DE7621102U1 - ROTARY LISTON ENGINE - Google Patents

Description

FABRIQUE NATIONAlT HERSTAL S.A., en abrege FN, 44Ü0 Herstdl (Belgium)

"Rotary piston engine"

The present invention relates to a novel rotary piston engine with a combustion system of Diesel, gasoline or gas engine types, as well as a new type of rotary piston compressor. As is known, the piston seal forms the main difficulty with all known rotary piston engines. In all rotary piston engines developed to date the rotary pistons always run in non-rotating ones Piston housings and the piston rings are therefore forced to follow the inner wall profile. It is understood that the more the inner wall deviates from the cylindrical shape, the more difficult it is to seal the rotary piston. It is a first task of the invention to make the inner wall of the piston housing of the rotary piston engines completely cylindrical in terms of a significant simplification of the piston sealing problem.

On the other hand, the classic two- or four-stroke engines with piston rod and crank have the disadvantage of one unavoidable shift between ignition and the moment when the energy generated during the combustion process is made available. This is an inherent, essential

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lighter and as an inevitable disadvantage of the piston rod crank mechanism. bias means that at the moment of maximum pressure during the combustion process, the connecting rod is practically in the extension of the crank, so the driving torque is practically zero. When according to the invention Rotary piston engine, however, the aforementioned displacement is zero. Ls gives a driving moment during the whole Combustion process and this driving moment is exclusively through the thermodynamic laws of the processes determined in gaseous media. Hence the great flexibility of the rotary piston engine according to the invention.

The rotary piston engine according to the invention is characterized in that it consists of a cylindrical outer shell and an inner body concentric with the outer shell, with between the outer shell and the inner body a coaxial, also cylindrical rotary piston runs, and that a pressure chamber for the compressed Combustion gas or gasification mixture is provided for feeding the rotary piston engine concerned.

According to a preferred embodiment of the invention In the rotary piston engine, the aforementioned inner body is the aforementioned pressure chamber for the combustion gas Bew. VergasunfaSgemiscii forming hollow body.

Gemä'ss Lrfindung of the pressure prevailing in said pressure chamber is generated by the Obtrgan _B of compressed by the rotary piston gas mixture in the same, and returns this ge _b ebenialls vorverbrennta ousgemisch voi 'of ignition from the pressure chamber into the combustion

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room v., urtick.

According to the invention, the aforementioned cylinderf ordered O-shaped rotary lobes made up of two parallel rotating pistons with the generators of the cylinder and connected by means of two flanges Arms, of which one flange is extended for the purpose of reducing the drive torque generated.

The characteristics and advantages of the inventive Systems are explained by the following detailed description of some exemplary embodiments. This without any restrictive description given on the basis of the accompanying drawings, where

FIG. 1 shows a longitudinal section of a motor according to the invention made according to the broken line CÜEFGH in FIG. I;

Figure 2 shows a cross-section of the engine according to the line AB of Figure 1 Figure 1 reproduces;

Figure 3 is a perspective view of the rotary piston of the engine according to Figures 1 and 2 without shows its piston rings schematically;

Figures 4-7 schematically illustrate several sections explaining the cotation process of the rotary piston in question reproduce,

the figures 8-12 the "transition of the combustion gas or schematically explain gasification mixture under pressure in the aforementioned pressure chamber,

Figure 13 is a perspective view of a variant of the rotary piston according to the invention reproduces schematically; and

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the figures 1Η-Ί8 several the figures H-7 show corresponding views of a Drahkolberi compressor.

As can be seen from Figures 1 and 2 of the accompanying drawings, there is a device according to the invention Rotary piston engine from a cylindrical outer shell 1 and a coaxial also cylindrical inner hollow body 2, whereby between this outer shell and this hollow body a likewise cylindrical one rotating about the common axis hollow rotary piston 3 is arranged.

The outer shell 1 provided with the cover 1 'and the inner hollow body 2 are connected to one another by wedges U. The rotary piston 3 is mounted in the hollow body by means of ball bearings or similar devices 5, specifically directly on the Rear side and by means of a piston cover 3 'acting as a pivot bearing on the front side. At the back is between the outer shell and the piston extension a ball bearing or a similar device 6 is arranged.

