EP1856375B1 - Moteur à pistons oscillants - Google Patents

Moteur à pistons oscillants Download PDF

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Publication number
EP1856375B1
EP1856375B1 EP05822093A EP05822093A EP1856375B1 EP 1856375 B1 EP1856375 B1 EP 1856375B1 EP 05822093 A EP05822093 A EP 05822093A EP 05822093 A EP05822093 A EP 05822093A EP 1856375 B1 EP1856375 B1 EP 1856375B1
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EP
European Patent Office
Prior art keywords
piston
pistons
housing
oscillating
axis
Prior art date
Legal status (The legal status 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 status listed.)
Not-in-force
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EP05822093A
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German (de)
English (en)
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EP1856375A1 (fr
Inventor
Herbert Hüttlin
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HUETTLIN, HERBERT
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Individual
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Priority claimed from DE102005010775A external-priority patent/DE102005010775B3/de
Priority claimed from DE102005024751.2A external-priority patent/DE102005024751B4/de
Application filed by Individual filed Critical Individual
Priority to PL05822093T priority Critical patent/PL1856375T3/pl
Publication of EP1856375A1 publication Critical patent/EP1856375A1/fr
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Publication of EP1856375B1 publication Critical patent/EP1856375B1/fr
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
    • F01C9/00—Oscillating-piston machines or engines
    • F01C9/005—Oscillating-piston machines or engines the piston oscillating in the space, e.g. around a fixed point

