Prior art A great many motors and machines are known in the prior art. The most common of all mechanic rotary piston machines converting gas or liquid medium pressure to rotary motion, or vice versa, is the piston machine employing a crankgear which eventually developed into reciprocating internal combustion engines utilised especially in the automotive industry. The design of these engines is generally well known. They are fitted with pistons reciprocating along a straight-line path between bottom and top dead centres. The reciprocating-to-rotary motion conversion, passes through the bottom and top dead centres and ineffective distribution of forces applied to the piston rod all cause great losses of the expanding medium energy, which is the factor limiting the efficiency of this type of engine. When the piston stops and starts in both dead centres, the mechanism must overcome acceleration forces generated by the masses of the entire piston plus approximately one third of the piston rod. These moving masses generate well known inertial forces and moments that limit engine speed, lower specific power, cause undesired vibrations of engine parts, generate noise, and reduce life time.

However, there are also designs of internal combustion engines fitted with rotary pistons where no crankgear is required. Up to now, the principle of a mechanic crankgear-free rotary piston combustion engine has been most satisfactorily utilised by the engine design with a rotary piston moving inside a stator along a shortened epitrochoid curve. The faces of motor's rotary piston are formed by three identical curves.

Piston curve intersections, i e. piston tips, are fitted with radial sealing blades copying the inner face of the stator casing. This creates three separated chambers that periodically change their volume. The piston moves inside the cavity thanks to two gears with offset centrelines.

There are three working cycles per one piston revolution. Once geared, which is required due to the design nature, such a single-piston engine is equivalent to any conventional two-cylinder four-stroke engine. A classic example of such an engine is the so called Wankel engine as described in US Patents No. 3,442,257 and 4,434,757 and DE Patent Nr. 3,027,208. Some difficulties still persist with this type of engine, especially with regard to insufficient chamber tightness and sealing blades wear. As a result the fuel mixture leaks and miXes with exhaust gasses. Another drawback limiting any broader use of this type of engines is its higher oil consumption. Burnt oil and imperfect fuel combustion products generate greater quantities of harmful exhaust gasses than conventional piston engines. Another problem is the heat dissipation from the rotary piston. Yet another persisting problem concerns the balancing of moving parts to cancel out vibrations.

There is an engine/machine described in CA Patent No. 2,192,714 that deploys swing pistons. However, it has a very complex design comprising a large number of parts, which results in a higher fault rate and increased engine/machine wear. In addition, the compression ratio of combustion chamber volumes is very unfavourable. There are also problems with the friction of moving parts.

Another type of engine deploying rotary piston motion is an engine whose shaped piston moves inside a cylindrical chamber of a toroid- shaped stator as described, for instance, in CS Author's Certificate AO 195 393. The said shaped piston has one or two opposing wedge- shaped protrusions, against which sealing blades positioned asymmetrically in the stator slide. The engine's stator is divided into separate working chambers by the circular motion of the piston and reciprocating movements of sealing blades. This type of engine requires a special control mechanism to assure reliable sealing blade control. In addition, the rotor blades need to be sealed in the stator casing, for instance by radial sealing blades. These difficulties practically prevent the achievement of the required compression pressures in the described types of rotary combustion engine.

That is why a need arose to design a motor or machine with an improved technical specification, of a simple design, comprising a minimum number of parts and having an improved cylinder-piston tightness. This effort resulted in the invention as described below.

Outline of the invention To describe this invention, the terminology used in definitions and in the description of the invented method and machine needs to be explained. The following terms and the meanings set below them have been used to describe the motor/machine: 1. Rotary ring The rotary ring with a toothed outer contour in the shape of a broken spherical triangle functions in this case as a rotary piston, while a working cavity inside the ring forms the rotary piston's inner working face, unlike the rotary piston used, for instance, in the Wankel engine, where the piston's outer face is the working face. The piston's working face is to be understood as the surface that is in contact with the work medium (combustible mixture, pressure liquid or pressure gas).

2. Oval stationary element The oval stationary element of an approximately elliptical shape functions in this case as the cylinder, in terms of an analogical stator in the Wankel engine, the difference being that the inner working face of the rotary ring moves along the outer working face of the stationary element functioning as the cylinder. This arrangement creates two working chambers of complementarily changing volumes.

3. Spark or compression ignition system The spark/compression ignition system shall in this case be understood as a system of spark plugs or heater plugs including relevant combustible mixture delivery or fuel injection systems.

In terms of the above terminology, the outlined deficiencies are eliminated by the method of converting the energy of the burnt combustible mixture or pressure medium to rotary motion, or the method of converting rotary motion to the pressure medium in the crankgear-free rotary piston motor/machine. The principle of the method according to present invention is that the rotary motion is derived from the pressure of the burnt combustible mixture or pressure medium acting in the working chambers enclosed by the outer face of the oval stationary element, inner face of the rounded spherical triangle shaped working cavity and flat lateral faces of the working cavity. The movement of the inner face of the rounded spherical triangle shaped working cavity along the outer face of the oval stationary element makes the rotary ring with the toothed outer contour in the shape of a broken spherical triangle to rotate around a fluctuating axis of rotation alternately positioned in the end positions, which provides three different output axes of rotation. The first two output axes of rotation are determined by the fixed distance of the axes of two pinions mating with the toothing of the rotary ring with the toothed outer contour in the shape of a broken spherical triangle. In the reversible method of converting rotary motion to pressure medium energy, the medium pressurisation in the working chambers, enclosed by the outer face of the oval stationary element, inner face of the rounded spherical triangle shaped working cavity and flat lateral faces of the working cavity, is reciprocally derived from the first two input pinion axes through the gearing of the pinions and the rotary ring with the toothed outer contour in the shape of a broken spherical triangle. This allows the pressurised liquid or gas medium to be withdrawn from the working chamber outlet.

