EP0888496A1

EP0888496A1 - Process for generating a physical power with reciprocating internal combustion engines

Info

Publication number: EP0888496A1
Application number: EP97953930A
Authority: EP
Inventors: Martin Wimmer
Original assignee: Individual
Current assignee: Individual
Priority date: 1996-12-30
Filing date: 1997-12-30
Publication date: 1999-01-07
Also published as: DE19654710A1; AU5764498A; WO1998029644A1

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

Method for generating physical power with

Reciprocating internal combustion engines

The invention relates to a method for generating physical power with reciprocating piston internal combustion engines according to the preamble of claim 1, ff., And four possible designs of reciprocating piston internal combustion engines according to patent claims 12-15.

Such methods are generally known and are operated in so-called four-stroke and two-stroke engines with different fuels (gasoline, diesel, biological fuels, gases, hydrogen, etc.). Four so-called cycles (suction, compression, work, ejection) are carried out by reversing cycles of a piston, the crankshaft making two revolutions (720 °) in the so-called four-stroke process for one work cycle, and one revolution (360 °) in the so-called Two-stroke process.

In the four-stroke process, the mixture located in the combustion chamber is ignited during these two revolutions, the ignition initiating the working stroke. In this known method, the exhaust valve usually opens at the end of the work cycle and closes shortly after the start of the intake cycle, so that the exhaust valve is open during the entire exhaust cycle. The intake valve opens towards the end of the exhaust stroke and closes shortly after the start of the compression stroke, so that the intake valve is open during the entire intake stroke. The mixture is ignited shortly before the end of the compression stroke. This four-stroke process has the advantage that the filling of the cylinder can be influenced over the entire speed range by the choice of the control times, ie the opening and closing times of the valves. However, it is directly dependent on the stroke volume of the piston. However, by using only every second crankshaft revolution to generate work, the power density of a four-stroke engine is low. In the two-stroke process, one work cycle takes place during each revolution of the crankshaft, which means that the power density is also higher than in the four-stroke process. In the generally known two-stroke process, the mixture is moved by the piston moving upwards into the crankshaft located below the piston. sucked in and pre-compressed as the piston moves down. During this downward movement of the piston, the exhaust port in the cylinder wall is released, whereby the exhaust gas, which is still under high pressure, escapes into an exhaust system. At the same time, mixture pre-compressed by the downward movement of the piston in the crankshaft chamber reaches the cylinder chamber through so-called overflow channels and drives residual gases out of this cylinder chamber. Although the generally known two-stroke process has the great advantage that a work cycle is associated with each crankshaft revolution, the two-stroke process is no longer used frequently in motor vehicle construction today because of its poor exhaust gas behavior. A major disadvantage, which leads to poor exhaust gas behavior, is the fact that oil has to be added to the fuel, for example because of the flow through the crankshaft housing, in order to provide lubrication in the area of the crankshaft and also the cylinder, and that unburned fresh gas components when changing the gas are released into the exhaust system, which gives the two-stroke engine its poor exhaust behavior.

In the two described and generally known methods, fresh air is drawn in by the piston movement. In the so-called four-stroke process due to the downward movement of the piston, through channels with time-controlled valves, directly into the cylinder chamber, with the so-called two-stroke process through the upward movement of the piston, through channels with time control systems (lower piston edge, rotary valve, diaphragm, etc.) in the crankshaft space.

It is therefore the object of the present invention to provide a generic method for generating physical power with reciprocating piston internal combustion engines, which has a high power density and, depending on the design, also a good exhaust gas behavior.

Another object is to provide reciprocating internal combustion engines that operate using such a method.

The first object is achieved according to the characterizing part of claim 1 in that during each reversing cycle, by utilizing vibrations processes in the exhaust system and not by charging the Firschgase or by the suction lifting movement of the piston (apart from its time control function when opening and closing any inlet and outlet channels), a gas change in the cylinder chamber is effected and that this means that every reversing cycle the piston can ignite the mixture.

