WO2009013110A1 - Moteur à pistons rotatifs - Google Patents

Moteur à pistons rotatifs Download PDF

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Publication number
WO2009013110A1
WO2009013110A1 PCT/EP2008/058659 EP2008058659W WO2009013110A1 WO 2009013110 A1 WO2009013110 A1 WO 2009013110A1 EP 2008058659 W EP2008058659 W EP 2008058659W WO 2009013110 A1 WO2009013110 A1 WO 2009013110A1
Authority
WO
WIPO (PCT)
Prior art keywords
piston
compressor
working
working piston
rotary
Prior art date
Application number
PCT/EP2008/058659
Other languages
German (de)
English (en)
Inventor
Franz Ackerl
Original Assignee
Franz Ackerl
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Franz Ackerl filed Critical Franz Ackerl
Priority to AT08785918T priority Critical patent/ATE556194T1/de
Priority to EP08785918A priority patent/EP2171212B1/fr
Publication of WO2009013110A1 publication Critical patent/WO2009013110A1/fr

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Classifications

    • 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 separated by motor housing walls, but are interconnected by a respective overflow, wherein the compressor and Ar Beitskolben are substantially circular arc-shaped 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 bounded
  • Movement principle of the conventional reciprocating engine make a steadily rotating movement principle of variably designed, eccentric or centric about a rotation axis rotating piston elements usable.
  • From DE 195 27 277 Al 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 have each other overlapping 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 takes place both a fuel enrichment and an ignition of the air / fuel mixture.
  • 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 approximately 20
  • an opening angle volume present on the side of the working rotors must be the same, so that these unused components of the intake volume reduce the compression ratio achievable with the rotary piston engine to such an extent that no engine power that can be used for economic implementation can be achieved cause the compressors or work rotors rolling against each other a high component wear and make a complex seal the compressor or working piston tracks by means arranged on the circumference of the compressor or piston sealing rings together Backstops required.
  • DE 32 42 431 A1 discloses a rotary 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 present invention is therefore based on the object to avoid the disadvantages mentioned and a respect constructive and motor characteristics to provide improved 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 compressor piston paths arranged in a common compressor plane compressor pistons as well as working piston paths of the arranged in a plane parallel to the compressor level working piston in a rail crossing each overlap, wherein arranged in the compressor plane compressor piston tracks separated from the arranged in the working plane working piston paths by motor housing walls, however are interconnected by a respective overflow.
  • the axes of rotation of the compressor and working pistons 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 bounded respectively by piston crowns or interconnected and wherein the Verêtrkolbenbahnen and the Working piston tracks - the geometry of the compressor and working piston accordingly - are formed substantially Vietnamese nikringnutförmig, 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 are guided. While arranged in a common compressor or working plane compressor or Häkolbenbahn- outer walls merge into each other, arranged in a common compressor or working plane compressor or working piston inner wall paths 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.
  • the term "stripping" of the piston crowns is understood in the present context merely to convey the air / fuel mixture compressed or expanded in the compressor and working piston paths and not to directly contact the piston bottoms with the sealing edge During stripping, the compressor pistons arranged in the compressor plane slide as well The working pistons, which are arranged in the working plane, always pass close to each other in the course of their rotational movement without rubbing against one another, thus avoiding frictional wear between the compressor pistons or between the working pistons.
  • 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.
  • each case a plurality of compressor or working piston can be rotatably mounted about the axes of rotation.
  • a Verreterz. Working piston per compressor or working piston path is provided, it is also conceivable to arrange in the compressor or working piston each several, preferably two compressor or working piston, taking into account 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 / working piston has cavities which pass through piston walls and preferably radially are limited 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 / working piston inner webs in the web crossing region in each case have a concave curvature, which is defined by an overlapping of the compressor / working piston web with the compressor which is assigned to the respectively opposite compressor / working piston.
  • / Working piston inner wall or by an imaginary volume intersection between a rotationally symmetrical about a rotational axis arranged compressor / Häkolbenbahn- outer wall and a rotationally symmetrical about the respective opposite axis of rotation arranged compressor / working piston inner wall path results.
  • the concave curvatures result by engagement of the compressor / working piston in the respective opposite compressor / piston associated compressor / working piston inner wall path.
  • the course of the compressor or working piston outer walls is continued by the concave curvatures arranged on the compressor or working piston inner walls.
  • the compressor or working piston outsides are not only from now on guided along the associated compressor or working piston outer walls, but also in the previously critical, for a compression or expansion of the air / fuel mixture relevant rail 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.
  • insulating rings are provided which are arranged between the carrier disc and the compressor / working piston are.
  • the insulating rings it is advisable to manufacture the insulating rings from a material of low thermal conductivity, e.g. Aluminum titanate.
  • balancing weights are attached to the carrier discs.
  • the arrangement of the drive and motor shafts two particularly preferred embodiments of the rotary piston engine according to the invention are proposed:
  • a single motor shaft is arranged, wherein the arranged on one of the motor shafts in the compressor plane and in the working plane compressor and working piston rotate in the same direction.
  • 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.
  • the rotary piston engine according to the invention are arranged between the arranged in the compressor plane compressor piston trains and in the Working plane arranged working piston paths preferably provided obliquely through a central engine block portion of the compressor plane extending in the working plane overflow.
  • the overflow are formed in a special construction by form elements, wherein the compressor plane separating the plane of the work plane motor housing walls are provided with slots into which the mold elements are inserted.
  • the mold elements according to the invention can have a respectively desired geometry and replace a difficult production of curved overflow wells or a complicated cast with lost shape.
  • 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 undesirable overlap of the piston paths of the compressor in the working plane.
  • 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.
  • Overflow channels favor an 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.
  • 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 injector to the sucked air before entering the
  • Compressor piston tracks or directly in the
  • Compressor piston paths preferably in the region of an opening into the compressor piston recesses suction, enrich with fuel.
  • each working piston path is a spark plug assigned, wherein the spark plugs are preferably arranged in the region of the outlet openings of the transfer channels or are held in openings which lead to the working piston paths.
  • the compressed air / fuel mixture can thus not relax before the power stroke into a separate combustion chamber volume and a higher compression ratio is achieved.
  • 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.