Definitions

  • the invention relates to a rotary piston machine, comprising a housing, in which a first and at least a second piston are arranged, which can rotate together in the housing about a housing-fixed axis of rotation, and when revolving about the axis of rotation about a perpendicular to the axis of rotation and through the housing center extending pivot axis to each other in opposite directions perform reciprocal pivotal movements, wherein the first piston has a first end surface and the at least second piston one of the first end surfaces facing the second end surface, wherein the end surfaces define a working chamber, wherein the pistons are arranged so that the axis of rotation the working chamber runs.
  • Such a reciprocating engine is from the document FR 2 322 282 A known.
  • Oscillating piston engines and in particular a rotary piston engine according to the present invention can be used as internal combustion engines (internal combustion engines), as pumps or as compressors.
  • An oscillating piston engine according to the present invention is preferably used as an internal combustion engine and described as such in the present specification.
  • a working chamber is formed in each case, so that the known "oscillating piston engine” has two working chambers. Both working chambers, which are arranged diametrically opposite with respect to the housing center are, zoom in and out in the same direction in the reciprocating pivotal movement of the piston.
  • the pistons of these known reciprocating engines are arranged in the housing so that they are perpendicular to the axis of rotation in its TDC position in which the volumes of the two working chambers are minimal. In this position, the centrifugal forces acting on the piston are maximum when the piston is rotated about the axis of rotation. This leads to the fact that at high speeds, the expansion or the pivoting apart of the pistons must take place against the centrifugal forces, because the centrifugal forces counteract the Wegschwenkenden movement of the pistons.
  • the working chambers are always outside and perpendicular to the axis of rotation in this oscillating piston engine.
  • the pistons of the known oscillating piston machines essentially have the shape of a ball wedge, and the geometry of the working chambers is correspondingly the same.
  • the present invention aims to provide a deviating from the above-described concept of the known oscillating piston engine new concept of a rotary piston engine.
  • a known oscillating piston machine has according to a first embodiment, two pivot pistons, which are arranged in a spherical housing.
  • the two pistons rotate together around a housing-fixed axis of rotation. During the orbital movement of the two pistons about the axis of rotation, they perform pivoting movements about an axis perpendicular to the axis of rotation extending pivot axis.
  • the two pistons are arranged in the housing so that the axis of rotation passes through the working chamber, which is formed by two mutually facing end surfaces of the two pistons.
  • a total of four pistons are arranged in the housing.
  • the invention has for its object to provide a new concept for a rotary piston machine of the type mentioned.
  • this object is achieved in terms of the aforementioned reciprocating piston engine in that the first and the at least second piston are slidably mounted in a piston cage which is arranged in the housing concentric to the axis of rotation about this, wherein the piston cage with respect to the first and at least second piston the rotational movement is rotationally fixed about the axis of rotation, and that the piston cage approximately perpendicular to the axis of rotation has a bore in which the first and at least second piston partially and slidably received therein, and which limits the working chamber in the circumferential direction.
  • the new concept of the oscillating piston engine according to the invention therefore consists in arranging the at least two pistons so that the at least one working chamber is not perpendicular to the axis of rotation but rather to the axis of rotation or about the axis of rotation.
  • the limit to the working chamber the centrifugal forces acting on the two pistons when revolving around the axis of rotation are less due to the smaller spacing of the pistons from the axis of rotation and also act in the direction of disengagement of the two pistons, ie the centrifugal forces support the working cycle of expansion.
  • the centrifugal forces occurring perpendicular to the axis of rotation during rotation of the pistons about the axis of rotation thus support the expansion of the at least one working chamber.
  • the first and the at least second piston are slidably mounted in a piston cage, which is arranged in the housing concentric to the axis of rotation about this, wherein the piston cage with the first and at least second piston with respect to the rotational movement about the rotational axis is rotatably connected.
  • the piston cage and the first and at least second piston thus form the "inner machine” or the “inner engine” of the oscillating piston engine.
  • the sliding bearing of the two pistons in the piston cage serves for the pivotal movement of the two pistons about the pivot axis, while the pistons, due to their rotation with respect to the rotational movement about the rotational axis, rotate together with the piston cage with the latter around the axis of rotation.
  • the piston cage can now advantageously serve as a drive or driven member.
  • the piston cage has approximately perpendicular to the axis of rotation on a bore in which the first and at least second piston partially and slidably received therein, and which limits the working chamber in the circumferential direction.
  • the bore thus defines together with the two mutually facing end surfaces of the first and at least second piston, the at least one working chamber of the oscillating piston engine.
  • the geometry of the bore of the piston cage is also selected, for example circular or, as likewise mentioned above, oval or of another shape corresponding to the shape of the end faces of the pistons.
  • a working chamber corresponding to a curved cylinder or a toroidal section is formed.
  • the pistons are then preferably sealed against the wall of the bore of the piston cage by means of seals, which in the case of a circular bore and circular end surfaces are advantageously designed as adapted to the shape of the working chamber piston rings.
  • first and second end faces of the first and at least second pistons are circular.
  • the first and at least second piston at least in the region which adjoins their end faces, cylindrical and thus very similar in this area classic piston reciprocating engines.
  • An advantage that results from this is that as seals for the two pistons piston rings, if necessary with appropriate curvature, can be used, so that can be used here on long-standing experience in solving sealing problems in reciprocating engines.
  • the through the two end surfaces The first and at least second piston limited working chamber has in this embodiment, the geometry of a bent about the pivot axis of the cylinder or Toroidabites.
  • a deviating geometry for example an oval shape, can be selected, which contributes to an enlargement of the at least one working chamber, in particular when the interior of the housing has ball symmetry.
  • first and the at least second piston are formed substantially arcuate.
  • first and at least second pistons may be limited to the area adjacent their end surfaces, i. Facing away from the end faces outer sides of the piston can, as will be described hereinafter, are used as functional elements for the control of the piston for deriving the pivotal movement of the orbital motion of the piston and to have other shapes.
  • first piston and / or the at least second piston at least one running member, which is guided during rotation of the first and / or at least second piston along a correspondingly shaped cam, to the pivoting movements of the first and at least second piston generate, with the cam on Housing is arranged with respect to the axis of rotation at least approximately maximum distance.
  • a comparable control mechanism for the pivoting movements of the piston is provided, but there is the control cam with a smaller distance to the axis of rotation in the vicinity of the end faces of the housing.