Due to the type of gas exchange in the cylinder space according to the invention, which can take place with each reversing cycle of the piston, that is to say with each revolution of the crankshaft, and through the ignition of the fresh gas thereby entering the cylinder space with each reversing cycle of the piston, the generally known so-called two and four-stroke procedure changed.

Every time the crankshaft rotates, the gas is changed without using the piston’s suction lifting action (suction into the cylinder space through the cylinder head in the four-stroke process, suction into the crankshaft space below the piston in the two-stroke process), and / or without using a supercharger, only by using the Vibration processes in an appropriately designed exhaust system (resonance exhaust system), which is known from two-stroke engines in racing.

In connection with variable control times of the corresponding control devices (channels or valves), the process results in a fresh gas change and a working cycle with each crankshaft revolution. This achieves a power density that corresponds to that of the two-stroke process, but, depending on the design of the reciprocating piston internal combustion engines possible by the process (no more flow through the crankcase space), does not have its disadvantages.

The invention is based on the findings of the inventor in accordance with published patent application DE 44 46 057 AI and international publication number WO 96/19650, each dated June 27, 1996, in particular patent claim 19. These findings of the inventor led to the combination of features of the four-stroke process with features of the two-stroke process according to the invention, since based on these findings of the applicant a gas change even without the suction Stroke effect of the piston (apart from its timing function when opening and closing any inlet and outlet channels) is possible. The gas exchange in so-called reciprocating piston internal combustion engines of all types can only be brought about by utilizing the vibrations of a correspondingly designed exhaust system which is described below as a resonance exhaust system by two-stroke engines in racing.

In the case of a resonance exhaust system, the pressure waves which arise from the respective number of combustions and which emerge from the cylinder space after the combustion through the exhaust port are transformed into frequent vacuum waves (intake) and frequency by the shape of the latter with diffusers, cones, counter cones and tailpipe nozzle Counter pressure waves (charging of the fresh gases sucked into the resonance exhaust system by the vacuum wave) are converted. The resulting vacuum waves are strong enough to trigger a gas change alone, and the counter pressure waves are strong enough to achieve a charging effect.

For example, an engine originally designed for operation according to the so-called four-stroke process, with a corresponding change in the valve timing in conjunction with an appropriately designed exhaust system (resonance exhaust system), perform one work cycle with every revolution of the crankshaft, i.e. convert to the mode of operation of the two-stroke process.

Also e.g. With an engine designed for operation according to the so-called two-stroke process, with a corresponding change in the duct routing and timing of the ducts, in connection with an appropriately designed exhaust system (resonance exhaust system), a working cycle takes place with every revolution of the crankshaft, without the fresh gases being released beforehand by the To manage crankshaft space.

Also possible are designs of new engines, the outlet through channels with valves in the cylinder head, the inlet through channels in the cylinder wall or the outlet through channels in the cylinder wall and the inlet through channels with valves in the cylinder head. The method according to the invention has the advantage, on the one hand, that a work cycle is assigned to each crankshaft revolution, so that the power density in the method according to the invention corresponds to that of the two-stroke method, but without, on the other hand, the mixture having to be directed through a crankshaft space, since the crankshaft space is - as in the four-stroke method - separated from the cylinder chamber and the mixture does not flow through it.

With an appropriate design of the duct routing and control systems as well as control times and fuel allocations, it is e.g. possible to significantly improve the exhaust gas behavior of the reciprocating internal combustion engines that are possible as a result.

To date, patent claims have been issued for reciprocating piston internal combustion engines which carry out a work cycle with each crankshaft revolution, such as, for example, US Pat. No. 4,162,662 (Jean Melchior), US Pat. No. 5, 140,958 (Kobayshi et al. / Toyota) and DE patents 4012 491 AI, 4012 471 AI, 4012 474 AI (Dr. Krüger / Volkswagen), or EP-AO 459 848 (Jean Melchior et al.) And others, but these do not use the vibration processes in a correspondingly designed exhaust system ( Resonance exhaust system) to change the gas, but try, for example by purging the fresh gases to a pressure higher than the normal ambient pressure to produce a flushing of the cylinder space. It is not described how the strokes are ejected and sucked in with these reciprocating piston internal combustion engines, but only how the cylinder chamber is flushed through a charge.

