DE8517587U1 - Stator-rotor group for a rotary piston-like machine with compression and expansion chambers - Google Patents

Description

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Federal Patent Law DIPLOMPHYSICIST DR. RER. NAT. RICHARD BlERL sooo Munich 2

PATENT ANWALTSBORO · SONNENWEG 2. 7218 TROSSINGEN 1 Vt-RTRETER

at the European Patent Office D-8000 Munich

"Stator-Rotor Group GM" Gebhard Hauser, 72o8 Spaichingen Hol a / DrBiAp / 06/11/85

Description on page 7

GEBIIARD HOUSES
Balgheimerstr. 4th

72o8 Spaichingen

Stator-rotor group

for a rotary piston-like machine with compression and expansion chambers

The invention relates to a stator-rotor group for a machine with compression and expansion chambers, whose Gas contents are limited by at least two pairs of pistons rotating around an axis, with suction and exhaust ducts in a circumferential allocation within a cylindrical ring duct between two housing shells for the supply of fresh gas and removal of exhaust gas, as well as for the conduction of cooling liquid, furthermore inlet and outlet openings, those of the Kölberipäären themselves closed during circulation or be opened.

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The field of application of the invention extends according to the preamble of claim I. is reproduced, on such machines in which air volumes are compressed alternately by piston assemblies, then ejected and then again the trapped volume of gas in the same chamber through opposite one Movement of one or the associated piston (s) expands, or gas volumes are sucked into the chambers from the outside will. Such machine groups are required for piston compressor stations, for example. These are always Piston compressors suffer from the disadvantage of sealing problems when it comes to screw compressors on the other hand have the disadvantage of higher manufacturing costs, but the advantage of lower power consumption. That is why practice is now turning more towards piston compressors.

Another important field of application of the subject of the invention is piston internal combustion engines, which still have disadvantages in the known designs despite a high level of development, either because of the parts to be moved back and forth in the conventional reciprocating engine or because of the difficult manufacture and sealing problems in the so-called rotary piston engine or because of fuel consumption at the gas turbine. In DE-OS 23 57 585 a rotary motor is described, which is part of this No longer has disadvantages, but still either because of the valves or because of the sealing problems or the considerable consumption does not meet the expectations of a largely flawless internal combustion engine. The rotary engine known from this publication is based on a rotor with cylinder heads, therein ent = holding spark plugs and fuel ^ injectors

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and equipped with valves that can be controlled via camshafts. Between the cylinder heads and the stator are in the latter Combustion chambers formed; Furthermore, a compressor designed as a turbo compressor is included in the course of the intake duct, which compresses the sucked in air.

Both the essential design elements and the essential design features agree exactly match the two applications, piston compressors and internal combustion engines. The difference is there

only in the fact that in the piston compressor there is a gas ! preferably air, using the inlet port

an external work or by an engine unit is sucked in, compressed and discharged via the outlet opening, while in the piston internal combustion engine air or a gas mixture is also sucked in, compressed and then ejected by igniting the gas mixture with power output. Constructive sub-problems, such as concerning sealing elements, often cause in übereinstimmerder manner considerable effort or involve mangling \, also needed with the associated control elements in many types of construction valves.

As already mentioned, the internal combustion engine needs

ϊ 25 according to the known construction still assemblies, at ^ which is consumed by reciprocating parts and their mass acceleration forces energy, and further more energy loss for the control of valves, and finally ensured compared to the known prior art because of the unfavorable assignment from the working chambers and combustion chambers to the rotor and stator there is no sufficiently residue-free combustion of the fuel mixture. The present invention lies

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^c therefore the task is based on the previously known piston

«To improve system constructions and also those of the

- cited piston compressors and the piston internal combustion engines still required mass acceleration energies 5 and other energy losses to use for control purposes! avoid or at least noticeably reduce it, so that

'which is an elaborate mass balancing, as is the case with Koiben-

and rotary piston engines is necessary - the same applies to compressors - and therefore smoother running. 1o can be enough. Linked to this goal is that too f additional task that the stator-rotor according to the invention

Group for piston compressors or piston internal combustion engines to be relatively easy to manufacture and a low

; should have res power-to-weight ratio.

