EP0410132B1 - Flow channel - Google Patents

Flow channel Download PDF

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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
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EP
European Patent Office
Prior art keywords
flow
cross
intake
valve
channel
Prior art date
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Expired - Lifetime
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EP90111537A
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German (de)
French (fr)
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EP0410132A1 (en
Inventor
Winfried Dipl.-Ing. Distelrath (Fh)
Roland-Detlev Dipl.-Ing. Zebli
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Dr Ing HCF Porsche AG
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Dr Ing HCF Porsche AG
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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.

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  • 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)

Description

Die Erfindung betrifft einen Strömungskanal nach dem Oberbegriff des Patentanspruchs 1.The invention relates to a flow channel according to the preamble of patent claim 1.

Bei einem bekannten Strömungskanal - DE-OS 35 08 763 - ist das Strömungsprofil so gestaltet, daß es sich zum Ventilsitzring hin kontinuierlich verjüngt. Diese Gestaltung geht auf die physikalische Grundlage zurück, daß die geringsten Verluste in einem Strömungskanal bei ungehinderter Strömung dann auftreten, wenn der Querschnitt des Strömungskanals kontinuierlich verengt bzw. die Geschwindigkeit des Gasstroms kontinuierlich erhöht wird. Bei einem Strömungskanal mit einem Ventil ist aber eine ungehinderte Strömung nicht realisierbar, weil besagtes Ventil einen erheblichen Strömungswiderstand verursacht, der im Zusammenhang mit einem derartigen Strömungsprofil einen optimierten Betrieb einer Brennkraftmaschine beeinträchtigt.In a known flow channel - DE-OS 35 08 763 - the flow profile is designed so that it tapers continuously towards the valve seat ring. This design is based on the physical basis that the lowest losses occur in a flow channel with unimpeded flow when the cross section of the flow channel is continuously narrowed or the speed of the gas flow is continuously increased. In the case of a flow channel with a valve, however, an unimpeded flow cannot be achieved because said valve causes considerable flow resistance, which in connection with such a flow profile impairs optimized operation of an internal combustion engine.

Außerdem ist ein Einlaßkanal für eine Brennkraftmaschine bekannt, DE-D 1.476.080, der über seine Länge eine ungleichmäßige Verjüngung aufweist, weshalb mit dieser Ausgestaltung ein optimierter Strömungsgeschwindigkeitsverlauf des Gasstroms nicht erreicht wird. Kurz vor dem Ventilsitz weist dieser Einlaßkanal eine Erweiterung seines Querschittes auf. In einem solchen Einlaßkanal, der dem Oberbegriff von Anspruch 1 entspricht, ist aber die Erhöhung sowie danach die Verringerung der Luftgeschwindigkeit nicht gleichmäßig.In addition, 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.

Aufgabe der Erfindung ist es, einen Ansaugkanal für eine Brennkraftmaschine so auszubilden, daß die Strömungsgeschwindigkeit des Gasstroms dem durch das Einlaßventil hervorgerufenen Widerstand in Richtung bessere Brennkraftmaschinen-Betriebseigenschaften Rechnung trägt.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.

Diese Aufgabe wird durch die kennzeichnenden Merkmale des Patentanspruchs 1 gelöst. Weitere, die Erfindung ausgestaltende Merkmale sind in den Unteransprüchen enthalten.This object is achieved by the characterizing features of patent claim 1. Further features embodying the invention are contained in the subclaims.

Die mit der Erfindung hauptsächlich erzielten Vorteile sind darin zu sehen, daß der Gasstrom in den beiden Kanalabschnitten der Saugrohranlage und dem Zylinderkopf einen optimierten Strömungsgeschwindigkeitsverlauf aufweist, wodurch der Gasstrom bis zum Querschnittsübergangsbereich beschleunigt und danach verzögert wird. Letzteres bewirkt eine Reduktion des Strömungswiderstands, wodurch der Liefergrad der Brennkraftmaschine verbessert wird. Dies wiederum wirkt sich leistungserhöhend und verbrauchsreduzierend aus.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.

In der Zeichnung sind Ausführungsbeispiele der Erfindung dargestellt, die nachstehend näher beschrieben sind.In the drawing, embodiments of the invention are shown, which are described in more detail below.

Es zeigt

Fig. 1
einen Teilquerschnitt einer Brennkraftmaschine im Bereich einer Ansauganlage und eines Zylinderkopfs,
Fig. 2
ein Diagramm, aus dem der Verlauf der Strömungsgeschwindigkeit eines Gasstroms in einer Ansauganlage hervorgeht,
Fig. 3
eine schematische Ansicht in Pfeilrichtung A der Fig. 1,
Fig. 4
eine Ansicht entsprechend Fig. 3 einer weiteren Ausführungsform.
It shows
Fig. 1
a partial cross section of an internal combustion engine in the area of an intake system and a cylinder head,
Fig. 2
1 shows a diagram from which the course of the flow velocity of a gas stream in an intake system emerges,
Fig. 3
2 shows a schematic view in the direction of arrow A in FIG. 1,
Fig. 4
a view corresponding to FIG. 3 of a further embodiment.

