NO327338B1 - Rotary machine - Google Patents

Abstract

The present invention relates to a rotary machine which can be used in various applications such as an internal combustion engine or compressor. Furthermore, the invention relates to an assembly of two or more rotary machines and an internal combustion engine based on the rotary machine. The machine is mainly formed by a helical helical rotor connected to an output shaft pin, which helical rotor rotates in a cylindrical housing. The machine is further provided with rotating chamber sub-bodies whose rotation is synchronized with the rotating helical rotor. The chamber divider bodies divide the helical screw grooves into chambers whose volume varies with rotation of the helical rotor.

Description

The present invention relates to a rotary machine which can be used in various applications such as an internal combustion engine or a compressor. Furthermore, the invention relates to an assembly of two or more rotary machines and an internal combustion engine based on the rotary machine. The machine is mainly formed by a helical screw-shaped rotor connected to an output shaft pin, which screw-shaped rotor rotates in a cylindrical housing. The machine is further provided with rotating chamber parts whose rotation is synchronized with the rotating screw-shaped rotor. The chamber dividing bodies divide the helical screw grooves into chambers whose volume varies with rotation of the helical rotor.

Various forms of compressors and internal combustion engines have previously been known. Screw compressors are previously generally known with screw-shaped rotors.

Combustion engines are known within rotating machines as engines based on the so-called Wankel principle, where an eccentrically rotating rotor forms chambers in a housing and where gas exchange and combustion take place in one or more of the formed chambers.

However, it is known that existing internal combustion engines are not very efficient and that they, among other things, has a large rotating mass, i.e. there is a large mass in the rotating parts. Furthermore, the gas exchange in traditional combustion engines is often poor, which means that the supply of oxygen through supplied air is not necessarily optimal and the removal of burnt gases is not optimal either. In addition, the actual utilization of power in a traditional piston engine is not optimal as a linear movement is created in a piston in a cylinder and this linear movement must further be transferred to rotary movement which occurs in a sinusoidal transmission where the torque increases from low (nearly zero) towards maximum and then again decrease to nearly zero. Traditional piston engines are also critical in relation to the unbalancing of rotating mass, as there is a transfer from linear to rotary motion continuously in the engine.

It is a purpose of the present invention to produce a rotary machine which in various applications can be used both as a compressor and as an internal combustion engine in that the technical core of the present invention will be included in various embodiments in these applications. The purpose is also to produce a rotary machine that has better properties than previously known solutions. In connection with the particular application of the rotary machine according to the present invention as an internal combustion engine, a number of the above disadvantages with balancing, gas exchange and power transmission to the output shaft can be improved.

Of known solutions, reference should be made to GB 2 131 877, which describes a worm gearbox with a helical screw and two drives. The solution can be used in a compressor or pump by forming cells that carry fluid.

Furthermore, GB923,042 describes a compressor built according to the same principle as in GB 2,131,877. Furthermore, EP 517,250 also describes a screw compressor similar to the above-mentioned solutions.

According to the present invention, a rotary machine has been produced on this basis, essentially including a screw shaft with one or more helical screw grooves, which screw shaft is designed at least at one end in the longitudinal direction of the screw shaft for connection with a motor or a drive mechanism. The rotary machine is characterized by: - the screw shaft is rotatably placed in a housing with an internal cylindrical shape where the internal diameter of the housing is essentially the same as the outer diameter of the screw shaft, which housing is essentially closed at each of the ends of the screw shaft with a through opening for the screw shaft's connection with motor or drive mechanism and which housing includes storage for the screw shaft, - the helically shaped screw grooves extend in a helical form from one end of the screw shaft to the opposite end of the screw shaft, - the rotary machine includes one or more rotatingly arranged chamber part bodies which chamber part bodies are each designed as a substantially circular body with a center of rotation, which chamber divider bodies each have a number of triangular shaped chamber divider blades projecting from the center of the chamber divider body with the narrowest end at the center of the chamber divider body, which chamber divider blades are spaced apart and which chamber divider bodies are root is located at the outer edge of the screw shaft with an axis of rotation extending substantially perpendicular to the axis of rotation of the screw shaft and where the rotation of each of the cam parts bodies is synchronized with the rotation of the screw shaft, so that the cam parts blades on the cam parts bodies protrude into the helical screw grooves in the screw shaft and follow the movement of the screw track when the screw shaft rotates so that a chamber divider blade on a chamber divider body follows a helical track and separates the helical groove into a chamber on each side of the chamber divider body upon rotation of the screw shaft, which chambers have varying volumes as the screw shaft rotates as the total volume of the helical groove is bisected by the chamber divider body and after each time the screw shaft rotates, the volume on each side of the chamber dividing body will change between essentially 0 and 100% and the two chambers together at any time form a total volume substantially equal to the volume of the helical screw groove and - that at least one inlet opening is provided in the housing t to the interior of the cylindrical housing into the helical screw groove at one end of the cylindrical housing and at least one outlet opening in the housing to the interior of the cylindrical housing into the helical screw groove at one end of the cylindrical housing.

If chamber parts are placed on opposite sides of the screw shaft's longitudinal direction, these chamber parts must be counter-rotating.

The number of helical grooves in the screw shaft can in various embodiments be equal to the number of chamber dividing blades on the chamber dividing bodies, but it can also be different.

In order to achieve a good seal between the chamber divider bodies and the helical screw groove so that each helical screw groove is divided into different chambers by the chamber divider body, the profile of each chamber divider blade is preferably designed to complement the internal shape of the helical screw groove. The chamber divider body can be flat on its upper side and slightly conical with curved surfaces on its underside so that the shape is complementary to the screw groove and so that sealing is achieved with the screw groove when a chamber divider blade moves into the screw groove and follows this while both the screw shaft and the chamber divider body rotate.

The chamber dividing bodies can have a number of different shapes and can in one embodiment be a flat disk or plate. The chamber dividing bodies can also have a flat upper side and a curved or pyramidal lower side or they can be more spherical. As long as the chamber dividing body or at least each chamber dividing blade has a shape that is complementary to the interior of the helical groove, then the chamber dividing bodies and/or the chamber dividing blades can otherwise be designed so that they are appropriate in relation to heat development, pressure conditions, storage etc.

