JPS5920849B2 - A device that scavenges and supplies air to the cylinders of a two-stroke internal combustion engine. - Google Patents

Description

DETAILED DESCRIPTION OF THE INVENTION The invention relates to a device for scavenging and charging the cylinders of a two-stroke internal combustion engine, in particular a diesel engine, according to the preamble of claim 1.

As is known, the maximum amount of scavenging air is allowed to flow into the cylinder chamber as a piston as tightly as possible over the cross-sectional area of the cylinder, and the combustion gases present in the cylinder chamber are forced out according to the displacement body principle. In theory, the cylinders of a two-stroke internal combustion engine can be effectively scavenged and charged with air or a mixture of fuel and air.

In order to scavenge and supply air to the cylinder effectively, it is necessary to open the air passage to obtain the maximum net passage area (the product of the geometric passage area and the flow coefficient) and to displace the air. The flow piston is kept as tight as possible and as few separations occur in each flow line and/or vortex as possible, i.e. as the air or gas mixture enters the cylinder chamber, which is filled with combustion gases. It is necessary that the mixed region last as short as possible.

Previously known scavenging systems (H.L.H. List, “Conversion of Supply Air for Internal Combustion Engines ° 1 Part 2” (published in Vienna, 1955), page 122; P.H. Speitzer, 112-stroke diesel engine, "Scavenging" (1978)
(Published in New York, 1930), p. 16; 11 Shipbuilding and Sailing Records (Published in March 1930, p. 382), this type of displacement type scavenging is hardly ever carried out.

Known scavenging systems, in which air scavenges the cylinder chamber in a flowing state extending in the direction of the cylinder axis, are provided with an inlet slit on the periphery of the cylinder casing, which is directly controlled by a piston, and a cylinder cover. Recently adopted devices with an externally controlled outlet opening in the region of the engine and scavenging in the same direction as the compression stroke of the engine are hardly suitable for constructing air pistons acting as displacement bodies. None or not suitable at all.

In this system, the scavenging air enters the inlet slit in a generally radial direction, so that a swirl must be created to ensure a stable axial flow.

However, such a swirl precludes or makes it difficult to form a displacement air piston that fills the cylinder cross-section as uniformly as possible.

This is because a lump of heart remains in the central region that is not scavenged or is insufficiently scavenged.

Recently adopted scavenging systems configured with opposite longitudinal scavenging have been designed with inlet slits distributed around the cylinder casing as an air passage blocking mechanism. It is equipped with a slide and, in the case of an air passage provided in the cylinder cover, with a valve opening toward the cylinder chamber.

In the case of inlet slits distributed around the casing in the area of the cylinder cover, a swivel must also occur, so that the +1 displacement body piston 11
In the case of conventionally used radial slides, apart from the inability to form In the case of , a gap always remains between the slide and the cylinder wall due to structural constraints, so the slide contacts the cylinder wall like a valve seat during compression, combustion, and expansion of air within the cylinder. Never.

Due to the construction of such a slide, it is not possible to seal the combustion chamber to a degree comparable to that of a valve, even though the slide is expensive to process and manufacture.

When using an air passage that can be closed by a valve that extends through the cylinder cover, if a valve body is installed that prevents the smooth inflow of air, the inflowing gas will be deflected by about twice as much. It will flow.

Therefore, the individual streamlines of the gas flow are torn apart and the mixing region becomes wider! Due to the relatively long length (extension), problems occur in the gas flow, such that the formation of the "displacement piston" is severely restricted.

SUMMARY OF THE INVENTION It is therefore an object of the invention to provide a device for scavenging and supplying air, which is designed to form a displacement air piston as far as possible.

The air passage blocking mechanism provided in the cylinder chamber of the device of the present invention must have a valve-like sealing action in the closed position so that the above-mentioned obstruction does not appear in the air flow.

The above object has thus been achieved according to the invention by a configuration according to the features recited in claim 1.

It is provided on the combustion chamber side surface of the cylinder cover through which the scavenging and air supply medium flows in the axial direction, and is held in a state without play by being pressed in the axial direction of the cylinder. The axial slide is forced towards the cylinder cover by the ignition pressure in the cylinder chamber and comes into contact with the cylinder cover like a valve.

For example, as soon as the pressure in the cylinder decreases after the piston has moved downwards and the exhaust slit has been opened and a pre-evacuation has taken place, the axial slide is released from the loaded condition.

The axial slide then rests without play on the cylinder cover, but moves unloaded.

