EP1686261A1 - Collecteur d' chappement - Google Patents

Collecteur d' chappement Download PDF

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Publication number
EP1686261A1
EP1686261A1 EP04818504A EP04818504A EP1686261A1 EP 1686261 A1 EP1686261 A1 EP 1686261A1 EP 04818504 A EP04818504 A EP 04818504A EP 04818504 A EP04818504 A EP 04818504A EP 1686261 A1 EP1686261 A1 EP 1686261A1
Authority
EP
European Patent Office
Prior art keywords
diameter
exhaust manifold
main tube
tube
internal combustion
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Withdrawn
Application number
EP04818504A
Other languages
German (de)
English (en)
Inventor
Hiroshi c/o YANMAR CO. LTD. OMOTE
Shunji c/o YANMAR CO. LTD. HAMAOKA
Keiichi c/o YANMAR CO. LTD. TSUJIMOTO
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Yanmar Co Ltd
Original Assignee
Yanmar Co Ltd
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Yanmar Co Ltd filed Critical Yanmar Co Ltd
Publication of EP1686261A1 publication Critical patent/EP1686261A1/fr
Withdrawn legal-status Critical Current

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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
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02F—CYLINDERS, PISTONS OR CASINGS, FOR COMBUSTION ENGINES; ARRANGEMENTS OF SEALINGS IN COMBUSTION ENGINES
    • F02F1/00—Cylinders; Cylinder heads 
    • F02F1/24—Cylinder heads
    • F02F1/42—Shape or arrangement of intake or exhaust channels in cylinder heads
    • F02F1/4264—Shape or arrangement of intake or exhaust channels in cylinder heads of exhaust channels
    • 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
    • F01N13/18—Construction facilitating manufacture, assembly, or disassembly