  • the advantage of the greater spacing of the cam from the axis of rotation is improved lever ratios to derive the pivotal movements of the at least two pistons from the orbital motion about the axis of rotation.
  • the at least one running member is a ball which is rotatably mounted in a ball socket on a housing facing outside of the first and / or at least second piston, and if the control cam as a groove with a part-circular cross-section in the housing is formed, in which the ball partially engages.
  • Such a control mechanism which uses a ball as the at least one running member, has the advantage of optimized friction reduction of the control mechanism, since the ball in the ball socket of the at least one piston is freely rotatable, as well as in the groove in the housing, so that the ball Camber may follow due to their all-round rotation with particularly low friction.
  • the ball socket may be formed to hold the ball captive, or the ball may be lubricated by a lubricating film. which is provided by an oil lubrication, be held by adhesive forces in the ball socket.
  • both the first and the at least second piston on a running member in the form of a ball, which run in the same groove-shaped cam in the housing at a distance from each other.
  • this may be a roller, the running surface of which is formed part-circular transverse to the circumferential direction of the roller, wherein the roller is mounted on a shaft which is connected at the end to the first or second piston.
  • the cam is again preferably formed as a groove with a part-circular cross-section in the housing into which the roller partially engages.
  • the advantage of the design of the at least one running element as a roller or guide roller with shaft connection of the roller to the piston eliminates the oil adhesion of the ball to the piston necessary in the above-mentioned freely rotatable ball in all directions. Nevertheless, the entire width of the piston guide surfaces is used.
  • the bearing of the at least one roller on the shaft is preferably carried out via precision needle roller bearings, and the roller is in particular preferably releasably connected to the piston.
  • the piston cage is connected to at least one drive and / or output shaft, which runs parallel to the axis of rotation.
  • This refinement has the advantage that the oscillating-piston engine can be designed to be of compact overall construction, since there is no offset between the axis of rotation and the drive and / or output shaft. Furthermore, no transmission for transmitting the rotational movement of the piston cage to the drive and / or output shaft or vice versa is required.
  • the at least one drive and / or output shaft is arranged at a lateral distance from the axis of rotation and with the piston cage via at least one gear assembly, for example.
  • a sprocket or belt drive assembly is connected.
  • the advantage of this measure is that the at least one drive and / or output shaft with lateral offset to at least one working chamber, which is yes on the axis of rotation, is arranged.
  • This in turn means that for the at least one working chamber in the case of using the oscillating piston engine as an internal combustion engine to be provided ignition or glow plug with the drive and / or output shaft does not collide.
  • the fuel injection nozzle and optionally inlet and outlet nozzles can also be arranged on the front side of the housing.
  • combined spark plug injector arrangements can be provided.
  • a channel passes through the piston cage, which opens on the one hand in the bore and on the other hand leads to the housing to communicate depending on the rotational position with an inlet or with an outlet opening in the housing.
  • the piston cage acts by means of the aforementioned channel or opening as a kind of valve for the inlet and outlet openings in the housing. It is therefore not necessary to provide the inlet and outlet openings in the housing with separate valves, nor to provide for the time of opening or closing a complex control of the valve, as is the case with classical reciprocating engines. Enabling the inlet and outlet ports to admit combustion air and / or fuel and vent burnt combustion mixture takes place in the correct cycle automatically by the orbital movement of the piston cage around the axis of rotation.
  • the piston cage has at least one channel for a medium, in particular cooling / lubricating medium, which extends at least partially around and through the interior of the piston cage.
  • the piston cage advantageously performs another function, namely the supply of all moving parts within the housing with a cooling and / or lubricating medium.
  • the supply of a cooling / lubricating medium can take place via connections arranged on the housing, in which case the at least one channel preferably extends on the outside of the piston cage as an annular channel, so that the at least one channel always communicates with the supply connections.
  • a bore passes through the piston cage at the level of the pivot axis in its direction, which bore preferably widens toward its ends.
  • This hole is advantageously used as a further coolant / lubricant channel, which contributes to a particularly intensive circulation of such a cooling / lubricating medium, since this bore extends perpendicular to the axis of rotation and thus the cooling / lubricating medium currently located therein when the piston cage rotates about the axis of rotation Centrifugal forces are applied to move the cooling / lubricating medium towards the flared ends of the bore. This advantageously occurs a ventilation effect on the circulation of the cooling / lubricating medium.
  • a third and fourth piston are arranged in the housing, which are pivotable about the same pivot axis or a different pivot axis and can rotate with the first and second pistons about the axis of rotation and define a second working chamber.
  • the four pistons are arranged so that the first and second working chamber when rotating the piston about the axis of rotation in the same direction zoom in and out.
  • This design contributes to the fact that the four pistons represent a mass-balanced system in each circulating and pivoting position.
  • the first and second pistons and the third and fourth pistons are arranged with respect to the axis of rotation so that the pivotal movements of all pistons take place in the same plane.
  • the two working chambers are in a section along the axis of rotation and perpendicular to the pivot axis always in one and the same plane.
  • first and second pistons and the third and fourth pistons are arranged with respect to the axis of rotation such that the pivoting movements of the first and second pistons in a first plane and the pivotal movements of the third and fourth pistons in a second plane, wherein the first and the second plane are rotated relative to each other by an angle other than 0 ° with respect to the axis of rotation.
  • the two working chambers formed by the four pistons are not in a common plane as in the aforementioned embodiment, but are offset from each other by an angle other than 0 ° with respect to the axis of rotation.
  • This has the advantage over the aforementioned embodiment that the above-mentioned control curve or in the case of four pistons two cams and guided therein running organs, which are preferably designed as balls, must not have their end point in or before the orthogonal to the axis of rotation but can extend beyond the orthogonal, since due to the offset of the two pairs of pistons to each other, the running members in the UT position, ie at maximum open working chambers, can not collide with each other, since the pairs of pistons are mutually rotated by an angle not equal to 0 °.
  • the maximum volume of the two working chambers (UT position of the piston) can be increased due to a larger opening angle of the two piston pairs.
  • the piston cage extends on both sides of the pivot axis or pivot axes and also receives the third and fourth piston.
  • the piston cage receives all four pistons.
  • the piston cage if this is provided for the first and second pistons as described above, for the third and fourth piston also has a bore in which the third and fourth pistons slidably mounted and with respect to the rotational axis with the piston cage are connected, said bore then limits together with the end surfaces of the third and fourth piston, the second working chamber.
