EP0101431A2 - Distribution par tiroir multiple - Google Patents

Distribution par tiroir multiple Download PDF

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Publication number
EP0101431A2
EP0101431A2 EP83890129A EP83890129A EP0101431A2 EP 0101431 A2 EP0101431 A2 EP 0101431A2 EP 83890129 A EP83890129 A EP 83890129A EP 83890129 A EP83890129 A EP 83890129A EP 0101431 A2 EP0101431 A2 EP 0101431A2
Authority
EP
European Patent Office
Prior art keywords
slide
rotary
rotary valve
valves
outlet
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Withdrawn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
EP83890129A
Other languages
German (de)
English (en)
Other versions
EP0101431A3 (fr
Inventor
Harald Rus
Georg Dipl. Ing. Enzinger
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 EP0101431A2 publication Critical patent/EP0101431A2/fr
Publication of EP0101431A3 publication Critical patent/EP0101431A3/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Withdrawn legal-status Critical Current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
    • F01L7/04—Rotary or oscillatory slide valve-gear or valve arrangements with cylindrical, sleeve, or part-annularly shaped valves surrounding working cylinder or piston
    • F01L7/045—Rotary or oscillatory slide valve-gear or valve arrangements with cylindrical, sleeve, or part-annularly shaped valves surrounding working cylinder or piston with two or more valves arranged coaxially
    • 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
    • F02B1/00—Engines characterised by fuel-air mixture compression
    • F02B1/02—Engines characterised by fuel-air mixture compression with positive ignition
    • F02B1/04—Engines characterised by fuel-air mixture compression with positive ignition with fuel-air mixture admission into cylinder
    • 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 a multiple slide control, in particular for two and four-stroke engines in single or Aehrylinderausment, with at least two controlling, provided in rotary slide sealing surfaces, which slide in the same direction, pass through openings for the media to be controlled and to control the rotary slide at different speeds are circulated, the slower rotating outer slide having more passage openings than the faster rotating inner slide.
  • the rotary valve In the area of the combustion chamber of reciprocating piston engines for controlling gas exchange operations, the rotary valve is a known such construction element.
  • the rotary slide valve in the cylinder head and / or in the cylinder wall serves to periodically release the inlet and the outlet. It is rotatably mounted and rotates at a rational speed ratio to the crankshaft.
  • the invention has as its object to optimize the gas exchange with the rotary valve, to reduce the dead zones by means of a swirling gas flow, to thermally decouple the inlet and outlet, to make it possible to change the control times during operation with the aid of the phase shift, a simple possibility for Add stratified charge, solve the existing problems of the rotary valve, such as sealing, cooling and reaction forces, and enlarge the duct cross-sections.
  • the outer rotary valve is rotated at half the speed when using two nested rotary valves or the middle rotary valve when using three nested rotary valves than the inner and the opening of the slower rotating rotary valve than separate inlet or outlet valves are designed.
  • the outer rotary valve has a much larger wall thickness, in particular a wall thickness four times as large as the inner one.
  • the invention is characterized in that the speeds of the three rotary valves from the inside to the outside essentially obtained as 2: 1: 2.
  • the outer and the inner rotary valve are arranged in the cylinder head and gears are provided for driving both rotary valves.
  • the inner rotary valve has a greater wall thickness than the outer one.
  • the invention is characterized in that the drive takes place via two gears which can be moved independently of one another. Furthermore, the drive takes place via two gearwheels fastened on a common axis. Furthermore, the invention is characterized by a stratified charge in terms of flow technology, the fatter mixture components being brought into the immediate vicinity of the spark plug through the opening by centrifugal force separation, even during the inflow process, by means of a flow divider.
  • FIG. 6 to 9 represent a further embodiment of this type.
  • FIGS. 10 to 13 show further exemplary embodiments in a more constructive representation.
  • the inlet channel 15 is closed and the opening 11 of the inner rotary valve 2 moves past the inlet 14, so that the inlet channel 15 then remains closed by the full part of the inner rotary valve and compression can take place.
  • the openings 11 of the inner rotary valve 2 and the openings 4, 5 of the outer rotary valve 1 on the one hand and the openings 4, 5 of the outer rotary valve 1 meet with regard to the wall of the cylinder 6 on the other , together at the beginning of the exhaust bar. That is, the gap lengths of the inner rotary valve 2 and the outer rotary valve 1 add up, the same applies to the gap lengths of the outer rotary valve 1 and the channel openings 14, 15 in the cylinder 6.