The rotary piston 3 is provided with inner piston rings 7 and outer piston rings 8, which are respectively with the Inner hollow body 2 and the outer shell 1 are in contact.

The wall of the rotary piston is provided with two openings 9 and IU provided (Fig.3), separated by wall parts 11 and 12 are separated, of which a side wall 11 'or 12' is an effective piston side. These effective piston sides 11 'and 12 'stand in with the gas mixture during the expansion stage Contact. The aforementioned wall sections are with interior longitudinal segments 7 'and socket longitudinal segments 8' (p. Nbb.2).

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The inner room 2 ^{1 of} the aforementioned Huhlkuryers i is a pressure chamber in which the pressure is generated by the combustion gas (z, B, air) or by a gasified mixture (z, B, air-fuel mixture). In this possibly cell-shaped inner chamber is axially arranged a camshaft 13 driven by the rotary piston 3 and rotating at the same speed, the task of which is four inlet valves arranged in the hollow body, ie the inlet valves 14 and 14 'and the return valves 15 and 15' for the combustion gas or the gasified mixture to control. These valves are connected to the chambers η formed by the aforementioned openings 9 and 10. The inner chamber 2 'must be sealed.

The outer shell 1 has two inlet valves 16

■ and 17 for the entry of the combustion gas or the gasified

Mixture and with two outlet valves 18 and 19 for the relaxed Provided exhaust gases. These valves 18 and 19 are also connected to chambers 9 and 10 »All valves are controlled by cams not shown. In addition, the outer shell 1 with two, mechanically through the rotary piston by means of a mechanism not shown, flap valves 20 and 20 projecting into the openings of the piston 21 (Fig.2). These flap valves 20 and 21 are also suitable, not shown in Figures 1 and 2 Provide sealing devices.

The inner hollow body 2 and the outer shell 1 are cooled by means of the cooling water circulation lines 22 and 23.

In Figures 1 and 2, the internal valves 14, 14 ', 15 and 15', as well as the camshaft 13 are shown.

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The presence of these valves and this shaft facilitates that Explanation of the principle of action. Ea goes without saying that this valve and camshaft mechanism by a perforated distribution box must be replaced can. The solution of the inner holes is already a better mechanical one The solution is, the explanation of the mode of operation of the rotary piston engine according to the invention is nevertheless found here Hand of the valve and camshaft mechanism, which allows an easier explanation of the basic principle, instead.

After the previous description of the various parts of the rotary piston engine according to the invention, it is now the turn of the explanation of the revolution cycle of the rotary piston with reference to FIGS. 4-7. Although the rotary piston engine according to the invention differs fundamentally from the conventional four-stroke engine, it also works according to the four-stroke principle. In the aforementioned drawings, the Drehrichtun _b by a small arrow and indicated at the same time the respective position of the rotary piston. In the description below, the angles are counted from the vertical on the side of the top flap valve.

In the schematic Figure 4, the rotary piston is 30 ° away from its initial position. It is assumed that the Motor with normal output will. The relaxed combustion gases are indicated by crosses on the schematic illustrations indicated.

The intake valves 16 and 17, as well as the exhaust valves 18 and 19 are open, while all valves 14, 14 ', and 15 'of the inner chamber 2 are closed. The inner chamber 2

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is under pressure (pressure P). The generation of this pressure will also be described. The gas mixtures - combustion gas and gasification mixture - are shown schematically on the schematic figures by dots, their Density represents the pressure. Since z, B. the combustion gas in the inner chamber 2 is pressurized is the density of the dots bigger there.

Since the inlet valves are open during the rotation up to 180 °, the rotary piston generates negative pressure in the inner chamber 2 and in the shell 1, which is caused by the sucked in combustion gas (e.g. air) or by the gasification mixture ^ is balanced. Since, moreover, the exhaust valves are open are, the exhaust gases are expelled through the rotary piston. In the position explained by Figure 5, the rotary piston has rotated 180 ° after the previous lifting of the Flap valves 20 and 21. The outlet valves 18 and 19, as well as the inlet valves 16 and 17 have closed relaxed exhaust gases are discharged and the entire free space between the inner chamber 2 and the outer shell 1 is with Combustion gas or filled with gasified fuel under a pressure that is temporarily close to the external pressure. There were in this way so far two combustion gas or. Mixed gas charges sucked in. The pressure P still prevails in the inner chamber 2.

