DE19654710A1 - Method for generating physical power with reciprocating piston internal combustion engines - Google Patents

Abstract

In a process for generating a physical power with reciprocating internal combustion engines, in at least one piston-cylinder unit a piston reciprocates within a cylinder and the reciprocating movement is transmitted by a connecting rod to a crankshaft. The piston compresses a mixture of fresh gas and fuel, which is then ignited and moves the piston in the opposite direction. The resulting exhaust fume pressure wave flows into an appropriate exhaust system (resonance exhaust system) designed with a diffuser, cone, matching cone and end tubular nozzle in which negative pressure and counter-pressure waves are generated. The thus generated negative pressure wave empties the cylinder chamber and aspirates fresh gas through an inlet, whereas the counter-pressure wave generated in the exhaust system loads additional fresh gas. These negative and counter-pressure waves cause a gaseous exchange in the area of the bottom dead centre, without requiring that the piston reciprocates through an empty stroke as in the four-stroke process or that the crankshaft chamber below the piston be crossed by a flow of gas as in the two-stroke process. Four embodiments of the reciprocating internal combustion engine are thus possible, in which the exhaust gas pressure wave resulting from combustion flows out of the cylinder chamber into an appropriate exhaust system (resonance exhaust system) through at least one outlet channel, either directly through the cylinder wall or through a valve opening arranged in the cylinder head and closable by at least one outlet valve. Fresh gas is aspirated into the exhaust system by the negative pressure wave generated therein and flows through an inlet channel into the cylinder chamber, either directly through the cylinder wall or through a valve opening arranged in the cylinder head and closable by at least one inlet valve. The overpressure wave generated in the same exhaust system causes the cylinder chamber to be charged with gas.

Description

The invention relates to a method for generating physical power Reciprocating internal combustion engines according to the preamble of claim 1, ff., and four possible versions of reciprocating internal combustion engines according to the Claims 12-15, ff.

Such methods are generally known and are used in so-called four-stroke and two-stroke engines with different fuels (petrol, diesel, biologi fuels, gases, hydrogen, etc.). Four so-called bars (Suction, compression, working, ejecting) through reversing cycles a piston, the crankshaft two rotations (720 °) at the performs so-called four-stroke processes for one work cycle, and one revolution hung (360 °) in the so-called two-stroke process.

In the four-stroke process, ignition occurs during these two revolutions of the mixture in the combustion chamber, with the ignition initiating the work cycle tet. In this known method, the outlet valve usually opens at the end of the work cycle and closes shortly after the start of the intake cycle, so that the off let valve is open during the entire exhaust stroke. The inlet valve opens towards the end of the exhaust stroke and closes shortly after the start of compression  tion stroke, so that the inlet valve is open during the entire intake stroke is. The mixture is ignited shortly before the end of the compression stroke.

This four-stroke process has the advantage that over the entire speed range the cylinder filling through the choice of timing, i.e. the opening and the closing times of the valves, can be influenced in the degree of filling. she but is directly dependent on the stroke volume of the piston. By using just everyone second crankshaft revolution to generate work, however, is the power density of a four-stroke engine low.

In the two-stroke process, the crankshaft occurs during each revolution Working cycle, so the power density is higher than with the four-stroke process. In the generally known two-stroke process, the mixture is characterized by the piston moving upwards in the crankshaft located below the piston sucked in and pre-compressed as the piston moves down. At this downward movement of the piston becomes the outlet channel in the cylinder wall released, whereby the still under high pressure exhaust gas in one Exhaust system escapes. At the same time, through the downward movement of the Piston pre-compressed in the crankshaft chamber, mixture by so-called Overflow channels in the cylinder space and drives residual gases from this cylinder space. Although the well-known two-stroke process has the great advantage that a work cycle is assigned to each crankshaft revolution, the two-cycle ver do not drive today in motor vehicle construction because of its poor exhaust behavior used more often. A major disadvantage, which leads to bad exhaust behavior leads to the fact that, for example, because of the flow through the Crankshaft housing the fuel must be buried in order for a To provide lubrication in the area of the crankshaft and also of the cylinder, and that When the gas is changed, unburned fresh gas is released into the exhaust system , which gives the two-stroke engine its poor exhaust behavior.