The cylindrical housing in which the screw shaft moves has an internal cylindrical shape and can externally have any shape and can thereby form part of a larger construction. Several rotary machines according to the invention can of course be placed side by side or above each other or in some other way. In some embodiments, several housings can also be arranged so that two housings also share a chamber dividing body, i.e. the chamber dividing body protrudes into two helical grooves with different chamber dividing blades at the same time. In such designs, the rotation of each screw shaft must be synchronized with each other and with the chamber dividing body.

The screw shaft is suitable for transporting and possibly compressing a fluid such as a liquid or gas. In order for the fluid to enter the helical groove in the rotary machine, there is therefore an inlet opening through the housing towards the screw shaft. The inlet opening is preferably located on the side of the screw where the chamber dividing body moves into the helical screw groove so that when the screw and the chamber dividing body rotate, a chamber is formed where the volume expands and the fluid is thereby drawn into the chamber. When the screw shaft has moved so that the chamber blade has followed the helical groove to the end, the valve surface leaves the helical groove and the chamber is filled with fluid. Furthermore, the next valve face will enter the helical groove as the screw shaft continues to rotate and will push the fluid content of the helical groove forward in the groove after the chamber part blade moves along the helical groove and forms a chamber which has a reducing volume. If the end of the chamber is closed, the chamber dividing blade will compress the fluid against the closed surface. In the opposite case, the movement of the chamber dividing body will be able to push the fluid out of the chamber that is formed on the upper side (the pushing side) of the chamber dividing body. As the screw shaft rotates, the reducing volume chamber will meet an outlet opening from the cylindrical housing and from the helical screw track, as indicated above, and pressurized fluid will flow out. The completion of this "emptying" of the chamber occurs when the chamber parting blade leaves the helical groove and the screw shaft continues to rotate with an empty groove. Whether a compression is to be created or only a "movement" of fluid through the helical groove is thereby determined by the location of an outlet opening and the shape of the outlet opening. If the opening is an elongated slit that is open to the chamber with reducing volume, then the fluid in the chamber will constantly be pushed out. If the opening is small in area and is placed in such a way in the cylindrical housing that the opening is only uncovered when the chamber dividing body has passed almost through the entire helical groove, then a pressure will be formed in the chamber of the helical groove which has reducing volume and it will be pressurized fluid flowing out of the outlet opening.

In one embodiment, a through-flow opening can therefore have a length in the direction of rotation corresponding to all or part of the angle of rotation over which the helical groove in the screw shaft extends.

If the pressurized fluid is to make several passes through the screw shaft, for example for combustion of pressurized fluid and expansion, then the fluid must be transferred from one side of the cylindrical housing to the opposite side of the cylindrical housing in the longitudinal direction, as the chamber parts are counter-rotating and the screw only rotates one way. This can happen in a channel or pipe connection between one end of the house and the opposite end of the house.

In one embodiment of the invention, the helical groove of the screw shaft is therefore formed at one or both of its ends in the longitudinal direction with a sealing closure, which sealing closure is formed with a through-flow opening that coincides with the inlet and/or outlet opening in the cylindrical housing. Furthermore, the helical groove of the screw shaft can at one or both of its ends in the longitudinal direction be formed with sealing ends, which sealing ends are each formed with one or more flow-through openings, of which one of the flow-through openings coincides with an inlet and/or outlet opening in the cylindrical housing and a of the flow openings at one end of the cylindrical housing communicates with a flow opening at the other end of the cylindrical housing outside the inner cylindrical space.

In order to further facilitate the fluid flow and to be able to use several grooves in the screw shaft at the same time, in one embodiment, at one of or at each end of the cylindrical housing in the longitudinal direction, one or more chambers are formed, each of which is connected to the cylindrical housing through a

gj through-flow opening.

A rotary machine as stated above can, for example, be used as a compressor in one or more stages. In such an application, non-return valves can be used in connection with the flow openings and/or in connection with transfer between different sides of the machine in the longitudinal direction to ensure that the fluid, which in the case of a compressor will preferably be gas, is compressed into, for example, a collection chamber between two step or during exhaust or the like.

Depending on the rotary machine's function and area of application, it may be necessary to place cooling on the outside of the cylindrical housing, for example by cooling fins or passages for liquid cooling. Adequate storage and sealing must of course also be used for the various rotation shafts for the chamber parts and for the screw shaft.

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In various embodiments, seals or one or more sealing devices can thereby be placed or formed at the outer edge of the screw shaft against the cylindrical housing. Furthermore, there may be a sealing device installed at the screw shaft's passage in the housing. There can also be a sealing device at the edge of the chamber dividing body towards the inside of the helical groove.

To ensure that the rotary machine can be connected to a gear connection, a generator or a motor or the like, the screw shaft can be designed with a shaft pin or a recess in at least one end for a fixed or detachable connection with a motor or a drive.

In a preferred embodiment, the rotary machine according to the present invention can be used as an internal combustion engine.

When the screw shaft rotates in the cylindrical housing, each helical groove will meet a chamber dividing blade on each of the chamber dividing bodies during one round of rotation. Thereby, each helical groove will form two chambers - twice during one round. One chamber will have an increasing volume and the other chamber will have a decreasing volume. In other words, one chamber will suck while the other compresses. Furthermore, one chamber can be used for expansion (increasing volume) and the next for displacement (reducing volume). By using a connection between one end of the cylindrical housing and the opposite end in the longitudinal direction, as stated above, it will thereby be possible to carry out four passes in a continuous cycle in the machine. This is, among other things, coinciding with the four strokes of a four-stroke internal combustion engine, intake, compression, expansion and exhaust. When, for example, three helical tracks are used, each of which is divided into two chambers each, this corresponds to six cylinders in an internal combustion engine. Each track is divided into two chambers - twice during one round of rotation if there are two chamber dividing bodies and thereby performs the four strokes during one round of rotation - and the machine will during two rounds of rotation thereby perform the aforementioned four strokes six times when there are three helical tracks - which corresponds to a six-cylinder combustion engine with four strokes. The cylinder volume in each cylinder will be equivalent to the total volume of a helical track. Thus, the machine is a significant saving in the number of moving parts and rotating mass compared to an ordinary internal combustion engine with linear piston movement and transition from linear movement to rotary movement.

