EP0625631B1 - Verbesserter Drehschieber - Google Patents

Verbesserter Drehschieber Download PDF

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Publication number
EP0625631B1
EP0625631B1 EP94400922A EP94400922A EP0625631B1 EP 0625631 B1 EP0625631 B1 EP 0625631B1 EP 94400922 A EP94400922 A EP 94400922A EP 94400922 A EP94400922 A EP 94400922A EP 0625631 B1 EP0625631 B1 EP 0625631B1
Authority
EP
European Patent Office
Prior art keywords
valve
passage
fluid
rotary 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
EP94400922A
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English (en)
French (fr)
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EP0625631A1 (de
Inventor
Stephen Glover
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.)
IFP Energies Nouvelles IFPEN
Original Assignee
IFP Energies Nouvelles IFPEN
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Publication date
Application filed by IFP Energies Nouvelles IFPEN filed Critical IFP Energies Nouvelles IFPEN
Publication of EP0625631A1 publication Critical patent/EP0625631A1/de
Application granted granted Critical
Publication of EP0625631B1 publication Critical patent/EP0625631B1/de
Anticipated expiration legal-status Critical
Expired - Lifetime 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
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L7/00—Rotary or oscillatory slide valve-gear or valve arrangements
    • F01L7/02—Rotary or oscillatory slide valve-gear or valve arrangements with cylindrical, sleeve, or part-annularly shaped valves
    • 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
    • F02B75/00—Other engines
    • F02B75/02—Engines characterised by their cycles, e.g. six-stroke
    • F02B2075/022—Engines characterised by their cycles, e.g. six-stroke having less than six strokes per cycle
    • F02B2075/027—Engines characterised by their cycles, e.g. six-stroke having less than six strokes per cycle four