In the two described and generally known methods, the suction takes place fresh air due to the piston movement. With the so-called four-stroke ver  drive through the downward movement of the piston, through channels with time control ten valves, directly into the cylinder chamber, using the so-called two-stroke process through the upward movement of the piston, through channels with time control systems (lower piston edge, rotary valve, membrane, etc.) in the crankshafts room.

It is therefore the object of the present invention, a generic Method for generating physical power with reciprocating To create internal combustion engines, which has a high power density and depending on Design also has a good exhaust behavior.

Another job is to create reciprocating internal combustion engines that work according to such a procedure.

The first object is according to the characterizing part of claim 1 solved that during each reversing cycle, by using Schwin processes in the exhaust system and not by charging the fresh gas se or by the suction stroke movement of the piston (except for its time Chen control function when opening and closing any existing inputs and Exhaust channels), a gas change in the cylinder space is caused and that each reversing cycle of the piston can ignite the mixture.

Due to the type of gas exchange according to the invention in the cylinder space, which in each Reverse cycle of the piston, i.e. every revolution of the crankshaft can find and by igniting the resulting in the cylinder space Fresh gas at every piston reversal cycle becomes the well known so-called two- and four-stroke procedures changed.

There is a gas change with every crankshaft revolution, without utilization the suction stroke effect of the piston (suction into the cylinder space through the cylinder head in the four-stroke process, suction into the crankshaft chamber below the piston in the two-stroke process), and / or without sole off use of a charge only by utilizing the vibration processes  in an appropriately designed exhaust system (resonance exhaust system) that by Two-stroke engines are known in racing.

In connection with variable control times of the corresponding control devices (Channels or valves) is carried out by the process with every crankshaft revolution a fresh gas change and a work cycle. This achieves a power density which corresponds to that of the two - stroke procedure, however, depending on the interpretation of the by the Procedure possible reciprocating piston internal combustion engines (there is no flow of the crankcase space more necessary), does not have its disadvantages.

The inventions are the knowledge of the inventor according to the published patent application DE 44 46 057 A1 and the international publication number WO 96/19650 from June 27, 1996, in particular based on claim 19. This Findings of the inventor led to the linking of Features of the four-stroke process with features of the two-stroke process, because on on the basis of this knowledge of the applicant a gas change even without the suction Lifting action of the piston (apart from its time control function when opening and Closing any inlet and outlet channels) is possible. Only by Exploitation of the vibrations of an appropriately designed exhaust system that described below, from two-stroke motors in racing as a resonance puff system is known, the gas change in so-called reciprocating Internal combustion engines of all kinds are brought about.

In a resonance exhaust system, the number of Ver Burning frequency pressure waves coming from the cylinder space after burning exit through the outlet duct, by shaping the same with a diffuser Ren, cones, counter cones and tailpipe nozzle in frequent vacuum waves (Suction) and frequent back pressure waves (charging by the negative pressure wave into the resonance exhaust system.

The resulting vacuum waves are strong enough to change gas selenium alone, and the counter pressure waves are strong enough to effect.  

So z. B. a, originally for operation according to the so-called four-stroke drive designed engine, with a corresponding change in the valve timing in conjunction with an appropriately designed exhaust system (resonance exhaust system) perform one working cycle with every revolution of the crankshaft, So be converted to the mode of operation of the two-stroke process.

Also z. B. in one, for operation according to the so-called two-stroke drive designed motor, with a corresponding change in the channel guides and Control times of the channels in connection with an appropriately designed off puff system (resonance exhaust system), one ar with every revolution of the crankshaft beitstakt take place without the fresh gases through the crankshaft chamber beforehand conduct.

