EP1856375B1 - Oscillating piston engine - Google Patents
Oscillating piston engine Download PDFInfo
- 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.)
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- 230000033001 locomotion Effects 0.000 claims abstract description 47
- 230000010355 oscillation Effects 0.000 claims abstract 10
- 230000001050 lubricating effect Effects 0.000 claims description 18
- 230000005540 biological transmission Effects 0.000 claims description 8
- 239000002826 coolant Substances 0.000 claims description 2
- 238000001816 cooling Methods 0.000 description 16
- 238000002485 combustion reaction Methods 0.000 description 13
- 239000000203 mixture Substances 0.000 description 11
- 238000002955 isolation Methods 0.000 description 7
- 230000006835 compression Effects 0.000 description 6
- 238000007906 compression Methods 0.000 description 6
- 239000000446 fuel Substances 0.000 description 4
- 238000010586 diagram Methods 0.000 description 3
- 238000002347 injection Methods 0.000 description 3
- 239000007924 injection Substances 0.000 description 3
- 238000005461 lubrication Methods 0.000 description 2
- 230000001404 mediated effect Effects 0.000 description 2
- 238000000034 method Methods 0.000 description 2
- 238000007789 sealing Methods 0.000 description 2
- 239000000853 adhesive Substances 0.000 description 1
- 230000001070 adhesive effect Effects 0.000 description 1
- WYTGDNHDOZPMIW-RCBQFDQVSA-N alstonine Natural products C1=CC2=C3C=CC=CC3=NC2=C2N1C[C@H]1[C@H](C)OC=C(C(=O)OC)[C@H]1C2 WYTGDNHDOZPMIW-RCBQFDQVSA-N 0.000 description 1
- 238000010276 construction Methods 0.000 description 1
- 230000000694 effects Effects 0.000 description 1
- 239000000314 lubricant Substances 0.000 description 1
- 210000000056 organ Anatomy 0.000 description 1
- 238000007493 shaping process Methods 0.000 description 1
- 230000001360 synchronised effect Effects 0.000 description 1
- 238000009423 ventilation Methods 0.000 description 1
Images
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
- 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.
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Abstract
Description
Die Erfindung betrifft eine Schwenkkolbenmaschine, mit einem Gehäuse, in dem ein erster und zumindest ein zweiter Kolben angeordnet sind, die gemeinsam in dem Gehäuse um eine gehäusefeste Drehachse umlaufen können, und die beim Umlaufen um die Drehachse um eine senkrecht zur Drehachse und durch die Gehäusemitte verlaufende Schwenkachse zueinander gegensinnige hin- und hergehende Schwenkbewegungen ausführen, wobei der erste Kolben eine erste Endfläche und der zumindest zweite Kolben eine der ersten Endflächen zugewandte zweite Endfläche aufweist, wobei die Endflächen eine Arbeitskammer begrenzen, wobei die Kolben so angeordnet sind, dass die Drehachse durch die Arbeitskammer verläuft.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.
Eine derartige Schwenkkolbenmaschine ist aus dem Dokument
Schwenkkolbenmaschinen und insbesondere eine Schwenkkolbenmaschine gemäß der vorliegenden Erfindung können als Brennkraftmaschinen (Verbrennungsmotoren), als Pumpen oder als Kompressoren verwendet werden. Eine Schwenkkolbenmaschine gemäß der vorliegenden Erfindung wird vorzugsweise als Brennkraftmaschine verwendet und als solche in der vorliegenden Beschreibung beschrieben.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.
Im Falle der Verwendung einer Schwenkkolbenmaschine als Brennkraftmaschine werden die einzelnen Arbeitstakte des Einlassens, verdichtens, zündens des verbrennungsgemisches und des Expandierens und Ausstoßens des verbrannten verbrennungsgemisches durch hin- und hergehende Schwenkbewegungen der einzelnen Kolben zwischen zwei Endstellungen vermittelt.In the case of using an oscillating piston engine as an internal combustion engine, the individual working cycles of the intake, compression, ignition of the combustion mixture and the expansion and expulsion of the combusted combustion mixture are mediated by reciprocating pivotal movements of the individual pistons between two end positions.
Bei einer aus dem Dokument
Die Kolben dieser bekannten Schwenkkolbenmaschinen sind in dem Gehäuse so angeordnet, dass sie in ihrer OT-Stellung, in der die Volumina der beiden Arbeitskammern minimal sind, senkrecht zur Drehachse stehen. In dieser Stellung sind beim Umlaufen der Kolben um die Drehachse die auf die Kolben wirkenden Zentrifugalkräfte maximal. Dies führt dazu, dass bei hohen Drehzahlen das Expandieren bzw. das Auseinanderschwenken der Kolben gegen die Fliehkräfte erfolgen muss, weil die Fliehkräfte der auseinanderschwenkenden Bewegung der Kolben entgegenwirken. Die Arbeitskammern liegen bei dieser Schwenkkolbenmaschine stets außerhalb und senkrecht zur Drehachse.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 auseinanderschwenkenden movement of the pistons. The working chambers are always outside and perpendicular to the axis of rotation in this oscillating piston engine.
Die Kolben der bekannten Schwenkkolbenmaschinen weisen im Wesentlichen die Form eines Kugelkeils auf, und entsprechend ist auch die Geometrie der Arbeitskammern.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.
Obwohl die aus
Die aus
Der Erfindung liegt die Aufgabe zugrunde, für eine Schwenkkolbenmaschine der eingangs genannten Art ein neues Konzept anzugeben.The invention has for its object to provide a new concept for a rotary piston machine of the type mentioned.
Erfindungsgemäß wird diese Aufgabe hinsichtlich der eingangs genannten Schwenkkolbenmaschine dadurch gelöst, dass der erste und der zumindest zweite Kolben in einem Kolbenkäfig gleitend gelagert sind, der im Gehäuse konzentrisch zur Drehachse um diese drehbar angeordnet ist, wobei der Kolbenkäfig mit dem ersten und zumindest zweiten Kolben bezüglich der Umlaufbewegung um die Drehachse drehfest verbunden ist, und dass der Kolbenkäfig etwa senkrecht zur Drehachse eine Bohrung aufweist, in der der erste und zumindest zweite Kolben teilweise und darin gleitend aufgenommen sind, und die die Arbeitskammer in Umfangsrichtung begrenzt.According to the invention 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.
Das gegenüber der aus
Der erste und der zumindest zweite Kolben sind in einem Kolbenkäfig gleitend gelagert, der im Gehäuse konzentrisch zur Drehachse um diese drehbar angeordnet ist, wobei der Kolbenkäfig mit dem ersten und zumindest zweiten Kolben bezüglich der Umlaufbewegung um die Drehachse drehfest verbunden ist.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.
Der Kolbenkäfig und der erste und zumindest zweite Kolben bilden somit die "Innenmaschine" oder den "Innenmotor" der Schwenkkolbenmaschine. Die gleitende Lagerung der beiden Kolben in dem Kolbenkäfig dient der Schwenkbeweglichkeit der beiden Kolben um die Schwenkachse, während die Kolben auf Grund ihrer bezüglich der Umlaufbewegung um die Drehachse drehfesten Verbindung mit dem Kolbenkäfig mit diesem gemeinsam um die Drehachse umlaufen. Der Kolbenkäfig kann nun vorteilhafterweise als Antriebs- oder Abtriebsorgan dienen.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.
Der Kolbenkäfig weist etwa senkrecht zur Drehachse eine Bohrung auf, in der der erste und zumindest zweite Kolben teilweise und darin gleitend aufgenommen sind, und die die Arbeitskammer in Umfangsrichtung begrenzt.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.
Die Bohrung definiert somit zusammen mit den beiden einander zugewandten Endflächen des ersten und zumindest zweiten Kolbens die zumindest eine Arbeitskammer der Schwenkkolbenmaschine. Je nach Geometrie der Endflächen der beiden Kolben ist auch die Geometrie der Bohrung.des Kolbenkäfigs gewählt, also beispielsweise kreisförmig oder wie ebenfalls oben erwähnt oval oder von anderer Form entsprechend der Form der Endflächen der Kolben. Bei einer kreisförmigen Ausgestaltung der Endflächen der beiden Kolben entsteht in Verbindung mit der kreisförmigen Bohrung im Kolbenkäfig eine Arbeitskammer, die einem gekrümmten Zylinder oder einem Toroidabschnitt entspricht. Die Kolben sind dann vorzugsweise gegen die Wand der Bohrung des Kolbenkäfigs mittels Dichtungen abgedichtet, wobei diese im Fall einer kreisförmigen Bohrung und kreisförmigen Endflächen vorteilhafterweise als an die Form der Arbeitskammer angepasste Kolbenringe ausgeführt sind.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. Depending on the geometry of the end faces of the two pistons, 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. In a circular configuration of the end faces of the two pistons, in conjunction with the circular bore in the piston cage, 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.
In einer bevorzugten Ausgestaltung ist vorgesehen, dass die erste und zweite Endfläche des ersten und zumindest zweiten Kolbens kreisförmig ausgebildet sind.In a preferred embodiment, it is provided that the first and second end faces of the first and at least second pistons are circular.
Bei dieser Ausgestaltung sind der erste und zumindest zweite Kolben zumindest im Bereich, der sich an ihre Endflächen anschließt, zylindrisch und somit in diesem Bereich klassischen Kolben von Hubkolbenmotoren sehr ähnlich. Ein Vorteil, der sich hieraus ergibt, ist, dass als Dichtungen für die beiden Kolben Kolbenringe, ggfls mit entsprechender Krümmung, verwendet werden können, so dass hier auf seit langem bestehende Erfahrungen bei der Lösung von Dichtungsproblemen bei Hubkolbenmotoren zurückgegriffen werden kann. Die durch die beiden Endflächen des ersten und zumindest zweiten Kolbens begrenzte Arbeitskammer besitzt bei dieser Ausgestaltung die Geometrie eines um die Schwenkachse gebogenen Zylinders oder Toroidabschnitts.In this embodiment, 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 Toroidabschnitts.
