EP1472435B1 - Moteur a pistons oscillants - Google Patents

Moteur a pistons oscillants Download PDF

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Publication number
EP1472435B1
EP1472435B1 EP02716733A EP02716733A EP1472435B1 EP 1472435 B1 EP1472435 B1 EP 1472435B1 EP 02716733 A EP02716733 A EP 02716733A EP 02716733 A EP02716733 A EP 02716733A EP 1472435 B1 EP1472435 B1 EP 1472435B1
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EP
European Patent Office
Prior art keywords
pistons
housing
oscillating
piston
piston machine
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EP02716733A
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German (de)
English (en)
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EP1472435A1 (fr
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Herbert Hüttlin
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Individual
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Priority to AT02716733T priority Critical patent/ATE343710T1/de
Publication of EP1472435A1 publication Critical patent/EP1472435A1/fr
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
    • F01C9/00—Oscillating-piston machines or engines
    • F01C9/005—Oscillating-piston machines or engines the piston oscillating in the space, e.g. around a fixed point
    • 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
    • F01C3/00—Rotary-piston machines or engines with non-parallel axes of movement of co-operating members
    • F01C3/02—Rotary-piston machines or engines with non-parallel axes of movement of co-operating members the axes being arranged at an angle of 90 degrees

Definitions

  • the invention relates to a rotary piston machine, arranged with four in an internally spherical shaped housing and around a substantially housing-fixed housing-fixed axis in the housing together encircling pistons, which run when circulating in the housing reciprocating pivotal movements about a common pivot axis which substantially extends through the housing center, wherein each two adjacent pistons execute opposing pivoting movements, each piston having a working side and a rear side facing away from it, wherein between each two opposite working sides of two adjacent pistons and the housing, a respective working chamber is formed, while between each two Rear sides of adjacent two pistons and the housing in each case a counter to the working chambers in volume increasing or decreasing secondary chamber is formed, wherein the secondary chambers with a fluid . preferably air, are floatable, and wherein the fluid is compressed in the secondary chambers by the pivotal movement of the associated piston.
  • a fluid preferably air
  • Oscillating piston engines belong to a category of internal combustion engines in which the individual power strokes of the intake, compression, ignition, expansion and expulsion of the combustion mixture are mediated by reciprocating pivotal movements of the individual pistons between two end positions.
  • the oscillating piston run in the housing about a common housing-fixed orbital axis, wherein the circulation movement of the piston is converted via corresponding intermediate links in a rotational movement of an output shaft.
  • the pivot piston When rotating the pivot piston in the housing, the pivot piston perform the reciprocating pivoting movements.
  • the housing has on the inside a cylinder geometry.
  • the pistons of the known Schwenkkolbenmashenine are designed as two-armed lever. Two adjacent pistons are in rolling engagement with each other.
  • the pistons are each arranged pivotably about a piston axis parallel to a central axis of the housing, which lies on the cylinder axis.
  • the piston axes extend in the immediate vicinity of the housing inner wall, each piston having its own piston axis.
  • a housing-fixed curved piece is provided, along which the individual pistons are guided.
  • the individual working chambers which are each formed by two adjacent pistons, are formed between the sides of the pistons facing the housing inner wall and the housing inner wall.
  • the known oscillating piston engine has proven to be favorable in terms of their running properties and their torque curve, can be regarded as a disadvantage of the known oscillating piston engine that the mass distribution of the piston is still optimized due to the housing geometry and the housing inner side storage of the individual pistons.
  • the known from the document US-A-3 075 506 known oscillating piston engine differs from the previously described known oscillating piston engine in that the housing is designed to be a total of spherically symmetrical. In the housing, a total of four pistons are arranged, of which two are arranged diametrically opposite each other with respect to the pivot axis.
  • the oscillating piston engine described therein is designed as an internal combustion engine. It has, in accordance with the number of four pistons, two working chambers which are diametrically opposed with respect to the pivot axis and which, in the direction of the reciprocating pivoting movement of the four pistons, reduce in size and enlarge in the same direction.
  • the work cycles are offset from the first working chamber to the second working chamber by 180 °, that is, for example, if the working stroke of expanding the ignited fuel-air mixture takes place in the first working chamber, the working stroke of the intake of fresh air takes place in the second working chamber.
  • a secondary chamber is formed between each two adjacent pistons, so that the known oscillating piston engine has a total of two secondary chambers. These subchambers are flooded with air to cool the pistons via the piston recesses.
  • FR-A-75 26570 describes a likewise spherically symmetrical constructed oscillating piston engine.
  • GB-A-2 262 965 A discloses a rotary piston machine having a toroidal cylinder in a cylindrical housing.
  • This known oscillating-piston engine is designed with a self-charging effect, with two chambers, each on either side of a piston, communicating with one another via a line on the outside of the housing.
  • DE-A-197 47 445 A1 discloses a rerder adopted for a medium, that is a pump for gases or liquids, with a piston / cylinder unit, wherein the medium is sucked by a piston movement and promoted by opposite piston movement and due to the function of a valve device ,
  • the document US 6,241,493 B1 discloses a device for controlling the fluid flow through a rotary pump, a compressor or a motor.
  • a spherical housing rotates a first blade, which causes at least a second blade to pivot back and forth between alternately open and closed positions, and indeed, the second blade moves away from the first blade and approaches it again in an oscillating Move on.
