EP0112069B1 - Drehschieber - Google Patents

Drehschieber Download PDF

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Publication number
EP0112069B1
EP0112069B1 EP19830307074 EP83307074A EP0112069B1 EP 0112069 B1 EP0112069 B1 EP 0112069B1 EP 19830307074 EP19830307074 EP 19830307074 EP 83307074 A EP83307074 A EP 83307074A EP 0112069 B1 EP0112069 B1 EP 0112069B1
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EP
European Patent Office
Prior art keywords
rotor
cylindrical
sealing
rotary valve
gas
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
Application number
EP19830307074
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English (en)
French (fr)
Other versions
EP0112069A1 (de
Inventor
Peter William Gabelish
Albany Reginald Vial
Russell Walter Roberts
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Individual
Original Assignee
Individual
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Filing date
Publication date
Priority claimed from AU21439/83A external-priority patent/AU591052B2/en
Application filed by Individual filed Critical Individual
Publication of EP0112069A1 publication Critical patent/EP0112069A1/de
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Publication of EP0112069B1 publication Critical patent/EP0112069B1/de
Expired 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
    • F01L7/16—Sealing or packing arrangements specially therefor
    • 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
    • F01L7/021—Rotary or oscillatory slide valve-gear or valve arrangements with cylindrical, sleeve, or part-annularly shaped valves with one rotary valve
    • F01L7/024—Cylindrical valves comprising radial inlet and axial outlet or axial inlet and radial outlet