As a rotary machine according to the invention transports or compresses a fluid in several chambers which are formed in the helical screw grooves at the same time, it will also be possible to move the fluid between two or more different housings with screw shafts as it is not necessary for the fluid to move in chambers within the same screw shaft . This can be particularly advantageous in an application where, for example, a rotary machine as indicated above is used for compression and another, closely placed rotary machine is used for combustion and expansion, for example as an internal combustion engine. This can have special advantages, for example in connection with cooling, balancing and building up the rotary machine with special materials, where the compressing (and possibly transporting) rotary machine can be manufactured in a reasonable material without special heat properties. A closely placed rotary machine can be made of other materials that can withstand higher heat and higher pressure and can thereby be used for combustion and expansion of burnt gas in several chambers on several sides of the screw shaft, depending on how many helical grooves and chamber parts are fitted.

According to an alternative embodiment of the present invention, a special application of a rotary machine has been produced, essentially including two or more screw shafts, each of which is provided with one or more helical screw grooves, which screw shafts at least one end in the longitudinal direction of the screw shaft are each designed for connection with a engine or a drive train. The rotary machine is characterized by the fact that: - the screw shafts are each rotatably placed in their respective housings with an internal cylindrical shape where the internal diameter of the housing is essentially the same as the outer diameter of the screw shaft, which housings are each essentially closed at the ends of the screw shaft with a through opening for the screw shaft connection with a motor or drive mechanism and which housing each includes storage for the screw shaft located inside the housing, - the helically shaped screw grooves extend in a helical form from one end of the screw shaft to the opposite end of the screw shaft, - the rotary machine includes one or more rotating chambered parts bodies which chamber divider bodies are each formed as a substantially circular body with a center of rotation, which chamber divider bodies each have a number of triangular shaped chamber divider blades projecting from the center of the chamber divider body with the narrowest end at the center of the chamber divider body, which chamber divider blades are arranged with a mutual space and which chamber dividing bodies are rotatably located at the outer edge of the screw shafts with an axis of rotation mainly running perpendicular to the axis of rotation of the screw shaft and where the rotation of each of the chamber dividing bodies is synchronized with the rotation of the respective screw shaft where the chamber dividing bodies are placed, so that the chamber dividing blades on the chamber dividing bodies project into the helical screw grooves in the screw shaft and follows the movement of the screw groove as the screw shaft rotates so that a chamber divider blade on a chamber divider body follows a helical groove and separates the helical groove into a chamber on each side of the chamber divider body upon rotation of the screw shaft, which chambers have varying volumes as the screw shaft rotates as the total volume of the helical track is split in two by the chamber dividing body and as the screw shaft rotates the volume on each side of the chamber dividing body will change between essentially 0 and 100% and the two chambers together at all times form a total volume main caseli g equal to the volume of the helical screw groove, - that there is at least one inlet opening in each of the housings of the interior of the cylindrical housing into the respective helical screw groove at one end of the cylindrical housing and at least one outlet opening in each of the housings of the interior of the cylindrical housing into the respective helical screw groove at one of the ends of the cylindrical housing, and - a fluid connection is formed between at least one inlet opening in one of the housings and an outlet opening in another of the housings so that fluid transported through the rotary machine moves between the various houses.

It is preferred that the screw shafts in such an application are synchronized with each other and have the same rotational speed. However, different rotation speeds can occur when, for example, the compressing or transporting screw shaft rotates faster and compresses fluid into an intermediate chamber before transfer to the next housing. In such an application, non-return valves or pressure-controlled valves will be preferred in order to build up pressure in the chamber for further use in the next house.

If chamber parts are placed on opposite sides of the screw shafts' longitudinal direction, these chamber parts must be counter-rotating.

The number of helical grooves in the screw shafts can in various embodiments be equal to the number of chamber dividing blades on the chamber dividing bodies, but it can also be different.

In order to achieve a good seal between the chamber divider bodies and the helical screw groove in each of the screw shafts so that each helical screw groove is divided into different chambers by the chamber divider body, the profile of each chamber divider blade is preferably designed to complement the internal shape of the helical screw groove. The chamber divider body can be flat on its upper side and slightly conical with curved surfaces on its underside so that the shape is complementary to the screw groove and so that sealing is achieved with the screw groove when a chamber divider blade moves into the screw groove and follows this while both the screw shaft and the chamber divider body rotate.

The chamber dividing bodies can have a number of different shapes and can in one embodiment be a flat disk or plate. The chamber dividing bodies can also have a flat upper side and a curved or pyramidal lower side or they can be more spherical. As long as the chamber dividing body or at least each chamber dividing blade has a shape that is complementary to the interior of the helical groove, then the chamber dividing bodies and/or the chamber dividing blades can otherwise be designed so that they are appropriate in relation to heat development, pressure conditions, storage etc.

The cylindrical housings in which the screw shafts move have an internal cylindrical shape and can externally have any shape and can thereby form part of a larger construction. Several rotary machines according to the invention can of course be placed side by side or above each other or in some other way. In some embodiments, several housings can also be arranged so that two housings also share a chamber dividing body, i.e. that the chamber dividing body protrudes into two helical grooves with different chamber dividing blades at the same time. In such designs, the rotation of each screw shaft must be synchronized with each other and with the chamber dividing body.

The screw shafts are suitable for transporting and possibly compressing a fluid such as a liquid or gas. In order for the fluid to enter the helical groove in the rotary machine, there is therefore an inlet opening through the housing towards the screw shaft. The inlet opening is preferably located on the side of the screw where the chamber dividing body moves into the helical screw groove so that when the screw and the chamber dividing body rotate, a chamber is formed where the volume expands and the fluid is thereby drawn into the chamber. When then the screw shaft has moved so that the chamber blade has followed, the helical groove to the end, the valve face leaves the helical groove and the chamber is filled with fluid. Furthermore, the next valve face will enter the helical groove as the screw shaft continues to rotate and will push the fluid content of the helical groove forward in the groove after the chamber part blade moves along the helical groove and forms a chamber which has a reducing volume. If the end of the chamber is closed, the chamber dividing blade will compress the fluid against the closed surface. In the opposite case, the movement of the chamber dividing body will be able to push the fluid out of the chamber that is formed upstream (the pushing side) of the chamber dividing body. As the screw shaft rotates, the reducing volume chamber will meet an outlet opening from the cylindrical housing and from the helical screw track, as indicated above, and pressurized fluid will flow out. The completion of this "emptying" of the chamber occurs when the chamber parting blade leaves the helical groove and the screw shaft continues to rotate with an empty groove. Whether compression is to be created or just a "movement" of fluid through the helical groove is thereby decided, among other things. of the location of an outlet opening and the shape of the outlet opening. If the opening is an elongated slit that is open to the chamber with reducing volume, then the fluid in the chamber will constantly be pushed out. If the opening is small in area and is placed in such a way in the cylindrical housing that the opening is only uncovered when the chamber dividing body has passed almost through the entire helical groove, then a pressure will be formed in the chamber of the helical groove which has reducing volume and it will be pressurized fluid flowing out of the outlet opening. Alternatively, the fluid can be continuously pushed into a chamber through a pressure-controlled or non-return valve so that pressure is created in the chamber when the pressure in the chamber in the helical groove exceeds the pre-defined pressure in the valve.

