Classifications

• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
  • F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
  • F01C1/00—Rotary-piston machines or engines
  • F01C1/08—Rotary-piston machines or engines of intermeshing engagement type, i.e. with engagement of co- operating members similar to that of toothed gearing
  • F01C1/12—Rotary-piston machines or engines of intermeshing engagement type, i.e. with engagement of co- operating members similar to that of toothed gearing of other than internal-axis type
  • F01C1/123—Rotary-piston machines or engines of intermeshing engagement type, i.e. with engagement of co- operating members similar to that of toothed gearing of other than internal-axis type with tooth-like elements, extending generally radially from the rotor body cooperating with recesses in the other rotor, e.g. one tooth
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
  • F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
  • F01C1/00—Rotary-piston machines or engines
  • F01C1/08—Rotary-piston machines or engines of intermeshing engagement type, i.e. with engagement of co- operating members similar to that of toothed gearing
  • F01C1/12—Rotary-piston machines or engines of intermeshing engagement type, i.e. with engagement of co- operating members similar to that of toothed gearing of other than internal-axis type
  • F01C1/14—Rotary-piston machines or engines of intermeshing engagement type, i.e. with engagement of co- operating members similar to that of toothed gearing of other than internal-axis type with toothed rotary pistons
  • F01C1/20—Rotary-piston machines or engines of intermeshing engagement type, i.e. with engagement of co- operating members similar to that of toothed gearing of other than internal-axis type with toothed rotary pistons with dissimilar tooth forms
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
  • F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
  • F01C11/00—Combinations of two or more machines or engines, each being of rotary-piston or oscillating-piston type
  • F01C11/002—Combinations of two or more machines or engines, each being of rotary-piston or oscillating-piston type of similar working principle
  • F01C11/004—Combinations of two or more machines or engines, each being of rotary-piston or oscillating-piston type of similar working principle and of complementary function, e.g. internal combustion engine with supercharger
• • 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
  • F01C17/00—Arrangements for drive of co-operating members, e.g. for rotary piston and casing
  • F01C17/02—Arrangements for drive of co-operating members, e.g. for rotary piston and casing of toothed-gearing type
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
  • F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
  • F01C21/00—Component parts, details or accessories not provided for in groups F01C1/00 - F01C20/00
  • F01C21/18—Arrangements for admission or discharge of the working fluid, e.g. constructional features of the inlet or outlet
• • 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
  • F02B53/00—Internal-combustion aspects of rotary-piston or oscillating-piston 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
  • F02B55/00—Internal-combustion aspects of rotary pistons; Outer members for co-operation with rotary pistons
  • F02B55/02—Pistons

Definitions

• the invention relates to a rotary piston engine, comprising a compression stage and an expansion stage, each with a rotating working piston for compression or expansion of a working gas.
• a generic rotary piston engine is known from WO 2008/071326 A1.
• a rotary piston engine is an internal combustion engine based on rotating and functionally corresponding rotary pistons for the compression of combustion gases and expansion of burned gases.
• the combustion gas and the burnt gas are referred to in the context of this description simplifying as working gas.
• Rotary piston engines have much higher speeds than reciprocating engines such as. Otto engines with piston-connecting rod crankshaft, but perform the same work cycles, namely suction, compression, ignition and expansion. Since the compression volume in rotary piston engines is considerably smaller than in reciprocating engines, significantly more gas transitions occur between the power stroke units and the power density is much higher.
• the invention has for its object to provide a rotary piston engine, which allows even shorter gas paths than a conventional rotary piston engine.
• the rotary piston engine is provided according to claim 1, which summarizes a compression stage and an expansion stage, each with a rotating piston for compression or expansion of a working gas, the working piston of the compression stage and the expansion stage in axial direction are arranged one behind the other, preferably rotatable about a common axis of rotation.
• the working piston of the compression stage and the expansion stage can thus be arranged in the axial direction, ie along the axis of rotation, overlapping and immediately adjacent to each other, so that the gas paths between expansion and compression stage compared to the conventional solution are significantly shortened and solved the problem underlying the invention becomes.
• auxiliary pistons are also connected to the working pistons to form compression and expansion chambers of varying volume cooperate, arranged in the axial direction one behind the other and / or rotatable about a common axis, so that the rotational movements of the working and auxiliary pistons can be easily synchronized.
• the working piston of the compression stage and the expansion stage are arranged on a common shaft.
• the working piston of the compression stage and the expansion stage are rotatably connected or formed in one piece or in one piece. This allows the expansion stage to drive the compression stage according to the principle of an aircraft gas turbine almost lossless, so that the need for a clutch or power transmission device between expansion and compression stage is eliminated.
• the compressed working gas is discharged radially inward in the direction of the axis of rotation of the working piston for ignition.
• a volume within the working piston of the compressor and / or expansion stage for ignition and combustion of the working gas can be used and the gas paths between expansion and compression stage can be further reduced compared to the conventional solution.
• the compression stage fulfills at least one of the following requirements:
• the compressed working gas is passed to the ignition by the working piston.
• the compressed working gas can be introduced by a short path into an ignition chamber arranged inside the working piston. Short cable paths result in low pressure losses and high compression ratios.
• the working piston comprises at least one opening which penetrates the working piston.
• the compression stage in particular a compression chamber, which is formed by the working piston, the housing and an auxiliary piston cooperating with the working piston, in a certain rotational angle range of the working piston via the opening communicate directly with the ignition chamber.
• a check valve or one-way valve may be arranged between the compression chamber and the ignition chamber, preferably in the region of the opening, which only allows the working gas to pass from the compression chamber into the ignition chamber, but not vice versa
• the opening includes a plurality of parallel bores spaced axially from one another. - The opening penetrates the working piston substantially in the radial direction.
• the working piston comprises a lateral surface which defines at least one annular space portion together with a housing of the rotary piston engine. In this annulus section, the working gas can be sucked, mixed and compressed during a continuous rotational movement of the working piston.
• the lateral surface of the working piston is substantially cylindrical.
• the annular space section formed between the housing and the lateral surface can be ideally sealed.
• the lateral surface of the working piston can also be concave or convex.
• the working piston comprises at least one slide, which preferably projects radially from the lateral surface of the working piston.
• the slider causes in a continuous rotational movement of the working piston, that in the formed between the housing and the lateral surface annulus section initiated working gas is ideally sucked, mixed and compressed.
• the slider is formed involute in cross section.
• the flanks of the slide form parts of involutes. This can ensure that the working piston and the auxiliary piston seen in cross-section are particularly close in three points and are perfectly sealed against each other. Furthermore, optimum flow properties of the working gas result.
• the slider tapers from the base point to the tip and forms an acute angle in the crest region.
• the slider defines together with a housing of the rotary piston engine and the lateral surface of the working piston a preferably sealed on all sides annular space portion.
• the working piston comprises a plurality of slides, which protrude relative to the axis of rotation of the working piston at regular angular intervals from the lateral surface of the working piston. As a result, the number of working cycles per revolution of the working piston can be increased as desired.
• the working piston comprises three slides, which protrude relative to the axis of rotation of the working piston at angular intervals of 120 ° from the lateral surface of the working piston. The number of three sliders can give particularly advantageous performance characteristics of the motor.
• the opening terminates on a flank of the slider, preferably on a front in the direction of rotation flank of the slider.
• the working piston is designed as a double-walled hollow cylinder, wherein an inner cylinder of the working piston preferably has a greater axial length than an outer cylinder of the working piston.
