EP0016381B1 - Moteur à combustion interne à quatre temps à refroidissement par air, avec tiroir rotatif - Google Patents

Moteur à combustion interne à quatre temps à refroidissement par air, avec tiroir rotatif Download PDF

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Publication number
EP0016381B1
EP0016381B1 EP80101145A EP80101145A EP0016381B1 EP 0016381 B1 EP0016381 B1 EP 0016381B1 EP 80101145 A EP80101145 A EP 80101145A EP 80101145 A EP80101145 A EP 80101145A EP 0016381 B1 EP0016381 B1 EP 0016381B1
Authority
EP
European Patent Office
Prior art keywords
passage
crankcase
cylinder
cylinder head
bore
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
EP80101145A
Other languages
German (de)
English (en)
Other versions
EP0016381A1 (fr
Inventor
Günther Dylla
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.)
Dylla Norbert
Original Assignee
Dylla Norbert
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 Dylla Norbert filed Critical Dylla Norbert
Priority to AT80101145T priority Critical patent/ATE3663T1/de
Publication of EP0016381A1 publication Critical patent/EP0016381A1/fr
Application granted granted Critical
Publication of EP0016381B1 publication Critical patent/EP0016381B1/fr
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
    • F01B—MACHINES OR ENGINES, IN GENERAL OR OF POSITIVE-DISPLACEMENT TYPE, e.g. STEAM ENGINES
    • F01B15/00—Reciprocating-piston machines or engines with movable cylinders other than provided for in group F01B13/00
    • F01B15/007—Reciprocating-piston machines or engines with movable cylinders other than provided for in group F01B13/00 having spinning cylinders, i.e. the cylinders rotating about their longitudinal axis
    • 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
    • F01L7/04—Rotary or oscillatory slide valve-gear or valve arrangements with cylindrical, sleeve, or part-annularly shaped valves surrounding working cylinder or piston
    • 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
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
    • F02B75/00—Other engines
    • F02B75/34—Ultra-small engines, e.g. for driving models
    • 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 invention relates to an air-cooled, rotary valve-controlled four-stroke internal combustion engine with a cylinder liner rotatably mounted about its axis in a bearing bore of the cylinder block, which has a fixedly connected to it, sealingly abutting the cylinder head, forming the rotary slide valve, and via a gear transmission from the crankshaft in Ratio 1: 2 is driven, the bottom having a passage opening and the cylinder head having at least one inlet and one outlet opening, all three of which are arranged on the same diameter.
  • Known rotary vane-controlled four-stroke internal combustion engines of this type are used in practice primarily as model engines, that is to say for driving model aircraft, model ships and model cars. Up to a cubic capacity of about 6 cc, such rotary valve-controlled four-stroke internal combustion engines also work relatively well. With a larger displacement, however, cooling and lubrication is no longer sufficient with air-cooled engines.
  • the heat generated in the rotating cylinder liner must namely be transferred to the cylinder block via its outer wall and from there via cooling fins to the outside air. Some of the heat is also transferred from the bottom of the cylinder liner to the cylinder head.
  • a water-cooled, rotary valve-controlled four-stroke internal combustion engine is also known (US Pat. No. 1,614,634), in which a helical groove which is open towards the cylinder liner is incorporated into the wall of the bearing bore for the cylinder liner.
  • An inlet channel is provided in the cylinder head and communicates with this helical groove via an annular channel.
  • Lubricating oil is pressed into the helical groove through this inlet channel and the ring channel. This lubricating oil lubricates the rotating cylinder liner and then enters the crankcase.
  • the cylinder block is double-walled, with cooling water being pumped through the cavity between the two walls.
  • this known water-cooled internal combustion engine is considerably more expensive than an air-cooled engine due to the water cooling.
  • a water pump, a cooler and a driven fan must also be provided for the cooling water.