In the position explained by Figure 6, after the two flap valves 20 and 21 have been closed, the has Rotary piston exposes the return valves 15 and 15 ', which are already a few degrees before they are fully opened

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opened by the piston (pre-opening). The combustion | gas or the gasification mixture under pressure now fills the |

free spaces between the aforementioned flap valves and the |

effective sides 11 'and 12' of the piston. The two like that I.

The spaces formed gradually enlarge as a result of the |

I Keep turning the piston and its pressure corresponds theoretically to f

s the pressure prevailing in the inner chamber. If the volume ξ

the inner chamber 2 is significantly larger than that of the two I.

Spaces between the flap valves and the effective sides | of the piston and the shape and size of the valves are appropriate |

are chosen with a view to the greatest possible extent restriction of the pressure loss, the pressure only changes | very little in the variable spaces between the flap valves and the effective sides of the rotary piston.

If the amounts of combustion gas or gasification mixture between the two flap valves 20 and 21
and the effective sides 11 'and 12' of the rotary piston large
are enough (these are calculated quantities)
to ensure complete combustion of the fuel,
the valves 15 and 15 'close. At this moment,
if the quantities sucked in are quantities of combustion gas, the two quantities of combustion gas are injected, with the
Injection is controlled by the injection pump. the
Ignition takes place either with spark plugs or as in a diesel engine
spontaneously by compression ignition according to the set
Compression ratio instead. If the quantities sucked in
Are gas mixtures, the ignition takes place by means of spark plugs.

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- 9 -

Figure 6 relates to the beginning of the combustion process. The cross-hatches relate on the hot combustion air-fuel mixture. By the enthalpy increase caused relaxation of the mixture forms the first stroke of the rotary piston engine, the rotating Rotary piston compresses the two new combustion gas quantities or gasification mixtures.

The pressure loss Δ P in the inner chamber 2 is only a small fraction of the pressure P. In the position illustrated in Figure 6, that in the relevant The pressure prevailing inside the chamber is therefore P - ΔΡ

Figure 7 shows the rotary piston at the end of the relaxation process and at the end of the compression Combustion gas or the gasification mixture. At this moment, i.e. after one rotation of the rotary piston, of approximately 320 °, the inlet valves of the inner chamber 2 open. Gasification mixtures into the inner chamber, the pressure of which increases accordingly by the value ΔP. The one prevailing in the inner chamber The pressure is now again P - Δρ + ΔΡ = P (initial pressure).

After the position explained by Figure 7, a new cycle begins with the one shown in Figure 4 Location. It should be noted that two combustion processes have taken place per revolution of the rotary piston and two quantities of combustion gas or gasification mixtures were sucked in.

It was previously stipulated that the one in the inner chamber prevailing pressure between the values P and P - Δ Ρ

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varies. From the basic principle of the rotary piston engine according to the invention it can be seen that this pressure is maintained by the motor itself during its successive revolutions will ·

Initially, the pressure prevailing in the motor at rest corresponds to the external pressure. It has been through so far in all the previous figures explained assuming that the engine is working at normal power and that in the Inside chamber there is a pressure P which corresponds to the pressure at the end of the compression process.

The following lines examine how this one Pressure is created in the chamber. The one in the inner chamber The pressure prevailing in the motor at rest naturally corresponds to the external pressure. In the description below the pressure build-up in the inner chamber will be as follows Symbols used:

V, = volume of the inner chamber
τ = compression ratio

V., = volume at the end of the compression process Assuming that V, = kV ₃

First, the above symbols need to be explained in more detail.
- V, = volume of the inner chamber, ie the space in which the compressed gas mixture is located.