In one embodiment, a through-flow opening can therefore have a length in the direction of rotation corresponding to all or part of the angle of rotation over which the helical groove in the screw shaft extends.

If the pressurized fluid is to make several passes through the screw shaft or between several screw shafts, for example for combustion of pressurized fluid and expansion, then the fluid must be transferred from one side of the cylindrical housing to the opposite side of the cylindrical housing in the longitudinal direction, as the chamber parts are counter-rotating and the screw only rotates one way or to the opposite side (if the screws rotate the same way) in the next house. This can happen in a channel or pipe connection between one end of the house and the opposite end of the house or the next house. Thus, in a preferred embodiment, several housings with screw shafts can be placed one after the other in the longitudinal direction so that the outlet from the first immediately transitions to the inlet in the next housing.

In one embodiment of the invention, the helical groove of the screw shaft is therefore formed at one or both of its ends in the longitudinal direction with a sealing closure, which sealing closure is formed with a through-flow opening that coincides with the inlet and/or outlet opening in the cylindrical housing. Furthermore, the helical groove of the screw shaft can at one or both of its ends in the longitudinal direction be formed with sealing ends, which sealing ends are each formed with one or more flow-through openings, of which one of the flow-through openings coincides with an inlet and/or outlet opening in the cylindrical housing and a of the flow openings at one end of the cylindrical housing communicates with a flow opening at the other end of the cylindrical housing outside the inner cylindrical space or another housing.

In order to further facilitate the fluid flow and to be able to use several grooves in the screw shaft at the same time, in one embodiment, one or more chambers are formed at one or at each end of the cylindrical housing in the longitudinal direction, each of which is connected to the cylindrical housing through a flow opening. In this application where several housings with screw shafts are used, several housings can share the same or several chambers.

A rotary machine as stated above can, for example, be used as a compressor in one or more stages. In such an application, non-return valves can be used in connection with the flow openings and/or in connection with transfer between different sides of the machine in the longitudinal direction to ensure that the fluid, which in the case of a compressor will preferably be gas, is compressed into, for example, a collection chamber between two step or during exhaust or the like. Depending on the rotary machine's function and area of application, it may be necessary to place cooling on the outside of the cylindrical housing, for example by cooling fins or passages for liquid cooling. Adequate storage and sealing must of course also be used for the various rotation shafts for the chamber parts and for the screw shaft.

In various embodiments, seals or one or more sealing devices can thereby be placed or formed at the outer edge of the screw shaft against the cylindrical housing. Furthermore, there may be a sealing device installed at the screw shaft's passage in the housing. There can also be a sealing device at the edge of the chamber dividing body towards the inside of the helical groove.

To ensure that the rotary machine can be connected to a gear connection, a generator or a motor or the like, the screw shaft can be designed with a shaft pin or a recess in at least one end for a fixed or detachable connection with a motor or a drive.

In a preferred embodiment, the rotary machine according to the present invention can be used as an internal combustion engine.

When the screw shafts rotate in each of the cylindrical housings, each helical groove will meet a chamber dividing blade on each of the chamber dividing bodies during one round of rotation. Thereby, each helical groove will form two chambers - twice during one round. One chamber will have an increasing volume and the other chamber will have a decreasing volume. In other words, one chamber will suck while the other compresses. Furthermore, one chamber can be used for expansion (increasing volume) and the next for displacement (reducing volume). By using a connection between one end of the cylindrical housing and the opposite end in the longitudinal direction or transfer to another housing, as indicated above, it will thereby be possible to carry out four passes in a continuous cycle in the machine or in two subsequent housings which form a machine. This is, among other things, coinciding with the four strokes of a four-stroke internal combustion engine, intake, compression, expansion and exhaust. When, for example, three helical tracks are used, each of which is divided into two chambers each, this corresponds to six cylinders in an internal combustion engine. Each track is divided into two chambers - twice during one round of rotation if there are two chamber dividing bodies and thereby performs the four strokes during one round of rotation - and the machine will during two rounds of rotation thereby perform the aforementioned four strokes six times when there are three helical tracks - which corresponds to a six-cylinder combustion engine with four strokes. The cylinder volume in each cylinder will be equivalent to the total volume of a helical track. Thus, the machine is a significant saving in the number of moving parts and rotating mass compared to an ordinary internal combustion engine with linear piston movement and transition from linear movement to rotary movement.

According to the present invention, an internal combustion engine based on the rotary machine as indicated above in one of the two applications has also been produced. The internal combustion engine essentially includes at least one screw shaft with one or more helical screw grooves, which screw shaft is designed in at least one end in the longitudinal direction of the screw shaft for connection to an engine or a drive mechanism. The internal combustion engine is characterized by: - the screw shaft is rotatably placed in a housing with an internal cylindrical shape where the internal diameter of the housing is essentially the same as the outer diameter of the screw shaft, which housing is essentially sealed at each end of the screw shaft with a through opening for the screw shaft's connection with engine or drive mechanism and which housing includes storage for the screw shaft, - the helically shaped screw grooves extend in a helical form from one end of the screw shaft to the opposite end of the screw shaft, - the internal combustion engine includes one or more rotatingly arranged chamber dividing bodies which chamber dividing bodies are each designed as a substantially circular body with a center of rotation, which chamber divider bodies each have a number of triangular shaped chamber divider blades projecting from the center of the chamber divider body with the narrowest end at the center of the chamber divider body, which chamber divider blades are spaced apart and which chamber divider bodies are rotatingly located at the outer edge of the screw shaft with an axis of rotation extending substantially perpendicular to the axis of rotation of the screw shaft and where the rotation of each of the cam parts bodies is synchronized with the rotation of the screw shaft, so that the cam parts blades on the cam parts bodies project into the helical screw grooves in the screw shaft and follow the movement of the screw track when the screw shaft rotates so that a chamber divider blade on a chamber divider body follows a helical track and separates the helical groove into a chamber on each side of the chamber divider body upon rotation of the screw shaft, which chambers have varying volumes as the screw shaft rotates as the total volume of the helical groove is bisected by the chamber divider body and after as the screw shaft rotates, the volume on each side of the chamber dividing body will change between substantially 0 and 100% and the two chambers together at any time form a total volume substantially equal to the volume of the helical screw track and - that at each end of the cylindrical hu viewed longitudinally or in connection with several cylindrical housings, four chambers (A-D) are formed where the first chamber (A) and the third chamber (C) are placed on the same side of the cylindrical housing and the second chamber (B) and the fourth chamber (D) is placed on the same side of the cylindrical housing, - where the first chamber (A) has a flow opening to the outside of the engine and a flow opening into the cylindrical housing, - the second chamber (B) has a flow opening into the cylindrical housing and a flow opening into a flow transfer body, which flow transfer body leads from the flow opening in the second chamber (B) to a flow opening into the third chamber