  • a housing inner wall of the housing is substantially spherical.
  • a housing inner wall of the housing is oblong in the direction of the axis of rotation along a plane which includes the axis of rotation.
  • “Oblong” here means that the housing of the oscillating piston engine consists of two halves of the ball between which an elongated in the direction of the axis of rotation section is interposed.
  • the oblong shape of the housing inner wall of the housing advantageously opens up the possibility of providing the following preferred embodiments.
  • a pivotable about the pivot axis hollow pin is arranged, which has in its wall an opening which communicates depending on the rotational position of the hollow pin with the first working chamber or optionally with the second working chamber.
  • This hollow pin can be advantageously used to supply fresh air, in particular pressurized fresh air, via the provided in the hollow pin circumferentially limited opening in the working chamber, or if two working chambers are provided, alternately in the two working chambers.
  • combustion air can be passed under a form in the working chambers, whereby a higher compression of the fuel-air mixture in the working chambers can be achieved.
  • the oscillating piston engine is particularly suitable as a diesel engine.
  • the hollow pin is connected to a gear which, when the pistons rotate about the axis of rotation, sets the hollow pin in rotation about the pivot axis.
  • the transmission has a worm gear connected to the hollow pin, which meshes with at least one toothing arranged on the housing, which extends around the axis of rotation.
  • Such a transmission is structurally particularly simple, can be accommodated without increased space in the housing and with appropriate design of the worm teeth, the rotational speed of the hollow pin can then be adjusted depending on the speed of rotation of the piston about the axis of rotation.
  • Fig. 1 to 10 such as Fig. 11 and 12 is a provided with the general reference numeral 10 oscillating piston engine shown in various views. Further details of the oscillating piston engine 10 are in Fig. 13 to 15 shown.
  • the oscillating piston engine 10 is designed as an internal combustion engine in the present embodiment.
  • the oscillating piston engine 10 has a housing 12, which is composed of two housing halves 14 and 16.
  • the housing halves 14 and 16 each have a flange 18a and 18b, via which the housing halves 14 and 16 are detachably connected to each other.
  • inlet ports 20 and 24 are arranged for fresh air / fuel with respect to the center of the housing, the openings of which pass through the housing (see. Fig. 9 ).
  • outlet 22 and 26 are provided.
  • the inlet ports 20 and 24 serve to supply fresh air or combustion air, while the outlet ports 22 and 26 are used for ejecting combusted fuel-air mixture.
  • the inlet ports 20 and 24 are each assigned a port for a fuel injection nozzle, as shown for the inlet port 24 with a port 25 (see also Fig. 9 ). In Fig. 2 a corresponding port 21 for the inlet port 20 is shown.
  • a plurality of terminals 28 to 38 for the supply and discharge or circulation of a cooling / lubricating medium through the interior of the oscillating-piston engine 10 are arranged on the housing.
  • a housing inner wall 39 is substantially spherical or has ball symmetry, such as for example Fig. 3 evident.
  • pistons 40 to 46 are arranged, which together in the housing 12 about an axis of rotation 48 according to an arrow 49 (FIG. Fig. 3 ) can run around.
  • the pistons 40 to 46 perform a pivoting movement superimposed on the revolving movement about a pivot axis 50 which is common to all four pistons 40 to 46 between two end positions, the one end position in FIG Fig. 3 (so-called UT position), and the other end position in Fig. 6 (so-called TDC position) is shown.
  • Both the axis of rotation 48 and the pivot axis 50 which are to be understood as geometric axes, pass through the center of the housing 12 of the spherical housing. Furthermore, the pivot axis 50 is always perpendicular to the axis of rotation 48, but runs around the latter, however, according to the orbital motion of the pistons 40 to 46 about the axis of rotation 48.
  • pistons 40 to 46 are each two pistons with respect to the pivot axis 50 diametrically opposite, in each pivotal position of the pistons 40 to 46, which are the pistons 40 and 44 on the one hand and the pistons 42 and 46 on the other.
  • the pistons 40 to 46 are individually supported in the housing 12, i. not rigidly connected in pairs.
  • Each of the pistons 40 to 46 has an end surface, that is, the piston has an end surface 52, the piston 42 has an end surface 54, the piston 44 has an end surface 56 and the piston 46 has an end surface 58.
  • Each facing end surfaces which in the present case, the end surfaces 54 and 56 of the pistons 42 and 44 and the end surfaces 52 and 58 of the pistons 40 and 46, each defining a working chamber 60 and 62, which serve as combustion chambers.
  • the axis of rotation 48 passes through both working chambers 60, 62, preferably centrally in each position of the pistons.
  • each piston 40 to 46 a running member 64 (piston 40), 66 (piston 42), 68 (piston 44) and 70 (piston 46) on.
  • the running members 64 to 70 are balls, each in a ball socket 72, as in Fig. 15 is shown for the piston 40, are mounted, wherein the ball socket is arranged on an outer side of the respective piston 40 to 46, which faces the housing inner wall 39.
  • the balls 64 to 70 can, as in Fig. 3 is loosely supported in the ball pans 72 and held there by adhesion by means of a lubricating film, the ball pans 72 then not extending beyond the diameter of the balls 64 to 70, or the ball pans can, as in Fig. 15a ) and b), by means of an extension 74 extending beyond the ball diameter, the balls 64 to 70 hold in a form-fitting and thus captive manner.
  • the balls 64 to 70 are freely rotatable in the ball sockets 72 in all directions about their respective ball center.
  • the running members or balls 64 to 70 are assigned two control cams in which the balls 64 to 70 run. More specifically, the balls 64 and 70 of the pistons 40 and 46 associated with a first control cam 76 which is formed as a groove with a part-circular cross-section in the housing inner wall 39. A corresponding control cam 78 is assigned to the running members or balls 66 and 68 of the pistons 42 and 44.
  • the balls 64 and 70 thus run in the same control cam 76, and the balls 66 and 68 in the same control cam 78.
  • the balls 64 and 70 on the one hand and the balls 66 and 68 on the other are each offset from each other with respect to the axis of rotation 48 by 180 °.
  • the cams 76 and 78 are arranged with respect to the axis of rotation 48 at least approximately the maximum distance, as from Fig. 3 shows that they are located almost at the height of the pivot axis 50.
  • the cams 76 and 78 are generally substantially orthogonal to the axis of rotation 48th
  • the pistons 40 to 46 are mounted in the housing 12 in a piston cage 80 which revolves around the axis of rotation 48 together with the pistons 40 to 46, which is described in more detail below with further details of the pistons 40 to 46.
  • a piston cage 80 which revolves around the axis of rotation 48 together with the pistons 40 to 46, which is described in more detail below with further details of the pistons 40 to 46.
  • the piston cage 80 is shown in non-sectional views.
  • the piston cage 80 is in the embodiment shown, and preferably a one-piece component, but instead of a one-piece design but also a multi-piece design is conceivable.
  • the piston cage 80 extends along the axis of rotation 48 over the entire length of the housing 12, wherein shaft extensions 86 and 88 of the piston cage 80 protrude from the housing.
  • the piston cage 80 in each case has a main bearing section 82 or 84 adjoining the shaft extensions 86 and 88 on, via which the piston cage 80 is rotatably mounted in the housing 12 about the axis of rotation 48.
  • the bearing sections 82 and 84 are connected at the center of the housing via a middle section 90, which has a pin-like section 92 extending along the pivot axis 50, on which the pistons 40 to 46 are mounted toward the center of the housing or to the pivot axis 50.
