EP0656992B1 - Moteur a deux temps a cylindres rotatifs - Google Patents

Moteur a deux temps a cylindres rotatifs Download PDF

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Publication number
EP0656992B1
EP0656992B1 EP93919205A EP93919205A EP0656992B1 EP 0656992 B1 EP0656992 B1 EP 0656992B1 EP 93919205 A EP93919205 A EP 93919205A EP 93919205 A EP93919205 A EP 93919205A EP 0656992 B1 EP0656992 B1 EP 0656992B1
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EP
European Patent Office
Prior art keywords
cylinder
rotor
exchange
gas
rotary
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EP93919205A
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German (de)
English (en)
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EP0656992A1 (fr
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Josef Gail
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Individual
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Individual
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
    • F02B57/00—Internal-combustion aspects of rotary engines in which the combusted gases displace one or more reciprocating pistons
    • F02B57/08—Engines with star-shaped cylinder arrangements
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01B—MACHINES OR ENGINES, IN GENERAL OR OF POSITIVE-DISPLACEMENT TYPE, e.g. STEAM ENGINES
    • F01B13/00—Reciprocating-piston machines or engines with rotating cylinders in order to obtain the reciprocating-piston motion
    • F01B13/04—Reciprocating-piston machines or engines with rotating cylinders in order to obtain the reciprocating-piston motion with more than one cylinder
    • F01B13/06—Reciprocating-piston machines or engines with rotating cylinders in order to obtain the reciprocating-piston motion with more than one cylinder in star arrangement
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L7/00—Rotary or oscillatory slide valve-gear or valve arrangements
    • F01L7/12—Rotary or oscillatory slide valve-gear or valve arrangements specially for two-stroke engines
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02G—HOT GAS OR COMBUSTION-PRODUCT POSITIVE-DISPLACEMENT ENGINE PLANTS; USE OF WASTE HEAT OF COMBUSTION ENGINES; NOT OTHERWISE PROVIDED FOR
    • F02G1/00—Hot gas positive-displacement engine plants
    • F02G1/04—Hot gas positive-displacement engine plants of closed-cycle type
    • F02G1/043—Hot gas positive-displacement engine plants of closed-cycle type the engine being operated by expansion and contraction of a mass of working gas which is heated and cooled in one of a plurality of constantly communicating expansible chambers, e.g. Stirling cycle type engines
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
    • F02B75/00—Other engines
    • F02B75/02—Engines characterised by their cycles, e.g. six-stroke
    • F02B2075/022—Engines characterised by their cycles, e.g. six-stroke having less than six strokes per cycle
    • F02B2075/025—Engines characterised by their cycles, e.g. six-stroke having less than six strokes per cycle two
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02G—HOT GAS OR COMBUSTION-PRODUCT POSITIVE-DISPLACEMENT ENGINE PLANTS; USE OF WASTE HEAT OF COMBUSTION ENGINES; NOT OTHERWISE PROVIDED FOR
    • F02G2244/00—Machines having two pistons

Definitions

  • the invention relates to a two-stroke internal combustion engine.
  • a two-stroke internal combustion engine of the cylinder rotor type is known.
  • This internal combustion engine comprises a cylinder rotor with a plurality of cylinders arranged at equal angular intervals around the axis of rotation of the cylinder rotor.
  • the pistons which are radially displaceable in the cylinders, are supported by articulated connecting rods on a single, common eccentric bearing of a crankshaft which is fixedly connected to a housing enclosing the cylinder rotor.
  • inlet and outlet gas exchange slots are provided in the cylinders, which, as is customary in two-stroke internal combustion engines, are controlled, ie opened and closed, by the radially outer edge of the pistons.
  • the two-stroke internal combustion engine known from US-A-3 739 756 differs from conventional star-shaped engines, in which the pistons, which are displaceable in radial, but stationary, cylinders, operate on a rotating crankshaft, essentially in that the internal combustion engine in the US -A-3 739 756 the crankshaft is stationary and instead the cylinders rotate.
  • the stroke length is comparatively long in relation to the diameter of the pistons, with the result that comparatively high combustion chambers have to be flushed and filled when the gas is changed in the stroke direction. It is comparatively difficult to ensure adequate purging of the combustion chambers, especially since the circumferential surface area of the cylinders available for accommodating gas exchange slots is limited.
  • the kinematics of the crankshaft gear used there cause asymmetries in the stroke movement, which also has an effect on the control angles or control times available for the gas exchange.
  • the kinematics of articulated connecting rods means that the radial thrust of the pistons cannot be optimally converted into a torque acting on the cylinder rotor, which worsens the use of force.
  • International application WO90 / 15918 discloses a further cylinder rotor machine that can be used as an internal combustion engine or as a compressor.
  • the machine has a cylinder rotor rotating about a first axis of rotation, which comprises three pairs of cylinders offset by 120 °.
  • the cylinders of each pair running radially to the first axis of rotation are arranged coaxially and rigidly connected to one another by a common piston rod.
  • the cylinder rotor is surrounded by a stationary housing, in which a crankshaft enclosed by the cylinders is rotatably supported about a second axis of rotation arranged with a predetermined eccentricity relative to the first axis of rotation.
  • each pair of pistons are rotatably guided on an eccentric bearing of the crankshaft, the eccentric disk of which is firmly connected to the crankshaft.
  • the eccentric bearings define third axes of rotation offset by 120 ° relative to one another about the second axis of rotation, whose radial distance from the second axis of rotation is also equal to the predetermined eccentricity. In this way it is achieved that each pair of pistons is non-rotatably supported on the cylinder rotor relative to the eccentric axis even if its eccentric axis currently coincides with the axis of rotation of the cylinder rotor.
  • the support takes place exclusively via the other two pairs of pistons, without the cylinder rotor also having to be torque-proof coupled to the crankshaft via a gear transmission or the like. Since the eccentric bearings define fixed axes of rotation relative to the crankshaft, the piston rods do not have to be articulated via double bearings on both the piston and the crankshaft.
  • the known cylindrical rotor machine can be built relatively small in relation to its performance.
  • the cylinders are open towards the circumference of the cylinder rotor and are closed off from the outside by the housing which closely surrounds the cylinder rotor.
  • the housing surrounding the cylinder rotor must be tolerated with a minimal annular gap in order to avoid pressure losses, or else sealing elements must be used. Reliable sealing by means of a closely tolerated annular gap is difficult to achieve due to different thermal expansions, particularly when designed as an internal combustion engine, and reliable sealing with sealing strips or the like also leads to problems due to the high sliding speeds on the outer circumference.
  • a rotary slide valve control arrangement which rotates synchronously with the cylinder rotor is provided between at least one gas exchange channel which is stationary with respect to the housing and the ends of the inlet-side gas exchange channels and / or outlet gas-exchange channels remote from the slot.
  • the cylinder rotor comprises three pairs of cylinders arranged coaxially arranged at 120 ° to each other, the pistons of which are also rigidly connected to one another in pairs by means of the piston rods, that the crankshaft has a predetermined axis about the first axis of rotation Eccentricity is rotatably offset second axis of rotation offset and define the eccentric bearing by 120 ° around the second axis of rotation offset and by the predetermined eccentricity parallel to the second axis of rotation offset third axes of rotation for the piston rods of piston pairs.