  • the fluid is moved through an inlet in the housing as the second vane approaches the closed position as the fluid enters the housing when the second vane reaches the open position.
  • the one blade performs a pure rotational movement and no pivoting movement, while the other blade is pivotable.
  • This known device is therefore based on a completely different operating principle than the aforementioned known oscillating piston engine.
  • This known oscillating piston engine has two pivotable pistons, which rotate in a housing about a common axis of rotation. Each of the two pivot pistons has its own pivot axis, which is arranged eccentrically with respect to the center of the housing.
  • a swivel-type piston engine only has one pivotable piston.
  • the document DE 195 22 094 A1 discloses a tilt piston engine, the tilting piston of which consists of a circular disk which is tiltably mounted on its axis of rotation. This tilt piston performs only pivotal movements, but does not run in the housing.
  • a device with at least two rotating in an annular space rotary piston which limit in its direction of rotation an expansion chamber in the annulus forward and backward, wherein the rotary piston are connected via a gear assembly so with a common torque transmission shaft, that the Volume of the expansion chamber in the circulation direction alternately reduced and enlarged.
  • the gear arrangement has between the torque transmission shaft and at least one of the two expansion pistons defining a rotary piston at least one kinked and with respect to its cyclic rotational phase shift not compensated universal joint.
  • two adjacent pistons approach or move away from one another in that the pistons have varying rotational speeds when circulating in the housing.
  • the invention has for its object to provide a rotary piston engine of the type mentioned, which is improved with little design effort in terms of their efficiency.
  • this object is achieved with respect to the aforementioned reciprocating engine, characterized in that the secondary chambers communicate with a respective working chamber via at least one inlet valve, which allows a transfer of the compressed fluid from both secondary chambers into the respective working chamber.
  • the individual pistons circulating in the housing are pivotable about a common pivot axis, which lies essentially on a diameter of the spherical housing, as a result of which the pistons have a housing-centered bearing.
  • the housing of the oscillating piston engine according to the invention is spherical, which has the advantage that the overall arrangement of the piston can be formed in conjunction with their housing-centered storage with a particularly homogeneous mass distribution.
  • the spherical configuration of the oscillating-piston engine according to the invention offers the advantage of the largest possible working volume with a substantially more compact overall dimension of the oscillating-piston engine.
  • the individual working chambers can thus be designed with large volumes with the smallest possible overall dimensions of the oscillating piston engine.
  • Yet another advantage of the spherical configuration is that with respect to the position of the common pivot axis relative to the axis of rotation a largely free choice exists.
  • Each piston has a radially extending working side and a rear side facing away from this, wherein a respective working chamber between two opposite working sides and the housing is formed, while between each two rear sides of adjacent pistons and the housing in each case a counter to the working chambers in Volume-increasing or decreasing secondary chamber is formed.
  • the advantage of this measure is that the formed between two backs of two adjacent two piston secondary chambers, which in the back and forth Pivoting movements of the individual pistons behave in relation to their volume in opposite directions to the working chambers, in which the working cycles of suction, compression, expansion and ejection can be used for different purposes, namely on the one hand for cooling the piston, or as pressure chambers, as in hereafter descriptive embodiments is provided.
  • the aforementioned secondary chambers can be flooded with a fluid, preferably air.
  • the oscillating piston engine according to the invention is used as an internal combustion engine can be introduced by this measure in an advantageous manner in the secondary chambers fresh air for cooling the piston rear sides, the housing inner wall and the central piston bearing. This advantageously results in an increase in the overall efficiency in comparison to other internal combustion engines of known type.
  • the fluid is compressed in the secondary chamber by the pivotal movement of the associated pistons.
  • the at least one secondary chamber not only serves to cool the piston, the housing and the piston bearing, but at the same time as a pressure chamber, which in the case of using the oscillating piston engine according to the invention as an internal combustion engine for precompression of the combustion air , which was previously sucked into the at least one secondary chamber, can serve.
  • the aforementioned fluid is preferably fresh air.
  • the secondary chambers communicate with the at least one working chamber via at least one inlet valve which allows passage of the compressed fluid from both secondary chambers into the respective working chamber.
  • the erfindungacatee oscillating piston engine can be used as a self-boosting internal combustion engine.
  • a self-charging effect is integrated into the machine in the oscillating-piston engine according to the invention.
  • This self-charging effect is made possible by the secondary chambers which increase or decrease in the opposite direction to the working chambers.
  • the precompressed in the at least one secondary chamber fluid for example, precompressed combustion air, then compressed into the at least one working chamber, for example, if this is just in the intake stroke or at the end thereof.
  • the combustion air can be loaded with a pre-pressure in the at least one working chamber, so that in this way compression pressures can be achieved, which may be sufficient for operation of the rotary piston engine according to the invention as a diesel engine.
  • the Daufladesky can be accomplished in the context of this preferred embodiment without the cultivation of a charge air compressor, whereby a self-charging of the oscillating piston engine according to the invention with minimal design effort is possible.
