US20090026009A1 - Exhaust member - Google Patents

Exhaust member Download PDF

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Publication number
US20090026009A1
US20090026009A1 US11/909,320 US90932006A US2009026009A1 US 20090026009 A1 US20090026009 A1 US 20090026009A1 US 90932006 A US90932006 A US 90932006A US 2009026009 A1 US2009026009 A1 US 2009026009A1
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Prior art keywords
partition wall
wall
exhaust
arc
line
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Abandoned
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US11/909,320
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English (en)
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Kenji Itoh
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Proterial Ltd
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Individual
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Assigned to HITACHI METALS, LTD. reassignment HITACHI METALS, LTD. ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: ITOH, KENJI
Publication of US20090026009A1 publication Critical patent/US20090026009A1/en
Abandoned legal-status Critical Current

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    • 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
    • F01N13/107—More than one exhaust manifold or exhaust collector
    • 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
    • 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
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
    • F02B37/00—Engines characterised by provision of pumps driven at least for part of the time by exhaust
    • F02B37/02—Gas passages between engine outlet and pump drive, e.g. reservoirs
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
    • F02B37/00—Engines characterised by provision of pumps driven at least for part of the time by exhaust
    • F02B37/02—Gas passages between engine outlet and pump drive, e.g. reservoirs
    • F02B37/025—Multiple scrolls or multiple gas passages guiding the gas to the pump drive
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
    • F02B39/00—Component parts, details, or accessories relating to, driven charging or scavenging pumps, not provided for in groups F02B33/00 - F02B37/00
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02T—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO TRANSPORTATION
    • Y02T10/00—Road transport of goods or passengers
    • Y02T10/10—Internal combustion engine [ICE] based vehicles
    • Y02T10/12—Improving ICE efficiencies

Definitions

  • the present Invention relates to an exhaust member for engines, such as an exhaust manifold, a turbine housing, etc., which is free from the likelihood of cracking to its outer surface.
  • Some exhaust members for multi-cylinder (series-four-cylinder, series-six-cylinder, etc.) engines such as exhaust manifolds, turbine housings, etc., have divided exhaust ports to prevent the interference of an exhaust gas discharged from each engine cylinder, and backpressure increase. The division of the exhaust port stabilizes the performance and operation of the engine.
  • the exhaust manifold M comprises branch tubes BR 1 -BR 4 connected to four exhaust outlets EX 1 -EX 4 of the engine E, and a downstream-side tubular portion 30 m to which the branch tubes BR 1 -BR 4 converge.
  • the tubular portion 30 m comprises a flange 31 m formed at a downstream-side end periphery, and two exhaust ports Pa, Pb separated by a partition wall 32 m .
  • the branch tubes BR 1 , BR 4 converge to the exhaust port Pb, and the branch tubes BR 2 , BR 3 converge to the exhaust port Pa.
  • An upstream-side tubular portion 30 t of the turbine housing T comprises a flange 31 t formed at an upstream-side end periphery, and two intake ports Qa, Qb separated by a partition wall 32 t .
  • the flange 31 t has substantially the same shape as that of the flange 31 m of the exhaust manifold M.
  • the partition wall 32 t and the intake ports Qa, Qb are shaped and arranged such that when the flange 31 t is connected to the flange 31 m of the exhaust manifold M via a gasket S with bolts BT, the partition wall 32 m of the exhaust manifold M is smoothly connected to the partition wall 32 t of the turbine housing T, and the exhaust ports Pa, Pb are smoothly connected to the intake ports Qa, Qb.
  • downstream-side tubular portion 30 m of the exhaust manifold M and the upstream-side tubular portion 30 t of the turbine housing T have essentially the same shape and function as is clear from FIG. 8 , explanation will be made only on the downstream-side tubular portion 30 m . Its explanation is applicable to the upstream-side tubular portion 30 t of the turbine housing T, or tubular portions of other similar exhaust members, as it is.
  • a partition wall 32 connected to the inner wall of the tubular portion 30 is repeatedly subjected to compression stress and tensile stress by heating and cooling due to the start and stop of the engine E.
  • the expansion and shrinkage of the partition wall 32 is constrained by the flange 31 formed at a periphery of the tubular portion 30 , cracks CRK are likely to be generated in a connecting portion 34 of the partition wall 32 and the tubular portion 30 .
  • an exhaust gas is likely to leak.