Definitions

  • the present invention relates to a rotary valve for transferring a fluid between a fluid source and a combustion chamber of an internal combustion engine, comprising at least one substantially cylindrical surface and a lateral flank.
  • the present invention relates more particularly to a rotary valve for controlling the admission of gas, in particular of an air-fuel mixture into a combustion chamber of an engine, comprising an intrinsic sealing system.
  • the present invention applies to two-stroke or four-stroke internal combustion engines having one or more cylinders supplied by a gas, in particular an air-fuel mixture.
  • the distribution of a fuel mixture into the combustion chamber can be carried out, in a known manner, by parts driven by a reciprocating movement such as valves.
  • the applicant has protected, in French patent application FR-2,655,653 a system of this type.
  • the performance of the engine can be limited by the injection systems with valves, in particular with regard to the control of the beginning and the end of the injection and the section of passage of the carburetted air (oscillation problems ).
  • the bushels thus disclosed have an axis of rotation situated in a plane perpendicular to the axis of the cylinder, are pierced with a transverse channel for communicating the intake duct and the combustion chamber and are connected to means d drive allowing them to rotate as a function of the rotation speed of the engine crankshaft.
  • Sealing devices are sometimes provided for this purpose, either upstream or downstream of each plug, or in both places.
  • Patent application FR-2,559,208 relates to a plug for controlling the exhaust and / or the admission of gas from and / or to a combustion chamber to which one or more sealing members is applied.
  • the improvement envisaged in this prior art consists of lubrication and cooling of the contact surface between the sealing member (s) and the plug.
  • this plug comprises at least one flow channel of said fluid having an inlet orifice and an outlet orifice, the inlet orifice belongs to said lateral surface of the plug and is placed at a non-zero distance from l the axis of rotation of the plug while the outlet orifice belongs to the cylindrical surface of said plug and is offset radially relative to the inlet orifice.
  • the flow channel disclosed by this prior art comprises an intrinsic fuel trapping means consisting of an elbow formed by said channel and capable of retaining said fuel under the effect of the centrifugal force created by the rotation of the plug.
  • the present invention relates to an improvement made to the latter type of plug.
  • the present invention relates to a rotary plug with intrinsic sealing which also allows better heat exchange with the surrounding elements.
  • the plug with intrinsic tightness according to the prior art has hot zones in which thermal stresses develop which can cause deformations of the plug.
  • the optimization of the heat exchange obtained according to the invention therefore not only makes it possible to reduce the thermal stresses but also to take advantage of the heating of certain zones to heat the fuel present near the zone (s) hot.
  • This heating by creating a vaporization of the fuel, allows a better preparation of the fuel mixture. This mixture is thus partially homogenized before it is introduced into the combustion chamber.
  • a substantially cylindrical rotary plug intended for the admission of a fluid into a combustion chamber of an internal combustion engine, comprising at least one internal channel bent by flow of said fluid, each channel having an inlet orifice situated on the lateral flank of said plug and an outlet orifice belonging to the cylindrical surface of said plug, the thickness of the wall of the plug between the external face of the channel and the outside bushel being very weak at the elbow.
  • At least one of the outlet orifices of at least one of said internal channels and at least one elbow belong to the same cross section of the plug.
  • At least one of said elbows of at least one of said channels is placed in such a way that its upper surface faces the inlet opening of the cylinder head during the combustion phase.
  • the profile of the channel is such that the mixture first crosses the plug substantially longitudinally to exit in a substantially radial direction.
  • the channel successively has two bends, the first to reverse the direction of the substantially longitudinal flow, the second bend intended to have a radial flow at the outlet.
  • the rotary plug has two channels arranged symmetrically with respect to an axial plane.
  • the zone of the channel located near the entrance of the channel has at least one strongly inclined face in order to effectively direct the mixture inside the bushel.
  • Figure 1 shows an exploded perspective example of a rotary valve according to the invention.
  • the plug according to the invention comprises two identical channels, arranged symmetrically with respect to an axial plane of the plug.
  • Each channel may comprise, in known manner, an inlet orifice 2 of the mixture, belonging to the lateral surface and an outlet orifice 3 forming part of the cylindrical surface of the plug.
  • the channel is substantially oriented parallel to the longitudinal axis.
  • the channel is preferably oriented radially.
  • Each channel advantageously has at least one bend 4, the thickness of the wall at the bend being relatively small.
  • the elbow has a concavity turned towards the outside of the plug so as to form, under the effect of centrifugal force, a retention pocket 20 for the component (s) heavier (s) of the mixture .
  • FIG. 2 which illustrates a section located near the inlet of the plug, two channels 1 and 1 ′ appear in the form of a portion of the crown and arranged symmetrically with respect to the axial plane ⁇ 2 .
  • FIG. 3 is a section little different from that of FIG. 2.
  • the plane of symmetry a3 has turned slightly with respect to the plane of symmetry ⁇ 2.
  • Each channel is therefore twisted between these two cuts.
  • One of the faces 11, 11 'of each channel has not changed orientation while the other face 12, 12' defines a smaller opening angle. Therefore, between sections A and B, the area of each defined channel by faces 12 and 12 'is strongly inclined. This characteristic makes it possible to better direct the fluid inside each channel.
  • Figure 5 which corresponds to a section close to the bottom of each channel, looks like Figure 4. The following comments are valid for each of these figures.
  • each channel consists of a narrowing of the pocket 20, 20' to lead to the zone 40, 40 'of substantially tubular outlet.
  • the axis of the tubular zone 40, 40 ' is preferably radial in order to promote the speed of the fluid leaving.
  • the flow of the fluid through the channel according to the invention is therefore the following.
  • the fluid enters each channel through the inlet orifice 2 located on the lateral flank of the plug, and thanks to the inclination mentioned above, it is rapidly directed towards the interior of the channel; the fluid then travels along a path substantially parallel to the longitudinal axis of the plug, the thickness of the wall of the channel becoming smaller as the penetration into the plug.
  • outlet zone 40, 40 'of the channel and the retention pocket 20, 20' are preferably located longitudinally at the same level of the plug, allows the retention pocket to face a certain phase. of the operating cycle, at the inlet, that is to say at the combustion chamber.
  • the direction of rotation as shown in FIGS. 1 to 5 is an example according to which the outlet orifice 3 of a channel comes first opposite the inlet orifice of the combustion chamber, then the pocket 20 of the same channel passes in front of this same orifice in the direction of rotation indicated in FIGS. 1 to 5.
  • the fuel mixture is first injected into the combustion chamber (intake phase), then a few degrees crankshaft later, the pocket 20 comes opposite the intake orifice. At this time combustion takes place (or has just occurred) so that a large mass of energy is released from the combustion chamber. Part of this energy can therefore be transmitted to the pocket 20; the transmission is all the more important as the wall thickness of the plug is thin in this zone.
  • the therms are thus advantageously captured by the fuel so that the wall 21 of the plug is never subjected to overheating liable to degrade it.
  • the plug rotates in the opposite direction to that indicated in FIGS. 1 to 5.
  • the pocket 20 'of the other channel 1' comes opposite the intake orifice during combustion.
  • This other implementation of the invention allows more time to introduce the fuel into the plug if one wishes to benefit from the preheating effect of the fuel, the aid for vaporization of the fuel and the cooling of the wall. .
  • FIGS. 6 to 9 Another embodiment of the invention, illustrated by FIGS. 6 to 9 also makes it possible to obtain the characteristics set out above.
  • FIG. 6 schematically represents the geometry of the channels 1, 1 ′ and their positioning in a plug according to another embodiment of the invention.
  • each channel which here describes a bend 25 in the form of a hairpin which creates a change in the direction of circulation of the fluid.
  • a connection zone 35 is also provided between the elbow 25 and the radial outlet zone 40.
  • each channel 1 The flow of the fluid in each channel 1 is first substantially longitudinal, then a reversal of direction takes place before the radially oriented outlet.
  • Figures 7 and 8 show the change in geometry from input A 'to level B' in Figure 6. This change will not be further discussed since already explained for the previous embodiment.
  • Figure 9 shows a cross section along C 'of Figure 6. It appears that the pocket 20, the radial outlet area 40 and the outlet orifice 3 belong to the same cross section.
  • FIG. 10 concerning the section D ′ rather shows the bottom 25, 25 ′ of each channel, bottom in the form of a hairpin.
  • This geometry will preferably be adopted when better aerodynamics of the internal channel and / or better flow are sought.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Taps Or Cocks (AREA)
  • Valve-Gear Or Valve Arrangements (AREA)
  • Fuel-Injection Apparatus (AREA)
  • Sliding Valves (AREA)
  • Cylinder Crankcases Of Internal Combustion Engines (AREA)

