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WO1991010811A1 - Moteur a combustion interne a piston rotatif - Google Patents

Moteur a combustion interne a piston rotatif Download PDF

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Publication number
WO1991010811A1
WO1991010811A1 PCT/EP1990/002047 EP9002047W WO9110811A1 WO 1991010811 A1 WO1991010811 A1 WO 1991010811A1 EP 9002047 W EP9002047 W EP 9002047W WO 9110811 A1 WO9110811 A1 WO 9110811A1
Authority
WO
WIPO (PCT)
Prior art keywords
ring
combustion engine
housing
internal combustion
piston internal
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.)
Ceased
Application number
PCT/EP1990/002047
Other languages
German (de)
English (en)
Inventor
Huschang Sabet
Dietrich Eckhardt
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
Priority to JP91500115A priority Critical patent/JPH05507984A/ja
Publication of WO1991010811A1 publication Critical patent/WO1991010811A1/fr
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

Links

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
    • F01C1/00—Rotary-piston machines or engines
    • F01C1/02—Rotary-piston machines or engines of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents
    • F01C1/063—Rotary-piston machines or engines of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents with coaxially-mounted members having continuously-changing circumferential spacing between them

Definitions

  • the invention relates to a rotary piston internal combustion engine with a housing having a cylindrical inner surface and radial inlet and outlet openings, with a rotor rotating within the housing at a uniform speed and having a cylindrical circumferential surface, with a plurality of radially angularly spaced apart from one another a hub projecting at a uniform speed concentrically to the rotor, engaging in working chambers within the rotor and connected to the rotor via at least one crank mechanism, and with pistons passing through the rotor wall, the working chambers alternating with the inlet and outlet openings of the housing its connecting channels, the openings on the housing side of which are enclosed by sealing rings arranged in the rotor wall and abutting against the inner surface of the housing,
  • the invention is based on the object, the known rotary piston internal combustion engine. To improve the machine in such a way that a long running time is guaranteed even at high speeds.
  • the invention is based on the idea of minimizing wear on the sealing rings and on the inner surface of the housing by using suitable sealing ring materials and arrangements.
  • the sealing rings arranged in the ring grooves of the rotor wall consist of a ceramic material and have a ground and / or polished sliding surface adapted to the curved inner surface of the housing and under the action of a spring against the inner surface of the housing can be pressed.
  • the ceramic material expediently has a Mohs hardness of over 8.5, preferably from 9 to 9.5.
  • a ceramic material made of silicon nitride or silicon carbide has proven to be particularly suitable.
  • the inner surface of the housing is provided with a wear-resistant coating, preferably made of chromium oxide or nickel, with embedded silicon crystals (Nikasil).
  • these expediently have a circular outline.
  • the sliding surface adapted to the inner surface of the housing nevertheless ensures that the sealing ring is automatically aligned in the annular groove.
  • the sliding surface can be chamfered or rounded all around in the area of its outer and inner edge.
  • a preferred embodiment of the invention provides that a spring, preferably designed as a wave spring, is arranged between the sealing ring and the base of the annular groove.
  • a spring ring slotted on one side is advantageously arranged between the sealing ring and the spring, which rests sealingly against the outer flanks of the ring groove.
  • the slot of the spring ring of overlapping vom ⁇ ring made of metal or ceramic material arranged so that it can also escape through the slot of the spring ring not komprimier ⁇ tes gas.
  • a particularly good sealing effect during the compression process and during the expansion of the pressurized combustion gases is advantageously achieved in that the diameter of the annular groove in the area of its inner flanks is smaller than that of the sealing ring, spring washers and / or intermediate ring. This measure enables the end face of the sealing ring opposite the sliding surface with the pressure of the compressed fuel-air mixture or the combustion gases.
  • a further advantageous embodiment of the invention provides that the annular groove has on its outer flank an annular shoulder facing away from the base of the groove.
  • the sealing ring expediently has a greater width than the intermediate ring and at least partially overlaps the ring shoulder with its end face facing the groove base.
  • the sealing ring which overlaps the ring shoulder can be designed as a stepped ring and lie directly on the spring ring.
  • the inside width of the inlet and outlet openings is at least in the axial direction smaller than the inside diameter of the sealing rings. This ensures that the sealing rings bear evenly against the inside surface of the housing when the inlet and outlet openings are passed over.
  • FIG. 1 shows a longitudinal section through a rotary piston internal combustion engine in two sectional planes forming an angle with one another along the Section line 1-1 of Fig. 2;
  • Fig. 2 shows a section along the section line 2-2
  • FIG. 1; 3 shows an enlarged detail from FIG. 2.
  • the rotary piston internal combustion engine essentially consists of a stationary housing 10, which has a cylindrical inner surface 12 and radial inlet and outlet openings 14, 16, a rotor 18 rotating therein at a uniform speed, and a rotor 18 mounted in the rotor 18 and rotating at a non-uniform speed Hub 20 with four radially outwardly projecting, piston-shaped pistons 22.