Versions of new engines are also possible, the outlet of which through Kanä le with valves in the cylinder head, and their inlet through channels in the Cylinder wall takes place or its outlet takes place through channels in the cylinder wall and their inlet is through channels with valves in the cylinder head.

The method according to the invention has the advantage on the one hand that each crankshaft lenumrehung a work cycle is assigned, so that the power density when invented The method according to the invention corresponds to that of the two-stroke method, but without on the other hand, the mixture must be directed through a crankshaft chamber, because As with the four-stroke process, the crankshaft chamber is separated from the cylinder chamber and is not flowed through by the mixture.

By appropriately designing the channel guides and control systems as well as control times and fuel allocations, it is z. B. possible, the exhaust gas behavior of the possible piston internal combustion engine seem to improve significantly.  

So far, there are claims for reciprocating internal combustion engines has been divided, which perform a work cycle with each crankshaft revolution such as U.S. Patent 4,162,662 (Jean Melchior), U.S. Patent 5,140,958 (Kobayashi et al. / Toyota) and DE patents 40 12 491 A1, 40 12 471 A1, 40 12 474 A1 (Dr. Krüger / Volkswagen), or EP-A-0 459 848 (Jean Melchior et al.) and others, but these do not use the vibration processes in one appropriately designed exhaust system (resonance exhaust system) for gas exchange, but try z. B. by charging the fresh gases to a higher pressure than the normal ambient pressure to produce a flushing of the cylinder space.

It is not described how the clocks in these reciprocating piston internal combustion engines Ejection and suction take place, but only like the flushing of the cylinder space runs through a charge.

Charging alone does not create an oscillation process per se, but it is for an optimal filling is necessary.

In the method according to the invention, the fuel is the fresh gas before it Inflow into the cylinder chamber supplied, for example, through an inlet port naleinjection can take place, the injection jet on the valve plate or ge is aimed. With inlet ducts in the cylinder wall, the injection jet must hit the Cylinder interior to be directed.

In another preferred embodiment, the fuel is the fresh gas after its inflow into the cylinder chamber, which is done, for example, by a Injector can be made, which is attached to the cylinder wall and in the front injected compressed air.

In a third embodiment of the method according to the invention, the Fuel the fresh gas after it flows into a ver with the cylinder space bound antechamber fed.

The fuel is preferably supplied to the fresh gas by at least an injector.  

The fresh gas can, according to a further embodiment of the invention driving additionally pressurized flow into the cylinder space, the Pressure increase of the fresh gas, for example in a mechanical charger or in an exhaust gas turbocharger.

The mixture is preferably ignited by at least one third party ignition device, such as in a gasoline engine.

The ignition of the mixture can also be achieved by compressing the mixture as auto-ignition, as is the case for example with a diesel engine is.

According to one embodiment of the method, the outlet (valve in the cylinder head or channel in the cylinder wall) before the inlet (valve in the cylinder head or channel in the cylinder wall) and closes in time before the inlet, so that both the outlet and the inlet ge during a predetermined period of time opens.

According to a further embodiment of the method, the outlet (valve in the Cylinder head or channel in the cylinder wall) before the inlet (valve in the Cylinder head or channel in the cylinder wall) and closes after the intake, so that the outlet is significantly longer than the outlet during a predetermined period of time Are open.

According to a preferred embodiment of the method, the outlet (valve in the Cylinder head or channel in the cylinder wall) can be changed over time by a control system before opening the inlet (valve in the cylinder head or channel in the cy linderwand), which is also controlled by a tax system in its total opening time riabel is controllable and closes, changeable over time by a control system, during or after closing the inlet so that during a changeable Ren time span, both the outlet and the inlet are open.  