(C),

- the third chamber (C) has a through-flow opening to the flow transfer body as well as a through-flow opening to the cylindrical housing, - the fourth chamber (D) has a through-flow opening to the cylindrical housing and a through-flow opening to the outside of the engine, and - that a fuel supply device is fitted upstream in the rotation process of the third chamber (C) or at the third chamber (C).

Each of the chambers A-D can have very varying sizes and these chambers can be very small, i.e. they are made up of the volume in the transfer member, for example, to the next chamber. This will depend on dimensioning and the need for pressure build-up, fluid transfer and volume storage for further processing in the next chamber in the screw shaft.

Fuel can be added in connection with the transfer of pressurized gas from the second chamber B to the third chamber C or alternatively fuel can be added before the gas is drawn into the first chamber A or somewhere in between. Addition of fuel will preferably be done by otherwise known means and the fuel can be a flammable liquid based on oil such as petrol or diesel or it can be an alcohol or synthetically produced fuel. Furthermore, different mixtures of these or a flammable gas such as hydrogen can be used.

In various embodiments, the internal combustion engine can essentially also include an ignition device in connection with the cylindrical housing at the third chamber C. This would be natural to use an ignition device that is adapted to the fuel that is added and if the fuel is expected to be able to self-ignite under special conditions that can is achieved in the internal combustion engine, an ignition device can for example be omitted or used only in connection with a cold internal combustion engine and then switched off when operating temperature or other suitable operating conditions have been achieved. In one embodiment, the ignition device can provide spark ignition and is synchronized with the screw shaft. This will most often be a spark plug and a system with charging of one or more coils (coilers) can, for example, be used at the same time as the discharge of this takes place in synchronization with the rotation of the screw shaft, so that the spark ignites the fuel-added, compressed gas mixture at the right time.

Alternatively, the ignition device can be a glow device.

In various embodiments, the chambers on each side of the cylindrical housing can have a number of different locations and shapes. In one embodiment, the chambers (A-D) may be substantially semi-circular and may be arranged so that together they form a cylindrical chamber on each side of the cylindrical housing.

In order for the gas exchange between the cylindrical housing and the various chambers as mentioned above to be as suitable as possible for a good flow of gas in the internal combustion engine according to the invention, the flow openings between the chambers and the cylindrical housing must be well aligned with the flow openings in the tight ends of the screw shaft at the same time as they must be adapted for gas exchange through the rotation cycle of the propeller shaft. This is affected by designing the flow openings, particularly between the chamber and the cylindrical housing, with a suitable length in relation to the proportion of the rotation angle that the screw shaft completes where a chamber dividing blade moves through a helical groove. In other words, if there is to be an opening towards the helical track for a long period, for example when expanding the space in the helical chamber, then the opening must cover a large part of the rotation angle through which the helical track moves when it rotates. If the helical groove moves through 180 degrees of the screw shaft, then the flow opening should be an elongated slit that covers approximately or equivalently to this, i.e. a semicircular slit. Different flow openings are specified in the preferred embodiment. The flow-through opening between the first chamber A and the cylindrical housing can be slot-shaped with an extent corresponding mainly to a large part of the angle of rotation over which the helical groove in the screw shaft extends. This ensures good access to gas (e.g. air) from the outside of the engine through chamber A by the fact that the opening towards the cylindrical housing allows gas to flow into the cylindrical housing continuously while the screw shaft rotates through an angle of rotation corresponding mainly to the angle of rotation of the helical groove. Furthermore, the flow-through opening between the second chamber B and the cylindrical housing can have an extent that corresponds substantially to all or part of the angle of rotation over which the helical groove in the screw shaft extends. The flow opening between the third chamber C and the cylindrical housing can have an extent that corresponds mainly to a smaller part of the angle of rotation over which the helical groove in the screw shaft extends and the flow opening is placed mainly upstream in the chamber in relation to the direction of rotation of the screw shaft. This means that the opening between the third chamber C and the cylindrical housing is revealed immediately when the chamber in the helical groove is very small and where the chamber will expand due to the rotation of the screw shaft and the movement of the chamber dividing blade in the groove. Thus, pressurized gas will be able to flow quickly into a relatively small chamber and this will continue at the same time as the chamber in the helical groove expands (and thereby sucks gas out of chamber C) until the flow opening into the cylindrical housing from the third chamber C is covered by the sealing end surface of the screw shaft. Then, ignition of the trapped gas in this chamber in the helical groove of the propeller shaft can cause a further expansion that drives the propeller shaft around. It will be obvious that this will entail a relatively high pressure against the chamber part blade in this helical groove and the chamber part blade as well as the chamber part body's storage, design and dimensioning must therefore be adapted to be able to withstand this pressure. Furthermore, the exhaust that is formed in this chamber will follow the helical groove further forward where the next chamber divider body will push a chamber divider blade into this groove and will be able to create a chamber with reducing volume so that the exhaust is pushed out towards the fourth chamber D. In order for the exhaust to continuously could flow easily out of the chamber in the helical groove, then the flow opening between the fourth chamber D and the cylindrical housing should be open throughout much or substantially all of the angle of revolution that the propeller shaft covers to push the chambering blade through the entire helical propeller groove which is filled with exhaust . This can be accomplished by the flow opening between the fourth chamber D and the cylindrical housing being slot-shaped with an extent that corresponds mainly to a large part of the angle of rotation over which the helical groove in the screw shaft extends.