The possibilities of converting the burnt combustible mixture or pressure medium energy to rotary motion according to the present invention can be further extended by the utilisation of a third output/input axis of rotation that is identical to the axis of an inner gear ring compassing both pinions on their outer perimeter or of an outer gear ring mating with the pinions.

The above method of converting the burnt combustible mixture or pressure medium energy to rotary motion or rotary motion to the pressure medium in a crankgear-free rotary piston motor/machine led to the development of new types of crankgear-free rotary piston engines/machines, each of them essentially consisting of at least one oval stationary element and one rotary ring with a toothed outer contour in the shape of a broken spherical triangle. The oval stationary element is of an approximately elliptical shape and is positioned in series and/or in parallel inside a rounded spherical triangle shaped working cavity.

This working cavity is located inside the flat rotary ring with the toothed outer contour in the shape of a broken spherical triangle. At the same time, the oval stationary element and the rotary ring with the toothed outer contour in the shape of a broken spherical triangle are cinematically linked by at least two opposite pinions mating with the outer toothing of the rotary ring. At least one of these pinions can be used to supply utilisable torque to drive other driven accessories such as a vehicle transmission.

From the above description of a crankgear-free rotary piston engine/machine design according to the present invention another essential feature is clear, which is that the outer face of the oval stationary element, the inner face of the rounded spherical triangle shaped working cavity and the two flat lateral faces of the said working cavity generally create two working chambers of complementarily varying volumes. The working cavity's flat lateral faces are produced by a flange or the stationary part of the engine/machine block.

In a preferred embodiment of the present invention, the invention also relates to an arrangement where the pinions mate with the inner gear ring, compassing both pinions on their outer perimeter, or with an outer gear ring.

According to the present invention, a four-stroke spark-ignition crankgear-free rotary piston combustion engine can be constructed, whose essential feature, in combination with some of the above features, is that the working chambers of complementarily varying volumes contain synchronously controlled intake and exhaust valves or ports. The working chambers of complementarily varying volumes also contain a spark ignition system and mixture delivery and/or fuel injection system.

In the first preferred embodiment of the present invention of a four-stroke spark-ignition crankgear-free rotary piston combustion engine the invention also relates to an arrangement, wherein at least one synchronously controlled valve or port and/or at least one spark ignition system and mixture delivery and/or fuel injection system are contained in the oval stationary element.

In the second preferred embodiment of the present invention of a four-stroke spark-ignition crankgear-free rotary piston combustion engine the invention also relates to an arrangement, wherein at least one synchronously controlled valve or port and/or at least one spark ignition system and the mixture delivery system are contained in at least one flat lateral face of the working cavity produced by a flange.

According to the present invention a four-stroke compression- ignition crankgear-free rotary piston combustion engine can also be constructed, whose essential feature, in combination with some of the above features, is that the working chambers of complementarily varying volume contain synchronously controlled intake and exhaust valves, as well as a compression ignition system, including a fuel injection.

In the first preferred embodiment of the present invention of a four-stroke compression-ignition crankgear-free rotary piston combustion engine the invention also relates to an arrangement, wherein at least one synchronously controlled valve or port and/or at least one compression ignition system are contained in the oval stationary element.

In the second preferred embodiment of the present invention of a four-stroke compression-ignition crankgear-free rotary piston combustion engine the invention also relates to an arrangement, wherein at least one synchronously controlled valve or port and/or at least one compression ignition system with a fuel injection are contained in at least one flat lateral face of the working cavity produced by a flange or part of the engine body.

However, according to the present invention a two-stroke compression-ignition crankgear-free rotary piston combustion engine can also be constructed, whose essential feature, in combination with some of the above features, is that the working chambers of complementarily varying volumes are interconnected through the oval stationary element by a synchronously controlled relief check valve and contain intake and exhaust valves and ports. One working chamber always functions as an intake chamber and the other working chamber always functions as a combustion chamber, the latter containing a compression ignition system with a fuel injection fitted to the stationary element.

However, according to the present invention, a two-stroke spark- ignition crankgear-free rotary piston combustion engine can also be constructed, whose essential feature, in combination with some of the above features, is that the working chambers of complementarily varying volumes are interconnected through the oval stationary element by a synchronously controlled relief check valve and contain intake and exhaust valves and ports. One working chamber always functions as an intake chamber and the other working chamber always functions as a combustion chamber, the latter containing a spark ignition system and/or fuel delivery system fitted to the stationary element.

What is essential for the preferred embodiment of the two-stroke crankgear-free rotary piston combustion engine according to the present invention is that the synchronously controlled intake and exhaust ports are of a slot design, while the rotary ring with the toothed outer contour in the shape of a broken spherical triangle acts as the intake and exhaust port closure.

What is essential for the preferred embodiment of the four-stroke crankgear-free rotary piston combustion engine according to the present invention is that the working chambers of complementarily varying volumes contain four synchronously controlled four-stroke timed valves.

