EP2240674B1 - Zweitakt-maschine mit gegenläufigen radialdrehkolben - Google Patents

Zweitakt-maschine mit gegenläufigen radialdrehkolben Download PDF

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Publication number
EP2240674B1
EP2240674B1 EP08719206.8A EP08719206A EP2240674B1 EP 2240674 B1 EP2240674 B1 EP 2240674B1 EP 08719206 A EP08719206 A EP 08719206A EP 2240674 B1 EP2240674 B1 EP 2240674B1
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EP
European Patent Office
Prior art keywords
oil
plungers
pistons
inner sidewalls
gap
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.)
Active
Application number
EP08719206.8A
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English (en)
French (fr)
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EP2240674A4 (de
EP2240674A2 (de
Inventor
Evgeniy Khoronskiy
Boris Moukhaev
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.)
Khoronskiy Evgeniy
Moukhaev Boris
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Individual
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Priority claimed from US11/827,595 external-priority patent/US7584726B2/en
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Publication of EP2240674A2 publication Critical patent/EP2240674A2/de
Publication of EP2240674A4 publication Critical patent/EP2240674A4/de
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Publication of EP2240674B1 publication Critical patent/EP2240674B1/de
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Classifications

    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02BINTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
    • F02B75/00Other engines
    • F02B75/28Engines with two or more pistons reciprocating within same cylinder or within essentially coaxial cylinders
    • F02B75/282Engines with two or more pistons reciprocating within same cylinder or within essentially coaxial cylinders the pistons having equal strokes
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01BMACHINES OR ENGINES, IN GENERAL OR OF POSITIVE-DISPLACEMENT TYPE, e.g. STEAM ENGINES
    • F01B1/00Reciprocating-piston machines or engines characterised by number or relative disposition of cylinders or by being built-up from separate cylinder-crankcase elements
    • F01B1/06Reciprocating-piston machines or engines characterised by number or relative disposition of cylinders or by being built-up from separate cylinder-crankcase elements with cylinders in star or fan arrangement
    • F01B1/0603Reciprocating-piston machines or engines characterised by number or relative disposition of cylinders or by being built-up from separate cylinder-crankcase elements with cylinders in star or fan arrangement the connection of the pistons with an element being at the outer ends of the cylinders
    • F01B1/0606Reciprocating-piston machines or engines characterised by number or relative disposition of cylinders or by being built-up from separate cylinder-crankcase elements with cylinders in star or fan arrangement the connection of the pistons with an element being at the outer ends of the cylinders with cam-actuated distribution member(s)
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01BMACHINES OR ENGINES, IN GENERAL OR OF POSITIVE-DISPLACEMENT TYPE, e.g. STEAM ENGINES
    • F01B7/00Machines or engines with two or more pistons reciprocating within same cylinder or within essentially coaxial cylinders
    • F01B7/02Machines or engines with two or more pistons reciprocating within same cylinder or within essentially coaxial cylinders with oppositely reciprocating pistons