~ -x - compression ratio, the value of which determines the moment at which valves IU and 14 'are opened. The opening of these valves m and 14 'corresponds to that of valves 15 and 15'. The compression ratio also determines the

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Opening dciuer of valves 14, 14 ¹ , 15 and 15 'for a certain number of revolutions, as well as the moment of closing

of valves 15 and 15 ',

V ₃ = volume at the end of the compression process. At normal output, during the compression stages, when the gas pressure in the space between the piston and the flap valves approaches the pressure prevailing in the inner chamber, the valves 14 and 14 'open. In the present _{exemplary embodiment, V 3 is} the sum of the two combustion gas or gas mixture quantities located between the piston and the flap valves, shortly before the valves 14 and 14 'open. |

The volume V, is approximately equal to the volume of the end '[the compression process between the piston and the cylinder i of the conventional piston engines The head located quantity of gas. j

k = ratio between the volume of the inner chamber and:

the volume at the end of the compression process. ^:

) The build-up of pressure in the inner chamber of the

The rotary piston engine according to the invention is illustrated using an example ■ ·!

educated. The following values are chosen for τ and k:! τ = 8 and k = 3, that is, V _k = 3 V ₃ J

The transfer of the compressed gas can be described using the schematic figures 0-12.

- In the position explained by Figure 8, the> Gas quantities at the end of the compression stage; the valves 14 and 14 'are about to open and the valves [ and 15 'are closed.

- In the position explained by Figure 9, the valves 14 and 14 'are open and the compressed gas mixture is located

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are in the inner chamber and the valves 15 and 15 'are closed.

- In the position illustrated by Figure 10 is the first Transfer stage ended and the valves 14, 14 ', 15 and 15' closed.

- In the position s-.ud die Valves 14 and 14 'closed and valves 15 and 15' opened and the crossing begins in the other direction.

- The crossover is in the position explained in Figure 12

ended in the other direction and the valves 14, 14 ', 15 \ and 15' are closed.

The pressure losses occurring during the pressure build-up in the inner chamber are neglected.

The initial pressure in the inner chamber is therefore P = Patm and the state changes as follows during the first Rotation of the rotary piston.

- Figure 8. From the thermodynamic gas laws the following pressure value in space V,:

ρ = ρ _ο τ ^Ύ = 1 χ 8 ¹ ' ⁴ = 18.38 kg / cm ³

with ρ = initial pressure with the adiabatic pressure change.

2 In the present case ρ = ρ atm = 1 kg / cm.

- Figure 9. The pressure increases in the inner chamber.

- Figure 10. The pressure in the inner chamber is now approximately

ρ = = 6.12 6 kg / cm ² because V, = 3 V

(first approximation: a constant gas temperature is assumed)

- Figure 11. The crossover in the opposite direction begins, as a result of which the pressure in the inner chamber drops.

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- Figure 12. ι ^ r Druok in the inner chamber amounts now

ρ a | 6.126 = 4.565 kg / cm ²

Second turn:

- Figure 8 = p _R = 4.595 kg / cm ²

- Figure 9: p _{] <;} > 4.595 kg / cm

- Figure 10: p _k = 4.595 + 6.126 = 10.721 kg / cm ² ■

q 2 \

- Figure 12: ρ = j- 10.721 = 8.040 kg / cm ■

Third turn:

- Figure 8: p _R = 8.040 kg / cm

- Figure 10: ρ = 8.040 + 6.126 = 14.166 kg / cm

- Figure 12: P _k = f 14.166 = 10.625 kg / cm ²

Fourth turn:

- Figure 8: p _R = 10.625 kg / cm

- Figure 10: p, = 10.625 + 6.126 = 16.751 kg / cm

3 2

- Figure 12 = ρ = - 16.751 = 12.563 kg / cm

^K 4
Twentieth rotation:

- Figure 8: p _R = 18.300 kg / cm ²

- Figure 10: p, = 18.300 + 6.126 = 24.425 kg / cm ²

3 2

- Figure 12: P _k = ^, 24.426 = 18.319 kg / cm

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-m-

The limits arise from the foregoing considerations of the pressure prevailing in the inner chamber. This

2 Pressure varies between lü.3B and 18.38 + 6.126 kg / cm i i.e.

between the limit values with an infinitely large number of tours, the general law! can be written as follows;

with V ₁ = k V "

2
If ρ * ρ atm «1 kg / cm gives the following expression:

YVi T

This relationship only applies to an infinite number of revolutions, but already after 20 revolutions after starting the Engine, the pressure values in the inner chamber differ only about 0.30% from their limit values.