  • the common pivot axis of the piston is inclined or perpendicular to the axis of rotation.
  • This measure has the advantage that the interaction between the reciprocating pivotal movements of the piston and the orbital motion of the piston can be realized structurally simple and kinematically low. While the oblique or vertical arrangement is preferred, it is also conceivable, the common pivot axis of the piston and the common axis of rotation are parallel, for example, to coincide. Allen configurations, however, have in common that the angle between the pivot axis and the axis of rotation during the course of the oscillating piston engine is fixed.
  • the pistons are pivotably mounted on a pivot pin forming the pivot axis, which is rotatably connected to the axis forming a rotating shaft about the axis of rotation.
  • the pivot pin forming the pivot axis is correspondingly arranged perpendicular to the shaft forming the revolving axis and rotatably connected thereto by the revolving axis.
  • the shaft is led out of the housing.
  • the wave forming the common revolving axis can simultaneously serve as the input or output axis.
  • the rotational movement of the pistons in the housing can thus be converted directly into a rotational movement of the shaft without intermediate links, wherein this rotational movement can then be tapped outside the housing as drive energy.
  • the shaft ends approximately on the housing center.
  • This embodiment has the advantage that only one bearing is needed for the shaft on the housing, whereby the design effort of the oscillating piston engine according to the invention is further reduced.
  • the two pistons of a double piston extending from the pivot axis substantially radially in the opposite direction to the respective opposite housing inner wall.
  • a total of four pistons are arranged in, in conjunction with the aforementioned preferred embodiment then two double pistons are arranged in the housing. These two double pistons intersect approximately in the form of an x on the common pivot axis.
  • the pistons are guided during rotation in the housing along at least one control cam formed on the housing for controlling the reciprocating pivoting movements.
  • the provision of the control cam has the advantage that the pivoting movements of the individual pistons are precisely controlled in a defined manner.
  • the provision of the at least one control cam on the housing differs from the aforementioned known oscillating piston engine, in which a housing-fixed curved piece is arranged centrally in the housing.
  • the pistons are mounted on the housing center around the common pivot axis, and the control cam is formed on the housing, as a result of which the pivoting movements of the pistons can take place with a large stroke.
  • control cam is formed as at least one introduced into the housing groove, in each of which engages at least one piston member associated with the piston-fixed guide member.
  • the provision of a groove in the wall of the housing has the advantage that the respective engaging in the groove piston-fixed guide member is guided on two sides, namely on the two opposite side walls of the groove.
  • the guide member has at least one roller, or the guide member is formed as a sliding bearing.
  • the guide member has at least one roller, the advantage is that the leadership of the individual pistons in the groove is carried out with very little friction, whereby energy losses are reduced when revolving the piston in the housing.
  • the guide member has two rollers, one of which is in contact with one side surface of the groove and the other with the opposite side surface of the groove.
  • This measure has the advantage that the two individual rollers do not have to reverse their direction of rotation when running in the groove, depending on whether they come into contact with the one side surface or the other side surface of the groove.
  • the one roller is always in contact with the one side surface of the groove, resulting in a same over a full rotation of the roller in the groove same direction of rotation of this roller results, while the other roller is always in contact with the opposite side surface, and this also during rotation in the groove thus undergoes no reversal of direction.
  • each double piston has only one guide member.
  • control cam may also be preferably formed as at least one projecting from the housing inwardly projection on which the pistons are guided along.
  • the advantage of this measure is that the pistons can be guided directly with a piston own surface without the provision of a roller on the inwardly projecting projection, whereby a structurally particularly simple embodiment of the oscillating piston engine is achieved.
  • the pistons are designed such that the working chamber formed by two adjacent pistons is formed kugelkeilförmig, and that the width of the working chamber in the plane perpendicular to the pivot axis of the piston is variable.
  • This embodiment of the piston leads to an enlarged compared to the aforementioned known oscillating piston engine working volume, which in the case of use of the Inventive oscillating piston engine can lead to an increased power output as an internal combustion engine.
  • At least one inlet valve for flooding the secondary chambers is provided on the housing.
  • this inlet valve can also be designed as a simple check valve or flutter valve, because a negative pressure and an overpressure occur alternately as a result of the constant alternating volume change. over which the intake valve is automatically controlled. In this way, expensive valve controls, such as a camshaft or even expensive valves, such as solenoid valves, can be saved.
  • the at least one secondary chamber communicates with the at least one working chamber via a line arranged on the outside of the housing, wherein the at least one inlet valve, through which fluid passes from the secondary chamber into the working chamber, is arranged on the housing.
  • the at least one secondary chamber communicates with the at least one working chamber through the intermediate piston, wherein the inlet valve, through which the fluid passes from the secondary chamber into the working chamber, is arranged on the piston.
  • the first embodiment has the advantage that the pistons are structurally easier manufacturable, because no valves must be integrated into the piston, but only an additional inlet valve must be provided on the housing