By charging alone, no vibration process is generated per se, but this is necessary for optimal filling.

In the method according to the invention, the fuel is supplied to the fresh gas from its inflow into the cylinder space, which can be done, for example, by an inlet port injection, the injection jet of which is directed onto the valve plate (s). In the case of intake ducts in the cylinder wall, the injection jet must be directed towards the interior of the cylinder. In another preferred embodiment, the fuel is supplied to the fresh gas after it has flowed into the cylinder space, which can be done, for example, by an injection valve which is attached to the cylinder wall and injects into the pre-compressed air.

In a third embodiment of the method according to the invention, the fuel is supplied to the fresh gas after it flows into a prechamber connected to the cylinder space.

The fuel is preferably supplied to the fresh gas by at least one injection valve.

According to a further embodiment of the method according to the invention, the fresh gas can additionally flow into the cylinder space under pressure, the pressure increase of the fresh gas being able to take place, 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, for example in the case of a gasoline engine.

However, the mixture can also be ignited by compression of the mixture as self-ignition, as is the case, for example, with a diesel engine.

According to one embodiment of the method, the outlet (valve in the cylinder head or channel in the cylinder wall) opens in front of the inlet (valve in the cylinder head or channel in the cylinder wall) and closes in front of the inlet, so that both the outlet and also for a predetermined period of time the inlet is open.

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

According to a preferred embodiment of the method, the outlet (valve in the cylinder head or channel in the cylinder wall) opens in a time-variable manner by a control system before opening the inlet (valve in the cylinder head or channel in the cylinder wall), which is also variably controllable in its total opening time by a control system is, and closes, changeable in time by a control system before, during or after the inlet is closed, so that both the outlet and the inlet are open during a variable period.

The second object on which the invention is based is achieved by four possible designs of reciprocating piston internal combustion engines which operate according to one of the previously described methods, with at least one cylinder closed by a cylinder head at one end and in which an axially movable piston is inserted at one end of the connecting rod pivotally connected to the piston, the other end of which is rotatably mounted on a crankshaft, at least one intake port and valve in the cylinder head or an intake port in the cylinder wall and at least one exhaust port and valve in the cylinder head or an exhaust port in the cylinder wall, and, if not only channels in the cylinder wall are used for the inlet and outlet alone, at least one control shaft which urges the inlet and / or the outlet valve into an opening and closing movement and which is in drive connection with the crankshaft via a drive device what Hu Piston internal combustion engines are characterized in that the outlet duct with an appropriately designed exhaust system

(Resonance exhaust system) is connected, which converts the exhaust pressure waves into negative pressure and back pressure vibrations.

If not only channels in the cylinder wall are used alone (the opening and closing times of which are regulated by the piston and / or timing systems), a camshaft which acts on the intake valve and / or the exhaust valve is driven at the speed of the crankshaft, so that an opening and closing operation of the intake valve and / or the exhaust valve are assigned to the reversing cycle of the piston, that is to say each revolution of the crankshaft. This ensures that with every crankshaft revolution, in connection with the design of the valve timing, a gas change, which generates the resonance vibrations through the appropriately designed exhaust system, can take place in the cylinder chamber.

In all designs, an exhaust system is connected to the exhaust duct, which is designed as a resonance exhaust system and converts the exhaust gas pressure wave into vacuum and counterpressure vibrations.

The invention is explained in more detail below using an example with reference to the drawings. The following can be seen in these:

Figures 1A-1D show the four possible designs of the reciprocating piston internal combustion engines according to the invention, the single cylinder engine with two overhead camshafts for the exhaust and the inlet valve in the cylinder head in Figure 1A, the single cylinder engine with an overhead camshaft for the exhaust valve in the cylinder head and an inlet duct in the cylinder wall in FIG. 1B, which acts as a single-cylinder engine with an overhead camshaft for the inlet valve in the cylinder head and an outlet duct 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 1D, are shown in connection with the necessary resonance exhaust system.