  • the outer rotary valve 1 has a wall thickness that is approximately four times as large as the inner one.
  • the mode of operation of this rotary slide unit (start of outlet, start of inlet, start of compression and start of the work cycle) is analogously the same as set out above when describing FIGS. 1 to 4.
  • This embodiment Fig. 5 offers a possibility of increasing the opening angle.
  • the radius 16 of the outer rotary valve 1 is increased, as shown.
  • FIG. 5 shows the position of the outlet 5 and the opening 11 in the inner rotary valve 2 to the outlet duct 14 after a 90 ° crank angle outlet.
  • the opening 11 in the inner rotary valve 2 is still congruent with the outlet 5 and the outlet 5 is congruent with the outlet channel 14.
  • the outlet channel 14 is closed by the full wall parts of the inner rotary valve 2.
  • the inner rotary valve 2 rotates twice as fast, double arrow 12, as the outer rotary valve 1, single arrow 13.
  • 6 to 9 illustrate a multiple rotary valve in triple design.
  • This multiple slide is divided into two groups; the first group comprises the inner rotary valve 2 and an orifice 19, the second group consists of the middle rotary valve 3 and the outer rotary valve 1.
  • This second group lies between the orifice 19 and the wall of the cylinder 6.
  • opening angles of 45 ° each opening angles of 45 ° each.
  • the purpose of this construction is therefore also to enlarge the channel cross-sections.
  • the inner rotary valve 2 rotates faster (double arrow 12) than the central rotary valve 3 (single arrow 13).
  • the operation of this triple rotary valve is as follows
  • Outlet Fig. 6.
  • the opening 20 of the outer rotary valve 1 and the opening 21 of the inner rotary valve 2 are seen in the direction of rotation in front of the outlet channel 14.
  • the outlet channel 14 is closed by the fixed wall parts of the outer rotary valve 1 and the inner rotary valve 2.
  • Inlet 4 and outlet 5 of the middle rotary valve 3 enclose an angle 21 of 90 °.
  • the middle rotary valve 3 now moves 22.5 ° twice, which is 45 ° further, see also FIG. 7.
  • the outer rotary valve 1 and the inner rotary valve 2 turn twice 45 °, this is 90 ° further.
  • the openings 20 and 21 are after 45 ° (not 90 0 ) crank angle congruent with the outlet channel 14, inlet 4 and outlet 5 are also congruent with this outlet channel 14.
  • outlet can take place.
  • Inlet Fig. 7.
  • the openings 20 and 21 are seen in the direction of rotation, in front of the inlet channel 15.
  • the inlet channel 15 is closed by the fixed wall parts of the outer rotary valve 1 and the inner rotary valve 2.
  • Inlet and outlet 4, 5 of the central slide valve 3 are open for the inlet.
  • FIGS. 10 and 11 relate to a constructive embodiment of the rotary slide valve construction according to FIGS. 1 to 4.
  • the outer rotary slide valve 1 and the inner rotary slide valve 2 are located in the cylinder head 6 and are driven from the outside via gear wheels 7, 8.
  • FIG. 11 shows a section along the line XI-XI in FIG. 10. This is the simplest installation option for the rotary slide unit.
  • the spark plug 23 is flushed free of incoming fresh gases. As stated, the drive takes place via the separately running gears 7 and 8.
  • the outer rotary valve 1 and the inner rotary valve 2 are located in the cylinder head 6 and are driven from the outside via gear wheels 9, 10.
  • the cut is made as indicated in the other embodiment, Fig. 10 at XII-XII.
  • the thicker inner rotary valve 2 carries the opening 11, which is designed in the shape of a manifold, and the inflowing fresh gas in the direction of ZY. linder redirects.
  • the opening 24 and the flow divider 25 are located on the outside of the manifold.
  • the richer mixture components located here are branched off in the immediate vicinity of the spark plug 23.
  • the size of the inner slide valve 2 creates space for cooling.
  • FIG. 13 shows a section which is performed as indicated in the other embodiment in FIG. 10 under XI-XI.
  • the outer rotary valve 1 and the inner rotary valve 2 are located in the cylinder head 6 and are driven from the outside via separate gear wheels 7, 8.
  • the flow distribution is achieved by the same principles, but on elements of the cylinder head 6. That is, flow divider 25 and opening 24 are components of the cylinder head 6.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Control Of Throttle Valves Provided In The Intake System Or In The Exhaust System (AREA)
  • Valve-Gear Or Valve Arrangements (AREA)
  • Combustion Methods Of Internal-Combustion Engines (AREA)
  • Multiple-Way Valves (AREA)
EP83890129A 1982-08-18 1983-08-12 Distribution par tiroir multiple Withdrawn EP0101431A3 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
AT3128/82 1982-08-18
AT312882 1982-08-18