  • the second embodiment has the advantage that as an intake valve again simple setback - or flutter valves can be used, and the function of these valves is independent of the ambient pressure of the housing.
  • a controlled valve in the form of a solenoid valve or, in the simple case, a valve controlled via a camshaft is used.
  • the pistons for achieving large-volume working chambers are preferably arranged such that two adjacent pistons alternately move towards and away from one another due to the pivoting movements.
  • oscillating piston engine 10 serves as an internal combustion engine, but can also be used in other applications, for example as a compressor.
  • the oscillating piston engine 10 has a housing provided with the general reference numeral 12, which is composed of a first housing half 14 and a second housing half 16.
  • the two housing halves 14 and 16 are connected via a respective annular flange 18 and 20 firmly together.
  • An inner wall 22 of the housing 12 is spherical. Also on the outside, the housing 12 of the oscillating piston engine 10 has a ball symmetry.
  • Fig. 1 the housing 12 is shown partially broken away, so that in Fig. 1 further details of the oscillating piston engine 10 can be seen within the housing 12.
  • housing 12 In the housing 12 is a plurality and four pistons 24, 26, 28 and 30 are arranged in the present embodiment, wherein the piston 30 is concealed in Fig. 1, and, for example. In the exploded perspective view in Fig. 4 and in Fig. 7 is recognizable.
  • pistons 26 and 30 are firmly connected to a double piston, and also the pistons 24 and 28 form a one-piece rigid double piston.
  • the pistons 24 to 30 are pivotable about a common pivot axis 32, and at the same time the pistons 24 to 30 can rotate about a common axis of rotation 34 in the housing 12, wherein the reciprocating pivotal movements of the orbital motion superimpose, as will be described in more detail below ,
  • the double piston formed from the pistons 24 and 28 has a bearing ring 36 fixedly connected to the two pistons 24 and 28 at one end of the pistons 24 and 28 and a second bearing ring 38 at the opposite end of the pistons 24 and 28.
  • the double piston formed from the pistons 26 and 30 is identical to the double piston formed from the pistons 24 and 28, and correspondingly has a first bearing ring 40 and a second bearing ring 42.
  • the first double piston formed from the pistons 24 and 28 and the second double piston formed from the pistons 26 and 30 are pivotably mounted on a journal 44 via the bearing rings 36 and 38 or 40 and 42, which forms the pivot axis 32.
  • the first double piston formed from the pistons 24 and 28 and the second double piston formed from the pistons 26 and 30 are arranged rotated on the journal 44 against each other by 180 °, wherein the first double piston formed from the pistons 24 and 28 and from the piston 26 and 30 formed second double piston on the axle journal 44 and the pivot axis 32 extend crosswise.
  • caps 46 and 48 The arrangement of the pistons 24 to 30 and the journal 44 is sealed at the ends of the journal 44 by caps 46 and 48.
  • the closure caps 46 and 48 each have an inwardly projecting annular flange 50, which engages in a respective groove 52 on the second bearing rings 38 and 42 in a sealing manner.
  • the caps 46 and 48 form on the outside a kugelkalottenförmigen termination of the arrangement of the pistons 24 and 30 at the two ends of the journal 44, which is adapted to the radii of curvature of the inner wall 22 of the housing 12.
  • the stub axle 44 is connected to a shaft 54 by the axle pin 44 is inextricably pressed into a bore of a ring 56 at one end of the shaft 54 so that the axle pin 44 equally protrudes from the ring 56 to both sides at the same time.
  • the pistons 24 to 30 are mounted with the bearing rings 36 to 42 on the both sides of the ring 56 projecting portions of the axle journal 44.
  • the ring 56 is fixedly connected to the shaft 54.
  • the axle pin 44 and thus the pivot axis 32 extends perpendicular to the revolving axis 34, which is formed by the shaft 54. Relative to the rotational axis 34 of the axle pin 44 is rotatably connected to the shaft 54, wherein the axle pin 44 but also with respect to the pivot axis 32 is held non-rotatably in the ring 56 of the shaft 54.
  • the shaft 54 is led out of the housing 12 as shown in FIG. 1 and serves as an output shaft for the oscillating piston engine 10.
  • a tubular extension 58 is correspondingly formed, through which the shaft 54 is led out of the housing 12.
  • the shaft 54 is mounted according to Figures 2 and 3 in the extension 58 by means of bearings 60 and 62 with an intermediate sleeve 64.
  • the axle pin 44 and thus the pivot axis 32 pass through the housing center, which is designated in FIG. 7 by the reference numeral 66.
  • the pistons 24 to 30 are therefore mounted pivotably on a housing-center pivot axis 32.
  • the revolving axis 34 also passes through the middle of the housing and intersects there the pivot axis 32 perpendicular.
  • the first double piston already mentioned above becomes from the relative to the pivot axis 32 and the housing center 66 substantially diametrically opposed pistons 24 and 28, and the second double piston is from the relative to the pivot axis 32 and the housing center 66 substantially diametrically formed opposite piston 26 and 30.
  • the first double piston formed from the pistons 24 and 28 is further provided with a piston-fixed guide member 68, and also the double piston formed by the pistons 26 and 30 is provided with a guide member 70.
  • the guide members 68 and 70 serve to control the reciprocal pivotal movements of the pistons 24 to 30 about the pivot axis 32 as the pistons 24 to 30 revolve about the revolution axis 34.
  • the guide members 68 and 70 are formed in the manner of Achsstäben.
  • two rollers 72 and 74 are arranged end.
  • the roller 72 has a larger outer diameter than the roller 74.
  • end rollers 76 and 78 are arranged, wherein the roller 76 has a larger outer diameter than the roller 78th
  • control cam for controlling the reciprocating pivotal movements of the pistons 24 to 30 a.
  • the control cam formed as a groove 80 is centered on the housing about the revolving axis 34 in extension of the shaft 54, i. the ring 56 of the shaft 54 arranged opposite.
  • the cam formed by the groove 80 is a closed curve without crossing points and has approximately the shape of a constricted on diametrically opposite sides of the circle.
  • the groove 80 has a stepped shape in the radial direction, ie, the side surfaces 82 and 84 of the groove 80 have a step (See Figures 12 to 14).
