SE189425C1

SE189425C1 -

Info

Publication number: SE189425C1
Authority: SE
Publication date: 1963-01-01

Description

Uppfinnare: F P SoBinger Prioritet begard fra'n den 16 september 1960 (USA) Forbranningsmotorer med fram- och Atergaende kolvar kunna utforas for hOgre effekt, ova eylinderantalet okas. Pit samma salt kunna forbriinningsmotorer av kolvrotortyp Minna hogre effekt, genom att antalet rotoroch husenheter okas. Detta kan exempelvis ske genom att ett flertal enheters axlar kopplas i serie med varandra. En pa detta satt delad axel utsattes emellertid for storre pa.- kanningar an en i ett stycke -Ward axel. Inventor: F P SoBinger Priority requested from 16 September 1960 (USA) Internal combustion engines with reciprocating pistons can be designed for higher power, while the number of cylinders is increased. Pit the same salt can combustion engines of piston rotor type Reduce higher power, by increasing the number of rotor and housing units. This can be done, for example, by connecting the axes of several units in series with each other. However, a split shaft placed on it was subjected to larger jugs than a one-piece shaft.

Det är kant, att maskiner med flera roterande kolvar och en aid i ett stycke: karma utforas utan mellanlager. Denna utforandeform liar emellertid visat sig otillfredsstallande, emedan de hOga gaskrafter, som uppsta i sadana maskiner, fOrorsaka en bojning av axeln, vilken bojning icke blott forkortar axelns livslangd, utan ocksa fororsakar myeket stora pafrestningar pa axellagren. Det ar ocksa kant, att enheternas i ett stycke utforda axel kart ges en storre diameter. Aven denna atgard minskar axelns hojning, komma likval andlagren att utsattas for stora pa, frestningar. It is an edge that machines with several rotating pistons and an aid in one piece: karma is performed without intermediate layers. However, this embodiment has proved unsatisfactory, because the high gas forces which arise in such machines cause a bending of the shaft, which bending not only shortens the life of the shaft, but also causes very large stresses on the shaft bearings. It is also possible that the units' one-piece challenge shaft maps are given a larger diameter. This action also reduces the height of the shoulder, even if the bearings are exposed to great strain, temptations.

Likasa är hunt, att mellanlagret for den i ett :stycke utfOrda axeln kan artordnas delat. Bortsett fran att narvaron av en delningsfog i lagerytan tvingar till hog tillverkningsprecision, är det vid denna konstruktion nOdvandigt, att mellanvaggen mellan enheterna bestar av ett flertal delar, for att det delade lagret skall kunrta byggas in i mellanvaggen. Om mellanyaggen yore tillverkad i ett styeke, maste det hal, som erfordrades for del delade lagret, utforas med sit stor diameter, att berbringsytan mellan rotorgavlarna och de narbelagna sidorna av husets mellanvagg vasentligt forminskades. Da maskiner av detta slag i allmanhet maste anordnas men en oljetatningsring i varje rotorgavel, vilken tatningsring Jigger an mot den intilliggande husgaveln och ,forhindrar, att smorjolja kom, mer Over till arbelskammaren, mdste denn-a tatningsring, till foljd av ovannamnda hals stora diameter, likaledes utfOras med en jamforelsevis stor diameter, varigenom oljetatningsringen skittle atsattas for stora, av centrifugalkraften fororsakade pakanningar. Likewise, it is hunt, that the intermediate bearing for the one-piece shaft can be sorted divided. Apart from the fact that the presence of a dividing joint in the bearing surface forces high manufacturing precision, it is necessary in this construction that the intermediate wall between the units consists of several parts, in order for the divided bearing to be able to be built into the intermediate wall. If the intermediate yoke yore is made in a styeke, the hall required for part of the divided bearing must be made with its large diameter, so that the bearing surface between the rotor ends and the adjacent sides of the intermediate wall of the housing is substantially reduced. Since machines of this kind generally have to be provided but an oil sealing ring in each rotor end, which sealing ring jigs against the adjacent end of the housing and, prevents lubricating oil from coming, more Over to the working chamber, this second sealing ring, due to the above diameter , likewise, is made with a comparatively large diameter, whereby the oil sealing ring skittle is deposited for large, pans caused by the centrifugal force.

