EP0469415A2 - Dispositif de barre d'étanchéité pour machine à piston rotatif - Google Patents

Dispositif de barre d'étanchéité pour machine à piston rotatif Download PDF

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Publication number
EP0469415A2
EP0469415A2 EP91112172A EP91112172A EP0469415A2 EP 0469415 A2 EP0469415 A2 EP 0469415A2 EP 91112172 A EP91112172 A EP 91112172A EP 91112172 A EP91112172 A EP 91112172A EP 0469415 A2 EP0469415 A2 EP 0469415A2
Authority
EP
European Patent Office
Prior art keywords
sealing strip
slot
radially
width
outer region
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Withdrawn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
EP91112172A
Other languages
German (de)
English (en)
Other versions
EP0469415A3 (en
Inventor
Jonathan Mark Lauter
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.)
John Deere Technologies International Inc
Original Assignee
John Deere Technologies International Inc
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 John Deere Technologies International Inc filed Critical John Deere Technologies International Inc
Publication of EP0469415A2 publication Critical patent/EP0469415A2/fr
Publication of EP0469415A3 publication Critical patent/EP0469415A3/de
Withdrawn legal-status Critical Current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
    • F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
    • F01C19/00—Sealing arrangements in rotary-piston machines or engines
    • F01C19/02—Radially-movable sealings for working fluids
    • F01C19/04—Radially-movable sealings for working fluids of rigid material
    • 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
    • F02B53/00—Internal-combustion aspects of rotary-piston or oscillating-piston engines
    • F02B2053/005—Wankel engines
    • 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
    • F02B53/00—Internal-combustion aspects of rotary-piston or oscillating-piston engines

Definitions

  • the invention relates to a sealing strip arrangement for a rotary piston internal combustion engine with a rotor that rotates in a housing and divides it into working chambers and has a slot on at least one apex edge, which receives a radially movable sealing strip that fits sealingly against a running surface inside the housing.
  • the rotor is exposed to the heat and pressure of the combustion gases.
  • the sealing strips are arranged within rotor slots with a certain space which allows the sealing strip to move radially in order to ensure constant contact between the sealing strip and the running surface in the rotor housing.
  • the high gas pressure acting on the outer surfaces of the sealing strip can push the sealing strip inwards and lift it off the running surface.
  • Attempts have been made to solve this problem by using tiltable sealing strips, spaces between the sealing strip and slot and sealing strips with protruding or projecting lugs and the like. This should indicate the gas pressure on the radially inner side of the sealing strip and press the sealing strip against the running surface.
  • an excessively large protrusion increases the side load on the sealing strip and thus the sealing strip friction, as a result of which the required radial mobility of the sealing strip can be impaired.
  • the object to be achieved with the invention is seen in providing a sealing strip arrangement of the type mentioned at the outset, in which the conformity between the sealing strip and the running surface is improved.
  • each slot has step-shaped side walls, through which an inner, narrower slot area and an outer, wider slot area are formed. These slit areas are connected to each other by an outwardly facing heel surface.
  • Each sealing strip has an outer head part, preferably with protrusions or protrusions on both sides.
  • the circumferential width of the projections is slightly larger than the corresponding width of the heel areas of the slots, so that there is contact between the sealing strip and the slot in the vicinity of the outer sealing strip edge. This reduces the bending forces and the side load on the sealing strip.
  • the side area of the sealing strip which is directly exposed to the high gas pressure, is also reduced by the heel areas. This leads to a further reduction in the stress between the sealing strip and the slot. These factors reduce the friction between the sealing strip and the slot and thus improve the ability of the sealing strip to maintain contact with the running surface of the housing without leakages or increased conforming forces occurring.
  • the rotary piston internal combustion engine of the Wankel type indicated in FIG. 1 contains a housing 10 with an inner running or working surface 12.
  • a rotor 16 with an essentially triangular cross section is rotatably mounted in the housing 10 via a conventional eccentric 17.
  • the housing 10 and the rotor 16 form three working chambers 14.
  • a stepped slot 18 extends axially inwards on each vertex edge of the rotor 16.
  • Each slot 18 has a narrower inner region 20, which is delimited by the side walls 21, 22, and a wider outer region 24, which is delimited by the side walls 25, 26.
  • the inner region 20 can be designed to converge slightly from a further upper region to a narrower lower region.
  • the areas 20 and 24 are connected via radially outwardly directed heel surfaces 27, 28 which run on both sides of the groove.
  • Each slot 18 receives a sealing strip 30 which is radially movable within the slot 18 in order to be able to maintain contact with the tread 12.
  • the sealing strip 30 is pressed radially outward against the running surface 12 by a conventional spring arranged under the sealing strip 30.
  • Each sealing strip 30 contains a lower part 32, which has a rectangular cross section and side surfaces 34, 36, and a head part 38 with a rounded outer surface 40. Between the head part 38 and the lower part 32, radially inwardly directed contact surfaces 42, 44, which are connected to the outer surface 40 via the side surfaces 46, 48.
  • the side surfaces 46, 48 of the head part 38 of the sealing strip 30 have a radial dimension which is greater than a radial dimension of the side walls 25, 26 of the outer region 24 of the slot 18. This ensures that the outer surface 40 does not fall behind the radially outer one Edge of the rotor slot 18 can dip and thus contact with the tread 12 is always maintained.
  • the passage opening reduces the pressure of the high-pressure side of the sealing strip 30, which communicates via the passage opening past the side surface of the sealing strip 30 to the area below the sealing strip 30, where the reduced pressure helps to move the sealing strip 30 radially outward and in contact with the Tread 12 presses. Since the passage opening lies between the side surface 48 and the side wall 26 and near the radially outer region of the sealing strip 30, only the extremely outer edge region of the sealing strip 30 is directly exposed to the high pressure prevailing on the right side of the sealing strip 30 in the working chamber.
  • the passage opening is dimensioned such that the pressure under the sealing strip 30 does not lead to excessive frictional pressure between the sealing strip 30 and the running surface 12, but on the other hand a reliable contact of the sealing strip 30 with the running surface 12 is ensured.
  • the width of the edges or projections 42, 44 of the sealing strip 30 is somewhat larger (approximately by 0.25 to 0.75 mm) than the width of the shoulder surfaces 27, 28 of the slot 18.
  • the sealing strip 30 and the slot 18 are dimensioned in such a way that when the sealing strip 30 is moved to one side of the slot 18, a contact between the rotor 16 and the sealing strip 30 through the side surface 46 of the head part 38 and the side wall 25 of the slot 18 or through the side surface 48 of the sealing strip 30 and the side wall 26 the slot 18 takes place. This engagement prevents contact between an outer region of the lower part 32 of the sealing strip 30 and an outer region of a side wall 21 of the inner region 20 of the slot 18.
  • This arrangement reduces the occurrence of bending forces and reduces side loads on the sealing strip 30. This increases the friction between the sealing strip 30 and the slot 18 is reduced and the ability of the sealing strip 30 to come into contact with the tread 12 while avoiding leakages and increased pressure forces is improved.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Sealing Using Fluids, Sealing Without Contact, And Removal Of Oil (AREA)
EP19910112172 1990-07-31 1991-07-20 Sealing strip arrangement for a rotary piston engine Withdrawn EP0469415A3 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
US560718 1983-12-12
US07/560,718 US5123820A (en) 1990-07-31 1990-07-31 Pressure assisted apex seal with stepped slot