Therefore, it can be said that the structure according to the present invention has the characteristics of a valve regarding the axial sliding operation as far as the sealing function is concerned.

In addition, the use of axial slides and the corresponding distribution of air passages provide a large number of air passages, preferably at least 10 air passages distributed over at least two concentric circles, and the cylinder chamber. Alternatively, it is possible to provide a passage opening corresponding to the air passage in a slide which rests against a limited cross section of the cylinder cover, ie the cross section accommodating the fuel injection valve.

The lateral non-spreading feature relates to the axis of the air passage and not to the cylinder axis of the internal combustion engine.

A flow without any lateral divergence is only possible in the air duct, since it is unavoidable that the jet of air flows out of the air duct with a swell.

Due to the lack of lateral spread, the flow coefficient is very high, providing the maximum net passage area for the flow created within the cylinder chamber.

This allows the maximum possible air volume or gas mixture to flow into the cylinder chamber through the cylinder cover in the axial direction of the cylinder, i.e. without a radial component and with a very uniform distribution over the cross section of the cylinder. can be done.

By shaping the cross-section of the inlet side of the air passage in the cylinder cover so as to obtain a flow without separation as it enters the air passage, and/or by shaping the cross section of the inlet side of the air passage in the cylinder cover so that the flow of air generated in the cylinder chamber is conveniently spread out and uniform. By configuring the outlet end of the air passage and the passage opening to discharge, the required flow characteristics can be significantly improved.

Such a significant improvement in flow properties can be achieved, for example, by lightly funneling the inlet and outlet edges of the air channels in the cylinder cover or the passage openings of the axial slides. .

It is convenient to spread out the jet of air in such a way that after passing a short distance the spread jet covers the entire cross-sectional area of the cylinder chamber as uniformly as possible, °C, so that the flow energy of the jet is lost over said distance, and the jet This can be ensured by ensuring that the flow is not disturbed in the opposite direction by the eddies.

In addition, the word “1 most convenient <11” mentioned above is
This means that the air is exhausted evenly.

When exhausting and charging cylinders, the device according to the invention increases the so-called time cross-section and increases the scavenging cut-off for the scavenging flow, which is a simple measure of the flow resistance that appears during the scavenging stroke. The area can be calculated based on the time cross section.

The time cross-section, known as the integral over time and the rotation of the crankshaft across the instantaneous cross-sectional area of the flow opening, represents the resistance against the scavenging air flow for a constant control time.

The time cross-sectional area can be described as the area under curve e in FIG. 10 for the flow entering the cylinder chamber.

In FIG. 10, the opening cross-sectional area of the exhaust slit (curve a) and the opening cross-sectional area of the inlet opening (curve e) are illustrated with respect to the angle α of the crankshaft, that is, with respect to time.

The increased time cross section means that the flow resistance in the gas stream is significantly reduced.

As a result, the rank angle required for the scavenging stroke can be designed to be small, and the net stroke can therefore be lengthened.

Do not mix significantly with scavenging air (because it is excluded)
The exhaust gas remains at a high temperature, which causes waste gas and
The output of the turbine can be increased, and the overall efficiency can be further increased by making better use of the waste heat.

Furthermore, it is known that for a given amount of excess scavenging air, displacement scavenging provides a higher degree of cleanliness than all other scavenging methods.

As a result, for the same kinematic average pressure and the same charge air pressure, more air can be provided for combustion, which prevents the unit fuel consumption from decreasing.

Another advantage of this new scavenging system is that it avoids the entrainment of solid combustion residues that occur when using valves.

This is because such solid fuel residues can always be removed from the openings of the air channels by means of the axial slide.

For this purpose, it is advantageous if all edges of the axial slide facing the cylinder cover and/or all edges of the cylinder cover facing the slide are sharply designed.

Furthermore, using the device according to the invention, for example, the known 11 swing valves 1! It is possible to re-air the cylinder by controlling the air, such as by using a mechanical control means such as a check valve or by using a mechanical control means such as a check valve.

As is well known, the principle of the swing valve has the following characteristics:
Immediately before the cycle of the air column reciprocating in the longitudinal direction during the supply air closes the inlet opening, that is, after the descending piston closes the exhaust slit, the period of the air column reciprocating in the length direction also moves toward the cylinder chamber in the time range n in Fig. 10. The amount of air supplied to the cylinder cover is adjusted in accordance with the opening cycle of the air inlet side opening provided in the cylinder chamber so that the cylinder cover has a half cycle.

