WO2012159616A1 - Moteur thermique - Google Patents

Moteur thermique Download PDF

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Publication number
WO2012159616A1
WO2012159616A1 PCT/DE2012/100119 DE2012100119W WO2012159616A1 WO 2012159616 A1 WO2012159616 A1 WO 2012159616A1 DE 2012100119 W DE2012100119 W DE 2012100119W WO 2012159616 A1 WO2012159616 A1 WO 2012159616A1
Authority
WO
WIPO (PCT)
Prior art keywords
heat engine
valve
engine according
valves
rotary
Prior art date
Application number
PCT/DE2012/100119
Other languages
German (de)
English (en)
Inventor
Rainer Schnur
Michael Schmidt
Original Assignee
Devetec Gmbh
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 Devetec Gmbh filed Critical Devetec Gmbh
Priority to EP12723089.4A priority Critical patent/EP2710237A1/fr
Publication of WO2012159616A1 publication Critical patent/WO2012159616A1/fr

Links

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
    • F01L7/10—Rotary or oscillatory slide valve-gear or valve arrangements with valves of other specific shape, e.g. spherical
    • 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
    • F01L7/026—Rotary or oscillatory slide valve-gear or valve arrangements with cylindrical, sleeve, or part-annularly shaped valves with two or more rotary valves, their rotational axes being parallel, e.g. 4-stroke
    • 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
    • F02B75/04—Engines with variable distances between pistons at top dead-centre positions and cylinder heads
    • F02B75/041—Engines with variable distances between pistons at top dead-centre positions and cylinder heads by means of cylinder or cylinderhead positioning
    • F02B75/042—Engines with variable distances between pistons at top dead-centre positions and cylinder heads by means of cylinder or cylinderhead positioning the cylinderhead comprising a counter-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
    • F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
    • F01L1/34—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift

Definitions

  • the invention relates to a heat engine with at least one working space forming arrangement of a reciprocating piston and a cylinder, a valve for the inlet of a pressurized working medium in the working space and a valve for the outlet of the relaxed working fluid in the working space.
  • the invention has for its object to provide a new heat engine of the type mentioned above, which allows an improved control of at least the inlet flow of the working medium with a simplified structural design.
  • the heat engine according to the invention which achieves this object is characterized in that at least the inlet valve is designed as a rotary slide valve.
  • the amount of working medium admitted at top dead center can be metered in more accurately by means of such a rotary valve control and more accurately comply with a high expansion ratio associated with high efficiency.
  • the rotary valve at least of the inlet valve coaxial to its axis of rotation, preferably peripheral closure surface for closing an opening of the working space, wherein in the closure surface opens an opening in a rotational position of the rotary valve, the opening for flow through the Working medium releases.
  • the closure surface has the shape of a spherical surface, which is particularly advantageous in terms of sealing effect and low wear.
  • the rotary valve of the inlet valve can be arranged in a standing under the output pressure of the working medium housing interior and be exposed to the respective opening closing section all around the pressure of the working medium.
  • the closure surface slidably bears against a ring seal which surrounds the opening and protrudes in particular against the closure surface.
  • the closure surface is formed by a polished metal surface, while the ring seal is e.g. made of a plastic.
  • a plurality of piston-cylinder assemblies arranged in a row are provided, and the rotary valves of at least the inlet valves are rotatable by a common shaft extending along the row.
  • At least the intake valves may be integrated into a cylinder head assembly common to the plurality of piston-and-cylinder assemblies.
  • the working space is connected to a, preferably for varying the amount of intake of working fluid in its volume adjustable, secondary chamber, wherein in particular the cylinder head assembly in addition to the intake valves and possibly exhaust valves may have such secondary chambers.
  • the cylinder head assembly comprises a housing corresponding to the above housing for receiving all Rotary valve of the inlet valves and their common shaft, wherein the interior of the housing can be acted upon by the pressure of the working medium.
  • the shaft common to the rotary valves of the intake valves is preferably mounted gas-tight in front side walls of this housing.
  • the cylinder head assembly may have another housing extending parallel to said housing for receiving all the rotary valves of the exhaust valves and their common shaft.
  • the diameter of the rotary valve of the inlet valve or the intake valves is greater than the diameter of the rotary valve of the exhaust valve or the exhaust valves.
  • the larger diameter of the rotary valve of the inlet valve advantageously allows the flow rate of larger amounts of working fluid within the short, at the top dead center for the inlet of the working fluid available time.
  • the cylinder head assembly further comprises a connected to the other housing, preferably extending parallel to said housings outlet channel for the relaxed working medium.
  • the phase position of the aperture in the closure surface of the rotary valve or the rotary valve with respect to the position of the associated piston is adjustable.
  • This adjustment possibility in particular in conjunction with the adjustability of the volume of the secondary chamber or secondary chambers, allows adaptation of the heat engine to different operating conditions, including different working media.
  • Fig. 1 shows a heat engine according to the invention in a cut
  • FIG. 2 shows a cylinder head assembly of the heat engine of Fig. 1 in a sectional plan view
  • FIG. 3 shows the cylinder head assembly of FIG. 2 in a view from below
  • FIG. 4 shows an intake valve rotary valve used in the heat engine of FIG. 1;
  • Fig. 5 is a rotary valve used in the heat engine of Fig. 1 for exhaust valves
  • a working in two-stroke heat engine has four arranged in a row cylinder 1, each with a reciprocating piston 2.
  • Reciprocating piston 2 and cylinder 1 each form a working or expansion space 3.
  • a moving through the piston 2 crankshaft is not shown.
  • One of the four piston-cylinder assemblies common cylinder head assembly 4 comprises a corresponding number of intake and exhaust valves, each with a rotary valve 5 and 6.
  • the four rotary valve 5 of the intake valves are rotationally fixed on a common shaft 7, the rotary valve 6 of the exhaust valves in the same On a shaft 8.
  • the shaft 7 with the rotary valves 5 is in a housing 9, the shaft 8 with the rotary valves 6 in a housing 10 of the
  • Cylinder head assembly 4 housed.
  • the housing 9 has an inlet 35 for a working medium, e.g. for water vapor. Over the length of both housings 9,10 extends a connected to the interior of the housing 10 outlet channel 1 1 for the relaxed working medium.
  • Each piston-cylinder arrangement is further associated with an associated with the respective working space 3, integrated into the cylinder head assembly 4 auxiliary chamber 12 whose volume is adjustable by a piston 13.
  • the shafts 7, 8 are rotatably mounted at the ends of the respective housings 9, 10 at 14 and 15 or 16 and 17, preferably by roller bearings.
  • the housing 10 for the rotary valves 6 of the outlet valves and the outlet channel 11 are approximately in the middle, and the housing 9 for the rotary valves 5 of the inlet valves and the secondary chambers 12 are laterally attached thereto. assigns. This arrangement makes it possible to make the cylinder head assembly compact with low material cost and high stability.
  • the rotary valve 5 each have a peripheral, coaxial with the axis of rotation closure surface 18 in the form of a spherical surface.
  • the polished closure surface 18 serving as control openings openings 19 and 20 are formed.
  • Further openings 21 are located between spokes 39 which connect a hub 23 and an outer ring 23 forming the closure surface 18.
  • the hub 22 has a central, a sliding fit forming bore 24 for the passage of the shaft 7.
  • the slotted hub 22 can be mounted on the shaft 7 in desired rotational positions.
  • the spherical, metallic closure surface 18 of the rotary valve 5 is in each case slidably against an annular seal 26 made of carbon, graphite or / and a plastic which a mouth opening of a scavenging or connecting channel 27 between the interior 36 of the Housing 9 and the relevant working space 3 surrounds.
  • Each of the two openings 19,20 is associated with such a flushing or connecting channel 27.
  • the rotary valve 6 shown separately in FIG. 5 has a spherical closure surface 28 with a recess 29, into which a through-opening 38 opens.
  • hub portions 30 are penetrated by a central, a sliding seat forming bore 31 for receiving the shaft 8.
  • connection channels 27 and 34 illustrate FIGS. 6 and 7.
  • the connecting channels 27 in each case surrounds a sealing ring 40 abutting against the relevant closure surface 18, which has a slotted supporting ring 41 and a not shown corrugated spring ring on an annular shoulder 42 of an annular insert 43 is seated. On the annular shoulder 42, a sealing O-ring 44 is further arranged.
  • the insert 43 with the rings 40,41 hold a threaded insert 45 and a locking plate 46 in place.
  • Threaded insert 45 is followed by a working space volume reducing filler 47 with a bevel 48 which is held axially by a groove 49 engaging in a spring ring 50.
  • a rotation lock is not shown pin.
  • the connecting channels 34 surrounds a sealing ring 51, to which a support ring 52 supporting the sealing ring adjoins.
  • the support ring 52 bears against an annular shoulder (not shown) in the interior of an insert 53.
  • a sealing O-ring 55 is arranged on an outer annular shoulder 54 of the insert 53.
  • a threaded ring 56 holds the insert 53 via a locking plate 57 in place.
  • the sealing ring 40 or 51 bears against the relevant closure surface 18 or 28 under tension. Abrasions are automatically compensated.
  • the working medium e.g. Water vapor
  • the openings 19,20 are aligned in the closure surface 18 of one of the rotary valve 5 to the respective connecting channels 27, working fluid can temporarily enter the working space 3 of the relevant piston-cylinder assembly.
  • the rotary valve 5 of the intake valves in diameter at least by a factor of 2.5 larger than the diameter of the rotary valve 6 of the exhaust valves, and two scavenging ports 27 are provided, there is a sufficiently larger passage cross-section to the respective working space within a short time sufficient fill.
  • the recess 29 with the passage opening 38 of the rotary valve 6 is in each case connected to the relevant connection. aligned channel 34, so that during the lifting movement of the piston 3, the relaxed working fluid can pass through the interior of the housing 10 into the outlet channel 1 1.
  • Deviating from the exemplary embodiment shown, devices could be provided which enable an adjustment of both the volumes of the secondary chambers and the valve timing during machine operation.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Valve-Gear Or Valve Arrangements (AREA)
  • Cylinder Crankcases Of Internal Combustion Engines (AREA)