  • the arrangement is made such that the rollers 72 and 76 larger outer diameter when revolving in the groove 80 abut only one side surface 84, while the rollers 74 and 78 of smaller outer diameter abut the opposite side surface 82, so that the respective direction of rotation Casters 72 to 78 over a full revolution through the groove 80 is the same.
  • the guide members 68 and 70 engage in the groove 80 offset by 180.degree., This wrap angle ratio of 180.degree. Being maintained over the circulation axis 34 over a full rotation of the pistons 24 to 30 in the housing 12 ,
  • the shape of the groove 80 is particularly clear from the illustration in Figures 6a) and 6b) show that show a section through the housing 12 along a plane perpendicular to the axis 34 and parallel to the pivot axis 32, wherein Fig. 6a) the housing 12 on the outside and Fig. 6b) shows the housing 12 inside.
  • FIGS. 5a) and 5b the double piston formed from the pistons 24 and 28 is shown in isolation.
  • Each of the pistons 24 to 30 has, as shown by the example of the pistons 24 and 28 in FIGS. 5a) and 5b), a working side and a rear side opposite thereto.
  • a working side is designated by the reference numeral 86.
  • the working side 86 is substantially smooth and flat and extends with its largest dimension parallel to the pivot axis 32.
  • a corresponding identically designed working side of the piston 28 is provided with the reference numeral 88.
  • a rear side 90 of the piston 24 opposite the working side 86 of the piston 24 is provided with a plurality of cavities 92 which are open toward the rear side 90 but which are closed on the working side 86.
  • a rear side 94 which is opposite to the working side 88 of the piston 28, is formed on the piston 28.
  • pistons 24 and 28 are also present in the identically formed pistons 26 and 30.
  • a working chamber is formed between the working sides of each adjacent piston 24 to 30, a working chamber is formed. Due to the design of the oscillating piston engine 10 with four pistons 24 to 30 are therefore two working chambers 96 and 98, wherein the working chamber 96 between the working sides of the adjacent pistons 24 and 26 and the working chamber 98 is formed between the working sides of the adjacent pistons 28 and 30.
  • the working chambers 96 and 98 are approximately in the form of ball wedges whose width in the plane perpendicular to the pivot axis 32, i. in the plane of Fig. 7, according to the reciprocating pivotal movements of the piston 24 to 30 is variable.
  • the working chambers 96 and 98 are bounded by the working sides of the pistons 24 to 30, the inner wall 22 of the housing 12 and the housing center 66 by the bearing rings 36 to 42, and the ring 56 of the shaft 54.
  • the secondary chambers 100 and 102 increase or decrease in volume in opposite directions to the working chambers 96 and 98.
  • the volumes of the working chambers 96 and 98 increase and decrease during rotation of the pistons 24 to 30 in the housing 12 about the axis 34 in the same direction, and also the secondary chambers 100 and 102 enlarge and shrink in the same direction.
  • the secondary chambers 100 and 102 can be flooded with a fluid, preferably air.
  • the auxiliary chamber 100 On the housing 12 of the auxiliary chamber 100 associated inlet valve 104 in a housing 12 formed on the valve housing 106 is present.
  • the inlet valve 104 is a flutter valve, which is biased in the direction of an arrow 108.
  • the intake valve 104 is controlled by the different pressure ratios between the sub-chamber 100 and the space outside the housing 12.
  • the secondary chamber 102 is associated with a further inlet valve 110, which is also arranged on the housing 12 in a valve housing 112 formed therein.
  • the intake valve 110 is a flutter valve, and its operation is the same as that of the intake valve 104.
  • the inlet valve 104 is located in a housing portion within the groove 80th
  • the introduced through the intake valves 104 and 110 in the secondary chambers 100 and 102 fluid preferably fresh air, initially serves to cool the piston 24 to 30, in particular their bearing rings 38 to 42 and the axle journal 44 and the inner wall 22 of the housing 12, further the cooling of the rollers 72 to 78 on the guide members 68 and 70 of the piston 24 to 30th
  • the sub-chambers 100 and 102 have not only the function of cooling in the illustrated embodiment, but also serve to compress the fluid introduced into the sub-chambers 100 and 102, i.e., to cool them. the fresh air.
  • This compression occurs starting from the position of the pistons 24 to 30 shown in FIG. 7 in that the pistons 24 and 26 pivot according to arrows 114 and 116 and the pistons 28 and 30 according to arrows 118 and 120, whereby the volume of the secondary chambers 100 and 102 is reduced. Due to the thereby continuously increasing pressure in the secondary chambers 100 and 102, the intake valves 104 and 110 in their closed position (arrow 108 in Fig. 7) is pressed so that the fluid can not escape from the secondary chambers 100 and 102 through the inlet valves 104 and 110, respectively.
  • the secondary chambers 100 and 102 also communicate with the working chambers 96 and 98 via a respective line outside the conduit 122 and 124, and via an inlet valve 126, which is a controlled valve, such as a solenoid valve.
  • the conduit 122 is connected at one end via an opening 128 in the housing 12 to the auxiliary chamber 102, while the conduit 124 is connected via an opening 130 in the housing 12 with the auxiliary chamber 100. In the region of the inlet valve 126, the lines 122 and 124 converge.
  • the fluid compressed in the secondary chambers 100 and 102 can then be introduced into the corresponding working chamber 96 or 98.
  • combustion air can be pre-compressed, i. be injected with an overpressure in the working chamber 96 and 98, whereby a self-charging effect of the oscillating piston engine 10 occurs.
  • the oscillating piston engine 10 further includes a spark plug 132 fixed to the housing 12, an injector 134 immediately adjacent to the spark plug 132 for injecting fuel, and an exhaust 136 visible only in FIG. 8 for discharging the combusted fuel-air mixture during operation of the oscillating piston engine 10.
  • FIGS. 9, 10 and 11 the functional principle of the oscillating piston engine 10 will be described in more detail below, wherein the individual movements of the pistons 24 to 30 can also be understood on the basis of the perspective illustrations in FIGS. 1 and 12 to 14.
  • the illustrations in FIG. 9 are highly schematic.
  • the pistons 24 and 26 are in the so-called top dead center (TDC), and the pistons 28 and 30 are in bottom dead center (TDC).
  • TDC top dead center
  • TDC bottom dead center