• the working piston cooperates with an auxiliary piston to define at least one compression chamber of variable volume.
• the working piston and the auxiliary piston together with the housing form a compression chamber with a decreasing volume, when the working piston and the auxiliary piston in the proper direction of rotation roll against each other.
• the working piston cooperates with an auxiliary piston to define at least one suction chamber with variable volume.
• the working piston and the auxiliary piston together with the housing form a suction chamber with an increasing volume when the working piston and the auxiliary piston in the proper direction of rotation roll against each other.
• the auxiliary piston comprises a substantially cylindrical lateral surface.
• the auxiliary piston comprises a matched to the number of slides of the working piston number of recesses.
• the working piston and the auxiliary piston are rotatable forcibly synchronized.
• the compression stage comprises an adjustable control element which allows and prevents an escape of the compressed working gas from the compression stage alternately.
• the expansion stage meets at least one of the following requirements:
• the ignited working gas is for expansion radially outward, leading away from the axis of rotation of the working piston, passed. Short conduction paths result in low pressure losses and high efficiency of the rotary piston engine.
• the ignited working gas is passed for expansion through the working piston of the expansion stage.
• the ignited working gas can be conducted in a short path into the expansion chamber. This results in very low pressure losses and a very high efficiency of the rotary piston engine.
• the working piston comprises at least one opening which penetrates the working piston.
• the expansion stage in particular an expansion chamber, which is formed by the working piston, the housing and an auxiliary piston cooperating with the working piston, communicate directly with the ignition chamber via the opening in a certain rotational angle range of the working piston.
• the aperture which penetrates the working piston of the expansion stage has a larger overall cross-sectional area than the aperture penetrating the working piston of the compression stage.
• the opening penetrates the working piston substantially in the radial direction.
• the ignited working gas can be directed by the shortest route into the expansion chamber. This results in particularly low pressure losses and a particularly high efficiency of the rotary piston engine.
• the working piston comprises a lateral surface which defines at least one annular space portion together with a housing of the rotary piston engine.
• the ignited working gas can be optimally expanded and ejected during a continuous rotational movement of the working piston.
• the lateral surface of the working piston is substantially cylindrical.
• the annular space section formed between the housing and the lateral surface can be ideally sealed.
• the lateral surface of the working piston can also be concave or convex.
• the working piston comprises at least one slide, which preferably projects radially from the lateral surface of the working piston. The slider causes in a continuous rotational movement of the working piston, that the energy released by combustion of the working gas optimally acts on the working piston and is converted into rotational energy.
• the slide is seen in cross-section evolvent-shaped.
• the flanks of the slide form parts of involutes. This can ensure that the working piston and the auxiliary piston seen in cross-section are particularly close in three points and are perfectly sealed against each other. Furthermore, optimum flow properties of the working gas result.
• This cross-sectional shape favors the flow characteristics of the expanding working gas in the annular space formed between the housing and the lateral surface.
• the slider defines together with a housing of the rotary piston engine and the lateral surface of the working piston a preferably sealed on all sides annular space portion.
• the working piston comprises a plurality of slides, which protrude relative to the axis of rotation of the working piston at regular angular intervals from the lateral surface of the working piston. As a result, the number of working cycles per revolution of the working piston can be increased as desired.
• the working piston comprises three slides, which protrude relative to the axis of rotation of the working piston at angular intervals of 120 ° from the lateral surface of the working piston. With this number of slides, particularly advantageous line properties of the motor can result.
• the opening terminates on a flank of the slider, preferably on the rearward in the direction of rotation flank of the slider.
• the expansion energy of the ignited working gas can additionally be used as a drive for accelerating the working piston.
• the ending on the flank of the slide opening acts as a nozzle, so that the working piston is acted upon the outlet of the working gas with a torque.
• the working piston is designed as a single-walled cylinder. In this design, the working piston can be produced inexpensively.
• the working piston cooperates with an auxiliary piston to define at least one variable volume expansion chamber.
• the working piston and the auxiliary piston together with the housing form an expansion chamber with an increasing volume when the working piston and the auxiliary piston in the proper direction of rotation roll against each other.
• the auxiliary piston comprises a substantially cylindrical lateral surface.
• the auxiliary piston comprises a matched to the number of slides of the working piston number of recesses.
• the working piston and the auxiliary piston are forcibly rotatable.
• the expansion stage includes an adjustable control, which allows the penetration of the ignited working gas in the expansion stage alternately and prevented.
• the ignition chamber is at least partially radially disposed within the working piston of the compression stage and / or radially within the working piston of the expansion stage. This arrangement proves to be particularly compact.
• the ignition chamber can communicate in a preferably adjustable rotational angle range of the working piston with the compression stage, in particular with the compression chamber.
• the optimum ignition timing and the optimal time window for introducing the working gas into the ignition chamber vary with the operating conditions of the rotary piston engine.
• the inventively provided adjustability of the time window for the introduction of the working gas into the ignition chamber and / or the inventively provided adjustability of the ignition timing in relation to a rotational angle position of the working piston of the compression stage can significantly improve the performance of the rotary piston engine.
• the ignition chamber can communicate in a preferably adjustable rotational angle range of the working piston with the expansion stage, in particular with the expansion chamber.
• the ignited working gas is not suddenly introduced into the expansion chamber.
• better expansion characteristics can be achieved.
• the slide of the working piston can be acted upon at right angles to the force of the expanding working gas.
• the optimal time window for introducing the working gas into the expansion chamber varies with the operating conditions of the rotary piston engine.
• the inventively provided adjustability of the time window for the introduction of the working gas into the expansion chamber in relation to a rotational angle position of the working piston of the expansion stage can significantly improve the performance of the rotary piston engine.
• the ignition chamber can communicate in a preferably adjustable rotational angle range of the working piston neither with the compression stage nor with the expansion stage. As a result, a compressed working gas can also be enclosed in the ignition chamber without separate valves.
• the ignition chamber comprises an ignition chamber inlet, which can communicate in a preferably adjustable rotation angle range of the working piston of the compression stage via the opening with a compression chamber.
• the ignition chamber comprises a Zündschank, which can communicate in a preferably adjustable rotation angle range of the working piston of the expansion stage via the opening with an expansion chamber.
• the ignition chamber includes a spark plug that is aligned substantially parallel to an axis of rotation of the power pistons.
• the ignition chamber is at least partially axially disposed within the working piston of the compression stage and / or at least partially axially within the working piston of the expansion stage.
• the ignition chamber is at least partially formed within the working piston of the compression stage and / or at least partially within the working piston of the expansion stage, wherein the Zündzigabitese preferably in the radial Direction and / or circumferentially offset from one another, preferably are different in size.
• the ignition chamber is arranged eccentrically to the axis of the working piston of the compression stage and / or eccentrically to the axis of the working piston of the expansion stage, wherein the distance of the ignition chamber from the axis of the working piston is preferably greater than the distance of the ignition chamber from a lateral surface of the working piston.
• the Zündschausgang is located radially and / or circumferentially offset from the ignition chamber, preferably radially outside the Zündwaiteingangs and / or offset in the direction of rotation of the working piston to Zündwaiteingang.
• the rotary piston engine has a control console that meets at least one of the following requirements:
• the control console is adjustable, preferably rotatable, arranged in the housing of the rotary piston engine.
• the control panel can be rotated relative to the housing of the rotary piston engine by an angle of +/- 30 °, preferably +/- 20 °, preferably +/- 10 °, more preferably +/- 5 ° relative to the axis of rotation of the working piston.