The task described above is carried out by a

]; tor-rotor group for a rotating piston-type machine with ji compression and Exp of Si ons chambers with the Teilmerkmai 2o ^len of the preamble of 1.Anspruchs by their Kombinai tion with the partial features of the characterizing part of the

I. claim resolved.

¹ In internal combustion engines according to this teaching is

25 a technical advance in addition to the elimination of the above-mentioned deficiencies in engines of the prior art achieved in that its moving parts move in circular paths or on those that are superimposed on a circular path, thus power losses and mass accelerations avoided

& that there are additional modules for the control

λ rest and both the space requirement and the power-to-weight ratio can be significantly reduced, so that a relatively simple manufacturability and a

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More favorable adaptability to the assemblies or machines to be driven by the internal combustion engine is achieved, The requirements for the prescribed technical progress are met by ring segment pistons be brought into circulation within a cylindrical ring channel, this orbital movement being a forward and backward partial movement is superimposed, and the pistons on piston carriers that can move relative to one another are arranged, which can be designed like a full disk or an annular disk. In the application In piston internal combustion engines, the stator-rotor group according to the invention provides the further advantage that in the case of quarter-stroke engines, all four strokes are accommodated four times on a single revolution can be.

Developments of the invention are the subject matter of the subclaims. The following are exemplary embodiments described in detail using the drawing. They represent:

Fig.1a) A first embodiment

with piston carrier, which vollschei- \

are ben-like, with \

a stator or housing, the ί

composed of two half-shells |

^lb sets is in the axial section |

1b) a section I belonging to this

in the joint surface of the two |

Half-shells of the housing in case 1

a piston compressor I

Fig.1c) do. in the case of a piston 1

Internal combustion engine I

Fig.2) a diagram of the mutual |

Movements of rotary pistons or |

Ring piston carriers and crank |

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Gebhard Hauser, 72o8 Spaichingen

Hoi a / DrBi / bp / 11.o6.85 ". ,. ". "

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block disks during a partial revolution

Fig.3a) a second embodiment with piston carriers as piston ring disks are designed with shoulder ball bearings, but otherwise the Ausführungsbeispiei Fig.1a) and 1b) correspond, in axial section, upper part

Fig.3b) do., In axial section, lower part;

Fig.4a) to Fig.3a) and 3b), like Fig.1b), a

Associated cross-section A-B-C-D through the space between crank block disks with a view of the epicyclic gear;

Fig.4b) in partial section (A-B-C in Fig.4a) the Pair of crank block disks;

Fig.4c) spatially assigned to Fig.4b) in Plan view of the coupling group;

4d) also spatially assigned in a side view of the connecting rod element the coupling group;

Fig.4e) also spatially assigned in side view on the bearing pin and the planetary gear the clutch group;

Fig. 5) a detailed representation, partly in section, with emphasis on the coupling group for the shoulder bearing of the piston ring disc

a) in the partial plan view of the piston ring a representation of the mutual Position of the annular piston, bulge for the connecting rod element, mass balancing element and bearing

place the eccentric shaft;

b) in partial section CA-E in Fig. 5a) through, an annular piston;

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11oi a / DrBi / bp / 11.o6.85 Description - page

c) in partial axial section (G-H in Fig. 5a) through a piston ring disk in front of an end face of the annular piston;

d) in partial axial section (J-K in

Fig. 5c) through a ring piston:

Fig. 6) a detailed representation of the connecting rod Ιο Elements in

a) a detail from the axial section through the stator-rotor group;

in partial axial section of the annular disk-shaped piston carrier with shoulder bearings and connecting rod eccentric group;

b) the coupling group of one type j of the eccentric connecting rod pair with

Planetary gear from the point of view perpendicular to the axis,

from the view of the masses

equals elements,

j and with a view of the eccentric disk,
30th

j c) in plan view together with the

j career;

j d) in plan view with dashed lines

3 5 drawn planet gear

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and in section, AB with planet gear also shown in dashed lines.
4o