  • 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 between the ribs and the piston trajectory delimiting
  • Walls form areas with stagnant cooling air or there is an unimpeded flow of cooling air through all
  • 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 can be conveyed from at least one of the compressor / working piston tracks in the respective axially behind it (s) compressor / working piston track (s).
  • the passage opening is preferably arranged within the web crossing region of two adjacent compressor / working piston paths.
  • the piston trajectory limiting components which are in the present embodiment to piston carrier discs or These notches, which are preferably arranged in the form of a plurality of staggered rows along the sealing regions, fluidize any laminar flow of the air-fuel mixture leaving 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.
  • Fig.l a first embodiment of a rotary piston engine according to the invention in an oblique view with partially cut motor housing
  • FIG. 2 shows a motor shaft drive shaft arrangement of the rotary piston engine according to the invention according to a first embodiment in exploded view Fig.3 a motor shaft drive shaft arrangement of the rotary piston engine according to the invention according to a first embodiment in combination
  • FIG. 5 shows a compressor or working piston assembly including motor shaft according to a first embodiment of the rotary piston engine according to the invention in an oblique view
  • FIG. 6 shows a rotor assembly including motor shaft according to a first embodiment of the rotary piston engine according to the invention in an oblique view
  • FIG. 7 shows an operating shaft motor shaft drive shaft rotor arrangement of the rotary piston engine according to the invention according to a first embodiment in an oblique view.
  • FIG. 8 shows an operating shaft motor shaft drive shaft rotor arrangement of the rotary piston engine according to the invention according to a first embodiment in plan view 9 shows a plan view of the invention
  • FIG. 10 shows a motor housing according to a first embodiment of the rotary piston engine according to the invention in an oblique view.
  • FIG. 10a shows a half-section illustration of the motor housing in the case of a vertical passage through the web crossing region
  • FIG.10b is an exploded view of the engine block section including inventive mold elements Fig.10c shown in Fig.10b components in the assembly
  • FIG. 11 shows a motor housing of a first embodiment of the rotary piston engine according to the invention as shown in FIG. 10 in an isometric half-section view in horizontal direction
  • FIG. 12 shows a motor housing of a first embodiment of the rotary piston engine according to the invention according to FIG. 10 in an isometric half-section view in vertical direction
  • FIG. 13 shows a motor housing together with flanged gear housing according to a first embodiment of the invention
  • 16 is a front view of a motor housing of the rotary piston engine according to the invention, including inserted
  • Fig.17 is a schematic representation of the compressor level together with each stripping compressor piston to a
  • Time t 2 19 is a schematic representation of the compressor level together with each stripping compressor piston to a
  • Fig.20 is a schematic representation of the compressor level together with each stripping compressor piston to a
  • Time t 4
  • Figure 21 shows two overflow channel forming mold elements according to a first embodiment of the invention
  • Circular piston engine in an oblique view Fig.22 two an overflow channel forming mold elements according to a first embodiment of the invention
  • FIG. 25 shows a schematic representation of the compressor level including rotating compressor piston according to a first
  • Fig.27 shows a second embodiment of a rotary piston engine according to the invention in an oblique view with partially cut motor housing Fig.28 a compressor / working piston assembly together with motor shaft according to a second embodiment of Rotary piston engine according to the invention in isometric
  • Exploded view Fig.29 an assembled rotor assembly including motor shaft according to a second embodiment of the rotary piston engine according to the invention in normal view
  • FIG. 30 shows a motor shaft drive shaft arrangement of the rotary piston engine according to the invention according to a second
  • 31 shows a motor shaft drive shaft arrangement of the rotary piston engine according to the invention according to a second
  • Embodiment in Compilation Fig. 32 is a plan view of the invention
  • Fig.25 including partially cut rotor assemblies Fig.33 a motor housing according to a second embodiment of the rotary piston engine according to the invention in
  • FIG. 34 shows a motor housing according to a second embodiment of the rotary piston engine according to the invention along section line B-B in FIG
  • 35 shows a motor housing according to a second embodiment of the rotary piston engine according to the invention
  • FIG. 36 shows a motor housing according to a second embodiment of the rotary piston engine according to the invention in vertical
  • Halbloppydars notorious Fig.37 is an assembly view of a motor housing according to a second embodiment of the invention
  • Rotary piston motor insertable drive shaft with reversing gear in an oblique view
  • Fig.38 is an exploded view of a motor housing including
  • Housing covers according to a second embodiment of the rotary piston engine according to the invention in plan view 39 shows a motor housing according to a second embodiment of the rotary piston engine according to the invention in a horizontal
  • Fig.40 is a schematic representation of the compressor level including rotating compressor piston according to a second
  • Fig.42 is a schematic representation of the compressor level including rotating compressor piston according to a second
  • 43 is a schematic representation of the working plane including rotating working piston according to a second
  • Embodiment of the rotary piston engine according to the invention at a time T I 'Fig.44 a schematic representation of the working plane including rotating working piston according to a second
  • Fig.45 is a schematic representation of the working plane including rotating working piston according to a second
  • FIG. 46 shows an enlarged representation of the web crossing region in the compressor plane.
  • FIG. 47 shows a half-section view of the motor housing in the case of a vertically running through the web crossing region
  • Cutting guide including inventive recesses in the compressor piston inner walls Fig.48 is an isometric view of the working plane together
  • Fig.49 is an isometric view of the compressor level together
  • Fig.50 is an isometric view of the working plane together
  • Fig.51 is an isometric view of the compressor level
  • FIG. 53 shows an alternative embodiment of a compressor
  • Fig.54 is an isometric sectional view of the rotary piston engine with an inventive arrangement for piston cooling
  • Fig.55 is a schematic representation of the motor housing isometric sectional view of a passage opening for piston cooling having motor housing
  • Fig.56 is a perspective single view of the compressor shown in Figure 54 in the installed state compressor / piston Fig.57 a populated with compressor / working piston
  • FIG. 58 is a sectional view of the compressor plane provided with indentations according to the invention.
  • Time T I Fig.59 is a sectional view of the inventive
  • Time T 2 Fig.60 is a sectional view of the inventive
  • Time T 3 Fig.61 is a sectional view of the inventive
  • Fig.62 is a sectional view of the inventive
  • Fig.l 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 shows an exploded view of a motor shaft / drive shaft arrangement, wherein a hollow shaft piece 35 which can be pushed onto the drive shaft 13 can be seen, which in FIG its axial end portions with two pointing in diverging directions bevel gears 36, 37 is provided.
  • 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 mounting position of the drive shaft 13 assigning, polygonal 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 multi-edged 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 for fixing the bevel gears 38, 39 engage the motor shaft end 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 ball or cylindrical roller bearings bearing elements 45, while the motor shafts 2, 3 with directly to the ZOQO
  • 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.
  • Motor shaft / drive shaft arrangement according to Figure 3 can be seen, as by means of the translator unit 16 constituent bevel gears 36, 37, 38, 39 an opposite direction of rotation of the first motor shaft second