• the ignition chamber and / or the ignition chamber inlet and / or the ignition chamber outlet and / or the spark plug is / are arranged in the control console.
• the control console comprises a first cylindrical portion which is arranged radially within the working piston of the compression stage.
• This section preferably has no bearing function and is slightly spaced from the inner cylinder and / or the outer cylinder of the working piston of the compression stage, so that in each case results in a gap.
• a deep groove ball bearing can be provided between the first cylindrical portion of the control console and the working piston of the compression stage.
• the first cylindrical portion comprises the Zündsch having on a lateral surface a circumferential groove or groove. This groove or groove is swept in a corresponding rotational angle range of the working piston of the compression stage of the opening in the working piston of the compression stage and can communicate with this opening, so that the compressed working gas can flow into the ignition chamber.
• the channel or groove in the direction of rotation of the working piston of the compression stage at the end of the channel or groove, there is an opening through which the channel or groove leads into the ignition chamber. can communicate the channel.
• a corresponding groove or groove is provided for each opening per slide on the working piston of the compression stage.
• the control console comprises a second cylindrical portion which is disposed radially within the working piston of the expansion stage.
• This section preferably has no bearing function and is slightly spaced from the working piston of the expansion stage, so that there is a gap.
• a deep groove ball bearing can be provided between the second cylindrical portion of the control console and the working piston of the expansion stage.
• the control console on a lateral surface of the second cylindrical portion comprises a Zündhuntablauf with at least one circumferential opening which is swept in a corresponding rotational angle range of the working piston of the expansion stage of the opening in the working piston of the expansion stage and can communicate with this opening.
• a corresponding opening per slide on the working piston of the expansion stage is provided for each Zündsch.
• the housing is constructed in several parts of substantially plate-shaped parts.
• the modular design facilitates the assembly of the housing.
• the housing includes a front housing cover, a compression frame housing frame, an expansion stage housing frame, and a rear housing cover. Separate housing frames for the compression stage and the expansion stage, as well as double-sided housing covers, allow optimal mounting of the corresponding components.
• At least two housing parts are sealed against each other. This results in the operation of the rotary piston engine low pressure losses and high efficiency.
• the housing comprises a substantially cuboid outline. This design proves to be particularly compact and stable.
• the housing comprises an interface for a fuel feed and / or an interface for a housing cooling circuit and / or an interface for a control console cooling circuit and / or an exhaust gas outlet and / or interfaces for data and signal transmission.
• the housing comprises a fuel inlet, in which a ball check valve is arranged.
• the rotary piston engine has at least one shaft that meets at least one of the following requirements:
• the shaft is rotatably mounted in the housing.
• the shaft extends completely through the housing and protrudes on opposite sides of the housing.
• the shaft is designed as a working shaft on which the working piston of the compression stage and / or the working piston of the expansion stage is fixed or adjustable arranged / are.
• the shaft is designed as an auxiliary shaft on which auxiliary piston of the compression stage and / or the auxiliary piston of the expansion stage is fixed or adjustable arranged / are.
• the transmission is designed as a gear transmission.
• the gears of the gear transmission are arranged outside the housing.
• the gears of the gear transmission are designed as spur gears, preferably helical spur gears.
• the rotary piston engine has at least one cooling circuit.
• the rotary piston engine comprises at least two separate cooling circuits, for example for the housing and / or for the control console.
• the rotary piston engine has a carburetor for the treatment of the working gas.
• the rotary piston engine has an injection device for injecting the working gas into the compression stage or into the ignition chamber.
• a rotary piston engine comprising a compression stage and an expansion stage, each with a rotating piston for compression or expansion of a working gas and an ignition chamber for ignition and combustion of the working gas, wherein the ignition chamber in an adjustable rotation angle range of the respective working piston with the compression stage and / or communicate with the expansion stage.
• the beginning and / or the end of the rotation angle range is / are adjustable and / or the rotation angle range can be shifted as such.
• the ignition chamber can preferably communicate only with the compression stage, in a second adjustable rotation angle range preferably communicate neither with the compression stage nor with the expansion stage, and in a third adjustable rotation angle range preferably communicate only with the expansion stage.
• the rotary piston engine according to this aspect of the invention can be combined with any of the features mentioned in the description and the claims.
• the rotational angle range of the respective working piston in which the ignition chamber can communicate with the compression stage and / or with the expansion stage, is controlled or regulated as a function of a measured variable, preferably the rotational speed of the respective working piston.
• the beginning and / or the end of the rotation angle range is / are controllable and / or the rotation angle range can be shifted as such.
• Yet another aspect of the invention relates to a rotary piston engine, comprising a compression stage and an expansion stage, each with a rotating piston for compression or expansion of a working gas and an ignition chamber for ignition and combustion of the working gas, the ignition chamber at least partially radially within the working piston of the compression stage and / or is arranged radially within the working piston of the expansion stage.
• the rotary piston engine according to this aspect of the invention can be combined with any of the features mentioned in the description and the claims.
• the rotary piston engine is designed as a petrol-based diesel engine.
• the rotary piston engine comprises an ignition spiral to ignite the working gas in the ignition chamber.
• the glow spiral is preferably adjustable on Housing arranged to ensure a pinpoint, automatic ignition.
• the rotary piston engine includes an injector to inject the fuel directly into the ignition chamber.
• the injection valve is preferably arranged adjustably on the housing. This can ensure that the injection timing and the ignition timing take place simultaneously.
• the fuel is already injected in the compressor stage 2 or in the intake passage.
• measures for recovering energy from the exhaust gas are taken to increase the efficiency of the rotary piston engine.
• the exhaust gas of the rotary piston engine is withdrawn via at least one heat exchanger and / or via at least one turbine energy and returned to the rotary piston engine.
• the energy obtained from the exhaust gas can also be used to operate other energy-consuming components.
• the exhaust gas is used for heating and / or pre-compression of the intake air.
• FIG. 1 shows a side view of the rotary piston engine according to the invention.
• FIG. 2 shows a front view of the rotary piston engine according to the invention.
• Figure 3 shows a section III-III of Fig. 2, which passes through the working and auxiliary shafts.
• Figure 4 shows a perspective view of the front of the rotary piston engine according to the invention.
• FIG. 5 shows another perspective view of the front side of the invention
• Figure 6 shows a perspective view of the back of the rotary piston engine according to the invention.
• FIG. 7 shows a rear view of the rotary piston engine according to the invention.
• Figure 8 shows a perspective partial sectional view of the back of the invention
• FIG 9 shows a perspective partial sectional view of the working shaft of the rotary piston engine according to the invention with control console and without spur gear.
• Figure 10 shows a perspective view of the working shaft of the rotary piston engine according to the invention with control console and with spur gear.
• Figure 1 1 shows another perspective view of the working shaft of the invention
• Rotary piston engine with control console and with spur gear.
• Figure 12 shows a perspective view of the working shaft and the auxiliary shaft of the rotary piston engine according to the invention in the coupling state.
• FIG. 13 shows a perspective view of the control console of the rotary piston engine according to the invention.
• FIG. 14 shows another perspective view of the control console of the rotary piston engine according to the invention.
• Figure 15 shows an exploded view of the working shaft of the rotary piston engine according to the invention with control console.
• Figure 16 shows a perspective partial sectional view of the working shaft and the control console of the rotary piston engine according to the invention in the intended mounting state without spur gear.
• Figure 17 shows a perspective view of the front of the rotary piston engine according to the invention in the intended mounting state without spur gears and without front housing cover.