The second object on which the invention is based is achieved by four possible Che designs of reciprocating internal combustion engines, according to one of the previous described methods work with at least one of a cylinder head the one end closed cylinder, in which an axially movable piston is inserted, one pivotally connected at one end to the piston Connecting rod, the other end of which is rotatably mounted on a crankshaft, at least an intake port and valve in the cylinder head or an intake port in the Zylin derwand and at least one exhaust port and valve in the cylinder head or one Exhaust channel in the cylinder wall, and, if not only channels in the cylinder wall for the inlet and outlet are used alone, at least one the inlet and / or the exhaust valve in an opening and closing movement control shaft connected to the crankshaft via a drive device in drive connection stands, which reciprocating internal combustion engines are characterized in that the Exhaust duct with an appropriately designed exhaust system (Resonance exhaust system) is connected, that the exhaust pressure waves in sub converts pressure and back pressure vibrations.

If not only channels in the cylinder wall are used alone (their opening Opening and closing times by the piston and / or timing control system me are regulated), the inlet valve and / or the outlet valve is actuated beating camshaft driven at the speed of the crankshaft, so that ever the reversing cycle of the piston, i.e. every revolution of the crankshaft, an opening Assignment and closing operation of the intake valve and / or the exhaust valve assigned are. This ensures that with every crankshaft revolution, in Ver binding with the interpretation of the valve timing, a gas change through which appropriately designed exhaust system that generates resonance vibrations, in the Zy linderraum can be done.

In all designs, an exhaust system is connected to the exhaust duct, which is designed as a resonance exhaust system and the exhaust pressure waves in vacuum and converted back pressure vibrations.  

The invention is explained in more detail below using an example with reference to the drawings. The following can be seen in these:
Figs. 1A-1D show the four possible types of reciprocating internal combustion engines according to the invention, as a single-cylinder engine with dual overhead camshafts for the outlet and inlet valve in the cylinder head in Fig. 1A
which as a single-cylinder engine with an overhead camshaft for the exhaust valve in the cylinder head and an intake port in the cylinder wall in Fig. 1B,
which as a single-cylinder engine with an overhead camshaft for the intake valve in the cylinder head and an exhaust port in the cylinder wall in Fig. 1C,
and as a single-cylinder engine with an outlet duct in the cylinder wall and an inlet duct in the cylinder wall in FIG. 1D,
are shown in connection with the necessary resonance exhaust system.

However, single-cylinder engines are also conceivable that have several valves in the cylinder head and / or channels in the cylinder wall on the inlet and / or outlet side ha ben.

There are also multi-cylinder engines in the usual cylinder arrangements (For example in-line engine, V-engine, boxer engine, radial engine, etc.) conceivable.

FIGS. 2A-2C are diagrams of the opening and closing times of the valves in the cylinder head and / or the channels in the cylinder wall in dependence on the crank angle.

A piston 2 is arranged axially displaceably in the cylinder 1 . The cylinder 1 is connected at its upper end with a cylinder head 3, wherein between the Zy relieving 1 and the cylinder head 3, a cylinder head gasket 13 is arranged. In the cylinder head 3 , a cylinder head space 15 arranged coaxially to the cylinder is formed, which merges essentially continuously into the cylinder space 16 enclosed by the cylinder 1 .

The piston 2 is connected in a known manner via a connecting rod 5 to a crankshaft 4 which is rotatably supported in a crankshaft space below the cylinder 1 . The connecting rod 5 is pivotally supported with its upper end on the piston 2 and rotatably supported on the crankshaft 4 with its other lower end. In this way, a vertical reversing movement of the piston 2 is converted into a rotary movement of the crankshaft 4 in a generally known manner.