In order to maximize the total opening cross-sectional area of the air passage and at the same time ensure a sufficient contact area of the axial slide that contacts the cylinder cover, the shape of the passage opening provided in the air passage and the axial slide, as well as the axial direction Careful consideration must be given to the installation and operation of the adjustment element or rotary mechanism that reciprocates the slide.

For the air passages, it is advantageous to have a circular cross-section in order to avoid complex shapes that are difficult to manufacture, and therefore the air passages lie on the circumference of at least two circles concentric with respect to the cylinder axis. It is effective to consist of a large number of elongated holes of different hole diameters that are uniformly distributed.

Furthermore, each axial slide is provided with passage openings whose number and size are equal to the number of elongated holes provided in the cylinder cover.

In this case, the elongated diameter and the diameter of the passage opening are smaller than the half-pitch of the elongated holes in the corresponding concentric row.

Advantageously, the rotary mechanism for operating the axial slide is constructed and arranged in such a way that it offers no or at most only a slight resistance to the flow.

The dowel mechanism is, for example, a dowel pin that passes through the cylinder cover and can enter into the air passage and, with the interposition of a pretensioned resilient element, allows the axial slide to pass through the cylinder cover. It may also be a rotary pin that is adapted to come into contact with the.

Furthermore, the relief hole can be formed in such a way that the dowel pin can be moved into the open and/or closed position and with play without bumping inside the cylinder cover.

To control the axial slide, it is advantageous to use a simple hydraulic control of the type commonly used.

This is because the axial slide itself is not provided with a stopper to set the exact position of the axial slide.
This is because the fixation of the axial slide must be carried out by a hydraulic system.

Finally, the combustion conditions can be improved by taking structural measures such that the axial slide opens or closes two rows of slotted holes at different times, creating the known annular turbulence.

The abovementioned construction measures can thus be implemented, for example, by a very slight geometrical offset of the passage openings and slots of one row with respect to the other row.

In the device of the invention, the axial slide can be rotated intermittently to and fro without a substantial pressure difference between the combustion chamber and the air chamber.

Since the above-mentioned condition occurs immediately after the end of the preexhaust, the axial slide opens the air inlet passage at the moment this preexhaust ends.

"Pre-exhaust" refers to the cycle of a two-stroke engine.
The exhaust port is already open, but the air inlet port is still closed.

The axial slide returns to its original position just before the exhaust port closes.

The reason for this is that the moment the exhaust port closes, the pressure of the air in the combustion chamber begins to rise.

In a two-stroke engine where the piston controls the opening and closing of the exhaust port, the axial slide operates to open the exhaust port and reduce the pressure in the combustion chamber before the air inlet port opens. can be lowered.

Moving the axial slide only during periods when there is no substantial pressure difference between the combustion chamber and the air chamber has the effect of reducing the force or torque required to move the axial slide, and further reduces the amount of force or torque required to move the axial slide. This movement has the effect of reducing wear on the axial slide and cylinder head.

The present invention will now be described in detail with reference to embodiments illustrating the invention.

The upper part of the combustion chamber or cylinder chamber 1 of a cylinder 2 of a diesel engine (not shown) is closed by a cylinder cover 3, and a fuel injection device 4 is disposed in the center of the cylinder cover 3.

An exhaust slit 5 is provided on the outer surface of the cylinder 20, and the exhaust slit 5 is opened by the piston during the downward stroke and closed again during the compression stroke.

For diesel engines, supply air and
In the case of an engine, air passages 7 are provided in the cylinder cover 3 for supplying a mixture of air and fuel.

The air passage 7 consists of two circles 9 and 10 concentric with the cylinder axis.
(see FIG. 2) and are designed as elongated holes in the cylinder cover 3.

The diameter of the air passage 7 is different in each of the two rows of circles 9 and 10.

The cylinder 1 communicates via an air passage 7 with an air chamber 8, which is shown conceptually.

The opening and closing of the air passage or elongated hole 7 is controlled by an axial slide 11 provided with through holes 12 whose arrangement, shape and size correspond to that of the elongated hole 7.

The axial slide 11 is housed in a ring-shaped recess 13 in the cylinder cover 3 and has a swivel mechanism or swivel pin 14 extending through the elongated hole 7.
It is maintained by

These rotary pins 14 are carried by an adjusting arm 15 having leaf spring-like elasticity, so that the adjusting arm 15 can be axially slid even when the cylinder chamber 1 is under negative pressure. 11 is pressed in the axial direction toward the bottom of the cylinder cover 3 to apply precompression so that it comes into contact with the bottom of the cylinder cover 3.