Definitions

  • the present invention relates to an exhaust manifold for a supercharger-equipped internal combustion engine having multiple cylinders.
  • turbocharging systems in an exhaust manifold of an internal combustion engine with a supercharger.
  • One is a pulse turbocharging system and another is a constant-pressure turbocharging system.
  • the former it is set up so as to make an exhaust pulse large or enhance in an inlet-port section of a turbine, and the supercharger is driven by the enhanced exhaust pulse.
  • the latter its acceleration performance is improved, however, its fuel consumption at a rated horsepower point is increased.
  • it is set up so as to change the exhaust pulse into static pressure for using a part with high supercharger effectiveness.
  • its fuel consumption in a rated horsepower point is reduced, however, its acceleration performance is inferior as compared with the former. If both are set up so as to make a main tube's passage small, the exhaust pulse will become enhance, therefore the acceleration performance will be improved.
  • Fig.1 is a graph showing the relation between the load application time corresponding to the diameter of the main tube, and the fuel consumption. In this Fig.1, it turns out that the load application time(load making time) becomes long although the fuel consumption will become good when the diameter of the main tube is greatly set up, on the contrary, the load application time will become short although fuel consumption gets worse when the diameter of the main tube is set up small.
  • the diameter of the main tube is greatly set up provided on the constant pressure system for the purpose of improving the fuel consumption, although the load application time amount became long.
  • An object of the present invention is to provide a manifold for an internal combustion engine in which the fuel consumption is improved and the load application time is reduced or shorten.
  • an exhaust manifold for a supercharger-equipped internal combustion engine having multiple cylinders, characterized in that; the diameter D of a main tube of the exhaust manifold and the diameter d of a branch tube of the exhaust manifold satisfy the expression of 1.2 ⁇ (D/d) 2 ⁇ 2.5.
  • an exhaust manifold for a supercharger-equipped internal combustion engine having multiple cylinders, characterized in that; the diameter d of a branch tube of the exhaust manifold and the diameter de of an exhaust valve sheet satisfy the expression of 0.8 ⁇ (d/de) 2 ⁇ 1.2.
  • an exhaust manifold for a supercharger-equipped internal combustion engine having multiple cylinders, characterized in that; the diameter D of a main tube of the exhaust manifold and the diameter D1 of a passage connecting a branch tube to the main tube satisfy the expression of 0.7 ⁇ (D/D 1 ) 2 ⁇ 1.4.
  • an exhaust manifold for a supercharger-equipped internal combustion engine having multiple cylinders characterized in that; a branch tube of the exhaust manifold is smoothly connected to a main tube of the exhaust manifold, the radius R of the outer peripheral side of a connection connecting the branch tube to the main tube and the radius r of the connection satisfy the expression of 1.7 ⁇ R/r ⁇ 2.1.
  • the load application time (build up time) can be reduced without worsening the fuel consumption.
  • the same effectiveness or advantage as invention of claim 1 can be done so.
  • Fi.2 is a schematic appearance view of the exhaust manifold of the internal combustion engine according to the present invention.
  • the exhaust manifold 100 one end of a branch tube 2 is connected to a side wall of a main tube 1. Another end of the branch tube 2 is connected to an exhaust port 6 of a cylinder 10.
  • An exhaust valve 5 is arranged in the exhaust port 6 so as to be movable in the direction of the arrow. The exhaust port 6 can be opened and closed with the exhaust valve 5.
  • a structure of the exhaust manifold 100 is simplified by connecting each cylinder 10a-10f to a main tube 1 via each branch tube 2.
  • the dimension of the suitable diameter de of an exhaust valve sheet corresponding to the diameter D 2 of a boa, which is equivalent to a diameter of a piston 4, is determined.
  • the diameter d of the branch tube 2 is set up so that its dimension may not change rapidly from the diameter de of the exhaust valve sheet to the diameter D 1 of a connection 7.
  • a cross-section configuration of a passage of the branch tube 2 or a connection 7 is not limited in the form of circular.
  • the cross-section configuration of the passage of the branch tube 2 or the connection 7 is not formed of circular, it calculates the diameter of the circle of the same area, and applies the value of said calculated diameter as the diameter d of the branch tube 2 and the diameter D 1 of the connection 7, respectively.
  • Fig.5 is a graph showing the change of the load application time and the fuel consumption relating to the value of (the diameter D of the main tube / the diameter d of the branch tube) 2 . As shown in Fig.5, in the range of 1.2-2.5 of the value of (diameter D of the main tube / diameter d of the branch tube) 2 , it turns out that the fuel consumption hardly changes, and the load application time amount is short.
  • the diameter D of the main tube 1 is determined using the following expression (1). 1.2 ⁇ ( D / d ) 2 ⁇ 2.5
  • the fuel consumption at the load application time A is worse than the fuel consumption at the load application time B.
  • the difference (a-b) between the fuel consumptions (a) and (b) is very small. Namely, the fuel consumption hardly changes between the time A and the time B.
  • the load application time A is (B-A) shorter than the load application time B.
  • the load application time A is selects so that the difference (a-b) may be settled in the predetermined tolerance range, and then the diameter D of the main tube 1 corresponding to the time A can be derived based on the graph in shown Fig.1. Namely, it becomes possible to determine such value of the diameter D of the main tube 1 that reduces the load application time and prevents the increase in the fuel consumption.
  • Fig.6 is a graph showing the change of the load application time and the fuel consumption relating to the value of (diameter D of the main tube / diameter de of the exhaust valve sheet de) 2 . According to Fig.6, it turns out that the fuel consumption hardly changes and the load application time comes short when the value of (d/de) 2 exits between 0.8 and 1.2.
  • the diameter d of the branch tube 2 and the diameter de of the exhaust valve sheet are set up so that the following expression (2) may be satisfied. 0.8 ⁇ ( d / d e ) 2 ⁇ 1.2
  • Fig.7 is a graph showing the change of the load application time and the fuel consumption relating to the value of (diameter D of the main tube / diameter D 1 of the connection) 2 . According to Fig.7, it turns out that the fuel consumption hardly changes and the load application time comes short when the value of (diameter D of the main tube / diameter D 1 of the connection) 2 exits between 0.7 and 1.4.
  • the diameter D of the main tube 1 and the diameter D1 of the connection 7 are set up so that the following expression (3) may be satisfied. 0.7 ⁇ ( D / D 1 ) 2 ⁇ 1.4
  • Fig.8 is a graph showing the change of the load application time and the fuel consumption relating to the value of (outer periphery radius R / inner circumference radius r) 2 .
  • the outer periphery radius R" and the “inner circumference radius r” which are shown in Fig.8 are concretely shown in Fig.4 which is the cross-section schematic view showing the relation of the connection include angle of the branch tube 2 to the main tube 1 of the exhaust manifold 100.
  • the value of the outer periphery radius R and the inner circumference radius r are set up so that the following expression (4) may be satisfied. 1.7 ⁇ R / r ⁇ 2.1
  • the load application time can be short set up rather than the conventional exhaust manifold, without worsening fuel consumption.