  • JP 60-95118 U proposes, as shown in FIG. 11 , a partition wall 32 having a slit SLT deeper than the thickness of a flange 31 to absorb thermal expansion and shrinkage. It has been found, however, that the slit SLT causes turbulence in an exhaust gas flowing through the ports, resulting in backpressure increase and thus engine power decrease.
  • JP 2-39529 U proposes, as shown in FIG. 12 , an exhaust manifold locally having a thin-wall portion TW in a partition wall 32 , so that the thin-wall portion TW is easily deformed to alleviate thermal stress when the partition wall 32 is thermally deformed.
  • the thin-wall portion TW locally formed in the partition wall 32 can prevent the generation of cracks CRK, without disturbing the exhaust gas unlike when the slit SLT is formed in the partition wall 32 (JP 60-95118 U). It has been found, however that cracks CRK reaching the outer surface of the exhaust member are likely formed depending on the shape of the connecting portion 34 of the partition wall 32 and the tubular portion 30 . Also, in the shape of the partition wall 32 shown in FIG. 12 , thick connecting portions 34 make the overall exhaust manifold extremely heavy.
  • JP 7-217438 A proposes, as shown in FIG. 13 , an exhaust manifold comprising exhaust ports Pa, Pt each having a substantially trapezoidal cross section, and arcuate connecting portions 34 each having a small radius of curvature Rs for connecting a partition wall 32 and a linear inner wall 35 , thereby dispersing thermal stress in the linear inner wall 35 . It has been found, however, that cracks CRK reaching the outer surface of the exhaust member are likely formed depending on the shape of the connecting portion 34 connecting the partition wall 32 and the linear inner wall 35 . Also, the exhaust port is restricted to have a substantially trapezoidal cross section, resulting in extremely small freedom of design.
  • an object of the present invention is to provide an exhaust member free from the likelihood of cracking to its outer surface, without extreme restriction of the cross section shape of an exhaust port,
  • the minimum thickness A of said partition wall is 2-10 mm, and that said partition wall is tangentially connected to said inner wall with an arc having a radius of 2-13 mm in a transverse cross section of said tubular portion having said partition wall.
  • FIG. 2( a ) is a front view showing a downstream-side opening end surface of an exhaust member according to another preferred embodiment of the present invention.
  • FIG. 2( b ) is a front view showing a downstream-side opening end surface of an exhaust member according to a further preferred embodiment of the present invention.
  • FIG. 2( c ) is a front view showing a downstream-side opening end surface of an exhaust member according to a still further preferred embodiment of the present invention.
  • FIG. 3( a ) is a front view showing a downstream-side opening end surface of an exhaust member according to a still further preferred embodiment of the present invention.
  • FIG. 3( b ) is a front view showing a downstream-side opening end surface of an exhaust member according to a still further preferred embodiment of the present invention.
  • FIG. 3( c ) is a front view showing a downstream-side opening end surface of an exhaust member according to a still further preferred embodiment of the present invention.
  • FIG. 3( d ) is a front view showing a downstream-side opening end surface of an exhaust member according to a still further preferred embodiment of the present inventions
  • FIG. 4( a ) is a perspective view showing the shape of a test piece used in Example 1.
  • FIG. 4( c ) is an enlarged front view showing the shape of a partition wall of a test piece used in Example 1.
  • FIG. 4( d ) is a front view showing the shape of a test piece used in Comparative Example 1.
  • FIG. 4 ( e ) is a front view showing the shape of a test piece used in Comparative Example 2.
  • FIG. 5( a ) is a front view showing the shape of a test piece used in Example 2.
  • FIG. 5( b ) is an enlarged front view showing the shape of a partition wall of a test piece used in Example 2.
  • FIG. 5( c ) is a front view showing the shape of a test piece used in Comparative Example 3.
  • FIG. 6 is a schematic view showing a thermal fatigue test machine.
  • FIG. 7( a ) is a perspective view showing the turbine housing of Example 3 after the thermal fatigue test.
  • FIG. 7( b ) is a perspective view showing the turbine housing of Comparative Example 4 after the thermal fatigue test.
  • FIG. 8 is a cross-sectional view showing one example of the exhaust member connected to a series-four-cylinder engine.
  • FIG. 9 is an enlarged cross-sectional view taken along the line Z-Z in FIG. 8 .