  • the piston cage 80 has two bores 94 and 96, in which the pistons 40 to 46 are slidably mounted. More specifically, in the bore 94, the pistons 40 and 46 and in the bore 96, the pistons 42 and 44 slidably mounted.
  • the holes 94 and 96 are circular in shape, and accordingly, the end surfaces 52 to 58 of the pistons 40 to 46 are also formed circular.
  • the pistons 40 to 46 are mounted in the bores 94 and 96 by means of piston rings for sealing the working chambers 60 and 62, as in Fig. 3 for the piston 40 with seals 98 (outside) and 100 (inside) is shown.
  • the pistons 42 to 46 have according to Fig. 3 corresponding seals on its radial outer side and its radial inner side.
  • the bores 94 and 96 define, together with the end surfaces 52 to 58, the working chambers 60 and 62.
  • the pistons 40 to 46 rotatably connected to the piston cage 80, so that the pistons 40 to 46 rotate together with the piston cage 80 about the axis of rotation 48, while the pistons 40 to 46 according to their pivotal movements to the pivot axis 50 in the holes 94 and 96 are slidably movable to the individual Performing cycles of the inlet, compression, expansion and ejection.
  • the pistons 40 to 46 are substantially as in FIG Fig. 15 is shown arcuately formed, and also the working chambers 60 and 62 have approximately the shape of a curved or curved cylinder, wherein the curvature is concentric with the pivot axis 50.
  • piston cage 80 The arrangement of piston cage 80, the piston 40 to 46 together with the running members 64 to 70 forms the "inner engine” of the oscillating piston engine 10, i.
  • This arrangement includes all moving parts of the oscillating-piston engine 10.
  • a plurality of channels 102 and 104 respectively, which extend circumferentially and through the interior of the bearing portions 82 and 84 of the piston cage 80 and which communicate with the already mentioned above terminals 28, 30 and 36, 38, so that through the channels 102, 104, a cooling / lubricating medium for cooling and lubricating the piston cage 80 can be passed.
  • the channels 102 and 104 serve primarily for cooling the internal engine in the vicinity of the working chambers 60, 62.
  • Cooling / lubricating medium channels 106 and 108 are also formed in the housing 12, wherein in the piston cage 80 in the direction of the pivot axis 50, a bore 110 passes through its central portion 90, which also serves as a cooling / lubricating medium channel.
  • a cooling or lubrication of the pistons 40 to 46 and the running members 64 to 70 is accomplished in the center of the inner motor.
  • the lubricating film thereby formed also serves to hold the running members 64 to 70 in the ball sockets 72 of the pistons 40 to 46 by adhesion, unless as shown in FIG Fig. 15 is shown, this is accomplished by a positive connection.
  • the bore 110 widens at its two ends like a trumpet, in order to improve the distribution of the cooling / lubricating medium in the center of the housing 12 yet.
  • Fig. 9 and 10 are two further holes or channels 114 and 116 are provided in the piston cage 80, which open on the one hand in the bores 94 and 96, and on the other hand to the housing inner wall 39, at the level of the inlet and outlet ports 20 and 22 and 24 and 26 lead.
  • the channels 114 and 116 serve to engage in a rotational position of the piston cage 80 about the axis of rotation 48 through the inlet port 20 and 24, a fuel-air mixture in the working chambers 60, 62, and in a different rotational position burned fuel-air mixture through the outlet 22 and 26 eject.
  • In the other rotational positions of the piston cage 80 closes these nozzles.
  • the piston cage 80 thus simultaneously assumes the function of a valve for releasing and closing the connecting pieces 20 to 26.
  • each have a spark plug 118 and 120 are provided, which are arranged on the rotation axis 48 and rotate together with the piston cage 80 about this. Electrical leads (not shown) are connected in accordance with example by slip rings with the spark plugs 118 and 120.
  • the candles 118 and 120 are accordingly glow plugs.
  • the offset by 180 ° with respect to the axis of rotation 48 arrangement of the connecting pieces 20 and 22 relative to the connecting pieces 24 and 26 serves that at least in one of the working chambers 60 and 62 when rotating the piston 40 to 46 about the axis of rotation 48 by 360 ° always an expansion process he follows.
  • a working cycle of expansion is taking place in the working chamber 60
  • a working cycle of the discharge of burned fuel-air mixture takes place in the working chamber 62, and vice versa.
  • each of the working chambers 60 and 62 has once had the four power strokes of intake, compression, expansion and ejection.
  • Fig. 10A is a slightly modified embodiment of a rotary piston engine 10 'shown, which differs from the oscillating piston engine 10 only in that the holes 94' and 96 'in the piston cage 80' and correspondingly the end surfaces 52 'and 54' (the same applies to the end faces, not shown 56 'and 58') not circular, but as in Fig. 10A for example, are shown, oval or elliptical. As a result, the working chambers 60 'and 62' can be enlarged relative to the circular configuration.
  • FIG. 16 and 17 Yet another embodiment of an oscillating piston engine 10 "is shown, which differs from the oscillating piston engine 10 or oscillating piston engine 10 'as follows.
  • the housing 12 of the oscillating piston engine 10 and the oscillating piston engine 10 has ball symmetry
  • the housing 12 "of the oscillating piston engine 10" is formed oblong. More specifically, the housing 12 "consists of two hemispheres 13" and 15 “, between which is interposed an elongate portion 17" extending in the direction of the axis of rotation 48. In this way, the housing 12 "is pivoted in the direction of the axis of rotation 48" Version of the housing 12 longer, which allows the following measures.
  • a hollow pin 122 is arranged, which has an opening 124 in its wall.
  • the central portion 90 “has on the axis of rotation 48" two openings 126 and 128, with which communicates the opening 124 of the hollow pin 122 depending on its rotational position, wherein the opening 124 can communicate with only one of the openings 126 and 128.
  • the hollow pin 124 is "rotatably mounted about the pivot axis 50" in the central portion 90.
  • the rotational movement of the hollow pin 122 about the pivot axis 50 " is derived from the orbital motion of the piston cage 80" about the rotation axis 48 ".
  • the central portion 90" at one end has a gear 130 which has a worm toothing 132 firmly connected to the hollow pin 122 ,
  • the worm gear or worm wheel 132 meshes with a toothing 134 arranged concentrically about the axis of rotation 48, so that when the center section 90 "including the hollow pin 122 rotates about the axis of rotation 48, the worm toothing 132 and thus the hollow pin 122 are set in rotation about the pivot axis 50" ,
  • an inlet 136 is also provided for fresh air, which can be closed and opened by a conventional valve device 138, for example.
  • Fresh air in particular precompressed fresh air, can now be introduced into the interior of the hollow pin 122 through the inlet 136, and depending on the rotational position of the hollow pin 122 relative to the openings 126, 128, the fresh air is introduced into the working chambers 60 "or 62", and although in addition to the supply of fuel-air mixture through the connecting pieces 20 "and 24".
  • the oscillating piston engine 10 is a motor with so-called. Charging.
  • the worm toothing 132 and the toothing 134 are correspondingly designed so that the rotational movement of the hollow pin 122 about the pivot axis 50 "is synchronized with the piston positions of the pistons 40" to 46 "in a suitable manner
  • Working chamber 60 "or in the working chamber 62” should preferably then take place or the opening 124 should communicate with the respective opening 126 and 128 when the ignition of the through the inlet nozzle 20 "and 24" embedded fuel-air mixture just before its ignition
  • a 360 ° rotation of the hollow pin about the axis of rotation 48 should cause a 360 ° rotation thereof about the pivot axis 50.
  • the oscillating piston engine 10 "corresponds to the embodiments of the oscillating piston engine 10 or 10 ', so that reference is made to the description there.
