EP0059047A2 - Culasse de cylindre à tiroir rotatif - Google Patents

Culasse de cylindre à tiroir rotatif Download PDF

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Publication number
EP0059047A2
EP0059047A2 EP82300708A EP82300708A EP0059047A2 EP 0059047 A2 EP0059047 A2 EP 0059047A2 EP 82300708 A EP82300708 A EP 82300708A EP 82300708 A EP82300708 A EP 82300708A EP 0059047 A2 EP0059047 A2 EP 0059047A2
Authority
EP
European Patent Office
Prior art keywords
cylinder head
port
rotary valve
valve
bearing means
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Withdrawn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
EP82300708A
Other languages
German (de)
English (en)
Other versions
EP0059047A3 (fr
Inventor
Fred L. Baldwin
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.)
Individual
Original Assignee
Individual
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 Individual filed Critical Individual
Publication of EP0059047A2 publication Critical patent/EP0059047A2/fr
Publication of EP0059047A3 publication Critical patent/EP0059047A3/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Withdrawn legal-status Critical Current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
    • 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
    • F01L7/026—Rotary or oscillatory slide valve-gear or valve arrangements with cylindrical, sleeve, or part-annularly shaped valves with two or more rotary valves, their rotational axes being parallel, e.g. 4-stroke

Definitions

  • This invention relates to a rotary valve cylinder head for an internal combustion engine.
  • a rotary valve cylinder head for an internal combustion engine comprises a cylinder head body defining a cylindrical region therein and having a dual port combustion chamber disposed adjacent the head end of the cylindrical region, one port being an inlet port and the other port being an exhaust port; a piston reciprocatable within the cylindrical region; and rotary valve devices disposed in the cylinder head body for controlling flow of gas to and from the combustion chamber, characterized in that the rotary valve devices include:- (a) a pair of generally cylindrical rotary valve members each defining a radial passageway extending transversely therethrough for flow of gas, the valve members being substantially parallel to each other on opposite sides of the cylindrical region and each valve member being rotatable to a position in which its respective passageway communicates with the combustion chamber; (b) two bearing means, each disposed between a respective valve member and the cylinder head body; and (c) a separate sealing member received by each bearing means and disposed around a respective one of the two ports between the respective bearing means, and the cylinder head body.
  • a rotary valve cylinder head includes a cylinder head body 10 which is mounted on the crankcase (not shown) of an internal combustion engine of the spark-ignition, four-stroke cycle design.
  • Body 10 defines a cylindrical region which is rigidly sleeved with cylinder 12.
  • Cylinder 12 co-operates with closing surface portion 13 of body 10 so as to define a combustion chamber 14 at the head end thereof, the head end being the uppermost end of the cylindrical region.
  • a piston 16 is reciprocatable in cylinder 12 and is connected in conventional manner by a piston rod 18 to the crankshaft (not shown) of the engine. Piston rod 18 is connected to piston 16 in conventional manner by a wrist pin 20. Piston 16, cylinder 12 and the closing surface portion 13 of body 10 form a variable volume combustion chamber 14 of the engine.
  • the cylinder head body 10 is water-cooled in conventional manner by water jacket compartments 22 in body 10 and surrounding the cylinder 12.
  • Body 10 is provided with an inlet port 24 which communicates with an inlet passage 26 in an intake manifold 28 and leading to a carburetor (not shown) in a conventional manner.
  • Body 10 is also provided with an exhaust port 30 which communicates with an exhaust passage 32 in a suitable exhaust manifold 34.
  • the flow of the air-fuel mixture to the combustion chamber 14 and flow of exhaust gases from the combustion chamber is controlled by rotary valve means.
  • Such rotary valve means comprise a pair of rotary valve members 36 and 38, each of which is configured as a generally cylindrical member.
  • Valve members 36 and 38 are disposed substantially parallel to each other on opposite sides of the cylindrical region. While only a single piston and a single cylinder are disclosed, it is to be understood that by appropriate placement of the flow passageways in each valve member, four or six cylinders can be accommodated by a single pair of valve members.
  • Valve member 36 is rotatably journalled within bearing means formed by a curved sealing screen 39 which is disposed between valve member 36 and surface 40 of body 10.
  • Valve member 38 is rotatably journalled within bearing means formed by a curved sealing screen 41 which is disposed between valve member 36 and surface 42 of body 10.
  • Valve member 36 is provided with a radial passageway 44 extending transversely therethrough and is constructed and arranged to communicate with intake port 24 through an aligned port 60 in sealing screen 39.
  • a different radial passageway, appropriately linearly spaced and angularly indexed from passageway 44 is provided for-each cylinder.
  • Valve member 38 is provided with a radial passageway 46 extending transversely therethrough and constructed and arranged to communicate with exhaust port 30 through an .aligned port 61 in sealing screen 41.
  • a different radial passageway appropriately linearly spaced and angularly indexed from passageway 46 is provided for each additional cylinder in line.
  • passageway 44 When passageway 44 is aligned with intake port 24, the intake gases in intake passage 26 are in communication with the combustion chamber 14 by way of an intake port passage 25 formed in body 10 at surface portion 13 and by way of an aligned port in sealing screen 39.
  • passageway 46 When passageway 46 is aligned with exhaust port 30, the exhaust gases are allowed to flow to exhaust passageway 32 from combustion chamber 14 by way of an exhaust port passage 31 formed in body 10 at surface portion 13 and by way of an aligned port in sealing screen 41.
  • a spark plug 50 is mounted in a bore 52 in body 10 in a suitable manner such that the electrode 54 of spark plug 50 is positioned in a bore 56 in communication with the combustion chamber 14.
  • Each of the valve members 36 and 38 is constructed of a cylindrical bar made of a suitable metal or metal alloy.
  • the material selected must be capable of withstanding the high temperatures known to be present within cylinder heads that are associated with internal combustion engines.
  • Each sealing screen 39 and 41 is constructed of a self-lubricating graphite material which is also capable of withstanding the high temperatures which are present. While various suitable graphite materials may be used, illustrative of the preferred material is a fine grade metal-impregnated graphite which exhibits increased thermoconductivity, strength, hardness, lubricity and wear' resistance. Also acceptable for use with this invention are pure graphite materials, graphitized carbon materials and ceramic-impregnated graphite materials. One example of a fine grade metal-impregnated graphite material is graphite bronze.
  • the cylinder body 10 may be provided with a bank of a plurality of cylinders and associated rotary valve means. With such a bank of a plurality of cylinders and rotary valves, the series of passageways 44 and 46 will be spaced longitudinally along the length of the associated valve member.
  • Sealing screen 39 includes a generally rectangular opening (aligned port) 60 which is disposed over corresponding port passage 25.
  • sealing screen 41 includes a generally rectangular opening (aligned port) 61 which is disposed over corresponding port passage 31. Although these two rectangular openings are in fact aligned with their respective intake and exhaust ports, a portion of each sealing screen extends into its corresponding port passage.
  • each valve, members 36 and 38 respectively, provides backing to the sealing screens thus enabling relatively thin screens to be used, while still withstanding the pressures exerted by the gases within the cylinder. As the force on the screens increases, the friction between the valve members and the screens also increases.
  • sealing screens 39 and 41 are nonrotational but do have movement to the extent that they are compliant with their respective valve members. The movement which is permitted might only amount to a small fraction of a mm between hot and cold extremes and pressure extremes within the cylinder head body, but throughout this movement cycle, a sealed interface between the sealing screens and the inlet and exhaust ports of the cylinder is required.
  • metal seals 68 and 69 are respectively disposed around the inlet port and around the exhaust port. In the exemplary embodiment, these metal seals are constructed of inconel, an alloy which is highly resistant to heat.
  • Each 0-ring seal is of an endless loop design and is larger in size than the corresponding metal seals so as to lie outward of the metal seals.
  • Each 0-ring seal is, in the exemplary embodiment, constructed of an elastomeric material.
  • FIG. 1 is actually a full section view and what is disclosed by the two illustrated cross-sectional portions of each seal is an endless seal configured as a band or loop that encircles the outer perimeter of its respective port, thus assuring sealing at - all locations around the ports.
  • the metal seals provide the first point or location of sealing and the 0-rings provide secondary or back-up sealing.
  • metal seal 69 (which is substantially the same as metal seal 68) is configured with a C-shaped lateral cross-section. Such a seal . exhibits a sufficient degree of elasticity in order to maintain a sealed interface. at high pressures.
  • seal arrangement 69' is illustrated and this seal arrangement represents the preferred style for the exemplary embodiment.
  • Seal arrangement 69' has an E-shaped lateral cross section. This type of seal works on many of the same principles of the C-shaped seal, except that it is more suitable for large flange deflections. The deflections permitted by the FIG. 3 and FIG. 4 seals allow the various sealing screens to move slightly with changes in pressure and temperature without permitting gapping or separation between the sealing screen and the cylinder head body. The result is an improved sealing concept for rotary valve cylinder head construction which is compatible with the graphite sealing sleeves that provide a self-lubricating configuration for smooth and virtually indefinite operation of the rotary valve members.
  • FIG. 5 illustrates an omega-shaped (lateral cross section) metal seal 74 which includes outwardly flared ends (edges) that are compressed between the two surfaces to be sealed. These ends are contoured so as to provide a full flat surface for sealing and seal 74 is able to expand from its compressed state with deflection of the sealing screen.
  • FIG. 6 illustrates a large radiused, inconel C-shaped seal 75 which operates on the same type of compressive and elasticity principles of those earlier-disclosed seals, but additionally includes an elastomeric 0-ring 76 . immediately behind seal 75 within the same groove. It is also to be understood that for each of the four metal seal arrangements disclosed, a back-up 0-ring seal, such as seals 70 and 71, may also be employed.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Cylinder Crankcases Of Internal Combustion Engines (AREA)
  • Portable Nailing Machines And Staplers (AREA)
  • Gasket Seals (AREA)
EP82300708A 1981-02-25 1982-02-12 Culasse de cylindre à tiroir rotatif Withdrawn EP0059047A3 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
US23788781A 1981-02-25 1981-02-25
US237887 1981-02-25