In FIGS. 1A and 1C is in the cylinder head 3, an intake port is provided with an inlet 12 in front employed membrane 17 which opens into the cylinder head chamber 15. The mouth of the intake port 12 in the cylinder head space 15 is closed by an intake valve 6 ( Fig. 1A, 1C). The intake valve 6 ( Fig. 1A, 1C) is struck in a known manner by a rotating intake camshaft 8 for opening and closing the mouth of the intake port 12 into the cylinder head space 15 . Conventional valve return mechanisms, which are not shown in the schematic representation of FIGS. 1A, 1C, tension the inlet valve 6 in its closed position.

In FIGS. 1B and 1D, an inlet channel with an inlet diaphragm 17 vorange set 19 is provided in the cylinder 1, which opens into the cylinder chamber 16. The opening of the inlet channel 19 into the cylinder space 16 is opened and closed by the reversing piston in connection with a variable time control system 21 ( FIGS. 1B, 1D).

Furthermore, in the cylinder head 3 there is an outlet duct 14 (FIGS . 1A, 1B) which leads out of the cylinder head chamber 15 ( FIG. 1A) opposite the mouth of the inlet duct 12 or which leads above the mouth of the inlet duct 19 through the cylinder wall into the cylinder chamber 16 ( Fig. 1B) leads out of the cylinder head space 15 . The mouth of the exhaust passage 14 is closed by an exhaust valve 7 ( Fig. 1A, 1B), which is acted upon by an exhaust camshaft 9 for opening and closing, the exhaust valve 7 ( Fig. 1A, 1B) by a known valve return mechanism in the Is held in the closed position.

The mouth of the outlet duct 25 (Fig. 1C, 1D) from the cylinder chamber 16 is opened ersystem by the reversing piston in connection with a variable time STEU and closed (Fig. 1C, 1D).

The arrangements of the inlet ducts ( 12 and 19 ) and the outlet ducts ( 14 and 25 ) shown in FIGS . 1A-1D are particularly advantageous for carrying out the method according to the invention, since the exhaust gas pressure wave combined with the design of the resonance exhaust system with diffuser ( 26 ), cone ( 27 ), Ge conical ( 28 ) and tailpipe nozzle ( 29 ) arising, negative and counter pressure waves allow a quick gas change.

A spark plug 10 is provided in the cylinder head, essentially in the region of the cylinder axis, and an injection valve 11 is laterally offset from it. The spark plug 10 and the injection valve 11 function in a manner known to the person skilled in the art and can also be arranged in another way. For example, the injection valve 11 can also be provided in the intake manifold (inlet channels 12 and 19 ); but it can also be arranged on the cylinder wall and / or the cylinder head. In addition, multiple spark plugs and / or injection valves can be provided in a respective arrangement.

If the internal combustion engine according to the invention is designed as a self-igniter, the spark plug can be omitted and replaced by a glow plug if necessary. In the case of a compression-ignition engine (diesel engine), a prechamber can also be provided in the cylinder head, which is connected to the cylinder head space 15 and into which the injection valve opens. Basically, the injection valve 11 can also open directly into the cylinder head space 15 in a compression-ignition engine.

Referring to FIGS. 1A-1C, the crankshaft 4 is provided with a dash-dot line Drawn Neten drive gear 20 and the camshaft 8 and / or 9 are each provided 24 with a corresponding drive wheel 22 and / or. The drive wheels 20 , 22 and / or 24 are connected to one another via a rotating drive means 18 or via gear wheels. The drive wheels 20 , 22 and / or 24 can be chain sprockets or toothed belt wheels, for example, the rotating drive means 18 being formed by a drive chain or a toothed belt. The diameter of the drive wheels 20 , 22 and / or 24 is essentially identical, so that the respective speed of the camshafts 8 and / or 9 corresponds to that of the crankshaft 4 .

But there are also other power transmission mechanisms between the crankshaft 4 and the camshafts 8 and / or 9 conceivable, such as a vertical shaft gear or other transmission mechanisms.

Fig. 2A shows a circle, which gives a rotation of the crankshaft schematically, wherein the direction of rotation corresponds to the clockwise direction (arrow x). The top dead center OT, in which the piston assumes its uppermost position and the bottom dead center UT, in which the piston assumes its lowest position, are drawn on the circle.