From the above relationship it can also be seen immediately that the two limit values approach one another as the k value increases. For example, for V = 10 V ₃ (k = 10) and τ = 8

or 18.379 <ρ, == ζ 20.217 kg / cm ²

This means that the greater the volume of the inner chamber compared to the volume V ₃ , the lower the pressure fluctuations in the inner chamber at normal output and the longer the relevant pressure build-up time. This is relatively short. For example, with a number of revolutions of 600 rpm during the starting period, the pressure in the inner chamber has practically reached its limit value after just 2 seconds (up to 0.3% after 20 revolutions).

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τ ^γ

It is on the term -r- of the expression of the upper one

γ τ ^Ύ

Pressure limit value (τ ¹ + —r—) that the above-defined

The sign "Δ ρ" relates.

During the tempering period, the inner chamber can of course can also be instantly pressurized by their connection to an auxiliary pressure vessel for the combustion gas or the gasification mixture.

The rotary piston engines according to the invention are extreme simple design. All main parts, i.e. the rotary piston, the inner chamber, the outer shell and the valves, are bodies of revolution whose manufacture takes place without special machines. In addition, their number is limited to a minimum.

The engine according to the invention is always balanced, since the stressed sides of the rotary piston always occur simultaneously be charged.

In addition, the effect of the motor according to the invention very supple. Immediately after ignition, it already generates a drive torque and its power is exclusively from depending on the thermodynamic gas laws.

With the description of the motor circuit it has become shown that there are two combustion stages per revolution in contrast to the classic four-stroke engine with one combustion stage every two crankshaft revolutions. Hence the performance four times as large with the same stroke volume. The power of the motor according to the invention can, however, be multiplied by a multiple increase, because the rotary piston, in contrast to the embodiment illustrated by Figures 1-7, instead of two arms, one may have a larger number of arms. Since the compression and

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Relaxation strokes are directly proportional to the rotary piston diameter, a diameter enlargement enables a corresponding increase Increasing the number of arms with comfortable compression and relaxation strokes. A rotary piston engine according to the invention with four arms has sixteen combustion stages each two revolutions. In general, the number of combustion stages corresponds to the square of the number of rotary piston arms relationship

η = (n)
cb

with η = number of combustion stages per two revolutions n, = number of arms of the rotary piston

Now it is the turn of the number of valves in the motor according to the invention. In the previous description of a Exemplary embodiment, it has been shown that an inventive Rotary piston engine with two piston arms 2x4 = 8 valves (or 4 valves + 4 openings), whereby the term valve is to be understood in the broader sense of the word. This number of valves is by no means prohibitive, as there are also 4 combustion stages per 2 revolutions. A conventional one Four-stroke engine needs 4 cylinders with 2 valves per cylinder for 4 combustion stages each 2 revolutions, i.e. all with 8 Valves.

How does the number of valves change depending on the

Piston arm number. For a rotary lobe with 3 arms, there are 9

2 combustion stages each two revolutions, since η = (η,); this requires 2 χ 6 = 12 valves (or 6 external valves + 6 internal openings). A rotary piston with 4 arms has 16 combustion stages two turns each; this requires 2 χ 8 = valves (or 8 valves + 8 openings). With a rotary piston

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with 5 arms there are 2 5 combustion processes each two revolutions ; j

j this requires 20 valves. This shows that the total j

number of valves the number of combustion stages per two revolutions j corresponds if the number of piston arms is four, but is smaller than the number of combustion stages for larger numbers of piston arms. This leads to the general relationship between valve number and piston arm number.

With η = number of valves
s

η = number of combustion stages per 2 revolutions

n, = number of piston arms
b

is η = 4 η,
sb

or, since nc = (n,),

η = 4Wn
s Vc

If you compare this with the classic four-stroke engine, you can see that the number of valves in such an engine is twice as large as the number of cylinders, ie twice as large as the number of combustion stages per two revolutions. So, for n ¹ = number of valves in a classic four-stroke engine, one has:

ⁿ 's = ^{2 n} c
If you compare the two engines with each other, you can see

that η must be at least 4 (η, = 2 is the minimum number), c b

So η <η '
s ⁵ ^ s

where η = η ¹ for η = 4 (η, = 2). The difference n '-η sscb ss

increases with increasing number of piston arms. It is also closed notice that for n,> 4 (n "> 16)

b c

η <η
s ⁵ ^ c

If the piston arm number is greater than 4, the valve number is

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less than the number of combustion stages per two revolutions. These are the laws for the number of valves in the rotary piston engines according to the invention.

