EP1528234B1 - Acht-Takt-Brennkraftmaschine mittels einem Nehmerzylinder - Google Patents

Acht-Takt-Brennkraftmaschine mittels einem Nehmerzylinder Download PDF

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Publication number
EP1528234B1
EP1528234B1 EP03025319A EP03025319A EP1528234B1 EP 1528234 B1 EP1528234 B1 EP 1528234B1 EP 03025319 A EP03025319 A EP 03025319A EP 03025319 A EP03025319 A EP 03025319A EP 1528234 B1 EP1528234 B1 EP 1528234B1
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EP
European Patent Office
Prior art keywords
cylinder
slave cylinder
master cylinder
slave
stroke
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 - Lifetime
Application number
EP03025319A
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English (en)
French (fr)
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EP1528234A1 (de
Inventor
Lung-Tan Hu
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Individual
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Individual
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Priority to AT03025319T priority Critical patent/ATE362581T1/de
Priority to DE60313868T priority patent/DE60313868T2/de
Priority to ES03025319T priority patent/ES2285022T3/es
Priority to EP03025319A priority patent/EP1528234B1/de
Publication of EP1528234A1 publication Critical patent/EP1528234A1/de
Application granted granted Critical
Publication of EP1528234B1 publication Critical patent/EP1528234B1/de
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    • 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
    • F02B75/021—Engines characterised by their cycles, e.g. six-stroke having six or more strokes per cycle
    • 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
    • F02B41/00—Engines characterised by special means for improving conversion of heat or pressure energy into mechanical power
    • F02B41/02—Engines with prolonged expansion
    • F02B41/06—Engines with prolonged expansion in compound cylinders