Alternativ zu einer kreisförmigen Ausgestaltung der Endflächen des ersten und zumindest zweiten Kolbens kann jedoch auch eine davon abweichende Geometrie, beispielsweise eine ovale Form, gewählt werden, was insbesondere dann, wenn der Innenraum des Gehäuses Kugelsymmetrie aufweist, zu einer Vergrößerung der zumindest einen Arbeitskammer beiträgt.As an alternative to a circular configuration of the end faces of the first and at least second pistons, however, 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.
In einer weiteren bevorzugten Ausgestaltung sind der erste und der zumindest zweite Kolben im Wesentlichen bogenförmig ausgebildet.In a further preferred embodiment, the first and the at least second piston are formed substantially arcuate.
Es versteht sich, dass die bogenförmige Gestalt des ersten und zumindest zweiten Kolbens auf den an ihre Endflächen angrenzenden Bereich begrenzt sein kann, d.h. von den Endflächen abgewandte Außenseiten der Kolben können, wie hiernach noch beschrieben wird, als Funktionselemente für die Steuerung der Kolben zur Ableitung der Schwenkbewegung aus der Umlaufbewegung der Kolben genutzt werden und dazu andere Formgestaltungen aufweisen.It will be understood that the arcuate shape of the 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.
In einer weiteren bevorzugten Ausgestaltung weist der erste Kolben und/oder der zumindest zweite Kolben zumindest ein Lauforgan auf, das beim Umlaufen des ersten und/oder zumindest zweiten Kolbens entlang einer entsprechend ausgebildeten Steuerkurve geführt ist, um die Schwenkbewegungen des ersten und zumindest zweiten Kolbens zu erzeugen, wobei die Steuerkurve am Gehäuse mit bezüglich der Drehachse zumindest näherungsweise maximalem Abstand angeordnet ist.In a further preferred embodiment, the 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.
Bei der bekannten Schwenkkolbenmaschine ist ein vergleichbarer Steuermechanismus für die Schwenkbewegungen der Kolben vorgesehen, jedoch befindet sich dort die Steuerkurve mit geringerem Abstand zur Drehachse in der Nähe der Stirnseiten des Gehäuses. Der Vorteil der größeren Beabstandung der Steuerkurve von der Drehachse besteht in verbesserten Hebelverhältnissen, um die Schwenkbewegungen der zumindest zwei Kolben aus deren Umlaufbewegung um die Drehachse abzuleiten.In the known oscillating piston engine, 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.
In diesem Zusammenhang ist es weiterhin bevorzugt, wenn das zumindest eine Lauforgan eine Kugel ist, die drehbar in einer Kugelpfanne an einer dem Gehäuse zugewandten Außenseite des ersten und/oder zumindest zweiten Kolbens gelagert ist, und wenn die Steuerkurve als Nut mit teilkreisförmigem Querschnitt im Gehäuse ausgebildet ist, in die die Kugel teilweise eingreift.In this context, it is further preferred if 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.
Ein solcher Steuermechanismus, der als das zumindest eine Lauforgan eine Kugel verwendet, hat den Vorteil einer optimierten Reibungsverminderung des Steuermechanismus, da die Kugel in der Kugelpfanne des zumindest einen Kolbens frei drehbar ist, und ebenso in der Nut im Gehäuse, so dass die Kugel der Steuerkurve auf Grund ihrer allgerichteten Drehbarkeit mit besonders geringer Reibung folgen kann.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.
Die Kugelpfanne kann so ausgebildet sein, dass sie die Kugel unverlierbar hält, oder die Kugel kann mittels eines Schmierfilms, der durch eine Ölschmierung bereitgestellt wird, durch Adhäsionskräfte in der Kugelpfanne gehalten werden.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.
Vorzugsweise weist sowohl der erste als auch der zumindest zweite Kolben ein Lauforgan in Form einer Kugel auf, die in derselben nutförmigen Steuerkurve im Gehäuse im Abstand voneinander laufen.Preferably, 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.
Alternativ zur Ausgestaltung des zumindest einen Lauforgans in Form einer Kugel kann dieses eine Rolle sein, deren Lauffläche quer zur Umfangsrichtung der Rolle teilkreisförmig ausgebildet ist, wobei die Rolle auf einer Welle gelagert ist, die endseitig mit dem ersten oder zweiten Kolben verbunden ist. Die Steuerkurve ist dabei wiederum vorzugsweise als Nut mit teilkreisförmigem Querschnitt im Gehäuse ausgebildet, in die die Rolle teilweise eingreift.As an alternative to the design of the at least one running element in the form of a ball, 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.
Der Vorteil der Ausgestaltung des zumindest einen Lauforgans als Rolle bzw. Führungsrolle mit Wellenverbindung der Rolle mit dem Kolben lässt die bei der vorstehend genannten in allen Richtungen frei drehbaren Kugel notwendige Öladhäsion der Kugel an dem Kolben entfallen. Dennoch wird die ganze Breite der Kolbenführungsflächen genutzt. Die Lagerung der zumindest einen Rolle auf der Welle erfolgt vorzugsweise über Präzisions-Nadellager, und die Rolle ist insbesondere vorzugsweise lösbar mit dem Kolben verbunden.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.
Vorzugsweise ist der Kolbenkäfig mit zumindest einer Antriebs- und/oder Abtriebswelle verbunden, die parallel zur Drehachse verläuft.Preferably, the piston cage is connected to at least one drive and / or output shaft, which runs parallel to the axis of rotation.
Dies kann vorzugsweise so realisiert sein, dass die zumindest eine Antriebs- und/oder Abtriebswelle konzentrisch zur Drehachse angeordnet und drehfest mit dem Kolbenkäfig verbunden ist.This can preferably be realized in such a way that the at least one drive and / or output shaft is arranged concentrically with respect to the axis of rotation and is connected in a rotationally fixed manner to the piston cage.
Diese Ausgestaltung hat den Vorteil, dass die Schwenkkolbenmaschine insgesamt kompakt bauend ausgebildet werden kann, da zwischen der Drehachse und der Antriebs- und/oder Abtriebswelle kein Versatz besteht. Des Weiteren ist auch kein Getriebe zur Übertragung der Drehbewegung des Kolbenkäfigs auf die Antriebs- und/oder Abtriebswelle bzw. umgekehrt erforderlich.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.
Alternativ hierzu ist es jedoch ebenso bevorzugt, wenn die zumindest eine Antriebs- und/oder Abtriebswelle mit seitlichem Abstand zur Drehachse angeordnet ist und mit dem Kolbenkäfig über zumindest eine Getriebeanordnung, bspw. eine Zahnkranz- oder Riemenantriebsanordnung, verbunden ist.Alternatively, however, it is also preferred if 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.
Der Vorteil dieser Maßnahme besteht darin, dass die zumindest eine Antriebs- und/oder Abtriebswelle mit seitlichem Versatz zur zumindest einen Arbeitskammer, die ja auf der Drehachse liegt, angeordnet ist. Dies führt wiederum dazu, dass die für die zumindest eine Arbeitskammer im Fall der Verwendung der Schwenkkolbenmaschine als Brennkraftmaschine vorzusehende Zünd- oder Glühkerze mit der Antriebs- und/oder Abtriebswelle nicht kollidiert. Bei der vorher genannten Maßnahme ist es nämlich ggf. erforderlich, die Zünd- oder Glühkerze von der Drehbewegung des Kolbenkäfigs und der damit verbundenen Antriebs- und/oder Abtriebswelle zu entkoppeln, oder die Kerze selbst mit rotieren zu lassen, was jedoch eine elektrische Kontaktierung der Kerze über Schleifkontakte erforderlich macht.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. In the aforementioned measure, it may be necessary to decouple the ignition or glow plug from the rotational movement of the piston cage and the associated drive and / or output shaft, or to let the candle itself rotate, but this is an electrical contact Candle over sliding contacts required.
Bei der vorstehend genannten Maßnahme können zusätzlich auch die Kraftstoff-Einspritzdüse und ggf. Einlass- und Auslassstutzen ebenfalls auf der Stirnseite des Gehäuses angeordnet werden. Dabei können kombinierte Zündkerzen-Einspritzdüsen-Anordnungen vorgesehen werden.In the above-mentioned measure, in addition, the fuel injection nozzle and optionally inlet and outlet nozzles can also be arranged on the front side of the housing. In this case, combined spark plug injector arrangements can be provided.
In einer weiteren bevorzugten Ausgestaltung geht durch den Kolbenkäfig ein Kanal hindurch, der einerseits in der Bohrung mündet und andererseits zum Gehäuse hin mündet, um je nach Drehstellung mit einer Einlass- oder mit einer Auslassöffnung im Gehäuse zu kommunizieren.In a further preferred embodiment, 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.
Der Vorteil dieser Maßnahme besteht darin, dass der Kolbenkäfig mittels des zuvor genannten Kanals oder Öffnung als eine Art Ventil für die Einlass- und Auslassöffnungen im Gehäuse wirkt. Es ist daher nicht erforderlich, die Einlass- und Auslassöffnungen im Gehäuse mit separaten Ventilen zu versehen, noch für den Zeitpunkt des Öffnens oder Schließens eine aufwendige Steuerung des Ventils vorzusehen, wie dies bei klassischen Hubkolbenmotoren der Fall ist. Das Freigeben bzw. Verschließen der Einlass- und Auslassöffnung zum Einlassen von Verbrennungsluft und/oder Brennstoff und zum Auslassen verbrannten Verbrennungegemisches erfolgt im richtigen Takt automatisch durch die Umlaufbewegung des Kolbenkäfigs um die Drehachse.The advantage of this measure is that 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.