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Gebhard Hauser, 72o8 Spaichingen Description - page

11o1 β / DrBi / bp / 06/11/85 ^e

In Fig, 1a, the Stätor ^ rotor group is in cross section shown as it is installed in a front 1 and a rear housing shell 2, the by the screw connections 3 and 4 with close tolerance, S, as described in more detail below, joined together are. The housing shells enclose a one concentric around the axis 5 with a gas-tight fit Annular channel 6, channels 7, 8 for conducting cooling liquid and an exhaust gas 9, as well as an intake duct not visible in this cross section. In the back Housing shell 2 is concentric with the stub shaft 1o by means of the one-piece disk 11 in a hub 12 fastened by screw connections 13, 14.

On the inner edge parts 15 and 16 of the housing shells 1, 2, the full disk-like Kolbenträ ^ ger 17, 18 out, which by means of fitting grooves 19 on their Butt surface 2o of the opposite outer ring surfaces connected to one another in a seal-fitting manner and by means of a step groove arrangement 21, 22 in the inner edge parts 15, 16 of the housing shells 1 and 2 are slidably mounted with a tight La ^ fsitz. On the stub shaft 1o is the actual shaft 23, which is connected to a crank block

\. Disk 24 integrally integrally connected and with

25 of the other crank block disk 25, which is mirror-inverted but offset by 180 °, is void spacers shown is rigidly connected by means of

: of the stub shaft extension 26 and the latter (25) on the

posterior socket 27, in both cases with ; 3o by means of needle roller bearings.

Each of the two crank block disks 24 and 25

P possesses, mirror images of each other,

;; an edge attachment 28 or 29, in the eye 3o, 31

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the bearing pin 32, 33 of a rotating on the core gear 34 planetary gear 35 and 36, which is with a Eccentric connecting rod coupling group (eccentric disk 37, 38, connecting rod element 39, 4o and counter pin 41, 42) combined with an epicyclic gear and with the latter in an eye 43, 44 each radially opposite Edge attachment 29, 28 are stored. The actual shaft 22 is near its free end 45 by the with the help of the cover plate 46 secured ball bearings 46a counter-supported.

It can readily be seen that the pair of crank block disks 24, 25 with the pair of piston carriers 18, 19 in terms of rotation through the mentioned epicyclic gear is coupled by in the course of the process of the planet gears 42, 43 on the core gear 34 the Pair of crank block disks 24, 25 upon rotation of the eccentric disks 37 because of the caused thereby Displacement on the circumference are rotated with irregular speed, so that the Kolbenträ- | ger are rotated faster in one half of a revolution range and slower in the other than the Crank block disks 24, 25.

This transformation of the rotational movement from a uniform to a non-uniform movement takes place in the same way when the actual shaft 23 is driven, the piston disks 17, 18 and thus the integrally connected with them,

ring segment piston, not shown, in the concen- '.

Irish cylindrical annular channel are advanced on the pendulum kreisför- [-shaped orbit 6; these

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oscillating rotation is used in the case of a non-uniform drive of the ring segment piston, such as. in piston internal combustion engines, as a result of the cyclically changing speed of the connecting rod elements also transferred to the actual shaft 23 in a pendulous manner, that their rotation is uniform. On the other hand, the ring cylinder-piston pairs become uniform Rotation, then as a result of the pendulum motion of the eccentric connecting rod coupling group a pendulum rotation of the actual shaft; this movement ratio is also reversible, similar as in the case described above.

In Fig.1b, a radial cross-section A-B-C-D In Fig.1a of the stator-rotor group is again the cut outer edge of the front housing shell 1 can be seen, at the lateral end of which the flange connection 47 of the intake duct (s) 48 on the one hand and the flange connection 49 of the exhaust gas duct (s) 5o is attached. In the cylindrical Ring channel 6 are the pair of ring segment pistons 51 and 52 of a piston carrier 18, which is itself in this Representation is not visible, and the other pair of ring segment piston 53, 54 together with his Piston carrier 55, shown in section, guided in a tight running seat. In this representation you can also see the spacers 56, 57 with which the crank block disks 24, 25 (the latter not visible) with one another are rigidly connected.