The time of opening the exhaust valve 7 or the exhaust duct 25 leading from the cylinder space is designated AO and is preferably in the range between 110 degrees and 65 degrees, preferably between 95 degrees and 65 degrees, more preferably between 80 degrees and 65 degrees bottom dead center UT.

The time of opening of the inlet valve 6 or of the inlet channel 19 ending in the cylinder space is designated EO and is after the opening time AO of the outlet valve 7 or outlet channel 25 , preferably between 75 degrees before bottom dead center UT and bottom dead center UT itself .

The point in time at which the exhaust valve 7 or the exhaust port 25 leading from the cylinder chamber is closed is designated AS and is preferably in the range between bottom dead center UT and about 110 degrees after bottom dead center UT, preferably 5 degrees to 95 degrees after bottom dead center Subtitles

The time of closing the inlet valve 6 or the inlet channel 19 leading into the cylinder space is designated ES and is preferably in the range between the bottom dead center UT and about 100 degrees after the bottom dead center UT, preferably in the range between 30 degrees and 75 degrees after bottom dead center UT.

The angular ranges given in connection with FIG. 2A also apply to the following examples of FIGS. 2B and 2C, only the ratio se of the opening and closing times (AO, EO, ES, AS) to one another being changed there. It is advantageous if the position of the opening time and / or the closing time is asymmetrical with respect to the bottom dead center UT.

In FIG. 2B, the opening times AO and EO correspond to the opening times described in connection with FIG. 2A; however, the closing time AS is later than the closing time ES. With this arrangement, the counterpressure wave that arises in connection with the exhaust system (resonance exhaust system), with its supercharging effect, increases its performance.

In Fig. 2C, a special embodiment of the method according to the invention is shown, the opening times AO and EO being variable with respect to one another by variable control systems such that the crankshaft angle between AO and EO can be designed differently, but is always AO before EO; the closing times AS and ES can also be changed with respect to one another by means of variable control systems in such a way that the crankshaft angle between AS and ES can be designed differently, wherein AS can be either before, essentially at the same time or after ES. With this arrangement, the vacuum and counter-pressure waves that arise in connection with the exhaust system (resonance exhaust system), with their suction and charging effects, increase performance.

Reference list

1

cylinder

2nd

piston

3rd

Cylinder head

4th

crankshaft

5

Connecting rod

6

Inlet valve

7

Exhaust valve

8th

Intake camshaft

9

Exhaust camshaft

10th

spark plug

11

Injector

12th

Inlet port cylinder head

13

Cylinder head gasket

14

Exhaust port cylinder head

15

Cylinder head space

16

Cylinder space

17th

Inlet membrane

18th

Drive means

19th

Inlet duct cylinder wall

20th

drive wheel

21

Timing control system intake duct cylinder wall

22

drive wheel

23

Timing control system exhaust duct cylinder wall

24th

drive wheel

25th

Exhaust duct cylinder wall

26

Diffuser of the resonance exhaust system

27

Cone of the resonance exhaust system

28

Counter cone of the resonance exhaust system

29

Tail pipe nozzle of the resonance exhaust system

Claims (15)