En mellanvagg ulford i flera delar fordrar dessutom extra kylkanaler for varje del, saval som bultar for sammanfogning av delarna. Detta medfar en relativt stor hygglangd och ett stort antal delar. An intermediate wall ulford in several parts also requires extra cooling ducts for each part, as well as bolts for joining the parts. This entails a relatively large felling length and a large number of parts.

Genom foreliggande uppfirtning undvikas de ovan namnda naekdelarna hos khnda konstruktioner. The present invention avoids the above-mentioned nude parts of similar constructions.

Forbranningsmotorn enligt uppfinningen bestar av minst tva maskinenheter, vilka vardera besta av ett has, sammansatt ar tva parallella gavlar och en mellan dem anordnad mantel och en med ett flertal utsprang forsedd rotor, som med sina utsprang glidande anligger mot mantelns insida och Or roterbart lagrad i huset pa en excentrisk del av en axel, som Or utfard i ett stycke och är gemensam for hada enheterna och anordnad med tva inbordes 1800 farskjuta a excenterskivor, en fOr varje enhet, varvid i huset for vardera enheten anordnats inlopps- och utloppskanaler. Den kannetecknas darav, att de hada enheternas inloppsoppningar och utloppsoppningar ligga mitt for varandra i axiell led och att den i ett stycke utforda axeln Indian excenterskivorna stades av ett hogst halvcylindriskt mellanlager, vars stadjande verkan ãr riktad mot de hada enheternas i lika riktning verkande farbranningstryck. The internal combustion engine according to the invention consists of at least two machine units, each consisting of a shaft, composed of two parallel ends and a jacket arranged between them and a rotor provided with several projections, which with their projections slidably abut against the inside of the jacket and rotatably mounted in the housing on an eccentric part of a shaft, which Or is extended in one piece and is common to the two units and arranged with two inboard 1800 boat gears of eccentric plates, one for each unit, the inlet and outlet ducts being arranged in the housing for each unit. It can be characterized by the fact that the inlet openings and outlet openings of the had units lie opposite each other in the axial direction and that the one-piece challenge shaft of the Indian eccentric plates was supported by a highly semi-cylindrical intermediate bearing,

Om detta forslag enligt uppfinningen tilllampas, kan en axel, utford i ett stycke och med en jamfarelsevis liten diameter, an:vandas, utan att axeln utsattes far storre bojning an den, som erhalles rid anvandning av ett delat lager enligt ovan. Uppfinningen har dessutom den fiirdelen, att det halveylindris- 2- - ka lagret kan anvandas vid en mellanvagg utford i ett stycke, varigenom maskinens totala bygglangd forminskas, och dess montering, fOrenklas. Det halvcylindriska lagret kan utan svarighet monteras in i mellanvaggen °eh fOrutsatter ett hal 1 derma, som endast har obetydligt stiirre diameter an diametem hos axelns excentriska del. Harigenom uppnas storsta mojliga ytkontakt mellan rotorerna och de angransande mellanvaggssidorna. If this proposal according to the invention is applied, a shaft, challenged in one piece and with a comparatively small diameter, can be used, without the shaft being subjected to a greater bending than that obtained by using a split bearing as above. The invention also has the advantage that the semi-cylindrical bearing can be used in a one-piece intermediate wall challenge, whereby the total construction length of the machine is reduced, and its assembly is simplified. The semi-cylindrical bearing can be mounted in the intermediate wall without responsibility, provided that it has a halo which has only a slightly larger diameter than the diameter of the eccentric part of the shaft. This achieves the largest possible surface contact between the rotors and the adjacent middle wall sides.