Die Brennkraftmaschine 1 umfaßt in dem dargestellten Bereich eine Ansauganlage 2 und einen Zylinderkopf 3. Die Ansauganlage 2 ist bei 4 mit einem nicht näher dargestellten Sammler versehen und schließt mit einem Befestigungsflansch 5 an den Zylinderkopf 3 an. Zwischen Ansauganlage 2 und Zylinderkopf 3 erstreckt sich ein Ansaugkanal 6, der in einen ersten Kanalabschnitt 7 - Länge ca. 100 bis 120 mm - in der Ansauganlage 2 und einen zweiten Kanalabschnitt 8 im Zylinderkopf 3 gegliedert ist.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.

Ein von einer nicht gezeigten Nockenwelle betätigtes Ventil 9 ist am Ende des Ansaugkanals 6 vorgesehen, das einen Ventilschaft 10 und einen Ventilteller 11 aufweist; der Ventilteller arbeitet mit einem Ventilsitz 12 zusammen. Der Ventilschaft 10 ist axialbeweglich in einer Ventilführung 13 angeordnet, die ihrerseits in einer Bohrung 14 im Zylinderkopf 3 ruht. Der Ventilschaft 10 ist örtlich, und zwar im Bereich einer Krümmung 15 des Kanalabschnitts 8, einem Gasstrom ausgesetzt, der durch das Ventil 9 gesteuert wird. Ist das Ventil 9 geöffnet, gelangt der Gasstrom in einen Brennraum 16.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.

Der Ansaugkanal 6 mit kreisrundem Querschnitt weist folgendes Strömungsprofil auf: über eine wesentliche Teillänge des Ansaugkanals 6 verjüngt sich sein Querschnitt gleichmäßig konisch, und zwar stromabwärts - Strömungsrichtung S - bis zu einem Querschnittsübergangsbereich 17, der - in Strömungsrichtung S gesehen - relativ kurz vor dem Ventilschaft 10 liegt.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.

Nach dem Querschnittsübergangsbereich 17 erweitert sich ebenfalls gleichmäßig und konisch der Ansaugkanal 6. Die Querschnittsverjüngung wird durch Q1>Q2 und die Querschnittserweiterung durch Q3<Q4 definiert. Die Querschnittsverjüngung Q1>Q2 beträgtje nach Art und Größe der Brennkraftmaschine zwischen 18 und 24 % betragen.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.

Gemäß Fig. 2 ist der Verlauf der Strömungsgeschwindigkeit des Gasstroms im Ansaugkanal 6 dargestellt. Dabei ist auf der Ordinate die Geschwindigkeit in m/s und auf der Abszisse die Länge des Ansaugkanals in mm aufgetragen. Die durchgezogene Linie 18 gibt die kontinuierliche knickfreie Beschleunigung BK bis zum Querschnittsübergangsbereich 17 und danach die kontinuierliche Verzögerung VK des Gasstroms wieder. Die strichpunktierte Linie 19 gibt den Verlauf der Strömungsgeschwindigkeit des Gasstroms nach dem Stand der Technik wieder. Diese Gegenüberstellung macht deutlich, daß die Linie 19 einen Knick 20 im Strömungsprofil aufweist und der Gasstrom bis kurz vor dem engsten Querschnitt im Bereich des Ventilsitzringes beschleunigt wird. Das schraffierte Dreieck 21 stellt die Reduktion des Strömungswiderstands dar; bei 22 hat der Gasstrom Ventilspaltgeschwindigkeit.2, 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.

Aus Fig. 3 gehen zwei parallel zueinander verlaufende Ansaugkanäle 23, 24 hervor. Beide Ansaugkanäle 23, 24 sind über ihre gesamte Länge im wesentlichen getrennt voneinander und konisch ausgebildet. Außerdem weisen sie prinzipgleiche Strömungsprofile auf. Diese Ausführung eignet sich für eine Brennkraftmaschine mit wenigstens zwei Einlaßventilen pro Zylinder, die im Zylinderkopf angeordnet und von beispielsweise zwei Nockenwellen betätigt werden.3 shows two 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.