  • additional units are also subject to wear and are therefore prone to repair and malfunction. They also increase the overall weight of the engine, which is particularly disadvantageous for model engines.
  • the invention has for its object to provide an air-cooled, rotary valve-controlled four-stroke internal combustion engine of the type mentioned, in which sufficient cooling and lubrication is ensured in a simple manner without essential additional units.
  • At least one first channel extending from the crankcase to the cylinder head is provided, which opens into a second channel on the cylinder head side and that otherwise All-round closed crankcase communicates with the outside air via an inlet channel and an automatically acting valve arrangement, which allows outside air to flow into the crankcase when the piston moves upwards from its lower dead center to its top dead center and closes the inlet channel when the piston moves downward, so that the inlet valve closes Crankcase intake air is displaced through the first and second channels.
  • the rotary valve-controlled four-stroke internal combustion engine achieves excellent cooling and significantly improved lubrication of the cylinder liner by very simple means that do not require any significant design effort. It is only necessary to provide one or expediently several channels acting as cooling air channels in the cylinder block adjacent to the outer wall of the cylinder liner and an outlet channel and the valve arrangement mentioned above in the cylinder block or cylinder head.
  • the piston moving up and down then also serves as a pump for the cooling air. As it moves up, it draws cool outside air into the crankcase. When the piston moves downward, this can only be displaced by the cooling air ducts and the outlet duct, since during the downward movement of the piston, the valve arrangement closes the inlet channel.
  • the air flowing along the outer wall of the cylinder liner cools the cylinder liner, this cooling extending over a larger circumferential area of the cylinder liner, since the latter rotates past the cooling air channels.
  • the cooling air also pulls oil droplets out of the crankcase into the cooling air channel or channels. These oil droplets attach themselves to the outer wall of the cylinder liner and are also taken into the gap between the cylinder liner and the bearing bore when the cylinder liner rotates.
  • the cooling air channels also ensure excellent lubrication, in particular of the parts of the cylinder liner that are distant from the crankshaft.
  • a cylinder liner 3 is rotatable about its axis and can be displaced to a limited extent in the axial direction.
  • the upper end of the cylinder liner 3 is closed by a bottom 4 which is firmly connected to the cylinder liner.
  • This bottom 4 has an eccentrically arranged through bore 5.
  • the bottom 4 rests with a flat sealing surface 4a on the cylinder head 6 and is initially held against the cylinder head 6 with little force by springs, not shown, which act on the flange 7.
  • the cylinder head 6 has an inlet opening 8 and an invisible outlet opening, which is arranged on the same diameter, but which displaces the inlet opening 8 in the circumferential direction. Another opening, which is also arranged on the same diameter, serves to receive a glow plug.
  • the bottom 4 forms a rotary slide valve which interacts with the cylinder head 6.
  • crankcase 9 adjoins the cylinder block 2 at the bottom. Only to simplify the drawings, cylinder block 2 and crankcase 9 are shown in one piece in the exemplary embodiment shown, but in practice both parts are usually manufactured separately and screwed together during assembly.
  • the crankshaft 10 is mounted in the crankcase 9. It carries a pinion 11, which drives the bevel gear 13, which is fixedly connected to the cylinder liner 3, in a 1: 2 ratio via a first bevel gear 12.
  • four, axially parallel grooves 14, which are open towards the outer wall 3a of the cylinder liner 3 and are used as cooling air channels and for the supply of lubricant, are provided in the wall of the bearing bore 1.
  • the grooves 14 extend from the crankcase 9 to approximately the cylinder head 6 over approximately the entire length of the cylinder liner 3.
  • the grooves 14 open into an annular channel 15 which is incorporated into the cylinder head-side end 2a of the cylinder block 2.