In einer weiteren bevorzugten Ausgestaltung weist der Kolbenkäfig zumindest einen Kanal für ein Medium, insbesondere Kühl-/ Schmiermedium auf, der sich zumindest teilumfänglich und durch das Innere des Kolbenkäfigs erstreckt.In a further preferred embodiment, 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.
Hierbei ist von Vorteil, dass der Kolbenkäfig vorteilhafterweise eine weitere Funktion wahrnimmt, nämlich die Versorgung aller beweglichen Teile innerhalb des Gehäuses mit einem Kühl-/ und/oder Schmiermedium. Die Zufuhr eines Kühl-/Schmiermediums kann über am Gehäuse angeordnete Anschlüsse erfolgen, wobei in diesem Fall der zumindest eine Kanal sich vorzugsweise auf der Außenseite des Kolbenkäfigs als Ringkanal erstreckt, so dass der zumindest eine Kanal stets mit den Versorgungsanschlüssen kommuniziert.It is advantageous that 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.
In einer weiteren bevorzugten Ausgestaltung geht durch den Kolbenkäfig auf Höhe der Schwenkachse in deren Richtung eine Bohrung hindurch, die sich vorzugsweise zu ihren Enden hin erweitert.In a further preferred embodiment, a bore passes through the piston cage at the level of the pivot axis in its direction, which bore preferably widens toward its ends.
Diese Bohrung dient vorteilhafterweise als weiterer Kühl-/ Schmiermittelkanal, was zu einer besonders intensiven Umwälzung eines solchen Kühl-/Schmiermediums beiträgt, da sich diese Bohrung senkrecht zur Drehachse erstreckt und somit das darin gerade befindliche Kühl-/Schmiermedium beim Umlaufen des Kolbenkäfigs um die Drehachse mit Zentrifugalkräften beaufschlagt wird, die das Kühl-/Schmiermedium zu den sich erweiternden Enden der Bohrung hin bewegen. Hierdurch tritt vorteilhafterweise ein Ventilationseffekt bei der Umwälzung des Kühl-/Schmiermediums auf.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.
In einer weiteren bevorzugten Ausgestaltung sind in dem Gehäuse ein dritter und vierter Kolben angeordnet, die um dieselbe Schwenkachse oder eine von dieser verschiedenen Schwenkachse verschwenkbar sind und mit dem ersten und zweiten Kolben um die Drehachse umlaufen können und eine zweite Arbeitskammer definieren.In a further preferred embodiment, 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.
In dieser Ausgestaltung wird auch bei der erfindungsgemäßen Schwenkkolbenmaschine ein bezüglich der Drehachse vorteilhaft symmetrisches und somit massenausgeglichenes System geschaffen.In this refinement, a system which is advantageously symmetrical and thus mass-balanced with respect to the axis of rotation is also created in the case of the oscillating-piston engine according to the invention.
Dabei ist es bevorzugt, wenn die vier Kolben so angeordnet sind, dass sich die erste und zweite Arbeitskammer beim Umlaufen der Kolben um die Drehachse gleichsinnig vergrößern und verkleinern.It is preferred if 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.
Diese Ausgestaltung trägt dazu bei, dass die vier Kolben in jeder Umlauf- und Schwenkstellung ein massenausgeglichenes System darstellen.This design contributes to the fact that the four pistons represent a mass-balanced system in each circulating and pivoting position.
Bei einer Ausgestaltung der Schwenkkolbenmaschine mit insgesamt vier Kolben ist es in einer ersten Ausgestaltung vorzugsweise vorgesehen, dass der erste und zweite Kolben und der dritte und vierte Kolben bezüglich der Drehachse so angeordnet sind, dass die Schwenkbewegungen aller Kolben in derselben Ebene erfolgen.In one embodiment of the oscillating piston engine with a total of four pistons, it is preferably provided in a first embodiment that 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.
Bei dieser Ausgestaltung liegen die beiden Arbeitskammern in einem Schnitt entlang der Drehachse und senkrecht zur Schwenkachse stets in ein und derselben Ebene.In this embodiment, 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.
Noch bevorzugter ist es, wenn der erste und zweite Kolben und der dritte und vierte Kolben bezüglich der Drehachse so angeordnet sind, dass die Schwenkbewegungen des ersten und zweiten Kolbens in einer ersten Ebene und die Schwenkbewegungen des dritten und vierten Kolbens in einer zweiten Ebene erfolgen, wobei die erste und die zweite Ebene bezüglich der Drehachse relativ zueinander um einen Winkel ungleich 0° verdreht sind.It is even more preferable if the 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.
Bei dieser Ausgestaltung liegen entsprechend die beiden durch die vier Kolben gebildeten Arbeitskammern nicht wie bei der zuvor genannten Ausgestaltung in einer gemeinsamen Ebene, sondern sind bezüglich der Drehachse zueinander um einen Winkel ungleich 0° versetzt. Dies hat nun den Vorteil gegenüber der zuvor genannten Ausgestaltung, dass die oben genannte Steuerkurve bzw. im Fall von vier Kolben zwei Steuerkurven und die darin geführten Lauforgane, die vorzugsweise als Kugeln ausgebildet sind, ihren Endpunkt nicht in oder vor der Orthogonalen zur Drehachse haben müssen, sondern über die Orthogonale hinausreichen können, da aufgrund des Versatzes der beiden Kolbenpaare zueinander die Lauforgane in der UT-Stellung, d.h. bei maximal geöffneten Arbeitskammern, nicht miteinander kollidieren können, da die Kolbenpaare zueinander um einen Winkel ungleich 0° verdreht angeordnet sind. Auf diese Weise kann gegenüber der zuvor genannten Ausgestaltung das maximale Volumen der beiden Arbeitskammern (UT-Stellung der Kolben) aufgrund eines größeren Öffnungswinkels der beiden Kolbenpaare vergrößert werden. Wie bei einer der oben genannten Ausgestaltungen ist es bevorzugt, wenn sich die beiden Arbeitskammern auch bei dieser Variante gleichsinnig vergrößern und verkleinern, was durch eine entsprechende Formgebung der Steuerkurven erzielt wird.In this embodiment, accordingly, 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 °. In this way, compared to the aforementioned embodiment, 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. As with any of the above embodiments, it is preferred when the two working chambers zoom in and out in the same direction in this variant, which is achieved by a corresponding shaping of the cams.
Besonders bevorzugt ist es im Rahmen der zuvor genannten Ausgestaltung, wenn der Winkel zumindest annähernd 90° beträgt.It is particularly preferred in the context of the aforementioned embodiment, when the angle is at least approximately 90 °.
Bei dieser Ausgestaltung wird wieder eine möglichst hohe Symmetrie der Massenverteilung der Kolben in dem Gehäuse erreicht.In this embodiment, the highest possible symmetry of the mass distribution of the pistons in the housing is again achieved.
In einer weiteren bevorzugten Ausgestaltung erstreckt sich der Kolbenkäfig beidseits der Schwenkachse oder Schwenkachsen und nimmt auch den dritten und vierten Kolben auf.In a further preferred embodiment, the piston cage extends on both sides of the pivot axis or pivot axes and also receives the third and fourth piston.
Insgesamt wird somit ein besonders einfacher und wenig Teile erfordernder Aufbau geschaffen, bei dem der Kolbenkäfig alle vier Kolben aufnimmt. Für den dritten und vierten Kolben weist der Kolbenkäfig, wenn dies für den ersten und zweiten Kolben wie oben beschrieben vorgesehen ist, für den dritten und vierten Kolben ebenfalls eine Bohrung auf, in der der dritte und vierte Kolben gleitend gelagert und bezüglich der Drehachse drehfest mit dem Kolbenkäfig verbunden sind, wobei diese Bohrung dann zusammen mit den Endflächen des dritten und vierten Kolbens die zweite Arbeitskammer begrenzt.Overall, a particularly simple and little parts requiring structure is thus created in which the piston cage receives all four pistons. For the third and fourth 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.
In einer weiteren bevorzugten Ausgestaltung ist eine Gehäuseinnenwand des Gehäuses im Wesentlichen kugelförmig.In a further preferred embodiment, a housing inner wall of the housing is substantially spherical.
Mit dieser Ausgestaltung wird vorteilhafterweise eine Schwenkkolbenmaschine mit Kugelsymmetrie geschaffen, die sich bereits bei der bekannten Schwenkkolbenmaschine bewährt hat.With this embodiment, advantageously a rotary piston machine is provided with ball symmetry, which has already proven itself in the known oscillating piston engine.
Alternativ hierzu kann jedoch auch vorgesehen sein, dass eine Gehäuseinnenwand des Gehäuses im Schnitt entlang einer Ebene, die die Drehachse beinhaltet, in Richtung der Drehachse oblong ist.Alternatively, however, it can also be provided that 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" bedeutet hier, dass das Gehäuse der Schwenkkolbenmaschine aus zwei Kugelhälften besteht, zwischen die ein in Richtung der Drehachse länglicher Abschnitt zwischengefügt ist. Die Oblong-Form der Gehäuseinnenwand des Gehäuses eröffnet vorteilhafterweise die Möglichkeit, folgende bevorzugte Ausgestaltungen vorzusehen."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.