  • the compressor piston 7 and the working piston 8 have an identical geometry according to FIG. 4:
  • the compressor and working pistons 7, 8 according to the invention essentially circular-arc-shaped or annular segment-shaped and have a concentric to 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 or interconnected by concave piston bottoms 34.
  • sealing edges 63 are provided at the piston bottoms 34.
  • the compressing and working pistons 7, 8, which are 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 form the inside 17a, 18a and the outside 17b, 18b Connecting piston walls 54, 55 together. 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. 6).
  • the motor shafts 2, 3 are provided for the purpose of a solid connection with the carrier discs 5, 6 with in Fig.5 apparent polygonal wave regions 56 and 57.
  • 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. 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.
  • 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 become (Fig.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 project beyond the inner sides 17a, 18a of the compressor / power pistons 7, 8 or the inner piston walls 54 with their outer diameter in order to form a tear-resistant connection between the compressor / power pistons 7, 8 and to allow the carrier discs 5, 6.
  • balancing weights 22 are screwed with screws 25 to the support plates 5, 6.
  • Such rotor assemblies 58 are (in blanking of the motor housing 4) shown in Figures 7 and 8 in an assembly position, wherein at the rotatable about the first axis of rotation 14 first shaft 2 a at a first
  • Compressor piston carrier plate 5a fastened first
  • FIG. 9 shows the shaft arrangement according to FIG. 7 or FIG. 8 in a state installed in the motor housing 4, this illustration being a horizontal section through the motor housing 4 according to FIG.
  • 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. After the polygonal Openings 100 of the rotor shafts 102 which enclose the polygonal shaft regions 57 shown in FIG. 3 are screwed onto the threaded sections 94 of the motor shafts 2, 3 in FIG. 14 (top left).
  • 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.
  • the motor housing 4 shown in FIGS. 10-12 alone, ie without rotor or shaft arrangements, has a motor block section 4a and a peripheral housing section 4b.
  • the engine block section 4a and the peripheral housing section 4b are each manufactured separately by the malleable casting process and are 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 shown in Figures 10-12 results.
  • the motor housing 4 accommodates a compressor plane 9 and a working plane 10 separated therefrom by motor housing walls 67.
  • a "compressor plane” is understood to mean a system of compressor piston lanes IIa, IIb, while the term “working plane” denotes a system of working piston lanes 12a, 12b.
  • the compressor piston paths IIa, IIb provided for receiving the compressor pistons 7a, 7b and the working piston tracks 12a, 12b provided for receiving the power pistons 8a, 8b are clearly visible.
  • the compressor piston webs IIa, IIb and the working piston webs 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 paths IIa, IIb 12a, 12b measured radially relative to the axes of rotation 14, 15 corresponds essentially to a cross-sectional width of the compressor and power pistons 7a which is likewise measured radially to the rotational axes 14, 15. 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 IIa is arranged parallel to the first working piston path 12a and the second compressor piston path IIb parallel to the second working piston path 12b, the compressor piston paths IIa and IIb and the working piston paths 12a and 12b in a web crossing region 62, 62 'merge into each other.
  • overlapping or communicating with one another results in the adjacent compressor piston paths IIa, IIb and the working piston paths 12a, 12b each have a figure-of-eight shape of the first and second compressor or working piston paths IIa, IIb arranged in the compressor and working planes 9, 10,
  • FIG. 16 shows a frontal view of the compressor piston paths IIa and IIb, but FIGS
  • the compressor or working piston outer wall 19b, 19b ', 20b, 20b' merge into one another, while the compressor or working piston inner walls 19a, 19a ', 20a, 20a' are each closed (This is particularly evident in Figures 10 and 11).
  • the compressor / Häkolbenbahn- inner walls 19a, 19a ', 20a, 20a' have in the web crossing regions 62, 62 'in each case a concave curvature 64, 65 on.
  • an upper track crossing area 62 and a lower track crossing area 62 ' are differentiated from each other in the following.
  • 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 holes 95, two conical bearing seats 90, 91 are provided, which have a press fit to in Fig.8 apparent, attached to 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 in one to a Longitudinal view through the motor housing 4 as shown in FIG 12 apparent central oil chamber 113 leads.
  • lubrication openings 110 are also provided in the housing walls 67, which also 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).
  • an oil filling opening 28 In the oil filling 28, a ⁇ lraumver gleichschraube 29 shown in Fig.l including an oil level measuring rod 97 is inserted.
  • an oil chamber closure plate 143 including an oil drain plug 145 is arranged on the underside of the motor housing 4, as can be seen in a representation of a second embodiment of the motor housing according to FIG.
  • 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).
  • a cooling water inlet 106 shown in FIG. 10 is provided which leads to a cooling water jacket 112 adjacent to the compressor piston paths IIa, IIb and to the working piston paths 12a, 12b in FIGS. 9 and 11.
  • the motor housing 4 also has a corresponding, in a cooling water outlet 106a arranged on a bottom region (FIG. 16).
  • continuous slots 68, 69 are provided in the motor housing walls 67 of the engine block section 4a separating the compressor plane 9 from the working plane 10.
  • These slots 68, 69 are curved and provided for receiving form elements 32, 33 shown in FIGS. 21 and 22.
  • the shaped elements 32, 33 which are likewise curved in accordance with the course of curvature of the slots 68, 69, serve to form overflow channels 70, 71 which respectively lead from the compressor piston paths IIa, IIb to the working piston paths 12a, 12b.
  • the shaped elements 32, 33 are chamfered on 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 representation according to FIG. 22).
  • the mutually facing sides 32a, 33a of the shaped elements 32, 33 can be profiled or rugged in order 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. Since the slots 68, 69 and the mold elements 32, 33 are curved, 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.
  • an outlet opening 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 IIa, IIb to the working piston paths 12a, 12b.
  • FIG. 10a shows a half-section illustration of the motor housing 4 with a sectional view running vertically through the web crossing regions 62, 62.
  • the perspective according to FIG. 10a shows only the second overflow channel 71, the course of the first overflow channel 70 being mirrored about the sectional plane (see also FIG. 10b).
  • Fig. 10b shows an exploded view of one with two
  • Motor block portion 4a can be seen while the peripheral housing portion 4b is hidden.
  • 10c shows an assembly of the components exploded in FIG. 10b, wherein the overflow channels 70, 71 constituted by the inserted pairs of molded elements 32, 33 are shown by dashed lines.
  • FIGS. 10a-c further show how the transfer ports 70, 71, with their inlet ports 70a, 71a and their outlet ports 70b, 71b, respectively, extend beyond the concave convexities 64, 65 of the compressor / power piston track.
  • the curved course of the transfer passages 70, 71 is required so as not to cut the compressor piston tracks IIa, IIb, 12a, 12b in an area which is 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 paths IIa, IIb to the respectively behind arranged working piston paths 12a, 12b during ignition of the air / fuel mixture to strong axial Impacts on the compressor and piston 7a, 7b, 8a, 8b and their bearings and a restless running of the motor shafts 2, 3 would lead.
  • 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 shank portion 115a, 116a and a centric 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 mold elements 32, 33 buried in the slots 68, 69 could e.g. be attached from the side of the central oil chamber 113 with screws.