  • the working chamber 96 formed between the pistons 24 and 26 and the working chamber 98 formed between the pistons 28 and 30 have their minimum volume.
  • the guide member 70 of the double piston formed from the pistons 26 and 30 is located in the groove 80 at one vertex (see Fig. 11a) in Fig. 11), while the guide member 68 of the piston formed from the piston 24 and 28 on the double opposite vertex of the groove 80 is located (position c) in Fig. 11).
  • the working chambers 96 and 98 are shown with their maximum volume, the pistons 24 and 26 completed in this state, the expansion stroke and the pistons 28 and 30 have completed the working cycle of the suction.
  • the pistons 24 to 30 of FIG. 10c) from the initial position have to 90 ° about the axis of rotation 34 (see also Fig. 13).
  • the guide members 68 and 70 are now opposite each other at the crests of the narrow side of the groove 80 (position b) and d) in Fig. 11).
  • the working chambers 96 and 98 occupy their maximum volume, the secondary chambers 100 and 102 have their minimum volume, ie the air present in the secondary chambers 100 and 102 is now maximally compressed.
  • the inlet valve 126 is now opened by a corresponding control, whereby the entire existing in the secondary chambers 100 and 102 compressed air is introduced into the working chamber 98.
  • the secondary chambers 100 and 102 enlarge correspondingly.
  • the enlargement of the secondary chambers 100 and 102 now causes a negative pressure relative to the environment in the secondary chambers 100 and 102, so that fresh air is sucked into the secondary chambers 100 and 102 through the inlet valves 104 and 110, which thereby open automatically.
  • the pistons 24 to 30 have moved so far by 180 ° about the axis 34 in the housing 12. It follows that the oscillating piston engine 10 performs two full cycles of operation over a full revolution of the pistons 24 to 30 through 360 ° about the axis of rotation, i. the working cycles of suction, compression, expansion and ejection occur twice over a full 360 ° rotation.
  • Fig. 11 the characteristic of the working curve for the guide members 68 and 70 of the piston 24 to 30 is shown.
  • This illustration shows that the stroke of the oscillating pistons piston is given by the difference of the radii R2 and R1, wherein the radius R1 of the distance of the center of the groove 80 from the center of the groove 80 on the short axis and the radius R2 of the distance of Center of the groove 80 from the center of the groove 80 on the big axis.
  • FIGS. 15 to 17 show an embodiment of an oscillating-piston engine 10 'which is slightly different from the oscillating-piston engine 10 and differs from the oscillating-piston engine 10 only by the structural design of the self-charging effect previously described with reference to the oscillating piston engine 10.
  • the working chambers 96 'and 98' communicate with the secondary chambers 100 'and 102' via a housing-external line as in the previous embodiment, but directly via the pistons 24 'to 30' themselves, in which in each case an inlet valve 154 to 160 is arranged.
  • the intake valves 154 to 160 are formed as flutter valves.
  • the intake valves 154 to 160 open and close automatically, depending on the pressure difference between the secondary chambers 100 ', 102' and the working chambers 96 ', 98', which occurs during reciprocating pivoting movements of the pistons 24 'to 30'.
  • the intake valves 154 to 160 are biased toward the sub-chambers 100 'and 102'.
  • Fig. 15 the working chamber 96 'between the pistons 24' and 26 'is shown in a position in which the pistons 24' and 26 'are at top dead center. If now by means of the spark plug 132 'in the working chamber 96' existing fuel-air mixture ignited, occur in the working chamber 96 'extremely high pressures on, so that the intake valves 154 and 156 remain closed against this pressure until the working chamber 96 'is ready for sucking again after the exhaust stroke.
  • FIG. 15 all four intake valves 154 to 160 are shown in their closed position.
  • the pistons 24 ', 26' and 28 ', 30' have moved apart about the pivot axis 32 'and thereby further moved by about 45 ° about the rotational axis 34' in the housing 12 '.
  • the inlet valves 154 and 156 are still in their closed position, because the pressure in the working chamber 96 'is even higher than in the secondary chambers 100' and 102 '.
  • the inlet valves 158 and 160 are in their open position, since the empty in Fig. 15 and thus pressureless working chamber 98 'has a lower internal pressure than the secondary chambers 100' and 102 '.
  • FIG. 17 shows that the inlet valves 154 and 156 remain closed until the working chamber 96 ', in which the previously ignited fuel-air mixture further expands, has reached its maximum volume as shown in FIG.
  • FIGS. 15 to 17 are also an illustrative representation of the pistons 24 to 30 in the exemplary embodiment according to FIGS. 1 to 8, which move in the same way between the end positions according to FIGS. 15 and 17 Similarly, the sequence of Figures 15-17 further illustrates the control of the piston movements by means of the guide members 68 and 70 or 68 'and 70'.
  • FIG. 18 another embodiment of a provided with the general reference numeral 10 '' shown oscillating piston engine, which differs from the two previous embodiments by the type of control of the pivoting movements of the piston 24 "to 30".
  • the control cam provided to control the pivotal movements of the pistons 24 '' to 30 '' is formed as two projections 164 and 166 protruding inwardly from the housing 12 ''
  • the protrusions 164 and 166 have one groove 80 as opposed to the one
  • the pistons 24 '' to 30 '' are each formed with bearing surfaces 168 through which the pistons 24 '' to 30 '' on the projections 164 and 166 for controlling the pivotal movements of Piston 24 '' to 30 '' are guided in a sliding manner.
  • pistons 24 '' to 30 '' in contrast to the previous embodiments thus only guided on one side, so that it may be necessary under certain circumstances, in the TDC position of respective piston pairs 24 '' and 26 'or 28' 'and 30 "inject compressed air to initialize the opening pivotal movement of the pistons 24" and 26 ".
  • the shaft 54 is supported on both sides of the housing 12", i. does not end as in the previous embodiments in the housing center 66 ''.
  • the shaft 54 '' is thus still mounted on a second bearing 170.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Reciprocating Pumps (AREA)
  • Compressors, Vaccum Pumps And Other Relevant Systems (AREA)
  • Cylinder Crankcases Of Internal Combustion Engines (AREA)