  • the fuel supply and the exhaust gas discharge take place through channels 34 which are arranged at an angular distance from one another and pass through the rotor wall 24 and which alternately connect the working chambers 30 to the inlet and outlet openings 14 and 16, respectively.
  • the fuel-air mixture supplied to two working chambers 30 at the same time via two opposite inlet openings 14 and channels 34 is compressed during the oscillating movement of the pistons 22 between them and the side walls 36 of the ribs 32 and in the channels 34.
  • the compressed mixture is ignited at the dead center of the pistons 22 by means of two spark plugs 40 screwed into the housing jacket 38.
  • the expanding combustion gases drive the pistons 22 and the ribs 32 apart and then escape through the channels 34 into the outlet openings 16.
  • the relative movement between the pistons 22 and the rotor 18 is transmitted with the aid of four connecting rods 44 articulated on bolts 42 of the hub 20 to the crank pins 46 of four crank shafts 48 which axially penetrate the ribs 32 and thus is converted into a rotary movement puts.
  • Gear wheels 50 connected on the face side to the crankshafts 48 mesh with the teeth of an internally toothed ring gear 52 elastically connected to the housing 10 and thereby convert the rotary movement of the crankshafts 48 into a rotary movement of the rotor 18 relative to the housing 10.
  • the rotor rotation can be achieved by means of an output shaft 62, which is connected in one piece to the end face part 28 and is supported in the bearings 54, 56 of the housing covers 58, 60, is transmitted to a consumer.
  • sealing strips 64 are provided on the free ends of the pistons 22 moving along the inside of the rotor wall 24 and on the end faces of the pistons 22 and the hub 20.
  • a pressure equalization between the working chambers 30 or a escape of the compressed fuel-air mixture via the annular gap 66 between the rotor peripheral surface 68 and the inner housing surface 70 is through the openings 74 of the channels 34 on the rotor circumferential surface 68 enclosing sealing rings 72, which are each arranged in an annular groove 76 in the rotor wall 24 and bear against the inner surface 70 of the housing.
  • the sealing rings 72 which are inserted radially displaceably in the ring grooves 76, consist of a ceramic material of great hardness such as silicon nitride or silicon carbide and, with their ground or polished sliding surface 78 adapted to the curvature of the housing inner surface 70, against the housing inner surface 70 provided with a wear-resistant coating 80 pressed.
  • the sealing rings 72 are pressed on once by a spring 82 inserted into the annular groove.
  • a spring 82 inserted into the annular groove.
  • the end face 86 of the sealing ring 72 facing the base 84 of the annular groove 76 becomes via the gap 66 and an annular gap 89, which remains free between the inner flank 88 of the annular groove 76 and the sealing ring 72, is acted upon by the overpressure prevailing in the working chamber 30 from the channel 34, so that the contact pressure of the spring 82 is increased.
  • the coating 80 on the inner surface 70 of the housing can consist of different materials. However, it has been shown that a 3/10 to 4/10 mm thick plasma-sprayed coating made of chromium oxide in combination with ceramic sealing rings made of silicon carbide or a 2/10 to 3/10 mm thick, electro- lyolytically applied coating made of nickel with embedded silicon carbide crystals (Nikasil) together with sealing rings made of silicon nitride ensure good running properties and low wear.
  • the sealing ring 72 shown in FIG. 3 has a circular outline and, together with a shaft spring 82, a spring ring 90 slotted on one side on the shaft spring 82, and a closed intermediate ring 92 arranged between the spring ring 90 and the sealing ring 72, are in one Annular groove 76 used, which has on its outer flank 94 an annular shoulder 96 facing away from the groove base 84.
  • the diameter of the annular groove 76 on its inner flank 88 is slightly smaller than the inner diameter of the sealing ring 72, the intermediate ring 92 and the spring ring 90, so that the compressed fuel-air mixture or the expanding, pressurized exhaust gas from the channel 34 can penetrate between the bottom 84 of the annular groove 76 and the underside of the spring ring 90 facing the bottom 84 of the annular groove 76.
  • the spring ring 90 lies sealingly against the outer flank 94 of the annular groove 76 and thereby blocks the mixture or the exhaust gases from escaping to the outside.
  • the intermediate ring 92 resting on the upper side of the spring ring 90 covers the slot of the spring ring 90, so that only a very small amount of gas can pass through there. This amount of gas is further reduced due to the very narrow gap between the end face 86 of the sealing ring 72 and the ring shoulder 96.
  • the annular shoulder 96 in the annular groove 76 enables to make the wall thickness of the ceramic sealing ring 72 relatively large and thereby reduce the risk of breakage without increasing the contact pressure acting on the ceramic sealing ring 72 and thus the sliding friction between the sealing ring 72 and the inner housing surface 70 by increasing the area exposed to the gas pressure.
  • the sealing ring 72 can be made relatively flat, as a result of which the elastic adaptation of the sliding surface 78 to the housing inner surface 70 is facilitated in the case of a sealing ring 72 which is slightly warped during operation.
  • the inner diameter of the sealing rings 72 is larger than the clear width of the inlet and outlet openings 14, 16, so that the sealing rings 72 abut a portion of their sliding surface 78 against the housing inner surface 70 when they pass the inlet and outlet openings.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Pistons, Piston Rings, And Cylinders (AREA)
  • Cylinder Crankcases Of Internal Combustion Engines (AREA)