So ist es bevorzugt, wenn im Gehäuse ein um die Schwenkachse schwenkbarer Hohlzapfen angeordnet ist, der in seiner Wand eine Öffnung aufweist, die in Abhängigkeit der Drehstellung des Hohlzapfens mit der ersten Arbeitskammer oder ggf. mit der zweiten Arbeitskammer kommuniziert.Thus, it is preferred if in the housing 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.
Dieser Hohlzapfen kann vorteilhafterweise dazu genutzt werden, Frischluft, insbesondere unter Druck stehende Frischluft, über die in dem Hohlzapfen vorgesehene umfänglich begrenzte Öffnung in die Arbeitskammer, oder falls zwei Arbeitskammern vorgesehen sind, wechselweise in die beiden Arbeitskammern, zuzuführen. Hierdurch kann Verbrennungsluft unter einem Vordruck in die Arbeitskammern geleitet werden, wodurch eine höhere Verdichtung des Brennstoff-Luftgemisches in den Arbeitskammern erzielbar ist. Auf diese Weise eignet sich die Schwenkkolbenmaschine insbesondere als Dieselmotor.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. As a result, 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. In this way, the oscillating piston engine is particularly suitable as a diesel engine.
Dabei ist es bevorzugt, wenn der Hohlzapfen mit einem Getriebe verbunden ist, das beim Umlaufen der Kolben um die Drehachse den Hohlzapfen in Drehung um die Schwenkachse versetzt.It is preferred if 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.
Auf diese Weise wird die Drehbewegung des Hohlzapfens, um dessen Öffnung mit der einen oder anderen Arbeitskammer kommunizieren zu lassen, auf vorteilhaft einfache Weise direkt aus der Umlaufbewegung der Kolben um die Drehachse abgeleitet, ohne dass ein externer Steuermechanismus erforderlich ist. Bei entsprechender Wahl des Übersetzungsverhältnisses des Getriebes wird auf einfache Weise eine Synchronisation der Drehgeschwindigkeit des Hohlzapfens mit der Drehzahl der Schwenkkolbenmaschine erreicht.In this way, the rotational movement of the hollow pin to communicate with the opening of one or the other working chamber, derived in an advantageously simple manner directly from the orbital motion of the piston about the axis of rotation, without an external control mechanism is required. With a suitable choice of the transmission ratio of the transmission synchronization of the rotational speed of the hollow pin is achieved with the speed of the oscillating piston engine in a simple manner.
Dabei ist es weiterhin bevorzugt, wenn das Getriebe eine mit dem Hohlzapfen verbundene Schneckenverzahnung aufweist, die mit zumindest einer am Gehäuse angeordneten Zahnung kämmt, die sich um die Drehachse herum erstreckt.It is further preferred if 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.
Ein solches Getriebe ist konstruktiv besonders einfach, lässt sich ohne erhöhten Platzbedarf im Gehäuse unterbringen und bei entsprechender Gestaltung der Schneckenverzahnung kann dann die Drehgeschwindigkeit des Hohlzapfens in Abhängigkeit von der Drehzahl der Umlaufbewegung der Kolben um die Drehachse abgestimmt werden.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.
Weitere Vorteile und Merkmale ergeben sich aus der nachfolgenden Beschreibung und der beigefügten Zeichnung.Further advantages and features will become apparent from the following description and the accompanying drawings.
Es versteht sich, dass die vorstehend genannten und nachstehend noch zu erläuternden Merkmale nicht nur in der jeweils angegebenen Kombination, sondern auch in anderen Kombinationen oder in Alleinstellung verwendbar sind, ohne den Rahmen der vorliegenden Erfindung zu verlassen.It is understood that the features mentioned above and those yet to be explained not only in the respectively specified Combination, but also in other combinations or alone, without departing from the scope of the present invention.
Ausführungsbeispiele der Erfindung sind in der Zeichnung dargestellt und werden mit Bezug auf diese hiernach näher beschrieben. Es zeigen:
- Fig. 1
- eine perspektivische Gesamtansicht einer Schwenkkolbenmaschine, gemäß einem ersten Ausführungsbeispiel;
- Fig. 2
- eine Ansicht der Schwenkkolbenmaschine in
Fig. 1 in Richtung der Pfeile II inFig. 1 ; - Fig. 3
- einen Längsschnitt durch die Schwenkkolbenmaschine entlang einer Ebene parallel zur Drehachse und senkrecht zur Schwenkachse, wobei die Kolben der Schwenkkolbenmaschine in einer ersten Betriebsstellung dargestellt sind;
- Fig. 4
- eine Darstellung der Schwenkkolbenmaschine in derselben Betriebsstellung der Kolben wie in
Fig. 3 , leicht perspektivisch und die Kolben nicht im Schnitt; - Fig. 5
- eine mit
Fig. 4 vergleichbare Darstellung der Schwenkkolbenmaschine, wobei die Kolben in einer zweiten Betriebsstellung dargestellt sind; - Fig. 7
- eine Darstellung der Schwenkkolbenmaschine in derselben Betriebsstellung der Kolben wie in
Fig. 6 , leicht perspektivisch und die Kolben nicht im Schnitt; - Fig. 8
- einen Schnitt durch die Schwenkkolbenmaschine entlang der Linie VIII-VIII in
Fig. 3 ; - Fig. 9
- einen Schnitt durch die Schwenkkolbenmaschine entlang der Linie IX-IX in
Fig. 3 ; - Fig. 10
- einen Längsschnitt entlang der Linie X-X in
Fig. 3 durch die Schwenkkolbenmaschine gemäß denFig. 1 bis 9 ; - Fig. 10A
- eine mit
Fig. 10 vergleichbare Darstellung eines abgewandelten Ausführungsbeispiels der Schwenkkolbenmaschine; - Fig. 11
- einen Längsschnitt durch die Schwenkkolbenmaschine vergleichbar mit
Fig. 3 oder4 , wobei jedoch der Kolbenkäfig und die Kolben nicht im Schnitt dargestellt sind; - Fig. 12
- eine Ansicht der Schwenkkolbenmaschine, bei der eine Gehäusehälfte abgenommen ist;
- Fig. 13
- eine perspektivische Darstellung der Anordnung aus Kolbenkäfig und Kolben in Alleinstellung und perspektivisch;
- Fig. 13
- eine perspektivische Darstellung der Anordnung aus Kolbenkäfig und Kolben in Alleinstellung und perspektivisch;
- Fig. 14
- eine perspektivische Ansicht einer Innenseite einer Gehäusehälfte der Schwenkkolbenmaschine in Alleinstellung;
- Fig. 15a) bis d)
- verschiedene perspektivische Ansichten bzw. Schnitte eines Kolbens der Schwenkkolbenmaschine einschließlich Lauforgan in Alleinstellung;
- Fig. 16
- einen Längsschnitt durch eine Schwenkkolbenmaschine gemäß einem weiteren Ausführungsbeispiel;
- Fig. 17
- einen Längsschnitt durch die Schwenkkolbenmaschine in
Fig. 17 in einem Schnitt entlang einer Ebene, die bezüglich der Schnittebene inFig. 16 um 90° gedreht ist; - Fig. 18
- eine perspektivische Gesamtansicht einer Schwenkkolbenmaschine gemäß einem weiteren Ausführungsbeispiel;
- Fig. 19
- einen Längsschnitt durch die Schwenkkolbenmaschine in
Fig. 18 entlang einer Ebene parallel zur Drehachse und senkrecht zur Schwenkachse; - Fig. 20
- eine perspektivische Darstellung einer Hälfte der Schwenkkolbenmaschine in
Fig. 18 ; - Fig. 21
- eine perspektivische Darstellung der Anordnung aus Kolbenkäfig und Kolben der Schwenkkolbenmaschine in
Fig. 18 in Alleinstellung und perspektivisch; - Fig. 22
- ein Diagramm, das die einzelnen Arbeitstakte der Schwenkkolbenmaschine in
Fig. 18 veranschaulicht; - Fig. 23
- eine perspektivische Gesamtansicht einer Schwenkkolbenmaschine gemäß einem weiteren Ausführungsbeispiel;
- Fig. 24
- einen Schnitt durch die Schwenkkolbenmaschine in
Fig. 23 entlang der Linie XXIV-XXIV inFig. 23 ; - Fig. 25
- einen Längsschnitt durch die Schwenkkolbenmaschine in
Fig. 23 , wobei die Schnittebene inFig. 25 senkrecht zur Schnittebene inFig. 24 verläuft; - Fig. 26
- eine mit
Fig. 25 vergleichbare Schnittdarstellung des Gehäuses gemäß einem gegenüberFig. 25 abgewandelten Ausführungsbeispiel; - Fig. 27
- eine
Fig. 26 entsprechende Darstellung der Schwenkkolbenmaschine gemäßFigur 26 , wobei inFig. 27 zusätzlich der Kolbenkäfig mit den darin aufgenommenen Kolben im Längsschnitt dargestellt ist; und - Fig. 28
- eine Darstellung ähnlich zu
Fig. 24 , wobei jedoch der Kolbenkäfig in einer um 90° versetzten Drehstellung in Bezug aufFig. 24 im Längsschnitt dargestellt ist.