Definitions

  • the present invention relates to valves and more particularly to rotary valves.
  • the present invention relates to rotary valves for reciprocating heat engines and particularly for internal combustion engines.
  • valves employed in internal combustion piston engines known rotary valves have not been widely accepted as they have not provided the advantages of conventional valves in respect of simplicity of construction, cost of manufacture, oil consumption, durability and ruggedness.
  • a rotary valve arrangement is disclosed in U.S. Patent No. 985,618 to Miller.
  • the patent to Miller discloses a rotary valve including a valve housing formed integral with the head of the engine and which receives a valve rotorwhichcommunicates with the combustion chamber via an annular sealing ring generally coaxial with the port communicating with the combustion chamber. More particularly the patent to Miller relates to this annular sealing member and its configuration whereby under combustion pressures the sealing members is forced into sealing contact with the valve rotor.
  • Rotary valves are also disclosed in U.S. Patents Nos. 1347978 and 1573022, both to Wehr. The earlier patent to Wehr discloses a rotary valve assembly having a split housing to support a bush having a cylindrical inner surface to receive the valve rotor.
  • This sleeve has a cylindrical outer surface eccentric with respect to the inner surface.
  • the valve rotor communicates with the combustion chamber by means of a port extending through the sleeve and part of the housing.
  • the split housing is mounted on the cylinder and forms the head of the engine.
  • the second patent to Wehr is a modification of the device disclosed in his earlier patent, and more particularly describes a means of biasing the sleeve into sealing contact with the valve rotor.
  • the U.S. Patent No. 1887997 to Cross also relates to a rotary valve arrangement and in particular relates to an annular sealing element which surrounds the port exiting from the combustion chamber and which sealingly engages the valve rotor.
  • This annular sealing member is generally coaxial with the port extending from the combustion chamber.
  • U.S. Patent No. 2048134 describes a rotary valve arrangement with the rotor being supported by a housing consisting of two portions which are spring biased together so as to engage the valve rotor.
  • An annular sealing element surrounds the port exiting from the combustion chamber and also sealingly engages the valve rotor.
  • U.S. Patent No. 1997133, to Cross is an improvement on Cross's earlier Patent No. 1887997, and particularly relates to the annular sealing element surrounding the port exiting from the combustion chamber and sealingly engaging the rotor. It is again pointed out that this annular sealing element is generally coaxial with the port exiting from the combustion chamber.
  • the present invention consists in a rotary valve mechanism for a reciprocating heat engine having a cylinder a piston reciprocating therein and a cylinder-head defining a combustion chamber, the rotary valve mechanism consisting of a cylindrical valve rotor supported for rotation in said cylinder head, the valve rotor 15 having at least one gas port passing through its cylindrical surface, mechanical means to rotate said valve rotor in a timed relationship with the movement of said piston, a floating valve housing assembly in said cylinder head providing a cylindrical inner surface in sliding sealing contact with the outer cylindrical surface of said valve rotor, said floating valve housing assembly being free to thrust against said valve rotor under the influence of the pressure of the working gases in the engine cylinder and defining a gas conducting port to provide a communication path between said rotor gas port and said combustion chamber, characterized in that said cylindrical surfaces are divided into three axially adjacent cylindrical zones comprising one inner gas-sealing zone axially positioned between two outer load-bearing zones, and inner gas sealing zone including totally within its axial length said
  • an improved rotary valve is provided which results from the realisation that many of the disadvantages of prior rotary valves, as described previously, can be overcome by providing a two part seal arrangement to sealingly connect the rotor with the head or block of an engine.
  • a first sealing device is employed to engage the rotor and then a resilient seal is used to connect the sealing device with the head or block of the engine. This allows movement of the valve rotor while still maintaining sealing contact therewith.
  • a particular advantage of such a combination is that it is considerably less complex than previous valve assemblies.
  • FIGS 1 to 3 there is schematically depicted a rotary valve assembly 10 in association with a cylinder head 11 mounted on an engine block 49.
  • the rotary valve assembly 10 includes a rotor 15 which includes longitudinally extending passages 16 and 17 which terminate on the longitudinal periphery surface of the rotor 15 so as to provide two rotor ports 43 and 44.
  • the rotor ports 43 and 44 are angularly spaced about the longitudinal axis of the rotor 15 so as to alternately communicate with a head port 19 extending from the chamber 14.
  • the passages 16 and 17 control the flow of fuel to, and flow of expended exhaust gases from, the combustion chamber 14.
  • the rotor 15 In operation of the valve assembly 10, the rotor 15 is rotated about its longitudinal axis so that the passages 16 and 17 are alternately brought into communication with the combustion chamber 14 in a timed sequence with movement of the piston 12.
  • the assembly 10 further includes a sealing combination 20 illustrated in Figure 3 in a parts exploded end elevation.
  • the sealing combination 20 includes a split housing 23 consisting of a bottom member 21 which co-operates with a top member 22 to define a generally circular cavity 26 which rotatably receives the generally cylindrical rotor 15.
  • the members 21 and 22 also co-operate to define a cube and have their end faces spaced by a gap 51.
  • the split housing 23 further includes bolts 24; which in combination with springs 25 secure the two support members 21 and 22 together and bias them toward the rotor 15.
  • the member 21 is formed with the port 19 extending from the chamber 14.
  • a split generally cylindrical hollow rotor seal 27 in the form of a sleeve which is supported on the generally cylindrical surfaces 28 and 29 of the members 21 and 22. As the two members 21 and 22 are urged together by means of the springs 25, the seal 27 is biased to define a generally cylindrical configuration conforming to the outer cylindrical surface of the rotor 15.
