Power plants – Combustion products used as motive fluid – External-combustion engine type
Reexamination Certificate
2002-01-04
2003-08-05
Richter, Sheldon J. (Department: 3748)
Power plants
Combustion products used as motive fluid
External-combustion engine type
C123S059100
Reexamination Certificate
active
06601379
ABSTRACT:
TECHNICAL FIELD
The invention relates to a working procedure for an internal combustion engine and in particular this invention relates to an internal combustion engine incorporating a first cylinder having a displaceable first piston therein which is connected to a crank shaft, and a first cylinder volume which is formed between the first piston and the first cylinder and which is adapted to be filled via a fresh gas inlet with fresh gas during the expansion thereof in the course of a suction stroke, whereby the fresh gas is adapted to be compressed during a subsequent compression stroke where the first cylinder volume is reduced in size.
BACKGROUND OF THE INVENTION
In the case of known combustion engines using internal combustion, the combustion chambers relating to a respective cylinder (e.g., amongst others, engines of the Ricardo, Perkins, Hercules, Deutz, ACO type) are arranged statically in the cylinder head, the engine block and/or in the engine pistons. A proposal, which remains theoretical but which envisaged, includes a rotating combustion chamber in which a partial quantity of a fatty mixture was to be burnt, was disclosed in European Patent Application No. EP-A-0 074 174, it being intended that this mixture should then be used as an igniter for a weaker mixture contained in the conventional combustion chamber.
A feature common to all the embodiments was the short time period that was available for the evaporation of the fuel and the burning thereof, which was necessitated by the construction and the procedures adopted. A further disadvantage was that the combustion process took place in a variable volume and that it had to occur at approximately −15° before and up to +35° after the top dead center position. As a consequence thereof, there was incomplete combustion of the fuel, which results in the production of harmful exhaust gases. In the case of fuels which require more time for the preparation of the mixture (diesel) or for the combustion thereof (alcohol), there is an additional limitation with regard to the maximum possible rotational speed. The available combustion period is in the general order of magnitude of approximately 0.001 seconds. The compromises created include as illustrative examples: increasing the excess quantity of air or accepting an incomplete combustion process lead to a lowering of efficiency as well as an increase in the emission of harmful materials. In the case of the known working procedures, a reduction in the quantity of excess air would lead to incomplete combustion, to further energy losses and also to an increase in the emission of harmful substances. An increase in the theoretical efficiency by reducing the temperature of the exhaust gas is only made possible through increased expenditure for the apparatus.
In order to prolong the time required for preparing the mixture and for prolonging the combustion period, the fuel may be premixed with air in a carburetor, or, in the case of indirect fuel injection, in the suction channel intake, although the problems can only be reduced to a limited extent thereby.
SUMMARY OF THE INVENTION
An aspect of the present invention is to achieve improvements and especially higher performances, a higher level of efficiency and preferably good exhaust gas values in comparison with the conventional working procedures and internal combustion engines.
In accordance with the present invention, this aspect is achieved in the case of the working process or procedure mentioned hereinabove in that a fresh gas is compressed in a first cylinder volume incorporating a first piston during successive compression strokes and the compressed gas is then forced into one of at least two combustion chambers in which combustion of a mixture consisting of the compressed fresh gas and at least partially evaporated fuel is initiated after the combustion chamber has been closed relative to the first cylinder volume, whereafter the combustion chamber is opened relative to a second cylinder volume and the expanding combustion gases from the combustion chamber are applied to a second piston in the second cylinder volume for performing a working stroke and following the completion of the working stroke, exhaust gases are expelled from the second cylinder volume.
In the case of the internal combustion engine mentioned hereinabove, this aspect is achieved in that, outside the first cylinder volume, there are provided at least two mutually separated combustion chambers into which a compressed fresh gas, which is chargeable with fuel and is ignitable therein, is adapted to be alternately fed from the first cylinder volume during successive compression strokes, and, following the ending of a respective compression stroke, each of the combustion chambers is connectable during a working stroke to a second cylinder volume which is formed between a second cylinder and a second piston that is connected to the crank shaft, whereby the second piston is displaceable by the ignition of the compressed fresh gas that is charged with fuel in such a manner that the second cylinder volume will be expandable, and exhaust gas will be expellable by the second piston from the second cylinder volume during an exhaust stroke occurring subsequent to the working stroke.
Thus, in accordance with another aspect of the present invention, it is envisaged that the suction intake port and compression strokes should be spatially separated from the working and the exhaust strokes and that they should be carried out in two different cylinders. Between these two cylinders, there are disposed at least two combustion chambers into which the fresh gas that was compressed by the first cylinder is successively, i.e., in a cyclical sequence, fed during the compression stroke or towards the end of the compression stroke.
Advantageously, the combustion chambers are closed relative to the first cylinder volume towards the end of the compression stroke, for example, at the top dead center position of the first piston following the compression stroke. Since the combustion process is not initiated in the first cylinder volume used for compression purposes, the engine is not inclined to ignite the compressed fresh gas mixture prior to the top dead center position of the first piston and thus to premature formation of a high pressure.
Thereafter, fuel can be supplied, by means of an injection nozzle for example, into the combustion chambers, which are separated from the two cylinder volumes, at a selected time point in dependence on the desired evaporation period and ignition period and following the desired evaporation period, the ignition process can be initiated by means of a spark plug. Due to the fact that the fuel is injected into the previously emptied hot combustion chamber, the process of evaporation or mixture-preparation and distribution of the fuel in the fresh gas is extremely efficient, such efficiency not generally being attainable, for example, in the case of a conventional internal combustion engine using an injection process prior to the top dead center position. The ignition process, which is effected by means of a spark plug, can take place at a desirable time point prior to the opening of the combustion chamber relative to the second cylinder volume which is then at the start of the working stroke, whence the combustion process will have been completed or finished to a sufficient extent before the gas reaches the second cylinder volume. Hereby, the ignition process can be initiated at a suitable position within the combustion chamber so that the combustion gases will expand in an appropriate manner into the second cylinder volume. Advantageously, the flame front will expand in a direction opposite to this expansion of the combustion gases flowing into the second cylinder volume.
It is also possible for the ignition process to take place at a time point at which the combustion volume is already open relative to the second cylinder volume.
Basically, it is possible for the first cylinder and the second cylinder to have different capacities so tha
Chambers David A.
Diro Konstruktions GmbH & Co. KG
Husch & Eppenberger LLC
Muir Robert E.
Richter Sheldon J.
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