgaskrümmer (2) nach Anspruch 2, wobei eine Mittelachse (42) des ersten Einlasskanals (8) sich an dem ersten Abschnitt (22) des ersten Einlasskanals (8) unter einem spitzen Winkel (α) zu einer Stromaufwärtsrichtung (44) der Hauptkanalachse (38) erstreckt, vorzugsweise unter einem Winkel (α) in einem Bereich von 30 bis 45 Grad.
  4. Abgaskrümmer (2) nach einem der Ansprüche 2 oder 3, wobei der kreuzende Wandabschnitt (20) zumindest einen Teil eines Abweisers (50) bildet, der zwischen dem ersten Einlasskanal (8) und dem Hauptkanal (12) angeordnet ist, und wobei der Abweiser (50) sich in Richtung auf die Hauptkanalachse (38) erstreckt.
  5. Abgaskrümmer (2) nach den Ansprüchen 2 bis 4, wobei der Abweiser (50) einen ersten Wandabschnitt (52) aufweist, der eine Begrenzungsfläche des Hauptkanals (12) bildet, und wobei der erste Wandabschnitt (52) sich unter einem spitzen Winkel (β) zu der Stromaufwärtsrichtung (44) der Hauptkanalachse (38) erstreckt, der kleiner ist als der Winkel (α) der Mittelachse (42) des ersten Abschnitts (22) des ersten Einlasskanals (8) zu der Stromaufwärtsrichtung (44).
  6. Abgaskrümmer (2) nach einem der Ansprüche 1 bis 5, wobei eine Innenfläche (61) des Hauptkanals (12) gegenüber dem ersten Einlasskanal (8) an einem Übergang zwischen dem Verbreiterungsabschnitt (54) und dem zweiten Hauptkanalabschnitt (40) eine abrupte Richtungsänderung (63) ausbildet, sodass während einer Benutzung des Abgaskrümmers (2) in Abgasen ein Wirbel gebildet wird.
  7. Abgaskrümmer (2) nach einem der Ansprüche 1 bis 6, wobei der Verbreiterungsabschnitt (54) sich stromaufwärts eines Endpunktes (64) des kreuzenden Wandabschnitts (20) über eine Distanz erstreckt, die eine Länge innerhalb eines Bereichs von 1,2 bis 1,7 mal einem hydraulischen Durchmesser des zweiten Hauptkanalabschnitts (40) hat.
  8. Abgaskrümmer (2) nach einem der Ansprüche 1 bis 7, wobei der Verbreiterungsabschnitt (54) sich stromabwärts eines Endpunktes (64) des kreuzenden Wandabschnitts (20) über eine Distanz erstreckt, die eine Länge innerhalb eines Bereichs von 2 bis 3 mal einem hydraulischen Durchmesser des zweiten Hauptkanalabschnitts (40) hat.
  9. Abgaskrümmer (2) nach einem der vorhergehenden Ansprüche, wobei der zweite Abschnitt (26) des ersten Einlasskanals (8) an einem Einlass (29) des ersten Einlasskanals (8) angeordnet ist, und wobei die erste Einlasskanalquerschnittsfläche (24) einen hydraulischen Durchmesser innerhalb eines Bereichs von 0,65 bis 0,85 mal einem hydraulischen Durchmesser der zweiten Einlasskanalquerschnittsfläche (28) hat, vorzugsweise innerhalb eines Bereichs von 0,68 bis 0,75 mal dem hydraulischen Durchmesser der zweiten Einlasskanalquerschnittsfläche (28).
  10. Abgaskrümmer (2) nach Anspruch 9, wobei die erste Hauptkanalquerschnittsfläche (32) einen hydraulischen Durchmesser innerhalb eines Bereichs von 0,8 bis 0,99 mal einem hydraulischen Durchmesser der zweiten Hauptkanalquerschnittsfläche (48) hat, vorzugszweise innerhalb eines Bereichs von 0,92 bis 0,98 mal dem hydraulischen Durchmesser der zweiten Hauptkanalquerschnittsfläche (48).
  11. Abgaskrümmer (2) nach Anspruch 9 oder 10, wobei die zweite Einlasskanalquerschnittsfläche (28) und eine dritte Hauptkanalquerschnittsfläche (36) des dritten Hauptkanalabschnitts (34) hydraulische Durchmesser von im Wesentlichen derselben Größe haben.
  12. Abgaskrümmer (2) nach einem der vorhergehenden Ansprüche, wobei die zweite Hauptkanalquerschnittsfläche (48) denselben hydraulischen Durchmesser wie eine dritte Hauptkanalquerschnittsfläche (36) des dritten Hauptkanalabschnitts (34) hat.
EP16730039.1A 2015-06-04 2016-05-27 Abgassammler Active EP3303793B1 (de)

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SE1550729A SE538932C2 (en) 2015-06-04 2015-06-04 Exhaust Manifold
PCT/SE2016/050489 WO2016195573A1 (en) 2015-06-04 2016-05-27 Exhaust manifold

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US10760538B2 (en) 2017-10-26 2020-09-01 500 Group, Inc. Customizable engine air intake/exhaust systems
US10570813B2 (en) 2017-10-26 2020-02-25 500 Group, Inc. Turbocharger exhaust manifold with turbine bypass outlet

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DE842873C (de) * 1950-06-25 1952-07-03 Maschf Augsburg Nuernberg Ag Abgassammler fuer aufgeladene Brennkraftmaschinen mit nachgeschalteter Abgasturbine
SE506211C2 (sv) 1995-07-21 1997-11-24 Volvo Ab Kollektoranordning för primärpipor till ett grenat avgasrör
US5860278A (en) 1996-12-23 1999-01-19 Chrysler Corporation Apparatus and method for providing a compact low pressure drop exhaust manifold
JP2000104545A (ja) * 1998-09-25 2000-04-11 Kubota Corp 複数の気筒を備えたエンジンの排気マニホールド
US7171805B2 (en) 2005-04-20 2007-02-06 Daimlerchrysler Corporation Deflector style exhaust manifold
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SE1550729A1 (en) 2016-12-05
BR112017026081B1 (pt) 2023-02-07
SE538932C2 (en) 2017-02-21
BR112017026081A2 (de) 2018-08-21
EP3303793A1 (de) 2018-04-11
KR20180009765A (ko) 2018-01-29

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