Abstract

L'invention concerne un moteur thermique comprenant au moins un agencement formant un compartiment de travail (3) et constitué d'un piston de levée (2) et d'un cylindre (1), une soupape pour l'admission d'un fluide de travail sous pression dans le compartiment de travail (3) et une soupape pour la sortie du fluide de travail du compartiment de travail (3). Selon l'invention, au moins la soupape d'admission est conçue comme une soupape à tiroir rotatif.
PCT/DE2012/100119 2011-05-20 2012-04-27 Moteur thermique WO2012159616A1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
EP12723089.4A EP2710237A1 (fr) 2011-05-20 2012-04-27 Moteur thermique

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE201110076157 DE102011076157A1 (de) 2011-05-20 2011-05-20 Wärmekraftmaschine
DE102011076157.8 2011-05-20

Publications (1)

Publication Number Publication Date
WO2012159616A1 true WO2012159616A1 (fr) 2012-11-29

Family

ID=46148595

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/DE2012/100119 WO2012159616A1 (fr) 2011-05-20 2012-04-27 Moteur thermique

Country Status (3)

Country Link
EP (1) EP2710237A1 (fr)
DE (1) DE102011076157A1 (fr)
WO (1) WO2012159616A1 (fr)

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102013212805A1 (de) 2013-07-01 2015-01-08 Evonik Industries Ag Verwendung von hoch effizienten Arbeitsmedien für Wärmekraftmaschinen

Citations (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US411944A (en) * 1889-10-01 Valve for steam-engines
GB191323123A (en) * 1913-10-13 1914-10-13 Harold Wade Improvements in or relating to Valves for Internal Combustion Engines.
GB191402879A (en) * 1914-02-04 1914-11-12 John William James Improvements in Valves for Internal Combustion and other Engines.
JPS5431818A (en) * 1977-08-17 1979-03-08 Sunao Igarashi Rotary valve engine
EP0071478A1 (fr) * 1981-07-30 1983-02-09 George Jennings Coates Moteur à combustion interne
US5655494A (en) * 1994-08-26 1997-08-12 Three Star Enterprises, Inc. Variable roller valve system for internal combustion engine
US5711265A (en) * 1996-07-22 1998-01-27 Duve; Donald A. Rotary valve drive mechanism
US6158465A (en) * 1998-05-12 2000-12-12 Lambert; Steven Rotary valve assembly for engines and other applications
WO2001042628A1 (fr) * 1999-12-10 2001-06-14 Jamal Umar Qattan Systeme de tetes de soupapes rotatives pour moteurs a combustion interne polycylindriques
WO2008080929A1 (fr) * 2006-12-28 2008-07-10 Perkins Engines Company Limited Soupape rotative pour moteur à combustion interne
DE102008058585A1 (de) 2008-11-22 2010-05-27 Netzsch-Feinmahltechnik Gmbh Rührwerkskugelmühle
DE102009024436A1 (de) 2009-06-05 2010-12-16 Devetec Gmbh Wärmekraftmaschine

Patent Citations (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US411944A (en) * 1889-10-01 Valve for steam-engines
GB191323123A (en) * 1913-10-13 1914-10-13 Harold Wade Improvements in or relating to Valves for Internal Combustion Engines.
GB191402879A (en) * 1914-02-04 1914-11-12 John William James Improvements in Valves for Internal Combustion and other Engines.
JPS5431818A (en) * 1977-08-17 1979-03-08 Sunao Igarashi Rotary valve engine
EP0071478A1 (fr) * 1981-07-30 1983-02-09 George Jennings Coates Moteur à combustion interne
US5655494A (en) * 1994-08-26 1997-08-12 Three Star Enterprises, Inc. Variable roller valve system for internal combustion engine
US5711265A (en) * 1996-07-22 1998-01-27 Duve; Donald A. Rotary valve drive mechanism
US6158465A (en) * 1998-05-12 2000-12-12 Lambert; Steven Rotary valve assembly for engines and other applications
WO2001042628A1 (fr) * 1999-12-10 2001-06-14 Jamal Umar Qattan Systeme de tetes de soupapes rotatives pour moteurs a combustion interne polycylindriques
WO2008080929A1 (fr) * 2006-12-28 2008-07-10 Perkins Engines Company Limited Soupape rotative pour moteur à combustion interne
DE102008058585A1 (de) 2008-11-22 2010-05-27 Netzsch-Feinmahltechnik Gmbh Rührwerkskugelmühle
DE102009024436A1 (de) 2009-06-05 2010-12-16 Devetec Gmbh Wärmekraftmaschine

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
ROBERT H. THURSTON: "A History of the Growth of the Steam-Engine", 31 December 1878, D. APPLETON AND COMPANY, New York, article CHAPTER IV: "The modern steam engine", XP002686096 *

Also Published As

Publication number Publication date
DE102011076157A1 (de) 2012-11-22
EP2710237A1 (fr) 2014-03-26

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