The leaf-spring-like adjusting arms 15 all have adjusting bushes 1 which are engaged with an adjusting mechanism (not shown) which opens and closes an axial slide 11 , conceptually represented by a pivot lever 17 .
6 is connected.

The adjusting drive, which is preferably constructed in a conventional hydraulic system, serves to move the axial slide intermittently in accordance with the operating tact of the engine, and in the embodiment shown is reciprocating. However, in other configurations it can be operated continuously.

In order to allow the air to flow unhindered into the bore 7 of the cylinder cover 3, the plate 15 is arranged in the passage cross-section of the elongated hole 7, at least in the open position of the axial slide 11. They are shaped and guided so that they do not touch (see Figure 3).

Furthermore, in order not to disturb the flow state, it is necessary that the dowel pin 14 be offset out of the elongated hole 7 at the end position of the reciprocating axial slide 11.

For this reason, for manufacturing reasons, the slotted hole 7 was similarly bored.
A supplementary passage or relief hole 18 is provided in the cylinder cover 3 which extends parallel to the cylinder cover 3, and a portion of the circumference of the supplementary passage or relief hole 18 intersects with the elongated hole 7.
It opens toward the elongated hole 7.

Configured in this way, the dowel pin 14 is axially slid next to the elongated hole 7, which allows the dowel pin 14 to move along an arc during movement of the axial slide 11. It will be located in an adjacent chamber that accommodates eleven end positions.

The position and diameter of the escape hole or adjacent chamber 18 correspond to the fact that the rotary pin 14 has completely turned from the cross-sectional passage of the elongated hole 7 through which the air is guided, and the diameter of the circular trajectory connecting the rotary pin 14 at this time corresponds to It is larger than the diameter of the locus of the circle connecting the center points of the elongated holes 7 lined up on the concentric circles 9, and all sides of the drive pin 14 are in an open state in the escape hole 18, and the escape hole 1
It is selected so that it does not hit the side of 8.

The number of rotary pins 140 is a minimum of 4 in the illustrated embodiment.
The number of elongated holes 7 can be set between 1 and 7.

As can be seen from FIG. 2, the elongated holes 7 are provided in the cylinder chamber 1 in order to supply air as uniformly as possible over the cross section of the cylinder chamber 1 by a large number of jets of air.
or distributed over the cross-section of the cylinder cover 3 on two concentric circles 9 and 10 as evenly and symmetrically as possible.

The size and number of the elongated holes 7 are determined based on the requirement to obtain as large a total opening cross-sectional area as possible in order to ensure a flow velocity as low as possible for a given scavenging volume and to allow each jet of air to flow smoothly. Determined accordingly.

On the other hand, the size and number of the elongated holes 7 are such that when the axial slide 11 is closed, the cylinder chamber 1 is connected between the elongated hole 7 including the relief hole 18 and the through hole 12 provided in the axial slide 11.
The opposite requirement is that the necessary overlap must be provided to cover the gap.

In the illustrated embodiment, an eight-division is chosen for the arrangement of the elongated holes 1 on two concentric circles 9 and 10, so that the reciprocating rotational movement of the axial slide 11 takes place over an angular range of 22.5°. It turns out.

As mentioned above, the left half of FIGS. 1 and 2 shows the axial slide 11 in the open state, while the right half shows the hole 7 and the through opening 12 in the closed state of the axial slide 11. 18 and thus the hole 7.18 and the axial slide 110 in the positional relationship described above.
The state of overlap between the passage opening 12 can be understood from FIG.
It can be understood from FIG. 2 that a minimum degree of overlap is ensured between 0 and 0.

The movement of the axial slide 11 does not take place directly from the piston 6 or directly from the crankshaft;
Since it is controlled by a hydraulic drive which rotates the axial slide 11, it is possible to open and close the axial slide 11 almost instantaneously, i.e. within a very short time, during which the piston 6 moves into the cylinder. There is actually almost no movement within 1.

When air flows into the elongated hole 7 and enters the cylinder chamber 1, the elongated hole 7 The inlet edge 19 of the passage opening 12 and the outlet edge 20 of the passage opening 12 are rounded.

In contrast, in the second embodiment, as shown, the mutually opposite edges 21 and 22 of the elongated hole 1 and the passage opening 12 of the axial slide 24 are designed as sharp edges. Therefore, by moving the axial slide, the combustion residue adhering to the edge 2L22 can be removed.