  • the engine block section 4a has corresponding recesses 118, which can be seen in FIG. 11, for receiving the form elements 32, 33 or for receiving the closure elements 115, 116.
  • the recesses 118 are provided with threaded bores 109, which are in alignment 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 apparent means in Fig.9 Screw members 105 can be fixed in the recesses 118 of the engine block section 4a.
  • visible seals 104 are inserted into the recesses 118 in FIG. 16, which seals the central oil space 113 against oil loss and the compressor or working piston paths IIa, IIb, 12a, 12b Protect 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 can be screwed by means of nuts 84 after a successful placement of the housing covers 80a, 80b and thereby the housing covers 80a, 80b can be fixed to the motor housing 4.
  • the housing covers 80a, 80b do not directly adjoin the compressor or working piston paths IIa, IIb, 12a, 12b.
  • the substantially spectacle-shaped spacer inserts 82 are clearly visible in the exploded view according to FIG.
  • the compressor and working piston paths IIa, IIb, 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 On the side of the working level 10 or on the side of the second housing cover 80b, the distance insert 82 also performs 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, eg aluminum titanate.
  • the first housing cover 80a has an intake opening 30 which can be seen in FIG. 13, while the second housing cover 80b is provided with an exhaust opening 31 which can be seen in FIG.
  • the suction opening 30 opens into the compressor plane 9 or into the compressor piston webs IIa, IIb, while the exhaust port 31 in the lower web crossing region 62 'opens into the working plane 10 or into the working piston webs 12a, 12b.
  • first housing cover 80a is provided with two recesses 119, through which fuel injection nozzles 27a, 27b opening into the compressor piston paths IIa, IIb protrude.
  • second housing cover 80b has two further recesses 120, through which protrude into the working piston paths 12a, 12b spark plugs 26a, 26b project, as shown in Fig.14 bottom right.
  • the rotary piston engine 1 according to the invention is therefore an engine operating with internal and intermittent combustion.
  • a gear housing 85 adjoins the first housing cover 80a.
  • 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 drive shaft 13 is pushed through in Fig.9 apparent bushings 47 of the gear housing 85 and the bevel gears 36, 37 carrying hollow shaft piece 35 in the manner already described on the figures 2 and 3 on the Drive shaft 13 attached.
  • the bearing elements 45 are pushed together with shaft seals in the bearing bushes 47 of the gear housing 85 and fixed with screw caps 147 in the position shown in Figure 9.
  • 3 bevel gears 38, 39 with the bevel gears 36 37 of the drive shaft 13 - is the position of sitting on the motor shafts 2, 3 Verreterz. Working piston 7a, 7b, 8a, 8b to each other by means of a (not shown) template determined.
  • a template may for example consist of a studded plate, which fit into corresponding holes of the rotor assemblies 58.
  • an oil chamber closing element 77 including an oil level measuring rod 97 is also inserted into the gear housing 85.
  • FIGS. 17-20 it can now be seen how the geometry of the concave curvatures 64, 65 provided in the web crossing region 62, 62 'at the compressor / working piston web inner walls 19a, 19a', 20a, 20a 'comes about (constructively):
  • the concave bulges 64, 65 result in each case by the subtraction of an imaginary one Volume intersection between the rotationally symmetrical about a rotational axis 14, 15 arranged compressor / working piston outer wall 19b, 19b ', 20b, 20b' and the rotationally symmetrical about the respective opposite axis of rotation 14, 15 arranged compressor / Häkolbenbahn- inner wall 19a, 19a ' , 20a, 20a '.
  • a sealing edge 63a, 63b, 63c, 63d is provided on the piston bottoms 34a, 34b, 34c, 34d, the compressor pistons 7a, 7b in the region of the compressor piston outer sides 17b, 17b '.
  • the curvature of the piston bottoms 34a, 34b, 34c, 34d corresponds to the course of a cycloid-shaped rolling curve, which the sealing edge 63a, 63b, 63c, 63d of a about the axis of rotation 14, 15 rotating compressor piston 7a, 7b in the web crossing region 62, 62 'on the piston head 34a , 34b, 34c, 34d or on the radial cross section of the opposite direction of rotation about the respective opposite rotational axis 14, 15 rotating, lying in the common compressor plane 9 compressor piston 7a, 7b, 8a, 8b draws.
  • a sealing edge 63a ', 63b', 63c ', 63d' is provided on the piston bottoms 34a ', 34b', 34c ', 34d' of the working pistons 8a, 8b in the region of the working piston outer sides 18b, 18b ' Curvature of the piston heads 34a ', 34b', 34c ', 34d' corresponds to the course of a cycloid-shaped rolling curve, which the sealing edge 63a ', 63b', 63c ', 63d' of a rotating about the rotation axis 14, 15 working piston 8a, 8b in the web crossing region 62nd , 62 'on the piston head 34a', 34b ', 34c ', 34d' or on the radial cross section of the opposite direction of rotation about the respective opposite rotational axis 14, 15 rotating, lying in the common working plane 10 working piston 8a, 8b records (see also Figures 24 and 26).
  • 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.
  • FIG. 17-20 this shows schematically how the sealing edge 63b of the first compressor piston 7a rotating in the direction of rotation 43 (clockwise in FIG. 17) defines the piston crown 34c of the second compressor piston rotating in the direction 44 (counterclockwise in FIG 7b in the according to Fig.17 upper rail crossing region 62 'strikes. If one continues the illustrated cycle of motion, the piston bottom 34b of the first compressor piston 7a would next be stripped off the sealing edge 63c of the second compressor piston 7b.
  • 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 crown 34d of the piston second compressor piston 7b through the sealing edge 63a of the first compressor piston 7a.
  • the term "stripping" of the piston crowns 34 in the present context is understood merely as conveying the air / fuel mixture compressed or expanded in the compressor and working piston webs IIa, IIb, 12a, 12b and does not directly contact the piston bottoms 34
  • the compressor pistons 7a, 7b arranged in the compressor plane 9 and the working pistons 8a, 8b arranged in the working plane 10 always slide close to each other during their rotational movement without rubbing against each other.
  • the designated sealing edge clearance is less than or equal to one between the compressor / power piston 7a, 7b, 8a, 8b and those portions of the motor housing 4 and the Verêtrz. Working piston paths IIa, IIb, 12a, 12b, along which the compressor / working pistons 7a, 7b, 8a, 8b are guided during their rotational movement.
  • the course of the compressor or working piston outer walls 19b, 19b ', 20b, 20b' is limited by the pressure on the compressor or working piston inner walls 19a, 19a', 20a, 20a 'arranged concave vaults 64, 65 in one of the Overflow channels 70, 71 or continued to the input and output ports 70a, 70b, 71a, 71b immediately adjacent area, there are no sealing problems between the rotating compressor or piston 7a, 7b, 8a, 8b.
  • wear-prone sealing rings including complicated backstops according to the prior art can therefore be dispensed with.
  • 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 approximately to zero or at least kept negligible (see in particular FIG. 19).
  • FIG. 52 A tangent 151 is marked on the front piston bottom 34c of FIG second compressor piston 7b, which is currently swept off 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 webs IIa, IIb and the working piston webs 12a, 12b intersect in an upper and a lower web crossing region 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 progression of the overflow channels 70, 71 can not be directly recognized on the basis of the two-dimensional image in FIGS. 23-26, but can be understood from the profile of the slots 68, 69 sheltering the mold elements 32, 33.
  • the first overflow channel 70 opens with a first output port 70b apparent in Fig. 24 immediately adjacent to in the working plane 10 located upper rail crossing region 62 and the end region 65b of the concave curvatures 65 of the working piston inner wall 20a.
  • the second overflow channel 71 opens with a second outlet mouth 71b visible in FIG. 24 immediately adjacent to the upper rail crossing region 62 located in the working plane 10 or to the end region 64b of the concave curves 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.