Publications (2)

Publication Number Publication Date
EP0101431A2 true EP0101431A2 (fr) 1984-02-22
EP0101431A3 EP0101431A3 (fr) 1985-01-23

Family

ID=3545737

Family Applications (1)

Application Number Title Priority Date Filing Date
EP83890129A Withdrawn EP0101431A3 (fr) 1982-08-18 1983-08-12 Distribution par tiroir multiple

Country Status (3)

Country Link
US (1) US4481917A (fr)
EP (1) EP0101431A3 (fr)
JP (1) JPS5993912A (fr)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0745179A4 (fr) * 1994-02-25 1997-12-10 Hansen Engine Corp Moteur a combustion interne dote d'un assemblage de tiroirs de rotation a calage de distribution variable
DE102015005316A1 (de) * 2015-04-27 2016-10-27 Thai Thanh An Ventilvorrichtung mit langsam drehenden Drehventilen für Verbrennungsmotoren

Families Citing this family (20)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CA1292702C (fr) * 1989-06-23 1991-12-03 George Ristin Tiroir rotatif permettant la combustion etagee dans un moteur a combustioninterne
US5111783A (en) * 1990-12-26 1992-05-12 Jack P. Janetatos Rotary valve system for internal combustion engines
US5205251A (en) * 1992-08-05 1993-04-27 Ibex Technologies, Inc. Rotary valve for internal combustion engine
US5315963A (en) * 1993-04-14 1994-05-31 Warf Donald W Sleeve-type rotary valve for an internal combustion engine
US5367989A (en) * 1993-12-06 1994-11-29 Peyer; Peter Valve shutter control
US5572967A (en) * 1994-08-26 1996-11-12 Three Star Enterprises, Inc. Variable roller valve system for internal combustion engine
US5706775A (en) * 1996-04-12 1998-01-13 New Avenue Development Corp. Rotary valve apparatus for internal combustion engines and methods of operating same
US5967108A (en) * 1996-09-11 1999-10-19 Kutlucinar; Iskender Rotary valve system
RU2159857C2 (ru) * 1999-02-25 2000-11-27 Миронов Александр Александрович Двигатель внутреннего сгорания с золотниковым газораспределительным механизмом
US6443110B2 (en) 1999-12-10 2002-09-03 Jamal Umar Qattan Rotary valve head system for multi-cylinder internal combustion engines
US6397795B2 (en) 2000-06-23 2002-06-04 Nicholas S. Hare Engine with dry sump lubrication, separated scavenging and charging air flows and variable exhaust port timing
US7213546B2 (en) 2001-03-21 2007-05-08 Steven Vermeer Engine airflow management system
US6644263B2 (en) 2001-12-04 2003-11-11 Nicholas S. Hare Engine with dry sump lubrication
WO2006096850A2 (fr) * 2005-03-09 2006-09-14 Zajac Optimum Output Motors, Inc. Moteur a combustion interne et procede associe
CZ304349B6 (cs) * 2011-02-28 2014-03-19 Zdeněk Novotný Dvoudobý zážehový motor
US8997627B2 (en) * 2011-04-29 2015-04-07 Paul Michael Passarelli Thermal engine with an improved valve system
US20140338631A1 (en) * 2013-05-17 2014-11-20 Benjamin Ellis Internal combustion engines and related methods
US9903238B2 (en) * 2015-02-11 2018-02-27 Microsteam, Inc. Rotary valve assembly having rotatable throttle and intake assemblies
US10955066B2 (en) 2017-02-21 2021-03-23 Deltavalve, Llc Fluid catalytic cracking unit valve
US10711667B2 (en) * 2018-01-31 2020-07-14 Jonathan TAVERNIER Internal combustion engine with tubular valves and braking system