Definitions

  • the invention relates to opposite radial rotary-piston engines that can be utilized in ground vehicles, water vehicles, aircraft, in combinations with generators, etc.
  • centrifugal-piston or rotary-piston engines which are intended to eliminate certain disadvantages of conventional piston engines.
  • ORPE centrifugal-piston or rotary-piston engines
  • Such constructions are described in DE3907307 , US6279518 , WO2005098202 , RU2143572 , JP7113452 .
  • the latter has the purpose "to suppress the side pressure applied to a piston, improve efficiency, reduce vibration and drastically reduce dimension and weight, by revolving a cam on the inner wall of an ellipse without using a crank, in reciprocating motion.”
  • the other above indicated constructions typically have similar purposes.
  • DE3907307 discloses a four-stroke engine wherein a cylinder block revolves inside a rotor, which is complicated, has a small resource of the valve system, and a des-balance with the revolving system including movable parts.
  • US6279518 discloses a four-stroke engine having a valve system and a conically shaped rotor.
  • Fig. 7 shows a conical rotor with an elliptical groove, and a series of pistons followers inside the groove. It is a complicated unit with substantial friction losses, which has a limited operation resource for its loaded parts. The construction does not eliminate the side forces exerted by the piston upon the cylinder walls.
  • RU 2143572 discloses a four-stroke engine, wherein the cylinder block revolves at an elliptical trajectory, and the inlet /outlet system includes a rotatable valve.
  • the construction is complicated and difficult to balance (which is admitted by its author).
  • the piston acts via its rod and a sliding bearing upon an elliptical housing. The place of contact with the housing experiences high friction and heating, and thus will have a short operation resource.
  • That engine however has also certain drawbacks and limitations. It is built as a four-stroke engine having a cylinder block revolving around and impelling a rotor. Reaction forces produced in support bearings are very significant that leads to a short operation resource period. It uses an inlet / outlet system based on a rotatable sliding valve. This necessitates the use of complicated sealing means that, as a rule, have very limited operation resource (typically 100 hours maximum). The rotating cylinder block with linearly reciprocating pistons is very hard to balance, and thusly will cause intensive destructive vibrations. These problems are successfully resolved in the present invention.
  • the inventive ORPE employs the mentioned non-typical form of conversion of the spinning motion of a rotor into a progressive linear stroke of a piston, and vice versa.
  • This constructive solution provides for substantial absorption of side forces exerted by the piston onto engine cylinder's walls and vice-versa, and for an essential improvement of the weight and fuel consumption / power output ratios, demonstrating useful advantages over all presently utilized engines known to the inventors, including the Wankel rotor engine.
  • the most important advantages of the invention are a simple design, low mass, long operation resource (supposedly over 1,000,000 km), low fuel consumption and high power torque, low level of pollutions (environmentally-friendly).
  • the engine's weight (without attached devices) is estimated about 30 kg. It has a displacement of 500 cc, and should deliver a 250 horse-power. In a more powerful version, the engine's own weight is estimated 65 kg (without attached devices), having a displacement of 1000 cc and should deliver a 500 horse-power.
  • the engines as described in the invention may be employed in different applications, such as for joint operation with generators, water and surface vehicles motors, for aircraft motors, and capable to successfully compete with traditional internal combustion engines.
  • the design solutions embodied in the engine's lubrication and cooling systems allow exploiting the engine at 12000-15000 rpm, which can provide for an efficient motor sports application.
  • the construction described in the present disclosure allows developing and manufacturing engines fueled by gasoline or natural gas, as well as diesel type engines employing the inventive principles.
  • the present disclosure describes a two-stroke opposite rotary-piston engine that comprises a cylinder block including a sleeve and two pistons slidely disposed therein arid oppositely movable, which pistons are forming a common combustion chamber situated between their heads, and forming a first gap with sleeve's sidewalls; a rotor having a surface formed by an ellipse or Cassini line; traverses attached to the pistons; rollers attached to the traverses and springly depressed against the rotor; oil tubes with end bushings; oil supply and withdraw means; two plungers disposed in each tube forming a second gap with the tube's sidewalls, essentially less than the first gap.
  • the plungers are attached to the traverses and oppositely movable, also including through throttling channels, outward surfaces forming external spaces with the bushings, and inward surfaces forming an internal space with the tube sidewalls, which internal space communicates with the oil supply means and the oil withdraw means.
  • Engine's oil drain means communicate the external spaces with the oil supply means. The engine absorbs side and inertial forces, is more efficient and clean.
  • FIGS. 1a, 1b , 2a, 2b , 3a, and 3b An embodiment of the inventive engine, fueled by gasoline, is illustrated in FIGS. 1a, 1b , 2a, 2b , 3a, and 3b .
  • the engine comprises a stationary cylinder block (1) fixedly mounted, e.g. on a vehicle; a cylindrically shaped sleeve (2) mounted to the block 1; two oppositely movable cylindrical pistons (3) slidely snug-fitting in the sleeve 2.
  • a first gap between the piston 3 and the sidewalls of the sleeve 2 is made in the size of about 50 micrometers.
  • the opposite pistons 3 each includes a bottom head.
  • the surfaces of the bottom heads and a portion of sidewalls of the sleeve 2 (between the bottom heads) collectively form a common work chamber and a common combustion chamber.
  • the block 1 includes a supporting bearing (preferably ball-bearing).
  • a spark-plug (16) and an injector (17) are installed in the block 1.
  • the block 1 and sleeve 2 include an inlet port (12) and outlet port (13), preferably milled out therein, to provide air supply and combustion products exhaust correspondingly.
  • the air supply is introduced from a supercharging air compressor (14), in this embodiment mechanically driven by the engine. In other embodiments, it may be driven by other means.
  • the compressor 14 is connected to the inlet port 12.
  • the engine comprises two fork-shaped traverses (4), each aforesaid traverse 4 is coupled with one of the pistons 3 by means of lock-nuts with a female threading screwable on a male threading of the traverse.