  • the intake opening 30 is arranged in the area of the upper rail crossing region 62 situated in the compressor plane 9, while the inlet openings 70a, 71a of the overflow ducts 70, 71 are arranged opposite thereto, namely on both sides of the lower rail crossing region 62 '.
  • the exhaust opening 31 is also located opposite the outlet openings 70b, 71b arranged on both sides of the upper track crossing area 62, namely in the area of the lower track crossing area 62 'located in the working plane 10.
  • the fuel injection nozzles 27a, 27b which are located in the compressor plane 9 and are not shown in FIGS. 48 and 49, are arranged adjacent to the intake opening 30 and point in the direction of one of the compressor piston paths IIa and IIb.
  • the spark plugs 26a, 26b which are also located in the working plane 10 and are also visible in FIGS. 48 and 49, are arranged opposite the exhaust opening 31 located on the lower rail crossing region 62 ', namely on both sides of the upper rail crossing region 62 and point in each case in the direction of one of the outlet openings 70b, 71b Overflow channels 70, 71.
  • the ignition of the air-fuel mixture thus takes place within the working piston paths 12a, 12b.
  • the spark plugs 26a, 26b and the fuel injection nozzles 27a, 27b according to FIGS. 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 IIa, IIb.
  • a second compressor piston 7b rotating from the direction of rotation 44 or an air / fuel mixture sucked into the second compressor piston path IIb from the rear piston crown 34d is already in the lower third of the second compressor piston path IIb and is supported by the front piston bottom 34c of the second compressor piston 7b compressed against the compressor piston outer side 17b of the rotating in the opposite direction 43 first compressor piston 7a.
  • 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 path IIb, and from the piston head 34c of the second compressor piston 7b and Compressor piston outer side 17b of the first compressor piston 7a.
  • the compressor piston outer side 17b of the first compressor piston 7a guided precisely on both the compressor piston web outer wall 19b of the first compressor piston path IIa and on the concave curvature 64 of the second compressor piston inner wall 19a ', ensures a reliable seal, so that undesired compression loss is precluded.
  • the front piston crown 34c of the second compressor piston 7b continues to rotate in the direction 44 until the air / fuel mixture carried in the second compressor piston path IIb successively compresses and finally into the intake port located at the compressor piston inner wall 19a ' 71a of the second transfer port 71 is pressed into it.
  • An eventual stripping of the front piston crown 34c of the second compressor piston 7b by the sealing edge 63b disposed on the rear piston crown 34b of the first compressor piston 7a has already become described with reference to FIGS 17-20 and is to be understood in detail at that point.
  • Fig.23 shown compression process by the front
  • Air / fuel mixture has reached its peak
  • 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.
  • Sealing that portion of the second working piston path 12b which acts as the combustion chamber is ensured since the working piston outer side 18b of the first working piston 8a is sealingly guided both on the working piston outer wall 20b and on the concave curvature 64 of the working piston inner wall 20a '.
  • the output of the rotary piston engine 1 according to the invention does not reduce the output of the rotary piston engine 1 according to the invention, since approximately half the working piston track 12a, 12b can be assumed as the effective working path of the working pistons 8a, 8b from the upper railway crossing region 62 Combustion chamber is a Ve despite the Schwarzben- offset 11.5 compared to conventional internal combustion engines with a compression ratio of 8.8-10 means a significant increase in engine performance and a reduction in fuel consumption and emissions.
  • 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 from the first working piston track 12a pushed through the exhaust port 31 into the open.
  • FIGS. 48 and 49 each show an isometric sectional view of the compressor plane 27 equipped with fuel injection nozzles 27a, 27b and the working plane 10 equipped with spark plugs 26a, 26b.
  • the figures 48 and 49 correspond to a snapshot, which was made at the time of the highest compression of the air / fuel mixture both in the compressor plane 9 and synchronously thereto in the working plane 10. It can be seen here that after completion of the compression of the air / fuel mixture transported in the compressor piston path IIb or at the time of ignition of this air / fuel mixture in the working piston path 12, a measured from the rear working piston bottom 34d 'to the output port 71b of the overflow 69 (on the axis of rotation 15 related) opening angle is about 27 °. However, this opening angle or the position of the working piston 8b at the time of ignition is shown purely by way of example in FIG. 48 and can be varied as desired by a corresponding arrangement of the working piston 8b on the motor shaft 3.
  • FIGS. 27-45 show a second preferred embodiment of the rotary piston engine 1 according to the invention four engine shafts 2a, 2b, 3a, 3b mounted in a motor housing 4, two motor shafts 2a, 2b aligned with each other along a first axis of rotation 14 and two motor shafts 3a, 3b aligned with each other along a second axis of rotation 15 (see also FIGS 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.
  • Fig.30 mounted by means of bearing elements 45 in the motor housing 4 drive shaft 13 with two pointing in diverging directions bevel gears 36, 37 equipped, while the motor shafts 2a, 2b, 3a, 3b in their mounting position in the drive shaft 13 end portions each with a Bevel gear 38a, 38b, 39a, 39b are provided.
  • Each of the motor shafts 2a, 2b, 3a, 3b has a construction according to FIG. 28: On the motor shaft end region facing the drive shaft 13 in the mounting position, a bevel gear wheel is produced either integrally with the motor shaft 2a, 2b, 3a, 3b or mounted thereon 38, 39, followed by a storage section 121, on which a pair Tapered roller bearings 59a / 59b, 60a / 60b can be placed and 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 threaded bore 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 central polygonal opening 100 which corresponds to the polygonal shaft jaws 98 (see FIG. 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) 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 at the aligned with the first motor shaft 2a, also A first working piston 8a is arranged around the first rotary shaft 14 rotatable second motor shaft 2b. 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 and 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 of travel 44a, while the fourth motor shaft 3b and the second working piston 8b rotate in a direction of rotation opposite thereto 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 arrangement according to FIG. 31 in a state installed in the motor housing 4.
  • the engine block section 4a of the motor housing 4 has four conical receivers 123 and four cylindrical receivers 124 adjoining them (see also FIGS. 30 and 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 shown in Fig.37, mounted in the motor housing 4:
  • the bevel gears 36, 37 of the reversing gear 66 are first positioned in the motor housing 4 , Then, in the present embodiment hexagonal formed drive shaft 13 is inserted in the insertion direction 132 through opening stub 130 of the motor housing 4 and through hexagonal openings of the bevel gears 36, 37 and screwed with these.
  • this is provided with counterbores 133 which are aligned with corresponding threaded holes 40 in shafts of the bevel gears 36, 37.
  • the rotor assemblies 58 preassembled in the manner described above become a stop section 129 visible in FIG. 30 on the motor shafts 2 a, 2 b, 3 a, 3 b pushed and fixed to the slotted shaft jaws 98 of the motor shafts 2a, 2b, 3a, 3b, by tightening screws 99 are screwed into the axial threaded holes 98a of the slotted shaft jaws 98.
  • Screwing in the conical Threaded 99a of the clamping screw 99 in the slotted shaft jaw 98 has the result that segments of the slotted shaft jaw 98 pressed against the multi-edged opening 100 of the rotor shaft 102 of the support plates 5a, 5b, 6a, 6b and the rotor assembly 58 thereby precisely on the motor shaft 2a, 2b , 3a, 3b is fixed (Fig.28 / Fig.29).
  • 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 show a motor housing 4 corresponding to the second embodiment of the rotary piston engine 1 according to the invention.