  • Two-stroke internal combustion engines of the cylinder rotor type according to the invention have a comparatively small stroke with a comparatively large displacement of the individual combustion chambers.
  • the short stroke makes the exact dimensioning of the opening and closing angles difficult.
  • the opening and closing angles of the inlet slots and outlet slots are symmetrical with the radially inner dead center position and the radially outer dead center position of the piston. Due to the symmetry, flushing losses, i.e. unused fuel or insufficient purging or insufficient fresh gas filling can flow off.
  • the aforementioned rotary slide control arrangement also controls the gas exchange of the individual cylinders and the resulting opening control angle of the intake and / or exhaust gas exchange channel related to the rotation of the cylinder rotor compared to the opening control angle of the associated cylinder-side Gas exchange slot changed, especially reduced.
  • the rotary valve control arrangement which can be provided both in the path of the inlet channels and the outlet channels and in both channels, takes over the gas exchange control together with the piston-controlled slots.
  • the distance of the rotary valve control arrangement from the gas exchange slots ensures a reduction the gas pressure, especially on the outlet side, so that the rotary valve control arrangement only has to meet limited sealing requirements.
  • the rotary slide valve control arrangement makes it possible to determine the start and end of the inlet independently of the start and end of the outlet, so that the gas exchange can be optimized.
  • the rotary slide valve control arrangement comprises a slide part which is movable in the circumferential direction of the cylinder rotor relative to the latter and has a control opening which connects the slot-distant end of the cylinder-side gas exchange channel to the stationary gas exchange channel during the gas exchange.
  • the slide part which is, for example, a ring enclosing the crankshaft, permits adjustment of the gas exchange, expediently in the form that a drive mechanism adjusts the slide part when the cylinder rotor is rotating, i.e. allowed during engine operation.
  • the rotary slide valve control arrangement can be realized using side surfaces integrally formed by the cylinder rotor or the housing.
  • the rotary slide valve control arrangement comprises pairs of annular sealing disks which are arranged axially to the side of the cylinder rotor and are, in particular, resiliently biased axially against one another, of which at least one advantageously consists of ceramic material.
  • the resilient preload ensures sufficient sealing forces.
  • the sealing washers have mutually coaxial, annular, interlocking projections on mutually opposite sides, which form a labyrinth of sealing between the sealing washers. In this way, one can be constructed with little construction material achieve reliable rotary valve control arrangement.
  • the ends of the gas exchange channels on the cylinder side preferably have a smaller distance from the first axis of rotation than the associated gas exchange slots.
  • the cylinder-side gas exchange channels run towards the axis of rotation of the cylinder rotor, so that the diameter of the rotary slide control arrangement and thus the relative speed of the sealing surfaces moving against one another can be kept small.
  • the rotary slide valve control arrangement assigned to the inlet gas exchange channels connects the inlet gas exchange channels one after the other with a stationary inlet channel for fresh air and a likewise stationary inlet channel for air-fuel mixture. Due to this two-part design of the gas inlet, when the gas is changed, the flushing process of the displacement can be started exclusively with fresh air in order to avoid flushing losses, in order to subsequently supply mixture in the course of the rotation.
  • rotary slide valve-like controls are provided on both the intake side and the exhaust side.
  • rotary valve control arrangements are used in the context of the invention in addition to gas exchange controls with piston-controlled gas exchange slots, it can be advantageous to reduce the number of rotary valves required.
  • the aim of a preferred embodiment of the invention is to facilitate the sealing of a cylinder rotor from the housing surrounding it in a simple manner.
  • the cylinder rotor encloses a central crankshaft chamber containing the crankshaft, from which the cylinders proceed, that the inlet gas exchange channels are designed as overflow channels that are open to the crankshaft chamber, and that radially within one the cylinder rotor on the housing rotatably supported bearing is introduced into the crankshaft chamber with respect to the housing stationary gas inlet channel.
  • Such a cylinder rotor internal combustion engine does not require a rotary valve on the inlet side.
  • the fresh gases are conducted into the crankshaft chamber via a channel which is guided through the cylinder rotor bearing in a stationary manner to the housing, from where they reach the combustion chambers of the cylinders in a piston-controlled manner via the overflow channels.
  • a rotary slide valve control arrangement is expediently provided on the outlet side, which in turn is preferably also used for gas exchange control, but alternatively can also be used only for the controlled passage of the exhaust gases through the housing.
  • the pistons are wider in the axial direction of the cylinder rotor than in its circumferential direction.
  • the outlet gas exchange slots are each provided in a wall region of the cylinder which extends essentially in the axial direction of the cylinder rotor, in particular at least approximately in the middle of this wall region, and inlet gas exchange slots are provided in the axial direction of the cylinder rotor on both sides of the outlet gas exchange slot.
  • the combustion chamber is based on the counterflow principle flows through gases, the fresh gases entering in the region of the longitudinal ends of the combustion chamber, preferably such that they flow essentially along the circumferential wall regions of the cylinder to the cylinder roof and from there flow back to the outlet gas exchange slots in the center region of the combustion chamber.
  • the cylinder roof expediently has two concavely curved convexities lying next to one another in the axial direction of the cylinder rotor. It has also proven to be expedient if two spark plugs are assigned to the cylinder, each of which works in one of the two domes.
  • the cylinders also have both outlet gas exchange slots and inlet gas exchange slots in the circumferential direction on both sides of the pistons.
  • This design which is made possible in a particularly simple manner by the crank chamber charge of the cylinders, symmetrizes the gas exchange flows both on the inlet side and on the outlet side, which benefits the optimization of the gas exchange.
  • pistons that are wider in the axial direction of the cylinder rotor than in its circumferential direction is not only advantageous in the case of two-stroke internal combustion engines with crank chamber charge.
  • This piston design generally facilitates the accommodation of the cylinders in the cylinder rotor, also in the case of other cylinder rotor machines designed as internal combustion engines or compressors, since the displacement can be increased without the diameter of the cylinder rotor having to be increased.
  • each cylinder comprises two circular-cylindrical cylinder chambers which are arranged next to one another in the axial direction of the cylinder rotor and which are separated by a Area of the cylinder roof are separated from one another by at least one overflow opening, one of the cylinder chambers being connected only to the inlet gas exchange duct and the other cylinder chamber being connected only to the outlet gas exchange duct, and that in each cylinder chamber one of two partial pistons of a double piston can be displaced .
  • overflow channels are preferably provided in the circumferential direction of the cylinder rotor on both sides of one cylinder chamber and outlet gas exchange slots in the circumferential direction of the cylinder rotor on both sides of the other cylinder chamber. In this way, the flushing behavior can be improved when trained as a two-stroke machine.
  • each double piston is expediently connected by separate piston rods to the two partial pistons of the double piston which is radially opposite in relation to the first axis of rotation, the two piston rods of each pair of double pistons being spaced apart on two in the direction of the second axis of rotation Eccentric bearings are performed.