  • the threading connection allows adjusting the compression ratio within a range of from 8 to 11 during the assembly process.
  • the engine comprises supporting rollers (5) to transmit forces from the pistons 3 and traverses 4, which rollers 5 are mounted to the traverses 4 by means of pins (not shown).
  • the engine comprises a stationary housing (11) fixedly mounted, e.g. on a vehicle.
  • the housing 11 includes a supporting bearing (10) (preferably, a ball bearing).
  • a supporting bearing 10 (preferably, a ball bearing).
  • FIGS. 1a, 1b , 2a, 2b the housing 11 is conventionally shown vertically positioned, though in reality it is typically positioned horizontally.
  • the housing 11 is filled up with oil for lubrication and other purposes as described further in the disclosure.
  • the engine comprises a rotor (8), having a closed inner operation surface formed by a predeterminedly curved line, for example, a closed symmetrical ellipse-type line or Cassini line mentioned hereinabove.
  • the rotor 8 is mounted on the supporting bearing installed within the housing 11 and on the supporting bearing installed within the cylinder block 1.
  • the engine comprises a rotatable power takeoff shaft (9) mounted at least on the supporting bearing 10.
  • the shaft 9 is fixed to the rotor 8.
  • the rotation torque of the rotor 8 is transmitted to the shaft 9 and can be further conveyed to a transmission.
  • the traverses 4 interact with springs (7), which springs depress the supporting rollers 5 against the rotor 8, providing for a mild unstressed engaging at engine's start.
  • the engine comprises an oil supply conduit (19) of low pressure with a reverse valve (not shown) mounted therein, and an oil withdraw conduit (20) of high pressure with a reverse valve and a pressure-reduction valve (both not shown) mounted therein.
  • the conduits 19 and 20 are connected to the housing 11, and used at least for lubrication of the engine and other purposes disclosed below.
  • the engine comprises an oil pump, shown in FIGS. 3b , 4a, 4b including two sections, each comprising a tube (15) and two opposite plungers (6) slidely snug-fitting within each tube 15.
  • Each plunger 6 has a piston portion and a rod portion.
  • the rod portions of plungers 6 are attached to the traverses 4 (as shown in FIG. 3b ) by means of pins (not shown).
  • a second gap between the pump tube 15 and the plungers 6 is made in the size of about 2 - 4 micrometers, i.e. essentially less than the first gap.
  • the tube 15 has an oil suction inlet connected to the oil supply conduit 19 and an oil discharge outlet connected to the oil withdraw conduit 20, which inlet and outlet are drilled in the pump tubes, as depicted in FIGS. 4a and 4b .
  • the oil pump includes guide bushings (18) coupled to both the ends of each tube 15, as shown in FIG. 4a .
  • the bushings 18 serve to close the tube 15 at its ends, and to guide the linear movement of the rod portion of plunger 6.
  • FIGS. 4a and 4b show: inward head surfaces (D) of the piston portions of plungers 6 inside the tube 15, so that the two surfaces D are facing each other; outward surfaces (C) of the piston portions of plungers 6 facing the bushings 18; an internal space (A) formed between the inward surfaces D and the inner sidewalls of the tube 15; external spaces (B) formed between the outward surfaces C, the rod portion sidewalls and the inner sidewalls of the bushings 18.
  • the oil pump includes two oil drain pipes (21), each communicating the external spaces B with the oil suction inlet ( FIGS. 4a and 4b ).
  • Each plunger 6 includes a through throttling channel (22) drilled preferably along the longitudinal axe of plunger 6 with a predeterminedly small diameter to provide necessary resistance to the oil cross-flow therethrough.
  • the purpose of making the channel 22 is to prevent the device from destroying by a hydro-impact during its operation.
  • the channel 22 has a perpendicular through portion capable to communicate the channel 22 with the space B.
  • a first function is the pumping of oil, which is a regular lubrication function common for an oil pump.
  • a second function of the plungers 6 is the absorption of side forces caused by the interaction between the rollers 5 and the rotor 8. Since the gap between the sleeve 2 and the piston 3 is essentially greater than the gap between the pump tube 15 arid the plunger 6 (the size of 50 micrometers against the size of from 2 micrometers to 4 micrometers respectively), the plunger 6 absorbs the aforesaid side forces.
  • a third function of the plungers 6 is the providing for parallel movement of the pistons 3 within the sleeve 2 due to the absorption of aforesaid side forces.
  • a fourth function of the plungers 6 is the providing for a predetermined volume of the combustion chamber and for absorption of inertial forces developed by the pistons 3 and substantially exerted onto the rotor 8. This is achieved due to operation of the plungers 6 as "hydro-lock" valves in a hydro-system in the uppermost and lowermost dead points of the piston's traveling.
  • FIG. 1b illustrates the positions of the pistons 3 with the traverses 4 situated in the uppermost dead-point wherein a common combustion chamber is formed by the pistons' heads and a respective portion of the sleeve's inner sidewalls (the uppermost dead-point corresponds to the minimal volume of the common combustion chamber).
  • a spark is produced by the spark-plug 16, igniting the fuel-air mixture in the combustion chamber that moves the pistons 3 with the traverses 4 in the opposite directions.
  • the rollers 5 depress the rotor's inner curved operation surface, impelling the rotor 8 to spin, which rotates the takeoff shaft 9.
  • the inlet port 12 and outlet port 13 are opened that provides for blowing the combustion products out and filling up the cylinder's sleeve 2 with a portion of fresh air supplied by the compressor 14.
  • the rotor 8 spins due to inertia, pushing the pistons 3 via the rollers 5 and traverses 4, which results in the movement of pistons towards each other up to the uppermost dead-point, compressing the air in the sleeve 2.
  • the pistons 5 pass the inlet port 12 and the outlet port 13, a portion of fuel is injected into the combustion chamber through the injector 17.
  • the mixture of fuel and air is intensely intermingled in the chamber up to the uppermost dead-point position of the pistons 3 (shown in FIG. 1b ).
  • the space A is contracting ( FIG. 4b ) and oil is ejected therefrom by the surfaces D into the withdraw conduit 20 via the oil discharge outlet. After the surface D passes the oil suction inlet, the oil left in the space A is confined and forms a hydro-lock in the space A, which determines the position of the uppermost dead-point of the engine.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Lubrication Of Internal Combustion Engines (AREA)
  • Hydraulic Motors (AREA)
  • Actuator (AREA)