Claims (17)

  1. Moteur à pistons oscillants avec quatre pistons (24 - 30) disposés dans un carter configuré en forme de sphère du côté intérieur (12) et tournant ensemble dans le carter (12) autour d'un axe de rotation (34) placé sensiblement au centre du carter, fixé au carter, et qui, lors de la rotation dans le carter (12), exécutent des mouvements oscillants de va-et-vient autour d'un axe de pivotement commun (32) qui passe sensiblement par le centre du boîtier (66), dans lequel à chaque fois deux pistons adjacents (24 - 30) exécutent des mouvements oscillants en sens inverse, dans lequel chaque piston (24 - 30) comporte une face de travail (86, 88) et une face arrière (96, 98) dirigée à l'opposé de celle-ci, un compartiment de travail étant formé entre deux faces de travail (86, 88) opposées l'une à l'autre de deux pistons adjacents (24 - 30) et le carter (12), tandis qu'un compartiment secondaire (100, 102), dont le volume augmente ou diminue dans le sens contraire des compartiments de travail (96, 98), est formé entre deux faces arrière (90, 94) de deux pistons adjacents (24 - 30) et le carter (12), et dans lequel les compartiments secondaires (100, 102) peuvent être remplis d'un fluide, de préférence de l'air, et dans lequel le fluide dans les compartiments secondaires (100, 102) est comprimé par le mouvement oscillant des pistons associés (24 - 30), caractérisé en ce que les compartiments secondaires (100, 102) communiquent chacun avec l'un des compartiments de travail (96, 98) par l'intermédiaire d'au moins une soupape d'admission (126) qui permet un transfert du fluide comprimé entre les deux compartiments secondaires (100, 102) et le compartiment de travail correspondant (96, 98).
  2. Moteur à pistons oscillants selon la revendication 1, caractérisé en ce que l'axe de pivotement commun (32) des pistons (24 - 30) s'étend en oblique ou perpendiculairement à l'axe de rotation (34).
  3. Moteur à pistons oscillants selon la revendication 1 ou 2, caractérisé en ce que les pistons (24 - 30) sont montés de manière pivotante sur un tourillon (44) formant l'axe de pivotement (32) qui est raccordé de manière solidaire en rotation à un arbre (56) formant l'axe de rotation (34) autour de l'axe de rotation (34).
  4. Moteur à pistons oscillants selon la revendication 3, caractérisé en ce que l'arbre (54) sort du carter (12).
  5. Moteur à pistons oscillants selon la revendication 3 ou 4, caractérisé en ce que l'arbre (54) se termine sensiblement au centre du carter.
  6. Moteur à pistons oscillants selon l'une quelconque des revendications 1 à 5, caractérisé en ce que deux pistons (24 - 30) sensiblement diamétralement opposés par rapport au centre du carter (66) sont raccordés fixement l'un à l'autre pour former un piston double.
  7. Moteur à pistons oscillants selon l'une quelconque des revendications 1 à 6, caractérisé en ce que, pendant la rotation dans le carter (12), les pistons (24 - 30) sont guidés le long d'au moins une came de commande formée dans le carter (12) pour la commande des mouvements oscillants de va-et-vient.
  8. Moteur à pistons oscillants selon la revendication 7, caractérisé en ce que la came de commande est formée comme au moins une rainure (80) aménagée dans le carter, dans laquelle s'engage au moins un organe de guidage (68, 70) fixé au piston, associé au piston respectif (24 - 30).
  9. Moteur à pistons oscillants selon la revendication 8, caractérisé en ce que l'organe de guidage (68, 70) comporte au moins un galet de roulement (72 - 78) ou est configuré comme un palier lisse.
  10. Moteur à pistons oscillants selon la revendication 9, caractérisé en ce que l'organe de guidage (68, 70) comporte deux galets de roulement (72 - 78) dont l'un est en contact avec une face latérale (82) de la rainure (80) et l'autre avec la face latérale opposée (84) de la rainure (80).
  11. Moteur à pistons oscillants selon la revendication 6 et l'une quelconque des revendications 8 à 10, caractérisé en ce que chaque piston double ne comporte qu'un seul organe de guidage (68, 70).
  12. Moteur à pistons oscillants selon la revendication 7, caractérisé en ce que la came de commande est configurée comme au moins un épaulement (164) faisant saillie vers l'intérieur à partir du carter (12"), le long duquel les pistons (24" - 30") sont guidés.
  13. Moteur à pistons oscillants selon l'une quelconque des revendications 1 à 12, caractérisé en ce qu'au moins une soupape d'admission (104, 110) est prévue sur le carter (12) pour remplir le au moins un compartiment secondaire (100, 102).
  14. Moteur à pistons oscillants selon l'une quelconque des revendications 1 à 13, caractérisé en ce que les compartiments secondaires (100, 102) communiquent avec le compartiment de travail correspondant (96, 98) par l'intermédiaire d'une conduite (122, 124) placée du côté extérieur du carter, la au moins une soupape d'admission (126), par l'intermédiaire de laquelle le fluide est transféré entre les compartiments secondaires (100, 102) et le compartiment de travail correspondant (96, 98), étant placée sur le carter (12).
  15. Moteur à pistons oscillants selon l'une quelconque des revendications 1 à 14, caractérisé en ce que les compartiments secondaires (100', 102') communiquent avec le compartiment de travail correspondant (96', 98') par l'intermédiaire des pistons (24' - 30') se trouvant entre eux, les soupapes d'admission (154 - 160), par l'intermédiaire desquelles le fluide est transféré entre les compartiments secondaires (100', 102') et les compartiments de travail (96', 98'), étant placées sur les pistons (24' - 30').
  16. Moteur à pistons oscillants selon l'une quelconque des revendications 1 à 15, caractérisé en ce que les pistons (24 - 30) sont configurés de telle manière que le compartiment de travail (96, 98) formé par deux pistons adjacents (24 - 30) a une forme de cône sphérique dont la largeur est variable dans le plan perpendiculaire à l'axe de pivotement (32) des pistons (24 - 30).
  17. Moteur à pistons oscillants selon l'une quelconque des revendications 1 à 16, caractérisé en ce que les pistons (24 - 30) sont disposés de telle manière que deux pistons adjacents (24 - 30) se rapprochent et s'éloignent alternativement l'un de l'autre en raison des mouvements oscillants.
EP02716733A 2002-02-06 2002-02-06 Moteur a pistons oscillants Expired - Lifetime EP1472435B1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
AT02716733T ATE343710T1 (de) 2002-02-06 2002-02-06 Schwenkkolbenmaschine