  • the seal assembly 20 acts as a seal in retaining the combustion gases within the chamber 14.
  • the extremities 30 of the seal 27 co-operate to define a generally arcuate shaped groove 32 within which is located a sealing strip 31 which is made of generally pliable material such as an elastomer so as to conform to its surrounding surfaces to prevent oil travelling along the groove 32.
  • the strip 31, which is also depicted in Figures 5 and 7, is biased to engagement within the groove 32 by means of a resilient leaf-type spring 33 also depicted in Figure 5.
  • the spring 33 could also take the form of coil springs.
  • the split seal 27, in combination with the spring-loaded housing 23 and with the sealing strip 31, enable the rotor 15 to be constructed of different material to that of the supporting and sealing combination 20 by compensating for different thermal expansion rates of the materials employed.
  • the split seal 27 in combination with the spring-loaded housing 23 compensates for the variation in expansion of the rotor 15 and of the seal assembly 20 due to changing the temperature conditions to which the valve assembly 10 is subjected to.
  • the sealing strip 31 has an end 46 of circular cross section and which is the pliable portion of the strip 31 which sealingly slidingly engages the surfaces 47 of the groove 32. As the seal 27 expands and contracts due to changing temperature conditions within the engine, the end 46 will compensate for movement between the surfaces 47. Additionally the sealing strip 31 slidingly engages the rotor 15 and acts to prevent oil passing the sealing strip 31. The strip 31 also forces oil through the passages 39, which drain oil from the grooves 38, by acting as a dam.
  • the rotor 15 is supported by means of bearings 34 while the seal 27 sealingly engages the external surface of the rotor 15. Accordingly the seal 27 provides an effective seal about the rotor 15 to inhibit the flow of oil to the combustion chamber 14 and the flow of gases through the valve assembly 10 other than that permitted to exit or enter by means of the passages 16 and 17. This is achieved by pressure being applied to the surfaces of the valve rotor 15 and the inner surface of the seal 27 in the area adjacent the port 19. This pressure is applied firstly to the flat surface 48 of the bottom member 21 and is transmitted to its inner surface 28 and then to the outer surface of seal 27.
  • the pressure which is largely proportional to the pressure of gas in the combustion chamber 14 is created by:
  • the split housing 23 is located in a cavity 45 provided in the head 11 and extending from the combustion chamber 14.
  • the split housing has a clearance 35 around its periphery to enable self alignment and movement of the sealing combination 20 relative to the head 11.
  • the split housing 23 is sealingly engaged with the head 11 by means of a resilient seal 36 which has flexible flanges so as to generally define a V-shape configuration in transverse longitudinal cross section.
  • the resilient seal 36 permits rocking movement of the members 21 and 22 while still retaining sealing contact between the head 11 and member 21 and clearance variations due to thermal expansion.
  • the seal 36 is resiliently deformed so that the flanges are biased to engage the head 11 and bottom member 21. Under high pressure conditions the flanges are forced outwardly to further enhance sealing contact with the head 11 and member 21.
  • the seal 36 would be machined from a single piece of high temperature alloy steel with the flanges tapering towards their inner extremities.
  • the seal 27 includes two oil ports 37 which deliver oil to the load bearing surfaces of the seal 27.
  • a passage 18 which provides for communication between the combustion chamber 14 and the passages 16 and 17.
  • the seal 27 is provided with two oil control grooves 38 which inhibit the transfer of oil from lubricated load bearing areas 52 to an area of the seal 27 which will be exposed to the combustion chamber 14, or ports 16 and 17.
  • the seal 27 also provides two load bearing areas 52 to support the split housing 23 and retains it in position.
  • passages 39 Communicating with the oil control grooves 38 are passages 39 which provide for the draining of oil from the grooves 38.
  • Oil is delivered to the ports 37 by means of an oil gallery 40 which is depicted in Figure 2.
  • the seal 27 would be provided with a location indentation 41 which receives a location peg 42 to prevent rotation of the seal 27.
  • oil control grooves 38 act as a barrier between the lubricated load bearing areas 52 and the areas exposed to the passages 16 and 17 and the port 19. More particularly side leakage from the hydrodynamically lubricated areas 52 enters the oil control grooves 38 and is carried by rotation of the rotor 15 to drainage passages 39.
  • Cooling of the rotary valve 10 may be achieved by a water jacket which permits the flow of water past the rotary valve assembly 10, and more particularly past the sides of the split housing 23.
  • Cooling of the rotary valve assembly 10 may also be achieved by a plurality of fins which dissipate heat by means of radiation and conduction to the surrounding air medium.
  • heat conduction from the rotor 15 is enhanced by the area of contact between the seal 27 and the rotor 15, and in turn the area of contact between the seal 27 and the support members 21 and 22 and the cube shape of the sealing combination 20.
  • the heat transfer between members 21 and 22 is enhanced by the large area of contact and contact pressure between the two members 21 and 22. This contact force results from transverse pressure between the vertical abutting sides of the seal members 21 and 22.
  • the area 48 of the sealing combination 20 exposed to the combustion chamber 14 is minimised, so too is the heat absorbed by the seal combination 20 due to its exposure to the heat within the combustion chamber 14.
  • the area 48 is reduced by providing the head 11 with flange portions 50 which project radially inwardly above the cylinder 13.
  • Heat aborption into sealing combination 20 is further reduced by minimising the length of port 19 in bottom member 21. Shortening of port 19 is made possible by split housing construction of seal assembly 20 in combination with resilient seal 36. To aid in heat transfer, the members 21 and 22 have elongated sides 53 and 54 to increase the area of contact between the members 21 and 22.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Valve Device For Special Equipments (AREA)