Claims (3)

  1. Zweitaktmotor mit gegenläufigen Radialdrehkolben, der Folgendes umfasst:
    ein unbewegliches Gehäuse,
    einen unbeweglichen Zylinderblock, der mit dem Gehäuse zusammengebaut ist, wobei der Block Folgendes einschließt:
    eine zylindrisch geformte Buchse, die innere Seitenwände hat, und zwei zylindrische Kolben, die jeweils einen unteren Kopf haben, der dem anderen gegenüberliegt, wobei die Kolben gleitend in der Buchse angeordnet sind, so dass ein erster Spalt mit einer vorbestimmten Größe zwischen den inneren Seitenwänden der Buchse und den Kolben gebildet wird, wobei die Kolben entgegengesetzt im Verhältnis zueinander beweglich sind, so dass eine gemeinsame Arbeitskammer und eine gemeinsame Verbrennungskammer durch die unteren Köpfe und die inneren Seitenwände der Buchse gebildet wird,
    einen Rotor, der eine geschlossene innere Betriebsfläche hat, die durch eine auf vorbestimmte Weise gekrümmte Linie gebildet wird, wobei der Rotor drehbar im Wesentlichen durch das Gehäuse und den Zylinderblock getragen wird,
    zwei Querstücke, die jeweils an einem der Kolben befestigt sind,
    eine Anzahl von Stützrollen, die an jedem der Querstücke befestigt sind, wobei die Rollen federnd gegen den Rotor niedergedrückt werden,
    zwei unbewegliche Ölpumpröhren, wobei die Röhren von beiden Enden mit Führungsmuffen verschlossen sind, wobei die Röhren innere Seitenwände der Röhre einschließen, wobei die Muffen innere Seitenwände der Muffen einschließen,
    Ölzufuhrmittel, um wenigstens Öl in die Röhren zuzuführen, Ölabzugsmittel, um wenigstens Öl aus den Röhren abzuziehen,
    zwei Tauchkolben, die gleitend innerhalb jeder der Röhren angeordnet sind, so dass ein zweiter Spalt mit einer vorbestimmten Größe zwischen den Tauchkolben und den inneren Seitenwänden der Röhre gebildet wird, wobei die Größe des ersten Spalts im Wesentlichen größer ist als die Größe des zweiten Spalts, wobei die Tauchkolben an den Querstücken befestigt und entgegengesetzt im Verhältnis zueinander beweglich sind, wobei sie durch die Führungsmuffen geführt werden, wobei die Tauchkolben jeweils einen Längsdurchgang-Drosselkanal und eine Außenfläche einschließen, wobei die inneren Seitenwände der Muffen und die Außenflächen im Wesentlichen zwei äußere Räume bilden, wobei die Tauchkolben jeweils eine Innenfläche einschließen, wobei die Innenflächen und die inneren Seitenwände der Röhre einen inneren Raum bilden, wobei der innere Raum in Verbindung mit den Ölzufuhrmitteln und den Ölabzugsmitteln steht, und
    Ölableitungsmittel zum Verbinden der äußeren Räume mit den Ölzufuhrmitteln.
  2. Motor nach Anspruch 1, wobei
    die auf vorbestimmte Weise gekrümmte Linie entweder eine geschlossene symmetrische Linie vom Ellipsentyp oder eine Cassini-Kurve ist.
  3. Motor nach Anspruch 1, wobei
    die vorbestimmte Größe des ersten Spalts im Wesentlichen gleich 50 Mikrometer ist und die vorbestimmte Größe des zweiten Spalts aus dem Bereich von 2 bis 4 Mikrometer gewählt ist.
EP08719206.8A 2007-07-12 2008-01-16 Zweitakt-maschine mit gegenläufigen radialdrehkolben Active EP2240674B1 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
US11/827,595 US7584726B2 (en) 2007-01-19 2007-07-12 Two-stroke opposite radial rotary-piston engine
PCT/IB2008/000471 WO2008087554A2 (en) 2007-01-19 2008-01-16 Two-stroke opposite radial rotary-piston engine