1. Method for generating physical power in a reciprocating piston internal combustion engine, in which in at least one piston-cylinder unit a piston ( 2 ) reverses in a cylinder ( 1 ) and the reversing movement via a connecting rod ( 5 ) to a crankshaft ( 4 ) transmits,
in which a mixture of fresh gas and fuel is compressed and ignited by a piston ( 2 ) moving in a first direction;
in which the ignited mixture burns and thereby moves the piston ( 2 ) in a second direction opposite to the first direction, characterized in that
that the exhaust gas pressure wave flows out through channels with timing systems into a so-called resonance exhaust system with diffuser ( 26 ), cone ( 27 ), counter-cone ( 28 ) and tailpipe nozzle ( 29 ) of known type and design,
that the exhaust gas pressure wave is used for generating speed-frequency pressure waves by this corresponding shaping,
that a first vacuum wave, which arises due to the transition from diffuser ( 26 ) to cone ( 27 ) when flowing through the exhaust gas pressure wave, empties the cylinder space, so that fresh gas can continue to be drawn into the cylinder space through this vacuum wave through channels with timing systems,
that, by the transition from the cone ( 28 ) to the tailpipe nozzle ( 29 ) when flowing through the exhaust gas pressure wave, the counter pressure wave achieves a charging effect of the fresh gases in the resonance exhaust system, so that during each reversing cycle of the piston in the area of the bottom dead center a gas change in Cylinder chamber ( 16 ) is effected without a charge of the fresh gases, without the lifting action of the piston by an idle cycle, as in the well-known four-stroke engine, or without flowing into a crankshaft lenraum below the piston as in the well-known two-stroke engine. 2. The method according to claim 1, characterized, that the fuel is fed to the fresh gas before it flows into the cylinder space leads. 3. The method according to claim 1, characterized, that the fuel supplied to the fresh gas after its inflow into the cylinder space leads. 4. The method according to claim 1, characterized, that the fuel the fresh gas after flowing into a with the cylinder space connected antechamber is fed. 5. The method according to any one of the preceding claims, characterized in that an injection device ( 11 ) is provided, which belbel each time a rotation of the cure ( 4 ) a predetermined amount of fuel to the fresh gas intended for combustion. 6. The method according to any one of the preceding claims, characterized, that the fresh gas flows under pressure into the cylinder chamber. 7. The method according to any one of the preceding claims, characterized, that the ignition of the mixture takes place by at least one external ignition device.   8. The method according to any one of claims 1-6, characterized, that the ignition of the mixture as a high compression of the mixture Auto ignition occurs. 9. The method according to any one of the preceding claims, characterized in
the opening of the outlet (AO) is earlier than that of the inlet (EO) and
that the time of closing the outlet (AS) is earlier than that of the inlet (ES), so
that both the outlet channel and the inlet channel are open for a predetermined period of time. 10. The method according to any one of claims 1-8, characterized in
the opening of the outlet (AO) is earlier than that of the inlet (EO) and
that the time of closing the outlet (AS) is after that of the inlet (ES), so
that the total opening time of the exhaust port is longer than the total opening time of the intake port. 11. The method according to any one of claims 1-8, characterized in
that the time of the opening of the outlet (AO) and that of the inlet (EO) can be varied with respect to one another by variable control systems in such a way that the crankshaft angle between AO and EO can be varied over the entire speed range, but is always AO before EO and
that the closing times AS and ES can also be changed with respect to one another by variable control systems, so
that the crankshaft angle between AS and ES can be designed richly differently over the entire speed range, with AS over this speed range both before and after ES. 12. reciprocating piston internal combustion engine, working according to a method of claims 1-11, with at least one of a cylinder head ( 3 ) at one end closed cylinder ( 1 ), in which an axially movable piston ( 2 ) is used; a connecting rod ( 5 ) pivotally connected to the piston ( 2 ) at its first end, the other end of which is rotatably mounted on a crankshaft ( 4 );