Claims (10)

1. Drehschieber für eine hin- und hergehende Wärmemaschine mit einem Zylinder (13), einem darin hin- und hergehenden Kolben (12) und einem Zylinderkopf (11), der eine Verbrennungskammer (14) bildet, wobei der Drehschieber aus einem zylindrischen Ventilrotor (15) besteht, der zur Drehung in dem Zylinderkopf gehaltert ist, wobei der Ventilrotor (15) mindestens eine Gasöffnung (18) aufweist, die sich durch seine Zylinderfläche erstreckt, mit mechanischen Mitteln zum Drehen des Ventilrotors in zeitlich abgestimmter Zuordnung zur Bewegung des Kolbens, mit einer schwimmenden Ventilgehäuseanordnung (20) in dem Zylinderkopf, welche eine zylindrische Innenwand in dichtenden Gleitkontakt mit der äußeren Zylinderfläche des Ventilrotors bringt, wobei die schwimmende Ventilgehäuseanordnung (20) frei ist, unter dem Einfluß des Druckes des Arbeitsgases in dem Motorzylinder (13) gegen den Ventilrotor (15) zu drücken und eine Gasleitungsöffnung (19) zu bilden, die einen Strömungspfad zwischen der Rotorgasöffnung (18) und der Verbrennungskammer (14) einrichtet, dadurch gekennzeichnet, daß die zylindrischen Flächen in drei axial benachbarte zylindrische Zonen unterteilt sind, welche eine innere Gasdichtungszone aufweist, die zwischen den zwei äußeren lasttragenden Zonen (52) liegt, wobei die innere Gasichtungszone innerhalb ihrer axialen Länge die Gasleitungsöffnung (18) un den zylindrischen Pfad zur Gänze einschließt, der von der Gasöffnung (18) bei ihrer Drehung überstrichen wird, daß die lasttragenden Zonen (52) mit einem flüssigen Schmiermittel versorgt werden und eine Vollschichtschmierung haben, um die Belastung aufzunehmen, die von dem Druck des Arbeitsgases in dem Maschinenzylinder ausgeübt wird, daß die innere gasdichtungszone keine Schmiermittelströmung aufnimmt und keine Vollschichtschmierung besitzt, daß die innere Gasdichtungszone Gasdichtheit zwischen dem Ventilrotor und dem schwimmenden Ventilgehäuse durch die enge Annäherung ihrer zwei Flächen und die durch Druck hervorgerufene Kraft ihre Trennung verhindern, daß Mittel (38) zwischen den äußeren lasttragenden Zonen (52) und der inneren Gasdichtungszone vorgesehen sind, um die Schmiermittelströmung von den äußeren lasttragenden Zonen (52) zu der inneren Gasdichtungszone zu unterbinden.
2. Drehschiebervorrichtung nach Anspruch 1, dadurch gekennzeichnet, daß die zuletzt erwähnten Mittel kreisförmige Nuten (38) in der Zylinderfläche der schwimmenden Ventilgehäuseanordnung aufweisen, welche die äußeren lasttragenden Zonen (52) von der inneren Gasdichtungszone trennen, daß ein fixierter Dam (31) jede der Nuten absperrt, daß Abströmkanäle (39) mit jeder der Nuten kommunizieren, um von ihnen Schmiermittel abzuleiten, das durch die äußeren lasttragenden Zonen (52) zu den Nuten (38) umgewälzt wurde, wobei die Anordnung der Dämme (31) in Bezug auf die Abströmkanäle derart ist, daß in die Nuten eintretendes Schmiermittel durch die Drehung des Ventilrotors zu den Dämmen geführt wird, welche das Schmiermittel in die Abströmkanäle umlenken.
3. Drehschiebervorrichtung nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, daß die schwimmende Ventilgehäuseanordnung (20) ein erstes Gehäuseteil (21), ein zweites Gehäseteil (22) und eine zylindrische Buchse (27) aufweist, wobei die ersten Gehäuseteile zusammenwirken, um eine innere zylindrische Fläche zu bilden, welche die zylindrische Buchse aufnimmt, wobei die zylindrische Buchse den Ventil rotor aufnimmt.