Publications (2)

Publication Number Publication Date
EP0059047A2 true EP0059047A2 (fr) 1982-09-01
EP0059047A3 EP0059047A3 (fr) 1983-11-02

Family

ID=22895660

Family Applications (1)

Application Number Title Priority Date Filing Date
EP82300708A Withdrawn EP0059047A3 (fr) 1981-02-25 1982-02-12 Culasse de cylindre à tiroir rotatif

Country Status (3)

Country Link
EP (1) EP0059047A3 (fr)
JP (1) JPS57143116A (fr)
AU (1) AU7955082A (fr)

Cited By (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3723596A1 (de) * 1987-07-16 1989-01-26 Squibb & Sons Inc Medizinisches pflaster
US5372104A (en) * 1993-10-08 1994-12-13 Griffin; Bill E. Rotary valve arrangement
US5417188A (en) * 1992-07-20 1995-05-23 Schiattino; Miljenko Double effect distribution sequential valve shaft assembly
ES2076063A2 (es) * 1992-04-24 1995-10-16 Santiago Antonio Serralvo Perfeccionamientos introducidos en motores de explosion.
WO2009000040A1 (fr) * 2007-06-27 2008-12-31 John Benson Saunders Moteur et soupape pour un moteur
WO2009039877A1 (fr) * 2007-09-19 2009-04-02 Lisa Dräxlmaier GmbH Culasse pour un moteur à combustion interne

Family Cites Families (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1077317A (en) * 1912-07-08 1913-11-04 Carl E Swenson Valve for internal-combustion engines.
US1513911A (en) * 1922-01-28 1924-11-04 Clyde W Keller Internal-combustion engine
DE412888C (de) * 1924-03-07 1925-04-30 Louis Albert Lohse Dichtung fuer ineinandersteckende, entgegengesetzt umlaufende roehrenfoermige Drehschieber an Explosionsmotoren
AT107467B (de) * 1924-08-22 1927-10-10 Roger Pierre Felix Lemasson Dichtungsvorrichtung für Kraftmaschinen.
US4019487A (en) * 1975-11-26 1977-04-26 Dana Corporation Rotary valve seal assembly
JPS6131123Y2 (fr) * 1978-06-22 1986-09-10

Cited By (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3723596A1 (de) * 1987-07-16 1989-01-26 Squibb & Sons Inc Medizinisches pflaster
ES2076063A2 (es) * 1992-04-24 1995-10-16 Santiago Antonio Serralvo Perfeccionamientos introducidos en motores de explosion.
US5417188A (en) * 1992-07-20 1995-05-23 Schiattino; Miljenko Double effect distribution sequential valve shaft assembly
US5372104A (en) * 1993-10-08 1994-12-13 Griffin; Bill E. Rotary valve arrangement
WO2009000040A1 (fr) * 2007-06-27 2008-12-31 John Benson Saunders Moteur et soupape pour un moteur
WO2009039877A1 (fr) * 2007-09-19 2009-04-02 Lisa Dräxlmaier GmbH Culasse pour un moteur à combustion interne

Also Published As

Publication number Publication date
JPS57143116A (en) 1982-09-04
EP0059047A3 (fr) 1983-11-02
AU7955082A (en) 1982-09-02

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Effective date: 19840703