According to the present invention a crankgear-free rotary piston motor in a hydraulic motor or flowmeter converter configuration can be constructed, whose essential feature is that the working chambers of complementarily varying volumes contain synchronously controlled inlet and outlet valves or ports.

In one preferred embodiment of the crankgear-free rotary piston motor in a hydraulic motor configuration according to the present invention, the invention also relates to an arrangement, wherein at least one synchronously controlled inlet or outlet valve or port is contained in the oval stationary element.

In another preferred embodiment of the crankgear-free rotary piston motor in a hydraulic motor configuration, the present invention also relates to an arrangement, wherein at least one synchronously controlled inlet or outlet valve or port is contained in at least one of the flat lateral faces of the working cavity.

An essential feature of the present invention is the reversibility of the process of supplying torque as the input energy and withdrawing pressure medium as the output energy, the design implication of which is that a crankgear-free rotary piston machine in a liquid or gas pump configuration can be constructed based on the principle of working chambers of complementarily varying volumes being fitted with synchronously controlled inlet and outlet valves or ports for the pumped liquid or gas medium. At the same time, at least one of the pinions or the rotary ring propels, i. e. is connected to the input torque.

In one of the preferred embodiments of the crankgear-free rotary piston machine in a pump configuration according to the present invention, the invention also relates to an arrangement, wherein at least one synchronously controlled inlet or outlet valve or port is contained in the oval stationary element.

In another preferred embodiment of the crankgear-free rotary piston machine in a pump configuration according to the present invention, the invention also relates to an arrangement, wherein at least one synchronously controlled inlet or outlet valve or port is contained in at least one of the flat lateral faces of the working cavity.

The present invention of the crankgear-free rotary piston motor/machine also relates to the solution feature, wherein the rotary rings with the toothed outer contour in the shape of a broken spherical triangle are angularly displaced by 30°, which eliminates the dead centre position in the rotation of the two rotary rings.

The present invention of the crankgear-free rotary piston motor/machine also relates to the solution feature, wherein the rotary rings with the toothed outer contour in the shape of a broken spherical triangle are angularly displaced by 60°, which balances the system in terms of vibrations.

The present invention of the crankgear-free rotary piston motor/machine also relates to the solution feature, wherein the tips of the rotary rings with the toothed outer contour in the shape of a broken spherical triangle are fitted with pieces made of high strength materials, preferably sintered carbides, and/or the oval stationary element tips are fitted with combined sprung sealing blades.

The present invention also relates to the solution featuring two or more combined sprung sealing blades positioned in parallel or in series within the slot in the oval stationary element, the sealing blades being pushed off the slot bottom by a corrugated spring wire.

The present invention also relates to the actual utilisation of the crankgear-free rotary piston motor for propelling a helicopter.

The present invention also relates to the actual utilisation of the crankgear-free rotary piston motor for propelling a transport vehicle or craft.

The present invention also relates to the actual utilisation of the crankgear-free rotary piston motor for propelling a stationary machine.

The present invention also relates to the utilisation of the crankgear-free rotary piston motor as a hydraulic motor.

The present invention also relates to the utilisation of the crankgear-free rotary piston motor as a pump for pumping fluids.

The present invention also relates to the utilisation of the crankgear-free rotary piston motor as a compressor.

Finally, the present invention also relates to the utilisation of the crankgear-free rotary piston motor as a flowmeter converter.

Advantages of the energy conversion in the rotary piston motor/machine according to the described invention arise especially from the fact that one design is universal for spark-ignition and compression-ignition engines, four-stroke and two-stroke engines, hydraulic motors or flowmeter converters. The method of energy conversion is also reversible for machines in the pump configuration for pumping liquid or gas pressure media where torque is supplied on the inlet and work is withdrawn at the outlet.

The advantages of a crankgear-free rotary piston motor/machine designed on the basis of the method of converting the energy of the burnt combustible mixture or pressure medium to rotary motion or the method of converting rotary motion to the pressure medium according to this invention arise, as the invention name suggests, especially from the fact that the motor or machine is of a simple crankgear-free design and comprises a limited number of moving parts, The motor/machine design provides for a high power-to-weight ratio. The design also improves waste heat dissipation and allows progressive ceramic and high-strength construction materials to be used, which permits combustion engine applications to run at higher temperatures and therefore with higher efficiency. It is also easier to seal the work chambers. Using two or more rotary rings functioning as rotary pistons, angularly displaced by 60° and restrained to identical pinions, balances the entire system in terms of vibrations as they are cancelled out. The 30° angular displacement of the two rotary rings in the hydraulic motor or flowmeter converter application eliminates the dead centre position in the rotation of the two rotary rings without a flywheel. Smooth motor operation with minimum flywheel weight requirements is achieved by at least three to six working strokes per one revolution of the rotary ring.

Advantages of the engines according to this invention will show themselves especially in the automotive industry. Not only does the engine design allow a transmission unit to be connected to it by a conventional flange connection, but its limited size also allows the engine to be mounted to some alternative positions not suitable for conventional piston motors. For instance an engine designed according to the present invention can be located under the rear seats, which would allow for more boot space both at the front and rear of the car.