4. Drehschiebervorrichtung nach Anspruch 3, dadurch gekennzeichnet, daß die zylindrische Buchse durch einen Längsschlitz unterbrochen ist, um Änderungen in ihrer Umfangserstreckung auszugleichen, daß sich zwei Umfangsnuten (52) um die Innenfläche der zylindrischen Buchse jeweils an den' Verbindungsstellen der äußeren lasttragenden Zonen mit der inneren Gasdichtungszone erstrecken, daß Schmiermittelöffnungen (37) in der zylindrischen Buchse vorgesehen sind, um Schmiermittel zu den lasttragenden Zonen zu leiten, daß Abschottungsmittel (31) in dem Schlitz angeordnet sind, um die Nuten zu unterbrechen, daß Schmiermittelabflußkanäle (39) in der Nähe der Abschottungsmittel (31) und an deren stromaufwärtigen Schieber angeordnet sind und sich von den Nuten erstrecken, um Schmiermittel von dem Rotor (15) wegzüleiten.
5. Drehschiebervorrichtung nach Anspruch 4, dadurch gekennzeichnet, daß Begrenzungskanten (30) des Längsschlitzes vom Außendurchmesser der Buchse zum Innendurchmesser abgeschrägt sind, um eine gerade Außennut (32) zu bilden, die um den Schlitz angeordnet ist, daß das Abschottungsmittel von einem biegsamen Dichtungsstreifen gebildet ist, der sich entlang der Länge der geraden Nut erstreckt und in diese von einer zweiten Feder (33) gedrückt wird, um die Oberflächen der geraden Nut und den Teil der Rotorfläche abzudichten, der zwischen ihnen liegt, so daß bei Endansicht von Rotor und Buchse das Volumen zwischen den Berührungslinien des biegsamen Dichtungsstreifens mit den Seiten der geraden Nut (32) und die freiliegende Oberfläche des Rotors vollständig von dem biegsamen Dichtungsstreifen ausgefüllt sind.
6. Drehschiebervorrichtung nach Anspruch 5, dadurch gekennzeichnet, daß die abgeschrägten Kanten (30) der Buchse, welche den Schlitz begrenzen, jeweils konkav gekrümmt sind, wenn man sie in Endansicht betrachtet, daß der Dichtungsstreifen (31) aus einem wärmebeständigen elastomeren Material hergestellt ist und einen Dichtungsabschnitt von im allgemeinen kreisförmigem Querschnitt hat, daß eine starre Kraftübertragungseinrichtung zwischen der zweiten Feder und dem Dichtungsteil des biegsamen Streifens angeordnet ist, um gleichmäßige Kontaktdruckverteilung entlang von deren Länge zu gewährleisten.
7. Drehschiebervorrichtung nach Anspruch 4, dadurch gekennzeichnet, daß eines der Gehäuseteile (22) einen engen Schiebesitz in dem äußeren Gehäuseteil (21) darstellt und daß beide Teile große, parallele und zusammenhängende Gleitflächen aufweisen, die übereinandergleiten, während sie in thermischem Kontakt derart bleiben, daß die Teile eine Relativbewegung in bezug aufeinander haben, um den Wärmeausdehnungsunterschied zwischen dem Ventilrotor (15) und der schwebenden Ventilgehäuseanordnung (20) aufzunehmen, ohne daß zwischen den Gehäuseteilen ein Verlust an gutem, thermischem Leitungspfad eintritt.
8. Drehschiebervorrichtung nach Anspruch 7, dadurch gekennzeichnet, daß die schwimmende Ventilgehäuseanordnung eine kubische Form hat und daß sich die zusammenhängende Gleitfläche der Teile parallel zu einem Paar von gegenüberliegenden Seiten des Würfels erstreckt.
9. Drehschiebervorrichtung nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, daß ein einstückiger, nachgiebiger und ringförmiger Dichtungsring (36) von im wesentlichen U-Querschnittsform in radialer Richtung um die Gasleitungsöffnung angeordnet ist und zwischen der schwimmenden Ventilgehäuseanordnung und dem Zylinderkopf liegt, wobei die Schenkel des U derart angeordnet sind, daß sie radial nach innen zeigen.
10. Drehschiebervorrichtung nach Anspruch 9, dadurch gekennzeichnet, daß der ringförmige Dichtungsring (36) aus einem einzigen Stück aus Hochtemperatur-Legierungsstahl herausgearbeitet ist und Flansche aufweist, die sich zu ihrem inneren Umfang verjüngen.
EP19830307074 1982-11-19 1983-11-18 Drehschieber Expired EP0112069B1 (de)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
AUPF689082 1982-11-19
AU6890/82 1982-11-19
AU21439/83A AU591052B2 (en) 1982-11-19 1983-11-16 A rotary valve