  • the guidance of the partial pistons on separate eccentric bearings facilitates the storage. It goes without saying that even in the case of elongated pistons of the type explained above, each piston rod can consist of two parts which are arranged at a distance from one another and which are in turn guided on two separate and spaced-apart eccentric bearings.
  • the feature of the piston rod and of the eccentric bearing guiding the piston rod is also intended to include multi-part piston rods and eccentric bearings which are optionally arranged at an axial distance.
  • the pistons are wider in the axial direction of the cylinder rotor than in its circumferential direction and in that the inlet gas exchange slots on the one hand and the outlet gas exchange slots on the other side are provided on opposite sides of the cylinders in the axial direction of the cylinder rotor.
  • the pistons have a piston roof that is convexly curved at least in the axial direction of the cylinder rotor and the cylinder roof has at least in the axial direction of the cylinder rotor is concavely curved, a direct-current flushing that is favorable in terms of combustion technology takes place.
  • the pistons preferably have, in the circumferential direction of the cylinder rotor, axially parallel to the first axis of rotation, essentially flat outer surfaces which merge into semi-cylindrical outer surfaces on the narrow sides. Pistons of this design are comparatively easy to seal and also easy to manufacture. It is also advantageous that the inflow and outflow area can be designed without vortex-forming corners in the area of the slots of the cylinders provided on the narrow sides.
  • the value of the predetermined eccentricity of the crankshaft explained at the outset is dimensioned such that the fourfold value of the eccentricity is smaller than that maximum width of the pistons in the circumferential direction of the cylinder rotor, that is to say smaller in the case of an axially elongated piston than the narrow side width of the pistons.
  • This dimensioning rule is expediently also used for cylindrical pistons, since it enables an optimal size-performance ratio.
  • the comparatively large displacement of the individual cylinders enables the degree of filling of the cylinders in fresh gases to be controlled if the inlet gas exchange duct is connected to a blower, the drive of which comprises a speed-controllable motor, in particular an electric motor.
  • a blower the drive of which comprises a speed-controllable motor, in particular an electric motor.
  • a speed control for the blower motor responsive to the speed of the cylinder rotor can be provided.
  • the performance of the two-stroke internal combustion engine can be optimized.
  • the housing completely surrounds the cylinder rotor and forms a blower housing with at least one cooling air intake opening in the region of its center and at least one outflow opening in the region of its outer circumference.
  • the cylinders can, as is customary in air-cooled engines, be provided with ribs to form a large temperature exchange surface which, in the arrangement of the cooling air openings mentioned, are flowed around radially around the axis of rotation of the cylinder rotor.
  • the air flow can also be increased by an external cooling air blower.
  • the cooling air intake opening is preferably located in the region of the outlet rotary valve control arrangement, so that it can also be used to cool it.
  • the cooling air flow is expediently conducted into the interior of the blower housing via ducts running radially past the rotary slide valve control arrangement.
  • the fan housing can optionally be provided on the outside with a suitable, sound-reducing coating.
  • the small size of the two-stroke internal combustion engines according to the invention in connection with their high performance and the high operational reliability and long service life due to the low piston speeds opens up a wide range of applications.
  • Special advantages result in stationary operation, in which the internal combustion engine is coupled to a working machine, in particular an electrical generator or the compressor of a heat pump.
  • the exhaust gas exchange duct of the internal combustion engine is connected to a heat exchanger, so that not only the heat pump for generating heat from a building heating system, but also the waste heat from the internal combustion engine can be used for heating purposes. Since the speed of the crankshaft is twice as high as the rotor speed, there is also a more favorable drive speed, for example for a three-phase generator, without the need for a transmission gear.
  • the housing preferably consists of two housing halves that are mirror-symmetrical to a plane of division running perpendicular to the first axis of rotation.
  • the division level expediently runs through the common inlet and / or outlet openings explained above.
  • the manufacture of the cylinder rotor is facilitated if it comprises two rotor parts forming the cylinder walls, of which a first rotor part forms an axially lateral wall of the cylinder rotor and a peripheral wall forming the cylinder roofs, and the second rotor part forms a further axial side wall and carries protruding projections in the axial direction, which delimit the cylinders between them in the circumferential direction.
  • a cylinder rotor manufactured in this way is not only stable, but also the surfaces to be manufactured with narrow tolerances are essentially accessible without undercuts so that they can be machined precisely in a simple manner.
  • the two-stroke internal combustion engine shown in FIGS. 1 and 2 comprises a housing 1 with an essentially cylindrical interior 3, in which a star-shaped cylinder rotor 5 is arranged so as to be rotatable about an axis of rotation 7.
  • the cylinder rotor 5 is mounted on roller bearings 9 on bearing lugs 11 of the housing 1.
  • the cylinder rotor 5 contains six cylinders 13, in each of which a piston 15 is arranged to be displaceable perpendicular to the axis of rotation 7.
  • the cylinders 13 and pistons 15 are aligned in pairs on opposite sides of the axis of rotation 7, i.e. coaxial, arranged.
  • the axes of the cylinder pairs are angularly offset from one another by 120 ° around the axis of rotation 7 and are preferably in the same axis-normal plane of the cylinder rotor.
  • the pistons 15 assigned to one another in pairs are rigidly connected to one another by piston rods 17.
  • a crankshaft 21 is rotatably mounted in roller bearings 19 about an axis of rotation 23 offset parallel to the axis of rotation 7 by an eccentricity e (FIG. 1).
  • the crankshaft 21 carries fixedly three eccentric circular disks 25 arranged axially next to one another, which sit in bearing openings 27 of the piston rods 17 and guide the piston rods 17 via needle bearings 29.
  • the eccentric circular disks 25 define eccentric bearings with eccentric rotary axes 31 that are parallel to the axis of rotation 23 of the crankshaft 21, but offset by the value of the eccentricity e relative to the axis of rotation 23.
  • the eccentric rotary axes 32 of the three eccentric circular disks 25 are also 120 ° from one another about the axis of rotation 23 offset around it.
  • the Eccentric circular disks 25 have a radius that is larger than the eccentricity e and are preferably connected to one another exclusively in their radial overlap region.
  • the pistons 15 move when the cylinder rotor 5 rotates about the axis of rotation 7 along a path that intersects the axis of rotation 7 in a plane normal to the axis.
  • the eccentric axis of rotation 32 which coincides with the center axis of the eccentric disk 25, also moves on this path.
  • the three pairs of pistons are guided on the crankshaft 21 exclusively via their piston rods 17.
  • the crankshaft 21 is in this case rotated relative to the cylinder rotor 5 and at an angular speed that is twice as large as the angular speed at which the cylinder rotor rotates about its axis of rotation 7.
  • the eccentricity e since the piston stroke is four times the eccentricity e, is comparatively small, for example in the order of 10 to 20 mm.
  • the radius of the eccentric circular disks 25 is smaller than four times the value of the eccentricity e and is normally around 2.5 to 3 times the value of the eccentricity e.
  • the cylinder rotor 5 has a central crankcase 31, which is mounted on the bearings 9 and to which the cylinders 13 are screwed.