The epicyclic gear is complete in the cavity 58 between the two crank block disks 24, 25

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"Stator-Rotor-Gnqjpe Oi" Gebhard Hauser, 72o8 Spaichingen 8 11o1 a / DrBi / bp / 06/11/85

Description - page 17

fitted, so that the core gear 34, the planetary gears 35, 36, the eccentric disks 37, 38 and connecting rod elements 39, 4o, their pivot pins 59, 60 and the counter pins 61, 62 for the eccentric disks 37, 38 can be seen; because the connecting rod elements 39, 4o to their counterparts 61, 62 as a result of the rotation the eccentric disks 37, 38 are pivoted back and forth, the recess 63 and a corresponding, in the opposite, not visible, crank block disk. Fig.1b gives the constructive Training of the stator-rotor group for use in piston compressors again.

Fig.1c shows the form in which the practically identical design of the stator-rotor group for the application in piston internal combustion engines differs from that in Fig.1b for piston compressors only differs by a combustion chamber 64 in the outer edge of the housing shell 1, in which a spark plug or a similar component is arranged which can cause the ignition of a gas mixture. In terms of the additional devices, such as voltage or power supply of such an ignition device, the control elements in connection with the rotating piston pairs ren or with external control, etc., reference can be made to the state of the art, which corresponds to the present case can be evaluated.

Otherwise, the embodiment of Fig.Ic differs from that of Fig.1b only still in that the piston carrier is disc-shaped so that the recesses 65, 66 for the Spacers 67, 68 between the washers of the piston

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Gebhard Häuser, 72o8 Spaichingen Description - page

11o1 a / DrBi / bp / 06/11/85

carrier (here is only the disc-shaped inner part

< 69 of the one piston carrier visible) and the visible recess 7o for the coupling group of eccentric disk 37 and connecting rod element 39 on the one hand, as well as planetary gear 35 and core gear 34 of the visible (ren piston carrier have a slightly different shape than

* in the case of the Ausführungsbeispieis of Fig. 1b, the

Another coupling group arranged opposite aur eccentric disc 38, connecting rod element 4o and planet wheel 36 is merely attached.

Of course, both designs of the piston carrier, Fig.Ib and Fig.1c with their Recesses for the spacers and the coupling groups, equivalent to each other and mutually interchangeable in terms of construction. Otherwise different the stator-rotor group does not differ from that in the case of application in internal combustion piston engines the application in piston compressors, except through a different angular position of the points of the smallest distance between the two pairs of pistons in relation to the circumference of the stator.

In Figure 2, the above-described movements of the individual parts of the coupling group, ie. the counter pin 41, 42 of the eccentric disks 37, 38 on the one hand and the pivot pin Jer connecting rod elements in Shown in the form of a diagram in which the pivot pin of a connecting rod element forcibly on the Orbit 77, but starting from the

Point 78, in the course of the first quarter of an orbit 79 by an angle of 90 ° + 24 °, that is, accelerated and

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extends to point 8o, while it is again due to the rotation of the relevant Eccentric disc, but in the opposite direction, during the second quarter of the revolution of the plan tenrads 35 on the orbit 79 shortened by the same angular section - so 9o ° - 24 ° - up to Point 81 is moved. If one thinks that at the same time one pair of pistons extended them Orbit between points 78 and 8o and the other pair of pistons the shortened angular sections between points 81 and 82, then one recognizes that this is an approximation of the two Ring segment piston in this case, and in the other case of reversing both paths a distance both piston pairs comes about from each other. The physical consequence of this is in one case the reduction in volume between the two pairs of pistons and, in the other case, an increase, in other words, in one case there is a compression of the gas volume and in the other there is one Expansion or a suction process takes place.