In the second embodiment shown in FIGS. 4 to 9, the axial slide 11 shown in FIG. 1 extends through the cylinder cover 3 as an elongated hole. It is replaced by an axial slide 24 mounted correspondingly to the air passage 7.

Each axial slide 24 has a rotating mechanism 1 extending through the cylinder cover 3 in a separate elongated hole.
4, it can be rotated.

The axial slide 24 is provided with a recess 25 on the side facing the combustion chamber or cylinder chamber 1 , the recess 25
The bottom surface 26 of the is designed as an inclined surface, and when the directional slide 24 is closed, the fixing latch 27 is designed as an inclined surface.
It fits on top of 6.

The hook 27 is secured by a holder 28 inserted through a hole extending through the cylinder cover;
The holder 28 is fixed to the cylinder cover 3 on the opposite side of the cylinder chamber 1 using screws and nuts 29.

The hole supporting the hook 27 is sealed by the abutment surface of the hook 27 in the axial direction under the action of the internal pressure of the cylinder.

The function of the latch 27 is that, in addition to the extremely eccentrically mounted adjustment pin 14, it also functions as a closed axial slide 2.
4 is to form a second fixed point that supports 4.

The hook 27 should be mounted on the rotary pin 2 in consideration of the location, as long as it does not obstruct the opening of the axial slide 24.
4, the latch 27 is arranged in mirror symmetry with the rotary pin 14 with respect to the radial plane of the cylinder axis extending through the center point of each elongated hole 7. has been done.

The free end of each dowel pin 14, on which each axial slide 24 is fixedly attached, projects from the cylinder cover 3, and is attached to the pivot lever 31 by means of a disk spring 30 providing axial pretension. The attached guide pin 32 is inserted into the slit 34 of the adjustment arm 33 (see FIG. 9).

The axial slides 24 arranged on concentric circles 9 and 10 are each connected to a common adjustment arm 33.

The adjustment arms 33 are each fixed to a central adjustment bush 16, and when the adjustment bushes 16 are reciprocated by an adjustment drive (not shown), the axial slides 24 can be opened and closed all at once. can.

As in the first embodiment (see spring element 15 in FIG. 3), the adjusting arm 33 allows air to flow from the air chamber 8 into the slot 7 of the cylinder cover 30 when the axial slide 24 is opened. It is designed in such a way that it does not prevent leakage.

It goes without saying that the invention is not limited to the illustrated embodiment.

For example, instead of arranging the elongated holes 7 concentrically in more than two rows or providing one axial slide in each elongated hole 7, more than one axial slide with passage openings can be used. It is also possible to provide one.

In addition, the air channels with mutually parallel axes may not be arranged parallel to the cylinder axis, as in the illustrated embodiment, but at an angle to the cylinder axis.

In addition, it is also possible, for example, to provide different degrees of funnel-shaped curvature around the outlet edge 20 of the air passage 7 or the passage opening 12 in various directions, thereby giving each jet of air a different width. be.

By designing the diameter of the passage opening 12 provided in the axial slide 11 to be slightly larger than the diameter of the air passage 7 provided in the cylinder cover 3 which corresponds to this passage opening,
Even if the passage opening and the air passage do not coincide exactly after the movement of the slide, an undisturbed air flow can still enter the cylinder.

[Brief explanation of the drawing]

FIG. 1 illustrates a first embodiment of the present invention by means of a longitudinal sectional view of a cylinder of an internal combustion engine taken along line I--I in FIG. FIG. 2 is a cross section taken along the line ■-■ in FIG. 1, and the left half in FIGS. half is
Figure 2 shows the arrangement with the axial slider closed at a point in time when it has not moved substantially with respect to the piston stroke, for example at a previous point in time with respect to the left side. FIG. 3 is a sectional view taken along the line ■-■ in FIG. FIG. 4 is a plan view of the cylinder cover from the cylinder chamber, showing on an enlarged scale a second embodiment of the invention in which each air passage is closed by a suitable axial slide; be. FIG. 5 is the same partial perspective view as FIG. 4, showing the second embodiment of the invention with the air passageway open. Figures 6 and 7 are the lines VI-vi and ■ in Figures 4 and 5.
- Cross-sectional view taken along line ■. FIG. 8 is a partial elevational view taken in the direction of arrow B in FIG. FIG. 9 is a plan view, equivalent to FIG. 3, of the second embodiment, looking at the cylinder cover from the outside. FIG. 10 is a diagram conceptually showing changes in the opening cross-sectional areas of the exhaust slit (curve a) and the air passage (curve e) with respect to the crank angle and therefore time. 1... Combustion chamber, 2... Cylinder, 3
... Cylinder cover, 4 ... Fuel injection device, 5 ... Exhaust slit, 6 ...
・Piston, 7...Air passage, 8...
Air chamber, 9, 10... Concentric circles, 11...
・Axial slide, 12...Through hole, 13...
... Ring-shaped recess, 14 ... Turning pin, 15 ... Adjustment arm having leaf spring-like elasticity, 16 ... Adjustment bush, 17 ...・・・・・・
Swivel lever, 18... Relief hole, 19...
・Entrance side edge, 20...Exit side edge, 21
．． 22... Edges facing each other, 24...
...Axial slide, 25...Indentation, 2
6... Bottom of the recess, 27... Metal hook, 28... Holder, 29... Nut, 30... Belleville spring, 31... Swivel lever, 32... Guide pin, 33... Adjustment arm, 34... Slit.