  • FIGS. 18 to 21 a further embodiment of a rotary piston machine 210 and the details are shown.
  • parts that are the same or comparable to parts of the oscillating piston engine 10, 10 'and / or 10 "have been given the same reference numerals, but increased by 200.
  • the oscillating piston engine 210 includes a housing 212 describe such aspects of the oscillating piston engine 210, which differ from the previously described embodiments.
  • the oscillating piston engine 210 has four pistons 240 to 246 in the housing 212, wherein the pistons 240 and 246 are arranged as the first piston pair and the pistons 242 and 244 as the second piston pair with respect to the rotational axis 248 so that the pivoting movements of the pistons 240 and 246 in a first plane and the pivoting movements of the pistons 242 and 244 take place in a second plane, wherein the first and the second plane with respect to the rotation axis 248 relative to each other by an angle other than 0 °, and in the present embodiment by 90 ° to each other.
  • Fig. 19 is a pivot axis 250 of the piston 242 and 244 located perpendicular to the plane of the Fig. 19 runs while a pivot axis 251 of the pistons 240 and 246 perpendicular to the pivot axis 250 and thus in the plane in Fig. 19 runs.
  • Fig. 21 clearly, in which a piston cage 280 of the oscillating piston engine 210th with the piston 240 to 246 and these associated running members 264, 266, 268, 270 are shown in the form of balls in isolation.
  • Fig. 21 shown parts of the oscillating piston engine 210 together again form the inner motor of the oscillating piston engine 210th
  • the piston cage 280 differs correspondingly from the piston cage 80 of the oscillating piston engine 10 in that the bores 294 and 296 defining the working chambers 260 and 262 are orthogonal to one another.
  • FIG. 3 shows the pistons 40 to 46, as already described above, in their maximum opening angle or in their BDC position in which the working chambers 60 and 62 assume their maximum volume.
  • Fig. 19 shows correspondingly the pistons 240 to 246 in their maximum opening angle with respect to the pivot axes 250 and 251, ie also in its UT position.
  • the working chambers 260, 262 of the oscillating piston engine 210 increase and decrease in the same direction. For example. when the working chamber 260 expands in the course of a power stroke, the working chamber 262 expands to draw in new fresh gas. The two processes thus take place temporally simultaneously, but spatially offset by 90 ° to each other. It thus always and desirably opens and closes both working chambers 260, 262 at the same time.
  • inlet ports 220 and 224 are not arranged diametrically opposite one another, as in the case of the oscillating piston engine 10, with respect to the axis of rotation 248, but offset by 90 ° relative to one another.
  • outlet pipe 222 of which in Fig. 18 only the outlet of the working chamber 260 associated 222 can be seen.
  • Fig. 22 3 is a diagram illustrating the operation of the oscillating piston engine 210 with respect to the expansion, ejection, suction, and compression strokes in the two working chambers 260 and 262.
  • cams 276 and 278 are shown unwound, it follows from this illustration that the two cams 276 and 278 now serpentine parallel to each other, while the cams 76 and 78 of the oscillating piston engine 10 mirror symmetry with respect to a median plane through the housing center of the housing 12 are formed and arranged mirror-symmetrically perpendicular to the axis of rotation 48.
  • Fig. 22 is also symbolically a rectangle for the respective piston pair 240, 246 (working chamber 260) and the associated running members 264, 270 shown in the form of a pitch circle, wherein the running members 264, 270 run along the control cam 276. The same is shown for the second piston pair 242, 244 and their running members 264, 270 with respect to the control cam 278 and the working chamber 262.
  • FIG. 23 to 28 another embodiment of a rotary piston machine 310 is shown.
  • those parts of the oscillating piston engine 310 which are comparable to the corresponding parts of the oscillating piston engine 10 or 210 have been given the same reference numerals, increased by 300. Only the differences of the oscillating piston engine 310 to the oscillating piston engine 10 will be described below. If some parts of the oscillating piston engine 310 are not described in detail below, the description of the oscillating piston engine 10 or the oscillating piston engine 10 ', 10 "and / or 210 applies to these parts.
  • the output and / or drive shaft is not arranged concentrically on the axis of rotation 348, but at a lateral distance from it.
  • the piston cage 380 is provided on the face side and concentrically with the axis of rotation 348 with a ring gear 440, which meshes with a gear ring 442 connected in a rotationally fixed manner to the drive and / or drive shaft 387.
  • the piston cage may be provided on the end face opposite the sprocket 440 with a second sprocket 444.
  • the drive and / or output shaft 387 is formed continuously between its shaft extensions 386 and 388, so that a drive connection with the piston cage 380 is required only via one of the sprockets 440 and 444, as in Fig. 25 is shown.
  • Fig. 26 in contrast represents a modified embodiment in which the drive and / or output shaft between the shaft extensions 386 'and 388' is not continuous, but the shaft extensions 386 'and 388' are both about sprockets 442 and 446 with the sprockets 440th and 444 in connection.
  • This embodiment makes it possible, the wave extensions 386 'and 388' contrary to the representation in Fig. 26 also with an axis offset and / or with different gear ratios to each other to design. For example, one unit may be driven via one of the shaft extensions 386 'or 388', and the other is connected to the drive train of the vehicle.
  • the drive and / or output shaft 387 is not on the axis of rotation 348 about which the piston cage 380 and the pistons 340 to 346 therein rotate, the spark plugs 418 and 420 at a respective end-side housing cover 448 and 450 , So be mounted on non-rotating parts, and in particular do not rotate with the piston cage 380.
  • the housing covers 448 and 450 are part of the housing 312 removable.
  • injection nozzles 452 and 454 on the front-side housing covers 448 and 450 can serve the two working chambers 360 and 362 (cf. Fig. 24 ) are arranged.
  • inlet stubs 490, 492 for air and outlet stubs 494, 496 for burnt mixture can be provided on the front side of the housing cover 448 and 450.
  • oscillating piston engine 310 Another difference between the oscillating piston engine 310 and the previously described oscillating piston engines 10, 10 ', 10 "and 210 is the design of the running members 364 to 370 associated with the pistons 340 to 346.
  • the running members 364 to 370 are each formed as a roller, as will be described hereinafter with reference to the running member 364 in the form of the roller 456.
  • the roller 456 has a tread 458, which is part-circular transverse to the circumferential direction of the roller 456.
  • the roller 456 is connected via a pin 460 to the piston 340, wherein the roller 456 is rotatable about the pin 460 relative to the piston 340.
  • the shaft 460 extends parallel to the axis of rotation 348.
  • the roller 456 is rotatably mounted on the pin 460 thereto, preferably via a needle bearing, in particular a precision needle bearing.
  • the roller 456 is also releasably connected to the piston 340 via locking rings arranged at the end of the pin 460.
  • each running member 364 to 370 runs in the form of a respective roller 456 in a cam 376 and 378, respectively, which engage and partially engage the runners 364 and 370, respectively are guided.
  • the arrangement of the pistons 340 to 346 can be chosen contrary to the illustration also according to the arrangement of the pistons 240 to 246 of the oscillating piston engine 210, that is such that the pivot pistons 340 and 346 relative to the pistons 342 and 344 offset by 90 ° with respect to the axis of rotation 348 are arranged to each other.
  • the cams 376 and 378 as in the oscillating piston engine 210 with two wave crests and two troughs may be configured to achieve greater pivot strokes of the pistons 340-346, as already described with respect to the oscillating piston engine 210.