• Figure 18 shows the rotary piston engine according to the invention in the intended mounting state without spur gears and without front housing cover in a working state of the compression stage.
• Figure 19 shows schematically the rotary piston engine according to the invention without spur gears and without front housing cover in a first operating state of the expansion stage.
• Figure 20 shows schematically the rotary piston engine according to the invention without spur gears and without front housing cover in a second operating state of the expansion stage.
• Figure 21 shows a schematic sectional view of a part of a rotary piston engine according to the invention according to the second embodiment of the invention.
• Figure 22 shows a schematic sectional view of a rotary piston engine according to the invention according to the third embodiment of the invention.
• Figure 23 shows a schematic side view of the working and auxiliary shafts of the rotary piston engine according to the invention according to the third embodiment of the invention, wherein the working and auxiliary pistons of the expansion and compression stage are shown overlapping.
• FIG. 24 shows a schematic sectional view of a rotary piston engine according to the fourth embodiment of the invention.
• FIG. 25 shows a schematic sectional view of a rotary piston engine according to the fifth embodiment of the invention.
• Figure 26 shows a schematic side view of the working and auxiliary shafts of the rotary piston engine according to the invention according to the fifth embodiment of the invention, the working and auxiliary pistons of the expansion and compression stage are shown overlapping sections.
• Figure 27 shows a schematic sectional view of the working shaft of the invention
• Figure 28 shows a schematic side view of the working shaft of the invention
• Rotary piston engine according to the fifth embodiment of the invention, wherein the working piston of the expansion stage and the compression stage are shown overlapping.
• FIG. 29 shows schematic side views of the working and auxiliary pistons of the compression stage of the rotary piston engine according to the fifth embodiment of the invention, FIG. 29A showing the working and auxiliary pistons of the compression stage in a rotational angle position at the beginning of the loading of the ignition chamber, while FIG - And auxiliary piston of the compression stage at the end of the loading of the ignition chamber shows.
• FIG. 30 shows schematic side views of the working and auxiliary pistons of the expansion stage of the rotary piston engine according to the invention according to the fifth embodiment.
• FIG. 30A shows the working and auxiliary pistons of the expansion stage in a rotational angle position at the beginning of the discharge of the ignition chamber
• FIG. 30B shows the working and auxiliary pistons of the expansion stage at the end of the discharge of the ignition chamber.
• Figure 31 shows various views of a control ring of the compression stage of the rotary piston engine according to the invention according to the fifth embodiment of the invention, wherein Fig. 31 A shows a section AB of Fig. 31 C, wherein Fig. 31 B shows a view A of FIG Fig. 31C shows a section CD of Fig. 31A.
• Fig. 32 shows various views of an expansion stage control ring of the rotary piston engine according to the fifth embodiment of the invention, Fig. 32A showing a section EF of Fig. 32C, Fig. 32B showing a view B of Fig. 32C, and Fig. 32C Section GH of Fig. 32A shows.
• FIG. 33 shows a schematic sectional view of a rotary piston engine according to the sixth embodiment of the invention.
• the housing 10 of the rotary piston engine 1 according to the invention comprises a front housing cover 101, a housing frame 102 for the compression stage 2, a housing frame 103 for the expansion stage 3 and a rear housing cover 104.
• the frame parts are connected via connecting means, For example, in the form of bolts 105 which penetrate the frame members 102, 103 and the front and rear housing covers 101 and 104, held together.
• connecting means For example, in the form of bolts 105 which penetrate the frame members 102, 103 and the front and rear housing covers 101 and 104, held together.
• On the housing are various peripheral interfaces such as connections for a fuel inlet 11 ( Figure 2), connections 12 ( Figure 2) for a housing cooling circuit, connections 13 for a control console cooling circuit, an exhaust pipe or exhaust 14, a fitting for spark plugs 15, an ignition cable 16 and an adjusting device 17 for a control console 6.
• connections for an electronic data and / or signal transmission can be provided.
• a working shaft 4 and parallel to an auxiliary shaft 5, which are located on located outside of the housing 10 spur gears 40, 50 in mesh, so that the rotational movements of the working shaft 4 and the auxiliary shaft 5 are coupled and zwangsssynchroninstrument accordingly.
• Control console 6 is accommodated, which is rotatable about the axis of rotation of the working shaft 4 relative to the housing 10, wherein the rotational or angular position of the control console 6 relative to the housing 10 via the adjusting device 17 can be changed.
• FIG. 2 shows a front view of the rotary piston engine 1 according to the invention.
• the housing 10 has a substantially parallelepipedal outline with corners rounded on the upper side and underside, whose centers of curvature coincide with the axes of rotation of the working shaft 4 and the auxiliary shaft 5.
• the depth of the housing 10, measured along the axes of rotation of the working shaft 4 and the auxiliary shaft 5 on the respective outer sides of the front and rear housing covers 101, 104 is, for example, about 175 mm at a total height of about 465 mm.
• the working and auxiliary shafts 4, 5 project about 87 mm beyond the front-side housing cover 101.
• the exhaust 14 protrudes about 124 mm beyond the outside of the rear housing cover .104.
• the total depth of the rotary piston engine 1 according to the invention measured along the axes of rotation of the working shaft 4 and the auxiliary shaft 5 of the over the front housing cover 101 above working and auxiliary shafts 4, 5 to the end of the exhaust 14, about 386 mm.
• the total width of the housing without exhaust 14, measured perpendicular to the axes of rotation of the working shaft 4 and the auxiliary shaft 5 is, for example, 311 mm and with exhaust, for example, 373 mm.
• the dimensions of the housing 10 may vary depending on the required rated power of the rotary piston engine 1 according to the invention.
• Figure 3 shows a section III - III of Figure 2, which passes through the working and auxiliary shafts 4, 5 of the rotary piston engine 1. Shown are again in section the components of the housing 10, namely the front housing cover 1, the housing frame 102 for the compression stage 2, the housing frame 103 for the expansion stage 3 and the rear housing cover 4.
• the working shaft 4 is opposite the housing 10 and the front side Housing cover 101 and relative to the control console 6 via a plurality of bearings, preferably angular contact ball bearings, rotatably mounted and thus relative to the housing 10 and the control console 6 rotatable.
• a working piston 20 of the compression stage 2 and a working piston 30 of the expansion stage 3 are arranged rotationally fixed.
• the auxiliary shaft 5 is opposite to the housing 10 and the front and rear housing covers 101, 104 via a plurality of rolling bearings, preferably angular contact ball bearings, rotatably mounted and therefore rotatable relative to the housing 10.
• a plurality of rolling bearings preferably angular contact ball bearings, rotatably mounted and therefore rotatable relative to the housing 10.
• On the auxiliary shaft 5, an auxiliary piston 25 of the compression stage 2 and an auxiliary piston 35 of the expansion stage 3 are arranged rotationally fixed.
• angular contact ball bearings it is possible to adjust the axial distance of the working piston 20, 30 or auxiliary piston 25, 35 in the housing 10 so that they do not touch the inside of the housing wall and between the working piston 20, 30 and auxiliary piston 25, 35 and the housing wall forms a minimum distance.
• the working piston 20 of the compression stage 2 comprises a substantially hollow cylindrical shape with double wall.
• the inner cylinder of the working piston 20 extends almost over the entire width of the frame parts 102, 103 of the housing 10 and sits directly on the working shaft 4, while the outer surface 22 of the outer cylinder with the frame part 102 of the compression stage 2 a plurality of chambers 23 divided by slide 23, 2b, 2c (FIG. 18) for the intake, mixing and compression of the working gas or of an air-fuel mixture.