- Fig. 1
- an overall perspective view of a rotary piston machine, according to a first embodiment;
- Fig. 2
- a view of the oscillating piston engine in
Fig. 1 in the direction of the arrows II inFig. 1 ; - Fig. 3
- a longitudinal section through the oscillating piston engine along a plane parallel to the axis of rotation and perpendicular to the pivot axis, wherein the pistons of the oscillating piston engine are shown in a first operating position;
- Fig. 4
- a representation of the oscillating piston engine in the same operating position of the piston as in
Fig. 3 , slightly perspective and the pistons not in section; - Fig. 5
- one with
Fig. 4 comparable representation of the oscillating piston engine, wherein the pistons are shown in a second operating position; - Fig. 7
- a representation of the oscillating piston engine in the same operating position of the piston as in
Fig. 6 , slightly perspective and the pistons not in section; - Fig. 8
- a section through the oscillating piston engine along the line VIII-VIII in
Fig. 3 ; - Fig. 9
- a section through the oscillating piston engine along the line IX-IX in
Fig. 3 ; - Fig. 10
- a longitudinal section along the line XX in
Fig. 3 by the oscillating piston engine according to theFig. 1 to 9 ; - Fig. 10A
- one with
Fig. 10 comparable representation of a modified embodiment of the oscillating piston engine; - Fig. 11
- a longitudinal section through the oscillating piston engine comparable to
Fig. 3 or4 but with the piston cage and pistons not shown in section; - Fig. 12
- a view of the oscillating piston engine, in which a housing half is removed;
- Fig. 13
- a perspective view of the arrangement of piston cage and piston in isolation and in perspective;
- Fig. 13
- a perspective view of the arrangement of piston cage and piston in isolation and in perspective;
- Fig. 14
- a perspective view of an inner side of a housing half of the oscillating piston engine in isolation;
- Fig. 15a) to d)
- various perspective views or sections of a piston of the oscillating piston engine including running member in isolation;
- Fig. 16
- a longitudinal section through a rotary piston machine according to another embodiment;
- Fig. 17
- a longitudinal section through the oscillating piston engine in
Fig. 17 in a section along a plane that is in relation to the cutting plane inFig. 16 rotated by 90 °; - Fig. 18
- an overall perspective view of a rotary piston machine according to another embodiment;
- Fig. 19
- a longitudinal section through the oscillating piston engine in
Fig. 18 along a plane parallel to the axis of rotation and perpendicular to the pivot axis; - Fig. 20
- a perspective view of a half of the oscillating piston engine in
Fig. 18 ; - Fig. 21
- a perspective view of the arrangement of piston cage and piston of the oscillating piston engine in
Fig. 18 in isolation and in perspective; - Fig. 22
- a diagram showing the individual working cycles of the oscillating piston engine in
Fig. 18 illustrated; - Fig. 23
- an overall perspective view of a rotary piston machine according to another embodiment;
- Fig. 24
- a section through the oscillating piston engine in
Fig. 23 along the line XXIV-XXIV inFig. 23 ; - Fig. 25
- a longitudinal section through the oscillating piston engine in
Fig. 23 , where the cutting plane inFig. 25 perpendicular to the cutting plane inFig. 24 runs; - Fig. 26
- one with
Fig. 25 Comparable sectional view of the housing according to one oppositeFig. 25 modified embodiment; - Fig. 27
- a
Fig. 26 corresponding representation of the oscillating piston engine according toFIG. 26 , where inFig. 27 in addition, the piston cage with the piston received therein is shown in longitudinal section; and - Fig. 28
- a representation similar to
Fig. 24 However, wherein the piston cage in a 90 ° offset rotational position with respect toFig. 24 is shown in longitudinal section.
In
Die Schwenkkolbenmaschine 10 ist in dem vorliegenden Ausführungsbeispiel als Brennkraftmaschine ausgelegt.The
Die Schwenkkolbenmaschine 10 weist ein Gehäuse 12 auf, das aus zwei Gehäusehälften 14 und 16 zusammengesetzt ist. Die Gehäusehälften 14 und 16 weisen jeweils einen Flansch 18a bzw. 18b auf, über den die Gehäusehälften 14 und 16 lösbar miteinander verbunden sind.The
Am Gehäuse 12 sind bezüglich dem Gehäusemittelpunkt diametral gegenüberliegend Einlassstutzen 20 und 24 für Frischluft/Brennstoff angeordnet, deren Öffnungen durch das Gehäuse hindurchgehen (vgl.
Des Weiteren sind am Gehäuse eine Mehrzahl an Anschlüssen 28 bis 38 für die Zufuhr und Abfuhr bzw. Zirkulation eines Kühl-/Schmiermediums durch das Innere der Schwenkkolbenmaschine 10 angeordnet.Furthermore, a plurality of
Bei dem Ausführungsbeispiel der Schwenkkolbenmaschine 10 ist eine Gehäuseinnenwand 39 im Wesentlichen kugelförmig ausgebildet bzw. besitzt Kugelsymmetrie, wie beispielsweise aus
Im Innern des Gehäuses 12 sind vier Kolben 40 bis 46 angeordnet, die in dem Gehäuse 12 gemeinsam um eine Drehachse 48 gemäß einem Pfeil 49 (
Sowohl die Drehachse 48 als auch die Schwenkachse 50, die als geometrische Achsen zu verstehen sind, gehen durch den Gehäusemittelpunkt des kugelförmigen Gehäuses 12 hindurch. Des Weiteren steht die Schwenkachse 50 stets senkrecht auf der Drehachse 48, läuft um Letztere jedoch entsprechend der Umlaufbewegung der Kolben 40 bis 46 ebenfalls um die Drehachse 48 um.Both the axis of
Von den Kolben 40 bis 46 stehen sich jeweils zwei Kolben bezüglich der Schwenkachse 50 diametral gegenüber, und zwar in jeder Schwenkstellung der Kolben 40 bis 46, wobei dies die Kolben 40 und 44 einerseits und die Kolben 42 und 46 andererseits sind. Die Kolben 40 bis 46 sind jedoch in dem Gehäuse 12 einzeln gelagert, d.h. nicht paarweise miteinander starr verbunden.Of the
Jeder der Kolben 40 bis 46 weist eine Endfläche auf, d.h. der Kolben weist eine Endfläche 52, der Kolben 42 eine Endfläche 54, der Kolben 44 eine Endfläche 56 und der Kolben 46 eine Endfläche 58 auf.Each of the
Jeweils einander zugewandte Endflächen, das sind im vorliegenden Fall die Endflächen 54 und 56 der Kolben 42 und 44 sowie die Endflächen 52 und 58 der Kolben 40 und 46, begrenzen jeweils eine Arbeitskammer 60 und 62, die als Brennkammern dienen. Die Drehachse 48 geht durch beide Arbeitskammern 60, 62 hindurch, und zwar vorzugsweise in jeder Stellung der Kolben mittig.Each facing end surfaces, which in the present case, the end surfaces 54 and 56 of the
Da jeweils benachbarte der Kolben 40 bis 46 beim Umlaufen um die Drehachse 48 zueinander gegensinnige Schwenkbewegungen ausführen, vergrößern und verkleinern sich die Arbeitskammern 60 und 62 stets gleichsinnig zueinander.Since in each case
Beispielsweise von dem in
Es versteht sich, dass die Kolben 40 und 46 beim Verschwenken um die Schwenkachse 50 stets links von der Linie VIII-VIII in
Um die Schwenkbewegungen der Kolben 40 bis 46 um die Schwenkachse 50 aus der Umlaufbewegung der Kolben 40 bis 46 um die Drehachse 48 abzuleiten, weist jeder Kolben 40 bis 46 ein Lauforgan 64 (Kolben 40), 66 (Kolben 42), 68 (Kolben 44) und 70 (Kolben 46) auf. Die Lauforgane 64 bis 70 sind Kugeln, die jeweils in einer Kugelpfanne 72, wie in
Die Kugeln 64 bis 70 können, wie in
Auf jeden Fall sind die Kugeln 64 bis 70 in den Kugelpfannen 72 in allen Richtungen um ihren jeweiligen Kugelmittelpunkt frei drehbar.In any case, the
Den Lauforganen bzw. Kugeln 64 bis 70 sind zwei Steuerkurven zugeordnet, in denen die Kugeln 64 bis 70 laufen. Genauer gesagt ist den Kugeln 64 und 70 der Kolben 40 und 46 eine erste Steuerkurve 76 zugeordnet, die als Nut mit teilkreisförmigem Querschnitt in der Gehäuseinnenwand 39 ausgebildet ist. Eine entsprechende Steuerkurve 78 ist den Lauforganen bzw. Kugeln 66 und 68 der Kolben 42 und 44 zugeordnet.The running members or
Die Kugeln 64 und 70 laufen somit in derselben Steuerkurve 76, und die Kugeln 66 und 68 in derselben Steuerkurve 78. Die Kugeln 64 und 70 einerseits und die Kugeln 66 und 68 andererseits sind dabei jeweils untereinander bezüglich der Drehachse 48 um 180° versetzt.The
Die Steuerkurven 76 und 78 sind mit bezüglich der Drehachse 48 zumindest näherungsweise maximalem Abstand angeordnet, wie aus
In
Die Kolben 40 bis 46 sind in dem Gehäuse 12 in einem um die Drehachse 48 gemeinsam mit den Kolben 40 bis 46 umlaufenden Kolbenkäfig 80 gelagert, der nachfolgend mit weiteren Einzelheiten der Kolben 40 bis 46 näher beschrieben wird. In
Der Kolbenkäfig 80 ist in dem gezeigten Ausführungsbeispiel und bevorzugt ein einstückiges Bauteil, wobei anstelle einer einstückigen Bauweise jedoch auch eine mehrstückige Bauweise denkbar ist.The
Der Kolbenkäfig 80 erstreckt sich entlang der Drehachse 48 über die gesamte Länge des Gehäuses 12, wobei Wellenfortsätze 86 und 88 des Kolbenkäfigs 80 aus dem Gehäuse herausragen.The
Der Kolbenkäfig 80 weist jeweils einen sich an die Wellenfortsätze 86 und 88 anschließenden Hauptlagerabschnitt 82 bzw. 84 auf, über die der Kolbenkäfig 80 in dem Gehäuse 12 drehbar um die Drehachse 48 gelagert ist. Die Lagerabschnitte 82 und 84 sind gehäusemittig über einen Mittelabschnitt 90 verbunden, der einen sich entlang der Schwenkachse 50 erstreckenden zapfenartigen Abschnitt 92 aufweist, an dem die Kolben 40 bis 46 zum Gehäusemittelpunkt bzw. zur Schwenkachse 50 hin gelagert sind.The