  • part of the ring channel 15 is formed by a ring shoulder 1 6 screwed into the sealing surface 4a on the circumference of the base 4.
  • This ring shoulder 16 has at the same time the effect that the sealing surface 4a resting on the cylinder head 6 is reduced and thus the friction between the two parts is reduced. In addition, lubricant can also penetrate better to the remaining sealing surface 4a.
  • An outlet channel 17 provided in the cylinder head 6 opens into the ring channel 15. However, this outlet channel may also be arranged at the end 2a of the cylinder block 2 on the cylinder head side.
  • a valve arrangement is also provided which controls the supply of outside air into the crankcase 9, which is otherwise closed on all sides.
  • this valve arrangement is formed by parts of the crankshaft and a housing part (connecting piece) 18 connected to the crankcase 9.
  • the crankshaft 10 has an axial bore 19 which is open towards the inside of the crankcase 9 and a radial bore 20 which is provided outside the actual crankcase in the region of the housing part 18.
  • the two bores 19 and 20 together form an inlet channel.
  • the housing part 18 surrounding the crankshaft 10 has an inlet opening 21, which extends over part of the circumference of the crankshaft 10 and lies with the radial bore 20 in a radial plane.
  • This inlet opening 21 can extend approximately over half the circumference of the crankshaft 10.
  • the inlet opening 21 is arranged opposite the radial bore 20 such that the radial bore 20 moves in the region of the inlet opening 21 when the piston 22 moves upward from its lower to its upper dead center in the direction A, as shown in FIG. 1.
  • the radial bore 20 rotates in a region of the housing connecting piece 18 which is not covered by the inlet opening 21. The radial bore 20 is thus closed by the nozzle 18 during the downward movement of the piston.
  • the heated exhaust air emerging from the outlet duct 17 can either be discharged into the open or can also be returned to the carburetor V via a connecting line 23.
  • the connecting line 23 prevents any oil droplets still present in the exhaust air from reaching the outside air. At the same time, however, it is also achieved that the oil droplets are supplied to the mixture via the carburetor V and cause additional lubrication between the piston 22 and the cylinder liner 3. So practically no oil is lost.
  • the connecting line 23 is expediently guided outside the cylinder head over a greater length, so that the connecting line 23 also serves as a heat exchanger and the exhaust air flowing through the connecting line 23 is cooled again by the outside air surrounding the connecting line 23.
  • FIGS. 5 and 6 show a further exemplary embodiment, the rotary vane-controlled four-stroke internal combustion engine functioning in the same way as the exemplary embodiment shown in FIGS. 1-4. Parts of the same function are therefore also designated with the same reference symbols, the above description being to be applied analogously.
  • a needle bearing consisting of a plurality of needles 24 is provided between the outer wall 3a of the cylinder liner 3 and the bearing bore 1 of the cylinder head 2.
  • the needles 24 are kept at a distance by cage rings 25.
  • the spaces 26 present between the individual needles 24 form the cooling air ducts in this exemplary embodiment.
  • the oil droplets entrained by the cooling air lubricate the bearing needles 24.
  • an inlet channel 27 is provided in the wall of the crankcase 9.
  • the valve flap 28 of a flutter valve is arranged on the inside of the crankcase 9.
  • the piston 22 moves upward, the valve flap 28 is lifted off the inlet channel 27 and cool outside air can flow into the interior of the crankcase 9.
  • the piston moves downward in direction B, an overpressure is achieved in the crankcase 9, which presses the valve flap 28 against the inner wall of the crankcase 9 and thus closes the inlet channel 27.
  • the cool outside air sucked into the crankcase can now only through the spaces 26, the ring channel 15 and the outlet channel 17 escape.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Cylinder Crankcases Of Internal Combustion Engines (AREA)
  • Lubrication Of Internal Combustion Engines (AREA)