• the chambers 2a, 2b, 2c (FIG. 18) are designed as annular space sections.
• the working piston 20 of the compression stage 2 comprises per slide 23 an opening 21 penetrating the outer cylinder of the working piston 10 (FIG.
• the opening 21 comprises three parallel bores which penetrate the outer cylinder of the working piston 20 in the radial direction in order to be able to communicate with the ignition chamber 60 of the rotary piston engine 1 in certain rotational angle ranges of the working piston 20.
• the working piston 30 of the expansion stage 3 Concentric with the inner cylinder of the working piston 20 of the compression stage 2, the substantially cylindrical working piston 30 of the expansion stage 3 is arranged.
• the outer circumferential surface 32 of the working piston 30 of the expansion stage 3 forms with the frame part 103 of the expansion stage 3 several subdivided by slide 33 and formed as annular space chambers chambers 3a, 3b, 3c (Fig. 19 and 20) for expansion of the ignited working gas.
• the working piston 30 of the expansion stage 3 comprises per slide 33 at least one opening 31 (FIG. 9), which is formed in the direction of rotation at the rear on each of the projecting over the lateral surface 32 in the radial direction slide 33.
• the opening 31 penetrates the working piston 30 of the expansion stage 3 in the radial direction in order to be able to move in at least one predetermined angle of rotation. rich of the working piston 30 to communicate with the ignition chamber 60 of the rotary piston engine 1 can.
• ring-shaped or disc-shaped cutting discs are arranged preferably rotationally fixed on the working shaft 4 are arranged and limit the chambers formed as annular space sections of the compressor and expansion stages 2, 3 in the axial direction.
• the cutting disc between the working pistons 20, 30 of the compression and expansion stage 2, 3 preferably accomplishes a labyrinth seal to allow passage of the working gas from one of the chambers 2a, 2b, 2c (FIG. 18) of the compression stage 2 into one of the chambers 3a, 3b 3c (FIGS. 19 and 20) of the expansion stage 3.
• the control console 6 is rotatable relative to the housing 10, wherein the rotational or angular position of the control console 6 relative to the housing 10 by actuation of the Verstellvorrich- device 17 in a predetermined angular range is adjustable.
• the outer cylinder of the working piston 20 of the compression stage 2 slides without contact over a first cylindrical portion 61 of the control console 6, while the working piston 30 of the expansion stage 3 slides without contact over a second cylindrical portion 66 of the control console 6.
• the second cylindrical portion 66 of the control console 6 has a slightly larger diameter than the first cylindrical portion 61 of the control console 6.
• the control console 6 can be rotated relative to the housing 10 by an angle of approximately +/- 10 ° relative to the rotational axis of the working pistons 20, 30 of the compressor and expansion stages 2, 3 by actuating the adjusting device 17.
• the ignition chamber 60, a Zündschzulauf 62, 63, 64 with radial bores 63 and an axial, opening into the ignition chamber 60 connecting bore 64, a Zündschablauf and a spark plug 65 are disposed within the control console 6 and formed.
• the spark plug 65 is intended aligned substantially parallel to a rotational axis of the working piston 20, 30.
• the first cylindrical section 61 of the control console 6 is arranged as intended radially within the working piston 20 of the compression stage 2, while the second cylindrical section Section 66 of the control console 6 is intended radially arranged within the working piston 30 of the expansion stage 3.
• the ignition chamber 60 is formed in the second cylindrical portion 66 of the control console 6 and is accordingly located radially within the working piston 30 of the expansion stage 3 as intended.
• the ignition chamber 60 has a volume of 13.44 cm 3 . It is, for example, milled into the control console 6 with a milling cutter.
• the radial inlet bores 63 at the front in the direction of rotation of the working piston 20, 30 front ends of the grooves 62 and leading into the ignition chamber 60 and the connecting bore 64 which extends in the axial direction parallel to the axes of rotation of the working piston 20, 30 have relatively to the compression volume as large a diameter as possible, so that a minimal flow resistance and a maximum compression can be achieved.
• the Zündschablauf extends over a rotational angle range of about 60 ° in a second cylindrical portion 66 of the control console 6 in the circumferential direction of the same.
• the ignition chamber 60 can communicate with the compression stage 2 and with the expansion stage 3 in an adjustable rotational angle range of the working piston 20 or the working piston 30.
• the Zündschzulauf 62, 63, 64 communicate in an adjustable rotation angle range of the working piston 20 of the compression stage 2 via the opening 21 in the working piston 20 of the compression stage 2 with the compression chamber, while the Zündschablauf in an adjustable rotation angle range of the working piston 30 of the expansion stage 3 via the opening 31 in the working piston 30 of the expansion stage 3 can communicate with the expansion chamber.
• the Zündhuntzulauf 62, 63, 64 as well as the Zündbibablauf is blocked in an adjustable rotation angle range of the working piston 20 and the working piston 30 so that the ignition chamber 60 can communicate with either the compression stage 2 or the expansion stage 3 and the compressed working gas in the Ignition chamber 60 is included.
• the ignition of the compressed working gas preferably takes place.
• the lateral surface 32 of the working piston 30 of the expansion stage 3 rolls on a lateral surface of the auxiliary piston 35 of the expansion stage 3 kind of involute in the ideal case without contact, radially above the outer surface 32 of the working piston 30 projecting involute slide 33 at angular intervals of 120 ° in corresponding recesses 36 in the lateral surface of the auxiliary piston 35 dip.
• the cutting discs between the working piston 20, 30 and the housing parts 101, 104 are received sealingly in corresponding recesses of the auxiliary piston 25, 35.
• Figures 4 and 5 show various perspective views of the front
• Figure 6 is a perspective view of the back
• Figure 7 is a rear view of the rotary piston engine according to the invention 1.
• On the back of the housing 10 is a scale on which the angular position of the control console 6 relative to the housing 10th is shown.
• Figure 8 shows a perspective partial sectional view of the back of the rotary piston engine according to the invention 1.
• parts of the front and rear housing covers 101, 104 and the housing frame 102, 103 of the compression stage 2 and the expansion stage 3 are omitted.
• the slides 23, 33 of the working pistons 20, 30 are aligned with respect to the common axis of rotation in the same angles of rotation and angular intervals.
• the cutting discs between the working piston 20, 30 and the housing parts 101, 104 during rolling of the working and auxiliary shafts 4, 5 are sealingly received in corresponding recesses of the auxiliary piston 25, 35.
• the chambers 2a, 2b, 2c FIG.
• Figure 9 shows a perspective partial sectional view of the working shaft 4 of the rotary piston engine 1 according to the invention with control console 6.
• the spur gear and provided between the piston 20 of the compression stage 2 and the front housing cover 101 cutting disc of the rotary piston engine 1 according to the invention are not shown.
• Figure 10 and 1 1 show various perspective views of the working shaft 4 in the intended mounting condition
• Figure 12 shows a perspective view of the working shaft 4 and the auxiliary shaft 5 in the coupling state on the end arranged, helical spur gears 40, 50, via which the rotational movements of the working shaft 4th and the auxiliary shaft 5 are coupled and zwangsssynchroninstrument.
• FIG. 13 shows a perspective view of the control console 6 of the rotary piston engine 1 according to the invention.
• FIG. 14 shows another perspective view of the control console 6,
• FIG. 15 shows an exploded view of the working shaft 4 with control console 6 arranged coaxially therewith.