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GB190921317A (en) * 1909-09-18 1910-05-26 Frederick Thomas Jackson Improvements in or relating to Mud and Splash Guards for Motorcars, Cycles, Motorcycles and the like.
GB191019791A (en) * 1910-08-24 1911-08-24 Thomas Norman Barker Improvements in and relating to Valves and Valve Gear for Internal Combustion Engines.
FR483896A (fr) * 1916-10-31 1917-08-17 William Birrell Perfectionnements aux moteurs à combustion interne
GB151994A (en) * 1920-10-04 1922-04-04 Alessandro Tebaldi Improvements in and relating to internal combustion engines with rotary distributingvalves
GB221841A (en) * 1923-05-15 1924-09-15 Clarence Elmer Bonner Improvements in internal combustion engines of the sleeve-valve type
US1570878A (en) * 1923-11-28 1926-01-26 Burt W Danford Valve structure
GB284941A (en) * 1927-08-02 1928-02-09 Charles Luyckx Improvements in or relating to rotary valves, particularly for internal combustion engines
US1817624A (en) * 1928-01-14 1931-08-04 Frank R Higley Internal combustion engine
FR691555A (fr) * 1930-03-07 1930-10-23 Perfectionnements dans la distribution des moteurs à explosions
DE678268C (de) * 1936-12-25 1939-07-12 Wilhelm Schindele Entlasteter Drehschieber fuer Brennkraftmaschinen
US2401932A (en) * 1945-01-22 1946-06-11 Jack & Heintz Prec Ind Inc Sleeve valve engine
AT184777B (de) * 1950-03-06 1956-02-25 Sebastien Jacques Marie Coic Drehschiebersteuerung für Brennkraftmaschinen
SE347787B (fr) * 1968-03-09 1972-08-14 E Lamperti
US3948241A (en) * 1973-08-02 1976-04-06 Melchior Frederick C Lubricating and sealing system for internal combustion engines

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0745179A4 (fr) * 1994-02-25 1997-12-10 Hansen Engine Corp Moteur a combustion interne dote d'un assemblage de tiroirs de rotation a calage de distribution variable
DE102015005316A1 (de) * 2015-04-27 2016-10-27 Thai Thanh An Ventilvorrichtung mit langsam drehenden Drehventilen für Verbrennungsmotoren
US10371022B2 (en) 2015-04-27 2019-08-06 An THAI THANH Valve apparatus having slowly revolving rotary valves for internal combustion engines

Also Published As

Publication number Publication date
JPS5993912A (ja) 1984-05-30
US4481917A (en) 1984-11-13
EP0101431A3 (fr) 1985-01-23

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Inventor name: ENZINGER, GEORG, DIPL. ING.

Inventor name: RUS, HARALD