In Fig. 4 ist ebenfalls ein Ansaugkanal 25 für eine Brennkraftmaschine mit zwei Einlaßventilen pro Zylinder dargestellt. Der Ansaugkanal 25 weist tendentiell ein Strömungsprofil wie in Fig. 2 dargestellt auf. Jedoch ist er in Strömungsrichtung S gesehen zunächst ein Einzelkanal 26, der dann durch eine Trennwand 27 in zwei getrennte Kanalbereiche 28, 29 aufgeteilt ist, die Hosenform aufweisend zu den Einlaßventilen führen. Die Trennwand 27 beginnt stromabwärts - Strömungsrichtung S - vor dem Ventilschaft 10 und ist als eine Art Strömungskörper mit symmetrisch stromlinienförmigem Profil ausgebildet. Er beginnt mit einer dem Gasstrom entgegengesetzten gerundeten Spitze SKS und erweitert sich kontinuierlich beiderseits einer Quermittelebene C-C auf eine maximale Breite SKmax, von wo aus sich das Profil auf eine reduzierte Breite SKred verjüngt. Der Strömungskörper, namentlich die Zusammenhänge SKmax und SKred können unter Berücksichtigung konstruktiver Gegebenheiten und minimaler Reibungs- und Druckverluste empirisch und/oder rechnerisch definiert werden. Schließlich sind bei dieser Ansaugkanalgestaltung Querschnittsübergangsbereiche 30, 31 in den Kanalbereichen 28, 29 vorgesehen. Bis zu den Querschnittsübergangsbereichen 30, 31 die stromabwärts - Strömungsrichtung S - relativ kurz vor dem Ventilschaft liegen, wird der Gasstrom beschleunigt und danach verzögert: letzteres wird durch die gleichmäßige Querschnittserweiterung der Kanalbereiche 28, 29 nach diesen Querschnittsübergangsbereichen erzielt.4 also shows an 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. Finally, with this intake duct design, 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.

Claims (8)

  1. A flow channel in an intake device and a cylinder head of an internal-combustion engine, wherein a gas flow is controlled by means of a valve which comprises a valve disc co-operating with a valve seat and a valve stem connected thereto and mounted so as to be axially movable in a valve guide, the valve stem being arranged adjacent to the valve-seat ring in the intake port in such a way that it is subjected to the gas flow, characterized in that the intake port (6), divided into a first portion (7) in the intake device (2) and a second portion (8) in the cylinder head (3), is provided downstream - in the direction of flow S - with a defined flow profile, the flow channel having a uniform cross-sectional narrowing (Q 1 > Q 2) as far as a cross-sectional area (17) situated upstream of the valve stem (10) and then a uniform cross-sectional widening (Q 3 < Q 4), and the velocity profile upstream of the cross-section transition region (17) being defined by a straight line (BK) and downstream of the cross-section transition region (17) by a second straight line (VK).
  2. A flow channel according to Claim 1, characterized in that the cross-sectional narrowing of the two portions (7, 8) of the port is inwardly tapered as far as a cross-sectional area (17).
  3. A flow channel according to Claim 2, characterized in that the cross-sectional narrowing (Q 1 > Q 2) is between 18% and 24%.
  4. A flow channel according to one or more of the preceding Claims, in conjunction with an internal-combustion engine, the cylinder head of which comprises at least two intake valves per cylinder, the said intake valves controlling the gas flow in the respective separate intake port between the intake device and the cylinder head, characterized in that the intake ports (20, 21) have the same flow profiles.
  5. A flow channel according to one or more of the preceding Claims, in conjunction with an internal-combustion engine, the cylinder head of which comprises at least two intake valves per cylinder, the said intake valves controlling the gas flow in the intake port between the intake device and the cylinder head, wherein downstream - in the direction of flow S - the intake port is first a single channel and is then divided into two separate channel areas by a separating wall starting upstream of the valve stems, characterized in that the flow profile extends over the single channel (26) and the channel areas (28, 29).
  6. A flow channel according to Claim 5, characterized in that the separating wall (27) is formed as a flow member with a symmetrically streamlined profile between the channel areas (28, 29).
  7. A flow channel according to Claim 6, characterized in that starting from a rounded tip Sk s opposite the gas flow the flow member is widened over a first section (Skmax), to which is adjacent a second inwardly tapered channel portion (Skred).
  8. A method of controlling the velocity of the gas flow in the flow channel according to Claim 1, characterized in that the velocity of the gas flow in the first channel portion (7) and in the second channel portion (8) is increased in a constant linear manner and is then reduced in a constant linear manner.
EP90111537A 1989-07-25 1990-06-19 Flow channel Expired - Lifetime EP0410132B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE3924544 1989-07-25
DE3924544A DE3924544A1 (en) 1989-07-25 1989-07-25 FLOW CHANNEL

Publications (2)

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

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EP90111537A Expired - Lifetime EP0410132B1 (en) 1989-07-25 1990-06-19 Flow channel

Country Status (6)

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

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3940838C1 (en) * 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
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ES2047203T3 (en) 1994-02-16
JPH03130528A (en) 1991-06-04
RU1796039C (en) 1993-02-15
EP0410132A1 (en) 1991-01-30
DE3924544A1 (en) 1991-02-07
US5050566A (en) 1991-09-24
DE59003768D1 (en) 1994-01-20
DE3924544C2 (en) 1991-08-01

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