Claims (23)

  1. Moteur à pistons oscillants, comportant un carter (12 ; 212 ; 312), dans lequel sont montés un premier et au moins un deuxième piston (40, 46 ; 240, 246 ; 340, 346), qui peuvent tourner conjointement dans le carter (12; 212 ; 312) autour d'un axe de rotation (48 ; 248 ; 348) solidaire du carter, et qui, lors de leur rotation autour de l'axe de rotation (48 ; 248 ; 348), effectuent des mouvements de pivotement en va-et-vient dans le sens opposé l'un à l'autre autour d'un axe de pivotement (50 ; 251 ; 350), perpendiculaire à l'axe de rotation (48 ; 248 ; 348) et passant par le milieu du carter, le premier piston (40 ; 240 ; 340) comportant une première surface d'extrémité (52 ; 252 ; 352) et ledit au moins un deuxième piston (46 ; 246 ; 346) comportant une deuxième surface d'extrémité (58 ; 258 ; 358) orientée vers la première surface d'extrémité (52 ; 252 ; 352), lesdites surfaces d'extrémité (52, 58 ; 252, 258 ; 352, 358) délimitant une chambre de travail (60 ; 260 ; 360), les pistons (40, 46 ; 240, 246 ; 340, 346) étant disposés de telle sorte que l'axe de rotation (48 ; 248 ; 348) passe à travers la chambre de travail (60 ; 260 ; 360), caractérisé en ce que le premier et ledit au moins un deuxième piston (40, 46 ; 240, 246 ; 340, 346) sont montés de manière à pouvoir coulisser dans une cage de piston (80 ; 280 ; 380), qui est montée dans le carter (12 ; 212 ; 312) concentriquement à l'axe de rotation (48 ; 248 ; 348) de manière à pouvoir tourner autour de celui-ci, la cage de piston (80 ; 280 ; 380) étant assemblée de manière solidaire en rotation avec le premier et ledit au moins un deuxième piston (40, 46 ; 240, 246 ; 340, 346) pour le mouvement de rotation autour de l'axe de rotation (48 ; 248 ; 348), et en ce que la cage de piston (80 ; 280) comporte un alésage (94 ; 294) sensiblement perpendiculaire à l'axe de rotation (48 ; 248), dans lequel le premier et ledit au moins un deuxième piston (40, 46 ; 240, 246) sont reçus partiellement et de manière à y coulisser, et lequel délimite la chambre de travail (60 ; 260) dans la direction périphérique.
  2. Moteur à pistons oscillants selon la revendication 1, caractérisé en ce que la première et la deuxième surface d'extrémité (52, 58 ; 252, 258 ; 352, 358) sont réalisées avec une forme circulaire.
  3. Moteur à pistons oscillants selon la revendication 1 ou 2, caractérisé en ce que le premier et ledit au moins un deuxième piston (40, 46 ; 240, 246 ; 346) sont réalisés avec une forme sensiblement cintrée.
  4. Moteur à pistons oscillants selon l'une quelconque des revendications 1 à 3, caractérisé en ce que le premier piston (40 ; 240 ; 340) et/ou ledit au moins un deuxième piston (46 ; 246 ; 346) comporte au moins un organe mobile (64, 70 ; 264, 270 ; 364, 370) qui, pendant la rotation du premier et dudit au moins un deuxième piston (40, 46 ; 240, 246 ; 340, 346), est guidé le long d'une courbe de commande (76 ; 276 ; 376), conçue de manière correspondante, pour générer les mouvements de pivotement du premier et dudit au moins un deuxième piston (40, 46 ; 240, 246 ; 340, 346), la courbe de commande (7 ; 276 ; 376) étant disposée sur le carter (12 ; 212 ; 312) à une distance au moins à peu près maximale de l'axe de rotation (48 ; 248 ; 348).
  5. Moteur à pistons oscillants selon la revendication 4, caractérisé en ce que ledit au moins un organe mobile (64, 70 ; 264, 270) est une sphère, qui est montée rotative dans un coussinet (72 ; 272) sur une face extérieure, orientée vers le carter (12 ; 212), du premier et dudit au moins un deuxième piston (40, 46 ; 240, 246), et en ce que la courbe de commande (76 ; 276) est réalisée sous la forme d'une rainure à section partiellement circulaire dans le carter (12 ; 212), dans laquelle la sphère s'engage partiellement.
  6. Moteur à pistons oscillants selon la revendication 4, caractérisé en ce que ledit au moins un organe mobile (364, 370) est un rouleau (456), dont la surface de roulement (458), transversalement à la direction périphérique du rouleau (456), est réalisée avec une forme partiellement circulaire, ledit rouleau (456) étant monté sur un tourillon (460), dont une extrémité est assemblée au premier ou au deuxième piston (340, 346), et en ce que la courbe de commande (376) est réalisée sous la forme d'une rainure à section partiellement circulaire dans le carter, dans laquelle le rouleau (456) s'engage partiellement.
  7. Moteur à pistons oscillants selon l'une quelconque des revendications 1 à 6, caractérisé en ce que la cage de piston (80 ; 280 ; 380) est reliée à au moins un arbre menant et/ou à un arbre mené, qui est orienté parallèlement à l'axe de rotation (48 ; 248 ; 348).
  8. Moteur à pistons oscillants selon la revendication 7, caractérisé en ce que ledit au moins un arbre menant et/ou un arbre mené est disposé concentriquement à l'axe de rotation (48 ; 248) et est assemblé solidaire en rotation avec la cage de piston (80 ; 280).
  9. Moteur à pistons oscillants selon la revendication 7, caractérisé en ce que ledit au moins un arbre menant et/ou un arbre mené est disposé à une distance latérale de l'axe de rotation (348) et est relié à la cage de piston (380) par l'intermédiaire d'au moins un système d'engrenage.
  10. Moteur à pistons oscillants selon l'une quelconque des revendications 1 à 9, caractérisé en ce qu'un conduit (114 ; 314) passe à travers la cage de piston (80 ; 280), lequel, d'un côté, débouche dans l'alésage (94 ; 294) et, de l'autre côté, débouche vers le carter (12 ; 212), pour pouvoir communiquer, en fonction de la position de rotation de la cage de piston (80 ; 280), avec une ouverture d'admission ou avec une ouverture d'évacuation dans le carter (12 ; 212).
  11. Moteur à pistons oscillants selon l'une quelconque des revendications 1 à 10, caractérisé en ce que la cage de piston (80 ; 280) comporte au moins un conduit (102 ; 302) pour un fluide, en particulier un fluide de refroidissement ou de lubrification, lequel s'étend sur au moins une partie de la périphérie et à travers l'intérieur de la cage de piston (80 ; 280).
  12. Moteur à pistons oscillants selon l'une quelconque des revendications 1 à 11, caractérisé en ce qu'un alésage (110), qui s'élargit de préférence vers ses extrémités, traverse la cage de piston (80) à la hauteur de l'axe de pivotement (50) dans la direction de celui-ci.
  13. Moteur à pistons oscillants selon l'une quelconque des revendications 1 à 12, caractérisé en ce que dans le carter (12 ; 212 ; 312) sont montés un troisième et un quatrième piston (42, 44 ; 242, 244 ; 342, 344), qui sont aptes à pivoter autour du même axe de pivotement (50 ; 251 ; 350) ou autour d'un axe de pivotement (250) différent de celui-ci, et qui peuvent tourner avec le premier et le deuxième piston (40, 46 ; 240, 246 ; 340, 346) autour de l'axe de rotation (48 ; 248 ; 348) et définissent une deuxième chambre de travail (62 ; 262 ; 362).
  14. Moteur à pistons oscillants selon la revendication 13, caractérisé en ce que les quatre pistons (40 - 46 ; 240 - 246 ; 340 - 346) sont disposés de telle sorte que la première et la deuxième chambre de travail (60, 62 ; 260, 262 ; 360, 362) deviennent plus grande et plus petite dans le même sens pendant la rotation des pistons (40 - 46 ; 240 - 246 ; 340 - 346) autour de l'axe de rotation (48 ; 248 ; 348).
  15. Moteur à pistons oscillants selon la revendication 13 ou 14, caractérisé en ce que le premier et le deuxième piston (40, 46 ; 340, 346) et le troisième et le quatrième piston (42, 44 ; 342, 344) sont disposés par rapport à l'axe de rotation (48 ; 348), de telle sorte que les mouvements de pivotement de tous les pistons (40 - 46 ; 340 - 346) s'effectuent dans le même plan.
  16. Moteur à pistons oscillants selon la revendication 13 ou 14, caractérisé en ce que le premier et le deuxième piston (240, 246) et le troisième et le quatrième piston (242, 244) sont disposés par rapport à l'axe de rotation (248), de telle sorte que les mouvements de pivotement du premier et deuxième piston (240, 246) s'effectuent dans un premier plan et les mouvements de pivotement du troisième et quatrième piston (242, 244) s'effectuent dans un deuxième plan, le premier et le deuxième plan étant tournés, par rapport à l'axe de rotation (248), l'un par rapport à l'autre selon un angle différent de 0°.
  17. Moteur à pistons oscillants selon la revendication 16, caractérisé en ce que l'angle mesure au moins à peu près 90°.
  18. Moteur à pistons oscillants selon l'une quelconque des revendications 13 à 17, caractérisé en ce que la cage de piston (80 ; 280 ; 380) s'étend des deux côtés de l'axe de pivotement (50 ; 350) ou des axes de pivotement (250, 251) et loge également le troisième et le quatrième piston (42, 44 ; 242, 244 ; 342, 344).
  19. Moteur à pistons oscillants selon l'une quelconque des revendications 1 à 18, caractérisé en ce qu'une paroi intérieure (39 ; 239) du carter est sensiblement sphérique.
  20. Moteur à pistons oscillants selon l'une quelconque des revendications 1 à 19, caractérisé en ce qu'une paroi intérieure (39") du carter (12") est oblongue dans la direction de l'axe de rotation (48") sur une coupe le long d'un plan contenant l'axe de rotation (48").
  21. Moteur à pistons oscillants selon la revendication 20, caractérisé en ce que dans le carter (12") est disposé un tourillon creux (122), qui est apte à tourner autour de l'axe de pivotement (50") et qui comporte dans sa paroi un orifice (124) qui, en fonction de la position de rotation du tourillon creux (122), communique avec la première chambre de travail (60") ou, le cas échéant, avec la deuxième chambre de travail (62").
  22. Moteur à pistons oscillants selon la revendication 21, caractérisé en ce que le tourillon creux (122) est relié à un engrenage (130) qui, lors de la rotation des pistons (40" - 46") autour de l'axe de rotation (48"), entraîne le tourillon creux (122) en rotation autour de l'axe de pivotement (50").
  23. Moteur à pistons oscillants selon la revendication 22, caractérisé en ce que l'engrenage (130) comporte une denture hélicoïdale ou une roue hélicoïdale (132), qui est reliée au tourillon creux (122) et qui engrène avec au moins une denture (134), disposée sur le carter (12") et s'étendant autour de l'axe de rotation (48").
EP05822093A 2005-02-25 2005-12-09 Moteur à pistons oscillants Not-in-force EP1856375B1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
PL05822093T PL1856375T3 (pl) 2005-02-25 2005-12-09 Maszyna z tłokami wahadłowymi