This concept has favourable effects on the passive safety elements of such a vehicle, as the boot spaces function as vehicle crusher zones absorbing kinetic energy in the case of a crash. Considering the advantageous car weight distribution and gravity centre positioning, the vehicle's performance should also improve. These aspects can have a substantial impact on vehicle design concepts in the future. In the spark or compression ignition engine, in two-stroke or four-stroke combustion chamber operation, the synchronous timing of the intake and exhaust valve opening, combustible mixture ignition or fuel injection are derived either directly from the motion of the rotary ring/rings, overpressure or underpressure, or from the pivot speed, as the number of the pivot's teeth is a suitable whole dividend of the number of the rotary ring's teeth. Such combustion engines can be conveniently utilised in the aviation industry to drive propelled aircraft. The engine can also be used to propel a helicopter, wherein the main uplift rotor propulsion is derived from the inner or outer gear ring and the stabilizing rear rotor propulsion is derived from one of the pinions. Pressure pump applications for a liquid or gas medium according to the present invention deliver an extra steady flow, where any equal angle of rotation of the rotary ring corresponds to an equal volume of pumped medium.

Description of the drawings The method of converting the burnt combustible mixture or pressure medium energy to rotary motion or the method of converting rotary motion to the pressure medium, as well as the actual crankgear- free rotary piston motorlmachine according to the present invention shall be explained in greater detail by describing the drawings. Fig. 1 shows the operating principle of the present invention. Fig. 2 shows the front and side views of a simple motorlmachine assembly according to the present invention. The valve operating gear and spark or compression ignition systems are not shown. Fig. 3 shows the <BR> <BR> synchronousty contro ! ! ed vaive operating gear and ignition system arrangements. Fig. 4 shows the valve timing of a spark or compression ignition system in a two-stroke combustion engine application. Fig. 5 shows the valve timing of a spark or compression ignition system in a four-stroke combustion engine application. Fig. 6 shows the valve timing for a hydraulic motor or pump application. Fig. 7 shows the dead zone compensation in a hydraulic motor or flowmeter converter application using two rotary rings as rotary pistons. Fig. 8 shows the vibration compensation using a 60° angular displacement of two rotary rings. Fig. 9 shows the intake and exhaust port design in a two-stroke engine configuration. Fig. 10 shows the longitudinal and cross sections of the engine/machine's extended assembly, Fig. 11 shows the combined sealing blade design. Fig. 12 shows the principle of linking two motors/machines according to the present invention in parallel by two pinions. Fig. 13 shows the principle of linking two motors/machines according to the present invention in parallel by three pinions. Fig. 14 shows a detailed linkage of two two-stroke motors/machines according to the present invention in parallel by three pinions. Fig. 15 shows a detailed linkage of motor/machine, the third output axis of rotation is led out through the centre of one of the stationary elements. Fig. 16 shows a detailed linkage of motorlmachine, the third output axis of rotation is led out through the centre of both stationary elements.

Examples of the invention's embodiments Example 1 This example of the practical embodiment of the present invention describes the basic principle of the conversion of burnt combustible mixture energy to rotary motion, where the output rotary motion is derived from the pressure of the burnt combustible mixture acting in the working chambers 7, 8 of complementarily varying volumes, the chambers being enclosed by the outer face of the oval stationary element 1, and the inner face of the rounded spherical triangle shaped working cavity 13 as shown in Fig. 1.

The movement of the inner face of the rounded spherical triangle shaped working cavity _ along the outer face of the oval stationary element 1 makes the rotary ring with the toothed outer contour in the shape of a broken spherical triangle 2 rotate around a fluctuating axis of rotation alternately positioned in the end positions 4, 5, which provides three output axes of rotation. The first two output axes of rotation are determined by the fixed distance of the axes of the two pinions 11 mating with the toothing of the rotary ring with the toothed outer contour in the shape of a broken spherical triangle 2 Example 2 This example of the practical embodiment of the present invention describes the first derived method of converting liquid or gas pressure medium energy to rotary motion, where the output rotary motion is derived from the medium pressure acting in the working chambers 7,8 enclosed by the outer face of the oval stationary element 1, the inner face of the rounded spherical triangle shaped working cavity 13 and the lateral faces of the said working cavity 13. The motion of the inner face of the rounded spherical triangle shaped working cavity 13 along the outer face of the oval stationary element 1 makes the rotary ring with the toothed outer contour in the shape of a broken spherical triangle 2 rotate around a fluctuating axis of rotation alternately positioned in the end positions. This arrangement provides three output axes of rotation.

The first two output axes of rotation are determined by the fixed distance of the axes of the two pinions 11 mating with the toothing of the rotary ring with the outer contour in the shape of a broken spherical triangle 2.

Example 3 This example of the practical embodiment of the present invention describes the second derived method of converting rotary motion to a liquid or gas pressure medium. In this reversible process the rotary motion to pressure medium conversion is derived from the first two input axes of rotation. The said conversion takes place through the first two axes of rotation, determined by the fixed distance of the pinions 11 mating with the toothing of the rotary ring with the toothed outer contour in the shape of a broken spherical triangle 2, making the said rotating ring 2 with the rounded spherical triangle shaped working cavity 13 rotate around the fluctuating axis of rotation alternately positioned in the end positions 4,5. This results in the compression and displacement of the liquid or gas medium in the said working chambers 7 8 enclosed by the outer face of the oval stationary element 1 and the inner face of the rounded spherical triangle shaped working cavity 13.