Claims (6)

  1. Im wesentlichen zylindrischer Drehschieber, der zum Einlaß eines Fluids in eine Brennkammer eines Motors mit innerer Verbrennung bestimmt ist, wenigstens einen gekrümmten inneren Strömungskanal (1, 1') dieses Fluids umfassend, wobei jeder Kanal eine Eintrittsöffnung (2, 2'), die auf der Seitenflanke dieses Schiebers angeordnet ist, eine Austrittsöffnung (3, 3'), die zur Zylinderfläche dieses Schiebers gehört und einen Krümmer (20, 20') hat, der dazu bestimmt ist, die schwersten Elemente des Fluids unter dem Einfluß der Zentrifugalkraft zurückzuhalten, wobei die Dicke (21, 21') der Wandung des Schiebers zwischen der Außenfläche des Kanals und dem Äußeren des Schiebers relativ gering in Höhe dieses Krümmers (20, 20') ist, dadurch gekennzeichnet, daß wenigstens eine der Austrittsöffnungen (3, 3') von wenigstens einem dieser Kanäle und wenigstens einer dieser Krümmer (20, 20') zu ein und dem gleichen Querschnitt des Schiebers gehören.
  2. Drehschieber nach Anspruch 1, dadurch gekennzeichnet, daß wenigstens einer dieser Krümmer (20, 20') wenigstens eines dieser Kanäle derart angeordnet ist, daß seine Saugseite gegenüber der Einlaßöffnung des Zylinderdeckels während der Verbrennungsphase sich befindet.
  3. Drehschieber nach einem der Ansprüche 1 oder 2, dadurch gekennzeichnet, daß das Profil jedes Kanals (1, 1') derart ist, daß das Fluid zunächst den Schieber im wesentlichen in Längsrichtung durchsetzt, um gemäß einer im wesentlichen radialen Richtung auszutreten.
  4. Drehschieber nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, daß jeder Kanal aufeinanderfolgend zwei Krümmer (25, 35) aufweist, den ersten (25), um den im wesentlichen longitudinalen Strömungssinn umzukehren, den zweiten Krümmer (35), der dazu bestimmt ist, eine im wesentlichen radiale Strömung am Austritt zu erhalten.
  5. Drehschieber nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, daß der Drehschieber zwei Kanäle (1, 1') aufweist, die symmetrisch bezogen auf eine Axialebene angeordnet sind.
  6. Drehschieber nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, daß die benachbart dem Eintritt (3) des Kanals angeordnete Zone des Kanals wenigstens eine stark geneigte Fläche aufweist, um wirksam das Gemisch in das Innere des Schiebers zu leiten.
EP94400922A 1993-05-21 1994-04-28 Verbesserter Drehschieber Expired - Lifetime EP0625631B1 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
FR9306278 1993-05-21
FR9306278A FR2705402B1 (fr) 1993-05-21 1993-05-21 Boisseau rotatif amélioré.