  • FIG. 10 is a schematic view explaining the mechanism of generating cracks.
  • FIG. 11 is a front view showing a downstream-side opening end surface of the exhaust member described in JU 60-95118 A.
  • FIG. 12 is a front view showing a downstream-side opening end surface of the exhaust member described in JU 2-39529 A,
  • FIG. 13 is a front view showing a downstream-side opening end surface of the exhaust member described in JP 7-217438 A.
  • FIG. 1( a ) is a front view showing an opening end surface 3 of an exhaust member in the first embodiment
  • FIG. 1( b ) is an enlarged view showing a portion X in FIG. 1( a ).
  • This exhaust member has a flange 1 having a substantially rectangular contour, and a partition wall 2 having a center portion with a substantially linear outer surface and both end portions each with a curved outer surface.
  • the partition wall 2 has the minimum thickness A in a range within 1 ⁇ 2 of the length of the partition wall 2 with its longitudinal middle point O as a center, and its curved outer surfaces are gradually wider outside that range (on the end portion sides).
  • Portions divided by a tangent line L 1 common to exhaust ports Pa and Pb shown in FIG. 1( a ) are called “flange 1 ” and “partition wall 2 ” connected to the flange 1 via a connecting portion 4 .
  • the flange 1 is above the tangent line L 1
  • the partition wall 2 is below the tangent line L 1 .
  • the smallest distance between the tangent line L 1 and the tangent line L 2 is defined as the length of the partition wall 2 .
  • a line connecting middle points of the width of the partition wall 2 is defined as a longitudinal centerline C of the partition wall.
  • a tangent line of the longitudinal centerline C at a position of 3 ⁇ 8 of the length of the partition wall 2 is defined as longitudinal centerline C.
  • Each outer surface 2 a of the partition wall 2 should exist on or outside each inner line (shown by the chain line) comprising a parallel line H 1 , E 2 separate from the longitudinal centerline C of the partition wall 2 by a distance of A/ 2 , and an arc R 1 , R 2 having a radius r 1 , r 2 which is tangentially connected to the parallel line H 1 , H 2 and the inner wall 5 of the tubular portion 10 .
  • tangentially connected used herein means that the tangent line of each arc K 1 , R 2 is in alignment with that of each parallel line H 1 , H 2 at a contact point of the arc R 1 , R 2 and the parallel line H 1 , H 2 .
  • each arc R 1 , R 2 corresponds to an arc having a radius r 1 , r 2 inscribed to the parallel line H 1 , H 2 and the inner wall 5 .
  • the partition wall 2 should have such thickness as to hold sufficient high-temperature strength. Because stress is concentrated particularly in the connecting portion 4 , the connecting portion 4 should be thicker than the center portion. However, too thick a partition wall 2 makes the exhaust member too heavy.
  • each outer surface 2 a of the partition wall 2 should exist on or inside each outer line (shown by the chain line) comprising a parallel line H 3 , H 4 separate from the longitudinal centerline C by a distance of 3/2 ⁇ A, and an arc R 3 , R 4 having a radius r 3 , r 4 and tangentially connected to the parallel line H 3 , H 4 and the inner wall 5 of the tubular portion 10 .
  • the arc R 3 , R 4 corresponds to an arc having a radius r 3 , r 4 and inscribed to the parallel line H 3 , H 4 and the inner wall 5 .
  • the partition wall 2 is so thick that an exhaust member is heavy.
  • the connecting portion 4 of the partition wall 2 and the inner wall 5 has too large a curvature to avoid stress concentration, resulting in high likelihood of cracking. Therefore, both of r 3 and r 4 should be 1 ⁇ 3 ⁇ A or more, preferably 1 ⁇ 2 ⁇ A or more.
  • r 3 r 4 in this embodiment, r 3 may not be equal to r 4 as in a subsequent embodiment. Particularly in that case, attention should be paid to avoid that r 3 and r 4 are too small.
  • the outer surface 2 a of the partition wall 2 may have a straight contour, but it preferably has a slightly curved contour.
  • the slightly curved contour may not be arcuate.
  • the thickness A 2 of the partition wall 2 is preferably 1.3 times or more, more preferably 1.5 times or more, of the minimum thickness A of the partition wall 2 .
  • the center region 21 is smoothly connected to the tapered region 4 a.