Example 4 This example of the practical embodiment of the present invention describes the third derived method of converting burnt combustible mixture energy or pressure medium energy to rotary motion or the reversible method of converting rotary motion to a pressure medium, wherein the third output/input axis of rotation is identical to the axis of rotation of the inner gear ring 10 compassing both pinions 11 on their outer perimeter, or the third output/input axis of rotation is identical to the centre of rotation of the outer gear ring 10 geared with the pinions 11.

Example 5 This example of the practical embodiment of the present invention describes the basic design of a spark-ignition four-stroke crankgear- free rotary piston combustion engine as shown in Fig. 2. It comprises one oval stationary element 1 and one rotary ring with a toothed outer contour in the shape of a broken spherical triangle 2. The oval stationary element 1 is located inside the rounded spherical triangle shaped working cavity 13 as shown in Fig. 1. The said working cavity 13 is located inside the rotary ring with the toothed outer contour in the shape of a broken spherical triangle 2. The oval stationary element 1 and the rotary ring with the toothed outer contour in the shape of a broken spherical triangle 2 are cinematically linked by a pair of pinions 117 from which the torque is withdrawn. The outer face of the oval stationary element 1, the inner face of the rounded spherical triangle shaped working cavity 13 and the two lateral planes 6 of the working cavity 13. which are produced by two flanges, create two working chambers 7, 8 of complementarily varying volumes. The said working chambers 7, 8 of complementarily varying volumes contain synchronously controlled valves 9, shown as V17 V2. V3, V4, or ports, while the oval stationary eiement 1 is fitted with a spark ignition system 14 including mixture delivery, as shown in Fig. 3.

In another variant embodiment of the present invention the spark ignition system 14 comprises a fuel injection system Example 6 This example of the practical embodiment of the present invention describes the basic design of a two-stroke compression-ignition crankgear-free rotary piston combustion engine, which is based on the previous example. The difference between the two designs is that the oval stationary element I comprises a synchronously controlled relief check valve 9, shown as V5 in Fig. 3. What is also essential for the preferred embodiment of the rotary piston engine is that the synchronously controlled intake and exhaust ports 9 as shown in Fig. 3 are of a slot design as shown in detail in Fig, 9. At the same time, the rotary ring with the toothed outer contour in the shape of à broken spherical triangle 2 acts as the intake and exhaust port closure.

Example 7 This example of the practical embodiment of the present invention describes the basic design of a compression-ignition crankgear-free rotary piston combustion engine as shown in Fig. 2. It comprises one oval stationary element 1 and one rotary ring with a toothed outer contour in the shape of a broken spherical triangle 2. The oval stationary element 1 is located inside the rounded spherical triangle shaped working cavity 13 as shown in Fig. 1. The said working cavity 13 is located inside the rotary ring with the toothed outer contour in the shape of a broken spherical triangle 2.

The oval stationary element 1 and the rotary ring with the toothed outer contour in the shape of a broken spherical triangle 2 are cinematically linked by a pair of pinions 11. The outer face of the oval stationary element 1, the inner face of the rounded spherical triangle shaped working cavity 13 and the two flat lateral faces of the working cavity 13, which are produced by the flange 6, create two working chambers 7, 8 of complementarily varying volumes. The working chambers 7, 8 of complementarily varying volumes contain synchronously controlled valves 9, shown as V1, V2, V3, V4, or ports, while the oval stationary element 1 is fitted with a compression ignition system 14 including a fuel injection system as shown in Fig. 3.

Example 8 This example of the practical embodiment of the present invention describes the first extended design of a two-stroke compression-ignition crankgear-free rotary piston combustion engine based on Example 7, the design being supplemented with a cinematic link of the two pinions 11 geared with the outer toothing 12 of the rotary ring 2 as shown in Fig. 2. At the same time, the pinions 11 are compassed on their outer perimeter by the inner gear ring 10. What is especially advantageous for higher power engines is that the tips of the rotary ring with the toothed outer contour in the shape of a broken spherical triangle 2 are fitted with pieces 15 made of high-strength materials, in this case sintered carbides, as these areas are extremely stressed as shown in Fig. 8. The tips of the oval stationary element 1 are fitted with combined sprung sealing blades 16 to improve the tightness of the combustion or pressure chambers as shown in Fig. 11.

The first variant invention embodiment of the four-stroke compression-ignition crankgear-free rotary piston combustion engine is a combination of Examples 7 and 8.

The second variant invention embodiment of the four-stroke spark-ignition crankgear-free rotary piston combustion engine is based on Example 5. Its design is supplemented with a cinematic link of the two pinions 11 that mate with the outer toothing 12 of the rotary ring 2 as shown in Fig. 2. At the same time, both pinions 11 are compassed on their outer perimeter by the inner gear ring 10. The tips of the oval stationary element 1 are fitted with combined sprung sealing blades 16 to improve the tightness of the combustion or pressure chambers. There are three combined sprung sealing blades 16 fitted side-by-side to the slot in the oval stationary element 1. The blades are pushed off the slot bottom by a corrugated spring wire 17 as shown in Fig. 11.

The third variant invention embodiment of the two-stroke spark- ignition crankgear-free rotary piston combustion engine is a combination of Examples 5 and 8.