Claims (10)

1. Moteur à combustion interne, à quatre temps, à tiroir rotatif et à refroidissement par air, ce moteur comportant une chemise de cylindre montée de façon à pouvoir tourner sur son axe dans un alésage de palier du bloc-cylindres, cette chemise ayant un fond qui y est assemblé fermement, qui vient s'appliquer hermétiquement sur la culasse et qui forme le tiroir rotatif, tandis qu'elle est entraînée à partir du vilebrequin et via une transmission par engrenages dans le rapport de 1:2, ce fond comportant une ouverture de passage, tandis que la culasse comporte au moins une ouverture d'admission et une ouverture d'échappement, ces trois ouvertures étant toutes disposées sur le même diamètre, caractérisé en ce que, de façon connue en soi, tout près de la paroi extérieure (3a) de la chemise de cylindre (3), dans le bloc-cylindres (2), on prévoit au moins un premier canal (14, 26) s'étendant du logement de vilebrequin (9) essentiellement jusqu'à la culasse (6), ce canal débouchant, du côté de la culasse, dans un deuxième canal (17), tandis que le logement de vilebrequin (9) qui, par ailleurs, est fermé de tous côtés, est mis en communication avec l'atmosphère extérieure via un canal d'admission (19, 20; 27) et un système de soupape (20, 21; 28) fonctionnant automatiquement, ce système de soupape laissant pénétrer l'air extérieur dans le logement de vilebrequin (9) lors de la course ascendante du piston (22) de son point mort bas à son point mort haut tandis que, lors de la course descendante du piston (22), il ferme le canal d'admission (19, 20; 27), si bien que l'air aspiré dans le logement de vilebrequin (9) est chassé à travers le premier et le deuxième canal (14, 26, 17) en vue d'assurer le refroidissement.
2. Moteur suivant la revendication 1, caractérisé en ce que, de façon connue en soi, le premier canal est une rainure (14) usinée dans la paroi de l'alésage de palier (1) et ouverte en direction de la paroi extérieure (3a) de la chemise de cylindre (3).
3. Moteur suivant la revendication 1, caractérisé en ce que la rainure (14) s'étend dans le sens axial de l'alésage de palier (1). ).
4. Moteur suivant les revendications 2 et 3, caractérisé en ce qu'on prévoit plusieurs rainures (14) qui, du côté de la culasse, débouchent dans un canal annulaire (15) connu en soi et communiquant avec le deuxième canal (17).
5. Moteur suivant la revendication 4, caractérisé en ce que le canal annulaire (15) est usiné dans le bloc-cylindres (2) à l'extrémité (2a) de celui-ci, qui est située du côté de la culasse.
6. Moteur suivant la revendication 1, caractérisé en ce que, entre la paroi extérieure (3a) de la chemise de cylindre (3) et l'alésage de palier (1), on prévoit un palier à aiguilles (24, 25), tandis que le premier canal est formé par les espaces intermédiaires (26) ménagés entre les aiguilles (24) du palier.
7. Moteur suivant la revendication 1, caractérisé en ce que le système de soupape (20, 21) est commande par le vilebrequin (10).
8. Moteur suivant la revendication 7, caractérisé en ce que le vilebrequin (10) a un alésage axial (19), un alésage radial (20) étant prévu à l'extérieur du logement de vilebrequin proprement dit (9), ces alésages formant ensemble le canal d'admission, tandis que, dans la zone de l'alésage radial (20), le vilebrequin (10) est entouré d'une pièce formant logement (18) comportant une ouverture d'admission (21) s'étendant sur une partie de la périphérie du vilebrequin (10) et située dans un plan radial avec l'alésage radial (20).
9. Moteur suivant la revendication 1, caractérise en ce que le deuxième canal (17) est relié à un carburateur (V) via une conduite de liaison (23).
10. Moteur suivant la revendication 1, caractérisé en ce que le système de soupape est constitué d'une soupape de retenue (28).
EP80101145A 1979-03-20 1980-03-06 Moteur à combustion interne à quatre temps à refroidissement par air, avec tiroir rotatif Expired EP0016381B1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
AT80101145T ATE3663T1 (de) 1979-03-20 1980-03-06 Luftgekuehlter, drehschiebergesteuerter viertakt- verbrennungsmotor.