In Fig, 3a is a second embodiment - upper part of an axial section - shown

represents, as the piston carrier 1o1, 1o2, per se in the same way by stepped grooves 1o3, 1, o4 in the central joint surface 1o5 is tightly and airtightly connected and offset from one another with not shown Ring segment piston pairs equipped, are not disc-shaped, but ring-shaped, so that they leave at least an interior space of diameter Io6 free. As a result, in this interior space

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the group of crank block disks 24, 25 * core gear 34 and planet gears 35 _s 36, as well as those with the planet gears, for example. 35 to a coupling group integrally combined bearing journals 32, 33 and counter journals 41, 42, in this case more spaciously dimensioned eccentric disks 37, 38 and connecting rod elements 39, 4c more spaciously used.

The actual difference from the exemplary embodiment in FIG. 1 is in the exemplary embodiment 3a and 3b (lower part of the axial section) in that the storage of the annular piston carrier by Shoulder bearing 111, 112 is formed. Apart from the dimensioning details, the construction is correct, as already mentioned, corresponds to that of the exemplary embodiment FIG.

The more spacious structural design of the interior and the coupling group is particularly in Fig.4 can be seen, which shows a cross section A-A-B-B in Fig.3a through the space between crank block disks and epicyclic gears. Because of the offset of this cut, the planet gear is in one case 35 and the core gear 34 in front of the recess 63 of the crank block disk 114 (partially cut in Figure 4a) and the connecting rod element 115 recognizable, which latter on a projection 116 of the annular The piston carrier is mounted by means of the pivot pin 59. The spacers 56, 57 of the crank block washer 24 - also cut - are in this embodiment in the free interior of the crank block disk 24 relatively freely configurable.

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The pair of crank block disks 24, 25 is shown separately in Figure 4b along the section line A-B-C Drawn in Figure 4a so that the spatial relationship between the edge attachment 28, the eye 43 and the Spacers 57, (and 57a) is understandable. Here it can be seen in particular that for the connection A screw connection with threaded part 117 and shaft or head recess 118 is provided for the crank block disks is.

To illustrate the installation of the coupling group with planet gear 35, eccentric disk 37 and Connecting rod element 39, as well as bearing pin 32 and counter pin 41, this coupling group is spatially assigned in FIG. 4c compared to the crank block disks 24, 25 with a partial section through the crank block disks of Fig. 4b reproduced. For the same reason, the side view of the coupling group is shown in spatial assignment in Figure 4d, in which the connecting rod element

? .o 39 in front of a mass balancing disk 119 and the planet gear 35 is visible. 4e shows the side view of the counter pin in a similar manner. In Fig. 5a, a detailed plan view of the annular piston carrier (1o2 in FIG. 3a), are the recess 113 and the projection 116 with the bearing eye 12o for the not shown Pivot pin of the connecting rod element can be seen separately. In addition, this Fig. 5a can be seen that how the ring segment pistons 121 and 122 are arranged on the piston carrier 1o2.

Fig.5b shows a partial section A-E in Fig.5a by being integral with the piston ring disk 116a

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11 o1 a / DrBi / bp / 11.o6.85 uescnreiDung öeite / z

connected ring segment piston 121 including the projection 116, the stepped grooves 1o4 and the annular projection 123 for shoulder positioning 112.

Fig.Sc shows a partial axial section G-H through the piston ring disk 1o2 in front of an end face of the ring segment piston 121. FIG. 5d shows a partial axial section through the ring segment piston 121 Against this, a sealing ring 124 is also shown, which is held by the cover plate 125. to this Fig. 5d also includes the representation of this ring segment piston 121 together with the piston carrier 1o2 in partial top view.

6a shows, in connection with further details, a section from an axial section through the stator-rotor group with special emphasis on part of the rear housing shell 2, the annular piston carrier 1o2 with shoulder bearing 112 and projection 116 with connecting rod element 115, crank block disk 25, Planet gear 35 and (partially) core gear 34. Fig. 6b shows the coupling group with the planet gear 35, which is structurally combined with the bearing pin 32, the counter pin 41 and the eccentric disk 38, as well as the mass balancing disk 119, in a side view with a top view of the counter pin 41, the Exrent disk 38 and the mass balancing disk 119, as well as in the plan view of the planetary gear Finally, the connecting rod element 115 in connection with the orbit of the pivot pin 59 on the orbit 128 of the crank block disk 25 is shown in FIG. In individual representation, namely in plan view

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and in section A-B, the connecting rod element 39, respectively, is shown separately in FIG. 6d, in this case the extension 126 is formed with two arms 127, 128 for the projection to be removed therebetween (116 in FIG. 4a) is.