  • the motor housing 4 houses a system already described in detail above on compressor piston paths IIa, IIb 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-section illustration according to FIG. 34). Also with regard to the formation of 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 sectional guide AA from 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 on the compressor piston inner wall 19a and an exit orifice 70b at the working shaft inner wall 20a disposed about the same rotation axis 14, while a second transfer passage 71, also substantially horizontally, has an entrance mouth 71a at the compressor piston inner wall 19a 'and an exit port 71b at the working piston path around the same rotation axis 15 -Interior wall 20a 'possesses.
  • the two transfer ports 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 4 a and wherein it is at the holes 74, 75 to oblique Zu Industriesbohrept, which lead from the side of the compressor or Häkolbenbahn- inner walls 19a, 19a ', 20a, 20a' respectively to the through hole 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 supply bores 75 in the Ver Whyrkolbenbahn- inner walls 19a, 19a 'thus form the entrance mouths 70a, 71a of the overflow channels 70, 71, while the mouths of the feed holes 74 in the working piston inner walls 20a, 20a', the output ports 70b, 71b of the overflow 70, 71 training.
  • the overflow channels 70, 71 run 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 a concomitant acceleration of the flow of air - / fuel mixture through the overflow channels 70, 71st
  • 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 IIa, IIb, 12a, 12b.
  • the motor housing 4 has two through bores 140 aligned with the axes of rotation 14, 15 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 an oil dip 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).
  • An oil chamber closure cap 136 which can be seen in FIG. 27, can be screwed onto the first insert 134, while an oil dipstick element 137, also shown in FIG. 27, can be screwed onto the second insert 135.
  • 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 closed at the bottom of the motor housing 4, as shown in Figure 33, with an oil chamber closing plate 143, including 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 a cooling water jacket 112 which is visible in FIGS. 34 and 35 and is adjacent to the compressor piston webs IIa, IIb and to the working piston webs 12a, 12b.
  • a housing cover 80a, 80b is attached to the side surfaces 107, 108 of the motor housing 4 provided with bolt elements 79 and screwed with screw 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 paths IIa, IIb, 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 trains IIa, IIb, while the Auspuff ⁇ réelle 31 also in the lower rail crossing region 62' in the working plane 10 and in the working piston paths 12a, 12b opens.
  • the intake opening 30 and the exhaust opening 31 are essentially at the same height or height, in contrast to the first embodiment of the rotary piston engine 1 according to the invention in the same (lower) web crossing region 62 '. This can also be seen in the schematic sectional views through the compressor or working planes 9, 10 according to FIGS. 40-45.
  • 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 invention Circular piston engine 1 (Fig.23-26) at the same height or in the same (upper) web crossing region 62 arranged.
  • Circular piston engine 1 Fig.23-26
  • the inlet and outlet ports 70a, 71a, 70b, 71 of the transfer ports 70, 71 are adjacent to opposite rail intersections 62, 62 ', respectively, 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 camber 65 of the compressor piston inner wall 19a 'of the second compressor piston path IIb, 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 IIa is arranged (Fig.40).
  • the exit port 70b of the first transfer passage 70 is located immediately adjacent the end portion 65b of the concave camber 65 of the working piston path inner wall 20a 'of the second working piston path 12b, while the exit port 71b of the second transfer passage 71 is immediately adjacent the end portion 64b of the concave cusps 64 of the working piston path Inner wall 20a of the first working piston track 12a is arranged (Fig.43).
  • the fuel injectors 27a, 27b placed in the compressor plane 9 and not shown in FIGS. 40-42 but visible in FIGS. 50 and 51 are arranged adjacent to the intake port 30 or in another region of the compressor piston webs IIa and IIb.
  • the spark plugs 26a, 26b which are also shown in FIGS. 50 and 51 and are placed in the working plane 10, are arranged opposite the exhaust opening 31 arranged in the lower rail crossing region 62 ', namely on both sides of the upper rail crossing region 62 and point in each case Direction of one of the output ports 70b, 71b of the transfer ports 70, 71st
  • Overflow channels 70, 71 in each case by an imaginary, through the
  • Fig.41 shows the comparison with Fig.40 by a quarter-turn in the compressor piston trains IIa, IIb according to their directions of rotation 43a, 44a moving forward 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 bottom 34c of the second compressor piston 7b against which the compressor piston outer side 17b of the rotating in opposite direction 43a first compressor piston 7a is compressed (top left).
  • This compression process is shown continued in Fig.42, wherein the compressed air / fuel mixture is forced 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 made a 180 ° rotation.
  • the ignition of the air / fuel mixture results in that the rear piston head 34d 'of the second working piston 8b receives a pressure pulse and the working piston 8b rotating in the second working piston web 12b is forwarded in the running direction 44b.
  • 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.
  • FIG. 44 shows the working pistons 8a, 8b moved forwards by a quarter turn in the working piston paths 12a, 12b in relation to their directions of travel 43b, 44b. It can also be seen how the front piston bottom 34c 'of the second working piston 8b is already in operation In the course of one of the ignition according to FIG. 43 preceding working cat, burned air / fuel or gas mixture drifts in front of it and pushes out through the exhaust opening 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 track 12a through the exhaust port 31 into the open.
  • FIGS. 50 and 51 each show an isometric sectional view of the compressor plane 27 equipped with fuel injection nozzles 27a, 27b and the working plane 10 equipped with spark plugs 26a, 26b.
  • Figures 50 and 51 correspond to a snapshot, which at the time of 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 has been made.
  • both the compression of the air / fuel mixture in the compressor piston path IIb and the expansion or ignition of this compressed air / fuel mixture in the working piston path 12b are due to the opposite directions of running of the respective compressor and power piston 7a, 7b arranged behind one another. 8a, 8b adjacent to the same trajectory crossing regions, in the present illustrations, respectively adjacent to the upper trajectory crossing region 62.
  • the comments made to adjust the opening angle to FIGS. 48 and 49 apply analogously to the present FIGS. 50 and 51.
  • 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 paths IIa, IIb could be made somewhat narrower than shown 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 IIa, IIb could also be increased in relation to their width.
  • the compressor piston inner walls 19a, 19a ' can be provided with one or more depressions 148, as shown schematically in FIG.
  • the recesses 148 each lead from one outside the lower one Web intersection region 62 'lying, the end portion 64a, 65a of the concave curvature 64, 65 adjacent region of the compressor piston inner wall 19a, 19a' to each of these compressor piston inner wall 19a, 19a 'adjacent concave vault 64, 65.
  • the recesses 148 are provided in order to prevent a "dead" closing angle volume X shown in FIG.
  • the front piston head 34d of the second compressor piston 7b has passed or closed the cross section of the inlet mouth 71a of the second overflow channel 71, so gives a small, in itself negligible (since only about 0.5% of the intake volume constituting), but possibly the movement of the compressor piston 7a, 7b braking "dead” Sch thoroughlywinkelvolumen X, which between the front piston crown 34c of the second compressor piston 7b, the compressor piston outer side 17b of the first compressor ⁇ piston 7a and the compressor piston inner wall 19a '(see Fig. 46).