However, single-cylinder engines are also conceivable which have several valves in the cylinder head and / or channels in the cylinder wall on the intake and / or exhaust side.

Multi-cylinder engines are also conceivable in the usual cylinder arrangements (for example in-line engines, V-engines, boxer engines, radial engines, etc.). FIGS. 2A-2C show diagrams of the opening and closing times of the

Valves in the cylinder head and / or the channels in the cylinder wall depending on the crankshaft angle.

A piston 2 is arranged axially displaceably in the cylinder 1. The cylinder 1 is connected at its upper end to a cylinder head 3, a cylinder head gasket 13 being arranged between the cylinder 1 and the cylinder head 3. In the cylinder head 3 there is formed a cylinder head space 15 arranged coaxially with the cylinder, which essentially merges 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 mounted in a crankshaft space below the cylinder 1. The connecting rod 5 is pivotally mounted on 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 IC, an inlet channel 12 with a pre-positioned inlet membrane 17 is provided in the cylinder head 3, which opens into the cylinder head space 15. The mouth of the intake port 12 in the cylinder head space 15 is closed by an intake valve 6 (Figures IN IC). The intake valve 6 (Figures IN IC) is acted upon 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 illustration of FIGS. 1A, IC, pretension the inlet valve 6 in its closed position.

In FIGS. 1B and 1D, an inlet channel 19 with an inlet membrane 17 placed in front is provided in cylinder 1, which opens into 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 space 15 (FIG. 1A) opposite the mouth of the inlet duct 12 or which extends above the mouth of the inlet duct 19 through the cylinder wall into the cylinder space 16 ( 1B) leads out of the cylinder head space 15. The mouth of the exhaust port 14 is closed by an exhaust valve 7 (FIG. IN 1B) which is acted upon by an exhaust camshaft 9 for opening and closing, the exhaust valve 7 (FIG. IN 1B) also a known valve return mechanism is held in the closed position. The mouth of the outlet channel 25 (figures IC, ID) from the cylinder space 16 is opened and closed by the reversing piston in connection with a variable time control system (figures IC, ID)

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 in conjunction with the design of the resonance exhaust system with diffuser (26 ), Cone (27), counter cone (28) and tailpipe nozzle (29) arising, under 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 arranged in the intake manifold (Inlet channels 12 and 19) can be provided, but it can also be arranged on the cylinder wall and / or the cylinder head. In addition, several 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-tinder, the spark plug can be dispensed with and, if necessary, can be replaced by a glow plug. In the case of a self-tinder (diesel engine), a prechamber can also be provided in the cylinder head, which is connected to the cylinder head space 15 and in which before the injector opens. In principle, the injection valve 11 can also open directly into the cylinder head space 15 in the case of a compression-ignition engine. According to FIGS. 1A-1C, the crankshaft 4 is provided with a drive wheel 20 shown in dot-dash lines, and the camshafts 8 and / or 9 are each provided with a corresponding drive wheel 22 and / or 24. 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.

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

2A shows a circle which schematically represents one revolution of the crankshaft, the direction of rotation corresponding to the clockwise direction (arrow x). The top dead center OT, in which the piston assumes its upper position and the lower 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 port 25 leading from the cylinder space is designated AO and is preferably in the range between 1 10 Grand and 65 Grand, preferably between 95 degrees and 65 degrees, more preferably between 80 degrees and 65 degrees before bottom dead center UT.

The time of opening of the inlet valve 6 or of the inlet channel 19 opening into 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 time of closing the exhaust valve 7 or the exhaust port 25 leading from the cylinder space is designated AS and is preferably in the range between the bottom dead center UT and about 110 degrees after the bottom dead center UT, preferably 5 degrees to 95 degrees after the bottom Dead center UT:

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 bottom dead center UT and about 100 degrees after 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 relationships 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 counter-pressure wave that arises in connection with the exhaust system (resonance exhaust system) comes into play with its supercharging effect.