  • the cylinders 13 are closed at the head end by cylinder roofs 33 which are firmly connected to them and, together with the cylinder roof 33 and a piston roof shown at 35, each delimit a combustion chamber 37 in which the pistons 15 rotating on a circular path between a radially inner dead center position and one radially outer dead center position to be moved back and forth. 39 denotes a possibly flywheel held on the crankshaft 21 to assist rotation.
  • the combustion chambers 37 are assigned spark plugs indicated at 41, which protrude into depressions 43 of the piston roof 35.
  • the troughs 43 also form a compression space for the air-fuel mixture to be ignited by the spark plug 41.
  • the supply of fresh air-fuel mixture and the outflow of the exhaust gases are provided with respect to the axis of rotation 23 on axially opposite sides of the cylinder rotor 5 in the individual cylinders 13 inlet channels 45 and, with respect to the cylinders 13, diametrically opposite outlet channels 47.
  • the inlet channels 45 and outlet channels 47 open into at least one inlet slot 51 and at least one outlet slot 53 in the position of the cylinder wall that is released from the radially outer edge 49 of the piston skirt when the pistons 15 are in the dead center position.
  • the slots 51 which are generally referred to as gas exchange or flushing slots , 53 are opened or closed for the gas exchange control by the piston 15 in the course of its stroke movement.
  • the slots 51, 53 can be arranged at the same height; expediently, however, the outlet slot 53 opens in front of the inlet slot 51 when the piston 15 moves radially inwards.
  • rotary valve control arrangements 55 and 57 are arranged, which arrange the ends of the gas exchange channels 45, 47 remote from the slot with a stationary inlet channel 59 provided on the housing side or a stationary one relative to the housing 1 Connect the outlet channel 61 in a position in which the slots 51, 53 are open.
  • the rotary slide valve arrangements 55, 57 not only form sealing housing bushings for the cylinder-side inlet channels 45 and outlet channels 47, but control the gas exchange in connection with the slots 51, 53, the rotary slide valve 55 shortening the actual intake opening time compared to the opening time defined by the inlet slot 51, by the rotary slide valve 55 compared to the inlet slot 51 later opens and / or closes earlier.
  • the rotary valve 57 also controls the outlet opening time by the outlet rotary valve 57 opening later than the outlet slot 53 and / or closing earlier than the outlet slot 53.
  • the gas exchange can be influenced in addition to the piston-controlled slots 51, 53 and optimized to avoid flushing losses or to improve the loading of the combustion chamber with fresh gases.
  • 3 shows a control diagram for one of the cylinders.
  • AT is the radially outer dead center and IT the inner dead center of the piston. The ignition takes place at the outer dead center.
  • the control diagram is run through in a clockwise direction, the control angle of 360 ° corresponding to one revolution of the cylinder rotor 5.
  • outlet slot 53 opens, and at the same time outlet rotary valve 57 opens (time A ' a ). This starts the exhaust phase.
  • the inlet slot 51 opens.
  • the flushing phase begins after that with the opening of the inlet rotary valve 55 at the time E ' a .
  • the rinsing phase ends with the closing of the outlet slide valve 57 (A ' z ). Since the rotary valve 57 closes before the inlet slot 51 (time E z ) and the inlet rotary valve 55 (time E ' z ) simultaneously close, flushing losses are avoided.
  • the outlet slot 53 closes after the inlet closes at time A z .
  • the control diagram of FIG. 3 represents only an example. In individual cases it may be sufficient if only the intake times or the exhaust times are varied, and accordingly either the intake rotary valve 55 or the exhaust rotary valve 57 can be omitted.
  • the rotary valves 55, 57 are of essentially identical construction and each comprise two annular sealing disks 63, 65 which are coaxial with the axis of rotation 7 and which are arranged axially next to one another and are axially resiliently pressed against one another.
  • the sealing disk 63 adjacent to the cylinder rotor 5 is provided with the holes 67 which match the slot-distant ends of the gas exchange channels 45, 47, while the sealing disk 65 which is remote from the cylinder rotor 5 each has a hole 69 which matches the gas exchange channel 59 or 61.
  • the sealing disk 63 is connected in a rotationally fixed manner to the cylinder rotor 5 and, like the sealing disk 65 connected in a rotationally fixed manner to the housing 1, can consist of ceramic material.
  • the sealing discs are provided on their axially adjacent flat sides with mutually coaxial, annular, mutually interlocking projections or ribs 71, which together form a labyrinth seal.
  • the rotary valves 55, 57 do not have to cope with excessively high pressure peaks, since the slots 51, 53 take over the pilot control of the gas exchange. Since the gas exchange channels 45, 47 on the cylinder side are inclined outwards from the slots 51, 53 towards the axis of rotation 7, the diameter of the sealing disks 63, 65 can be kept relatively small, so that the relative sliding speed between the sealing disks 63, 65 is low remains.
  • the rotor speed is only half as large as the output speed of the crankshaft 21 compared to conventional internal combustion engines of the cylinder rotor type.
  • 57 can also be designed in a different way and, for example, instead of the axially abutting surfaces, have cylindrical sealing surfaces or cone sealing surfaces.
  • the pistons 15 are narrower in the circumferential direction of the cylinder rotor 5 than in the direction of its axis of rotation 7.
  • the width of the pistons 15 in both the circumferential direction and in the axial direction of the cylinder rotor 5 is greater than the stroke and thus greater than four times the eccentricity e.
  • the pistons 15 can have a rectangular cross section or, as is shown in the exemplary embodiment in FIG.
  • the sealing disks 63, 65 can be held in an unadjustable manner on the cylinder rotor 5 or the housing 1.
  • the housing-side control disk is rotatably mounted on the housing 1 and on part of its outer circumference with a Tooth 73 provided.
  • the overlap angle of the opening 69 can be adjusted relative to the gas exchange duct on the housing side, for example the outlet duct 61, which means that depending on the direction of the adjustment, the start of the outlet or the end of the outlet is shifted with respect to the outlet ducts 47.
  • the rotation of the sealing disk 65 can also take place during engine operation.
  • the piston 15 again shows details of the rotary slide valves 55, 57 and the cross-sectional shape of the piston 15 in a radial view.
  • the piston 15 has flat flat sides 77 running parallel to one another in the circumferential direction, while the narrow side surfaces 79 of the piston have the shape of cylinder sections with a semicircular cross section.
  • the inlet channels 45 and outlet channels 47 expand towards the cylinder and open approximately tangentially into the narrow side surfaces 79.
  • the direction of purging of the combustion chamber is indicated by an arrow 81; the direction of movement of the cylinder 13 is indicated by an arrow 83.
  • the cylinder-side sealing disks 63 are fixedly attached to the cylinder rotor
  • the housing-side sealing disks 65 are axially movably guided thereon and are biased by springs 85 toward the cylinder rotor.
  • the combustion air is compressed by a blower 87 before fuel is mixed in a carburetor 89 or an injection pump and the air-fuel mixture is supplied to the combustion chambers via the inlet duct 59.