In all three variant embodiments of the present invention, as well as in the basic embodiment as described in Example 8, the engine can be made either exclusively of metal or a combination of metal and ceramic materials. If it is made of metal, the rotary ring 2 that is in contact with the lateral faces 6, in this case produced by flanges, is fitted with sealing segments 18 as shown in Fig. 10.

If ceramic materials are used in the engine, the sealing segments 18 may be omitted.

In all three variant embodiments of the present invention, as well as in the basic embodiment as described in Example 8, an outer gear ring 10 geared with pinions 11 may be used as the third axis of rotation.

Example 9 This example of the practical embodiment of the present invention describes the second extended design of a two-stroke or four-stroke compression-ignition or spark-ignition crankgear-free rotary piston combustion engine as described in Example 8 and its variants, the difference being the multiple arrangement of the system comprising two oval stationary elements 1 and two rotary rings with toothed outer contours in the shape of broken spherical triangles 2 as shown schematically in Fig 8 and in detail in Fig. 10. The rotary rings with toothed outer contours in the shape of broken spherical triangles 2 are angularly displaced by 604.

The functioning of the two-stroke spark/compression-ignition crankgear-free rotary piston combustible engine as described in Examples 6 to 9 is apparent from Figs. 3 and 4, where one active stroke corresponds to a 120° turn of the rotary ring 2 functioning as the rotary piston. When the rotary ring 2 is in its first position, all three synchronously controlled valves 9 are closed. These are the intake valve V1, exhaust valve V3 and relief check valve V5. The first working chamber 7 enters the underpressure (intake) phase while the second working chamber 8 enters the compression phase. The spark/compression ignition system 14 is passive. As the rotary ring 2 turns to its second position, the intake valve V1 opens for a moment, while the exhaust valve V3 and the relief check valve V5 remain closed.

Consequently, the first working chamber 7 starts to take in the combustible mixture or air, while the compressed combustible mixture in the second working chamber 8 is ignited by activating the spark/compression ignition system 14. As the rotary ring 2 continues to turn to the third position, the intake valve V1 closes, while the exhaust valve V3 and the relief check valve V5 remain closed. Consequently, the first working chamber 7 enters the phase of compressing the combustible mixture or air, while the ignited combustible mixture explodes in the second working chamber 8. The spark/compression ignition system 14 is passive. As the rotary ring 2 continues to turn to the fourth position, only the intake valve V1 remains closed. The exhaust valve V3 opens for a moment and subsequently also the relief check valve V5. Consequently, exhaust gases are discharged from the second working chamber 8 and then the compressed combustible mixture or air moves from the first working chamber 7 to the second working chamber 8 flushing the chamber in the process. The spark/compression ignition system 14 is passive. As the rotary ring 2 continues to turn, the process starts all over again, making the engine complete three strokes per one 360° turn of the rotary ring 2.

The functioning of the four-stroke spark/compression-ignition crankgear-free rotary piston combustible engine as described in Example 5 or Examples 7,8 and 9 is apparent from Figs. 3 and 5, where two active strokes correspond to a 240° turn of the rotary ring 2 functioning as the rotary piston. When the rotary ring 2 is in its first position, two synchronously controlled valves 9 are open. These are the intake valve V1 in the first working chamber 7 and the exhaust valve V3 in the second working chamber 8. The exhaust valve V2 in the first working chamber 7 and the intake valve V4 in the second working chamber 8 are closed. The spark/compression ignition system 14 is passive. The first working chamber 7 is in the phase of taking in the combustible mixture or air, while the second working chamber 8 is in the phase of exhausting combustion products. When the rotary ring 2 turns to its second position, the intake valve V1 in the first working chamber 7 and the exhaust valve V3 in the second working chamber 8 close after a moment. The exhaust valve V2 in the first working chamber 7 remains closed. After a moment the intake valve V4 in the second working chamber 8 opens. The spark/compression ignition system 14 is passive.

As the rotary ring 2 turns to its third position, the intake valve V1 in the first working chamber 7, the exhaust valve V3 in the second working chamber 8 and the exhaust valve V2 in the first working chamber 7 are all closed. Only the intake valve V4 in the second working chamber 8 is open. The first working chamber 7 enters the phase of compressing the combustible mixture or air, while the second working chamber 8 starts to take in the combustible mixture or air. The spark/compression ignition system 14 is passive. As the rotary ring 2 turns to its fourth position, the intake valve V1 in the first working chamber 7, the exhaust valve V3 in the second working chamber 8 and the exhaust valve V2 in the first working chamber 7 all remain closed.