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE2910822A DE2910822C2 (de) 1979-03-20 1979-03-20 Luftgekühlter, drehschiebergesteuerter Viertakt-Verbrennungsmotor
DE2910822 1979-03-20

Publications (2)

Publication Number Publication Date
EP0016381A1 EP0016381A1 (fr) 1980-10-01
EP0016381B1 true EP0016381B1 (fr) 1983-06-01

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ID=6065855

Family Applications (1)

Application Number Title Priority Date Filing Date
EP80101145A Expired EP0016381B1 (fr) 1979-03-20 1980-03-06 Moteur à combustion interne à quatre temps à refroidissement par air, avec tiroir rotatif

Country Status (3)

Country Link
EP (1) EP0016381B1 (fr)
AT (1) ATE3663T1 (fr)
DE (1) DE2910822C2 (fr)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE10222751A1 (de) * 2002-05-23 2004-01-08 Heinz Lammert Viertakt-Verbrennungsmotor, Kurbeltrieb für einen Verbrennungsmotor sowie Mehrzylinder-Verbrennungsmotor
US7406938B2 (en) 2003-09-24 2008-08-05 Rcv Engines Limited Cooling mechanisms for rotary valve cylinder engines

Families Citing this family (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
IT1264947B1 (it) * 1993-07-19 1996-10-17 Fin Gef Srl Motore a combustione interna a quattro tempi, di elevata semplicita' meccanica
GB9615063D0 (en) * 1996-07-18 1996-09-04 Lawes Keith T Internal combustion engine
IT1292223B1 (it) * 1997-05-07 1999-01-29 Giorgio Enrico Falck Motore a combustione interna provvisto di distribuzione a fodero rotante
US6289872B1 (en) * 1999-02-04 2001-09-18 Dimitrios Dardalis Rotating sleeve engine
GB0023595D0 (en) * 2000-09-27 2000-11-08 Rcv Engines Ltd Rotating cylinder valve engine

Family Cites Families (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CH57126A (de) * 1911-04-19 1913-01-02 Paul Gerhardt Verbrennungsmotor mit als Zylinderlaufmantel ausgebildetem Drehschieber
GB116170A (en) * 1917-06-16 1918-06-06 Charles Frederick Ryland Improvements in the Valves of Internal Combustion and other Engines.
US1861106A (en) * 1925-12-26 1932-05-31 Jean A H Barkeij Internal combustion engine
US1614634A (en) * 1926-05-03 1927-01-18 Ole O Storle Revolving valve-sleeve gas engine
FR1419038A (fr) * 1964-10-15 1965-11-26 Système rotatif de distribution pour moteurs thermiques à pistons
FR1493527A (fr) * 1966-05-20 1967-09-01 Dispositif d'alimentation de moteur à explosion par chemise tournante
DE2449368A1 (de) * 1973-10-18 1975-04-24 Halder Engines Ltd Zweitakt-verbrennungskraftmaschine
DE2714351A1 (de) * 1977-03-31 1978-10-05 Dylla Norbert Drehschiebergesteuerter viertakt- verbrennungsmotor
DE2822651A1 (de) * 1978-05-24 1979-11-29 Habsburg Lothringen Leopold Vo Drehschiebersteuerung

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE10222751A1 (de) * 2002-05-23 2004-01-08 Heinz Lammert Viertakt-Verbrennungsmotor, Kurbeltrieb für einen Verbrennungsmotor sowie Mehrzylinder-Verbrennungsmotor
DE10222751B4 (de) * 2002-05-23 2004-06-24 Heinz Lammert Viertakt-Verbrennungsmotor, Kurbeltrieb für einen Verbrennungsmotor sowie Mehrzylinder-Verbrennungsmotor
US7406938B2 (en) 2003-09-24 2008-08-05 Rcv Engines Limited Cooling mechanisms for rotary valve cylinder engines

Also Published As

Publication number Publication date
ATE3663T1 (de) 1983-06-15
DE2910822A1 (de) 1980-09-25
DE2910822C2 (de) 1982-12-09
EP0016381A1 (fr) 1980-10-01

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