  • the connecting portion 4 b is preferably a curved line smoothly connecting the outer surface 2 a of the partition wall 2 to the inner wall 5 , more preferably an arc tangentially connected to the outer surface 2 a and the inner wall 5 .
  • the arc may have such a radius that the outer surface 2 a of the partition wall 2 exists between said inner line and said outer line, and the radius of the arc is preferably 1 ⁇ 3 ⁇ A or more, more preferably 1 ⁇ 2 ⁇ A or more.
  • each outer surface 2 a of the partition wall 2 exists in a region B 1 , B 2 sandwiched by said inner line and said outer line, cracking occurs predominantly in said center region 21 when a large thermal stress is applied to the partition wall 2 , with other regions suffering little cracking. Even if there are cracks near the connecting portion 4 of the partition wall 2 and the flange 1 , they propagate not toward the flange 1 but toward the partition wall 2 away from the flange 1 , so that cracks penetrating from the exhaust ports Pa or Pb to the outer surface of the exhaust member are hardly generated. Accordingly, the above shape of the partition wall 2 can provide an exhaust member free fi-om cracks in the tubular portion 10 without increasing the weight of the exhaust member.
  • FIG. 2( a ) shows an opening end surface 3 of an exhaust member in the second embodiment.
  • This exhaust member is substantially the same as that of the first embodiment except that both partition wall 2 and exhaust ports are inclined, so that it should meet all the conditions of the first embodiment.
  • FIG. 2( b ) shows an opening end surface 3 of an exhaust member in the third embodiment.
  • This exhaust member is substantially the same as that of the first embodiment except that a partition wall 2 has an S shape, so that it should meet all the conditions of the first embodiment.
  • FIG. 2( c ) shows an opening end surface 3 of an exhaust member in the fourth embodiment.
  • This exhaust member is substantially the same as that of the second embodiment except that a partition wall 2 has an S shape, so that it should meet all the conditions of the first embodiment.
  • FIG. 3( a ) shows an opening end surface 3 of an exhaust member in the fifth embodiment.
  • This exhaust member is substantially the same as that of the first embodiment except that the opening end surface 3 has a circular shape, so that it should meet all the conditions of the first embodiment.
  • FIG. 3( b ) shows an opening end surface 3 of an exhaust member in the sixth embodiment.
  • This exhaust member is substantially the same as that of the fifth embodiment except that both partition wall 2 and exhaust port are inclined, so that it should meet all the conditions of the first embodiment.
  • FIG. 3( c ) shows an opening end surface 3 of an exhaust member in the seventh embodiment.
  • This exhaust member is substantially the same as that of the fifth embodiment except that a partition wall 2 has an S shape, so that it should meet all the conditions of the first embodiment.
  • FIG. 3( d ) shows an opening end surface 3 of an exhaust member in the eighth embodiment.
  • This exhaust member is substantially the same as that of the sixth embodiment except that a partition wall 2 has an S shape, so that it should meet all the conditions of the first embodiment.
  • the partition wall 2 has the minimum thickness A in a range (center region 4 a ) within 1 ⁇ 2 of the length of the partition wall from the longitudinal middle point O of the partition wall as a center, and its outside region (end region 40 ) has a gradually increasing width.
  • a test piece TP having the shape shown in FIG. 4( a ) was produced from heat-resistant austenitic cast steel.
  • the test piece TP had a thickness of 20 mm
  • the tubular portion 10 had a thickness FW of 20 mm
  • the partition wall 2 had a length of 80 mm.
  • FIG. 4( b ) shows an opening end surface 3 of the test piece TP
  • FIG. 4( c ) is ail enlarged view showing the partition wall 2 .
  • the partition wall 2 has a 6-mm-thick flat-plate-shaped center region 21 in a range within 1 ⁇ 2(40 mm) of the length of the partition wall 2 from the longitudinal middle point O as a center, and an end region 40 comprising a tapered region 4 a and a connecting portion 4 outside the flat-plate-shaped center region 21 .
  • the minimum thickness A of the partition wall 2 is 6 mm, the same as that of the center region 21 , and the tapered region 4 a has a gradually and linearly increasing width from the end of the center region 21 .
  • the thickness A 2 is 10 mm at a position separate from the longitudinal middle point O of the partition wall 2 by a distance of 30 mm, 3 ⁇ 8 of the length of the partition wall 2 .