  • a "dead" closing angle volume X im is included between the front piston bottom 34a of the first compressor piston 7a, the compressor piston outer side 17b 'of the second compressor piston 7b and the compressor piston inner wall 19a' Region between the overflow channel inlet mouth 70a of the first transfer port 70 and the concave curvature 65th Thanks to the provision of the depressions 148 shown in FIG.
  • the compressed air / fuel mixture located in the "dead" closing angle volume X can now move into an expansion volume formed by the depressions 148 and from there into the region in front of the concave bulges 64, 65 of the compressor piston webs IIa, IIb or in the web crossing region 62, 62 '
  • This expanded air / fuel mixture is pushed back into one of the compressor piston paths IIa, IIb during the next intake cycle, ie in the present illustration according to FIG. 46 from the front piston bottom 34c of the second
  • the expansion volume formed by the depressions 148 must in this case be sufficiently large in order to prevent autoignition of the air / fuel mixture expanding into the depression 148 as a result of high compression ,
  • each compressor or working piston 7, 8 is guided in each compressor or working piston path IIa, IIb, 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 to arrange in the compressor or working piston paths IIa, IIb, 12a, 12b respectively several, for example, two or three compressor or piston 7, 8.
  • four compressor / working pistons 7, 8 would therefore revolve both in the compressor plane 9 and in the working plane 10.
  • FIGS. 53-55 shown proposed arrangement for piston cooling.
  • a number of inclined or / and curved ribs 152 are provided between the piston walls 54, 55 of the compressor / power pistons 7, 8.
  • 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 sections 152a, 152b of the ribs 152 are formed by the outer side 17b, 17b ', 18b, 18b' and the inner side 17a, 17a ', 18a, 18a' of the compressor / power piston 7a, 7b, 8a, 8b limiting side surfaces 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 one Extension 163 of the compressor / working piston 7a, 7b, 8a, 8b.
  • the cooling air 155 is first sucked in through an air filter 154 from an area outside the housing and through one of the two
  • Inlet opening 166 passing ribs 152 and the of the
  • Ridges 152 formed passageways 162 are in this case surrounded by cooling air 155 or flushed.
  • the cooling air 155 After passing through the working pistons 8a, 8b, the cooling air 155 is conveyed in the axial direction through a passage opening 159, shown in FIG. 54 and formed through a passage section 153, to the compressor piston paths IIa, IIb behind it.
  • the cooling air 155 again enters the compressor piston paths IIa, IIb in the rail crossing region 62, 62, wherein the ribs 152 of the compressor pistons 7a, 7b passing through the throughflow opening 159 during the rotation of the compressor pistons 7a, 7b or through the passageways 162 formed by the ribs 152 be lapped or flushed with cooling air 155.
  • an outlet opening 167 is provided on the side of the compressor piston paths IIa, IIb.
  • 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 opening 159 - as well as the inlet opening 166 - is arranged centrally between the piston paths IIa and IIb or 12a and 12b, so that by means of a single passage opening 159 or inlet opening 166 both adjacent compressor pistons 7a, 7b or working piston 8a, 8b are fed with cooling air 155.
  • the passage opening 159 is - as well as the inlet opening 166 - between the respective compressor / working piston paths IIa, IIb, 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 IIa, IIb, 12a, 12b into the cooling air 155.
  • the passage opening 159 or the inlet opening 166 are thus so arranged in the lower rail crossing region 16 'that they are only swept by the cavities 53 and the passageways 162 of the compressor / piston 7a, 7b, 8a, 8b and the piston inside and outside 17a, 17b, 17a ', 17b', 18a, 18b, 18a ', 18b', 19a, 19b, 19a ', 19b' 20a, 20b, 20a ', 20b' not surmounted.
  • the through 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 4a in which neither the explosion pressure occurring in the compressor or working piston paths IIa, IIb, 12a, 12b nor the expansion pressure nor the compression pressure / Fuel mixture can push into the area in which the cooling air 155 is guided.
  • An ideal area for the arrangement of the passage opening 159 is according to FIG.
  • 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 / piston 7a, 7b, 8a, 8b makes it necessary that the intake of fresh air to be compressed and the exhaust of combusted air-fuel mixture no longer axially, but from the side the outer walls 19b, 19b ', 20b, 20b' of the compressor or working piston paths IIa, IIb, 12a, 12b, for example, tangential to the compressor or working piston paths IIa, IIb, 12a, 12b in the web crossing region 62, 62 'takes place.
  • the scenario prevents the working pistons 8a, 8b from sweeping over the hot exhaust gas during the sweeping of an exhaust opening 31 running (for example according to FIG.
  • Compressor level 9 and the working level 10 arranged
  • Reversing gear 66 is not linear or axial as shown in Fig.54, but curved from the working plane 10 in the
  • Compressor level 9 must run.
  • FIG. 1 Another measure for optimizing the cooling air flow is shown in FIG. As can be seen in this figure, when the piston bottoms 34b, 34c of the compressor pistons 7a, 7b meet in the web crossing region 62 ', 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.
  • pressed the gap 168 and thus displaced in the gap 168 air-fuel mixture is displaced in the outflowing cooling air flow are on the compressor piston webs IIa, IIb facing side surface 157 of the working piston 8a, 8b sections, for example. arranged plate-shaped closure walls 169 arranged. In the present exemplary embodiment, these closure walls 169 are orthogonal to the outer sides 18b, 18b 'and the inner sides 18a, 18' of the working pistons 8a, 8b or run flat relative to their lateral surfaces 157.
  • 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 formed in the course of the compressor piston rotation between the piston heads 34b, 34c of the compressor piston 7a, 7b gap 168 through 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 air-fuel mixture trapped in the gap 168 between the compressor pistons 7a, 7b is therefore not forced outward - it being noted that the pressure loss would be extremely low even in such a case, since the gap 168 formed between the compressor piston bottoms 34b, 34c forms the through-opening 159 happened in the thousandth of a second range - but remains in the compressor piston lines IIa, IIb, where it mixes again with the Ansauglauft 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 can be used a series of flat, waffle-shaped notches 171 may be provided, which is a possible, from the
  • Piston webs IIa, IIb, 12a, 12b interrupting laminar flow of the air-fuel mixture by turbulence interrupts
  • 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, 7b, 8a, 8b limiting side surfaces 157, 158 may be provided (also shown in Fig.57).
  • the notches 171, 172 for example, in the form of rectangular or diamond-shaped recesses, are shown in FIG. 57 in the form of a plurality of staggered rows substantially concentric with the axes of rotation 14, 15 along the sealing areas 170 and 170, respectively. along the piston outer sides 17b, 17b ', 18b, 18b' adjacent side surfaces 157 arranged.
  • FIGS. 58-60 A further development of the rotary piston engine 1 is illustrated with reference to FIGS. 58-60.
  • Fig. 58 shows a
  • Compressor piston path IIb is redirected.
  • an indentation 174 is provided on the inner wall 19a 'of the second compressor piston track IIb 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 recess 174 has on the compression of the air Fuel mixture has no influence, as it is located in the intake of the compressor piston lines IIa, IIb.
  • the inner wall 19a of the first compressor piston path IIa is also provided with a recess 174 in a region immediately adjacent to the rail 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 has exhaust gas from the second working piston track 12b in FIG Direction of the exhaust opening 31 ausschiebt. Also from the first working piston path 12a flows at this time already pushed from the piston head 34a 'of the counter-rotating first working piston 8a exhaust gas to Auspuff ⁇ réelle 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 IIb is also provided with a semicircular indentation 175 in an area immediately adjacent to the track crossing area 16 'or the concave curvature 65.
  • housing cover 80a, 80b 78 Holes in housing cover 80a, 80b 78 Bolt elements 80a Housing cover on suction side 80b Housing cover on exhaust side
  • Oil chamber closure plate 144 Sealing element for oil chamber closure plate 143