Only the intake valve V4 in the second working chamber 8 is kept open for a moment. The first working chamber 7 enters the phase of spark/compression ignition of the combustible mixture. The spark/compression ignition system 14 in the second working chamber 8 is passive. As the rotary ring 2 turns to its fifth position, the intake valve V1 in the first working chamber 7, the exhaust valve V2 in the first working chamber 7, the exhaust valve V3 in the second working chamber 8 and the intake valve V4 in the second working chamber 8 all remain closed. The first working chamber 7 enters the phase of ignited combustible mixture explosion, its spark/compression ignition system being passive. The second working chamber 8 enters the phase of combustible mixture compression, its spark/compression ignition system being passive. As the rotary ring 2 turns to its sixth position, the intake valve V1 in the first working chamber 7, the exhaust valve V3 in the second working chamber 8 and the intake valve V4 in the second working chamber 8 remain closed. After a moment the exhaust valve V2 in the first working chamber 7 opens. The spark/compression ignition system 14 in the first working chamber 7 is passive. The spark/compression ignition system 14 in the second working chamber 8 is active, i. e. the ignition takes place. As the rotary ring 2 turns to its seventh position, the intake valve V1 in the first working chamber 7, the exhaust valve V3 in the second working chamber 8 and the intake valve V4 in the second working chamber 8 remain closed. The exhaust valve V2 in the first working chamber 7 remains open. The spark/compression ignition system 14 in the first and second working chambers 7, 8 are passive. The first working chamber 7 enters the phase of exhausting combustion products. The combustible mixture explodes in the second working chamber 8. Shortly after the rotary ring 2 turns to its eighth position, the intake valve V1 in the first working chamber 7 and the exhaust valve V3 in the second working chamber open. The intake valve V4 in the second working chamber 8 remains closed. After a moment the exhaust valve V2 in the first working chamber 7 also closes. The spark/compression ignition systems 14 in the first and second working chambers 7,8 are passive. Finally, as the rotary ring 2 turns to its ninth and final position, the intake valve V1 in the first working chamber 7 and the exhaust valve V3 in the second working chamber 8 remain open. The intake valve V4 in the second working chamber 8 and the exhaust valve V2 in the first working chamber 7 remain closed. The first working chamber 7 is in the phase of taking in the combustible mixture or air, while the second working chamber 8 is in the phase of exhausting combustion products. Hereby the cycle is complete and starts all over again.

Example 10 This example of the practical embodiment of the present invention describes the basic design of a crankgear-free rotary piston hydraulic motor as shown in Fig. 2. It comprises one oval stationary element 1 and one rotary ring with a toothed outer contour in the shape of a broken spherical triangle 2. The oval stationary element 1 is located inside a rounded spherical triangle shaped working cavity 13 as shown in Fig. 1. The said working cavity 13 is located inside the rotary ring with the toothed outer contour in the shape of a broken spherical triangle 2. The oval stationary element 1 and the rotary ring with the toothed outer contour in the shape of a broken spherical triangle 2 are cinematically linked by a pair of pinions 11 supplying the desired torque. The outer face of the oval stationary element 1, the inner face of the rounded spherical triangle shaped working cavity 13 and the two lateral sides 6 produced by flanges create two working chambers 7, 8 of complementarily varying volumes. The said working chambers 7, 8 of complementarily varying volumes contain synchronously controlled inlet and outlet valves 9 as shown in Fig. 3.

As a variant embodiment of this Example, a flowmeter converter can be built using the technical features and systems described in this Example.

In two other variant embodiments of this Example, a different hydraulic motor or flowmeter converter can be built using the technical features and systems described above, the difference being that one flat lateral face 6 of the working cavity 13 can be formed by the front part of the hydraulic motor's or flowmeter converter's body.

Example 11 This example of the practical embodiment of the present invention describes the first extended design of a crankgear-free rotary piston hydraulic motor as described in Example 10 supplemented with a cinematic linkage of the two pinions 11 mating with the outer toothing 12 of the rotary ring 2 as shown in Fig. 2.

In its variant embodiment it is possible to build a flowmeter converter using said technical features and systems.

Example 12 This example of the practical embodiment of the present invention describes an extended design of a crankgear-free rotary piston hydraulic motor as described in Examples 10 or 11 in the multiple arrangement of the system comprising two oval stationary elements 1 and two rotary rings with toothed outer contours in the shape of broken spherical triangles 2 as schematically shown in Fig 7. Said rotary rings with toothed outer contours in the shape of broken spherical triangles 2 are angularly displaced by 30°.

As a variant embodiment of this Example, a flowmeter converter can be built using the technical features and systems as described in this Example.

Example 13 This example of the practical embodiment of the present invention describes the basic design of a crankgear-free rotary piston machine in a pump configuration for pumping a liquid or gas medium, as shown in Fig. 10. It comprises one oval stationary element 1 and one rotary ring with a toothed outer contour in the shape of a broken spherical triangle 2. The oval stationary element 1 is located inside the rounded spherical triangle shaped working cavity 13 as shown in Fig. 9. The said working cavity 13 is located inside the rotary ring with the toothed outer contour in the shape of a broken spherical triangle 2. The oval stationary element 1 and the rotary ring with the toothed outer contour in the shape of a broken spherical triangle 2 are cinematically linked by a pair of pinions 11. In this case the pinions 11 function as pump propulsion elements. The pinions 11 are connected to an external source of torque. The outer face of the oval stationary element 1, the inner face of the rounded spherical triangle shaped working cavity 13 and the two lateral flanges 6 create two working chambers 7, 8 of complementarily varying volumes. The working chambers 7, 8 of complementarily varying volumes contain synchronously controlled inlet and outlet valves 9 as shown in Fig. 3.

Example 14 This example of the practical embodiment of the present invention describes the first derived design of a crankgear-free rotary piston machine in a pump configuration for pumping a liquid or gas medium, as shown in Fig. 2. Its design is derived from Example 13 and supplemented by a cinematic link of the two pinions 11 mating with the outer toothing of the rotary ring 2.

In a variant embodiment of the present invention as described in this example, the pump may deploy an outer gear ring 10 geared with pinions 11 as the third axis of rotation.