Publications (3)

Publication Number Publication Date
EP2240674A2 EP2240674A2 (de) 2010-10-20
EP2240674A4 EP2240674A4 (de) 2013-08-28
EP2240674B1 true EP2240674B1 (de) 2016-01-13

Family

ID=41728597

Family Applications (1)

Application Number Title Priority Date Filing Date
EP08719206.8A Active EP2240674B1 (de) 2007-07-12 2008-01-16 Zweitakt-maschine mit gegenläufigen radialdrehkolben

Country Status (10)

Country Link
EP (1) EP2240674B1 (de)
JP (1) JP5074589B2 (de)
KR (1) KR101368521B1 (de)
AU (1) AU2008206784A1 (de)
DK (1) DK2240674T3 (de)
EA (1) EA201070142A1 (de)
ES (1) ES2561107T3 (de)
MX (1) MX2010000487A (de)
UA (1) UA99472C2 (de)
ZA (1) ZA201001021B (de)

Family Cites Families (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE372808C (de) * 1921-11-01 1923-04-05 Hermann Michel Verbrennungskraftmaschine mit feststehenden Zylindern und umlaufenden Schwungmassen
JPS5261609A (en) * 1975-11-17 1977-05-21 Combustion Res & Tech Reciprocating motion rotary engine
EP0280200B1 (de) * 1987-02-25 1992-05-06 Sampower Oy Kraftaggregat
AUPM982794A0 (en) 1994-12-02 1995-01-05 Advanced Engine Technology Pty Ltd New and improved rotary engine
SE508377C2 (sv) * 1996-07-12 1998-09-28 Gul & Co Dev Ab Anordning vid kraftmaskin med två kolvar
SE508376C2 (sv) * 1996-07-12 1998-09-28 Gul & Co Dev Ab Smörjanordning vid förbränningsmotor med kraftöverföring via ett kamkurvespår
AUPO157396A0 (en) 1996-08-09 1996-09-05 Aust Tech Pty. Ltd. Improvements in axial piston rotary engines
US6948458B2 (en) * 2003-02-12 2005-09-27 Amorn Ariyakunakorn Two-way cylinder engine

Also Published As

Publication number Publication date
KR20100045996A (ko) 2010-05-04
EA201070142A1 (ru) 2010-10-29
KR101368521B1 (ko) 2014-02-27
ZA201001021B (en) 2012-09-29
DK2240674T3 (en) 2016-02-29
AU2008206784A1 (en) 2008-07-24
EP2240674A4 (de) 2013-08-28
ES2561107T3 (es) 2016-02-24
MX2010000487A (es) 2010-05-03
JP2011503404A (ja) 2011-01-27
EP2240674A2 (de) 2010-10-20
UA99472C2 (uk) 2012-08-27
JP5074589B2 (ja) 2012-11-14

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