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  • General Engineering & Computer Science (AREA)
  • Compressors, Vaccum Pumps And Other Relevant Systems (AREA)

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.
PCT/EP2008/058659 2007-07-20 2008-07-04 Moteur à pistons rotatifs WO2009013110A1 (fr)

Priority Applications (2)

Application Number Priority Date Filing Date Title
AT08785918T ATE556194T1 (de) 2007-07-20 2008-07-04 Kreiskolbenmotor
EP08785918A EP2171212B1 (fr) 2007-07-20 2008-07-04 Moteur à pistons rotatifs

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
ATGM454/2007 2007-07-20
AT0045407U AT10063U1 (de) 2007-07-20 2007-07-20 Kreiskolbenmotor

Publications (1)

Publication Number Publication Date
WO2009013110A1 true WO2009013110A1 (fr) 2009-01-29

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EP (1) EP2171212B1 (fr)
AT (2) AT10063U1 (fr)
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Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN104040115A (zh) * 2011-08-02 2014-09-10 品牌产品Ipr控股两合有限公司 尤其具有围绕点燃室循环的旋转活塞的旋转活塞式发动机
CN113476915A (zh) * 2021-07-19 2021-10-08 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

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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
DE19527277A1 (de) 1994-11-17 1996-08-01 Josef Lipinski Brennkraftmaschine mit umlaufenden Kolben als 4-Scheiben-Kreiskolbenmotor
WO2002070878A1 (fr) 2001-03-07 2002-09-12 Abiti Ab Moteur rotatif

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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
DE19527277A1 (de) 1994-11-17 1996-08-01 Josef Lipinski Brennkraftmaschine mit umlaufenden Kolben als 4-Scheiben-Kreiskolbenmotor
WO2002070878A1 (fr) 2001-03-07 2002-09-12 Abiti Ab Moteur rotatif

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CN104040115A (zh) * 2011-08-02 2014-09-10 品牌产品Ipr控股两合有限公司 尤其具有围绕点燃室循环的旋转活塞的旋转活塞式发动机
CN113476915A (zh) * 2021-07-19 2021-10-08 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

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