Gemäß
Die Bohrungen 94 und 96 begrenzen zusammen mit den Endflächen 52 bis 58 die Arbeitskammern 60 und 62.The
In den Bohrungen 94 und 96 des Kolbenkäfigs 80 sind die Kolben 40 bis 46 drehfest mit dem Kolbenkäfig 80 verbunden, so dass die Kolben 40 bis 46 gemeinsam mit dem Kolbenkäfig 80 um die Drehachse 48 umlaufen, während die Kolben 40 bis 46 entsprechend ihrer Schwenkbewegungen um die Schwenkachse 50 in den Bohrungen 94 und 96 gleitend beweglich sind, um die einzelnen Arbeitstakte des Einlassens, Verdichtens, Expandierens und Ausstoßens auszuführen.In the
Die Kolben 40 bis 46 sind im Wesentlichen, wie in
Die Anordnung aus Kolbenkäfig 80, dem Kolben 40 bis 46 nebst den Lauforganen 64 bis 70 bildet den "Innenmotor" der Schwenkkolbenmaschine 10, d.h. diese Anordnung umfasst alle beweglichen Teile der Schwenkkolbenmaschine 10.The arrangement of
In den Lagerabschnitten 82 und 84 des Kolbenkäfigs 80 sind, wie beispielsweise in
Gemäß
Die Bohrung 110 erweitert sich an ihren beiden Enden trompetenartig, um die Verteilung des Kühl-/Schmiermediums im Zentrum des Gehäuses 12 noch zu verbessern.The
Gemäß
Wie weiterhin aus
Die um 180° bezüglich der Drehachse 48 versetzte Anordnung der Anschlussstutzen 20 und 22 gegenüber den Anschlussstutzen 24 und 26 dient dazu, dass zumindest in einer der Arbeitskammern 60 und 62 beim Umlaufen der Kolben 40 bis 46 um die Drehachse 48 um 360° stets ein Expansionsvorgang erfolgt. Wenn also in der Arbeitskammer 60 gerade ein Arbeitstakt des Expandierens stattfindet, findet in der Arbeitskammer 62 ein Arbeitstakt des Ausstoßens verbrannten Brennstoff-Luftgemisches auf, und umgekehrt.The offset by 180 ° with respect to the axis of
Nachfolgend wird die Funktionsweise der Schwenkkolbenmaschine 10 beschrieben.The operation of the oscillating-
Ausgehend von der Betriebsstellung der Kolben 40 bis 46 gemäß
Nach einer weiteren Drehung um 45° um die Drehachse 48 nehmen dann die Kolben 40 bis 46 die in
Nach einer vollen Drehung um 360° haben somit in jeder der Arbeitskammern 60 und 62 einmal die vier Arbeitstakte des Einlassens, Verdichtens, Expandierens und Ausstoßens stattgefunden.Thus, after a full 360 ° turn, each of the working
In
In
Während das Gehäuse 12 der Schwenkkolbenmaschine 10 und der Schwenkkolbenmaschine 10' Kugelsymmetrie besitzt, ist das Gehäuse 12" der Schwenkkolbenmaschine 10" oblong ausgebildet. Genauer gesagt besteht das Gehäuse 12" aus zwei Halbkugeln 13" und 15", zwischen die ein sich in Richtung der Drehachse 48" erstreckender länglicher Abschnitt 17" eingefügt ist. Auf diese Weise wird das Gehäuse 12" in Richtung der Drehachse 48" gegenüber der Ausführung des Gehäuses 12 länger, was folgende Maßnahmen ermöglicht.While the
So ist am Mittelabschnitt 90" des Kolbenkäfigs 80", der gemäß
Im Gehäuse ist ferner ein Einlass 136 für Frischluft vorgesehen, die durch eine beispielsweise übliche Ventilvorrichtung 138 geschlossen und geöffnet werden kann. Durch den Einlass 136 kann nun Frischluft, insbesondere vorkomprimierte Frischluft, in das Innere des Hohlzapfens 122 eingeleitet werden, und je nach Drehstellung des Hohlzapfens 122 relativ zu den Öffnungen 126, 128 wird dann die Frischluft in die Arbeitskammern 60" oder 62" eingeleitet, und zwar zusätzlich zu der Zufuhr von Brennstoff-Luftgemisch durch die Anschlussstutzen 20" und 24". Auf diese Weise ist die Schwenkkolbenmaschine 10" ein Motor mit sog. Aufladung.In the housing, an
Die Schneckenverzahnung 132 und die Zahnung 134 sind entsprechend so auszulegen, dass die Drehbewegung des Hohlzapfens 122 um die Schwenkachse 50" mit den Kolbenstellungen der Kolben 40" bis 46" in geeigneter Weise synchronisiert ist. Das heißt, die Frischluftzufuhr durch den Hohlzapfen 122 in die Arbeitskammer 60" bzw. in die Arbeitskammer 62" sollte vorzugsweise dann erfolgen bzw. die Öffnung 124 sollte mit der jeweiligen Öffnung 126 und 128 dann kommunizieren, wenn das Zünden des durch die Einlassstutzen 20" und 24" eingelassener Brennstoff-Luftgemisch gerade vor seiner Zündung steht. Eine 360°-Drehung des Hohlzapfens um die Drehachse 48" sollte eine 360°-Drehung desselben um die Schwenkachse 50 hervorrufen.The
Im Übrigen entspricht die Schwenkkolbenmaschine 10" den Ausgestaltungen der Schwenkkolbenmaschine 10 oder 10', so dass auf die dortige Beschreibung verwiesen wird.Incidentally, the
In
Die Schwenkkolbenmaschine 210 weist in dem Gehäuse 212 vier Kolben 240 bis 246 auf, wobei die Kolben 240 und 246 als erstes Kolbenpaar und die Kolben 242 und 244 als zweites Kolbenpaar bezüglich der Drehachse 248 so angeordnet sind, dass die Schwenkbewegungen der Kolben 240 und 246 in einer ersten Ebene und die Schwenkbewegungen der Kolben 242 und 244 in einer zweiten Ebene erfolgen, wobei die erste und die zweite Ebene bezüglich der Drehachse 248 relativ zueinander um einen Winkel ungleich 0°, und im vorliegenden Ausführungsbeispiel um 90° zueinander verdreht sind.The
Dies bedeutet, dass die Schwenkachse der Kolben 240 und 246 senkrecht zur Schwenkachse der Kolben 242 und 244 verläuft. In
Die um 90° bezüglich der Drehachse 248 versetzte Anordnung der Kolbenpaare 240, 246 und 242, 244 wird auch aus
Der Kolbenkäfig 280 unterscheidet sich entsprechend von dem Kolbenkäfig 80 der Schwenkkolbenmaschine 10 dadurch, dass die die Arbeitskammern 260 und 262 definierenden Bohrungen 294 und 296 orthogonal zueinander verlaufen.The
Durch die orthogonal zueinander liegende Anordnung der Arbeitskammern 260 und 262 aufgrund der entsprechend orthogonal zueinander verlaufenden Anordnung der Paare von Kolben 240, 246 einerseits und 242, 244 andererseits ist der maximale Öffnungswinkel der jeweiligen Paare von Kolben 240, 246 bzw. 242, 244 und damit das maximale Volumen der Arbeitskammern 260, 262 gegenüber der Schwenkkolbenmaschine 10 in
Dies ergibt bspw. ein Vergleich der
Während bei der Schwenkkolbenmaschine 10 alle vier Kolben 40 bis 46 um die gemeinsame Schwenkachse 50 verschwenkbar sind oder mit anderen Worten die Schwenkbewegungen der Kolben 40 bis 46 in derselben Ebene verlaufen und somit die Arbeitskammern 60 und 62 in einer selben Ebene angeordnet sind, bedeutet dies, dass sich die Lauforgane 64 und 66 einerseits und 68 und 70 andererseits bei dieser Anordnung etwa auf der Orthogonalen zur Drehachse 48 sehr nahe kommen, wodurch die zugehörigen Steuerkurven 76 und 78 so ausgebildet sein müssen, dass in der UT-Stellung die Lauforgane 64 und 66 einerseits und 68 und 70 andererseits nicht miteinander kollidieren.While in the
Durch die um 90° versetzte Anordnung der Kolbenpaare 240, 246 einerseits und 242, 244 andererseits gemäß der Schwenkkolbenmaschine 210 besteht dieses Problem nicht, da auch die Lauforgäne 264, 266 und 268, 270 um 90° zueinander versetzt in ihren Steuerkurven 276 bzw. 278 laufen. Dadurch können die Steuerkurven 276, 278 noch näher an die Orthogonale (Linie A in
Wie bei der Schwenkkolbenmaschine 10 vergrößern und verkleinern sich die Arbeitskammern 260, 262 der Schwenkkolbenmaschine 210 gleichsinnig. Bspw. wenn die Arbeitskammer 260 im Zuge eines Arbeitstaktes expandiert, expandiert die Arbeitskammer 262, um neues Frischgas anzusaugen. Die beiden Vorgänge erfolgen somit zeitlich gleichzeitig, jedoch räumlich um 90° zueinander versetzt. Es kommt dadurch somit immer und erwünschtermaßen zur Öffnung und Schließung beider Arbeitskammern 260, 262 zur gleichen Zeit.As with the
Gemäß
In
In den Diagrammen sind die Steuerkurven 276 und 278 abgewickelt dargestellt, wobei sich aus dieser Darstellung ergibt, dass die beiden Steuerkurven 276 und 278 nunmehr schlangenförmig parallel zueinander verlaufen, während die Steuerkurven 76 und 78 der Schwenkkolbenmaschine 10 spiegelsymmetrisch bezüglich einer Mittelebene durch den Gehäusemittelpunkt des Gehäuses 12 senkrecht zur Drehachse 48 spiegelsymmetrisch ausgebildet bzw. angeordnet sind.In the diagrams, the
In
In den
Bei der Schwenkkolbenmaschine 310 ist die Abtriebs- und/oder Antriebswelle nicht konzentrisch auf der Drehachse 348 angeordnet, sondern mit seitlichem Abstand zu dieser. Der Kolbenkäfig 380 ist stirnseitig und konzentrisch zur Drehachse 348 mit einem Zahnkranz 440 versehen, der mit einem mit der Antriebs- und/oder Antriebswelle 387 drehfest verbundenen Zahnkranz 442 kämmt. Zusätzlich zu dem Zahnkranz 440 kann der Kolbenkäfig auf der dem Zahnkranz 440 gegenüberliegenden Stirnseite mit einem zweiten Zahnkranz 444 versehen sein. Die Antriebs- und/oder Abtriebswelle 387 ist zwischen ihren Wellenfortsätzen 386 und 388 durchgehend ausgebildet, so dass eine Antriebsverbindung mit dem Kolbenkäfig 380 nur über einen der Zahnkränze 440 bzw. 444 erforderlich ist, wie es in
Da bei der Schwenkkolbenmaschine 310 die Antriebs- und/oder Abtriebswelle 387 nicht auf der Drehachse 348 liegt, um die der Kolbenkäfig 380 und die darin befindlichen Kolben 340 bis 346 rotieren, können die Zündkerzen 418 und 420 an einem jeweiligen stirnseitigen Gehäusedeckel 448 bzw. 450, also an nicht rotierenden Teilen, montiert werden und müssen insbesondere nicht mit dem Kolbenkäfig 380 mitrotieren. Die Gehäusedeckel 448 und 450 sind Teil des Gehäuses 312 abnehmbar.Since in the
Ebenso können bei der Schwenkkolbenmaschine 310, wie dargestellt, Einspritzdüsen 452 und 454 an den stirnseitigen Gehäusedeckeln 448 und 450 den beiden Arbeitskammern 360 und 362 (vgl.
