EP0410132B1 - Strömungskanal - Google Patents

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Publication number
EP0410132B1
EP0410132B1 EP90111537A EP90111537A EP0410132B1 EP 0410132 B1 EP0410132 B1 EP 0410132B1 EP 90111537 A EP90111537 A EP 90111537A EP 90111537 A EP90111537 A EP 90111537A EP 0410132 B1 EP0410132 B1 EP 0410132B1
Authority
EP
European Patent Office
Prior art keywords
flow
cross
intake
valve
channel
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.)
Expired - Lifetime
Application number
EP90111537A
Other languages
German (de)
English (en)
French (fr)
Other versions
EP0410132A1 (de
Inventor
Winfried Dipl.-Ing. Distelrath (Fh)
Roland-Detlev Dipl.-Ing. Zebli
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.)
Dr Ing HCF Porsche AG
Original Assignee
Dr Ing HCF Porsche AG
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
Family has litigation
First worldwide family litigation filed litigation Critical https://patents.darts-ip.com/?family=6385764&utm_source=google_patent&utm_medium=platform_link&utm_campaign=public_patent_search&patent=EP0410132(B1) "Global patent litigation dataset” by Darts-ip is licensed under a Creative Commons Attribution 4.0 International License.
Application filed by Dr Ing HCF Porsche AG filed Critical Dr Ing HCF Porsche AG
Publication of EP0410132A1 publication Critical patent/EP0410132A1/de
Application granted granted Critical
Publication of EP0410132B1 publication Critical patent/EP0410132B1/de
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M35/00—Combustion-air cleaners, air intakes, intake silencers, or induction systems specially adapted for, or arranged on, internal-combustion engines
    • F02M35/10—Air intakes; Induction systems
    • F02M35/104—Intake manifolds
    • F02M35/108—Intake manifolds with primary and secondary intake passages
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M35/00—Combustion-air cleaners, air intakes, intake silencers, or induction systems specially adapted for, or arranged on, internal-combustion engines
    • F02M35/10—Air intakes; Induction systems
    • F02M35/10006—Air intakes; Induction systems characterised by the position of elements of the air intake system in direction of the air intake flow, i.e. between ambient air inlet and supply to the combustion chamber
    • F02M35/10072—Intake runners
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M35/00—Combustion-air cleaners, air intakes, intake silencers, or induction systems specially adapted for, or arranged on, internal-combustion engines
    • F02M35/10—Air intakes; Induction systems
    • F02M35/10091—Air intakes; Induction systems characterised by details of intake ducts: shapes; connections; arrangements
    • F02M35/10098—Straight ducts
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M35/00—Combustion-air cleaners, air intakes, intake silencers, or induction systems specially adapted for, or arranged on, internal-combustion engines
    • F02M35/10—Air intakes; Induction systems
    • F02M35/10091—Air intakes; Induction systems characterised by details of intake ducts: shapes; connections; arrangements
    • F02M35/10118—Air intakes; Induction systems characterised by details of intake ducts: shapes; connections; arrangements with variable cross-sections of intake ducts along their length; Venturis; Diffusers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M35/00—Combustion-air cleaners, air intakes, intake silencers, or induction systems specially adapted for, or arranged on, internal-combustion engines
    • F02M35/10—Air intakes; Induction systems
    • F02M35/104—Intake manifolds
    • F02M35/108—Intake manifolds with primary and secondary intake passages
    • F02M35/1085—Intake manifolds with primary and secondary intake passages the combustion chamber having multiple intake valves