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE102005010775A DE102005010775B3 (de) 2005-02-25 2005-02-25 Schwenkkolbenmaschine
DE102005024751.2A DE102005024751B4 (de) 2005-02-25 2005-05-24 Schwenkkolbenmaschine
PCT/EP2005/013254 WO2006089576A1 (fr) 2005-02-25 2005-12-09 Moteur à pistons oscillants

Publications (2)

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EP1856375A1 EP1856375A1 (fr) 2007-11-21
EP1856375B1 true EP1856375B1 (fr) 2010-05-19

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EP05822093A Not-in-force EP1856375B1 (fr) 2005-02-25 2005-12-09 Moteur à pistons oscillants

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US (1) US7658168B2 (fr)
EP (1) EP1856375B1 (fr)
JP (1) JP4818280B2 (fr)
AT (1) ATE468472T1 (fr)
DE (1) DE502005009616D1 (fr)
ES (1) ES2346552T3 (fr)
PL (1) PL1856375T3 (fr)
WO (1) WO2006089576A1 (fr)

Families Citing this family (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102006009198B4 (de) 2006-02-22 2010-03-25 Hüttlin, Herbert, Dr. h.c. Schwenkkolbenmaschine
DE102007030853A1 (de) 2007-06-26 2009-01-02 Hüttlin, Herbert, Dr. h.c. Rotationskolbenmaschine
DE102007039309B4 (de) * 2007-08-13 2010-08-19 Hüttlin, Herbert, Dr. h.c. Rotationskolbenmaschine
DE102007054321A1 (de) 2007-10-31 2009-05-07 Hüttlin, Herbert, Dr. h.c. Kolbenmaschine
CN101555826B (zh) * 2008-11-13 2011-07-20 靳北彪 弧形缸转子发动机
US8418672B2 (en) * 2010-03-04 2013-04-16 James L. Groves High leverage rotary internal combustion engine
DE102010022012A1 (de) 2010-05-25 2011-12-01 Herbert Hüttlin Aggregat, insbesondere Hybridmotor, Stromgenerator oder Kompressor
DE102012111812B3 (de) 2012-12-05 2013-12-12 Herbert Hüttlin Aggregat, insbesondere Verbrennungsmotor oder Kompressor
DE102015103734A1 (de) * 2015-03-13 2016-09-15 Innowatt GmbH Schwenkkolbenmaschine

Family Cites Families (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2501998A (en) * 1938-02-21 1950-03-28 Dutrey Andre Roto-volumetric pump
US3075506A (en) * 1961-07-31 1963-01-29 Differential Hydraulics Inc Spherical trajectory rotary power device
FR2322282A1 (fr) * 1975-08-26 1977-03-25 Etienne Charles Mouvement mecanique spherotatif
CA2474449C (fr) 2002-02-06 2009-06-09 Herbert Huettlin Moteur a pistons oscillants
AU2005230656B2 (en) * 2004-04-06 2010-09-16 Peraves Aktiengesellschaft Rotary-piston engine and vehicle comprising an engine of this type
DE102005010775B3 (de) * 2005-02-25 2006-04-20 Hüttlin, Herbert, Dr. h.c. Schwenkkolbenmaschine
DE102006009197B4 (de) * 2006-02-22 2008-09-11 Hüttlin, Herbert, Dr. h.c. Schwenkkolbenmaschine
DE102006009198B4 (de) * 2006-02-22 2010-03-25 Hüttlin, Herbert, Dr. h.c. Schwenkkolbenmaschine

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DE502005009616D1 (de) 2010-07-01
JP4818280B2 (ja) 2011-11-16
ES2346552T3 (es) 2010-10-18
ATE468472T1 (de) 2010-06-15
JP2008531904A (ja) 2008-08-14
US20080041225A1 (en) 2008-02-21
EP1856375A1 (fr) 2007-11-21
WO2006089576A1 (fr) 2006-08-31
PL1856375T3 (pl) 2010-10-29
US7658168B2 (en) 2010-02-09

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