It should also be noted that the double, triple or multiple version of the rotary piston is another Enlargement of the rotary piston engine power with simultaneous improvement of the constancy of the generated drive torque. This last property also offers the advantage of a lower flywheel mass. On the figure 13 is a Double rotary piston 30 shown schematically in a perspective view, the openings 9 'and 10' of the one Piston half are shifted by 90 ° with respect to the openings 9 and 10 of the other piston half. This is of course also the case for the arms 31 and 32, which are displaced by 90 ° with respect to the arms 11 and 12.

Of course, the scope of the invention is not exceeded in rural areas if a part of the rotary piston engine according to the invention replaced by an equivalent part wi ^ d. So lets For example, the separation mechanism with swing flap valves can also be designed differently and the flap valve can through the most diverse equivalent devices are replaced. This also applies to the inlet and outlet valves, whose task can be taken over by simple inlet and outlet openings.

The rotary piston engine according to the invention can be used in convert a rotary lobe compressor, with some parts remaining

let are.

The necessary changes to the images

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Ii 2, 4-7 are the following: Removal of valves 18 and 19 \ Replacement in place of valves 16 and 17 by continuously open inlet openings 43 and 44 (Fig. 14-1 * 0) for the gas to be compressed Valves 15 and 15 '; Retention of the valves 14 and 14 'or their replacement by a sleeve 40 attached to the piston, rotating with the piston and having openings 41 and 42. The immovable inner chamber 2 is also provided with two openings 41' and 42 '. The compressed gas is discharged axially through a channel on the side of the ball bearing 5 (Fig.l). This channel is not shown in any of the accompanying drawings.

The compressor thus obtained has the following cycle. It is assumed that the compressor is at normal output is working. In the position explained by Figure 14, the piston 3 is at the beginning of its cycle; the flap valves 20 and 21 are open and the space between the outer shell 1 and the inner hollow body 2 is filled with gas, the pressure of which corresponds approximately to the external pressure, if the supply pressure of the compressor is the external pressure.

In the position explained by Figure 15, the piston is already 30 ° away from its initial position; the Compression process and gas inlet begin.

In the position explained in Figure 16, the gas inlet stage is almost complete.

At the end of the compression stage, the openings 41 and 41 'and the openings 42 and 42' are connected to one another and is the compressed gas into the inner chamber 2 '

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pressed in, in the position shown in Figure 15 According to Figure 17, a new cycle begins.

The circuit of the compressor according to the invention thus corresponds to half a revolution of the rotary piston 3. In the figure 18 explained by the figure 16 corresponding to figure 16 Position, the piston 3 has practically rotated 360 °. There are four suction processes during one rotation of the piston and four compression operations took place.

The relationship between the number of compression stages per revolution of the piston and the number of piston arms can be broken down into the same way as the relationship between the combustion stage number and the piston arm number of the above-described invention Derive rotary piston engine. This relationship is as follows:

n _c = (n _b ) ²

where η = number of compression stages per revolution of the rotary piston (In the case of the rotary piston engine, this symbol means the number of combustion stages per two revolutions of the rotary piston)

n, = number of arms of the rotary piston ο

In the case of a compressor whose rotary piston is provided with 4 arms, there are 16 suction stages and 16 compression stages per rotation of the rotary piston.

In addition, since only the internal valves 14 and 14 ' (Fig. 1-7) or the equivalent openings 41 and 42 are available the following relationship applies:

ⁿ s ^{= n} b
where η = number of internal valves or internal openings

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These are the two laws governing the number of internal valves or inner openings of the rotary piston according to the invention compressor.

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Claims (16)