• FIG. 16 shows a perspective partial sectional view of the work shaft 4 and Figures 17 and 18 show schematically the rotary piston engine 1 according to the invention without spur gears and without the front housing cover 101 in.
• the control console 6 in the intended mounting state and Figures 17 and 18 the rotary piston motor according to the invention in the intended mounting state without spur gears and without front housing cover 101 in a working state of the compression stage first and second states of the expansion stage.
• FIGS. 18 to 20 indicate the intended direction of rotation of the working pistons 20, 30 and auxiliary pistons 25, 35.
• the working piston 20, 30 rotate in the illustration of Figures 18 to 20 in the clockwise direction and the auxiliary piston 25, 35 in the counterclockwise direction. It can be seen in Figures 18 and 19, the positions of the slide 23, 33 of the working piston 20, 30 at the time of ignition, ie at the end of the compression and before the start of the expansion.
• the displaced by 120 degrees slide 23, 33 of the working piston 20, 30 of the compression stage 2 and the expansion stage 3 form in cooperation with the associated auxiliary piston 25, 35 and the housing 10 each formed as annular space sections chambers 2a, 2b, 2c (Fig. 18) or 3a, 3b, 3c (Fig. 19).
• a chamber of the compression level 2 is characterized by the dense arrangement of the working piston 20 and the associated Auxiliary piston 25 also divided into two, with a lock between the two chamber sections is effected.
• the partial circular ring-shaped chambers 2a, 2b, 2c and 3a, 3b, 3c designed as annular space sections have approximately a volume of 147 cm 3 .
• the decreasing part of the two-part chamber 2c of the compression stage 2 forms the compression chamber.
• the enlarging part of the two-part chamber 2c of the compression stage 2 forms the suction chamber.
• the enlarging part of the two-part chamber 3c / 3c * of the expansion stage 3 forms the expansion chamber.
• a working gas is introduced into the suction chamber of the compression stage 2.
• the mixture preparation is realized by means of a carburettor (not shown) or the fuel is conveyed by an injection system directly into the compression chamber 2 c or into the ignition chamber 60.
• the maximum volume of the suction chamber 2a is about 147 cm 3 . Due to the rotational movement of the working piston 20 of the compression stage 2, the volume of the suction chamber varies, so that the working gas is sucked or sucked. During the rotation of the working piston 20 of the compression stage 2, which rotates, for example. At a speed of 10,000 rev / min, the suction chamber is filled per revolution three times with working gas. In the continuous rotation of the working piston 20 of the compression stage 2, the working gas is mixed in the chambers 2a and 2b.
• the ignition chamber inlet 62, 63, 64 is opened and the ignition chamber outlet is blocked, so that the ignition chamber 60 can only communicate with the compression stage 2. If the rotation angle range of 60 ° has passed through the slide 23, then the ignition chamber 60 closes again and communication between the compression chamber 2c and the ignition chamber 60 is interrupted. About 90 vol .-% of the compressed working gas are thus in the Ignition chamber 60 included. The remaining 10% by volume will be taken with the next spin. For this reason, the compression and thus the efficiency of the rotary piston engine 1 increase with increasing rotational speed of the working piston 20.
• a check valve can be arranged between the compression chamber 2c and the ignition chamber 60.
• Figures 18 and 19 show the rotational angular positions of the working piston 20, 30 at the time of ignition.
• the slide 23 on the working piston 20 of the compression stage 2 has pressed the compressed ignition mixture into the ignition chamber 60 and is located in the recess 26 of the auxiliary piston 25.
• the Zündschzulauf 62, 63, 64 as well as the Zündwaitablauf blocked so the ignition chamber 60 can communicate neither with the compression stage 2 nor with the expansion stage 3.
• the compressed working gas is enclosed in the ignition chamber 60.
• the working gas is now ignited at a pressure of 11 bar by the spark plug 65 protruding into the ignition chamber 60.
• the ignition point may preferably be controlled or controlled by a control device in relation to the rotational angle positions of the working pistons 20, 30 as a function of various measured variables, such as the rotational speed of the working pistons 20, 30, etc.
• Figure 20 shows the rotational angular position of the working piston 30 of the expansion stage shortly after ignition and during expansion.
• the slider 33 on the working piston 30 of the expansion stage 3 has now just emerged from the recess 36 of the auxiliary piston 35 of the expansion stage 3 and is driven by the expansion of the ignited working gas.
• the Zündschzulauf 62, 63, 64 is blocked and only the Zündwaitablauf open, so that the ignition chamber 60 can communicate only with the expansion stage 3.
• the working piston 30 of the expansion stage 3 has three frontal, offset by 120 ° to each other openings 31.
• the openings 31 of the working piston 30 and the Zündschablauf one above the other wherein the ignited working gas is pressed during the rotation angle range of about 60 ° in the expansion chamber.
• the aspirated gas volume occupies a much larger space, with the combustion gas flowing out of the ignition chamber 60 increasing its volume in fractions of a second.
• the burnt working gas is discharged through the opening 31 in the rotationally rearward flank of the spool 33 into the expansion chamber 3c *. Due to the resulting pressure, a force acts at right angles to the axis of rotation (in the tangential direction on the slide 33), so that the working piston 30 of the expansion stage 3 or the entire working shaft 4 is acted upon by a constant torque.
• the maximum torque resulting from the pressure is available, for example for driving a vehicle or the like.
• the combustion gas may leave the expansion stage 3 after combustion and expansion and is expelled via the exhaust gas outlet 14.
• the working piston 30 of the expansion stage 3 drives the working piston 20 of the compression stage 2.
• the chamber sections 2a, 2b, 2c (FIG. 18) and 3a, 3b, 3c (FIGS. 19 and 20) of the compression and expansion stages 2, 3 are, for example, sealed relative to the housing by non-contact seals, so that the compressed working gas only in the ignition chamber 60 is pressed and the expanding working gas does not overlap into the compression chamber after ignition has taken place.
• the control console 6 By turning the adjuster 17 formed as adjusting screw, the control console 6 can be rotated in the housing 10. By this rotation, thus, the position of the ignition chamber 60 can be adjusted. In combination with the inventively provided adjustability of the ignition timing, thus, the initiation of the working gas can be regulated exactly.
• the rotary piston engine 1 is designed as an internal combustion engine after the design of a water-cooled rotary piston engine with a compression of about 11: 1 with three ignitions per revolution.
• the translation of the working and the auxiliary shaft 4, 5 is 1: 1. Ignition takes place via a spark plug 65 of the Type NGK M16x1 (2-pin). Mixture formation takes place via a modified Walbro carburetor.
• Figure 21 shows a schematic sectional view of a part of the rotary piston engine 1 according to the invention according to the second embodiment of the invention.
• the auxiliary piston of the compression stage 2 and the expansion stage 3 and other elements are not shown for the sake of clarity.
• the rotary piston engine 1 between the compression chamber and the ignition chamber 60 and / or between the ignition chamber 60 and the expansion chamber comprises a valve 692, 693 and an automatic on / off closure.
• the valve 692 controls the gas transfer from the compression chamber into the ignition chamber 60 and / or the valve 693 regulates the gas transfer from the ignition chamber 60 in the expansion chamber.
• the ignition chamber 60 is formed in the control console 6, which is adjustable relative to the housing 10 about the axis of the working shaft 4, so that the ignition chamber 60 in an adjustable rotation angle range of the respective working piston 20, 30 with the compression stage 2 or with the compression chamber and / or. or communicate with the expansion stage 3 or with the expansion chamber.