in which fresh gas can flow through at least one inlet channel ( 12 ) with a preceding inlet membrane ( 17 ) and at least one inlet valve ( 6 ) into the cylinder space ( 16 ) formed in the cylinder ( 1 );
in which the exhaust gas pressure wave resulting from the combustion can flow out through at least one exhaust port ( 14 ) and at least one exhaust valve ( 7 ) provided in the cylinder head ( 3 );
in which the inlet and outlet valves ( 6 ; 7 ) are controlled by at least one control shaft ( 8 ; 9 ) acting on the opening and closing movement, preferably a camshaft, which is connected to the crankshaft ( 4 ) via a drive device ( 18 , 20 , 22 , 24 ) is in drive connection, characterized in that
that the outlet duct is connected to a so-called resonance exhaust system of known type and design and
that thereby the gas exchange can take place according to one of the method of claims 1 to 11. 13. Reciprocating internal combustion engine, working according to a method of claims 1-11, with at least one of a cylinder head ( 3 ) at one end closed cylinder ( 1 ), in which an axially movable piston ( 2 ) is used; a connecting rod ( 5 ) pivotally connected to the piston ( 2 ) at its first end, the other end of which is rotatably mounted on a crankshaft ( 4 );
in which fresh gas through at least one inlet channel ( 19 ), which opens with a preceding inlet membrane ( 17 ) and a time-variable control system ( 21 ) through the cylinder wall into the cylinder chamber ( 16 ), into the cylinder chamber ( 1 ) formed th cylinder chamber ( 16 ) can flow in;
in which the exhaust gas pressure wave resulting from the combustion can flow out through at least one exhaust port ( 14 ) and at least one exhaust valve ( 7 ) provided in the cylinder head ( 3 );
in which the exhaust valve ( 7 ) by at least one, the opening and closing movement acted on control shaft ( 9 ), preferably a camshaft is steered, which is in drive connection with the crankshaft ( 4 ) via a drive device ( 18 , 20 , 24 ) , characterized,
that the outlet duct is connected to a so-called resonance exhaust system of known type and design and
that thereby the gas exchange can take place according to one of the method of claims 1 to 11. 14. reciprocating piston internal combustion engine, working according to a method of claims 1-11, with at least one of a cylinder head ( 3 ) at one end closed cylinder ( 1 ), in which an axially movable piston ( 2 ) is used; a connecting rod ( 5 ) pivotally connected to the piston ( 2 ) at its first end, the other end of which is rotatably mounted on a crankshaft ( 4 );
in which fresh gas can flow through at least one inlet channel ( 12 ) with a preceding inlet membrane ( 17 ) and at least one inlet valve ( 6 ) into the cylinder space ( 16 ) formed in the cylinder ( 1 );
in which the exhaust gas pressure wave resulting from the combustion can flow through at least one outlet channel ( 25 ) in connection with a time-variable control system ( 23 ) through the cylinder wall from the cylinder space ( 16 ) formed in the cylinder ( 1 );
in which the inlet valve ( 6 ) is controlled by at least one, the opening and closing movement movement control shaft ( 8 ), preferably a camshaft, which is in drive connection with the crankshaft ( 4 ) via a drive device ( 18 , 20 , 22 ) , characterized,
that the outlet duct is connected to a so-called resonance exhaust system of known type and design and
that thereby the gas exchange can take place according to one of the method of claims 1 to 11. 15. reciprocating piston internal combustion engine, working according to a method of claims 1-11, with at least one of a cylinder head ( 3 ) at one end closed cylinder ( 1 ), in which an axially movable piston ( 2 ) is used; a connecting rod ( 5 ) pivotally connected to the piston ( 2 ) at its first end, the other end of which is rotatably mounted on a crankshaft ( 4 );
in which fresh gas through at least one inlet channel ( 19 ), which opens with a preceding inlet membrane ( 17 ) and a time-variable control system ( 21 ) through the cylinder wall into the cylinder chamber ( 16 ), into the cylinder chamber ( 1 ) formed th cylinder chamber ( 16 ) can flow in;
in which the exhaust gas pressure wave resulting from the combustion can flow out of the cylinder space ( 16 ) formed in the cylinder ( 1 ) through at least one outlet channel ( 25 ) in connection with a time-variable control system ( 23 ) through the cylinder wall; characterized,
that the outlet duct is connected to a so-called resonance exhaust system of known type and design and
that thereby the gas exchange can take place according to one of the method of claims 1 to 11.