Claims (1)

DiPLOMPHYSICIST DR. RER. NAT. RICHARD BIERL '..'. PATENT ADVOCATE at the German Patent Office Federal Patent Law 8000 Munich 2 PATENT ANWALTSBDRO SONNENWEG 2 - 7218 TROSSINGEN 1 REPRESENTATIVE at the European Patent Office D'8000 Munich "Stator-rotor group GM" Gebhard Hauser, 72o8 Spaichingen 11o1 a / DrBi / bp / 11.o6.85 Claims page 1 Protection claims 1. Stator-rotor group for a machine with compression and expansion chambers, the gas contents of which by at least two circularly revolving around an axis Piston pairs are limited, with a cylindrical ring duct with suction and exhaust ducts in a circumferential allocation within a housing double wall for the supply of fresh gas and removal of exhaust gas, as well as for the conduction of cooling liquid, furthermore inlet and outlet openings, which are closed by the piston pairs themselves during circulation or opened, f "Stator-rotor group GM",: .- .. '· .. *' .. * * ,. · ,,. ' Gebhard houses, 72o8 Spaichingen - ... 11o1 a / DrBi / bp / 1i7o6.85 claims - page characterized in that the stator, and inner <i <half of the same the rotor rotatable relative to each other arranged and the rotor ausgestat- at least with a pair of ring segment piston (51, 54, 52, 53) 'is 5 tet, rotate the piston in a cylindrical annular duct (6) at the periphery of the stator and thereby ι between themselves, ie. mutually movable forehead * walls (with cover plates 125) opposite ring segment piston (51, 54 or 52, 53) and the rigid housing cylinder walls between working chambers, the ; as a result of alternating enlargement and reduction j belong to the power section and / or the shut-off section, form and the Riugsegmentkolben (51, 52) in a radially outer section of the cylindrical ring-15 channel (6) are guided in a tight fit (without noticeable play), wherein (a) the stator has two circular housing shells (1, I '2) with an outer wall delimiting the housing and an inner shell that covers the portion of the cylindrical annular channel (6) with a cross-section of predominantly closed circular shape and one in the outer wall of one of these two shells (1,2) as an axis for the piston carrier (17, 18) in the right angle to the abutment surface (2o, 1o5) in the The outer wall of a shell (2) contains a stub shaft (1o) that is fixed to the housing, (b) the rotor has two piston carriers (17, 18) on which 2n ring segment pistons (51, 52) are attached axially symmetrically form-fitting or in one piece in accordance with the number of cycles 2n so that that their outer edges together with the inner part of the housing shells (1 * 2) deft cylindrical • ii ..11Ii U , fi , · ■> · ι > ι ι II "Statör-Rotor-Gruppe GM ¹ * Gebhard houses, 72o8 Spaichingen claims - page ^ 11o1 a / DrBi / bp / 11.o6.85 «j ^ piucne beite 3 Ring channel (6) - by means of guide grooves between |; each other and against the inner part of the Housing shells (1, 2) sealing - form, cure \ belblock disks (24, 25) in the axial direction | S outside the piston carrier (17, 18) and one (■■ Contains coupling group, the ring segment i piston (51 to 54) the piston carrier (17, 18) j a partial circumference length of 36o °: (2n χ 1.5) and * a mean distance of 36o °: (2n χ 3) ha-, ■; ben and] (b. *) the coupling group on the stub shaft (1o) Fixed, positively mounted core gear (34) with a diameter of 2n χ d sines Epicyclic gear - in the middle between the Scha len (1, 2) of the housing symmetrically to the abutment surface (2o, 1o5) used on the same - contains, on which according to the »number η of ring segment pistons (51 to 54) per \ piston carrier (17, 18) η pairs of planetary 1 wheels (35, 36) with diameter d rotate, the shafts (bearing journals 32, 33) axially symmetrical | metric to the core gear (34) in eyes (3o, 31) of the crank block disks (24, 25); are stored, and | (b. ₂ ) the crank block disks (24, 25) cup-shaped f with edge attachments (28, 29) for the eyes ^?: (3o, 31) trained, as well as with each other and * with the actual shaft (23), axially symmetrical I metric to the epicyclic gear in a down | was equal to the thickness of a pair of KoI- | girders (17, 18), are rigidly connected j • · »» Il III · I · · III I · · »I Il I I · I I Il wed "Stiitör-Rotör-Gruppe GM" Gebllard houses, 72o8 Spaichingeii 1'foi ä I DrM / bp / 11.06.85 claims - page (c) and the epicyclic gearbox between the piston carriers (17, 18) and the relevant pair of those interacting with the ring segment pistons (51 to 54) Crank block disks (24, 25) at least one or η pair (s) from radially opposite to each other associated eccentric discs (37, 38) and connecting rod elements (39, 4o) running on their circumference are arranged, which are guided at their other end over one on the relevant crank block disk (24, 25) Pivot pin (59, 6o), the piston carrier (17, 18) with the cup-shaped crank block disks (24, 25) alternately coupling, mounted and the eccentric disks (37, 38) of one crank block disk (24, 25) from those of the other by one Angles of 36o °: 2n are offset from one another. i 2. stator-rotor group according to claim 1, » g characterized in that the stator is one of the rotor Contains open-facing combustion chamber (64) that burns the compressed gas mixture in the respective The compression chamber serving as a power unit triggers and the ignition controlled by the circulation cycle as a result, between the ring segment pistons (51 to 54), an expansion energy is non-positively released, which a displacement of the ring segment piston in question in the direction of rotation and thus a rotation of the piston carrier (17, 18) causes. 3. stator-rotor group according to one of claims 1 and 2, • * · · ItI "Stator-Rotor-Group GM" «:», ** '' α "» »' ΉΊϋ' Gebhard Hauser, 72o8 Spaichingen. ... Get a / DrBi / bp / 1i7o6.85 claims characterized in that the piston carriers (17, 18) as full piston discs with bearing on a stub shaft extension (26) or a stub shaft shoulder (27) are formed by means of needle bearings. 4. stator-rotor group according to one of claims 1 and 2, characterized in that the piston carriers (1o1, 1o2) as piston ring disks with guidance by ring projections (123) and shoulder bearings (111, 112) are formed. 5. stator-rotor group according to one of claims 1 and 2, characterized in that a pair of eccentric disks (37, 38 or 1o7, 1o8) with associated Connecting rod elements (39, 4o or 1o9, 11o) in diametrically opposite recesses (63, 7o) of the two Crank block disks (24, 25) is housed. 6. stator-rotor group according to one of claims 1 to 5, characterized in that each pair of crank block disks (24, 25) by means of diametrically opposed spacers (67, 68 and 56, 57) which Piston carrier (17, 18) penetrating through openings (65, 66) or in an interior space thereof with a diameter 1o6 housed, are rigidly connected to each other, the length of which on the circumference of the orbit (128) the axes of the bearing journals (32, 33) of eccentrics or "Stator-Itotor Group GM" ♦: .... * '.. ".." * .. * ... Gebhard houses, 72o8 Spaichingen 11o1 a / DrBi / bp / 11 06.85 claims - page 6 The pivot pin (59, 60) of the connecting rod elements (39, 4o) is greater than the relative clearance by the required clearance The crank block disks (24, 25) and the piston carrier (17, 18) move against each other. T. stator-rotor assembly according to one of claims 1, 5 and 6, characterized by an arrangement of the combustion chamber (s) (64), the flange connection (47, 49) for the suction (48) and the suction channel (5o) on the circumference of the bearing shells (1, 2) of the stator according to the position of the minimum of the distances between the annular pistons (51 to 54), the area the maximum increase and that of the maximum decrease the volume between the ring segment pistons along the circumference, -I- ^ = ^^ 5> ^^ a ^ = fe ^ iS ^^> ^ 5 ^^ JA ^