• the diameters of the working and auxiliary pistons 20, 25 are selected so that their peripheral speeds are the same. The difference of the peripheral speeds is therefore equal to zero. This allows tighter tolerances, better compaction and less wear.
• Working piston 30 of the expansion stage 3 is selected to be larger in diameter than the working piston 20 of the compression stage 2. As a result, the torque is increased and the speed (depending on the combustion speed) is lowered.
• the diameter of the auxiliary piston 35 is to be reduced; the tolerances of the pistons 30, 35 involved can be expanded.
• the compression ratio is determined constructively.
• the Zündschausgang in the expansion stage 3 is radially outside the Zündwaiteingang in the compression stage 2.
• the ignition chamber 60 is arranged eccentrically to the axis of the working shaft 4 and preferably in the direction of the axis Auxiliary shaft 5 offset. As a result, the working gas only has to be kept in radia- ler direction in or out of the ignition chamber 60 are performed.
• the working chambers 2a, 2b, 2c of the compression stage 2 and the working chambers 3a, 3b, 3c of the expansion stage 3, which are formed in the radial direction between the lateral surfaces 22, 32 of the working piston 20, 30 and the housing parts 102, 103, are in the axial direction bounded by non-rotatably connected to the working shaft cutting discs 403, 405 and a stationary cutting disc 402.
• Figure 22 shows a schematic sectional view of a rotary piston engine 1 according to the invention according to the third embodiment of the invention.
• the housing 10 between the compression stage 2 and the expansion stage 3 on an intermediate part 105.
• the control console 6, which is arranged in the axial and radial direction substantially between the working piston 20 of the compression stage 2 and the working piston 30 of the expansion stage 3, is divided into two parts and is adjustable via an adjusting lever 6c in a predetermined rotational angle range relative to the intermediate part 105.
• At least part 6b of the control panel 6 is operable via the adjusting lever 6c extending inside the intermediate part 105 independently of the other part 6a.
• the ignition chamber 60 comprises a plurality of sections whose dimensions in the radial direction and / or in the circumferential direction increase from the ignition chamber inlet on the side of the compression stage 2 to the ignition chamber outlet on the side of the expansion stage 3.
• the ignition chamber 60 comprises a circumferentially extending, arc segment-like portion which is at least partially open radially outward to the working piston 30 of the expansion stage 3 out.
• FIG. 23 shows a schematic side view of the working and auxiliary shafts 4, 5 of the rotary piston engine 1 according to the invention according to the third embodiment of the invention, the working and auxiliary pistons 20, 25, 30, 35 of the expansion and compression stage 3, 2 are shown overlapping.
• the directions of rotation of the working and auxiliary shafts 4, 5 are indicated by arrows.
• the working piston 20, 30 of the compression stage 2 and the expansion stage 3 are - as shown - offset from one another such that the opening 21 at the front end of a slide 23 of the working piston 20 of the compression stage 2 is just closed by the auxiliary piston 25 of the compression stage 2, while the Opening 31 at the rear end of the associated slide 33 of the working piston 30 of the expansion stage 3 is just released by the auxiliary piston 35 of the expansion stage 3.
• the rotation angle range in which the ignition chamber 60 can communicate with the compression stage 2 preferably directly adjoins the rotation angle range in which the ignition chamber 60 can communicate with the expansion stage 3 without overlapping.
• the slides 23, 33 are arranged at regular intervals around the circumference of the working piston 20, 30 of the compression stage 2 and the expansion stage 3 and formed identically to form identical pairs of slides 23, 33.
• a corresponding number of work cycles described above per revolution of the working shaft 4 carried out analogously.
• FIG 24 shows a schematic sectional view of a rotary piston engine 1 according to the invention according to the fourth embodiment of the invention.
• the ignition chamber 60 is partially formed in the working piston 20 of the compression stage 2, partially in the working piston 30 of the expansion stage 3 and sections in a lying between the working piston 20, 30, rigidly connected to the working shaft 4 cutting disc 405, so that the ignition chamber 60 rotates with the working shaft 4 about its axis.
• each ignition chamber 60 is associated with a compression chamber 2a, 2b, 2c and an expansion chamber 3a, 3b, 3c.
• two adjustable relative to the housing 10 controls or control rings or control bars 620, 630 are provided, which is a communication of the ignition chamber 60 with the compression level 2 and / or with the expansion stage 3 temporarily enable and temporarily interrupt.
• the control strips 620, 630 are independently rotatable about the axis of the working shaft 4 via control levers 621, 631, which extend within the housing parts 101 and 104.
• the control strips 620, 630 are also substantially cylindrical and have slot-shaped openings 622, 632 which extend parallel to each other in the circumferential direction.
• the ignition chamber 60 can communicate with the compression stage 2 or with the compression chamber and / or with the expansion stage 3 or with the expansion chamber via these slot-shaped openings in an adjustable rotation angle range of the respective working piston 20, 30.
• the spark plug 15 extends from the side of the expansion stage 3 substantially parallel to the axis of the working shaft 4 through the control bar 630 of the expansion stage 3 into the ignition chamber 60 in order to ignite the compressed working gas.
• the spark plug 15 is thus adjustable together with the control bar 630 relative to the housing 10.
• the working piston 20 of the compression stage 2 has a smaller diameter but a greater axial length than the working piston 30 of the expansion stage 3.
• the ignition chamber 60 is arranged eccentrically to the axis of the working shaft 4 and the ignition chamber is radially outside the ignition chamber entrance.
• the portion 603 of the ignition chamber 60 formed in the working piston 30 of the expansion stage 3 has a smaller volume than the portion 602 of the ignition chamber 60 formed in the working piston 20 of the compression stage 2. Both portions 602, 603 of the ignition chamber 60 are offset in the radial direction and in the circumferential direction, but arranged overlapping each other, so that the sections 602, 603 can communicate with each other.
• the working gas in the ignition chamber 60 due to the centrifugal force is forced outwards in the radial direction in the direction of the ignition chamber outlet and the expansion stage 3.
• the Zündttingabites 603 is offset in the expansion stage 3 with respect to the Zündttingabrough 602 in the compression stage 2 radially outward and in the direction of rotation of the working shaft 4.
• the ignition chamber section 603 formed in the separating disk 405 preferably lies in the radial direction and in the circumferential direction between the two ignition chamber sections 602, 603.
• FIGS. 25 to 32 show a schematic sectional view of a rotary piston engine 1 according to the invention according to the fifth embodiment of the invention.
• the ignition of the working gas via a spark plug 15 which is arranged differently from the fourth embodiment on the side of the compression stage 2 in a relative to the housing 10 adjustable Zündstellring 610 and screwed from the outside.
• the Zündstellring 610 is arranged rotatable together with the spark plug 15 in its leadership in both directions, so that the respective exact ignition timing and the exact ignition point can be determined and adjusted.
• the spark triggers the explosion of the compressed gas, whereby a pressure wave from the ignition chamber 60 via the opening 31 in the expansion stage
• the Zündstellring 610 is independent of the control bars 620, 630 relative to the housing 10 adjustable.
• the position of the spark plug 15 is thus independent of the rotation angle range for effecting the gas transfer from the Versichtungscut 2 into the ignition chamber 60 and / or the rotation angle range for effecting the gas transfer from the ignition chamber 60 in the expansion stage 3 adjustable.
• the Zündttingabête 602, 603, 605 are flush with each other, wherein the formed within the cutting disc 405 Zündhuntabêt 605 extends along an oblique axis and the Zündttingabête 602, 603 steplessly bridged.