FIG. 2C shows a special embodiment of the method according to the invention, the opening times AO and EO being variable with respect to one another by means of variable control systems in such a way that the crankshaft angle between AO and EO can be designed differently, but AO is always 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, with AS being able to lie either before, essentially simultaneously 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, come into their own to increase performance. Reference list

1st cylinder

2. Piston 3. Cylinder head

4. Crankshaft

5. connecting rod

6. Inlet valve

7. Exhaust valve 8. Intake camshaft

9. Exhaust camshaft

10. Spark plug

11.Injection valve 12.Inlet duct cylinder head 13.Cylinder head gasket

14.Exhaust port cylinder head

15. Cylinder head space

16. Cylinder room

17. Inlet membrane 18. Drive means

19. Inlet duct cylinder wall

20. Drive wheel

21. Timing control system intake duct cylinder wall

22. Drive wheel 23. Timing system exhaust duct cylinder wall

24. Drive wheel

25. Exhaust duct cylinder wall

26. Diffuser of the resonance exhaust system

27. Cone of the resonance exhaust system 28. Cone of the resonance exhaust system 29. Tailpipe nozzle of the resonance exhaust system

Claims

P a t e n t a n s r u c h e

1 Method of Generating Physical Power in a Reciprocating

Internal combustion engine, in which in at least one piston-cylinder unit a piston (2) reverses in a cylinder (1) and transmits the reversing movement via a connecting rod (5) to a crankshaft (4), in which a mixture of fresh gas and fuel from a piston (2) moving in a first direction is compressed and ignited, in which the ignited mixture burns and thereby moves the piston (2) in a second direction opposite to the first direction, characterized in that the exhaust gas pressure wave through channels with temporal Control systems in a so-called resonance exhaust system with diffuser (26), cone (27), counter-cone (28) and tailpipe nozzle (29) of known type and design flows out, so that the exhaust gas pressure wave is used to generate speed-frequency pressure waves by this appropriate shape, that a first vacuum wave , which arises through the transition from diffuser (26) to cone (27) when flowing through the exhaust gas pressure wave ht, the cylinder chamber emptied, that fresh gas can now be sucked into the cylinder chamber through channels with time control systems, that the counter pressure wave, which arises through the transition from the counter cone (28) to the tailpipe nozzle (29) when flowing through the exhaust gas pressure wave, has a charging effect of the fresh gases in the resonance exhaust system is achieved, so that during each reversing cycle of the piston in the area of bottom dead center a gas change is effected in the cylinder space (16), without charging the fresh gases, without the piston lifting action due to an idle cycle, as in the case of well-known four-stroke engine, or without the need to flow into a crankshaft space below the piston as in the well-known two-stroke engine 2 The method according to claim 1, characterized in that the fuel is supplied to the fresh gas before it flows into the cylinder space

3 The method according to claim 1, characterized in that the fuel is supplied to the fresh gas after its inflow into the cylinder space

4 The method according to claim 1, characterized in that the fuel is supplied to the fresh gas after its inflow into a prechamber connected to the cylinder space

5 The method according to any one of the preceding claims, characterized in that an injection device (11) is provided, which for each revolution of the crankshaft (4) measures a predeterminable amount of fuel to the fresh gas intended for combustion

6 The method according to any one of the preceding claims, characterized in that the fresh gas flows additionally pressurized into the cylinder space

7 The method according to any one of the preceding claims, characterized in that the ignition of the mixture is carried out by at least one external ignition device 8. The method according to any one of claims 1-6, characterized in that the ignition of the mixture as a high compression of the mixture

Self ignition takes place

9. The method according to any one of the preceding claims, characterized in that the time of opening of the outlet (AO) before that of the inlet (EO) and that the time of closing the outlet (AS) before that of the inlet