Landscapes

  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Exhaust Silencers (AREA)
  • Fuel-Injection Apparatus (AREA)
EP04818504A 2003-11-17 2004-11-12 Collecteur d' chappement Withdrawn EP1686261A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2003386745A JP2005147014A (ja) 2003-11-17 2003-11-17 内燃機関の排気マニホールド
PCT/JP2004/016822 WO2005047691A1 (fr) 2003-11-17 2004-11-12 Collecteur d'échappement

Publications (1)

Publication Number Publication Date
EP1686261A1 true EP1686261A1 (fr) 2006-08-02

Family

ID=34587404

Family Applications (1)

Application Number Title Priority Date Filing Date
EP04818504A Withdrawn EP1686261A1 (fr) 2003-11-17 2004-11-12 Collecteur d' chappement

Country Status (6)

Country Link
US (1) US20070079608A1 (fr)
EP (1) EP1686261A1 (fr)
JP (1) JP2005147014A (fr)
KR (1) KR20060069876A (fr)
CN (1) CN1875185A (fr)
WO (1) WO2005047691A1 (fr)

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US9255506B2 (en) * 2013-03-15 2016-02-09 Rail Gas Technologies Locomotive natural gas storage and transfer system
CN106762194A (zh) * 2017-01-24 2017-05-31 李斯特技术中心（上海）有限公司 一种自然吸气发动机的排气通道

Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB158363A (en) 1919-11-04 1921-02-04 Gen Electric Improvements in and relating to electric resistance units
DE3121341A1 (de) 1981-05-29 1982-12-30 M.A.N. Maschinenfabrik Augsburg-Nürnberg AG, 8900 Augsburg "abgasleitungssystem zwischen einer nach dem stauprinzip aufgeladenen, mehrzylindrigen brennkraftmaschine und einem abgasturbolader"
JPS591833U (ja) 1982-06-28 1984-01-07 日産ディーゼル工業株式会社 内燃機関の過給装置
JPH0256820U (fr) 1988-10-19 1990-04-24
JPH0256821U (fr) 1988-10-19 1990-04-24
US5069036A (en) 1988-12-14 1991-12-03 Kloeckner-Humboldt-Deutz Ag Exhaust gas line system for a supercharged internal combustion engine
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

Family Cites Families (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2003485A (en) * 1931-07-11 1935-06-04 Cooper Bessemer Corp Exhaust manifold and connection
US2165360A (en) * 1938-01-10 1939-07-11 Ethyl Gasoline Corp Supercharger system for motor vehicles
US3491534A (en) * 1968-04-24 1970-01-27 Trans Dapt Of California Inc Exhaust manifold
US3457904A (en) * 1968-08-05 1969-07-29 Charles G Roberts Internal combustion engine with improved intake and exhaust
FR2378178A1 (fr) * 1977-01-24 1978-08-18 Semt Procede et dispositif d'amenagement de l'ecoulement des gaz dans un collecteur d'echappement d'un moteur a combustion interne
JPS6070753U (ja) * 1983-10-24 1985-05-18 株式会社新潟鐵工所 内燃機関のシリンダヘツド
US4644747A (en) * 1986-02-10 1987-02-24 General Motors Corporation Low-stress shielded exhaust passage assemblies
JPH11280470A (ja) * 1998-03-25 1999-10-12 Suzuki Motor Corp 排気マニホルド形状

Patent Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB158363A (en) 1919-11-04 1921-02-04 Gen Electric Improvements in and relating to electric resistance units
DE3121341A1 (de) 1981-05-29 1982-12-30 M.A.N. Maschinenfabrik Augsburg-Nürnberg AG, 8900 Augsburg "abgasleitungssystem zwischen einer nach dem stauprinzip aufgeladenen, mehrzylindrigen brennkraftmaschine und einem abgasturbolader"
JPS591833U (ja) 1982-06-28 1984-01-07 日産ディーゼル工業株式会社 内燃機関の過給装置
JPH0256820U (fr) 1988-10-19 1990-04-24
JPH0256821U (fr) 1988-10-19 1990-04-24
US5069036A (en) 1988-12-14 1991-12-03 Kloeckner-Humboldt-Deutz Ag Exhaust gas line system for a supercharged internal combustion engine
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

Also Published As

Publication number Publication date
JP2005147014A (ja) 2005-06-09
US20070079608A1 (en) 2007-04-12
KR20060069876A (ko) 2006-06-22
CN1875185A (zh) 2006-12-06
WO2005047691A1 (fr) 2005-05-26

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