Publications (2)

Publication Number Publication Date
EP0625631A1 EP0625631A1 (de) 1994-11-23
EP0625631B1 true EP0625631B1 (de) 1996-07-17

Family

ID=9447458

Family Applications (1)

Application Number Title Priority Date Filing Date
EP94400922A Expired - Lifetime EP0625631B1 (de) 1993-05-21 1994-04-28 Verbesserter Drehschieber

Country Status (7)

Country Link
US (1) US5437252A (de)
EP (1) EP0625631B1 (de)
JP (1) JPH074216A (de)
AT (1) ATE140514T1 (de)
DE (1) DE69400305T2 (de)
FR (1) FR2705402B1 (de)
TW (1) TW253926B (de)

Families Citing this family (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5839614A (en) 1991-12-06 1998-11-24 Aptar Group, Inc. Dispensing package
US5582140A (en) * 1995-05-04 1996-12-10 Strieber; Louis C. Rotatable timed mechanism for feeding vaporous fluid to a combustion cylinder
US6125819A (en) * 1995-08-08 2000-10-03 Strieber; Louis Charles Rotating piston engine with variable effective compression stroke
US5623901A (en) * 1996-08-14 1997-04-29 Hartzell; Mark E. Time twister cylinder head for use in internal combustion engines
US5967108A (en) 1996-09-11 1999-10-19 Kutlucinar; Iskender Rotary valve system
US6530504B2 (en) 2001-03-02 2003-03-11 Seaquist Closures Foreign, Inc. Multiple orifice valve
EP1709304A1 (de) * 2004-01-28 2006-10-11 Bishop Innovation Pty. Limited Öffnungsanordnung für einen drehschiebermotor
US7371265B2 (en) * 2005-03-25 2008-05-13 Gerfast Sten R Continuous hydrogen and alcohol generator from coal
CN110975503B (zh) * 2019-12-31 2021-11-23 巫溪县绿荫环保有限公司 双通道漆雾净化设备

Family Cites Families (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR456777A (fr) * 1913-04-17 1913-09-04 Guillaume Mounier Perfectionnements aux distributeurs rotatifs, plus particulièrement applicables aux moteurs à explosions pour automobiles
GB1478982A (en) * 1973-09-07 1977-07-06 Cross Mfg Co Rotary valves
EP0074174A1 (de) * 1981-08-01 1983-03-16 Richard Furneaux Kinnersly Brennkraftmaschine und Drehschieber dafür
DE3540441A1 (de) * 1985-11-14 1987-05-21 Ficht Gmbh Brennkraftmaschine mit einem drehbaren absperrorgan zur steuerung des gaswechsels
US4739737A (en) * 1986-09-03 1988-04-26 Volkswagen Ag Rotary valve for control of the cylinder charge change of an internal combustion engine
US5052349A (en) * 1990-07-30 1991-10-01 Terry Buelna Rotary valve for internal combustion engine
US5109814A (en) * 1991-05-10 1992-05-05 Coates George J Spherical rotary valve
FR2679960A1 (fr) * 1991-08-02 1993-02-05 Inst Francais Du Petrole Boisseau rotatif et utilisation dudit boisseau pour le transfert d'un fluide vers une chambre de combustion d'un moteur a combustion interne.
DE4125846A1 (de) * 1991-08-03 1993-02-04 Fichtel & Sachs Ag Bandbremse fuer aggregate, die mit verbrennungsmotoren angetrieben werden
US5152259A (en) * 1991-09-05 1992-10-06 Bell Darrell W Cylinder head for internal combustion engine

Also Published As

Publication number Publication date
DE69400305T2 (de) 1996-12-05
FR2705402B1 (fr) 1995-07-13
ATE140514T1 (de) 1996-08-15
TW253926B (de) 1995-08-11
DE69400305D1 (de) 1996-08-22
EP0625631A1 (de) 1994-11-23
JPH074216A (ja) 1995-01-10
US5437252A (en) 1995-08-01
FR2705402A1 (fr) 1994-11-25

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