  • the connecting portion 4 is in an arc shape having a radius of 7 mm and tangentially connected to the tapered region 4 a and the inner wall 5 of the tubular portion 10 . Table 1 shows the size of the test piece TP.
  • the test piece TP was subjected to a thermal fatigue test by a thermal fatigue-test apparatus described in Japanese Patent 2533885.
  • LPG from ail LPG source 52 and air from a compressor 53 are supplied to a burner 51 , and air is forcedly supplied to a combustion chamber 54 , so that LPG is ignited in the combustion chamber 54 and burned in the burner 51 .
  • Flame 55 from the burner 51 is injected into the combustion chamber 54 , and the resultant high-temperature combustion gas is caused to flow to the test piece TP via a combustion gas passage 56 a of a cooling block 56 to heat the test piece TP.
  • the combustion gas passage 56 a is cooled by water circulating in the cooling block 56 having cooling water inlet and outlet.
  • the test piece TP is provided with a sheath-type thermocouple 57 at its inlet.
  • the thermal fatigue test was conducted by repeating cycles each comprising two steps of (i) heating the test piece TP until the temperature detected in the sheath-type thermocouple 57 reached 950° C. amid then keeping it at that temperature for 10 minutes, and (ii) stopping the supply of the combustion gas and keeping it for 10 minutes, until cracking was observed in the test piece TP.
  • the thermal fatigue test revealed that the test piece TP of Example 1 had cracks in a longitudinal center portion of the partition wall 2 , but was free from cracks extending from the exhaust port to the outer surface of the test piece TP.
  • a test piece TP was produced in the same manner as in Example 1, except that the tapered region 4 a of the partition wall 2 was made to have a constant thickness of 6 mm, meaning that there was substantially no tapered region 4 a , and that the connecting portion 4 was formed by an arc having a radius of 2 mm and tangentially connected to the outer surface 2 a of the partition wall 2 and the inner wall 5 of the tubular portion 10 .
  • the minimum thickness A of the partition wall 2 was 6 mm, the same as the thickness of the center region 21 , and the thickness A2 of the partition wall 2 was 6 mm at a position of 30 mm, 3 ⁇ 8 of the length of the partition wall 2 from the middle point O.
  • Table 1 shows the size of the test piece TP.
  • the test piece TP of Comparative Example 1 was subjected to a thermal fatigue test as in Example 1, resulting in cracks extending from the connecting portion of the partition wall and the flange to the exhaust port to the outer surface of the test piece TP.
  • a test piece TP was produced in the same manner as in Example 1, except that the thickness A2 of the partition wall 2 was 30 mm at a position of 3 ⁇ 8 of the length of the partition wall from the longitudinal middle point O of the partition wall.
  • Table 1 shows the size of the test piece TP.
  • the partition wall 2 of this test piece TP had each outer surface 2 a existing beyond the region (hatched portion B 1 , B 2 ) described in Example 1 which was sandwiched by the inner and outer lines.
  • the test piece TP was subjected to the same thermal fatigue test as in Example 1, revealing that cracks were generated in the longitudinal center portion of the partition wall 2 , without cracks extending from the exhaust port to the outer surface of the test piece TP.
  • the test piece TP of Comparative Example 2 was as heavy as 1.1 times the test piece TP of Example 1, resulting in 10-% decrease in the cross section area of the exhaust port.
  • FIG. 5( a ) is an enlarged view showing the partition wall of the test piece TP.
  • the partition wall 2 With the longitudinal middle point O of the partition wall 2 as a center, the partition wall 2 has a 6-mm-thick, flat-plate-shaped center region 21 in a range within 112 of the length of the partition wall 2 , and an end region 40 comprising a tapered region 4 a and a connecting portion 4 outside the flat-plate-shaped center region 21 .
  • the center region 21 is inclined by an angle ⁇ 1 of 30° relative to the partition wall 2 of Example 1 and the tapered region 4 a is inclined by angle ⁇ 2 of ⁇ 45° relative to the partition wall 2 of Example 1, so that the overall partition wall 2 is in an S shape.
  • the minimum thickness A of the partition wall 2 is 6 mm, the same as the thickness of the center region 21 , and the tapered region 4 a is gradually linearly widening from the end of the center region 21 , so that the thickness A2 is 10 mm at a position of 3 ⁇ 8 of the length of the partition wall 2 from the longitudinal middle point O of the partition wall 2 .