The functioning of the crankgear-free rotary piston hydraulic motor or machine as described in Examples 10 to 12 or 13 to 14 is apparent from Fig. 6, where two active strokes correspond to a 120° turn of the rotary ring 2 functioning as a rotary piston. When the rotary ring 2 is in its first position, two synchronously controlled valves 9 are open. These are the inlet valve V1 in the first working chamber 7 and the outlet valve V3 in the second working chamber 8. The outlet valve V2 in the first working chamber 7 and the inlet valve V4 in the second working chamber 8 are closed. The first working chamber 7 is filled with a liquid or gas pressure medium. Subsequently, the second working chamber 8 discharges the liquid or gas pressure medium. As the rotary ring 2 turns to its second position, the inlet valve Vl in the first working chamber 7 and the outlet valve V3 in the second working chamber 8 remain open for a moment and then close. The outlet valve V2 in the first working chamber 7 and the inlet valve V4 in the second working chamber 8 remain closed for a moment and then open. As the rotary ring 2 turns to its third position, the inlet valve Vl in the first working chamber 7 and the outlet valve V3 in the second working chamber 8 remain closed. The outlet valve V2 in the first working chamber 7 and the inlet valve V4 in the second working chamber 8 remain open. The first working chamber 7 discharges the liquid or gas pressure medium.

Subsequently, the second working chamber 8 takes in the liquid or gas pressure medium. As the rotary ring 2 turns to its fourth position, the inlet valve V1 in the first working chamber 7 and the outlet valve V3 in the second working chamber 8 remain closed for a moment and then open. The outlet valve V2 in the first working chamber 7 and the inlet valve V4 in the second working chamber 8 remain open for a moment and then close. Finally, as the rotary ring 2 turns to its fifth position, two synchronously controlled valves 9 open again. These are the inlet valve V1 in the first working chamber 7 and the outlet valve V3 in the second working chamber 8. The outlet valve V2 in the first working chamber 7 and the inlet valve V4 in the second working chamber 8 remain closed. The first working chamber 7 takes in the liquid or gas pressure medium. Subsequently, the second working chamber 8 discharges the liquid or gas pressure medium and the process starts all over again.

Example 15 This example of the practical embodiment of the present invention describes a set of rotary motors/machines according to the present invention connected in parallel as shown in Fig. 12. Two rotary rings 2 mate with one another, while at their opposite sides the two rotary rings mate with pinions 11. The disadvantage of such an embodiment is that it does not compensate for vibrations.

Example 16 This example of the practical embodiment of the present invention describes a set of rotary motors/machines according to the present invention connected in parallel as shown in Figs. 13 and 14. Rotary rings 2 always mate with pinions 11. The set comprises two rotary rings 2 and three pinions 11. This embodiment does compensate for vibrations.

Example 17 This embodiment of the present invention describes a rotary piston motor with an outer gear ring 10 geared with pinions 11, the outer gear ring being arranged between two neighbouring rotary rings 2 and two stationary elements 1, so that it creates a flat face 6 dividing two neighbouring working cavities 13. The third output axis of rotation is led out through the centre of one of the stationary elements 1 as shown in Fig. 15.

Example 18 This embodiment of the present invention describes a rotary piston motor with an outer gear ring 10 geared with pinions 11, the outer gear ring being being arranged between two neighbouring rotary rings 2 and two stationary elements 1 ; so that it creates a flat face 6 dividing two neighbouring working cavities 13. The third output axis of rotation is led out through the centre of both stationary elements 1 as shown in Fig. 16.

Example 19 This embodiment of the present invention describes a rotary piston machine with an outer gear ring 10 geared with pinions 11, the outer gear ring being arranged between two neighbouring rotary tings 2 and two stationary elements 1 so that it creates a flat face 6 dividing two neighbouring working cavities 13. The third output axis of rotation is led out through the centre of one of the stationary elements 1 as shown in Fig. 15.

Example 20 This embodiment of the present invention describes a rotary piston machine with an outer gear ring 10 geared with pinions 11, the outer gear ring being arranged between two neighbouring rotary rings 2 and two stationary elements 1 so that it creates a flat face 6 dividing two neighbouring working cavities 13. The third output axis of rotation is led out through the centre of both stationary elements 1 as shown in Fig. 16.

Example 21 This embodiment of the present invention describes the use of the rotary piston motor in stationary installations such as stationary power generators.

Example 22 This embodiment of the present invention describes the use of the rotary piston motor in hand tools such as chainsaws, lawn mowers and compactors.

Example 23 This embodiment of the present invention describes the utilisation of the rotary piston motor/machine in airplanes, air-cushion vehicles, farming machines, construction machines, logging machines, mining machines, exploitation machines, freight transport vehicles and crafts, passenger vehicles and crafts, ships and snowmobiles.

Industrial applicability The method of converting a burnt combustible mixture or pressure medium energy to rotary motion or a method of converting rotary motion to a pressure medium can be applied in new designs of crankgear-free rotary piston motors or machines. The combustion engines according to the present invention can especially be used in the automotive industry.

A promising future may be anticipated with regard to their application in the aerial industry for propelling aircraft and helicopters. However, the combustion engines according to the present invention could also be applied in rail and waterway transport, farming machines, snowmobiles, stationary backup power sources and other similar applications. The present invention can also be used as a displacement machine in a hydraulic motor configuration. The rotary machine configuration according to the present invention can be utilised in liquid medium pressure pumps and flowmeter converters.