• the spark plug 15 is installed in the ignition chamber 60 (a spark plug 15 in each ignition chamber 60). This results in a construction of the working shaft
• the ignition pulse can be transmitted via sliding contacts or is carried out via induction.
• Figure 26 shows a schematic side view of the working and auxiliary shafts 4, 5 of the rotary piston engine 1 according to the invention according to the fifth embodiment of the invention, wherein the working and auxiliary pistons 20, 25, 30, 35 of the expansion and compression stage 3, 2 are shown overlapping sections ,
• the rotation angle ranges a1, ß1 of the respective working piston 20, 30 are indicated, in which the ignition chamber 60 via the openings 622, 632 of the control bars 620, 630 with the compression stage 2 or with the compression chamber and / or with the expansion stage 3 and . can communicate with the expansion chamber.
• Figure 27 shows a schematic sectional view of the working shaft 4 of the rotary piston engine 1 according to the invention according to the fifth embodiment of the invention.
• Figure 28 shows a schematic side view of the working shaft 4 of the rotary piston engine 1 according to the invention according to the fifth embodiment of the invention, wherein the working piston 20, 30 of the expansion stage 3 and the compression stage 2 are shown superimposed.
• Figure 29 shows schematic side views of the working and auxiliary pistons 20, 25 of the compression stage 2 of the rotary piston engine 1 according to the invention according to the fifth embodiment of the invention, wherein Fig. 29A, the working and auxiliary pistons 20, 25 of the compression stage
• FIG. 29B shows the working and auxiliary pistons 30, 35 of the compression stage 2 immediately after completion of the loading of the ignition chamber 60.
• the rotation angle range a1 ends offset by a rotation angle a2 against the direction of rotation of a connecting line of the axes of the working shaft 4 and the auxiliary shaft 5.
• the rotation angle range a1 and / or the rotation angle a2 can be adjusted by adjusting the control bar 620 relative to the housing 10. Thereby, the start and the end of the gas transfer from the compression stage 2 into the ignition chamber 60 (loading of the ignition chamber 60) can be set accurately.
• Figure 30 shows schematic side views of the working and auxiliary pistons 30, 35 of the expansion stage 3 of the rotary piston engine 1 according to the invention according to the fifth embodiment of the invention, wherein Fig. 30A, the working and auxiliary pistons 30, 35 of the expansion stage 3 in a rotational angle position immediately before the start of the discharge the ignition chamber 60 shows, while Fig. 30B shows the working and auxiliary pistons 30, 35 of the expansion stage 3 immediately after completion of the discharge of the ignition chamber 60.
• a communication of the ignition chamber 60 with the expansion stage 3 is only possible if the opening 31 of the slider 33 sweeps over the region of the opening 632 of the control bar 630 in the rotation angle range ß1.
• the rotation angle range ⁇ 1 begins by a rotation angle ß2 in the direction of rotation offset from the line connecting the axes of the working shaft 4 and the auxiliary shaft 5.
• the rotation angle range ß1 and / or the rotation angle ß2 can be adjusted by adjusting the control bar 630 relative to the housing 10. Thereby, the start and the end of the gas passage from the ignition chamber 60 to the expansion stage 3 (discharge of the ignition chamber 60) can be accurately set.
• FIG. 31 shows various views of a control element or control ring 620 of the compression stage 2 of the rotary piston engine 1 according to the invention according to the fifth exemplary embodiment of the invention, FIG. 31A showing a section AB from FIG. 31C, FIG. 31B a view A from FIG Fig. 31C shows while Fig. 31C shows a section CD of Fig. 31A.
• Figure 32 shows various views of a control or control ring 630 of the expansion stage 3 of the rotary piston engine 1 according to the invention according to the fifth embodiment of the invention, wherein Fig. 32A shows a section EF of Fig. 32C, wherein Fig. 32B shows a view B of Fig. 32C while Fig. 32C shows a section GH of Fig. 32A.
• the controls or control rings or control bars 620, 630 temporarily enable and interrupt communication of the ignition chamber 60 with the compression stage 2 and / or communication of the ignition chamber 60 with the expansion stage 3.
• the control bars 620, 630 are substantially cylindrical and have slot-shaped openings 622, 632 which extend parallel to each other in the circumferential direction.
• the ignition chamber 60 can communicate with the compression stage 2 or with the compression chamber and / or with the expansion stage 3 or with the expansion chamber via these slot-shaped openings in an adjustable rotation angle range of the respective working piston 20, 30.
• FIG. 33 shows a schematic sectional view of a rotary piston engine 1 according to the sixth embodiment of the invention.
• the rotary piston engine 1 is designed as a gasoline-based diesel.
• knock resistance will be disregarded.
• the process of knocking based on the fact that the gasoline-air mixture in the process of compression uncontrollably sooner or later leads to combustion. But exactly this property of the mixture leads to the rotational auto-igniter no disturbances, since this small difference is processed without a trace.
• the spark plug 15 is replaced by a glow spiral.
• the glow spiral is arranged in place of the spark plug 15 in Zündstellring 610. Identical as the spark plug 15 ignites the Glühspirale the gas through a window in the ignition chamber 60.
• the Glühspirale glows permanently, is adjustable with the Zündstellring 610 and is based on the exact Ignition point adjusted. Thus, a pinpoint ignition is ensured at all times. The ignition is automatic.
• an injection valve or an injection nozzle 611 is arranged in the ignition adjusting ring 610. This ensures that the injection timing and the ignition timing take place simultaneously. Since at the moment of injection and ignition of the control ring 620 blocks the opening 21 to the compressor stage 2, a flashback of the flame is excluded in the compressor stage 2 and the pressure wave can escape via the ignition chamber 60 only in the expansion stage 3.
• the desired and ideal point for triggering and escape of the pressure wave from the ignition chamber 60 is adjustable in dependence on the inertia of the gas and is controlled by means of the control ring 630.
• the fuel is supplied by direct injection. Because of the rotational speed of the rotary piston engine 1 mixing of the working gas is a challenge. Either is already injected in the compressor stage 2 or in the intake, which would allow a longer mixing, or it manages the injection directly into the compressor chamber at the inlet to the ignition 60th
• the hot exhaust gas of the rotary piston engine 1 is withdrawn via at least one heat exchanger and / or at least one turbine energy and returned to the system. It is further provided that the energy obtained from the exhaust gas is used to operate other energy-consuming components of a motor vehicle.
• the exhaust gas is used for heating and / or pre-compression of the intake air.

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• Engineering & Computer Science (AREA)
• Mechanical Engineering (AREA)
• General Engineering & Computer Science (AREA)
• Chemical & Material Sciences (AREA)
• Combustion & Propulsion (AREA)
• Output Control And Ontrol Of Special Type Engine (AREA)
• Percussive Tools And Related Accessories (AREA)
• Pistons, Piston Rings, And Cylinders (AREA)

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• 2010
  • 2010-02-01 DE DE102010006466A patent/DE102010006466B4/de not_active Expired - Fee Related
• 2011
  • 2011-02-01 RU RU2012137175/06A patent/RU2565486C2/ru not_active IP Right Cessation
  • 2011-02-01 KR KR1020127023729A patent/KR101524239B1/ko not_active IP Right Cessation
  • 2011-02-01 CN CN201180016645.9A patent/CN103003525B/zh not_active Expired - Fee Related
  • 2011-02-01 EP EP11704534A patent/EP2531699A2/de not_active Withdrawn
  • 2011-02-01 WO PCT/EP2011/000441 patent/WO2011092035A2/de active Application Filing

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