EXPECTATIONS 1, - Rotary piston engine ¹ , characterized in that it consists of a cylindrical outer shell (1) and a cylindrical inner body (2) concentric with this outer shell, between which a coaxial, likewise cylindrical rotary piston (3) rotates, as well as an inner chamber (2 ¹ ) for the combustion gas or the gasification mixture under pressure for the supply of the engine. 2. Rotary piston engine according to claim 1, characterized in that the aforementioned inner body (2) is a hollow body which forms the aforementioned inner ^{chamber (2 1} ) for the combustion gas or the gasification mixture under pressure. 3. Rotary piston engine according to claim 1, characterized in that the aforementioned inner chamber (2 ') for the Combustion gas or gasification mixture is a cell space. 4. Rotary piston engine according to claim 1, characterized in that the ^{pressure prevailing in the aforementioned inner chamber (2 1} ) is generated by transferring the gas mixture compressed by the rotary piston (3) into the same and that during the engine cycle, which is similar to that of a four-stroke engine is, the inner ^{chamber (2 1} ) returns the gas before the start of the combustion stage. 5. Rotary piston engine according to claim 1, characterized in that the outer wall of the aforementioned cylindrical Rotary piston (3) has at least two longitudinal openings (9, 10) connected to one another by longitudinal wall parts (11, 12), one side (11 ', 12') directed towards an opening of this Wall parts have an effective, i.e. gas-pressurized side of the rotary piston (3) and that one end of the 7621102 10/28/76 called rotary piston (3) is extended by a motor shaft. 6. "Rotary piston engine according to claim 5, characterized in that; the rotary piston (3) consists of at least two coaxial rings arranged one behind the other, which are connected to one another by means of at least two diametrically opposed longitudinal arms (11, 12), one side of which (II ¹ , 12 ') is one of the operative sides of the piston, and that one of the end rings is extended through the motor shaft. 7. Rotary piston engine according to claims 1 and 5, characterized in that the aforementioned outer shell (11) as Acts as a carrier for the separation mechanisms of the circulatory stages, these mechanisms, the number of which is that of the piston openings corresponds to protrude into these openings (9,10) and can withdraw from them to enable the rotation of the piston (3) . 8. Rotary piston engine according to claims 1 and 5, characterized in that the number of inlet valves (14, 14 ') and the number of outlet valves (15, 15') of the aforementioned inner ^{chamber (2?} ) For the combustion gas or gasification mixture under pressure corresponds to the number of piston arms (11,12), and that the number of inlet openings (16,17) of the outer shell for the combustion gas or gasification mixture, as well as the number of outlet openings (18,19) of the same for the exhaust gases also correspond to the number corresponds to the arms of the rotary piston, these openings being closed at the appropriate time by means of valves or distribution sleeves. 9. Rotary piston compressor j characterized in that it consists of a cylindrical outer shell (1) and one with the 7621102 10/28/76 the same concentric cylindrical inner body (2), between which a coaxial, likewise cylindrical rotary piston (3) rotert, and from a ^{pressure medium chamber (2 1} ) for feeding a pressure vessel or a pressure line consists.
j 10. Rotary piston compressor according to claim 9, characterized in that the aforementioned inner body (2) is a hollow body which forms the inner chamber (2 ¹ ) for the compressed medium. 11. Rotary piston compressor according to claim 9, characterized in that the aforementioned inner chamber (2 ¹ ) is a cell space for the compressed medium. 12. Rotary piston compressor according to claim 9, characterized in that in the aforementioned inner chamber (2 ·) the prevailing pressure is generated by transferring the medium compressed by the rotary piston (3) into the same. 13.- Rotary piston engine according to claim 9, characterized in that the outer wall of the aforementioned cylindrical rotary piston (3) has at least two longitudinal openings (9, 10) connected to one another by longitudinal wall parts (11, 12), one side (II ¹ , 12 ') of these wall parts forms an effective, ie pressurized, side of the rotary piston (3), and one end of the aforementioned rotary piston (3) is extended by the motor shaft. 14. Rotary piston compressor according to claim 13, characterized in that the rotary piston (3) consists of at least two coaxial rings arranged one behind the other are formed by at least two diametrically opposed longitudinal arms (11,12) are connected, and that this is one of the 7621102 10/28/76 End ring is extended by the motor shaft. 15. Rotary piston compressor according to claims 9 and 13, characterized in that the aforementioned outer shell (1) as a carrier for the separation mechanisms of the circulatory stages acts, these mechanisms, the number of which corresponds to that of the piston openings, in the openings (9,10) of the piston can protrude and withdraw from the same to allow rotation of the piston. 16.- Rotary piston compressor according to claims 9 and 13, characterized in that the number of inlet openings (41, 42) of the aforementioned inner chamber (2 ¹ ), and the number of inlet openings (43, 44) of the outer shell (1) the number of Arms (11,12) of the rotary piston (3) corresponds. 7621102 10/28/76