Definitions

  • the present invention is related to an eight-stroke internal combustion engine, which may be used in most any application of present uses of internal combustion engines, such as a transportation vehicle. More specifically this invention relates to an eight-stroke reciprocating piston driven internal combustion engine utilizing a slave cylinder working in cooperation with a master cylinder.
  • piston driven reciprocal internal combustion engines There are two main types of piston driven reciprocal internal combustion engines, they are the spark ignition engines, and the auto-ignition engines, also called diesel engines.
  • piston driven reciprocal engines for the most part, use either a two-stroke cycle or more commonly, a four-stroke cycle.
  • the main parts of these engines are; a cylinder containing a piston with a reciprocal movement which is converted into a rotational movement by means of a connecting rod and a crankshaft, and a cylinder head consisting of at least two valves, one exhaust valve and one intake valve.
  • the four stroke or four cycle engine begins by the piston drawing an atomized air-fuel mixture into the cylinder through the intake valve on the first down stroke, the first cycle; then with the valves closed the mixed gases are compressed on the first up stroke, the second cycle; and at or near the top of the first up stroke, the compressed mixture of air and fuel ignites, by either a spark or by auto-ignition, and the mixture, or most of the gas mixture, combusts to produce a second downward stroke the third cycle, which is the power stroke; the second upward stroke, the fourth cycle, pushes the burnt gas mixture and the remaining un-burned gas mixture out of an open exhaust valve to complete the fourth cycle where the rotary or centrifugal motion created by the process is carried by the flywheel for the cycles to continue until either the fuel is shut off or the spark is discontinued.
  • the efficiency of the energy produced depends, among other variables, on the amount of air-fuel mixture drawn or forced into the cylinder and the compression volume ratio. The higher the compression volume ratio, the higher the efficiency.
  • the compression volume ratio is limited, in the case of the gasoline engine, by the risk of premature ignition of the mixture and in the case of the diesel engine among other variables, by a sturdy and appropriate combustion chamber.
  • US-5056471 discloses a similar arrangement of a multi-cycle internal combustion engine capable of two-stage exhaust with the exhaust cylinder lead the combustion cylinder 30-90 degrees.
  • It is therefore an object of the present invention is to produce an eight-stroke reciprocating piston internal combustion engine with increased fuel efficiency according to claim 1.
  • Another object of the present invention is to produce an eight-stroke reciprocating piston internal combustion engine which is less polluting.
  • the slave cylinder By the use of a slave cylinder working in coordination with a master cylinder, the slave cylinder both receives cool atmospheric air and receives hot combustion gases from the master cylinder to create a second power-stroke in the slave cylinder.
  • the increased compression ratio of air in the slave cylinder allows compressed air to be injected into the master cylinder as the master cylinder is in the later half of it's power stroke, this causes a re-burn of the combustion gasses in the master cylinder.
  • This secondary combustion is transferred from the master cylinder, through the coordinate valve to the slave cylinder to produce a second power stroke within the slave cylinder.
  • the lower temperature in the slave cylinder makes it possible, by heat transfer, to substantially take full advantage of the heat energy created in the master cylinder.
  • the master cylinder and the slave cylinder there are eight working cycles or strokes, each within 90° of crankshaft revolution of each other.
  • the entire working process is from 0° to 810° of revolution crankshaft.
  • the master cylinder cycles work from 0° to 720° of revolution and slave cylinder cycles work from 90° to 810° of revolution.
  • the master cylinder begins to intake air and fuel at 0 degree of revolution and slave cylinder begins to intake air at 90° of revolution.
  • the engine metal will absorb the heat energy produced by combustion, and the cylinder will be cooled down by the cooling system. Resulting in wasted heat energy.
  • the eight-stroke piston engine uses cold air in the slave cylinder to combine with the "wasted" heat energy to produce power as when the cool air combines with the heat energy and un-burnt gases, the cool air inside the slave cylinder will expand. Therefore, the expanded air will continue the power cycle within the master cylinder by combusting most of the remaining un-burnt gases and as the master cylinder exhaust, it also produces a second power cycle within the slave cylinder without a spark.
  • the heat energy and un-burnt gases from the master cylinder will combine with the cool air in the slave cylinder. This will reduce the temperature in the master cylinder lowering the chance of pre-ignition detonation, thus allowing higher compression ratios and will also result in higher thermal efficiency, as the cooler slave cylinder air absorbs the heat energy and the engine metal will absorb less heat.
  • the embodiment of this invention is an internal combustion engine composed essentially of at least one pair of compressing cylinders. It is plausible that the master cylinder and the slave cylinder could be substantially more or substantially less than 90° off rotation of each other. For ease of explaining this invention the cylinders are discussed herein working 90° off rotation of each other. As well it is also plausible that the slave cylinder could potentially use a third valve giving more control to the coordinate valve port if required. It is also plausible, the displacement of the master cylinder and slave cylinder could be different. As well, the duration of the valve timing may be varied depending on the application requirements and variables in the engine tuning dynamics.
  • this eight-stroke internal combustion engine can be applied to both the spark ignition engine and the auto-ignition or diesel engine, and the invention could plausibly use a spark in the slave cylinder if so desired.
  • the eight-stroke internal combustion engine is generally referred to as 10, it is shown in a cutaway sectional elevation view, where engine 10 comprises a cylinder block 12, and within block 12, there is a master cylinder bore 14 and a slave cylinder bore 16.
  • the master cylinder 14 contains a piston 18 which is slidable movable by connecting rod assembly 20, rod 20 is rotationally supported by crankshaft 22, where crankshaft 22 is rotationally supported by cylinder block 12.
  • Slave cylinder bore 16 contains a piston 24 which is slidable movable by connecting rod assembly 26, rod 26 is also rotationally supported by crankshaft 22.
  • cylinder head 28 Fixed atop cylinder block 12 is a cylinder head 28. Above master cylinder 14, cylinder head 28 includes a spark plug 30, an intake valve 32 and a coordinate valve 34. Above slave cylinder 16, cylinder head 22 includes an open port 36 to coordinate valve 34, an intake valve 38 and an exhaust valve 40.
  • intake stroke, stroke #1 is at the beginning (0°) of the crankshaft 22 rotation cycle.
  • master cylinder 14 intakes air and fuel (A/F) through the master cylinder intake valve 32.
  • slave cylinder piston 24 is in the middle of its exhaust stroke, stroke #8.
  • intake, stroke #1 is at the middle (90°) of rotation, where the master cylinder 14 intakes A/F through the master cylinder intake valve 32 and slave cylinder 16 is finishing its exhaust stroke, stroke #8 (810° of its cycle rotation completion, or the beginning of a new cycle of rotation).
  • FIG. 5 shows master cylinder 14, upon sparkplug 30 ignition, stroke #5, at the beginning of the power stroke (360° of cycle rotation), where the master cylinder 14 begins combustion of A/F and the slave cylinder piston 24 is in the middle of compression, stroke #4, where the slave cylinder compresses Air only.
  • master cylinder 14 exhaust, stroke #7, at the beginning of the exhaust stroke (540° of cycle rotation), where the master cylinder 14 begins to exhaust combustion gases through the coordinate valve and the slave cylinder piston 28 is in the middle of the power stroke, stroke #6, where the slave cylinder 16 continues power stroke as the gases expand and are re-burned within both master cylinder 14 as it exhausts through coordinate valve and into slave cylinder 16 as slave cylinder piston 28 continues its power stroke.
  • FIG. 9 a diagram showing the eight-engine working cycles.