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
PCT/EP2002/001226 WO2003067033A1 (fr) 2002-02-06 2002-02-06 Moteur a pistons oscillants

Publications (2)

Publication Number Publication Date
EP1472435A1 EP1472435A1 (fr) 2004-11-03
EP1472435B1 true EP1472435B1 (fr) 2006-10-25

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ID=27675558

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EP02716733A Expired - Lifetime EP1472435B1 (fr) 2002-02-06 2002-02-06 Moteur a pistons oscillants

Country Status (10)

Country Link
US (1) US7563086B2 (fr)
EP (1) EP1472435B1 (fr)
JP (1) JP4129923B2 (fr)
CN (1) CN1329627C (fr)
BR (1) BR0205881A (fr)
CA (1) CA2474449C (fr)
DE (1) DE50208560D1 (fr)
DK (1) DK1472435T3 (fr)
ES (1) ES2274016T3 (fr)
WO (1) WO2003067033A1 (fr)

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DE102010019122A1 (de) * 2010-04-30 2011-11-03 Ernst Beck Schwenkkolbenmaschine mit einem um eine Schwenkachse oszillierenden Schwenkkolben

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DE10361566B4 (de) * 2003-12-23 2006-09-07 Hüttlin, Herbert, Dr. h.c. Schwenkkolbenmaschine
RU2403400C2 (ru) * 2004-04-06 2010-11-10 Перафес Акциенгезелльшафт Роторно-поршневой двигатель и транспортное средство, содержащее двигатель такого типа
DE102005024751B4 (de) * 2005-02-25 2015-10-22 Herbert Hüttlin Schwenkkolbenmaschine
PL1856375T3 (pl) * 2005-02-25 2010-10-29 Huettlin Herbert Maszyna z tłokami wahadłowymi
DE102005010775B3 (de) 2005-02-25 2006-04-20 Hüttlin, Herbert, Dr. h.c. Schwenkkolbenmaschine
KR101134649B1 (ko) * 2005-04-21 2012-04-09 주식회사 아덴 동력전환 장치와 이를 이용한 하이브리드 시스템
DE102005023721B3 (de) * 2005-05-17 2006-08-17 Hüttlin, Herbert, Dr. h.c. Schwenkkolbenmaschine
DE102005026661A1 (de) * 2005-05-31 2006-12-07 Hüttlin, Herbert, Dr. h.c. Rotationskolbenmaschine
DE102005038447B3 (de) * 2005-08-03 2007-01-25 Hüttlin, Herbert, Dr. h.c. Schwenkkolbenmaschine
DE102005062529B4 (de) * 2005-12-16 2007-09-20 Hüttlin, Herbert, Dr. h.c. Schwenkkolbenmaschine
WO2007076617A1 (fr) * 2005-12-30 2007-07-12 Peraves Ag Machine à pistons pivotants à préchambres de suralimentation sans soupape
US8322323B2 (en) * 2006-02-10 2012-12-04 Arnold Wagner Fluid system for oscillating-piston engines
AU2007218986A1 (en) 2006-02-22 2007-08-30 Peraves Ag Sealing system for an oscillating-piston engine
DE102006009198B4 (de) 2006-02-22 2010-03-25 Hüttlin, Herbert, Dr. h.c. Schwenkkolbenmaschine
DE102006009197B4 (de) * 2006-02-22 2008-09-11 Hüttlin, Herbert, Dr. h.c. Schwenkkolbenmaschine
DE102006027953A1 (de) * 2006-06-14 2007-12-20 Hüttlin, Herbert, Dr. h.c. Brennkraftmaschine, insbesondere für ein Arbeitsgerät
DE102007054321A1 (de) 2007-10-31 2009-05-07 Hüttlin, Herbert, Dr. h.c. Kolbenmaschine
DE102008012374B4 (de) * 2008-02-26 2011-02-17 Hüttlin, Herbert, Dr. h.c. Rotationskolbenmachine
EP2669471A1 (fr) * 2008-07-08 2013-12-04 RPM Group Limited Dispositif rotatif à chambre extensible
DE102010022012A1 (de) * 2010-05-25 2011-12-01 Herbert Hüttlin Aggregat, insbesondere Hybridmotor, Stromgenerator oder Kompressor
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US9528585B2 (en) 2012-06-29 2016-12-27 Peter Ross Taylor Piston engine
CN103147908B (zh) * 2013-02-28 2015-08-19 河南科技大学 一种液压马达
DE202013002034U1 (de) 2013-03-01 2013-04-04 GM Global Technology Operations LLC (n. d. Ges. d. Staates Delaware) Elektrische Maschine und Kraftfahrzeug mit einer elektrischen Maschine
WO2015139554A1 (fr) * 2014-03-18 2015-09-24 西安正安环境技术有限公司 Mécanisme anti-blocage de rotor de compresseur sphérique, mécanisme de puissance anti-blocage de compresseur sphérique, et compresseur sphérique
US10323517B2 (en) * 2016-11-08 2019-06-18 Thomas F. Welker Multiple axis rotary engine
RU2701651C1 (ru) * 2019-05-07 2019-09-30 Иван Владимирович Стаканов Сферический двигатель внутреннего сгорания

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DE102010019122B4 (de) * 2010-04-30 2012-06-21 Ernst Beck Schwenkkolbenmaschine mit einem um eine Schwenkachse oszillierenden Schwenkkolben

Also Published As

Publication number Publication date
CA2474449A1 (fr) 2003-08-14
DK1472435T3 (da) 2007-02-12
US7563086B2 (en) 2009-07-21
BR0205881A (pt) 2004-02-17
CN1329627C (zh) 2007-08-01
EP1472435A1 (fr) 2004-11-03
DE50208560D1 (de) 2006-12-07
WO2003067033A1 (fr) 2003-08-14
US20050008515A1 (en) 2005-01-13
JP2005526206A (ja) 2005-09-02
JP4129923B2 (ja) 2008-08-06
CA2474449C (fr) 2009-06-09
CN1617975A (zh) 2005-05-18
ES2274016T3 (es) 2007-05-16

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