Definitions

  • the invention relates to a flow channel according to the preamble of patent claim 1.
  • an inlet duct for an internal combustion engine is known, DE-D 1.476.080, which has an uneven taper over its length, which is why an optimized flow velocity profile of the gas flow is not achieved with this embodiment. Shortly before the valve seat, this inlet duct has an extension of its cross section. In such an inlet duct, which corresponds to the preamble of claim 1, the increase and then the decrease in air speed is not uniform.
  • the object of the invention is to design an intake duct for an internal combustion engine in such a way that the flow velocity of the gas stream takes into account the resistance caused by the inlet valve in the direction of better internal combustion engine operating properties.
  • the main advantages achieved by the invention are the fact that the gas flow in the two duct sections of the intake manifold and the cylinder head has an optimized flow rate profile, as a result of which the gas flow is accelerated up to the cross-sectional area and then decelerated.
  • the latter causes a reduction in the flow resistance, which improves the delivery rate of the internal combustion engine. This in turn increases performance and reduces consumption.
  • the internal combustion engine 1 comprises an intake system 2 and a cylinder head 3 in the area shown.
  • the intake system 2 is provided at 4 with a collector (not shown in more detail) and connects to the cylinder head 3 with a fastening flange 5.
  • Extending between intake system 2 and cylinder head 3 is an intake channel 6, which is divided into a first channel section 7 - length approx. 100 to 120 mm - in intake system 2 and a second channel section 8 in cylinder head 3.
  • a valve 9, actuated by a camshaft, not shown, is provided at the end of the intake duct 6 and has a valve stem 10 and a valve disk 11; the valve plate works together with a valve seat 12.
  • the valve stem 10 is axially movable in a valve guide 13, which in turn rests in a bore 14 in the cylinder head 3.
  • the valve stem 10 is exposed locally, specifically in the region of a bend 15 of the channel section 8, to a gas flow which is controlled by the valve 9. If the valve 9 is open, the gas flow enters a combustion chamber 16.
  • the intake duct 6 with a circular cross-section has the following flow profile: over a substantial part of the length of the intake duct 6, its cross-section tapers evenly conically, namely downstream - flow direction S - up to a cross-sectional transition region 17, which - seen in the flow direction S - is relatively short in front of the valve stem 10 lies.
  • the intake duct 6 After the cross-sectional transition area 17, the intake duct 6 also widens uniformly and conically.
  • the cross-sectional taper is defined by Q1> Q2 and the cross-sectional expansion by Q3 ⁇ Q4.
  • the cross-sectional taper Q1> Q2 is between 18 and 24% depending on the type and size of the internal combustion engine.
  • the course of the flow rate of the gas flow in the intake duct 6 is shown.
  • the speed in m / s is plotted on the ordinate and the length of the intake duct in mm on the abscissa.
  • the solid line 18 represents the continuous, kink-free acceleration B K up to the cross-sectional transition region 17 and then the continuous deceleration V K of the gas flow.
  • the dash-dotted line 19 shows the course of the flow velocity of the gas stream according to the prior art. This comparison makes it clear that the line 19 has a kink 20 in the flow profile and the gas flow is accelerated until just before the narrowest cross section in the region of the valve seat ring.
  • the hatched triangle 21 represents the reduction in the flow resistance; at 22 the gas flow has valve gap speed.
  • suction channels 23, 24 running parallel to one another. Both suction channels 23, 24 are substantially separate from one another and conical over their entire length. In addition, they have flow profiles of the same principle.
  • This version is suitable for an internal combustion engine with at least two intake valves per cylinder, which are arranged in the cylinder head and actuated by, for example, two camshafts.
  • the intake duct 25 for an internal combustion engine with two intake valves per cylinder.
  • the intake duct 25 tends to have a flow profile as shown in FIG. 2. However, viewed in the direction of flow S, it is initially a single channel 26, which is then divided by a partition 27 into two separate channel regions 28, 29, which have the shape of trousers and lead to the inlet valves.
  • the partition wall 27 begins downstream - flow direction S - in front of the valve stem 10 and is designed as a type of flow body with a symmetrically streamlined profile. It begins with a rounded tip SK S opposite to the gas flow and expands continuously on both sides Cross center plane CC to a maximum width SK max , from where the profile tapers to a reduced width SK red .
  • the flow body namely the interrelationships between SK max and SK red, can be defined empirically and / or computationally, taking into account structural conditions and minimal friction and pressure losses.
  • cross-sectional transition regions 30, 31 are provided in the duct regions 28, 29. The gas flow is accelerated and then decelerated up to the cross-sectional transition areas 30, 31 downstream - flow direction S - relatively short of the valve stem: the latter is achieved by the uniform cross-sectional expansion of the channel areas 28, 29 after these cross-sectional transition areas.

Landscapes

  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Cylinder Crankcases Of Internal Combustion Engines (AREA)
EP90111537A 1989-07-25 1990-06-19 Strömungskanal Expired - Lifetime EP0410132B1 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE3924544 1989-07-25
DE3924544A DE3924544A1 (de) 1989-07-25 1989-07-25 Stroemungskanal

Publications (2)

Publication Number Publication Date
EP0410132A1 EP0410132A1 (de) 1991-01-30
EP0410132B1 true EP0410132B1 (de) 1993-12-08

Family

ID=6385764

Family Applications (1)

Application Number Title Priority Date Filing Date
EP90111537A Expired - Lifetime EP0410132B1 (de) 1989-07-25 1990-06-19 Strömungskanal

Country Status (6)

Country Link
US (1) US5050566A (enExample)
EP (1) EP0410132B1 (enExample)
JP (1) JPH03130528A (enExample)
DE (2) DE3924544A1 (enExample)
ES (1) ES2047203T3 (enExample)
RU (1) RU1796039C (enExample)