  • the inlet rotary valve 55 can, as shown in FIG. 5, additionally or alternatively be used to control the start or end of the inlet also for controlling a second inlet channel 91, which in the direction of rotation of the cylinder barrel in front of the hole 69 of the housing-side sealing disk 65 in a further hole 93 this sealing washer flows.
  • the combustion chamber can first be flushed with fresh air during each working cycle before the air / fuel mixture is loaded into the combustion chamber. In this way, the flushing-related losses in fuel are reduced.
  • a compressor or a compressor arrangement of the type described in W090 / 15918 with double-used pistons or the compressor explained below with reference to FIGS. 9 and 10 can also be used.
  • the cylinder barrel 5 is essentially completely enclosed by the housing 1. Since the cylinders 13 each protrude radially, the cylinder rotor 5 acts as a radial fan. At least on the side of the outlet rotary valve 57, at least one cooling air inlet duct 95 (FIG. 1) opens radially within the central region of the housing 1 enclosed by the outlet rotary valve 57, which channel is passed through a plurality of circumferentially distributed radial channels 97 past the outlet rotary valve 57 into the interior of the housing 1 extends. In the area of the outer periphery of the housing, one or more cooling air outlets 99 are provided, via which the cooling air exits again.
  • the cooling air in the area of the outlet rotary valve 57 By supplying the cooling air in the area of the outlet rotary valve 57, the latter is primarily cooled.
  • the cylinders are provided with cooling fins in the usual way to improve the heat exchange. It goes without saying that an additional fan can be connected upstream of the cooling air duct 95.
  • the two-stroke internal combustion engine is also particularly suitable for stationary operation, since it has relatively small dimensions with high output and is durable due to the low piston speed and the short stroke.
  • the encasing by the housing 1 reduces the noise emission.
  • the housing 1 can on his Be additionally provided on the outside with sound insulation indicated at 101.
  • the internal combustion engine is particularly suitable for stationary applications in connection with a work machine 103 coupled to the crankshaft 21, which is in particular the compressor of a heat pump system or an electrical generator, especially a three-phase generator.
  • the use for driving a three-phase generator complies with the doubled crankshaft speed compared to the rotor speed.
  • the heat pump system is expediently part of a building heating system, into which the exhaust gas heat is also returned.
  • a heat exchanger provided for this purpose is indicated at 105 in FIG. 1.
  • FIGS. 6 and 7 show a variant of the two-stroke internal combustion engine explained above, which differs from this internal combustion engine primarily by the type of gas flow. Parts having the same effect are provided in FIGS. 6 and 7 with the reference numbers of FIGS. 1 to 5 and for distinction with the letter a. To explain the principle of operation of these components, reference is made to the description of FIGS. 1 to 5. Components 31, 32, 85, 89 and 101 and optionally components 73 and 75 are present, but are not shown in FIGS. 6 and 7. Components 55, 91, 93 have not been implemented.
  • the cylinder rotor 5a of the internal combustion engine shown in FIGS. 6 and 7 forms a crank chamber 107, radially inside the space delimited by the pistons 15a, into which the inlet channel 59a supplying the air-fuel mixture opens.
  • the inlet channel 59a leads radially through the housing la within the area enclosed by the bearing 9a of the cylinder rotor 5a.
  • the to the inlet slots 51a leading cylinder-side inlet channels 51a are designed as overflow channels which open with their radially inner ends on the side facing the crankshaft 21a outside the inner dead center position of the piston 15a in the crank chamber 107.
  • the pistons 15a are narrower in the circumferential direction of the cylinder rotor 5a than in the axial direction of the cylinder rotor 5a, the narrow side width here also being greater than four times the eccentricity e of the crankshaft 21a.
  • the pistons 15a have flat flat sides 79a and narrow sides 79a running parallel to one another in the form of cylinder sections with a semicircular cross section.
  • outlet slots 53a are provided on opposite sides of the pistons 15a in the circumferential direction, which are connected by separate outlet channels 47a to the rotary valve 57a provided exclusively on the outlet side.
  • the inlet slots 51a as well as the overflow channels 45a are arranged in the region of the semi-cylindrical narrow sides of the pistons and are shaped such that the flushing path 81a, the fresh gases entering the combustion chamber 37a via the outlet slots 51a, along the narrow side surfaces of the combustion chamber 37a shaped in accordance with the piston 15a to the cylinder roof 33a flows.
  • the cylinder roof 33a contains two concavities 109 lying next to one another in the longitudinal direction of the piston, which deflect the fresh gas flow towards the centrally arranged outlet slots 53a.
  • the elongated shape of the pistons 15a in connection with the explained arrangement of the slots 51a, 53a allows a reverse purge of the combustion chamber 37a.
  • the internal combustion engine comprises two spark plugs 41a, each associated with one of the domes 109, which ensure symmetrical ignition and are connected to an ignition system (not shown in more detail) via spark contact paths 111 arranged on the inner casing of the housing 1a.
  • the fan 87a which conveys the fresh air, is driven by an electric motor 113, the speed of which can be varied via a controller 115.
  • the controller 115 which possibly detects the current speed of the cylinder rotor 5a or the crankshaft 21a by means of a speed sensor 117, controls the boost pressure and thus the degree of filling of the combustion chambers 37a via the speed of the electric motor 113.
  • By suitably adjusting the degree of filling it can be achieved that some of the exhaust gases remain in the combustion chamber 37a and are thus returned to the combustion in the next working cycle in order to reduce the pollutant emissions. In this way, exhaust gas recirculation is not necessary.
  • variable-speed motor can also be used, for example a hydraulic motor or the like.
  • Components 113 to 117 can also be used in an internal combustion engine of FIGS. 1 to 5.
  • the internal combustion engine of FIGS. 6 and 7 can also be supplemented by components 103, 105.
  • the embodiments of the rotary slide valve explained with reference to FIGS. 1 to 5 can also be used in the internal combustion engine of FIGS. 6, 7. The same applies to the design of the machine cooling.
  • FIG. 8 shows a variant of the two-stroke internal combustion engine of FIGS. 6 and 7.
  • parts having the same effect are provided with the reference numbers from FIGS. 1 to 7 and for distinction with the letter b.
  • the primary difference between the two-stroke internal combustion engine according to FIG. 8 and the internal combustion engine according to FIGS. 6 and 7 is that instead of a single piston elongated in the axial direction of the cylinder rotor, a double piston consisting of two partial pistons 15b 'and 15b "is provided per cylinder
  • the partial pistons 15b 'and 15b “have a circular cylindrical cross-section and are arranged to be axially parallel to one another in two cylinder chambers 13b' and 13b" arranged side by side in the axial direction of the cylinder rotor 5b.
  • the cylinder chambers 13b 'and 13b "are separated from one another by a partition wall 119, which is provided in the area of the common cylinder roof 33b with at least one overflow opening 121 connecting the two combustion chambers 37b.
  • the cylinder roof 33b faces the combustion chambers 37b and is provided with bulges 109b for receiving the spark plugs 41b.
  • the circular cylindrical shape of the cylinder chambers 13b ', 13b "and the partial pistons 15b', 15b" of the double-piston arrangement simplifies the sealing without reducing the displacement which can be accommodated in the cylinder rotor 5b or having to increase the diameter of the cylinder rotor 5b.