Similar to the rotary machine described above, chamber parts which are placed on opposite sides of the longitudinal direction of the screw shaft must be counter-rotating. Furthermore, it is preferred that the number of helical grooves in the screw shaft corresponds to the number of chamber dividing blades on the chamber dividing bodies and that the profile of each chamber dividing blade is complementary to the internal shape of the helical screw groove. The chamber dividing bodies can be synchronized with the rotation of the screw shaft through a gear transmission or the chamber dividing bodies can be synchronized with the rotation of the screw shaft through an electrical transmission and electronic control of a motor that drives each or more of the chamber dividing bodies.

In various embodiments, seals or one or more sealing devices can thereby be placed or formed at the outer edge of the screw shaft against the cylindrical housing. Furthermore, there may be a sealing device installed at the screw shaft's passage in the housing. There can also be a sealing device at the edge of the chamber dividing body towards the inside of the helical groove.

In the following, mainly two embodiments of the invention are shown with reference to the attached figures. Figure 1 shows in section from above an embodiment of a rotary machine with a screw shaft and with the chamber parts according to the invention in a first position.

Figure 2 shows in perspective the rotary machine in Figure 1.

Figure 3 shows in section from above an embodiment of a rotary machine with a screw shaft and with the chamber parts according to the invention in a second position.

Figure 4 shows in perspective the rotary machine in Figure 3.

Figure 5 shows in section from above the embodiment of a rotary machine with a screw shaft and with the chamber dividing bodies according to the invention in a third position.

Figure 6 shows in perspective the rotary machine in Figure 5.

Figure 7 shows, in principle, an internal combustion engine based on the rotary machine as shown in figures 1-6.

Figure 1 shows in general the essential parts in a rotary machine according to the invention as stated above.

Figures 1 and 2 show a screw shaft 1 with helical grooves 2, 3 and 4. On each side of the screw shaft are shown chamber dividing bodies 10 and 20 with respectively rotation centers 11 and 21 and chamber dividing blades 12, 13 and 14 as well as 22, 23, 24.1 the figure is the chamber dividing blade 22 on its way into the helical groove 3 and the chamber dividing blade 13 is halfway through moving through the helical groove 2 while the chamber dividing blade 23 is on its way out of the helical groove 4.

When the chamber dividing blade 22 moves through the helical groove 3, an expanding volume is formed downstream (on the back) of the blade 22 and fluid is drawn into this expanding chamber until it is filled (when the chamber dividing blade leaves the screw groove. At the same time, the contents are pushed upstream (on the front side ) of the chamber dividing blade 22 through the screw and out at the other end of the screw shaft. This is the content of the helical groove 3.

In Figs 3 and 4, the chamber dividing blade 22 is halfway into the helical groove 3. The chamber dividing blade 13 is halfway through the helical groove 2.

In Figures 5 and 6, the chamber dividing blade 22 is on its way out of the helical groove 3 while the chamber dividing blade 23 is on its way into groove 2. The chamber dividing blade 13 has left the groove 2 and the chamber dividing body 14 is on its way into groove 1.

Figure 7 shows an internal combustion engine according to the present invention with a screw shaft and a housing as well as chamber parts.

The screw shaft has three helically shaped grooves (1, 2, 3) which are in tight contact with the inside of the cylindrical housing. Between these three wings, three helically shaped elevations are thereby formed which seal against the inside of the cylindrical housing. The screw shaft has a first and a second end in its longitudinal direction. In the preferred embodiment, a shaft pin protrudes from the housing at the other end.

The engine is shown with two semi-circular chambers at each end. At its first end, the engine has a chamber B for compressed gas which is compressed to chamber B by the screw shaft in the upper half and an exhaust chamber D in the lower half with outlet for exhaust if necessary. for exhaust systems.

At its other end, the housing has a chamber A for the intake of air, possibly connected to the intake manifold. Furthermore, at the other end, there is a chamber C for pressurized gas which is transported from chamber B through a fluid connection on the outside of the cylindrical housing. In connection with chamber C, the gas is fueled, although this can happen at any point after the gas flows into chamber A or before this.

The screw shaft is tight at its ends (tight plate) against the first and second ends of the housing except for an opening in each of the helical grooves at the first end and the second end in the helical recess. In other words, these openings are offset by 180 degrees along the axis of rotation of the rotor. These openings create a connection between chambers A, B, C and D throughout the cycle.

Chambers A and D (intake of air and exhaust of exhaust) have slit-shaped openings towards the helical groove of the screw shaft so that air is drawn in continuously by expansion of the volume in the helical groove and exhaust is pushed out by the volume in the helical groove after combustion by reduction of the volume by means of the chamber dividing blade on the chamber dividing body by rotation of the rotor.

The rotating chamber divider bodies on each side of the screw have a number of chamber divider blades corresponding to the number of helically shaped grooves in the rotor. These chamber dividing blades on either side of the rotating screw shaft divide each helical track into two chambers of varying volume. If the helical recesses twist over more than 180 degrees of the rotor's circle, then the chamber dividing blades on the rotating chamber dividing bodies will in some cases divide a helical groove in the screw shaft into three individual chambers. However, this is of little importance as this only happens for a short moment and only two of these chambers (the two foremost in the direction of rotation) contribute to the internal combustion engine's driving cycle. The helical tracks are thereby divided at all times into 6 chambers that participate in the cycle. This corresponds to 6 cylinders in a piston engine. Furthermore, the engine goes through the 4 strokes of a normal four-stroke engine - Intake - compression - expansion as a result of combustion - blowing out of the exhaust. Intake occurs by expansion of volume and exhalation occurs by pushing out exhaust (reduction of volume).

The rotating cam divider bodies with cam divider blades (the same number as the helical grooves) are driven by a transmission from the rotor (eg gears) in a 1:1 ratio, i.e. these cam divider bodies rotate as fast as the screw shaft, unlike in a conventional internal combustion engine with a transition from linear movement to rotary movement (piston engine) where the transmission ratio between drive shaft and camshaft for control of valves is 2:1. The chamber dividing bodies are counter-rotating (opposite ways) towards the other end of the engine.

The internal combustion engine works in a cycle where air is drawn into a first chamber A (on the other end of the engine housing) by the chamber being connected to a helical groove in the screw shaft which, when the screw shaft rotates, has an increasing volume and thereby sucks the air into this room. The helical groove is delimited at each end by a chamber dividing blade on each of the rotating chamber dividing bodies and when the rotation continues, an opening to the chamber B is revealed on the opposite side of the housing, i.e. at the first end of the housing. The air in the groove is then pressed into chamber B by the helical groove's volume being reduced through rotation against the chamber dividing blade on the rotating chamber dividing body which delimits this helical groove. In other words, the gas is compressed into chamber B. This happens because chamber B is connected to chamber A and acts as an equalizing chamber to create a more constant pressure towards the combustion chamber in the screw shaft. In this phase, fuel can also be added to the compressed air. Alternatively, fuel can be completely or partially added to the air that is drawn into the intake of chamber A.