  • the center region 21 is tangentially connected to the tapered region 4 a with arcs Ri and Ro having radii ri (3 mm) and ro (9 mm) in a bent portion 23 .
  • Ri an arc connecting the outer surfaces 2 a of the partition wall 2 on a smaller angle side
  • Ro an arc on the other side
  • the connecting portion 4 is formed by an arc Ra having a radius of 10 mm and an arc Rb having a radius of 5 mm both tangentially connected to the tapered region 4 a and the inner wall 5 of the tubular portion 10 .
  • An arc with an obtuse angle between the partition wall 2 and the inner wall 5 was Ra, and an arc with an acute angle was Rb.
  • Table 1 shows the size of the test piece TP.
  • a test piece TP was produced in the same manner as in Example 2, except that the tapered region 4 a of die partition wall 2 had a constant thickness of 6 mm, the same as that of the center region 21 , and that it had arcs Ra and Rb having radii of 8 mm and 2 mm, respectively, with substantially no tapered region 4 a .
  • Table 1 shows the size of the test piece TP.
  • the same thermal fatigue test as in Example 1 revealed that there were cracks extending from the exhaust port to the outer surface of the test piece TP in the connecting portions of the partition wall and the flange.
  • Example 1 Example 2
  • a turbine housing Ta shown in FIG. 7( a ) was produced.
  • the turbine housing Ta is used in series-four-cylinder, high-performance gasoline engine (not shown) with a displacement of 2000 cc.
  • a turbine in the turbine housing was rotated by the pressure of an exhaust gas discharged from the engine and gathered by an exhaust manifold, to drive a compressor concentric with the turbine to compress the mixed gas, which is returned to the engine to increase the power of the engine.
  • an opening end surface 3 of the turbine housing Ta has a substantially similar shape to that of the test piece TP of Example 1 shown in FIG. 4( b ). Accordingly, the shape of its partition wall 2 will be explained referring to FIG. 4( b ).
  • the partition wall 2 has a length of 40 mm and the minimum thickness A of 3 mm. With the longitudinal middle point O as a center, the partition wall 2 has a 3-mm-thick, flat-plate-shaped center region 21 in a range within 1 ⁇ 2 of the length of the partition wall 2 , and there is an end region 40 comprising a tapered region 4 a and a connecting portion 4 outside the flat-plate-shaped center region 21 .
  • the minimum thickness A of the partition wall 2 is 3 mm, the same as the thickness of the center region 21 , the tapered region 4 a becomes gradually linearly wider from an end of the center region 21 , and the thickness A2 is 5 mm at a position of 15 mm, 3 ⁇ 8 of the length of the partition wall 2 , from the longitudinal middle point O of the partition wall 2 .
  • the connecting portion 4 was in an arc shape having a radius of 3.5 mm, which tangentially connected the tapered region 4 a to the inner wall 5 of the tubular portion 10 .
  • Example 1 The same thermal fatigue test as in Example 1 was conducted on the turbine housing Ta using the thermal fatigue test machine 40 .
  • the thermal fatigue test comprised 1000 cycles each comprising two steps of (i) heating the turbine housing Ta until the temperature of a center portion of the partition wall 2 reached 1000° C., and keeping it for 10 minutes, and (ii) stopping the supply of a combustion gas to cool it, and keeping it for 10 minutes,
  • FIG. 7( a ) shows cracks CRK generated in the turbine housing Ta after the thermal fatigue test.
  • the cracks CRK were generated substantially in the center portion of the partition wall 2 , but no cracks penetrating to the outer surface of the turbine housing were observed.
  • the turbine housing Tb shown in FIG. 7( b ) was produced like the turbine housing Ta of Example 3, except that the tapered region 4 a of the partition wall 2 had a constant thickness of 3 mm, the same as that of the center region 21 , meaning that there was substantially no tapered region 4 a , and that an arc tangentially connected to the partition wall 2 and the inner wall 5 had a radius of 2 mm.
  • the opening end surface 3 of the turbine housing Tb has a substantially similar shape to that of the test piece TP of Comparative Example 1 shown in FIG. 4( d ).
  • each inner line comprising a parallel line H 1 , H 2 separate from the longitudinal centerline C of the partition wall by a distance of A/2, and an arc R 1 , R 2 tangentially connected to the parallel line H 1 , H 2 and the inner wall
  • each outer line comprising a parallel line H 3 , H 4 separate from the longitudinal centerline C of the partition wall by a distance of 3/2 ⁇ A
  • FIG. 7( b ) shows the cracks CRK.