  • the air-fuel mixture supplied via the inlet channel 59b flows via the crank chamber 107b and a plurality of overflow channels 45b arranged on both sides of one of the two partial pistons, here the partial piston 15b ', in the combustion chamber 37b of this partial piston via the crank chamber 107b. With its radially outer piston edge 49b, the partial piston 15b 'controls the inlet slots 5lb of the associated cylinder chamber 13b'.
  • the other partial piston 13b " is used exclusively for controlling outlet slots 53b of the other cylinder chamber 13b".
  • the outlet slots 53b are in turn arranged in the circumferential direction of the cylinder rotor 5b on both sides of the piston 15b ".
  • Outlet gas exchange channels 47b connect the outlet slots 53b to the rotary valve 57b provided exclusively on the outlet side and thus to a stationary outlet channel 61b on the housing side, as is shown in FIG. 6 and 7 is explained in detail.
  • the partial pistons 15b 'and 15b are each also assigned separate piston rods 17b' and 17b".
  • the two piston rods 17b 'and 17b "of the double piston are arranged at a distance from one another in the axial direction of the cylinder rotor 5b and are guided on eccentric circular disks 25b' and 25b" which are also arranged at a distance from one another.
  • the eccentric circular disks 25b 'and 25b in turn sit in needle bearings 29b in bearing openings 27b of the piston rods.
  • each of the partial pistons 15b' and 15b" is with a corresponding partial piston on the opposite side of the piston Rotation axis 7b of the cylinder rotor 5b arranged double piston rigidly connected.
  • the eccentric rotary axes defined by the eccentric circular disks 25b 'and 25b "of the double piston pair run coaxially here.
  • the cylinder rotor can essentially be composed of two components, one of which comprises one of the side walls and the circumferential wall which also forms the cylinder roofs and the other component comprises the other side wall and protrusions which form the circumferential walls of the cylinders.
  • Components of this type can be manufactured comparatively easily and precisely, since they have essentially no undercuts.

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  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)
  • Hydraulic Turbines (AREA)
  • Compressors, Vaccum Pumps And Other Relevant Systems (AREA)
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Claims (28)

  1. Moteur à bloc-cylindres rotatif réalisé sous la forme d'un moteur à combustion interne à deux temps, comprenant
    un carter (1),
    un vilebrequin (21) placé dans le carter (1),
    au moins un bloc-cylindres rotatif (5) placé dans le carter (1) de manière à pouvoir tourner autour d'un premier axe de rotation (7), comportant plusieurs cylindres (13) fermés radialement vers l'extérieur par des couvercles de cylindre (33) reliés de manière fixe au bloc-cylindres rotatif (5), et disposés à écarts angulaires égaux autour du premier axe de rotation (7) et du vilebrequin (21) avec des axes de cylindre s'étendant radialement par rapport au premier axe de rotation (7),
    un piston (15) mobile radialement par rapport au premier axe de rotation (7) dans chaque cylindre (13) délimitant par son couvercle de cylindre (33) et le piston (15) une chambre de combustion (37), les pistons (15) étant reliés au vilebrequin (21) par des tiges de piston (17), et des paliers d'excentrique (29),
    un dispositif de commande (49, 51, 53) de renouvellement des gaz comportant des canaux d'admission et d'échappement (45, 47) de renouvellement des gaz associés séparément à chaque cylindre (13), lesquels canaux débouchent par une de leurs extrémités dans le cylindre (13), dans au moins à chaque fois une lumière (51, 53) de renouvellement des gaz qui peut être commandée par l'arête (49) du piston (15) qui est extérieure radialement par rapport au premier axe de rotation (7), et
    un dispositif de commande (55, 57) à tiroirs rotatifs tournant de manière synchrone avec le bloc-cylindres rotatif (5), disposé entre au moins un canal (59, 61) de renouvellement des gaz fixe par rapport au carter (1) et les extrémités éloignées des lumières des canaux d'admission (45) et/ou d'échappement (47) de renouvellement des gaz côté cylindre,
       caractérisé en ce que le bloc-cylindres rotatif (5) comprend trois paires, dont la position angulaire est décalée de 120° l'une par rapport à l'autre, de cylindres (13) disposés sur le même axe, dont les pistons (15) sont également sensiblement reliés les uns aux autres par paires par une liaison sensiblement rigide, au moyen des tiges de piston (17),
    en ce que le vilebrequin (21) est disposé de manière à pouvoir tourner autour d'un deuxième axe de rotation (23) décalé avec parallélisme des axes d'une excentricité (e) prédéterminée par rapport au premier axe de rotation, et les paliers d'excentriques (29) définissent, pour les tiges de piston (17) des paires de pistons, des troisièmes axes de rotation (32) décalés de l'excentricité prédéterminée (e) par rapport au deuxième axe de rotation (23), avec parallélisme des axes, et dont la position angulaire est décalée de 120° autour du deuxième axe de rotation (23),
    et en ce que le dispositif de commande (55, 57) à tiroirs rotatifs commande également le renouvellement des gaz de chaque cylindre (13), et modifie, en particulier réduit, l'angle de commande d'ouverture, résultant de la rotation du bloc-cylindres rotatif (5), du canal d'admission et/ou d'échappement (45, 47) de renouvellement des gaz, comparé à l'angle de commande d'ouverture de la lumière (51, 53) de renouvellement des gaz associée, côté cylindre.
  2. Moteur à bloc-cylindres rotatif selon la revendication 1, caractérisé en ce que le dispositif de commande (55, 57) à tiroirs rotatifs comprend une partie formant tiroir (65), mobile par rapport au bloc-cylindres rotatif (5) dans le sens circonférentiel de celui-ci, et comportant une ouverture de commande (69) qui relie, pendant le renouvellement des gaz, l'extrémité éloignée de la lumière du canal (47) de renouvellement des gaz côté cylindre au canal (61) fixe de renouvellement des gaz.
  3. Moteur à bloc-cylindres rotatif selon la revendication 2, caractérisé en ce qu'à la partie formant tiroir (65) est associé un mécanisme d'entraînement (73, 75) qui permet un réglage de la partie formant tiroir (65) lorsque le bloc-cylindres rotatif (5) tourne.
  4. Moteur à bloc-cylindres rotatif selon l'une des revendications 1 à 3, caractérisé en ce que le dispositif de commande (55, 57) à tiroirs rotatifs comprend au moins une paire, disposée axialement à côté du bloc-cylindres rotatif (5), de rondelles d'étanchéité (63, 65) annulaires, appuyées l'une contre l'autre de manière étanche et en particulier précontraintes élastiquement axialement l'une contre l'autre.
  5. Moteur à bloc-cylindres rotatif selon la revendication 4, caractérisé en ce que les rondelles d'étanchéité (63, 65) présentent, sur leurs faces opposées, des protubérances (71) coaxiales, annulaires et en prise les unes avec les autres, sous la forme d'un labyrinthe d'étanchéité.