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  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Output Control And Ontrol Of Special Type Engine (AREA)
  • Valve-Gear Or Valve Arrangements (AREA)
  • Electrical Control Of Ignition Timing (AREA)
  • Electrical Control Of Air Or Fuel Supplied To Internal-Combustion Engine (AREA)

Claims (6)

  1. Acht-Takt-Brennkraftmaschine aufweisend:
    zumindest einen Hauptzylinder (14) und zumindest einen Nebenzylinder (16), wobei der Hauptzylinder (14) einen sich hin- und her bewegenden, an eine Kurbelwelle (22) gekuppelten Hauptkolben aufweist und wobei der Nebenzylinder (16) einen sich hin- und her bewegenden, mit der Kurbelwelle (22) gekuppelten Nebenkolben aufweist; wobei der Nebenzylinder (16) dem Hauptzylinder (14) folgt; und
    ein Kopf-Ventil zum Einlassen von Luft und einer Kraftstoffmischung in den Hauptzylinder (14) und zum Einlassen von Luft nur in den Nebenzylinder (16) und zum Auslassen von Abgasen aus dem Nebenzylinder (16), sowie Mittel zur Koordinierung des Austausches von Gasen zwischen dem Hauptzylinder (14) und dem Nebenzylinder (16), wobei das Mittel zum Koordinieren des Austausches von Gasen ein Koordinierungs-Ventil an einer Seite des Hauptzylinders (14) ist, wobei das Koordinierungs-Ventil eine Durchgangsöffnung ausreichender Größe aufweist, um das Fließen von Gasen durch diese zwischen dem Nebenzylinder (16) und dem Hauptzylinder (14) zu erlauben, wobei die Durchgangsöffnung Gase durch das Ventil von dem Hauptzylinder (14) an dem Nebenzylinder (16) kanalisiert, wobei das Koordinierungs-Ventil bei etwa 420 Grad der Zyklusumdrehung zum Initiieren eines Flusses komprimierter Luft von dem Nebenzylinder (16) an den Hauptzylinder (14) geöffnet ist, wobei der Fluss komprimierter Luft von dem Nebenzylinder (16) bei etwa 450 Grad der Zyklusumdrehung im Wesentlichen vollendet ist und die Temperatur der Verbrennungsgase in dem Hauptzylinder (14) gemischt wird mit und abgekühlt wird durch den Fluss von komprimierter, von dem Nebenzylinder (16) kommender Luft, wobei dadurch der Gesamt-Hitzeverlust verringert wird; wobei während des Auslasshubes des Nebenzylinders (16) das gesamte Arbeitsmedium durch die Abgasauslassmittel in den Nebenzylinder (16) verdrängt wird.
  2. Acht-Takt-Verbrennungsmaschine nach Anspruch 1, wobei der zweite Arbeitshub beginnt, wenn die komprimierte Luft von dem Nebenzylinder (16) vollständig in den Hauptzylinder (14) übergeführt und darin mit den Verbrennungsgasen bei ungefähr 450 Grad der Zyklusumdrehung vermischt ist, wobei die Hitzeenergie in den Verbrennungsgasen von dem Hauptzylinder (14) und die komprimierte Luft von dem Nebenzylinder (16) zur Herstellung des zweiten Arbeitshubs ohne zusätzlichen Kraftstoff in dem Nebenzylinder (16) durch die Durchgangsöffnung kombiniert werden.
  3. Acht-Takt-Verbrennungsmaschine nach Anspruch 1, wobei der Hauptzylinder (14) und der Nebenzylinder (16) im Abstand von 60 bis 120 Grad von einander operieren, wobei der Nebenzylinder (16) dem Hauptzylinder (14) folgt.
  4. Acht-Takt-Verbrennungsmaschine nach einem der voran stehenden Ansprüche, wobei der Hauptzylinder (14) und der Nebenzylinder (16) in einer V-Zylinderkonfiguration neben der Kurbelwelle (22), an die sie gekuppelt sind, angeordnet sind.
  5. Acht-Takt-Verbrennungsmaschine nach einem der voran stehenden Ansprüche, aufweisend eine Mehrzahl von Paaren von Hauptzylindern (14) und Nebenzylindern (16).
  6. Acht-Takt-Verbrennungsmaschine nach Anspruch 1, ferner aufweisend ein Auflade-Einlasssystem.
EP03025319A 2003-11-03 2003-11-03 Acht-Takt-Brennkraftmaschine mittels einem Nehmerzylinder Expired - Lifetime EP1528234B1 (de)