Related Child Applications (2)

Application Number Title Priority Date Filing Date
EP85201839A Division EP0197204A1 (de) 1982-11-19 1983-11-18 Drehschieber
EP85201839.9 Division-Into 1985-11-11

Publications (2)

Publication Number Publication Date
EP0112069A1 EP0112069A1 (de) 1984-06-27
EP0112069B1 true EP0112069B1 (de) 1987-04-01

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EP19830307074 Expired EP0112069B1 (de) 1982-11-19 1983-11-18 Drehschieber

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Families Citing this family (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB9000306D0 (en) * 1990-01-06 1990-03-07 Bullivant Nicholas T Rotary valve
GB2267934A (en) * 1992-06-01 1993-12-22 Lotus Car I.C engine or compressor rotary valve arrangement.
US5503124A (en) * 1992-11-06 1996-04-02 A. E. Bishop Research Pty. Limited Rotary valve with seal supporting tongue
CN115382586B (zh) * 2021-05-24 2024-05-28 广州万孚生物技术股份有限公司 驱动装置与医疗检测系统

Family Cites Families (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1513911A (en) * 1922-01-28 1924-11-04 Clyde W Keller Internal-combustion engine
DE886403C (de) * 1944-12-07 1953-08-13 Charlotte Heylandt Lagerung des Walzendrehschiebers im Zylinderkopf von Brennkraftmaschinen
US2617395A (en) * 1949-06-29 1952-11-11 Sudwerke G M B H Internal-combustion engine cooling for rotary valves
US3871340A (en) * 1972-10-03 1975-03-18 Tetrahedron Associates Inc Rotary valve internal combustion engine
US4019488A (en) * 1973-09-19 1977-04-26 Kremer Alphonse E Rotary valve engine with lubricator

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Publication number Publication date
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