Via a flow transmission such as a channel or a pipe, the pressurized gas (possibly with fuel) is transferred to chamber C, which also functions as an equalization chamber and supply chamber to the combustion "chamber" in the screw shaft.

A non-return valve may optionally be placed between chambers B and C. This valve may also be designed so that it is pressure-controlled and only opens when the pressure in chamber B is above a predetermined limit.

The flow opening in the end seal for the screw shaft towards the intake chamber A is downstream in the rotation cycle.

The flow opening towards chamber B is downstream in the direction of rotation so that only compressed air enters B.

The flow opening from chamber C towards the propeller shaft is upstream (early) in the rotation cycle so that pressurized air/fuel enters the rotor's helical recess when this is small. This opening is only open when the opening in the rotor's end seal is more than equal to the opening towards the cam dimension, i.e. only for a short moment. This connection is then closed and the spark plug (in the housing, towards the screw shaft) ignites. This drives the rotor around by expansion of the combustion gas chamber. This happens over 180 degrees (corresponding to a full stroke in a reciprocating engine) and then the opening in the end seal of the screw shaft is released towards the chamber D which has a slit opening towards the cylindrical housing to be able to receive exhaust gas which is pushed out through almost 180 degree rotation of the screw shaft before the opening in the end seal of the screw shaft disappears behind the end seal in chamber B towards the screw shaft.

The helical recess which has just delivered exhaust (which continuously pushes out exhaust) will, on the opposite side of the chamber divider blade on the chamber divider body a, begin to suck in gas to be compressed.

A helical track is thereby divided into two chambers by the chamber dividing body a. These are a chamber for pushing out exhaust and a chamber for sucking in gas. The upstream chamber sucks in, while the downstream chamber pushes out.

The same helical track is divided into two chambers by the chamber dividing body P where one chamber is in compression and one chamber is in combustion (expansion of gas). The upstream chamber (in the direction of rotation) is compressing while the downstream chamber (after the chamber dividing body P) is in combustion and expansion of gas.

Claims (1)