Jainford med en 1 ett stycke utford axel med forstarkt mellandel motstar konstruktionen enligt uppfinningen gastrycken bathe, varigenom axelns andlager icke komma att utsattas for alltfor stern pakanningar. Jainford with a one-piece challenge shaft with a reinforced intermediate part resists the construction according to the invention gas presses bathe, whereby the spirit bearings of the shaft will not be exposed to overly stern pans.

Pa hifogade ritning are utforandeexempel enligt uppfinningen framstallda i prineip. Ritningen visar: Fig. 1 ett langssnitt genera en motor med tva roterande kolvar langs linje 1-1 pa fig. 2; fig. 2 ett tvarsnitt tangs linje 2-2 pa fig. 1; fig. 3 ett tvarsnitt tangs linje 3-3 pa fig. 1; fig. 4 ett snitt tangs linje 4-4 pa fig. 3; fig. 5 en sidovy av ett mellanlager; fig. 6, en frontalvy av ett mellanlager, och fig. 7 en schematisk vy av ett monterat mellanlager. In the accompanying drawing, exemplary embodiments according to the invention are shown in principle. The drawing shows: Fig. 1 a longitudinal section of an engine with two rotating pistons along line 1-1 in Fig. 2; Fig. 2 is a cross-sectional view of line 2-2 of Fig. 1; Fig. 3 is a cross-sectional view taken along line 3-3 of Fig. 1; Fig. 4 is a sectional view taken along line 4-4 of Fig. 3; Fig. 5 is a side view of an intermediate layer; Fig. 6, a frontal view of an intermediate bearing, and Fig. 7 a schematic view of an assembled intermediate bearing.

En forbranningsmotor av kolvrotortyp be-star, som framgar av fig. 1, av tva lika upphyggda motorenheter A och. B, och mom varje enhet ar en i stort sett trekantig rotor 10, 10' anbragt excentriskt i ett hus, allmant betecknat med 12 resp. 12'. An internal combustion engine of the piston rotor type consists, as shown in Fig. 1, of two equally disassembled engine units A and. B, and mom each unit is a generally triangular rotor 10, 10 'arranged eccentrically in a housing, generally denoted by 12 resp. 12 '.

Huset 12, 12' bestar av en mantel 18, 18', vars inneryta har ett tvarsnitt, som i huvudsak motsvarar formen hos en tvabagig epitrokoid. Mantlarnas 18, 18' innerkonturer ligga mitt for varandra i axiell led. Vardera huset 12, 12' ar dessutom anordnat med gayar 22, 22' och 24, 24', varvid gavlarna 24, 24' are utforda som en mellanvagg i ett styeke. The housing 12, 12 'consists of a sheath 18, 18', the inner surface of which has a cross-section which substantially corresponds to the shape of a bivalve epitrocoid. The inner contours of the jackets 18, 18 'lie opposite each other in the axial direction. In addition, each housing 12, 12 'is arranged with gays 22, 22' and 24, 24 ', the ends 24, 24' being challenged as a partition in a styeke.

Gavlarna 22, 22.' och 24, 24' bara en gemensam axel 26, vars rotationscentrum sammanfaller med husets 12, 12' centrumlinje 16. Axeln 26 ar medelst lager 28, 28' roterbart lagrad i gavlarna 22, 22'. Den ar farsedd rued tva excenterskivor 30, 30', pa vilka rotorerna 10, 10' are roterbart ,anordnade medelst lagerhylsor 32, 32'. Excenterskivornas 30, 30' eentrumlinjer 14, 14' aro grskjutna ett avstand e fran centrumlinjen 16. Lagerhylsorna 32, 32' aro fast forbundna med rotorerna 10, 10' °eh aro forsedda med var sin kuggkrans 34, 31' med invandiga kuggar, som are I ingrepp med kugghjul 36, 36' med utvandiga kuggar, vilka kugghjul Aro fast monterade pa gavlarna 22, 22'. Gavlarna 22, 22. ' and 24, 24 'only a common shaft 26, the center of rotation of which coincides with the center line 16 of the housing 12, 12'. The shaft 26 is rotatably mounted in the ends 22, 22 'by means of bearings 28, 28'. It is provided with two eccentric discs 30, 30 ', on which the rotors 10, 10' are rotatable, arranged by means of bearing sleeves 32, 32 '. The center lines 14, 14 'of the eccentric discs 30, 30' are slid a distance away from the center line 16. The bearing sleeves 32, 32 'are fixedly connected to the rotors 10, 10' ° and are each provided with a toothed ring 34, 31 'with internal teeth, which are engaged with gears 36, 36 'with external teeth, which gears are fixedly mounted on the ends 22, 22'.

I enlighet med vad. som bast framgar av fig. 2, ar vardera rotorn 10, 10' fiirsedd med utsprang 38, 38', som barn radiellt rorliga tatningslister 40, 40'. Dessa tatningslister 40, 40' glida standigt Mugs de omgivande mant lamas 18, 18' innerytor 20, 20'. I rotorernas 10, 10' gavlar are mot gastrycken tatande gaveltatningar 76, 76' anurdnade. Nar rotorerun 10, 10' rotor a relativt resp. hus 12, 12', bildas mellan rotorernas axelparallella ytor 44, 44' och innerytorna 20, 20' pa (let omgivande husets innermantlar 18, 18' tre arbetsrum 42, 42' med fOranderlig volym. Rotorernas 10, 10' rotationsriktning liar angivits pa fig. 2 medelst en pil. Ett tandstift 46, 46' dr anordnat i vardera husets mantel 18, 18'. I enlighet med vad som bast framgar av fig. 1-4, are gavlarna 24, 24? fOrsedda med var sin inloppsoppning 48, 48', medan en utloppskanal 50, 50' ar anordnad i vardera manteln 18, 18'. Nar rotorerna 10, 10' rotera. sages en frisk bransle-luft-blandning genom inloppsoppningarna 48, 48' in i arbetskamrarna 42, 42'. Denna bransle-luft-blandning komprimeras sedan, antandes, expanderar och biases slutligen at genom utloppskanalerna 50, 50'. De narbelagna gavlarna 24, 24' ha var sin inloppsOppning 48, 48', som erhailer sin. tillforsel av friskgaser fran en gemensam inloppskanal 47. In accordance with what. As can be seen from Fig. 2, each rotor 10, 10 'is provided with projections 38, 38', which are radially movable sealing strips 40, 40 '. These sealing strips 40, 40 'constantly slide Mugs the surrounding mantle lamas 18, 18' inner surfaces 20, 20 '. In the gables of the rotors 10, 10 ', gable seals 76, 76' acting against the gas pressures are arranged. When the rotor 10, 10 'rotor a relatively resp. housing 12, 12 ', is formed between the axially parallel surfaces 44, 44' of the rotors and the inner surfaces 20, 20 'on the inner working shells 18, 18' of three working spaces 42, 42 'with variable volume. The direction of rotation of the rotors 10, 10' is indicated on Fig. 2 by means of an arrow A toothed pin 46, 46 'is arranged in the casing 18, 18' of each housing. 48 ', while an outlet channel 50, 50' is arranged in each jacket 18, 18 '. When the rotors 10, 10' rotate, a fresh fuel-air mixture is passed through the inlet openings 48, 48 'into the working chambers 42, 42'. This fuel-air mixture is then compressed, ignited, expanded and biased through the outlet ducts 50, 50 '. inlet duct 47.

Alla arhetseykelns pa varandra foljande faser, insugning, kompression, expansion och utblasning, aga rum i vardera arbetskammaren 42, 42', medan rotorn 10, 10' wider sig ett vary. All successive phases of suction cycle, intake, compression, expansion and exhaust, take place in each working chamber 42, 42 ', while the rotor 10, 10' widens.

Rotorns 10, 10' gavlar 44, 44' ar o anordnade med urtag 52, 52', som tillata en fri Overstromning av gaser fran mantelns 18, 18' ena trokoidbage till den andra, nar rotorn 10, 10' befinner sig i ovre dodpunkten. Urtagen 52, 52' are dessutom avpassade att go onskat kompressionsfarhallande. The ends 44, 44 'of the rotor 10, 10' are arranged with recesses 52, 52 ', which allow a free overflow of gases from one trocoid bag of the jacket 18, 18' to the other, when the rotor 10, 10 'is in the upper dead center. . The recesses 52, 52 'are also adapted to provide the desired compression retention.

Erik- utvaxlingsfarhallandet mellan kuggkransarna 34, 34' och kugghjulen 36, 36' ar 3:2, fullbordar rotor. 10, 10' ett vary omkring sin centrumlinje 14, 14', under samma tid som axeln 26 hinner rotor a Ire vary omkring sin centrumlinje 16. The Erik gear ratio between the gears 34, 34 'and the gears 36, 36' is 3: 2, completes the rotor. 10, 10 'a vary about its center line 14, 14', at the same time as the shaft 26 rotates a Ire vary about its center line 16.

Excenterskivorna 30, 30' och darigenom ocksa rotorerna 10, 10' are farskjatna 180° relativt varandra. Daremot are innerytornas 20, 20' konturer, inloppsoppningarna 48, 48', utloppskanalerna 50, 50' och tandmedlen eller tandstiften 46, 46' anordnade sã, att de ligga mitt for varandra i axiell led. Delta arrangemang medfor, trots att rotorerna 10, 10' och darigenom oeksa de av dessa bildade arbetskamrarna Oro forskjutna 180° relativt varandra, att enheternas A, B arbets- eller expansionsfaser alltid ske i arbetskammare med lika lage relatiyt huset 12, 12'. Hogsta gastryeket pa rotorn 10, 10' verkar alltsa i samma riktning yid vardera enheten, vid atforandeexemplet I riktning, uppat. Gastrycket verkar naturligtvis i samma riktning pa axeln 26. The eccentric discs 30, 30 'and thereby also the rotors 10, 10' are freshly spaced 180 ° relative to each other. On the other hand, the contours of the inner surfaces 20, 20 ', the inlet openings 48, 48', the outlet channels 50, 50 'and the tooth means or toothpicks 46, 46' are arranged so that they lie opposite one another in the axial direction. Delta arrangements mean, despite the fact that the rotors 10, 10 'and thereby the working chambers Oro formed by them are 180 ° offset relative to each other, that the working or expansion phases of the units A, B always take place in working chambers with equally low relative housing 12, 12'. The highest gas pressure on the rotor 10, 10 'thus acts in the same direction y each unit, in the behavioral example In the direction, upwards. The gas pressure naturally acts in the same direction on the shaft 26.

Som stod for axeln 26 mot detta gastryck al, forutom. andlagren 28, 28', ett mellanlager 50 anordnat, som ar belaget mellan exeenter- - 18941S -3 skivorna 30, 30'. Mellanlagret 56 har I huvudsak en halvcirkelformad profit., och dess lageryta 58 Jigger an mat axeln 26 pa den mot tandstiften 46, 46' motsatta sidan. Which stood for the shaft 26 against this gas pressure al, except. the spirit bearings 28, 28 ', an intermediate bearing 50 arranged, which is coated between the exeenter discs 30, 30'. The intermediate bearing 56 has a substantially semicircular profit, and its bearing surface 58 jigs abuts the shaft 26 on the side opposite to the toothed pins 46, 46 '.

Mellanlagret 56 Sr anordnat i mellanvaggen, som bildas .av de hada gavlarna 24, 24' och en. ringformad flans 60, som sammanbinder dessa gavlar. Flansen 60 Sr forsedd med en borrning, som bildar en lageryta 62 for lagrets 56 ytteryta 64. Denna borrning liar samma kriikningsradie som lagrets 56 ytteryta 64. Lagret 56 Sr anordnat med en styrlist 66, som griper i 1 ett motsvarande spar 68 i flansen 60. Av fig. 3 och 7 framgar, att oeksa styrlisten 66 liar samma krokningsradie som lagrets ytteryta 64, men ,att medelpunkten 59 for den eirkelbage, som bildar styrlistens 66 profit, Sr forskjuten i forhallande till lagrets mittpunkt 61 pa sadant satt, att styrlisten 66 fOrsvinner mot halvlagrets andar. Sparet 68 liar en siorre krakningsradie Sn styrlisten 66. The intermediate layer 56 Sr arranged in the intermediate wall, which is formed by the had ends 24, 24 'and a. annular flange 60, which connects these ends. The flange 60 is provided with a bore which forms a bearing surface 62 for the outer surface 64 of the bearing 56. This bore has the same radius of curvature as the outer surface 64 of the bearing 56. The bearing 56 is arranged with a guide strip 66 which engages in a corresponding groove 68 in the flange 60. From Figs. 3 and 7 it can be seen that the guide strip 66 has the same radius of curvature as the outer surface 64 of the bearing, but that the center point 59 of the circular bag which forms the profit of the guide strip 66 is offset from the bearing center 61 in such a way that the guide strip 66 Disappears against the spirits of the half-layer. The spar 68 liar a siorre cracking radius Sn guide strip 66.

Sam visats ph fig. 5, Sr styrlistens radiella hojd praktiskt taget lika med noll vid halvlagrets 56 andar, medan dess storsta radiella: hojd ligger i lagrets mittlinje 67. Genom denna konstruktion kan halvlagret 56 monteras in i mellanvaggens flans 60, utan att en jamfOrelsevis stor oppning maste anordnas i gaylarna 24, 24' resp. flansen 60. Halvlagrets 56 montage sker genom att axeln 26 jamte en av excenterskivorna 30, 30' forst stickas in genom mellanvaggen 24, 24' och sedan sh langt som mojligt fora& nedat i borrningen 62. Halvlagret 56 kan sedan skjutas iii axiellt ovanfOr axeln 26, tills styrlisten 66 och dess spar 68 aro mitt fOr varandra. Lagret 56 be-hover sedan f5ras blott en obetydlig straeka i radiell led utat. As shown in Fig. 5, the radial height of the guide strip is practically equal to zero at the spirals of the half bearing 56, while its greatest radial height is in the center line 67 of the bearing. large opening must be arranged in gaylarna 24, 24 'resp. the flange 60. The half-bearing 56 is mounted by first inserting the shaft 26 and one of the eccentric plates 30, 30 'through the intermediate wall 24, 24' and then as far as possible into the bore 62. The half-bearing 56 can then be slid axially above the shaft 26. , until the guide strip 66 and its groove 68 are opposite each other. The bearing 56 then only needs an insignificant straight radial outward line.

Da styrlisten 66 och ytterytan 64 ha samma radie, bestammes borrningens 62 diameter endast av excenterskivornas 30, 30' diameter. Harigenom uppnas storsta mojliga beroringsyta mellan rotorernas 10, 10' gavelytor och gavlarna 24, 24', och i rotorerna anordnade oljetatningar 75, 75' kunna darfor utfOras med en liten diameter, med motsvarande minskning av de pa dem verkande centrifugalkrafterna. Since the guide strip 66 and the outer surface 64 have the same radius, the diameter of the bore 62 is determined only by the diameter of the eccentric plates 30, 30 '. This achieves the largest possible contact surface between the end surfaces of the rotors 10, 10 'and the ends 24, 24', and oil seals 75, 75 'arranged in the rotors can therefore be made with a small diameter, with a corresponding reduction in the centrifugal forces acting on them.

Sedan mellanlag:ret 56 blivit insatt, skjutas rotorerna 10, 10' med sina lager 32, 32' over excenterskivorna 30, 30', och mantlarna 18, 18' liksom sidogavlarna 22, 22' fastas. Slutligen skjutas andlagerna 28, 28' in och skruvas fast till sidogavlarna 22, 22'. After the intermediate layer 56 has been inserted, the rotors 10, 10 'are pushed with their bearings 32, 32' over the eccentric plates 30, 30 ', and the sheaths 18, 18' as well as the side ends 22, 22 'are fixed. Finally, the spirit bearings 28, 28 'are pushed in and screwed to the side ends 22, 22'.

Kilsparsforbindelsen 66, 68 forhindrar saval axiell rOrelse som en vridning kring axeln av lagret 56. Lagret 56 fixeras medelst en skruv 70, som stickes in genom ett borrhal 72 i mellartvaggen 24, 24' och skruvas in i lagrets 56 gangade hal 74. Ocksh denna skruvforbindelse Eirhindrar, att lagret 56 vrides. The wedge pair connection 66, 68 prevents both axial movement and a rotation about the axis of the bearing 56. The bearing 56 is fixed by means of a screw 70, which is inserted through a drill hole 72 in the intermediate wall 24, 24 'and screwed into the threaded hole 74 of the bearing 56. screw connection Prevents the bearing 56 from turning.

Aven om lagret 56 liar betecknats sum halvcylindriskt eller halvlager, Sr det i utforan deexemplet enligt den ovan beskrivna uppfinningen ett cirkelsegment med en centrumvinkel nagot mindre an 180°. Uttrycken halvlager eller halvcylindriskt lager skola arbor tydas i enlighet harmed. Although the bearing 56 is denoted by a semi-cylindrical or semi-bearing bearing, in the embodiment of the invention described above a circle segment with a center angle slightly less than 180 °. The terms half-layer or semi-cylindrical layer shall arbor be interpreted accordingly.

Claims

Patent application:

A piston rotor type internal combustion engine, consisting of at least two machine units (A, B), each of which consists of a housing (12, 12 '), composed of two parallel ends (22, 22', 24, 24 ') and a jacket (18, 18 ') arranged between them and a rotor (10, 10') provided with a plurality of projections, which with their projections slidably abut against the inside of the jacket and are rotatably mounted in the housing (12, 12 ') on an eccentric part (30, 30 '), of a shaft (26), which is challenged 1 piece and Sr common to the liana units (A, B) and arranged with two inclined 180 ° offset eccentric discs (30, 30'), one for habit unit (A, B), the inlet and outlet channels (48, 48 ', 50, 50') being arranged in the housing (12, 12 ') for each unit, characterized in that the inlet openings of the two units (A, B) (48, 48 ') and outlet openings (50, 50') lie opposite each other in the axial direction and that the one-piece deflecting shaft (26) of the Indian eccentric plates (30, 30 ') are supported by a highly semi-cylindrical intermediate bearing (56), vars stodjancle ve rkan Sr directed at the combustion pressure of the two units (A, B) in the same direction.

2. An internal combustion engine according to claim 1, characterized in that the end caps (24, 24 ') of the two units (A, B) are connected to an intermediate wall in a styeke challenge, which is provided with a born-fling (62), in which the semi-cylindrical intermediate bearing (56) is mounted and fixed against displacement.

Combustion engine according to claim 2, characterized in that the intermediate bearing (56) on its outer surface (64) is fitted with a strip (66) which engages in a corresponding groove (68) in the intermediate wall (24, 24 ').

4. Internal combustion engine according to claim 3, characterized in that the strip (66) has the shape of a semicircle, the radius of which corresponds to the radius of the bore (62) of the intermediate wall (24, 24 ').

Internal combustion engine according to claim 4, characterized in that the strip (66) has the same radius of curvature as the outer surface (64) of the intermediate layer (56), the center point (59) having the circular bag, which forms the profile of the strip (66). led relative to the center (61) of the outer surface (64).

6. Internal combustion engine according to claim 5, characterized in that the strip (66) extends from one Linde of the bearing (56) and extends along its outer surface (64) to its other and the strip (66) has sin storsta ra- tentanspraken 1-7, kanneteeknad darav, aft diella hOjci pa. the middle of the outer surface of the layer. the intermediate layer (56) in the horn (62) is

7. Internal combustion engine according to any of the equipment against rotation. exam claims 1-6, kanneteeknad thereof, that the radius of. the outer surface of the diaphragm (56) is the following publications: same as the radius of the bore (62, 24 ') of the diaphragm (24, 24') and only slightly larger than