Auch können bei dieser Ausgestaltung Einlassstutzen 490, 492 für Luft und Auslassstutzen 494, 496 für verbranntes Gemisch stirnseitig an dem Gehäusedeckel 448 und 450 vorgesehen werden.Also, in this embodiment,
Ein weiterer Unterschied der Schwenkkolbenmaschine 310 zu den zuvor beschriebenen Schwenkkolbenmaschinen 10, 10', 10" und 210 besteht in der Ausgestaltung der Lauforgane 364 bis 370, die den Kolben 340 bis 346 zugeordnet sind.Another difference between the
Die Lauforgane 364 bis 370 sind jeweils als Rolle ausgebildet, wie hiernach mit Bezug auf das Lauforgan 364 in Form der Rolle 456 beschrieben wird. Die Rolle 456 weist eine Lauffläche 458 auf, die quer zur Umfangsrichtung der Rolle 456 teilkreisförmig ist. Die Rolle 456 ist über einen Zapfen 460 mit dem Kolben 340 verbunden, wobei die Rolle 456 um den Zapfen 460 relativ zum Kolben 340 drehbar ist. Die Welle 460 verläuft parallel zur Drehachse 348. Die Rolle 456 ist auf dem Zapfen 460 dazu vorzugsweise über ein Nadellager, insbesondere ein Präzisions-Nadellager, drehbar gelagert. Die Rolle 456 ist ferner über an dem Zapfen 460 endseitig angeordnete Sicherungsringe lösbar mit dem Kolben 340 verbunden.The running
Wie bei den zuvor beschriebenen Schwenkkolbenmaschinen 10, 10', 10" und 210 läuft jedes Lauforgan 364 bis 370 in Form einer jeweiligen Rolle 456 in einer Steuerkurve 376 bzw. 378, die in die Lauforgane 364 und 370 entsprechend teilweise eingreifen und entlang der sie entsprechend geführt sind.As in the previously described
Die Anordnung der Kolben 340 bis 346 kann entgegen der Darstellung auch gemäß der Anordnung der Kolben 240 bis 246 der Schwenkkolbenmaschine 210 gewählt werden, das heißt so, dass die Schwenkkolben 340 und 346 gegenüber den Kolben 342 und 344 um 90° bezüglich der Drehachse 348 versetzt zueinander angeordnet sind. In diesem Fall können auch die Steuerkurven 376 und 378 wie bei der Schwenkkolbenmaschine 210 mit zwei Wellenbergen und zwei Wellentälern ausgebildet sein, um größere Schwenkhübe der Kolben 340 bis 346 zu erreichen, wie dies bereits mit Bezug auf die Schwenkkolbenmaschine 210 beschrieben wurde.The arrangement of the
Des Weiteren ist es möglich, bei allen zuvor beschriebenen Schwenkkolbenmaschinen die von den beiden Arbeitskammern abgewandten Kammern zwischen den Kolben als Vordruckräume zu nutzen, wie dies bei der Schwenkkolbenmaschine gemäß
Claims (23)
- An oscillating piston machine, comprising a housing (12; 212; 312) in which a first and at least a second piston (40, 46; 240, 246; 340, 346) are arranged, which pistons (40, 46; 240, 246; 340, 346) can rotate together in the housing (12; 212; 312) about a rotational axis (48; 248; 348) which is fixed to the housing and which pistons, as they rotate about the rotational axis (48; 248; 348), carry out reciprocating oscillating movements in opposite directions to one another about an oscillation axis (50; 251; 350) which extends perpendicularly to the rotational axis (48; 248; 348) and through the centre of the housing, wherein the first piston (40; 240; 340) has a first end face (52; 252; 352) and the at least second piston (46; 246; 346) has a second end face (58; 258; 358) which faces the first end face (52; 252; 352), wherein the end faces (52, 58; 252, 258; 352, 358) bound a working chamber (60; 260; 360), wherein the pistons (40, 46; 240, 246; 340, 346) are arranged in such a way that the rotational axis (48; 248; 348) extends through the working chamber (60; 260; 360), characterized in that the first and the at least second piston (40, 46; 240, 246; 340, 346) are mounted in a sliding fashion in a piston cage (80; 280; 380) which is arranged in the housing (12; 212; 312) concentrically with respect to the rotational axis (48; 248; 348) so as to be rotatable about said rotational axis (48; 248; 348), wherein the piston cage (80; 280; 380) is connected in a rotationally fixed fashion to the first and at least second piston (40, 46; 240, 246; 340, 346) with respect to the rotating movement about the rotational axis (48; 248; 348), and that the piston cage (80; 280) has, approximately perpendicularly with respect to the rotational axis (48; 248), a bore (94; 294) in which the first and at least second pistons (40, 46; 240, 246) are received partially and so as to slide therein and which bounds the working chamber (60; 260) in the circumferential direction.
- The oscillating piston machine of Claim 1, characterized in that the first and the second end faces (52, 58; 252, 258; 352, 358) are of circular design.
- The oscillating piston machine of Claim 1 or 2, characterized in that the first and the at least second piston (40, 46; 240, 246; 346) are of essentially arcuate design.
- The oscillating piston machine of anyone of Claims 1 through 3, characterized in that the first piston (40; 240; 340) and/or the at least second piston (46; 246; 346) have at least one running member (64, 70; 264, 270; 364, 370) which, as the first and/or at least second piston (40, 46; 240, 246; 340, 346) rotates, is guided along a correspondingly designed control cam (76; 276; 376) in order to generate the oscillating movements of the first and at least second piston (40, 46; 240, 246; 340, 346), wherein the control cam (76; 276; 376) is arranged on the housing (12; 212; 312) at an at least approximately maximum distance from the rotational axis (48; 248; 348).
- The oscillating piston machine of Claim 4, characterized in that the at least one running member (64, 70; 264, 270) is a ball which is rotatably mounted in a ball socket (72; 272) on an outer side, facing the housing (12; 212), of the first or at least second piston (40, 46; 240, 246), and in that the control cam (76; 276) is embodied as a groove with a pitch-circle-shaped cross section in the housing (12; 212), into which groove the ball partially engages.
- The oscillating piston machine of Claim 4, characterized in that the at least one running member (364, 370) is a roller (456) whose running face (458) is constructed in the form of a pitch circle transversely with respect to the circumferential direction of the roller (456), wherein the roller (456) is mounted on a shaft (460) which is connected at the end side to the first or second piston (340, 346), and in that the control cam (376) is embodied as a groove with a cross section in the form of part of a circle in the housing, into which groove the roller (456) partially engages.
- The oscillating piston machine of any one of Claims 1 through 6, characterized in that the piston cage (80; 280; 380) is connected to at least one drive shaft and/or output shaft which extends parallel to the rotational axis (48; 248; 348).
- The oscillating piston machine of Claim 7, characterized in that the at least one drive shaft and/or output shaft is arranged concentrically with respect to the rotational axis (48; 248) and is connected in a rotationally fixed fashion to the piston cage (80; 280).