  • an exhaust gas in the exhaust port Pa or Pb ejected outside through the cracks CRK, causing exhaust interference and making the operation of the turbine housing unstable, resulting in decrease in engine performance.
  • the exhaust member of the present invention having the above structure is free from cracks penetrating to the outer surface without weight increase and substantial restriction in the cross section shape of the exhaust port, the engine operation is stabilized without performance decrease.

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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)
  • Supercharger (AREA)
US11/909,320 2005-03-24 2006-03-22 Exhaust member Abandoned US20090026009A1 (en)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
JP2005-086851 2005-03-24
JP2005086851 2005-03-24
PCT/JP2006/305706 WO2006101125A1 (ja) 2005-03-24 2006-03-22 排気系部品

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US10371043B2 (en) * 2015-04-09 2019-08-06 Borgwarner Inc. Exhaust gas supply arrangement of an exhaust gas turbocharger
US20190309676A1 (en) * 2018-04-06 2019-10-10 Toyota Jidosha Kabushiki Kaisha Internal combustion engine
CN110344927A (zh) * 2018-04-06 2019-10-18 丰田自动车株式会社 内燃机
US20200173333A1 (en) * 2018-11-30 2020-06-04 Hyundai Motor Company Turbocharger fastening structure
US11098636B2 (en) * 2019-12-18 2021-08-24 Caterpillar Inc. Joint Oc Exhaust manifold to turbine connection
US11236660B2 (en) * 2017-12-20 2022-02-01 Volvo Truck Corporation Sealing gasket, for sealing the connection between an exhaust manifold and a turbine
US20230374928A1 (en) * 2020-11-20 2023-11-23 Caterpillar Inc. Exhaust manifold having turbine connector with turbine foot
US11933863B2 (en) 2020-07-27 2024-03-19 Changxin Memory Technologies, Inc. Method for measuring shortest distance between capacitances and method for evaluating capacitance manufacture procedure

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KR20160070275A (ko) 2014-12-09 2016-06-20 현대자동차주식회사 차량용 배기가스 배출장치
WO2020105474A1 (ja) * 2018-11-21 2020-05-28 株式会社Ihi 排気タービン装置
CN114001692B (zh) * 2020-07-27 2023-04-07 长鑫存储技术有限公司 测量电容之间最短距离的方法及评价电容制程的方法

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Cited By (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US10371043B2 (en) * 2015-04-09 2019-08-06 Borgwarner Inc. Exhaust gas supply arrangement of an exhaust gas turbocharger
US11236660B2 (en) * 2017-12-20 2022-02-01 Volvo Truck Corporation Sealing gasket, for sealing the connection between an exhaust manifold and a turbine
US20190309676A1 (en) * 2018-04-06 2019-10-10 Toyota Jidosha Kabushiki Kaisha Internal combustion engine
CN110344927A (zh) * 2018-04-06 2019-10-18 丰田自动车株式会社 内燃机
CN110344928A (zh) * 2018-04-06 2019-10-18 丰田自动车株式会社 内燃机
US10774675B2 (en) 2018-04-06 2020-09-15 Toyota Jidosha Kabushiki Kaisha Internal combustion engine
US20200173333A1 (en) * 2018-11-30 2020-06-04 Hyundai Motor Company Turbocharger fastening structure
US10865691B2 (en) * 2018-11-30 2020-12-15 Hyundai Motor Company Turbocharger fastening structure
US11098636B2 (en) * 2019-12-18 2021-08-24 Caterpillar Inc. Joint Oc Exhaust manifold to turbine connection
US11933863B2 (en) 2020-07-27 2024-03-19 Changxin Memory Technologies, Inc. Method for measuring shortest distance between capacitances and method for evaluating capacitance manufacture procedure
US20230374928A1 (en) * 2020-11-20 2023-11-23 Caterpillar Inc. Exhaust manifold having turbine connector with turbine foot
US11988126B2 (en) * 2020-11-20 2024-05-21 Caterpillar Inc. Exhaust manifold having turbine connector with turbine foot

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WO2006101125A1 (ja) 2006-09-28
KR20070112150A (ko) 2007-11-22
CN101146983A (zh) 2008-03-19
EP1862653A1 (en) 2007-12-05

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