Families Citing this family (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3940838C1 (enExample) * 1989-12-11 1991-06-20 Dr.Ing.H.C. F. Porsche Ag, 7000 Stuttgart, De
US5265568A (en) * 1991-09-27 1993-11-30 Mazda Motor Corporation Intake system for internal combustion engine
JP3517957B2 (ja) * 1994-06-10 2004-04-12 マツダ株式会社 エンジンの吸気ポート構造およびその設定方法
US7200487B2 (en) * 2003-06-30 2007-04-03 Westport Power Inc. System and method for processing an accelerometer signal to assist in combustion quality control in an internal combustion engine
CA2444163C (en) * 2003-10-01 2007-01-09 Westport Research Inc. Method and apparatus for controlling combustion quality of a gaseous-fuelled internal combustion engine
US7444231B2 (en) * 2004-11-18 2008-10-28 Westport Power Inc. Method of mounting an accelerometer on an internal combustion engine and increasing signal-to-noise ratio
DE102005020228B4 (de) * 2005-04-30 2014-08-14 Audi Ag Einlasskanalanordnung in einem Zylinderkopf
JP4657177B2 (ja) 2006-08-29 2011-03-23 本田技研工業株式会社 内燃機関
FR2931207A1 (fr) * 2008-05-14 2009-11-20 Renault Sas Dispositif de transfert de gaz d'admission ou d'echappement
DE102019111421A1 (de) * 2019-05-03 2020-11-05 Man Energy Solutions Se Ladeluftleitung einer Brennkraftmaschine und Brennkraftmaschine

Family Cites Families (21)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB682450A (en) * 1948-08-06 1952-11-12 Fiat Spa Inlet conduit for internal combustion engines
GB881089A (en) * 1958-03-25 1961-11-01 Tatra Np Improvements in inlet ducts for internal combustion engines
DE1476080A1 (de) * 1965-01-05 1969-11-13 Motoren Werke Mannheim Ag Einlasskanal fuer Brennkraftmaschinen,insbesondere Dieselmotoren
CH524763A (de) * 1970-06-05 1972-06-30 Saurer Ag Adolph Zylinderkopf einer Kolbenbrennkraftmaschine mit Lufteinlasskanal
DE2243269C2 (de) * 1972-09-02 1982-04-22 Günter 8543 Hilpoltstein Elsbett Luftzuführungssystem, insbesondere Ansaugleitungssystem
US4069796A (en) * 1976-09-27 1978-01-24 General Motors Corporation Engine manifold with air gap insulator carburetor mounting
US4187823A (en) * 1978-03-03 1980-02-12 Caterpillar Tractor Co. High swirl inlet port
GB1600888A (en) * 1978-05-31 1981-10-21 Ricardo Consulting Engs Ltd Inlet ports in ic engines
GB2056553B (en) * 1979-08-22 1983-04-13 Ricardo Consulting Engs Ltd Directed inlet passages in ic engines
JPS58124019A (ja) * 1982-01-21 1983-07-23 Toyota Motor Corp 吸気２弁式内燃機関
JPS58150025A (ja) * 1982-03-03 1983-09-06 Toyota Motor Corp 内燃機関の吸気通路
US4574751A (en) * 1983-08-19 1986-03-11 Kabushiki Kaisha Toyota Chuo Kenkyusho Inlet port for internal combustion engine
SE443836B (sv) * 1984-05-22 1986-03-10 Saab Scania Ab Cylinderhuvud for forbrenningsmotor
JPS6119632U (ja) * 1984-07-10 1986-02-04 トヨタ自動車株式会社 複吸気弁エンジン
JPS6149120A (ja) * 1984-08-15 1986-03-11 Yamaha Motor Co Ltd ４行程内燃機関
US4719879A (en) * 1984-10-23 1988-01-19 Honda Giken Kogyo Kabushiki Kaisha Intake manifold
JPS61149519A (ja) * 1984-12-21 1986-07-08 Nissan Motor Co Ltd 多気筒内燃機関の吸気路装置
DE3510226A1 (de) * 1985-03-21 1986-10-02 Daimler-Benz Ag, 7000 Stuttgart Einspritzsystem einer brennkraftmaschine
JPH0415937Y2 (enExample) * 1985-10-14 1992-04-09
US4805569A (en) * 1987-02-13 1989-02-21 Mazda Motor Corporation Intake system for an engine
IT1223543B (it) * 1987-12-18 1990-09-19 Alfa Lancia Ind Dispositivo di aspirazione per un motore a c.i. pluricilindrico

Also Published As

Publication number Publication date
EP0410132A1 (de) 1991-01-30
JPH03130528A (ja) 1991-06-04
DE59003768D1 (de) 1994-01-20
DE3924544A1 (de) 1991-02-07
RU1796039C (ru) 1993-02-15
US5050566A (en) 1991-09-24
DE3924544C2 (enExample) 1991-08-01
ES2047203T3 (es) 1994-02-16

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