  6. Moteur à bloc-cylindres rotatif selon l'une des revendications 1 à 5, caractérisé en ce que les extrémités éloignées des lumières des canaux (45, 47) de renouvellement des gaz situés côté cylindre sont à une plus petite distance du premier axe de rotation (7) que les lumières (51, 53) de renouvellement des gaz associées.
  7. Moteur à bloc-cylindres rotatif selon l'une des revendications 1 à 6, caractérisé en ce que le dispositif de commande (55) à tiroirs rotatifs associé aux canaux d'admission (45) de renouvellement des gaz relie les canaux d'admission (45) de renouvellement des gaz l'un après l'autre à un canal d'admission (91) pour l'air frais, fixe par rapport au carter, et à un canal d'admission (59) également fixe pour le mélange air-carburant.
  8. Moteur à bloc-cylindres rotatif réalisé sous la forme d'un moteur à combustion interne à deux temps selon l'une des revendication 1 à 7, caractérisé en ce que le bloc-cylindres rotatif (5a, 5b) renferme une chambre de vilebrequin (107, 107b) centrale, contenant le vilebrequin, et dont partent les cylindres (13a, 13b), et en ce que les canaux d'admission (45a, 45b) de renouvellement des gaz sont réalisés sous la forme de canaux d'aspiration ouverts sur la chambre de vilebrequin (107, 107b), et en ce qu'un canal (59a, 59b) d'admission des gaz, fixe par rapport au carter (1a, 1b), est guidé dans la chambre de vilebrequin (107, 107b) radialement à l'intérieur d'un palier (9a, 9b) recevant le bloc-cylindres rotatif (5a, 5b) de manière mobile en rotation sur le carter (1a, 1b), et en ce que le dispositif de commande (57a, 57b) à tiroirs rotatifs est prévu uniquement entre un canal (61a, 61b) d'échappement de renouvellement des gaz immobile par rapport au carter (1a, 1b) et le canal (47a, 47b) d'échappement de renouvellement des gaz situé côté cylindre.
  9. Moteur à bloc-cylindres rotatif selon la revendication 8, caractérisé en ce que le dispositif de commande (57a, 57b) à tiroirs rotatifs réduit l'angle de commande d'ouverture, résultant de la rotation du bloc-cylindres rotatif (5a, 5b), du canal d'échappement (47a, 47b) de renouvellement des gaz, comparé à l'angle de commande d'ouverture de la lumière (53a, 53b) d'échappement de renouvellement des gaz située côté cylindre.
  10. Moteur à bloc-cylindres rotatif selon la revendication 8 ou 9, caractérisé en ce que les pistons (15a) sont plus larges suivant la direction axiale du bloc-cylindres rotatif (5a) que selon sa direction circonférentielle,
       en ce que les lumières (53a) d'échappement de renouvellement des gaz sont prévues à chaque fois dans une zone de paroi du cylindre (13a) s'étendant sensiblement selon la direction axiale du bloc-cylindres rotatif (5a), en particulier au moins sensiblement au centre de cette zone de paroi, et en ce que des lumières (51a) d'admission de renouvellement des gaz sont prévues, selon la direction axiale du bloc-cylindres rotatif (5a), de part et d'autre de la lumière (53a) d'échappement de renouvellement des gaz.
  11. Moteur à bloc-cylindres rotatif selon la revendication 10, caractérisé en ce que les canaux (51a) d'admission de renouvellement des gaz côté cylindre sont disposés de telle sorte que les gaz d'admission circulent en direction du couvercle de cylindre (33a), dans la zone de la zone de paroi du cylindre (13a) s'étendant sensiblement selon la direction circonférentielle du bloc-cylindres rotatif (5a).
  12. Moteur à bloc-cylindres rotatif selon la revendication 11, caractérisé en ce que le couvercle de cylindre (33a) présente deux cavités (109) concaves adjacentes selon la direction axiale du bloc-cylindres rotatif (5a).
  13. Moteur à bloc-cylindres rotatif selon l'une des revendications 10 à 12, caractérisé en ce que les cylindres (13a) présentent des lumières (53a) d'échappement de renouvellement des gaz ainsi que des lumières (51a) d'admission de renouvellement des gaz de part et d'autre des pistons (15a), selon la direction circonférentielle du bloc-cylindres rotatif (5a).
  14. Moteur à bloc-cylindres rotatif selon la revendication 8 ou 9, caractérisé en ce que chaque cylindre comprend deux chambres de cylindre (13b', 13b") circulaires cylindriques et disposées l'une à côté de l'autre selon la direction axiale du bloc-cylindres rotatif (5b), lesquelles chambres sont séparées par une paroi de séparation (119) munie, dans la zone du couvercle de cylindre (33b), d'au moins une ouverture d'aspiration (121), l'une (13b') des chambres de cylindre (13b', 13b") étant à chaque fois reliée exclusivement au canal (45b) d'admission de renouvellement des gaz et l'autre chambre de cylindre (13b") étant reliée uniquement au canal (47b) d'échappement de renouvellement des gaz,
       et en ce que dans chaque chambre de cylindre (13b', 13b"), l'un des deux pistons partiels (15b', 15b") d'un double piston peut être déplacé.
  15. Moteur à bloc-cylindres rotatif selon la revendication 14, caractérisé en ce que des canaux d'admission (45b) sont prévus de part et d'autre de l'une des chambres de cylindre (13b') selon la direction circonférentielle du bloc-cylindres rotatif (5b) et des lumières (53b) d'échappement de renouvellement des gaz sont prévues de part et d'autre de l'autre chambre de cylindre (13b") selon la direction circonférentielle du bloc-cylindres rotatif (5b).
  16. Moteur à bloc-cylindres rotatif selon la revendication 14 ou 15, caractérisé en ce que les deux pistons partiels (15b', 15b") de chaque double piston sont reliés par des tiges de piston partiel (17b', 17b") séparées aux deux pistons partiels (15b', 15b") du double piston opposé radialement par rapport au premier axe de rotation (7b), les deux tiges de piston partiel (17b', 17b") de chaque paire de doubles pistons étant guidées sur deux paliers d'excentrique (25b', 25b") disposés à distance selon la direction du deuxième axe de rotation (23b).
  17. Moteur à bloc-cylindres rotatif selon l'une des revendications 1 à 7,
    les canaux (47b) de renouvellement des gaz côté cylindre partant des cylindres (13b), tournant avec ces derniers, et se terminant dans une paroi axiale latérale du bloc-cylindres rotatif (5b),
    au moins un canal (59b) d'admission de renouvellement des gaz fixe et au moins un canal (61b) d'échappement de renouvellement des gaz étant prévus dans le carter (1b) et
    au moins le canal (61b) d'échappement de renouvellement des gaz se terminant dans le carter (1b) devant la paroi axiale latérale du bloc-cylindres rotatif (5b), et
    le dispositif (57b) de commande à tiroirs rotatifs comprenant au moins une lumière de distribution (69b) entourant en arc le premier axe de rotation (7b) pour relier le canal (61b) de renouvellement des gaz fixe, dans une zone d'angle de rotation prédéterminée, aux canaux (47b) tournants de renouvellement des gaz,
       caractérisé en ce que chaque cylindre comprend deux chambres de cylindre (13b', 13b") circulaires cylindriques et disposées l'une à côté de l'autre selon la direction axiale du bloc-cylindres rotatif (5b), lesquelles chambres sont séparées par une paroi de séparation (119) munie, dans la zone du couvercle de cylindre (33b), d'au moins une ouverture d'aspiration (121), l'une des chambres de cylindre (13b', 13b") étant à chaque fois reliée exclusivement au canal (45b) d'admission de renouvellement des gaz et l'autre chambre de cylindre (13"b) étant reliée uniquement au canal (47b) d'échappement de renouvellement des gaz,
       et en ce que dans chaque chambre de cylindre (13b', 13b"), l'un de deux pistons partiels (15b', 15b") d'un double piston peut être déplacé.