Abstract

Dans le cas de moteurs à combustion interne à piston rotatif travaillant selon le principe chat-et-souris, les espaces de travail (30) à l'intérieur du rotor (18), lequel tourne à vitesse uniforme dans le carter (10), doivent être rendus étanches entre eux et par rapport au carter (10). L'étanchéification par rapport au carter (10) est obtenue grâce à des bagues d'étanchéité (72) en une matière céramique. Lesdites bagues d'étancheité sont mobiles radialement dans des rainures annulaires (76) de la paroi du rotor, elles viennent s'appliquer contre la surface interne du carter (70) et entourent les orifices (74) des canaux (34) par lesquels arrive alternativement un mélange carburant-air et s'échappe le gaz brûlé.
PCT/EP1990/002047 1990-01-20 1990-11-29 Moteur a combustion interne a piston rotatif Ceased WO1991010811A1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
JP91500115A JPH05507984A (ja) 1990-01-20 1990-11-29 ロータリーピストン型内燃機関

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DEP4001647.1 1990-01-20
DE4001647 1990-01-20

Publications (1)

Publication Number Publication Date
WO1991010811A1 true WO1991010811A1 (fr) 1991-07-25

Family

ID=6398481

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/EP1990/002047 Ceased WO1991010811A1 (fr) 1990-01-20 1990-11-29 Moteur a combustion interne a piston rotatif

Country Status (2)

Country Link
JP (1) JPH05507984A (fr)
WO (1) WO1991010811A1 (fr)

Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3281064A (en) * 1963-12-18 1966-10-25 Daimler Benz Ag Seal construction
DE1808627A1 (de) * 1968-11-13 1970-06-04 Daimler Benz Ag Dichtleiste fuer eine Rotationskolben-Brennkraftmaschine
DE1751058A1 (de) * 1968-03-27 1971-04-22 Daimler Benz Ag Dichtleiste fuer eine Radialdichtung
DE2165339A1 (de) * 1971-12-29 1973-07-05 Degussa Dichtungswerkstoff, insbesondere fuer dichtleisten in rotationskolbenmotoren
DE2601374A1 (de) * 1975-01-17 1976-07-22 Caterpillar Tractor Co Scheiteldichtung fuer drehkolbenmaschinen
EP0035136A2 (fr) * 1980-02-25 1981-09-09 SABET, Huschang Machine à combustion interne à pistons rotatifs à arbre central
WO1990008879A1 (fr) * 1989-02-03 1990-08-09 Huschang Sabet Moteur a combustion interne a pistons rotatifs

Patent Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3281064A (en) * 1963-12-18 1966-10-25 Daimler Benz Ag Seal construction
DE1751058A1 (de) * 1968-03-27 1971-04-22 Daimler Benz Ag Dichtleiste fuer eine Radialdichtung
DE1808627A1 (de) * 1968-11-13 1970-06-04 Daimler Benz Ag Dichtleiste fuer eine Rotationskolben-Brennkraftmaschine
DE2165339A1 (de) * 1971-12-29 1973-07-05 Degussa Dichtungswerkstoff, insbesondere fuer dichtleisten in rotationskolbenmotoren
DE2601374A1 (de) * 1975-01-17 1976-07-22 Caterpillar Tractor Co Scheiteldichtung fuer drehkolbenmaschinen
EP0035136A2 (fr) * 1980-02-25 1981-09-09 SABET, Huschang Machine à combustion interne à pistons rotatifs à arbre central
WO1990008879A1 (fr) * 1989-02-03 1990-08-09 Huschang Sabet Moteur a combustion interne a pistons rotatifs

Also Published As

Publication number Publication date
JPH05507984A (ja) 1993-11-11

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