Claims (1)

[Claims] 1. A device for sweeping and inflating the cylinders of a two-stroke internal combustion engine with air or a mixture of fuel and air, comprising: Air or a mixture of fuel and air enters the cylinder chamber through a number of air passages in the cylinder cover, and this incoming flow passes through an exhaust slit in the cylinder case controlled by the piston. In a device adapted to discharge combustion gases, at least one axial slide 11° 24 is kept free of play by being pressed in the axial direction of the cylinder and has an intermittent reciprocating rotational movement. is disposed on the combustion chamber side surface of the cylinder cover 3 as a blocking mechanism, and corresponds to the air passage 7 provided in the cylinder cover 3 and the air passage 7 provided in the axial slides 11 and 24. The passage openings 12 are distributed over at least two circles 9, 10 substantially concentric with respect to the cylinder axis, so that the flow with respect to the axis of each air passage 7 does not spread substantially laterally (the cylinder A device characterized in that it is formed to fit into one chamber 1. 2. A patent characterized in that at least 10 air passages 7 are distributed in a cross section of the cylinder cover 3. 3. The device according to claim 1. 3. The device according to claim 1, characterized in that the air passage 7 is an elongated hole passing through the cylinder cover 3. 4. The device according to claim 1. one axial slide 11 with passage openings 12 having a number equal to the number of air passages 7 provided in the air passages 7 and having a size corresponding to the size of the respective air passage 7; and the diameter of the passage opening 12 is smaller than half the pitch of the air passage γ in the associated concentric circle 9°10.
Equipment described in Section. 5 axial slides 11, 24 at different times 2
5. Device according to claim 4, characterized in that it opens and closes the elongated holes 7 in the row. 6. Claims characterized in that the shape of the cross section on the entry side of the air passage 70 provided in the cylinder cover 3 is such that when air enters the air passage 7, a flow without separation is obtained. The device according to paragraph 1. 7 axial slides 11, 240 all of the edges 21 facing the cylinder cover 3 and edges 2 of the cylinder cover 3 facing the axial slides 11, 24;
2. Device according to claim 1, characterized in that all of 2 are formed with sharp edges. 8 A cylinder cover 3 whose diameter corresponds to the passage opening 12 provided in the axial slide 11.
9. The device according to claim 1, characterized in that it is designed to be slightly thicker than the diameter of the air passage 7 provided in the air passage 7. The device according to claim 1, characterized in that the turning mechanism 14 is formed in such a way that the flow resistance can be kept as low as possible. A rotary pin 14 extends through the cylinder cover 3 and abuts against the surface of the cylinder cover 3 facing the combustion chamber, with an elastic element 15 30 pressed by the axial slides 11 and 24 interposed therebetween. 11. The device according to claim 9, characterized in that the swivel pin 14 is adapted to fit into the air passage 7 provided in the cylinder cover 3. 10. The device according to claim 10. 12 A relief hole 18 is provided for the rotary pin 14, and the rotary pin 14 is provided with a relief hole 18 in the open position and the closed position.
12. A device according to claim 11, characterized in that it is shaped so that it can be inserted into it. 13. Device according to claim 1, characterized in that the axial slides 11, 24 are controlled and driven via a central bush 16. 14 The cross-sectional area of the air passage 7 and passage opening 12 arranged on one concentric circle is the same as the cross-sectional area of the air passage 7 and passage opening 12 arranged on the other concentric circle. Device according to claim 1, characterized in that: