EP2171212B1 - Moteur à pistons rotatifs - Google Patents

Moteur à pistons rotatifs Download PDF

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Publication number
EP2171212B1
EP2171212B1 EP08785918A EP08785918A EP2171212B1 EP 2171212 B1 EP2171212 B1 EP 2171212B1 EP 08785918 A EP08785918 A EP 08785918A EP 08785918 A EP08785918 A EP 08785918A EP 2171212 B1 EP2171212 B1 EP 2171212B1
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EP
European Patent Office
Prior art keywords
compressor
piston
working
working piston
engine
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EP08785918A
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German (de)
English (en)
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EP2171212A1 (fr
Inventor
Franz Ackerl
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Individual
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
    • F01C1/00—Rotary-piston machines or engines
    • F01C1/08—Rotary-piston machines or engines of intermeshing engagement type, i.e. with engagement of co- operating members similar to that of toothed gearing
    • F01C1/12—Rotary-piston machines or engines of intermeshing engagement type, i.e. with engagement of co- operating members similar to that of toothed gearing of other than internal-axis type
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
    • F01C1/00—Rotary-piston machines or engines
    • F01C1/08—Rotary-piston machines or engines of intermeshing engagement type, i.e. with engagement of co- operating members similar to that of toothed gearing
    • F01C1/12—Rotary-piston machines or engines of intermeshing engagement type, i.e. with engagement of co- operating members similar to that of toothed gearing of other than internal-axis type
    • F01C1/123—Rotary-piston machines or engines of intermeshing engagement type, i.e. with engagement of co- operating members similar to that of toothed gearing of other than internal-axis type with tooth-like elements, extending generally radially from the rotor body cooperating with recesses in the other rotor, e.g. one tooth
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
    • F01C11/00—Combinations of two or more machines or engines, each being of rotary-piston or oscillating-piston type
    • F01C11/002—Combinations of two or more machines or engines, each being of rotary-piston or oscillating-piston type of similar working principle
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
    • F01C21/00—Component parts, details or accessories not provided for in groups F01C1/00 - F01C20/00
    • F01C21/10—Outer members for co-operation with rotary pistons; Casings
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
    • F01C21/00—Component parts, details or accessories not provided for in groups F01C1/00 - F01C20/00
    • F01C21/18—Arrangements for admission or discharge of the working fluid, e.g. constructional features of the inlet or outlet

Definitions

  • the invention relates to a rotary engine, comprising rotatably mounted in a motor housing, rotatable about two axes of rotation and a drive shaft driving motor shafts, each of the axes of rotation at least one compressor piston and at least one working piston are rotatably mounted, wherein by means of a translator unit an opposite direction of rotation of the compressor piston and working piston is forced at synchronous speed, wherein compressor piston paths of the arranged in a common compressor plane compressor pistons as well as working piston paths of a plane parallel to the compressor plane arranged working piston in a railway crossing region overlap, wherein the arranged in the compressor plane Verêtrkolbenbahnen of arranged in the working plane working piston paths are separated by motor housing walls, wherein the compressor and the working piston formed in a substantially circular arc s ind and having a concentric with the respective axis of rotation extending inside and a concentric to the respective axis of rotation extending outside, wherein the inner sides and the outer sides are each limited by concave piston crowns or interconnected
  • From the DE 195 27 277 A1 is about a rotary engine with two arranged in a motor housing motor shafts known, to each of which a compressor rotor and a working rotor are attached.
  • the compressor and work rotors each have a sickle-shaped piston segment and are mounted centrally, wherein the two compressor piston segments and the two working piston segments each lie in a common plane and intersecting each other Have piston paths.
  • the two compressor piston segments have an opposite direction of rotation and alternately compress fresh air, which is sucked from an existing in the motor housing intake, against the wall of the coplanar arranged, each opposite piston segment.
  • the compressed fresh air is finally forced through an overflow into a combustion chamber in which both a fuel enrichment and an ignition of the air / fuel mixture takes place.
  • the ignited air / fuel mixture expands in sequence from the combustion chamber into the plane of the work rotors and drives them. Since the compressor or work rotors roll against each other, only a respective linear seal results between them and thus a compression loss. At the time of ignition of the air / fuel mixture, a considerably large compression space formed in the compressor piston path and also referred to as a "closing angle" remains due to the rotor or motor housing geometry.
  • the closing angle volume of a rotary piston engine according to DE 195 27 277 A1 is about 20% of the intake volume, with an existing on the side of the work rotors opening angle volume must be the same size for design reasons.
  • the DE 32 42 431 A1 discloses a rotary piston hot gas engine with continuous combustion using the Joule process.
  • a compressor piston and a working piston are arranged one behind the other on two motor shafts, wherein in each case a compressor piston path overlaps with a working piston track.
  • the two pairs of piston webs arranged one behind the other have an unspecified geometry and are not separated from one another by motor housing walls, but only by carrier disks rotating on the motor shafts.
  • the gas exchange takes place by means of an elaborate, running outside of the engine block pressure line system, the piston paths are opened and closed by specially designed rotary valve and passing this rotary valve passing gas to a working piston train upstream combustion chamber and ignited there, before it, controlled by a further rotary valve , is released into the working piston line.
  • a heat exchanger is integrated. Also, such a construction makes a relatively large distance between the inlet and outlet openings of the compressor and working piston track to the web crossing areas of the compressor / working piston tracks required and prevents the achievement of economic efficiency.
  • the DE 32 32 046 A1 discloses a rotary engine with each paired compressor and piston.
  • two separate transfer channels are present, which connect a compressor plane with a working plane
  • the pistons are not circular arc-shaped, but as a segment-shaped stepped disc elements.
  • the WO 02/070878 A discloses a rotary engine with in two planes one behind the other arranged rotary piston.
  • the air compressed by a first pair of pistons is enriched with fuel in a combustion chamber located outside the piston paths and ignited.
  • the pistons are designed as mutually rolling, partially recessed disc elements, wherein either both pistons of a mutually engaging piston pair each have convexly curved end faces or one of the pistons has a convexly curved end face, while the other piston has a concavely curved end face.
  • the DE 36 27 962 A1 discloses a rotary piston internal combustion engine with intermeshing, circular arc-shaped rotary piston.
  • This machine comprises a first and a second housing half.
  • two shafts are mounted parallel to each other, on each of which three compressor pistons are arranged. So there are a total of six compressor piston provided, which work together in pairs.
  • two shafts are mounted in the second housing half, on each of which three working pistons are arranged in pairs.
  • four axes of rotation / motor shafts are provided, each of the shafts either exclusively with compressor pistons or exclusively with working piston is equipped.
  • the compressor and work levels are therefore not arranged one behind the other, but next to each other.
  • the present invention is therefore based on the object to avoid the disadvantages mentioned and to provide an improved in terms of design and motor properties rotary engine.
  • the closing angle volume present in the compressor piston path at the end of a compression stroke should be reduced as far as possible.
  • a generic rotary piston engine comprises mounted in a motor housing, rotatable about two axes of rotation and driving a drive shaft motor shafts, each of the axes of rotation at least one compressor piston and at least one working piston are rotatably mounted, said means of a translator unit an opposite direction of rotation of the compressor piston and piston at synchronous speed is forced, wherein the compressor piston webs arranged in a common compressor plane compressor pistons as well as working piston paths of the one in the compressor plane In each case, working pistons arranged in a plane crossing region overlap parallel working planes, wherein the compressor piston paths arranged in the compressor plane are separated from the working piston paths arranged in the working plane by motor housing walls.
  • the axes of rotation of the compressor and the working piston are each co-linear with the axes of symmetry of the associated compressor and working piston paths.
  • the compressor and working piston are formed substantially circular arc and have a concentric to the respective axis of rotation extending inside and a concentric to the respective axis of rotation extending outside, wherein the inner sides and the outer sides are each bounded by concave piston crowns or interconnected and wherein the compressor piston flights and the working piston tracks - the geometry of the compressor and piston working - are formed substantially Vietnamese nikringnutförmig, wherein the compressor or working piston inner sides each along a compressor or working piston inner wall and the compressor or working piston outer sides each along a compressor - or working piston outer wall outer are guided, wherein the compressor / working piston inner web walls in the web crossing region each have a concave curvature, which is characterized by an overlapping of the compressor / working piston track with the respective opposite compressor / piston associated compressor / working piston inner wall or by an imaginary volume intersection between
  • the concave curvatures result by engagement of the compressor / working piston in the respective opposite compressor / piston associated Compressor / working piston rail inner wall. To a certain extent, therefore, the course of the compressor or working piston outer walls (interrupted by the web crossing regions) is continued by the concave curvatures arranged on the compressor or working piston inner walls.
  • compressor or working piston path outer walls arranged in a common compressor or working plane merge into one another, the compressor or working piston path inner walls arranged in a common compressor or working plane can thus be designed to be closed in each case.
  • a sealing edge is provided on the piston bottoms in the area of the compressor / working piston outer sides, the curvature of the piston bottoms corresponding to the course of a rolling curve which the sealing edge of a compressor / working piston rotating about the rotation axis in the web crossing region of the cross section of in opposite Direction of rotation about the respective opposite axis of rotation rotating, lying in the common compressor / work plane compressor / working piston cuts out.
  • the lying in a common compressor / working plane compressor / power piston according to the invention are arranged in a position about their respective axis of rotation, in which the sealing edge of a compressor / working piston while passing the web crossing region continuously the piston crown of each opposite compressor / working piston scrapes.
  • “stripping" of the piston heads is understood in the present context merely conveying the compressed and expanded in the compressor and piston pistons or expanded air / fuel mixture and no direct contacting the piston crowns through the sealing edge.
  • the compressor pistons arranged in the compressor plane as well as the working pistons arranged in the working plane always slide past one another in the course of their rotational movement without rubbing against one another. In this way, a frictional wear between the compressor piston or between the working piston is avoided.
  • the overflow each outside the concave curvatures of the compressor / working piston inner walls , but open directly adjacent to end portions of the concave curvatures in the compressor / working piston paths.
  • the edges of the inlet and outlet ports of the transfer ports may each be spaced 2 to 5 mm from the end portions of the concave cambers.
  • each accurately formed trained Kolbenbahnwandache are provided on which both the piston inner sides and the piston outer sides of the compressor or piston are performed, compression losses can be safely avoided.
  • unused opening angle can be approximately eliminated or reduced to a desired minimum on the part of the piston pistons.
  • compression ratio can be achieved over conventional internal combustion engines, a significant increase in engine performance and a reduction in fuel consumption and exhaust emissions.
  • a plurality of compressor or working piston can be rotatably mounted about the axes of rotation.
  • one compressor or working piston per compressor or working piston track is provided, it is also conceivable to use a plurality of, preferably two, compressor pistons or working pistons in each case in the compressor or working piston paths to arrange a corresponding offset distance and thus to achieve a higher number of work cycles per motor shaft revolution.
  • a clearance of a maximum of 2/10 mm, preferably a clearance, measured during the rotational movement of the compressor / working piston between the sealing edge of the one compressor / working piston and the piston head of the respectively opposite compressor / working piston ⁇ 1/10 mm is provided.
  • the sealing edge or the entire piston crown is formed as a separate, attachable to the compressor / working piston component.
  • Such a design allows a more targeted production of the compressor or working piston, since particularly stressed sections of the compressor / working piston can be made of specifically selected materials and optionally also replaced.
  • this is the sealing edge or the component forming the piston crown made of aluminum titanate.
  • Aluminum titanate is characterized by its good insulating properties or due to its low thermal expansion and is therefore particularly suitable to ensure compliance with an exact piston fit in the present application.
  • the compressor / piston according to the invention is made in a preferred embodiment in lightweight construction.
  • the compressor / power piston on cavities, which are bounded by piston walls and preferably radially to the axis of rotation extending webs.
  • the designed by the lightweight construction piston walls have an elasticity, which allows in the case of thermal expansion of the compressor / working piston targeted guidance of the piston curvature along the edge region of carrier discs described in more detail below.
  • the compressor or working piston outer sides are henceforth not only guided along the associated compressor or working piston outer walls, but also in the hitherto critical, for a compression or Expansion of the air / fuel mixture relevant to railroad crossing areas. Since the compressor or working piston so always a sealing guide surface is offered, compression losses can be avoided. On the Buffalo of the circumference of the compressor or piston arranged, wear-prone sealing rings including complicated backstops according to the prior art can therefore be dispensed with.
  • the compressor / power piston In order to attach the compressor / power piston in a solid manner to the motor shafts, it is provided in a further preferred embodiment of the rotary piston engine according to the invention, that the compressor / working piston are mounted on support disks, which are fastened to the motor shafts.
  • Rotary piston engine insulating rings provided, which are arranged between the carrier disk and the compressor / working piston.
  • the insulating rings made of a material with low thermal conductivity, such as aluminum titanate.
  • balancing weights are attached to the carrier discs.
  • a second embodiment of the rotary piston engine that along each axis of rotation two mutually aligned motor shafts are arranged and one of the two aligned motor shafts carrying the at least one compressor piston, while the other of these motor shafts carries the at least one working piston.
  • the two motor shafts by means of a reversing gear engaged with each other, so that an opposite direction of rotation of the two motor shafts or an opposite direction of rotation of the arranged on a rotation axis compressor and piston is forced, the reversing gear drives a arranged between the compressor plane and the working plane drive shaft.
  • an overflow channel leads from the arranged around the axis of rotation compressor piston inner wall to the arranged about the same axis of rotation working piston inner wall.
  • the motor housing wall slots together with the mold elements or the transfer channels introduced therein are curved in a preferred embodiment, wherein the transfer channels each outside the concave curvatures of the compressor / working piston inner walls, but preferably immediately adjacent to end portions of the concave curvatures in the compressor / Working piston tracks open.
  • the overflow can be performed in this way without unwanted overlapping of the piston paths from the compressor to the working level.
  • the inlet ports of the transfer ports are adjacent to a lower rail crossing region of the compressor piston paths, while output ports of the transfer ports are adjacent to an upper rail crossing region of the working piston tracks - or vice versa.
  • Such an oblique course of the overflow channels favors optimal turbulence of the air / fuel mixture.
  • the overflow channels each open outside the concave curvatures of the compressor / working piston inner walls, but preferably immediately adjacent to end portions of the concave curvatures in the compressor / piston working.
  • both the inlet ports and the outlet ports of the transfer ports are adjacent to either an upper rail crossing region or a lower rail crossing region of the compressor or working piston, a particularly simple, because straight transition of the compressed air / fuel mixture from the compressor level in the working plane or a shortening of the overflow and a concomitant increase in the flow volume can be made possible.
  • the motor shaft and drive shaft arrangement according to the second embodiment of the rotary piston engine according to the invention further brings with it the advantage of a more uniform load distribution.
  • the motor housing can be dimensioned smaller due to the arranged between the motor shafts reversing gear, whereby a common lubrication of bearing elements and gears of the reversing gear can be done and therefore only a single oil chamber is provided.
  • the elastic sealing element overlaps the circumference of the distance insert, the elastic sealing element is pressed from the housing cover to the distance insert as well as to side surfaces of the motor housing. Without the providence of the distance insert according to the invention an exact fit between the compressor / working piston and serving as a piston-line boundary inner surface of the housing cover could be made difficult, since the necessary for pressure maintenance in the compressor and working piston sealing elements when put on the bolt elements Nuts would give way in an incalculable way. A possible too close approach of the inner surface of the housing cover to the guided in the compressor / piston pistons compressor / piston could namely lead to a rubbing of the compressor / piston on the housing cover. On the side of the working level or on the side of a second housing cover, the distance insert also performs the function of thermal insulation between the working piston paths and the uncooled second housing cover.
  • each compressor piston path is associated with a fuel injection nozzle to the sucked air before entering the compressor piston trains or directly in the compressor piston paths, preferably in the region of opening into the compressor piston webs Intake opening to enrich with fuel.
  • each working piston path is assigned a spark plug, wherein the spark plugs are preferably arranged in the region of the outlet openings of the transfer channels or in Openings are held, which lead to the working piston paths.
  • the compressor piston inner walls in a special construction one or more recesses, which of a lying outside the web crossing region, the end portions of the concave curvature adjacent area of the compressor piston inner wall to the respective to the compressor piston inner wall adjacent concave curvature leads.
  • a "dead" closing angle volume trapped between the spill port mouth and the end portion of the concave camber is provided with a suitable expansion path in the web crossing region so that the piston motion is not decelerated and the compressed one in the "dead” closing angle volume Used air / fuel mixture during the next Ansaugzyklus or pushed by the subsequent compressor piston bottom in the Verêtrkolbenbahn and there can be compressed again.
  • the axial end portions of the ribs of the outside and the inside of the compressor / working piston bounding side surfaces are each spaced by a Distanzluster, so so measured along the axis of rotation axial extent of the ribs is smaller than the axial extent of the compressor / working piston. In this way it is prevented that form areas between the ribs and the walls delimiting the piston paths with stagnant cooling air or an unhindered flow of cooling air through all passage channels is ensured.
  • both the working piston and the compressor piston are cooled by means of inventive rib arrangements or passage channels.
  • at least one passage opening is provided in the motor housing, through which the cooling air from at least one of the compressor / working piston tracks in the respective axially underlying (s) compressor / working piston track (s) can be conveyed.
  • the passage opening is preferably disposed within the web crossing region of two juxtaposed compressor / working piston paths.
  • the piston trajectory limiting components which in the present embodiment to piston-carrier discs or Insulating rings facing sealing areas of the motor housing to provide a series of notches.
  • These indentations which are preferably arranged in the form of a plurality of mutually offset rows along the sealing regions, swirl a possible laminar flow of the air-fuel mixture emerging from the piston webs.
  • a further optimization of the rotary piston engine according to the invention is achieved by providing at least one indentation (communicating with the compressor / working piston tracks) on at least one of the inner walls of the compressor piston tracks or the working piston tracks in a region immediately adjacent to the concave curvature or the web crossing region. In this way, in the course of the piston rotation resulting suction and compression effects, which counteract the rotational movement of the compressor / working piston can be reduced or eliminated.
  • Fig. 1 shows a first preferred embodiment of a rotary piston engine 1 according to the invention with two mounted in a motor housing 4 motor shafts 2 and 3, which are each rotatable about a rotational axis 14, 15 and drive a drive shaft 13 by means of a trained in the form of bevel gears gear unit 16.
  • FIG.2 An exploded view of a motor shaft / drive shaft assembly, wherein a slidable on the drive shaft 13 hollow shaft piece 35 can be seen, which is provided in its axial end portions with two pointing in diverging directions bevel gears 36, 37.
  • the hollow shaft piece 35 has a plurality of radial bores 40 into which corresponding screw elements 41 can be inserted in order to fasten the hollow shaft piece 35 together with bevel gears 36, 37 to a fixing region 13a of the drive shaft 13. In this way, an undesired rotation of the bevel gears 36, 37 against a provided running direction 42 of the drive shaft 13 is prevented.
  • the motor shafts 2, 3 each have a in the mounting position of the drive shaft 13 assigning, multi-edged motor shaft end portion 49 on which bevel gears 38, 39 can be placed.
  • the bevel gears 38, 39 are provided with shafts 38 ', 39', each having an axial geometry corresponding to the geometry of the polygonal motor shaft end portion 49 for receiving the Motor shaft end portion 49 have.
  • the hollow shaft piece 35 and the shanks 38 ', 39' of the bevel gears 38, 39 are provided with radial bores 50, in which screw 51 engage for fixing the bevel gears 38, 39 on the motor shaft end portions 49. It is understood that both the fixing region 13a of the drive shaft 13 and the end regions 49 of the motor shafts 2, 3 are provided with receptacles (not shown) into which the screw elements 41, 51 can engage.
  • the drive shaft 13 on both sides of the bevel gears 36, 37 equipped with preferably designed as a ball or cylindrical roller bearings bearing elements 45, while the motor shafts 2, 3 with directly to the bevel gear shafts 38 ', 39 'adjacent bearing elements 46 are provided.
  • the bevel gears 36 and 38 and the bevel gears 37 and 39 are each arranged orthogonal to each other and engage in mounting position one another.
  • the compressor piston 7 and the working piston 8 have an identical geometry according to Figure 4
  • the compressor pistons and working pistons 7, 8 are substantially circular-arc-shaped or annular-segment-shaped and have an inner side 17 a, 18 a extending concentrically to the respective axis of rotation 14, 15 and an outer side 17 b, 18 b extending concentrically with the respective axis of rotation 14, 15 the outer sides 17b, 18b and the inner sides 17a, 18a are bounded or interconnected by concave piston bottoms 34.
  • sealing edges 63 are provided at the piston bottoms 34.
  • the compressor pistons and working pistons 7, 8 described in more detail below with regard to their offset position are manufactured in a preferred embodiment in lightweight construction and have webs 52 which connect those piston walls 54, 55 forming the inside 17a, 18a and the outside 17b, 18b , Between the webs 52 and between the piston walls 54, 55 cavities 53 are formed.
  • the compressor or working piston 7, 8 are provided in the region of the webs 52 with parallel to the axes of rotation 14, 15 projecting threaded bolt 23 which are screwed with nuts 24.
  • the threaded bolts 23 serve to fasten the compressor or working pistons 7, 8 to associated carrier disks 5, 6, which in turn are fastened to the motor shaft 2, 3 (see FIG Figure 6 ).
  • the motor shafts 2, 3 are for the purpose of a solid connection with the carrier discs 5, 6 with in Figure 5 apparent polygonal wave areas 56 and 57 provided.
  • the carrier disks 5, 6 have polygonal openings 100, 101 corresponding to these polygonal shaft areas 56, 57, which have an interference fit to the shaft areas 56, 57 (see also an exploded view of the rotary piston engine 1 according to FIG Figure 14 ).
  • the in the present conical gear 38, 39 opposite end portion of the motor shaft 2, 3 arranged first polygonal shaft portion 56 is formed in the present embodiment as a slotted shaft jaw 98, which is provided with an axial threaded hole 98a for receiving a clamping screw 99.
  • the clamping screw 99 has a threaded bore 98a of the slotted shaft jaw 98 corresponding to the conical threaded shaft 99a, as in Figure 5 seen.
  • An assembly referred to below as a rotor assembly 58 for fastening the compressor or working pistons 7, 8 to the motor shafts 2, 3 further comprises insulating rings 21 which are attached to the threaded bolts 23 before attachment of the carrier disks 5, 6 ( Figure 6 ).
  • the insulating rings 21 are intended to prevent heating of the uncooled carrier disks 5, 6 and associated unwanted expansions or pressing of the compressor / power pistons 7, 8 on adjacent housing walls.
  • the carrier disks 5, 6 with their outer diameter project beyond the inner sides 17a, 18a of the compressor / power pistons 7, 8 or the inner piston walls 54 in order to ensure a tear-resistant connection between the compressor / power pistons 7, 8 and the carrier disks 5, 6 to enable.
  • Such rotor assemblies 58 are (while blanking the motor housing 4) in the FIGS. 7 and 8th illustrated in an assembly position, wherein on the rotatable about the first axis of rotation 14 first shaft 2 a attached to a first compressor piston carrier disc 5a first compressor piston 7a and in the axial direction behind lying, attached to a first working piston carrier plate 6a first piston 8a are arranged , Parallel to this rotor or shaft arrangement, a second compressor piston 7b attached to a second compressor piston carrier disk 5b and a second compressor piston 6b mounted behind it in the axial direction are fastened to the second shaft 3 rotatable about the second axis of rotation 15b second piston 8b arranged.
  • Figure 9 shows the wave arrangement according to Figure 7 respectively.
  • Figure 8 in a built-in motor housing 4 state, which in this illustration is a horizontal section through the motor housing 4 according to Fig. 1 is.
  • the compressor piston carrier disks 5a, 5b together with the associated rotor arrangements 58 are placed on the motor shafts 2, 3, which are not yet equipped with the bevel wheels 38, 39.
  • the compressor piston carrier disks 5a, 5b each have a slotted rotor shaft 102 which can be pushed onto the polygonal shaft regions 57.
  • the in Figure 3 enclose visible polygonal wavy regions 57 are in Fig. 14 (top left) screwed union nuts 103 screwed onto the threaded portions 94 of the motor shafts 2, 3.
  • the union nuts 103 each have a conical opening and thereby press the individual segments of the slotted rotor shafts 102 to corresponding side surfaces of the polygonal shaft regions 57.
  • the compressor piston carrier disks 5a, 5b together with the associated rotor assemblies 58 are thus accurately fitting to the motor shafts 2, 3 fixed.
  • motor housing 4 has a motor block portion 4a and a peripheral housing portion 4b.
  • the engine block portion 4 a and the peripheral housing portion 4 b are each separated in Malleable cast produced and machined. Subsequently, the peripheral housing portion 4b is pushed over the engine block portion 4a and welded thereto. Side surfaces 107, 108 of the motor housing 4 are ground flat, so that finally a uniform motor housing 4, as in the Figures 10-12 shown, results.
  • the motor housing 4 accommodates a compressor plane 9 and a working plane 10 separated therefrom by motor housing walls 67.
  • compressor plane is understood to mean a system of compressor piston lanes 11a, 11b, while the term “working plane” refers to a system of working piston lanes 12a, 12b.
  • working plane refers to a system of working piston lanes 12a, 12b.
  • the compressor piston paths 11a, 11b provided for receiving the compressor pistons 7a, 7b and the working piston paths 12a, 12b provided for receiving the power pistons 8a, 8b are clearly visible.
  • the compressor piston webs 11a, 11b and the working piston tracks 12a, 12b are each arranged rotationally symmetrical about the axes of rotation 14, 15 and in the present exemplary embodiment have an identical annular-ring-shaped geometry.
  • a width of the compressor and working piston webs 11a, 11b 12a, 12b measured radially relative to the axes of rotation 14, 15 essentially also corresponds to one Radial to the axes of rotation 14, 15 measured cross-sectional width of the compressor and power piston 7a, 7b 8a, 8b, in particular a radially to the axes of rotation 14, 15 measured width of the piston heads 34a, 34b, 34c, 34d, 34a ', 34b', 34c ' , 34d '.
  • the compressor plane 9 is arranged parallel to the working plane 10 or the first compressor piston path 11a is arranged parallel to the first working piston path 12a and the second compressor piston path 11b parallel to the second working piston path 12b, wherein the compressor piston paths 11a and 11b as well as the working piston paths 12a and 12b in a railway crossing region 62, 62 'merge into each other.
  • the overlapping or communicating of the juxtaposed compressor piston paths 11a, 11b and the working piston paths 12a, 12b results in a figure-of-eight shape of the first and second compressor or compressor sections arranged in the compressor and working planes 9, 10.
  • Fig. 16 shows a frontal view of the compressor piston paths 11a and 11b, however, have the (behind it arranged) working piston paths 12a and 12b an analogous course as in Fig. 16 shown on the compressor piston webs 11a and 11b, on.
  • the compressor or working piston outer wall 19b, 19b ', 20b, 20b' merge into each other, while the compressor or working piston inner walls 19a, 19a ', 20a, 20a' are each closed (- this is in particular in the Figures 10 and 11 good to see).
  • the engine block portion 4a of the motor housing 4 is provided along the two axes of rotation 14, 15 with holes 95 through which the motor shafts 2, 3 are passed during assembly. Adjacent to the bores 95 are each two conical bearing seats 90, 91 are provided which an interference fit to in Figure 8 apparent, mounted on the motor shafts 2, 3 track bearings 59, 60 have.
  • the thrust bearings 59, 60 are designed in the present example as a tapered roller bearing and as such suitable to accommodate high radial and Achsschublasten.
  • an opening 111 is provided in each case, which leads to a longitudinal section through the motor housing 4 in accordance with Fig. 12 apparent central oil space 113 leads.
  • lubrication openings 110 are also provided in the housing walls 67, which likewise lead to the central oil chamber 113 and serve to lubricate the track bearings 59, 60 ( Fig. 11 ).
  • the central oil chamber 113 can be filled with oil via an oil filling opening 28 ( Fig. 12 ).
  • oil filling opening 28 is an in Fig. 1 shown oil chamber lock screw 29 including an oil level measuring rod 97 inserted.
  • an oil chamber closing plate 143 together with an oil drain plug 145 is arranged on the underside of the motor housing 4, as in a representation of a second embodiment of the motor housing described below fig.33 seen.
  • a splash lubrication with an oil level of the central oil chamber 113 must be performed up to the lubricating holes 110 and up to the openings 111.
  • a spray lubrication be provided, at the bottom of the central oil chamber 113 and the motor housing 4, one or more capsule pumps are arranged, which swirl oil in a defined radius (not shown).
  • cooling water inlet 106 is provided, which to a in the Figures 9 and 11 apparent, leading to the compressor piston paths 11a, 11b and to the working piston paths 12a, 12b adjacent cooling water jacket 112.
  • the motor housing 4 also has a corresponding cooling water outlet 106a arranged in a bottom area ( Fig. 16 ).
  • the shaped elements 32, 33 are chamfered at their mutually facing sides 32a, 33a, wherein the overflow channels 70, 71 are formed in each case by distances between these mutually facing sides 32a, 33a (see a schematic illustration according to FIG Figure 22 ).
  • the mutually facing sides 32a, 33a of the mold elements 32, 33rd be formed profiled or rugged to effect a particularly good mixing of a passing air / fuel mixture (not shown).
  • a first overflow channel 70 formed by a first pair of mold elements 32, 33 leads from the compressor piston inner wall 19a lying in the compressor plane 9 to the working piston inner wall 20a lying in the working plane 10, while a second pair of mold elements 32 through the second , 33 formed second overflow 71 from the lying in the compressor plane 9 compressor piston inner wall 19a 'to the lying in the working plane 10 working piston inner wall 20a' leads.
  • the overflow channels 70, 71 both curved and (viewed relative to the axes of rotation 14, 15) obliquely or diagonally through the provided in the housing walls 67 slots 68th , 69.
  • first transfer passage 70 thus extends obliquely through the first slot 68 and has an inlet mouth 70a in the compressor piston inner wall 19a and an output port 70b in the working piston inner wall 20a
  • second overflow 71 extends obliquely through the second slot 69 and an inlet mouth 71a in the compressor piston inner wall 19a 'and an output port 71b in the working piston inner wall 20a' has.
  • Fig. 10 in this case, such an outlet mouth 71b opening into the working plane 10 can be seen.
  • the overflow channels 70 and 71 thus run without detour in direct guidance from the compressor plane 9 into the working plane 10 or from the compressor piston paths 11a, 11b to the working piston paths 12a, 12b.
  • Fig. 10a a half-sectional view of the motor housing 4 with vertically through the web crossing regions 62, 62 extending cut can be seen.
  • the perspective according to Fig. 10a shows only the second overflow 71, wherein the course of the first transfer port 70 is to be imagined mirrored about the cutting plane (see also Fig. 10b ).
  • Fig. 10b shows an exploded view of a equipped with two pairs of mold elements 32, 33 motor housing 4 in a relation to the motor housing representation in Fig. 10 rear view, wherein only the understanding of the overflow channels 70, 71 essential portions of the engine block portion 4a are visible, while the peripheral housing portion 4b is hidden.
  • Fig. 10c shows an assembly of in Fig. 10b exploded components shown, wherein the constituted by the inserted form-element pairs 32, 33 overflow channels 70, 71 are shown by dashed lines.
  • overflow channels 70, 71 with their inlet mouths 70a, 71a and their outlet ports 70b, 71b each outside the concave bulges 64, 65 of the compressor / working piston inner walls 19a, 19a ', 20a, 20a', but preferably directly adjacent to end portions 64a, 64b, 65a, 65b of the concave bulges 64, 65 open into the compressor or working piston tracks 11a, 11b, 12a, 12b.
  • the curved course of the transfer passages 70, 71 is required so as not to cut the compressor tracks 11a, 11b, 12a, 12b in an area unsuitable for expansion of the air / fuel mixture.
  • the oblique guidance of the overflow channels 70, 71 caused by the bevelled form elements 32, 33 proves to be advantageous with regard to the flow profile of a compressed or expanded air / fuel mixture, since a direct guidance of the overflow channels 70, 71 in a straight line from the compressor piston webs 11a, 11b to the respectively behind arranged working piston paths 12a, 12b during ignition of the air / fuel mixture to strong axial shocks on the compressor and piston 7a, 7b, 8a, 8b and their bearings and a restless running of the motor shafts 2, 3 would lead , In such a straight design of the transfer channels 70, 71 would also have the compressor and piston 7a, 7b, 8a, 8b provided at those the mouths of the transfer ports 70, 71 facing sides with continuous walls, which, however, heat
  • the mold elements 32, 33 are provided with plate-shaped closure elements 115, 116 which serve to seal the areas of the thrust bearings 59, 60 which communicate with the central oil space 113.
  • the plate-shaped closure elements 115, 116 each have a shaft portion 115a, 116a and a central opening 117 for receiving the motor shafts 2, 3.
  • the closure elements 115, 116 are either made in one piece with the form elements 32, 33, but may also be designed as separate components. In the latter embodiment, the in the slots 68, 69 sunken mold elements 32, 33, for example, be attached from the side of the central oil chamber 113 with screws.
  • the engine block section 4a has for receiving the mold elements 32, 33 and for receiving the closure elements 115, 116 corresponding, in Fig. 11 apparent recesses 118.
  • the recesses 118 are provided with threaded bores 109 which are aligned in a aligned with the slots 68, 69 position of the mold elements 32, 33 with through holes in the closure elements 115, 116, so that the closure elements 115, 116 by means of Figure 9 apparent screw members 105 can be fixed in the recesses 118 of the engine block section 4a.
  • apparent seals 104 Before inserting the closure elements 115, 116 into the recesses 118 are in Fig. 16 apparent seals 104 inserted into the recesses 118, which protect the central oil chamber 113 against oil loss and the compressor or working piston tracks 11a, 11b, 12a, 12b against a compression loss.
  • the inlet ports 70a, 71a and the outlet ports 70b, 71b of the transfer ports 70, 71 may be provided with labyrinth seals.
  • Such labyrinth seals may e.g. be designed as on the piston-rail inner walls 19a, 19a ', 20a, 20a' provided around the input / output ports 70a, 70b, 71a, 71b extending groove-shaped recesses (not shown).
  • the groove-shaped depressions in this case preferably run concentrically with the openings formed by the inlet / outlet openings 70a, 70b, 71a, 71b.
  • Adjoining the housing surfaces 107, 108 of the motor housing 4 provided with bolt elements 79 are each a housing cover 80a, 80b.
  • the housing covers 80a, 80b are provided with bores 78 for receiving the bolt elements 79, wherein the bolt elements 79 after a successful placement of the housing cover 80a, 80b screwed by means of nuts 84 and thereby the housing cover 80a, 80b are fixed to the motor housing 4.
  • the housing covers 80a, 80b do not directly adjoin the compressor or working piston tracks 11a, 11b, 12a, 12b. According to Fig. 1 respectively.
  • Figure 9 it can be seen that the engine block section 4a of the motor housing 4 has a recess 81 open towards the compressor piston tracks 11a, 11b and a working piston tracks 12a, 12b, in which a spacer insert 82 made of a substantially rigid material can be inserted.
  • the substantially spectacle-shaped spacer inserts 82 are in the exploded view according to Fig. 14 clearly visible.
  • the compressor and working piston tracks 11a, 11b, 12a, 12b are thus exactly bounded by the spacer inserts 82, wherein an elastic sealing element 83 is arranged between the housing cover 80a, 80b and the rigid spacer insert 82. Since the elastic sealing element 83 overlaps the circumference of the distance insert 82, the elastic sealing element 83 is pressed by the housing cover 80a, 80b against the spacer insert 82 as well as on the side surfaces 107, 108 of the motor housing 4.
  • the rigid spacer insert 82 ensures an exact fit to the compressor / power pistons 7a, 7b, 8a, 8b.
  • the distance insert 82 also exerts the function of thermal insulation between the working piston paths 12a, 12b and the uncooled second housing cover 80b.
  • the spacer inserts 82 are therefore made of a material with low thermal conductivity, e.g. Aluminum titanate manufactured.
  • the first housing cover 80a has an in Fig. 13 apparent suction opening 30, while the second housing cover 80b with an in Fig. 1 apparent exhaust port 31 is provided.
  • the suction opening 30 opens into the compressor plane 9 or into the compressor piston webs 11a, 11b, while the exhaust port 31 opens into the working plane 10 or into the working piston webs 12a, 12b in the lower web crossing region 62 '.
  • the first housing cover 80a is provided with two recesses 119 through which fuel injection nozzles 27a, 27b opening into the compressor piston paths 11a, 11b protrude.
  • the second housing cover 80b has two further recesses 120, through which protrude into the working piston paths 12a, 12b spark plugs 26a, 26b protrude, as in Fig. 14 marked on the lower right.
  • the rotary piston engine 1 according to the invention is therefore an engine operating with internal and intermittent combustion.
  • a transmission housing 85 As in Fig. 13 can be seen adjacent to the first housing cover 80a, a transmission housing 85 at.
  • the gear housing 85 has a flange portion 85a, which is screwed with the interposition of a sealing element 146 by means of screws 88 on the first housing cover 80a.
  • the bearing elements 45 are pushed together with shaft seals in the bearing bushes 47 of the gear housing 85 and with screw caps 147 in the in Figure 9 fixed position shown.
  • a template may for example consist of a studded plate, which fit into corresponding holes of the rotor assemblies 58.
  • an oil chamber closure member 77 including an oil level measuring rod 97 is inserted into the transmission housing 85.
  • these views can be analogous to the working level 10, ie for the course of the working piston tracks 12a and 12b or for the interaction of the working piston 8a, 8b are thought.
  • the compressor piston inner sides 17a, 17a ' are guided in each case along the associated compressor piston inner webs 19a, 19a', while the compressor piston outer sides 17b, 17b 'are respectively guided along the associated compressor piston web outer walls 19b, 19b'.
  • the concave curvatures 64, 65 result in each case from the subtraction of an imaginary volume intersection between the rotationally symmetrical about an axis of rotation 14, 15 arranged compressor / working piston outer wall 19b, 19b ', 20b, 20b' and rotationally symmetrical around the respective opposite axis of rotation 14, 15 arranged compressor / working piston inner wall 19a, 19a ', 20a, 20a'.
  • the representational rolling curves thus correspond, viewed from one of the axes of rotation 14, 15 of the motor shafts 2, 3 following viewing direction, each extended cycloids.
  • piston bottoms 34a and 34c located in the compressor plane 9 and the piston bottoms 34a 'and 34c' of the compressor or working pistons 7a, 7b, 8a, 8b located in the working plane 10 are each referred to as "front”.
  • Designated piston bottoms, while located in the compressor plane 9 piston bottoms 34b and 34d and located in the working plane 10 piston bottoms 34b 'and 34d' of the compressor or piston 7a, 7b, 8a, 8b are each referred to as "rear" piston crowns.
  • the compressor / working pistons 7a, 7b, 8a, 8b located in a common compressor / working plane 9, 10 are arranged in a position about their respective axis of rotation 14, 15, in which the sealing edge 63a, 63b, 63c, 63d, 63a ' , 63b ', 63c', 63d 'of the one compressor / piston 7a, 7b, 8a, 8b while passing the web crossing regions 62, 62' continuously the piston crown 34a, 34b, 34c, 34d, 34a ', 34b', 34c ' , 34d 'of the respective opposite compressor / working piston 7a, 7b, 8a, 8b strips.
  • the sealing edge 63d of the second compressor piston 7b would strip the piston head 34a of the first compressor piston 7a, followed by stripping the piston bottom 34d of the second compressor piston 7b by the sealing edge 63a of the first compressor piston 7a.
  • the term "stripping" of the piston crowns 34 in the present context merely means conveying the air / fuel mixture compressed or expanded in the compressor and working piston webs 11a, 11b, 12a, 12b and does not directly contact the piston bottoms 34
  • the arranged in the compressor plane 9 compressor pistons 7a, 7b and arranged in the working plane 10 working piston 8a, 8b always slide close to each other during their rotational movement without rubbing against each other.
  • sealing edges 63a, 63b, 63c, 63d, 63a ', 63b', 63c ', 63d' slide past the associated piston bottoms 34a, 34b, 34c, 34d, 34a ', 34b', 34c ', 34d'. In this way rolling friction or frictional wear between the compressor pistons 7a, 7b or between the working pistons 8a, 8b can be avoided.
  • the designated sealing edge clearance is less than or equal to one between the compressor / power pistons 7a, 7b, 8a, 8b and those portions of the motor housing 4 and the compressor piston tracks 11a, 11b, 12a, 12b, respectively the compressor / power piston 7a, 7b, 8a, 8b are guided during the rotational movement.
  • a closing angle volume formed between the piston head 34c, the compressor piston outer side 17b and the compressor piston inner wall 19a ' can be reduced to approximately zero or at least kept negligible (see in particular FIG Fig. 19 ).
  • FIG. 52 A tangent 151 is drawn on the front piston crown 34c of the second compressor piston 7b, which is currently stripped off from the sealing edge 63b of the first compressor piston 7a.
  • the first compressor piston 7a as well as the first working piston 8a seated on the same motor shaft 2 rotate in the direction of travel 43, ie in the clockwise direction according to the present figures.
  • the second compressor piston 7b and the second working piston 8b seated on the same motor shaft 3 rotate in the direction of travel 44, ie in the counterclockwise direction according to the present figures.
  • the compressor piston paths 11a, 11b and the working piston tracks 12a, 12b intersect at upper and lower track intersection areas 62, 62 '.
  • a first inlet mouth 70a of the first overflow channel 70 and a second inlet mouth 71a of the second overflow channel 71 are arranged.
  • the spatial course of the overflow channels 70, 71 is based on the two-dimensional image in the Figures 23-26 not directly recognizable, but can be determined by the The overflow channels 70, 71 according to the bevelled geometry of the mold elements 32, 33 substantially at an angle of 45 ° relative to the axis of rotation 14, 15 from the compressor plane 9 in the Run working level 10, the first overflow channel 70 opens with an in Figure 24 apparent first exit port 70b immediately adjacent to the lying in the working plane 10 upper rail crossing region 62 and the end portion 65b of the concave curvatures 65 of the working piston inner wall 20a.
  • the second overflow channel 71 opens with an in Figure 24 apparent second exit port 71b immediately adjacent to the lying in the working plane 10 upper rail crossing region 62 and the end portion 64b of the concave curvatures 64 of the working piston inner wall 20a '.
  • edges of the inlet and outlet mouths 70a, 70b, 71a, 71b of the overflow channels 70, 71 are in a preferred embodiment each 2-5 mm from the end portions 64a, 64b, 65a, 65b of the concave vaults 64, 65 distanced.
  • suction port 30 is arranged in the area of the upper rail crossing region 62 located in the compressor plane 9, while the inlet ports 70a, 71a of the transfer ports 70, 71 are arranged opposite thereto, namely, on both sides of the lower rail crossing region 62 '.
  • Fig. 24 It can be seen that the exhaust opening 31 is also located opposite the outlet openings 70b, 71b arranged on either side of the upper track crossing region 62, namely in the area of the lower track crossing area 62 'located in the working plane 10.
  • spark plugs 26a, 26b are opposite to the arranged in the lower rail crossing region 62 'exhaust port 31, namely disposed on either side of the upper rail crossing region 62 and each point in the direction of one of the output ports 70b, 71b of the overflow channels 70, 71.
  • the ignition of the air-fuel mixture is thus within the working piston paths 12a, 12b.
  • the spark plugs 26 a, 26 b and the fuel injection nozzles 27 a, 27 b according to the Figures 48 and 49 are shown only schematically and do not correspond to the actual size ratios.
  • the rear piston bottoms 34b, 34d of the two compressor pistons 7a, 7b in each case suck air or air / fuel mixture from the region of the intake opening 30 into the compressor piston paths 11a, 11b.
  • Figure 23 is located in the running direction 44 second compressor piston 7b or from the rear piston crown 34d in the second compressor piston 11b aspirated air / fuel mixture already in the lower third of the second compressor piston 11b and is from the front piston crown 34c of the second compressor piston 7b against the Verêtrkolbens- Outside 17 b of the rotating in the opposite direction 43 first compressor piston 7 a compressed.
  • the air / fuel mixture is thus bounded (radially) from four sides, namely from the compressor piston inner wall 19a 'and the compressor piston wall outer wall 19b' of the second compressor piston 11b, and from the piston bottom 34c of the second compressor piston 7b and Compressor piston outside 17b of the first compressor piston 7a.
  • the compressor piston outer side 17b of the first compressor piston 7a accurately guided on both the compressor piston outer wall 19b of the first compressor piston path 11a and the concave convexity 64 of the second compressor piston inner wall 19a ' provides a reliable seal so that undesirable compression loss is precluded.
  • the working piston outer side 18b of the first working piston 8a closes the second working piston path 12b in the upper web crossing region 62 and provides the expanding air / fuel mixture with a suitable abutment.
  • a secure seal that acts as the combustion chamber portion of the second working piston track 12 b guaranteed, since the working piston outer side 18 b of the first working piston 8 a both on the working piston outer wall 20 b and on the concave curvature 64 of the working piston Innnenwandung 20a 'are sealingly guided.
  • the sealing edge 63a 'of the first working piston 8a is already outside the combustion chamber or outside the upper web crossing region 62' (as in FIG Figure 24 shown) to exclude the risk of burning off the sealing edge 63a '.
  • a compression ratio of about 11.5 is achieved despite the displacement of the working piston, which represents a considerable increase in engine power as well as a reduction in fuel consumption and exhaust compared to conventional internal combustion engines with a compression ratio of 8.8-10 .
  • the concrete compression ratio of the rotary piston engine 1 according to the invention can be adjusted by a correspondingly selected offset of the compressor piston 7a, 7b to the working piston 8a, 8b.
  • the ignition of the expanded from the first output port 70b air / fuel mixture results in a pressure pulsation of the rear piston crown 34b 'of the first working piston 8a and thus accelerated circulation of the first working piston 8a in the direction 43.
  • the combusted air / fuel mixture is subsequently from front piston head 34a 'of the first working piston 8a pushed out of the first working piston path 12a through the exhaust port 31 into the open.
  • FIGS. 27-45 show a second preferred embodiment of the rotary piston engine 1 according to the invention with four mounted in a motor housing 4 motor shafts 2a, 2b, 3a, 3b, along a first axis of rotation 14 two aligned motor shafts 2a, 2b are arranged and along a second axis of rotation 15 also two aligned Motor shafts 3a, 3b are arranged (see also an exploded view according to Fig.30 ).
  • the motor shafts 2a, 2b and 3a, 3b are respectively engaged with each other and with the drive shaft 13 by means of a reversing gear 66 in engagement.
  • a reversing gear 66 in engagement.
  • the according to Fig.30 By means of bearing elements 45 mounted in the motor housing 4 drive shaft 13 equipped with two pointing in diverging directions bevel gears 36, 37, while the motor shafts 2a, 2b, 3a, 3b in their mounting position of the drive shaft 13 end portions facing each with a bevel gear 38a, 38b, 39a, 39b are provided.
  • the first bevel gear 36 of the drive shaft 13 is orthogonally engaged with the bevel gear 38a of the first motor shaft 2a (rotatable about the first rotation axis 14) and the bevel gear 38b of the second motor shaft 2b (also rotatable about the first rotation axis 14), while the second bevel gear 37 of the drive shaft 13 is orthogonally engaged with the bevel gear 39a of the third (rotatable about the second rotation axis 15) motor shaft 3a and the bevel gear 39b of the fourth (also rotatable about the second rotation axis 15) motor shaft 3b.
  • Each of the motor shafts 2a, 2b, 3a, 3b has a structure according to Figure 28 On: At the motor shaft end portion facing the mounting position of the drive shaft 13, a bevel gear 38, 39 made integrally with or fitted with the motor shaft 2a, 2b, 3a, 3b is arranged, followed by a bearing portion 121 on which a pair of tapered roller bearings 59a / 59b, 60a / 60b and can be fixed by means of a bearing ring 122. An outer jacket of the paired tapered roller bearings 59a / 59b, 60a / 60b in each case runs conically tapered in the direction of the motor shaft end region.
  • a polygonal, slotted shaft jaw 98 is arranged at that to the mounted bevel gear 38, 39 opposite end portion of the motor shaft 2a, 2b, 3a, 3b.
  • the slotted shaft jaw 98 has an axial Tapped hole 98 a, which is provided for receiving a clamping screw 99.
  • the clamping screw 99 has a threaded bore 98a of the slotted wave jaw 98 corresponding conical threaded shaft 99a.
  • Each of the motor shafts 2a, 2b, 3a, 3b carries a compressor piston 7a, 7b or a working piston 8a, 8b, wherein the structure of such a rotor assembly 58 substantially corresponds to that already described with respect to the first embodiment of the rotary piston engine 1 of the invention:
  • the one identical geometry Compressor and working pistons 7, 8 are substantially circular arc-shaped or ring-segment-shaped and have a concentric with the respective axis of rotation 14, 15 extending inside 17a, 18a and concentric with the respective axis of rotation 14, 15 extending outside 17b, 18b, wherein the outer sides 17b, 18b and the inner sides 17a, 18a are bounded by concave piston bottoms 34 or connected to one another and sealing edges 63 are provided on the piston bottoms 34.
  • the compressor or working piston 7, 8 are provided with parallel to the axes of rotation 14, 15 projecting threaded bolt 23, which are screwed with nuts 24.
  • the threaded bolts 23 serve to fasten the compressor or working pistons 7, 8 to associated carrier disks 5, 6, which in turn are fastened to the motor shafts 2a, 2b, 3a, 3b.
  • the carrier disks 5, 6 each have a rotor shaft 102 which can be pushed onto the polygonal shaft jaws 98.
  • the rotor shaft 102 has a centric, corresponding to the polygonal shaft jaws 98 multi-edged opening 100 (see Figure 28 ).
  • FIG. 29 shows an assembly of a single such rotor assembly 58 in plan view.
  • Fig.31 all four rotor assemblies 58 are shown (with the motor housing 4 omitted) in an assembly position, wherein on the rotatable about the first axis of rotation 14 first motor shaft 2a, a first compressor piston 7a is arranged and aligned with the first motor shaft 2a, also about the first axis of rotation 14 rotatable second motor shaft 2b, a first working piston 8a is arranged. Parallel to this, a second working piston 8b is arranged on the third motor shaft 3a rotatable about the second rotation axis 3a, and a second working piston 8b on the fourth motor shaft 2b which is aligned with the third motor shaft 3a and also rotates about the second rotation axis 15.
  • the compressor pistons 7a, 7b coplanar or arranged in a compressor plane 9, while the working piston 8a, 8b are also coplanar or arranged in a working plane 10.
  • Fig.31 or in Fig.27 by means of the reversing gear 66, an opposite direction of rotation of the respective compressor and working pistons 7a, 7b, 8a, 8b arranged along a rotational axis 14, 15 is effected.
  • the first motor shaft 2a and the first compressor piston 7a rotate in the direction of travel 43a, while the second motor shaft 2b and the first working piston 8a rotate in a direction opposite to running direction 43a.
  • the third motor shaft 3a and the second compressor piston 7b rotate in the direction 44a, while the fourth motor shaft 3b and the second working piston 8b in a to rotate opposite direction of rotation 44b.
  • All motor shafts 2a, 2b, 3a, 3b or compressor and working pistons 7a, 7b, 8a, 8b have a synchronous speed.
  • fig.32 shows the shaft or rotor assembly according to Fig.31 in a built-in motor housing 4 state.
  • the engine block section 4a of the motor housing 4 has four conical receptacles 123 and four cylindrical receptacles 124 adjoining them (see also FIGS Fig.30 and Fig.35 ).
  • An inner bearing element 125 adjacent to the bevel gear 38a, 38b, 39a, 39b is inserted into the conical receptacles 123, while an outer bearing element 126 is inserted into the cylindrical receptacles 124.
  • Both bearing elements 125, 126 each have a conical bore and thereby form bearing seats for the paired tapered roller bearings 59a / 59b, 60a / 60b.
  • the outer bearing element 126 is screwed together with a sealing element by means of a screw member 128 on the engine block portion 4a and thereby fixes the tapered roller bearings 59a / 59b, 60a / 60b and thus the motor shafts 2a, 2b, 3a, 3b in their mounting position.
  • the drive shaft 13 as in Fig.37
  • the bevel gears 36, 37 of the reversing gear 66 are first positioned in the motor housing 4, then the hexagonal drive shaft 13 in the present embodiment in the insertion direction 132 through opening stub 130 of the motor housing 4 and through hexagonal openings of the bevel gears 36, 37 passed and screwed with these.
  • this is provided with counterbores 133, which correspond with Tapped holes 40 in shafts of the bevel gears 36, 37 are aligned.
  • the shaft jaws 98 of the motor shafts 2a, 2b, 3a, 3b are provided with suitable markings to allow a proper mounting of the rotor assemblies 58 and a desired offset of the compressor and working pistons 7a, 7b, 8a, 8b to each other.
  • FIGS. 33-38 a motor housing 4 corresponding to the second embodiment of the rotary piston engine 1 according to the invention is shown.
  • the motor housing 4 accommodates a system already described in detail above on compressor piston tracks 11a, 11b and working piston tracks 12a, 12b or a compressor plane 9 and a working plane 10 separated therefrom by motor housing walls 67 (see a half-sectional view in FIG Fig.34 ).
  • motor housing walls 67 see a half-sectional view in FIG Fig.34 .
  • the concave curvatures 64, 65 on the compressor and working piston inner walls 19a, 19a ', 20a, 20a' reference is made to the above statements on the first embodiment of the rotary piston engine 1 according to the invention.
  • Fig.35 shows an isometric sectional view along a section AA fig.33 (See also a corresponding plan view according to Fig.39 ).
  • a substantially horizontally guided first overflow channel 70 has an inlet mouth 70a at the compressor piston inner wall 19a and an outlet mouth 70b at the arranged around the same axis of rotation 14 working piston inner wall 20a, while a likewise substantially horizontally guided second overflow 71 a Entrance opening 71a on the compressor piston inner wall 19a 'and an output port 71b at the arranged around the same axis of rotation 15 working piston inner wall 20a' has.
  • the two transfer channels 70, 71 are in the present embodiment as bores 73, 74, 75 performed by the motor housing walls 67, wherein it is in the bore 73 each opening into the cylindrical receptacles 124 for outer bearing elements 126 through hole through the engine block 4a and where it is at the Drill holes 74, 75 are inclined feed bores, which lead from the compressor or working piston track inner walls 19a, 19a ', 20a, 20a' to the through-bore 73.
  • the through holes 73 are closed at the end with inserted from the sides of the cylindrical receptacles 124 threaded plug 76.
  • the mouths of the feed bores 75 in the compressor piston wall inner walls 19a, 19a 'thus form the inlet ports 70a, 71a of the transfer ports 70, 71, while the mouths of the supply bores 74 in the working piston inner passages 20a, 20a' are the outlet ports 70b, 71b of the transfer ports 70, 71 training.
  • the overflow channels 70, 71 according to the second embodiment of the rotary piston engine 1 according to the invention can thus be dispensed with the provision of form elements 32, 33 together with associated closure elements 115, 116 for forming diagonal overflow channels 70, 71.
  • the overflow channels 70, 71 according to the second embodiment of the rotary piston engine 1 according to the invention straight or substantially horizontally from the compressor plane 9 in the working plane 10. This allows a shortening of the overflow channels 70, 71 and an extension of the cross section of the overflow channels 70, 71 and an associated acceleration of the flow of the air / fuel mixture through the overflow channels 70, 71.
  • overflow channels 70, 71 respectively open outside the concave bulges 64, 65 of the compressor / working piston inner walls 19a, 19a ', 20a, 20a', but immediately adjacent end portions 64a, 64b, 65a, 65b of the concave bulges 64, 65th in the compressor / piston pistons 11a, 11b, 12a, 12b.
  • the motor housing 4 has two aligned with the axes of rotation 14, 15 through holes 140 for receiving the motor shafts 2a, 2b, 3a, 3b and a transverse bore 141 for receiving the drive shaft 13.
  • an oil filling opening 138 and a dipstick opening 139 are provided in the motor housing 4, which each lead to a central oil chamber 113 (see Fig.36 ).
  • the motor housing 4 threaded openings, in which inserts 134, 135 and a cooling water inlet 120 are screwed (see Fig.37 and fig.33 ).
  • On the first insert 134 is a in Fig.27 apparent oil chamber closure cap 136 screwed, while on the second insert 135 also in Fig.27 apparent dipstick element 137 can be screwed.
  • lubrication openings 110 are provided which lead to the central oil space 113 ( Fig.34 ).
  • An advantage of the arrangement of the drive shaft 13 between the compressor plane 9 and the working plane 10 according to the second embodiment of the rotary piston engine 1 according to the invention is also that a common lubrication of the thrust bearings 59a, 59b, 60a, 60b and the bevel gears 36, 37, 38a, 38b , 39a, 39b of the reversing gear 66 via a single central oil chamber 113 is made possible.
  • the central oil chamber 113 is at the bottom of the motor housing 4, as in fig.33 shown closed with an oil chamber closure plate 143 together with a sealing element 144.
  • the oil chamber closing plate 143 is a threaded hole for an oil drain plug 145 is arranged.
  • the cooling water inlet 106 feeds into the Figures 34 and 35 apparent cooling water jacket 112 adjacent to the compressor piston paths 11a, 11b and to the working piston paths 12a, 12b.
  • a housing cover 80a, 80b attached and screwed with nuts 84.
  • the insertion of rigid spacer inserts 82 in corresponding recesses 81 of the engine block section 4a and the provision of an arranged between the housing cover 80a, 80b and the rigid spacer insert 82 elastic sealing element 83 for accurate sealing of the compressor and working piston tracks 11a, 11b, 12a, 12b, including benefits is already Describe sufficiently for the first embodiment of the rotary piston engine according to the invention and applies analogously to the second embodiment.
  • the first housing cover 80a has an intake opening 30 and two recesses 120 for spark plugs 26a, 26b, while the second housing cover 80b is provided with an exhaust opening 31 and with recesses 119 for fuel injection nozzles 27a, 27b ( Fig.38 ).
  • the suction opening 30 opens in the lower web crossing region 62 'in the compressor plane 9 and in the compressor piston webs 11a, 11b, while the exhaust port 31 also in the lower web crossing region 62' in the working plane 10 and in the working piston paths 12a, 12b opens. Due to the opposite rotational direction of the successively arranged on a rotational axis 14, 15 compressor or piston 7a, 7b, 8a, 8b, the suction port 30 and the exhaust port 31 are thus in contrast to the first embodiment of the invention Rotary piston engine 1 substantially at the same height or in the same (lower) web crossing region 62 'arranged. This is also in the schematic sectional views through the compressor or working levels 9, 10 according to the Figures 40-45 seen.
  • both the inlet openings 70a, 71a of the overflow channels 70, 71 arranged in the compressor plane 9 and the outlet openings 70b, 71b of the overflow channels 70, 71 arranged in the working plane 10 are in contrast to the first embodiment of the rotary piston engine 1 (FIG. Fig.23-26 ) are arranged at the same height or in the same (upper) rail crossing region 62.
  • the entrance and exit ports 70a, 71a, 70b, 71 of the transfer passages 70, 71 are disposed adjacent to respective opposite rail crossing portions 62, 62 'as the intake port 30 and the exhaust port 31.
  • the entrance port 70a of the first transfer port 70 is located immediately adjacent the end portion 65b of the concave cove 65 of the compressor piston inner wall 19a 'of the second compressor piston path 11b, while the input port 71a of the second transfer port 71 immediately adjacent the end portion 64b of the concave camber 64 of the compressor piston path Inner wall 19a of the first compressor piston path 11a is arranged ( Fig.40 ).
  • the exit port 70b of the first transfer passage 70 is located immediately adjacent to the end portion 65b of the concave cove 65 of the working piston raceway inner wall 20a 'of the second working piston passage 12b, while the exit port 71b of the second overflow channel 71 is arranged immediately adjacent to the end region 64b of the concave bulges 64 of the working piston inner wall 20a of the first working piston path 12a ( FIGURE 43 ).
  • spark plugs 26a, 26b are opposite to the arranged in the lower rail crossing region 62 'exhaust port 31, namely disposed on either side of the upper rail crossing region 62 and each point in the direction of one of the output ports 70b, 71b of the transfer ports 70, 71st
  • Fig.41 shows the opposite Fig.40 by a quarter-turn in the Verêtrkolbenbahnen 11a, 11b according to their directions of rotation 43a, 44a advancing compressor piston 7a, 7b, previously sucked from the rear piston crown 34d of the second compressor piston 7b air / fuel mixture now from the front piston crown 34c of the second compressor piston 7b against the Compressor piston outside 17b of the rotating in opposite direction 43a first compressor piston 7a is compressed (top left).
  • This compaction process is in Fig.42 shown continued, wherein the compressed air / fuel mixture is pressed into the inlet mouth 71 a of the second transfer port 71 and into the working plane 10 located in the second working piston path 12 b is conveyed.
  • T 3 the compressor pistons 7a and 7b and the motor shafts 2a and 3a have completed a 180 ° rotation.
  • FIG.44 shows the opposite FIGURE 43 by a quarter-turn in the working piston tracks 12a, 12b according to their running directions 43b, 44b advancing working piston 8a, 8b, which also shows how the front piston crown 34c 'of the second working piston 8b already in the course of one Ignition according to FIGURE 43 previous Häkates burned air / fuel or gas mixture in front of him and ausschiebt through the exhaust port 31 (bottom left).
  • the ignition of the air / fuel mixture expanded from the first exit orifice 70b results in a pressure pulse on the rear piston bottom 34b 'of the first working piston 8a and thus an accelerated circulation of the first working piston 8a in the direction 43b.
  • the combusted air / fuel mixture is subsequently pushed by the front piston head 34a 'of the first working piston 8a from the first working piston path 12a through the exhaust port 31 into the open.
  • FIGS. 50 and 51 For a better understanding of the principle of operation according to the second embodiment of the rotary piston engine 1 according to the invention is in the FIGS. 50 and 51 in each case an isometric sectional view of the fuel injectors 27a, 27b populated compressor plane 9 and the assembled with spark plugs 26a, 26b working plane 10 shown.
  • the correspond FIGS. 50 and 51 a snapshot, which was made at the time of the highest compression or the ignition timing of the air / fuel mixture both in the compressor plane 9 and synchronous thereto in the working plane 10 of the rotary piston engine 1 according to the second embodiment.
  • the rotary piston engine 1 according to the invention can be operated in both embodiments with any fuels, including diesel fuel. In the latter case, the providence of the spark plugs 26a, 26b can be omitted.
  • a suitable adaptation of the piston geometry must be made. In order to achieve a compression ratio which is ideal for diesel ignition, therefore, the compressor pistons 7a, 7b or the compressor piston webs 11a, 11b could be made somewhat narrower are depicted as in the figures shown. Alternatively, a height (measured in the direction of the rotation axes 14, 15) of the compressor pistons 7a, 7b or of the compressor piston paths 11a, 11b could also be increased in relation to their width.
  • the compressor piston inner walls 19a, 19a 'with one or more depressions 148 as in Fig.47 shown schematically, be provided.
  • the depressions 148 each lead from a region of the compressor piston inner wall 19a, 19a 'adjacent to the end region 64a, 65a of the concave curvature 64, 65 to the concave one adjacent to the said compressor piston inner wall 19a, 19a' Buckle 64, 65.
  • the recesses 148 are provided to prevent an in Fig.46 shown, "dead" closing angle X, which results from the fact that in order to ensure the tightness of the compressor piston webs 11a, 11b between the overflow inlet port 71a and the end portion 64a of the first concave 64 and between the overflow inlet port 7oa and the end portion 65a the second concave vault 65, though minimal, must be spaced.
  • each compressor or working piston 7, 8 is guided in each compressor or working piston track 11a, 11b, 12a, 12b or is mounted on a motor shaft 2, 3, 2a, 2b, 3a, 3b, it is in an alternative construction (not shown) of the rotary piston engine 1 according to the invention also possible in the compressor or working piston tracks 11a, 11b, 12a, 12b each have a plurality, for example, two or three compressor or To arrange working piston 7, 8.
  • four compressor / working pistons 7, 8 would therefore revolve both in the compressor plane 9 and in the working plane 10.
  • a number of inclined or / and curved ribs 152 are provided in the manner of axial turbine blades. These ribs 152 are preferably arranged parallel to one another and distributed along the inner circumference 54a, 55a of the piston walls 54, 55. Passage channels 162, which permit transport of cooling air 155 sucked in via an inlet opening 166 provided in the motor housing 4, through the axial extent 163 of the compressor / working piston 7a, 7b, 8a, 8b, result between the ribs 152.
  • the axial end portions 152a, 152b of the ribs 152 are side surfaces defining the outer side 17b, 17b ', 18b, 18b' and the inner side 17a, 17a ', 18a, 18a' of the compressor / power piston 7a, 7b, 8a, 8b 157, 158 spaced by a distance measure 164, respectively.
  • the axial extent of the ribs 152 measured along the axis of rotation 14, 15 is thus smaller than the axial extent 163 of the compressor / working piston 7a, 7b, 8a, 8b.
  • the cooling air 155 is first sucked through an air filter 154 from a housing-external area and by one of both the (in Fig.54 blanked) housing cover 80b and the distance insert 82 in the axial direction passing through the inlet opening 166 in the web crossing region 62, 62 'between the working piston paths 12a, 12b out (see also Fig.55 ).
  • the ribs 152 passing through the inlet opening 166 during rotation of the working pistons 8a, 8b and the passageways 162 formed by the ribs 152 are in this case flushed or flushed with cooling air 155.
  • the cooling air 155 in the axial direction by a in Fig. 54 apparent, formed by a channel section 153 through opening 159 to the underlying compressor piston webs 11 a, 11 b conveyed.
  • the cooling air 155 occurs in the web crossing region 62, 62 'in the Ver Whyrkolbenbahnen 11a, 11b, wherein during the rotation of the Compressor piston 7a, 7b the passage opening 159 passing ribs 152 of the compressor piston 7a, 7b and the formed by the ribs 152 passageways 162 with cooling air 155 are flushed or flushed.
  • an outlet opening 167 is provided on the side of the compressor piston webs 11a, 11b.
  • the cooling air 155 which has passed through the working plane 10 as well as through the compressor plane 9, is subsequently connected by a discharge pipe 16 passing through the outlet opening 167, the working piston side sealing element 82 and the housing cover 80a passing through and a curved pipe passing through the transmission housing 85 161 dissipated.
  • the through hole 159 - as well as the inlet opening 166 - arranged centrally between the piston webs 11a and 11b and 12a and 12b, so that by means of a single passage opening 159 or inlet opening 166 both adjacent compressor pistons 7a, 7b and 8a working piston 8a be fed with cooling air 155.
  • the passage opening 159 is - as well as the inlet opening 166 - between the respective compressor / working piston tracks 11a, 11b, 12a, 12b bounding inner walls 19a, 19a ', 20a, 20a' and the outer walls 19b, 19b ', 20b, 20b' arranged to prevent passage of the air / fuel mixture from the compressor / piston pistons tracks 11a, 11b, 12a, 12b into the cooling air 155.
  • the passage opening 159 and the inlet opening 166 are therefore so in the lower rail crossing region 16 'arranged that they are swept only by the cavities 53 and the passageways 162 of the compressor / piston 7a, 7b, 8a, 8b and the piston inner and outer sides 17a, 17b, 17a', 17b ', 18a, 18b, 18a ', 18b', 19a, 19b, 19a ', 19b' 20a, 20b, 20a ', 20b' not surmounted.
  • the passage opening 159 leading from the working plane 10 into the compressor plane 9 is to be arranged in a region of the engine block section 4 a in which neither the explosion pressure occurring in the compressor or working piston tracks 11 a, 11 b, 12 a, 12 b nor the expansion pressure nor the compression pressure is the air pressure. / Fuel mixture can push into the area in which the cooling air 155 is guided.
  • FIG Fig.55 An ideal area for arranging the through hole 159 is according to FIG Fig.55 the located below a located at the height of the axes of rotation 13, 14 central rail crossing region 62 "located lower rail crossing region 62 ', so that in case of an encounter of piston crowns 34a, 34b, 34c, 34d, the through hole 159 is only then opened by the piston side surfaces 157, 158, if the partially released air-fuel mixture or exhaust gas has already been shielded from the piston bottom 34 of the respectively opposite working piston 8a, 8b from the through-opening 159.
  • the cooling-air flow therefore always remains separate from the alternating gas flow (intake, compression, expansion and exhausts).
  • the speed or the flow volume of cooling air 155 through the compressor / power pistons 7a, 7b, 8a, 8b can by the structural design of the ribs 152, in particular by determining their number, axial width, thickness 165 and their inclination to the axes of rotation 14th 15 are determined.
  • a described air cooling of the compressor / power piston 7a, 7b, 8a, 8b makes it necessary that the intake of fresh air to be compressed and the puffing of combusted air-fuel mixture no longer axially, but from the side of the outer walls 19b, 19b ', 20b, 20b 'of the compressor or working piston tracks 11a, 11b, 12a, 12b, for example, tangential to the compressor or working piston tracks 11a, 11b, 12a, 12b in the web crossing region 62, 62' takes place.
  • the scenario prevents the working pistons 8a, 8b from sweeping over (eg according to FIG Figure 11 ) in the direction of the axes of rotation 14, 15 extending or axially from the working piston paths 12a, 12b leading exhaust port 31, the hot exhaust gas in the passage channels 162 of the working piston 8a, 8b suck back.
  • Such an alternative arrangement of the intake port 30 and the exhaust port 31 is in Fig.54 shown.
  • passage section 159 forming the channel section 153 in the case of in Fig.27 illustrated second embodiment of the rotary piston engine 1 according to the invention with a arranged between the compressor plane 9 and the working plane 10 reverse gear 66 is not linear or axial as in Fig.54 shown, but curved from the working level 10 in the compressor plane 9 must run.
  • FIG.56 Another measure for optimizing the cooling air flow is in Fig.56 shown.
  • a gap 168 results which is caused by the opposite curvatures of the piston bottoms 34b, 34c and by the offset angle between the piston bottoms 34b, 34c is.
  • the closure walls 169 are located at those points of the working piston 8a, 8b, where they close the cooling air passage opening 159, when the in the course of the compressor piston rotation between the piston crowns 34b, 34c of the compressor piston 7a, 7b formed gap 168 via the passage opening 159 moves.
  • the closure walls 169 must be sufficiently wide to close the passageway 159 throughout the distance of the compressor pistons 7a, 7b passing through the gap 168 while passing the passageway 159, but should not be wider so as not to obscure the flow of the cooling air 155 to hinder.
  • the working piston 8a, 8b form in this way, together with the passage opening 159 window valves, which control the cooling air flow so that no mixing of cooling air 155 and air-fuel mixture can occur.
  • the enclosed in the gap 168 between the compressor piston 7a, 7b air-fuel mixture is therefore not forced into the open - it should be noted that the pressure loss itself in such Trap would be extremely low, since the formed between the compressor piston plates 34b, 34c gap 168 passes through the passage 159 in the thousandths of seconds - but remains in the Verêtrkolbenbahnen 11a, 11b, where it merges with the Ansauglauft again at the next intake stroke.
  • sealing areas 170 of the motor housing 4 pointing to the insulating rings 21 or to the carrier disks 5a, 5b, 6a, 6b may be provided a series of flat, waffle-shaped indentations 171 may be provided which interrupts any possible laminar flow of the air-fuel mixture leaving the piston webs 11a, 11b, 12a, 12b by swirling (purely by way of example in US Pat Fig.57 shown).
  • notches 172 can also be applied to the outer sides 17b, 17b ', 18b, 18b' and the piston bottoms 34a, 34b, 34c, 34d, 34a ', 34b', 34c ', 34d' of the compressor / power pistons 7a, Be provided 7b, 8a, 8b limiting side surfaces 157, 158 (also in Fig.57 shown).
  • notches 171, 172 are according to Fig.57 in the form of a plurality of mutually offset and substantially concentric with the axes of rotation 14, 15th extending rows along the sealing regions 170 and along the piston outer sides 17b, 17b ', 18b, 18b' adjacent side surfaces 157 arranged.
  • an indentation 174 is provided on the inner wall 19a 'of the second compressor piston track 11b in a region immediately adjacent to the web crossing region 16 or the concave curvature 64, from which air under normal pressure can flow into the prismatic volume 173 formed between the compressor pistons 7a, 7b. Due to the size of this semicircular indentation 174 formed in the present exemplary embodiment, it is possible to determine the desired negative pressure in each case in the prismatic volume 173. The indentation 174 has on the compression of the air-fuel mixture no influence, since it is in the intake of the compressor piston webs 11a, 11b.
  • the inner wall 19a of the first compressor piston web 11a is also provided with a recess 174 in a region immediately adjacent to the web crossing region 16 or the concave curvature 65.
  • Fig.61 shows an exhaust cycle in which the piston head 34c 'of the second working piston 8b rotating counterclockwise in the second working piston track 12b currently expels exhaust gas from the second working piston track 12b in the direction of the exhaust opening 31. Also from the first working piston track 12a flows at this time already from the piston head 34a 'of the counter-rotating first working piston 8a ejected exhaust gas to the exhaust port 31st
  • a cavity in the form of a substantially prismatic volume 173' forms between the piston head 34c 'of the second working piston 8b and the outer side 18b of the first working piston 8b, which progresses as the rotation proceeds the working piston 8a, 8b reduced.
  • an indentation 175 is provided on the inner wall 20a 'of the second working piston track 12b in a region immediately adjacent to the web crossing region 16' or the concave curvature 64, in which normal pressure prevails before the beginning of the compression. Due to the size of this semicircular indentation 175 formed in the present exemplary embodiment, the respective desired overpressure can be determined.
  • Fig.62 shows how the indentation 175 is reopened in the course of continued piston rotation and the remainder of the overpressure therein can relax back into the exhaust gas.
  • the inner wall 20a of the first working piston track 11b is also provided with a semicircular indentation 175 in an area immediately adjacent to the track crossing area 16 'or the concave curvature 65.
  • the indentation 175 has no influence on the compression and combustion of the air-fuel mixture transported in the working piston tracks 11a, 11b, since it is located in the exhaust area of the working piston tracks 11a, 11b.

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Abstract

Moteur à pistons rotatifs (1), comprenant des arbres moteur (2, 3) montés dans un carter de moteur (4), aptes à tourner autour de deux axes de rotation (14, 15) et entraînant un arbre d'entrée (13). Un piston de compresseur (7a, 7b) tourne respectivement autour de chaque axe de rotation (14, 15), et des pistons de travail (8a, 8b) sont montés rotatifs. Les pistons de compresseur et de travail (7a, 7b, 8a, 8b) ont sensiblement une forme d'arc de couronne et les trajectoires (11a, 11b, 12a, 12b) des pistons de compresseur et de travail sont de type gorge de couronne. Le but de l'invention est d'obtenir un rendement compression ou moteur élevé. A cet effet, les fonds de piston (34) présentent respectivement une arête d'étanchéité (63), la courbure des fonds de pistons (34) coïncidant avec le profil d'une courbure qui coupe l'arête d'étanchéité (63) d'un piston de compresseur/travail (7a, 7b, 8a, 8b) dans la zone de croisement (62, 62') des trajectoires à partir de la section transversale du piston de compresseur/travail (7a, 7b, 8a, 8b) tournant en sens inverse. L'arête d'étanchéité (63) d'un piston de compresseur/travail racle en continu le fond (34) du piston de compresseur/travail respectivement opposé lors de son passage de la zone de croisement (62, 62') des trajectoires.

Claims (15)

  1. Moteur à pistons rotatifs comprenant des arbres de moteur (2, 3) supportés dans un logement de moteur (4), capables de rotation autour de deux axes de rotation (14, 15) et entraînant un arbre moteur (13), dans lequel au moins un piston de compression (7a, 7b) et au moins un piston moteur (8a, 8b) sont supportés avec possibilité de rotation autour de chacun des axes de rotation (14, 15), dans lequel un sens de rotation inverse des pistons de compression (7a, 7b) et des pistons moteurs (8a, 8b) à vitesse de rotation synchrone est obtenu en force au moyen d'une unité de multiplication (16), dans lequel des trajectoires de piston de compression (11a, 11b) des pistons de compression (7a, 7b) disposés dans un plan de compression commun (9) et des trajectoires de piston moteur (12a, 12b) des pistons moteurs (8a, 8b) disposés dans un plan de travail (10) parallèle au plan de compression (9) se recoupent dans une zone de croisement de trajectoires (62, 62'), dans lequel les trajectoires de piston de compression (11a, 11b) disposées dans le plan de compression (9) sont séparées des trajectoires de piston moteur (12a, 12b) disposées dans le plan de travail (10) par des cloisons (67) du logement du moteur, dans lequel les pistons de compression et moteurs (7a, 7b, 8a, 8b) sont conformés pour l'essentiel en forme d'anneau circulaire et présentent une face intérieure (17a, 17a', 18a, 18a') concentrique de l'axe de rotation (14, 15) correspondant et une face extérieure (17b, 17b', 18b, 18b') concentrique de l'axe de rotation (14, 15) correspondant, les faces intérieures (17a, 17a', 18a, 18a') et les faces extérieures (17b, 17b', 18b, 18b') étant limitées chacune et reliées entre elles par des couronnes de piston concaves (34a, 34b, 34c, 34d, 34a', 34b', 34c', 34d') et les trajectoires de piston de compression (11a, 11b) ainsi que les trajectoires de piston moteur (12a, 12b) ayant pour l'essentiel la forme de gorges annulaires circulaires, dans lequel les faces intérieures (17a, 17a', 18a, 18a') des pistons de compression et moteurs sont guidées chacune le long d'une paroi intérieure (19a, 19a', 20a, 20a') des pistons de compression et moteurs et les faces extérieures (17b, 17b', 18b, 18b') des pistons de compression et moteurs sont guidées chacune le long d'une paroi extérieure (19b, 19b', 20b, 20b') des pistons de compression et moteurs, les parois intérieures (19a, 19a', 20e, 20a') des pistons de compression et moteurs présentant chacune dans la zone de croisement des trajectoires (62, 62') un arrondi concave (64, 65) qui est obtenu par un recoupement de la trajectoire de piston de compression/moteur (11a, 11b, 12a, 12b) avec la paroi intérieure (19a, 19a', 20a, 20a') de piston de compression/moteur associée au piston de compression/moteur (7a, 7b, 8a, 8b) opposé ou par une intersection d'ensembles de volume imaginaire entre une paroi extérieure (19b, 19b', 20b, 20b') de piston de compression/moteur disposée de façon symétrique en rotation autour d'un axe de rotation (14, 15) et une paroi intérieure (19a, 19a', 20a, 20a') de piston de compression/moteur disposée de façon symétrique en rotation autour de l'axe de rotation (14, 15) opposé, caractérisé en ce qu'un bord d'étanchéité (63a, 63b, 63c, 63d, 63a', 63b', 63c', 63d') est prévu sur chaque couronne de piston (34a, 34b, 34c, 34d, 34a', 34b', 34c', 34d') au niveau des faces extérieures (17b, 17b', 18b, 18b') des pistons de compression/moteurs, la courbure des couronnes de piston (34a, 34b, 34c, 34d, 34a', 34b', 34c', 34d') correspondant à la forme d'une came de roulement qui recoupe le bord d'étanchéité (63a, 63b, 63c, 63d, 63a', 63b', 63c', 63d') d'un piston de compression/moteur (7a, 7b, 8a, 8b) en rotation autour de l'axe de rotation (14, 15) dans la zone de croisement des trajectoires (62, 62') hors de la section du piston de compression/moteur (7a, 7b, 8a, 8b) tournant dans le sens opposé autour de l'axe de rotation (14, 15) opposé et situé dans le plan de compression/de travail (9, 10) commun, et les pistons de compression/moteurs (7a, 7b, 8a, 8b) se trouvant dans un plan de compression/de travail (9, 10) commun étant disposés dans une position autour de l'axe de rotation (14, 15) correspondant dans laquelle le bord d'étanchéité (63a, 63b, 63c, 63d, 63a', 63b', 63c', 63d') d'un piston de compression/moteur (7a, 7b, 8a, 8b) frotte constamment, pendant le franchissement de la zone de croisement des trajectoires (62, 62'), la couronne (34a, 34b, 34c, 34d, 34a', 34b', 34c', 34d') du piston de compression/ de travail (7a, 7b, 8a, 8b) opposé, des canaux de trop-plein (70, 71) étant disposés entre les trajectoires de piston de compression (11a, 11b) et les trajectoires de piston moteur (12a, 12b), de préférence en oblique du plan de compression (9) au plan de travail (10), et les canaux de trop-plein (70, 71) débouchant chacun à l'extérieur des arrondis concaves (64, 65) des parois intérieures de trajectoire de piston de compression/moteur (19a, 19a', 20a, 20a'), mais à proximité immédiate des parties d'extrémité (64a, 64b, 65a, 65b) des arrondis concaves (64, 65) dans les trajectoires de piston de compression/moteurs (11a, 11b, 12e, 12b).
  2. Moteur à pistons rotatifs selon la revendication 1, caractérisé en ce qu'il est prévu, pendant le mouvement de rotation des pistons de compression/moteurs (7a, 7b, 8a, 8b), un jeu de 2/10 mm au maximum, de préférence un jeu < 1/10 mm, mesuré entre le bord d'étanchéité (63a, 63b, 63c, 63d, 63a', 63b', 63c', 63d') d'un piston de compression/moteur (7a, 7b, 8a, 8b) et la couronne de piston (34a, 34b, 34c, 34d, 34a', 34b', 34c', 34d') du piston de compression/moteur (7a, 7b, 8a, 8b) opposé.
  3. Moteur à pistons rotatifs selon l'une des revendications 1 ou 2, caractérisé en ce que les pistons de compression/moteurs (7a, 7b, 8a, 8b) sont disposés sur des disques de support (5a, 5b, 6a, 6b) qui peuvent être fixés sur les arbres du moteur (2, 3).
  4. Moteur à pistons rotatifs selon l'une des revendications 1 à 3, caractérisé en ce qu'un seul arbre du moteur (2, 3) est disposé le long de chaque axe de rotation (14, 15), les pistons de compression et moteurs (7a, 7b, 8a, 8b) disposés sur l'un des arbres du moteur (2, 3) dans le plan de compression (9) et dans le plan de travail (10) tournant dans le même sens de rotation.
  5. Moteur à pistons rotatifs selon l'une des revendications 1 à 4, caractérisé en ce que les canaux de trop-plein (70, 71), de préférence de forme courbe, sont constitués par des éléments mis en forme (32, 33) qui sont introduits dans des fentes (68, 69) prévues dans des cloisons (67) du logement de moteur séparant le plan de compression (9) du plan de travail (10).
  6. Moteur à pistons rotatifs selon l'une des revendications 1 à 3, caractérisé en ce que deux arbres de moteur (2a, 2b, 3a, 3b) alignés l'un avec l'autre sont disposés le long de chaque axe de rotation (14, 15) et l'un des deux arbres de moteur (2a, 2b, 3a, 3b) alignés l'un avec l'autre porte au moins un piston de compression (7a, 7b) tandis que l'autre de ces arbres du moteur (2a, 2b, 3a, 3b) porte l'au moins un piston moteur (8a, 8b), les deux arbres du moteur (2a, 2b, 3a, 3b) étant en prise l'un avec l'autre au moyen d'une transmission réversible (66), de telle sorte qu'un sens de rotation en sens opposé des deux arbres du moteur (2a, 2b, 3a, 3b) ou un sens de rotation en sens opposé des pistons de compression et moteur (7a, 7b, 8a, 8b) disposés sur un axe de rotation (14, 15) soit obtenue en force, la transmission réversible (66) entraînant un arbre moteur (13) disposé entre le plan de compression (9) et le plan de travail (10).
  7. Moteur à pistons rotatifs selon l'une des revendications 1 à 6, caractérisé en ce qu'un canal de trop-plein (70, 71) mène de la paroi intérieure (19a, 19a') de la trajectoire du piston de compression disposée autour de l'axe de rotation (14, 15) à la paroi intérieure (20a, 20a') de la trajectoire de piston moteur disposée autour du même axe de rotation (14, 15).
  8. Moteur à pistons rotatifs selon l'une des revendications 1 à 7, caractérisé en ce qu'aussi bien les embouchures d'entrée (70a, 71a) que les embouchures de sortie (70b, 71b) des canaux de trop-plein (70, 71) sont voisines soit d'une zone de croisement des trajectoires supérieure (62), soit d'une zone de croisement des trajectoires inférieure (62') parmi les trajectoires de piston de compression ou moteurs (11a, 11b, 12a, 12b).
  9. Moteur à pistons rotatifs selon l'une des revendications 1 à 8, caractérisé en ce qu'il est prévu dans une partie de bloc moteur (4a) du logement du moteur (4) un évidement (81) ouvert vers les trajectoires de piston de compression/moteurs (11a, 11b, 12a, 12b), dans lequel un insert d'écartement (82) fabriqué dans un matériau sensiblement rigide peut être logé, l'insert d'écartement (82) étant pressé dans les évidements (81) par un couvercle de logement (80) qui peut être fixé sur le logement du moteur (4) dans une position voisine des pistons de compression et moteurs (7a, 7b, 8a, 8b), et un élément d'étanchéité (83) élastique qui recouvre la circonférence de l'insert d'écartement (82) étant disposé entre le couvercle de logement (80) et l'insert d'écartement (82).
  10. Moteur à pistons rotatifs selon l'une des revendications 1 à 9, caractérisé en ce que chaque trajectoire de piston de compression (11a, 11b) est associée à une buse d'injection de carburant (27a, 27b) pour enrichir en carburant l'air aspiré dans le logement du moteur (4) avant son entrée dans les trajectoires de piston de compression (11a, 11b) ou directement dans les trajectoires de piston de compression (11a, 11b), de préférence au niveau d'une ouverture d'aspiration (30) débouchant dans les trajectoires de piston de compression (11a, 11b).
  11. Moteur à pistons rotatifs selon l'une des revendications 1 à 10, caractérisé en ce que chaque trajectoire de piston moteur (12a, 12b) est associée à une bougie d'allumage (26a, 26b), les bougies d'allumage (26a, 26b) étant de préférence disposées au niveau d'embouchures de sortie (70b, 71b) des canaux de trop-plein (70, 71).
  12. Moteur à pistons rotatifs selon l'une des revendications 1 à 11, caractérisé en ce que les parois intérieures (19a, 19a') des trajectoires de piston de compression présentent un ou plusieurs renfoncements (148) qui vont d'une zone de la paroi intérieure (19a, 19a') de la trajectoire de piston de compression située en dehors de la zone de croisement des trajectoires (62, 62') et voisine des zones d'extrémité (64a, 64b, 65a, 65b) des arrondis concaves jusqu'à l'arrondi concave (64, 65) limitrophe de la paroi intérieure (19a, 19a') de la trajectoire de piston de compression.
  13. Moteur à pistons rotatifs selon l'une des revendications 1 à 12, caractérisé en ce qu'il est prévu entre les parois de piston (54, 55) d'au moins un des pistons de compression/moteurs (7a, 7b, 8a, 8b) un nombre quelconque de nervures (152) obliques et/ou courbées, lesquelles nervures (152) sont de préférence parallèles les unes aux autres et réparties le long de la circonférence intérieure (54a, 55a) des parois de piston (54, 55), des canaux de passage (162) étant formés entre les nervures (152) et permettant un transport d'air de refroidissement (154) aspiré par une ouverture d'entrée (166) prévue dans le logement du moteur (4) à travers l'étendue axiale (163) du piston de compression/moteur (7a, 7b, 8a, 8b).
  14. Moteur à pistons rotatifs selon la revendication 13, caractérisé en ce que les parties d'extrémité axiales (152a, 152b) des nervures (152) sont écartées chacune des surfaces latérales (157, 158) délimitant la face extérieure (17b, 17b', 18b, 18b') et de la face intérieure (17a, 17a', 18a, 18a') du piston de compression/moteur (7a, 7b, 8a, 8b) d'une dimension d'écartement (164).
  15. Moteur à pistons rotatifs selon la revendication 13 ou 14, caractérisé en ce qu'il est prévu dans le logement du moteur (4) au moins une ouverture de passage (159) à travers laquelle l'air de refroidissement (154) peut être amené d'au moins une des trajectoires de piston de compression/moteur (11a, 11b, 12a, 12b) dans la ou les trajectoires de piston de compression/moteur (11a, 11b, 12a, 12b) situées derrière dans le sens axial, l'ouverture de passage (159) étant de préférence disposée à l'intérieur de la zone de croisement des trajectoires (162, 162') de deux trajectoires de piston de compression/moteur (11a, 11b, 12a, 12b) situées l'une à côté de l'autre.
EP08785918A 2007-07-20 2008-07-04 Moteur à pistons rotatifs Active EP2171212B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
AT0045407U AT10063U1 (de) 2007-07-20 2007-07-20 Kreiskolbenmotor
PCT/EP2008/058659 WO2009013110A1 (fr) 2007-07-20 2008-07-04 Moteur à pistons rotatifs

Publications (2)

Publication Number Publication Date
EP2171212A1 EP2171212A1 (fr) 2010-04-07
EP2171212B1 true EP2171212B1 (fr) 2012-05-02

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EP08785918A Active EP2171212B1 (fr) 2007-07-20 2008-07-04 Moteur à pistons rotatifs

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EP (1) EP2171212B1 (fr)
AT (2) AT10063U1 (fr)
WO (1) WO2009013110A1 (fr)

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102011109966B4 (de) * 2011-08-02 2016-12-01 Brands & Products IPR-Holding GmbH & Co.KG Rotationskolbenmotor, insbesondere mit zündkammerumlaufenden Rotationskolben
CN113476915B (zh) * 2021-07-19 2022-07-22 中铁二十二局集团第一工程有限公司 一种建筑工程用泥浆处理装置

Family Cites Families (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB745746A (en) * 1953-04-27 1956-02-29 British Internal Combust Eng Improvements in or relating to rotary pumps and motors
US4236496A (en) * 1978-07-24 1980-12-02 Brownfield Louie A Rotary engine
DE3232046A1 (de) 1982-08-27 1984-03-01 Robert 8998 Lindenberg Messmer Maschine, insbesondere verbrennungskraftmaschine
DE3242431A1 (de) 1982-11-16 1984-05-17 Motos Motor GmbH, 4512 Wallenhorst Drehkolben-heissgasmotor mit kontinuierlicher verbrennung
DE3627962A1 (de) 1986-08-18 1988-03-17 Kurt Jauch Drehkolbenbrennkraftmaschine
DE3825372A1 (de) 1988-07-26 1990-02-01 Armin Mylaeus Drehkolbenmaschine
DE4440924A1 (de) 1994-11-17 1996-05-30 Josef Lipinski Brennkraftmaschine mit umlaufenden Kolben als 4-Scheiben-Kreiskolbenmotor
SE0100744L (sv) 2001-03-07 2002-09-08 Abiti Ab Rotationsmotor

Also Published As

Publication number Publication date
AT10063U1 (de) 2008-08-15
EP2171212A1 (fr) 2010-04-07
WO2009013110A1 (fr) 2009-01-29
ATE556194T1 (de) 2012-05-15

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