(ES) has, so that both the outlet channel and the

Inlet channel are open

10 Method according to one of claims 1-8, characterized in that the time of opening of the outlet (AO) is before that of the inlet (EO) and that the time of closing of 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 timing of the opening of the outlet (AO) and that of the inlet (EO) can be changed over time by variable control systems such that the crankshaft angle between AO and EO over the entire speed range can be designed differently, but always has AO before EO and that the closing times AS and Es can also be changed with respect to one another by means of variable control systems, so that the crankshaft angle between AS and ES can be designed differently over the entire speed range, with AS being able to lie both before and after ES over this speed range

12 reciprocating internal combustion engine, working according to a method of claims 1-1 1, with at least one of a cylinder head (3) at one end closed cylinder (1), in which an axially movable piston (2) is used, one at its first End of the connecting rod (5) pivotally connected to the piston (2), the other end of which is rotatably mounted on a crankshaft (4), in which fresh gas passes through at least one inlet channel (12) with a preceding inlet membrane (17) and at least one inlet valve (6 ) can flow 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), preferably a camshaft, which acts on the opening and closing movement, d ie with the crankshaft (4) via a drive device (18, 20, 22, 24) in drive connection, characterized in that the outlet channel is connected to a so-called resonance exhaust system of a known type and design and thereby the gas exchange according to a method of Claims 1 to 1 1 can take place.

13 reciprocating internal combustion engine, working according to a method of claims 1-1 1, with at least one of a cylinder head (3) closed at one end

Cylinder (1), in which an axially movable piston (2) is inserted, on one its first end with the piston (2) pivotally connected connecting rod (5), the other end of which is rotatably mounted on a crankshaft (4), in which fresh gas passes through at least one inlet channel (19) with a preceding inlet membrane (17) and a time-variable control system (21) through the cylinder wall into the cylinder chamber (16), into which the cylinder chamber (16) formed in the cylinder (1) can flow, in which the exhaust gas pressure wave generated by the combustion passes through at least one outlet channel (14) and at least an exhaust valve (7), which can flow out in the cylinder head (3), in which the exhaust valve (7) is controlled by at least one control shaft (9) which acts on the opening and closing movement, preferably a camshaft, which is connected to the crankshaft ( 4) via a drive device (18, 20, 24) in drive connection, characterized in that the outlet channel is known with a so-called resonance exhaust system Type and training is related and that the gas exchange can take place according to one of the method of claims 1 to 11

14 reciprocating internal combustion engine, working according to a method of claims 1-1 1, with at least one of a cylinder head (3) at one end closed cylinder (1), in which an axially movable piston (2) is used, one at its first End of the connecting rod (5) pivotally connected to the piston (2), the other end of which is rotatably mounted on a crankshaft (4), in which fresh gas passes through at least one inlet channel (12) with a preceding inlet membrane (17) and at least one inlet valve (6 ) can flow into the cylinder space (16) formed in the cylinder (1), in which the exhaust gas pressure wave caused by the combustion through at least one outlet channel (25) in connection with a time-variable control system (23) through the cylinder wall from the, in Cylinder (1) formed cylinder space (16) can flow out. in which the inlet valve (6) is controlled by at least one control shaft (8) which acts on the opening and closing movement, preferably a camshaft, which is in drive connection with the crankshaft (4) via a drive device (18, 20, 22) characterized in that the outlet duct is connected to a so-called resonance exhaust system of a known type and design and that the gas exchange can thereby take place according to one of the methods of claims 1 to 11

15 reciprocating internal combustion engine, working according to a method of claims 1-1 1, with at least one of a cylinder head (3) at one end closed cylinder (1), in which an axially movable piston (2) is used, one at its first End with the piston (2) pivotally connected connecting rod (5), the other end of which is rotatably mounted on a crankshaft (4); in which fresh gas flows through at least one inlet channel (19), which with a preceding inlet membrane (17) and a time-variable control system (21) through the cylinder wall into the cylinder chamber (16), in the cylinder chamber formed in the cylinder (1) (16) can flow in, in which the exhaust gas pressure wave generated by 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 in that the outlet duct is connected to a so-called resonance exhaust system of a known type and design and in that the gas exchange can take place according to one of the methods of claims 1 to 11