- The oscillating piston machine of Claim 7, characterized in that the at least one drive shaft and/or output shaft is arranged at a lateral distance from the rotational axis (348) and is connected to the piston cage (380) by means of at least one transmission mechanism arrangement.
- The oscillating piston machine of anyone of Claims 1 through 9, characterized in that a duct (114; 314) passes through the piston cage (80; 280), said duct (114; 314) opening at one end into the bore (94; 294) and at the other end opening into the housing (12; 212) in order to communicate with an inlet opening or with an outlet opening in the housing (12; 212) depending on the rotational position of the piston cage (80; 280).
- The oscillating piston machine of anyone of Claims 1 through 10, characterized in that the piston cage (80; 280) has at least one duct (102; 302) for a medium, in particular cooling medium/lubricating medium which extends at least partially over the circumference and through the interior of the piston cage (80; 280).
- The oscillating piston machine of anyone of Claims 1 through 11, characterized in that a bore (110) which is preferably widened in the direction of its ends passes through the piston cage (80) at the level of the oscillation axis (50), in the direction of said oscillation axis (50).
- The oscillating piston machine of anyone of Claims 1 through 12, characterized in that a third and fourth piston (42, 44; 242, 244; 342, 344) are arranged in the housing (12; 212; 312), which pistons (42, 44; 242, 244; 342, 344) can oscillate about the same oscillation axis (50; 251; 350) or an oscillation axis (250) which is different therefrom, and can rotate with the first and second pistons (40, 46; 240, 246; 340, 346) about the rotational axis (48; 248; 348) and define a second working chamber (62; 262; 352).
- The oscillating piston machine of Claim 13, characterized in that the four pistons (40-46; 240-246; 340-346) are arranged in such a way that as the pistons (40-46; 240-246; 340-346) rotate about the rotational axis (48; 248; 348), the first and second working chambers (60, 62; 260, 262; 360, 362) increase and decrease in size in the same direction.
- The oscillating piston machine of Claim 13 or 14, characterized in that the first and second pistons (40, 46; 340, 346) and the third and fourth pistons (42, 44; 342, 344) are arranged with respect to the rotational axis (48; 348) in such a way that the oscillating movements of all the pistons (40-46; 340-346) occur in the same plane.
- The oscillating piston machine of Claim 13 or 14, characterized in that the first and second pistons (240, 246) and the third and fourth pistons (242, 244) are arranged with respect to the rotational axis (248) in such a way that the oscillating movements of the first and second pistons (240, 246) occur in a first plane, and the oscillating movements of the third and fourth pistons (242, 244) occur in a second plane, wherein the first and second planes are rotated relative to one another by an angle which is unequal to 0° with respect to the rotational axis (248).
- The oscillating piston machine of Claim 16, characterized in that the angle is at least approximately 90°.
- The oscillating piston machine of anyone of Claims 13 through 17, characterized in that the piston cage (80; 280; 380) extends on either side of the oscillation axis (50; 350) or oscillation axes (250, 251) and also accommodates the third and fourth pistons (42, 44; 242, 244; 342, 344).
- The oscillating piston machine of anyone of Claims 1 through 18, characterized in that a housing inner wall (39; 239) of the housing is essentially spherical.
- The oscillating piston machine of anyone of Claims 1 through 19, characterized in that a housing inner wall (39") of the housing (12") is oblong in section in the direction of the rotational axis (48") along a plane which includes the rotational axis (48").
- The oscillating piston machine of Claim 20, characterized in that a hollow pin (122), which can rotate about the oscillation axis (50") and which has, in its wall, an opening (124) which communicates with the first working chamber (60") or, if appropriate, with the second working chamber (62") as a function of the rotary position of the hollow pin (122), is arranged in the housing (12").
- The oscillating piston machine of Claim 21, characterized in that the hollow pin (122) is connected to a transmission mechanism (130) which, when the pistons (40"-46") rotate about the rotational axis (48"), causes the hollow pin (122) to rotate about the oscillation axis (50").
- The oscillating piston machine of Claim 22, characterized in that the transmission mechanism (130) has a worm toothing or worm gear (132) which is connected to the hollow pin (122) and meshes with at least one toothing (134) which is arranged on the housing (12") and extends about the rotational axis (48").
Priority Applications (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
PL05822093T PL1856375T3 (en) | 2005-02-25 | 2005-12-09 | Oscillating piston engine |
Applications Claiming Priority (3)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE102005010775A DE102005010775B3 (en) | 2005-02-25 | 2005-02-25 | Rotatable reciprocating engine for use as compressor, has two pistons revolving in housing, in which centrifugal forces arising due to revolution of pistons act in pivoting direction of pistons during revolution of pistons |
DE102005024751.2A DE102005024751B4 (en) | 2005-02-25 | 2005-05-24 | Oscillating piston engine |
PCT/EP2005/013254 WO2006089576A1 (en) | 2005-02-25 | 2005-12-09 | Oscillating piston engine |
Publications (2)
Publication Number | Publication Date |
---|---|
EP1856375A1 EP1856375A1 (en) | 2007-11-21 |
EP1856375B1 true EP1856375B1 (en) | 2010-05-19 |
Family
ID=36000796
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP05822093A Not-in-force EP1856375B1 (en) | 2005-02-25 | 2005-12-09 | Oscillating piston engine |
Country Status (8)
Country | Link |
---|---|
US (1) | US7658168B2 (en) |
EP (1) | EP1856375B1 (en) |
JP (1) | JP4818280B2 (en) |
AT (1) | ATE468472T1 (en) |
DE (1) | DE502005009616D1 (en) |
ES (1) | ES2346552T3 (en) |
PL (1) | PL1856375T3 (en) |
WO (1) | WO2006089576A1 (en) |
Families Citing this family (9)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE102006009198B4 (en) * | 2006-02-22 | 2010-03-25 | Hüttlin, Herbert, Dr. h.c. | Oscillating piston engine |
DE102007030853A1 (en) | 2007-06-26 | 2009-01-02 | Hüttlin, Herbert, Dr. h.c. | Rotary piston engine e.g. internal combustion engine, has opening partially overlapping gas inlet opening in azimuthal angle region, and control element that is position adjustable to change dimension, initial angle or end angle of region |
DE102007039309B4 (en) * | 2007-08-13 | 2010-08-19 | Hüttlin, Herbert, Dr. h.c. | Rotary piston engine |
DE102007054321A1 (en) * | 2007-10-31 | 2009-05-07 | Hüttlin, Herbert, Dr. h.c. | piston engine |
CN101555826B (en) * | 2008-11-13 | 2011-07-20 | 靳北彪 | Arc cylinder rotary motor |
US8418672B2 (en) * | 2010-03-04 | 2013-04-16 | James L. Groves | High leverage rotary internal combustion engine |
DE102010022012A1 (en) * | 2010-05-25 | 2011-12-01 | Herbert Hüttlin | Aggregate, in particular hybrid engine, power generator or compressor |
DE102012111812B3 (en) | 2012-12-05 | 2013-12-12 | Herbert Hüttlin | Aggregate, in particular internal combustion engine or compressor |
DE102015103734A1 (en) * | 2015-03-13 | 2016-09-15 | Innowatt GmbH | Oscillating piston engine |
Family Cites Families (8)
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 (en) * | 1975-08-26 | 1977-03-25 | Etienne Charles | Pump for motor with spherical working chamber - has wedge shaped pistons contacting inside surface and mounted on drive spindle extending through side |
DK1472435T3 (en) * | 2002-02-06 | 2007-02-12 | Herbert Huettlin | Swing Piston Engine |
RU2403400C2 (en) * | 2004-04-06 | 2010-11-10 | Перафес Акциенгезелльшафт | Rotary piston engine and transport facility with such engine |
DE102005010775B3 (en) * | 2005-02-25 | 2006-04-20 | Hüttlin, Herbert, Dr. h.c. | Rotatable reciprocating engine for use as compressor, has two pistons revolving in housing, in which centrifugal forces arising due to revolution of pistons act in pivoting direction of pistons during revolution of pistons |
DE102006009197B4 (en) * | 2006-02-22 | 2008-09-11 | Hüttlin, Herbert, Dr. h.c. | Oscillating piston engine |
DE102006009198B4 (en) * | 2006-02-22 | 2010-03-25 | Hüttlin, Herbert, Dr. h.c. | Oscillating piston engine |
-
2005
- 2005-12-09 JP JP2007556497A patent/JP4818280B2/en not_active Expired - Fee Related
- 2005-12-09 PL PL05822093T patent/PL1856375T3/en unknown
- 2005-12-09 AT AT05822093T patent/ATE468472T1/en active
- 2005-12-09 ES ES05822093T patent/ES2346552T3/en active Active
- 2005-12-09 EP EP05822093A patent/EP1856375B1/en not_active Not-in-force
- 2005-12-09 WO PCT/EP2005/013254 patent/WO2006089576A1/en active Application Filing
- 2005-12-09 DE DE502005009616T patent/DE502005009616D1/en active Active
-
2007
- 2007-08-24 US US11/844,595 patent/US7658168B2/en not_active Expired - Fee Related
Also Published As
Publication number | Publication date |
---|---|
US7658168B2 (en) | 2010-02-09 |
ATE468472T1 (en) | 2010-06-15 |
JP2008531904A (en) | 2008-08-14 |
PL1856375T3 (en) | 2010-10-29 |
DE502005009616D1 (en) | 2010-07-01 |
WO2006089576A1 (en) | 2006-08-31 |
JP4818280B2 (en) | 2011-11-16 |
EP1856375A1 (en) | 2007-11-21 |
US20080041225A1 (en) | 2008-02-21 |
ES2346552T3 (en) | 2010-10-18 |
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