Priority Applications (4)

Application Number Priority Date Filing Date Title
AT03025319T ATE362581T1 (de) 2003-11-03 2003-11-03 Acht-takt-brennkraftmaschine mittels einem nehmerzylinder
DE60313868T DE60313868T2 (de) 2003-11-03 2003-11-03 Acht-Takt-Brennkraftmaschine mittels eines Nehmerzylinders
ES03025319T ES2285022T3 (es) 2003-11-03 2003-11-03 Motor de combustion interna de ocho tiempos con utilizacion de un cilindro subordinado.
EP03025319A EP1528234B1 (de) 2003-11-03 2003-11-03 Acht-Takt-Brennkraftmaschine mittels einem Nehmerzylinder

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
EP03025319A EP1528234B1 (de) 2003-11-03 2003-11-03 Acht-Takt-Brennkraftmaschine mittels einem Nehmerzylinder

Publications (2)

Publication Number Publication Date
EP1528234A1 EP1528234A1 (de) 2005-05-04
EP1528234B1 true EP1528234B1 (de) 2007-05-16

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EP03025319A Expired - Lifetime EP1528234B1 (de) 2003-11-03 2003-11-03 Acht-Takt-Brennkraftmaschine mittels einem Nehmerzylinder

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EP (1) EP1528234B1 (de)
AT (1) ATE362581T1 (de)
DE (1) DE60313868T2 (de)
ES (1) ES2285022T3 (de)

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US7143725B1 (en) * 2005-11-22 2006-12-05 Lung Tan Hu Dual six-stroke self-cooling internal combustion engine

Family Cites Families (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR935962A (fr) * 1946-10-16 1948-07-06 Procédé pour utiliser complètement la détente des gaz brulés dans les moteurs à explosion à cylindres, et moteur à explosion à deux cylindres jumelés réalisant ce procédé
US3991721A (en) * 1974-01-17 1976-11-16 Hurd Fraser A Low emission compound combustion engine
WO1991005945A1 (en) * 1989-10-19 1991-05-02 Gianni Zanieri An endothermic engine with an otto-cycle and double combustion diesel cycle
US5056471A (en) * 1990-10-12 1991-10-15 Husen Norman R Van Internal combustion engine with two-stage exhaust
SE514528C2 (sv) * 2000-01-20 2001-03-05 Scania Cv Ab Förfarande och anordning för energiöverföring i en fyrtaktsförbränningsmotor samt förbränningsmotor med minst en dylik anordning
US6393841B1 (en) * 2001-06-28 2002-05-28 Norman Robert Van Husen Internal combustion engine with dual exhaust expansion cylinders

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
None *

Also Published As

Publication number Publication date
ATE362581T1 (de) 2007-06-15
DE60313868D1 (de) 2007-06-28
EP1528234A1 (de) 2005-05-04
ES2285022T3 (es) 2007-11-16
DE60313868T2 (de) 2008-01-24

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