Publications (2)

Publication Number Publication Date
EP0469415A2 true EP0469415A2 (fr) 1992-02-05
EP0469415A3 EP0469415A3 (en) 1992-05-27

Family

ID=24239056

Family Applications (1)

Application Number Title Priority Date Filing Date
EP19910112172 Withdrawn EP0469415A3 (en) 1990-07-31 1991-07-20 Sealing strip arrangement for a rotary piston engine

Country Status (4)

Country Link
US (1) US5123820A (fr)
EP (1) EP0469415A3 (fr)
JP (1) JPH04232301A (fr)
CA (1) CA2045062A1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO1993025801A1 (fr) * 1992-06-09 1993-12-23 Manfred Max Rapp Machine a piston

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP6149851B2 (ja) * 2014-12-08 2017-06-21 マツダ株式会社 ロータリーピストンエンジンのアペックスシール構造

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR1464911A (fr) * 1965-11-26 1967-01-06 Renault Perfectionnements aux segments d'étanchéité radiaux pour moteurs rotatifs
AT256552B (de) * 1963-10-17 1967-08-25 Ustav Pro Vyzkum Motorovych Vo Kolbendichtung für Drehkolbenbrennkraftmaschinen
DE1907039B2 (de) * 1968-02-13 1975-05-15 The Secretary Of State For Defence Of The United Kingdom Of Great Britain And Northern Ireland, London Radiale Dichtungsanordnung für eine Kreiskolbenkraftmaschine

Family Cites Families (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2866417A (en) * 1956-06-11 1958-12-30 Hanomag Ag Rotary piston machine
GB983025A (en) * 1962-03-31 1965-02-10 Daimler Benz Ag Improvements relating to pistons for rotary-piston internal combustion engines
DE1201137B (de) * 1963-05-15 1965-09-16 Eugen W Huber Dr Ing Druckentlastete Dichtleiste fuer Rotationskolbenmaschinen
US3758243A (en) * 1972-04-24 1973-09-11 Gen Motors Corp Rotary machine apex seal
US3873250A (en) * 1973-12-03 1975-03-25 Ford Motor Co Apex seal having gas pressure bias for a rotary engine
US4317648A (en) * 1978-11-13 1982-03-02 Toyo Kogyo Co., Ltd. Apex seal for rotary piston engines with separate sealing and support pieces

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
AT256552B (de) * 1963-10-17 1967-08-25 Ustav Pro Vyzkum Motorovych Vo Kolbendichtung für Drehkolbenbrennkraftmaschinen
FR1464911A (fr) * 1965-11-26 1967-01-06 Renault Perfectionnements aux segments d'étanchéité radiaux pour moteurs rotatifs
DE1907039B2 (de) * 1968-02-13 1975-05-15 The Secretary Of State For Defence Of The United Kingdom Of Great Britain And Northern Ireland, London Radiale Dichtungsanordnung für eine Kreiskolbenkraftmaschine

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO1993025801A1 (fr) * 1992-06-09 1993-12-23 Manfred Max Rapp Machine a piston
US5681156A (en) * 1992-06-09 1997-10-28 Rapp; Manfred Max Piston machine having a piston mounted on synchronously rotating crankshafts

Also Published As

Publication number Publication date
US5123820A (en) 1992-06-23
EP0469415A3 (en) 1992-05-27
CA2045062A1 (fr) 1992-02-01
JPH04232301A (ja) 1992-08-20

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