  18. Moteur à bloc-cylindres rotatif selon la revendication 17, caractérisé en ce que les deux pistons partiels (15b', 15b") de chaque double piston sont reliés par des tiges de piston partiel (17b', 17b") séparées aux deux pistons partiels (15b', 15b") du double piston opposé radialement par rapport au premier axe de rotation (7b), les deux tiges de piston partiel (17b', 17b") de chaque paire de doubles pistons étant guidées sur deux paliers d'excentrique (25b', 25b") disposés à distance selon la direction du deuxième axe de rotation (23b).
  19. Moteur à bloc-cylindres rotatif réalisé sous la forme d'un moteur à combustion interne à deux temps selon l'une des revendications 1 à 18, caractérisé en ce que les pistons (15) sont plus larges selon la direction axiale du bloc-cylindres rotatif (5) que selon sa direction circonférentielle, et
       en ce que les lumières (45) d'admission de renouvellement des gaz d'une part, et les lumières (47) d'échappement de renouvellement des gaz d'autre part, sont prévues sur des côtés opposés du cylindre (13), selon la direction axiale du bloc-cylindres rotatif (5).
  20. Moteur à bloc-cylindres rotatif selon la revendication 19, caractérisé en ce que les pistons (15) comportent des surfaces extérieures (77) sensiblement planes, s'étendant selon la direction circonférentielle du bloc-cylindres rotatif (5) en étant parallèles au premier axe de rotation (7), lesquelles surfaces se transformant en surfaces extérieures (79) semi-cylindriques sur les côtés étroits.
  21. Moteur à bloc-cylindres rotatif selon la revendication 19 ou 20, caractérisé en ce que les pistons (15) comportent un couvercle de piston (35) voûté de manière convexe au moins selon la direction axiale du bloc-cylindres rotatif (5), et en ce que le couvercle de cylindre (33) est voûté de manière concave au moins selon la direction axiale du bloc-cylindres rotatif (5).
  22. Moteur à bloc-cylindres rotatif selon l'une des revendications 1 à 21, caractérisé en ce que le canal (45a) d'admission de renouvellement des gaz est relié à une soufflante (87a) dont l'entraînement comprend un moteur (113) à vitesse réglable, en particulier un moteur électrique.
  23. Moteur à bloc-cylindres rotatif selon l'une des revendications 1 à 22, caractérisé en ce que le quadruple de l'excentricité (e) prédéterminée est inférieur à la largeur maximale des pistons (15, 15a) selon la direction circonférentielle du bloc-cylindres rotatif (5, 5a).
  24. Moteur à bloc-cylindres rotatif selon l'une des revendications 1 à 23, caractérisé en ce que le carter (1, la) renferme complètement le bloc-cylindres rotatif et constitue un carter de soufflante comportant au moins une ouverture (95, 95a) d'aspiration d'air froid dans la zone de son centre et au moins une ouverture (99, 99a) d'échappement dans la zone de sa périphérie extérieure.
  25. Moteur à bloc-cylindres rotatif selon la revendication 24, caractérisé en ce qu'un dispositif de commande (57, 55a) à tiroirs rotatifs tournant de manière synchrone avec le bloc-cylindres rotatif (5, 5a) est prévu entre un canal (61, 61a) de renouvellement des gaz immobile par rapport au carter de soufflante et les canaux d'échappement (47, 49a) de renouvellement des gaz côté cylindre, et en ce qu'au moins une ouverture (95, 95a) d'aspiration d'air froid est reliée avec l'intérieur du carter de soufflante par des canaux (97, 97a) s'étendant dans la zone du dispositif (57, 57a) de commande à tiroirs rotatifs et le longeant radialement.
  26. Moteur à bloc-cylindres rotatif selon l'une des revendications 1 à 25, caractérisé en ce qu'une machine productrice à travail (103, 103a), en particulier un compresseur d'une pompe à chaleur ou un générateur électrique, est couplée au vilebrequin (21, 21a).
  27. Moteur à bloc-cylindres rotatif selon la revendication 21, caractérisé en ce que le canal (47, 47a) d'échappement de renouvellement des gaz est relié à un échangeur de chaleur (105, 105a), en particulier une installation de chauffage de bâtiment.
  28. Moteur à bloc-cylindres rotatif selon l'une des revendications 1 à 27, caractérisé en ce que le bloc-cylindres rotatif (5c) comprend deux parties de rotor formant les parois de cylindre (133), une première partie de rotor formant une paroi latérale axiale (133) du bloc-cylindres rotatif et une paroi périphérique constituant l'ensemble des couvercles de cylindre (33c), et la deuxième partie de rotor constituant une autre paroi latérale axiale (133) et portant des protubérances (151) qui font saillie selon la direction axiale et délimitent les cylindres (15c) entre eux selon la direction circonférentielle.
EP93919205A 1992-08-28 1993-08-27 Moteur a deux temps a cylindres rotatifs Expired - Lifetime EP0656992B1 (fr)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE4228639A DE4228639A1 (de) 1992-08-28 1992-08-28 Zylinderläufermaschine
DE4228639 1992-08-28
PCT/EP1993/002325 WO1994005902A1 (fr) 1992-08-28 1993-08-27 Moteur a cylindres rotatifs

Publications (2)

Publication Number Publication Date
EP0656992A1 EP0656992A1 (fr) 1995-06-14
EP0656992B1 true EP0656992B1 (fr) 1997-01-22

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EP93919205A Expired - Lifetime EP0656992B1 (fr) 1992-08-28 1993-08-27 Moteur a deux temps a cylindres rotatifs

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US (1) US5720241A (fr)
EP (1) EP0656992B1 (fr)
AT (1) ATE148201T1 (fr)
DE (2) DE4228639A1 (fr)
WO (1) WO1994005902A1 (fr)

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FR2891582A1 (fr) * 2005-10-03 2007-04-06 Jacques Busseuil Mecanisme a pistons et cylindres rotatifs
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US8986253B2 (en) 2008-01-25 2015-03-24 Tandem Diabetes Care, Inc. Two chamber pumps and related methods
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Also Published As

Publication number Publication date
US5720241A (en) 1998-02-24
EP0656992A1 (fr) 1995-06-14
ATE148201T1 (de) 1997-02-15
WO1994005902A1 (fr) 1994-03-17
DE4228639A1 (de) 1994-03-03
DE59305283D1 (de) 1997-03-06

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