1. Rotary machine essentially including a screw shaft (1) with one or more helical screw grooves (2, 3, 4), which screw shaft (1) is designed in at least one end in the longitudinal direction of the screw shaft for connection to a motor or a drive mechanism, where: - the screw shaft (1) is rotatably placed in a housing with an internal cylindrical shape where the internal diameter of the housing is essentially the same as the outer diameter of the screw shaft (1), which housing is essentially closed at each end of the screw shaft (1) with a through opening for the connection of the screw shaft (1) with the motor or drive mechanism and which housing includes storage for the screw shaft (1), - the helically shaped screw grooves (2, 3,4) extend in a helical form from one end of the screw shaft (1) to the opposite end of the screw shaft (1), characterized by - the rotary machine includes one or more rotatingly arranged chamber parts bodies (10, 20), which chamber parts bodies (10, 20) are each designed as a mainly circular body with a rotation nter (11, 21), which chamber dividing bodies (10, 20) each have a number of triangular shaped chamber dividing blades (12, 13, 14, 22, 23, 24) projecting from the center of the chamber dividing body (10, 20) with the narrowest end at the chamber dividing body (10, 20) center, which chamber divider blades (12, 13, 14, 22, 23, 24) are arranged with a space between them and which chamber divider bodies (10, 20) are rotatably arranged at the outer edge of the screw shaft (1) with a rotation axis (11 , 21) mainly running perpendicular to the rotation axis of the screw shaft (1) and where the rotation of each of the chamber dividing bodies (10, 20) is synchronized with the rotation of the screw shaft (1), so that the chamber dividing blades (12, 13, 14, 22, 23, 24) on the chamber divider bodies (10, 20) project into the helical screw grooves (2, 3, 4) in the screw shaft (1) and follow the movement of the screw groove (2, 3, 4) when the screw shaft (1) rotates so that a chamber divider blade (12, 13 , 14, 22, 23, 24) on a chamber dividing body (10, 20) follows a helical groove (2, 3, 4) and separates the helical groove (2, 3, 4) in a chamber on each side of the chamber dividing body (10, 20) upon rotation of the screw shaft (1), which chambers have varying volumes when the screw shaft (1) rotates as the total volume of the helical groove is divided in two by the chamber dividing body ( 10, 20) and as the screw shaft (1) rotates, the volume on the right side of the chamber dividing body (10, 20) will change between mainly 0 and 100% and the two chambers together at all times form a total volume mainly equal to the volume of the helical screw groove (2, 3, 4) and - that there is at least one inlet opening in the housing to the interior of the cylindrical housing into the helical screw groove (2, 3, 4) at one end of the cylindrical housing and at least one outlet opening in the housing to the interior of the cylindrical housing into the helical screw groove (2, 3, 4) at one of the ends of the cylindrical housing. 2. Rotary machine according to claim 1, characterized in that chamber parts (10, 20) which are placed on opposite sides of the longitudinal direction of the screw shaft (1) are counter-rotating. 3. Rotary machine according to claims 1-2, characterized in that the number of helical grooves (2, 3, 4) in the screw shaft (1) corresponds to the number of chamber divider blades (12, 13, 14, 22, 23, 24) on the chamber divider bodies (10, 20). 4. Rotary machine according to claims 1-2, characterized in that the number of helical grooves (2, 3, 4) in the screw shaft (1) is different from the number of chamber divider blades (12, 13, 14, 22, 23, 24) on the chamber divider bodies (10, 20). 5. Rotary machine according to any one of claims 1-4, characterized in that the profile of each chamber dividing blade (12, 13, 14, 22, 23, 24) is complementary to the internal shape of the helical screw groove (2, 3, 4). 6. Rotary machine according to any one of claims 1-5, characterized in that the helical groove (2, 3, 4) of the screw shaft (1) is formed at one or both of its ends in the longitudinal direction with a sealing closure, which sealing closure is formed with one or more flow openings that coincide with the inlet and/or the outlet opening in the cylindrical housing. 7. Rotary machine according to any of claims 1-6, characterized in that a flow opening has a length in the direction of rotation corresponding mainly to all or part of the angle of rotation over which the helical groove (2, 3, 4) in the screw shaft (1) extends. 8. Rotary machine according to any one of claims 1-7, characterized in that the helical grooves (2, 3, 4) of the screw shaft (1) are formed at one or both of their ends in the longitudinal direction with sealing ends, which sealing ends are each formed with one or more flow-through openings, of which one of the flow-through openings coincides with a inlet and/or outlet opening in the cylindrical housing and one of the flow openings at one end of the cylindrical housing is connected to a flow opening at the other end of the cylindrical housing outside the inner cylindrical space. 9. Rotary machine according to any one of claims 1-8, characterized in that one or more chambers are formed at one or at each end of the cylindrical housing in the longitudinal direction, each of which is connected to the cylindrical housing through a flow opening. 10. Rotary machine according to any one of claims 1 -9, characterized in that the rotation of the chamber dividing bodies (10, 20) is synchronized with the rotation of the screw shaft (1) through a gear transmission. 11. Rotary machine according to any one of claims 1 -8, characterized in that the rotation of the chamber dividing bodies (10, 20) is synchronized with the rotation of the screw shaft (1) through an electrical transmission and electronic control to a motor that drives each or more of the chamber dividing bodies (10, 20). 12. Rotary machine according to any one of claims 1-11, characterized in that a sealing device is placed at the outer edge of the screw shaft (1) against the cylindrical housing. 13. Rotary machine according to any one of claims 1-12, characterized by the fact that a sealing device is placed at the screw shaft (1) passage in the housing. 14. Rotary machine according to any one of claims 1-13, characterized in that a sealing device is placed at the edge of the chamber dividing body (10, 20) against the inside of the helical groove (2, 3, 4). 15. Rotary machine according to any one of claims 1-13, characterized in that the screw shaft (1) is designed with a shaft pin or a recess in at least one end for fixed or detachable connection with a motor or a drive unit. 16. Combustion engine essentially including a screw shaft (1) with one or more helical screw grooves (2, 3, 4), which screw shaft (1) is designed in at least one end in the longitudinal direction of the screw shaft (1) for connection with an engine or a drive mechanism , where: - the screw shaft (1) is rotatably placed in a housing with an internal cylindrical shape where the internal diameter of the housing is essentially the same as the outer diameter of the screw shaft (1), which housing is essentially sealed at each end of the screw shaft (1) with a through opening for the connection of the screw shaft (1) with motor or drive mechanism and which housing includes storage for the screw shaft (1), - the helically shaped screw grooves (2, 3, 4) extend in a helical form from one end of the screw shaft (1) to the opposite end of the screw shaft (1), characterized in that the internal combustion engine includes one or more rotatingly placed chamber dividing bodies (10, 20), which chamber dividing bodies (10, 20) are each designed as a mainly circular body with a center of rotation (11, 21), which chamber dividing bodies (10, 20) each have a number of triangular chamber divider blades (12, 13, 14, 22, 23, 24) projecting from the center of the chamber divider body (10, 20) with the narrowest end at the center of the chamber divider body (10, 20), which chamber divider blades (12, 13, 14, 22, 23, 24) are placed with a space between them and which chamber dividing bodies (10, 20) are rotatably placed at the outer edge of the screw shaft (1) with an axis of rotation (11,21) mainly running perpendicular to the axis of rotation of the screw shaft (1) and where the rotation of each of the chamber divider bodies (10, 20) is synchronized with the rotation of the screw shaft (1), so that the chamber divider blades (12, 13, 14, 22, 23, 24) of the chamber divider bodies (10, 20) protrude into the helical screw grooves (2, 3, 4) in the screw shaft (1) o g follows the movement of the screw track (2, 3, 4) when the screw shaft (1) rotates so that a chamber divider blade (12, 13, 14, 22, 23, 24) on a chamber divider body (10, 20) follows a helical groove (2, 3 , 4) and separates the helical groove (2, 3, 4) into a chamber on each side of the chamber dividing body (10, 20) by rotation of the screw shaft (1), which chambers have varying volumes when the screw shaft (1) rotates as the total the volume of the helical groove (2, 3, 4) is split in half by the chamber divider body (10, 20) and as the screw shaft (1) rotates, the volume on each side of the chamber divider body (10, 20) will change between essentially 0 and 100% and the two chambers together at all times form a total volume substantially equal to the volume of the helical screw groove (2, 3, 4) and - that at each end of the cylindrical housing in the longitudinal direction a total of four chambers (A-D) are formed where the first chamber (A) and the third chamber (C) are placed on the same side of the cylindrical housing and the second chamber (B) and the fourth chamber (D) is placed on the same side of the cylindrical housing, - where the first chamber (Å) has a flow opening to the outside of the engine and a flow opening into the cylindrical housing, - the second chamber B has a flow opening into the cylindrical housing and a flow opening into a flow transfer body, which flow transfer body leads from the flow opening in the second chamber (B) to a flow opening into the third chamber (C), - the third chamber (C) has a flow opening to the flow transfer body as well as a flow opening to the cylindrical housing , - the fourth chamber (D) has a through-flow opening to the cylindrical housing and a through-flow opening to the outside of the engine, and - that a fuel supply device is placed upstream in the rotation process of the third chamber C or at the third chamber C. 17. Internal combustion engine according to claim 16, characterized by the helical groove (2, 3, 4) of the screw shaft (1) is formed at one or both of its ends in the longitudinal direction with a sealing closure, which sealing closure is provided with a through-flow opening which coincides with the through-flow openings in the cylindrical housing when the screw shaft ( 1) rotates, 18. Combustion engine according to claims 16-17, characterized in that an ignition device is placed in the third chamber C. 19. Internal combustion engine according to claim 18, characterized in that the ignition device is placed in a separate chamber between the third chamber C and the flow opening of the cylindrical housing. 20. Internal combustion engine according to claims 18-19, characterized in that the ignition device provides spark ignition and is synchronized with the screw shaft (1). 21. Internal combustion engine according to claims 18-19, characterized in that the ignition device is a glow device. 22. Combustion engine according to one or more of claims 16-21, characterized in that the chambers (A-D) are mainly semicircular 23. Combustion engine according to one or more of claims 16-22, characterized in that the flow opening between the first chamber A and the cylindrical housing is slit-shaped with an extent that corresponds mainly to a large part of the angle of rotation as the helical groove (2, 3, 4 ) in the screw shaft (1) extends over. 24. Combustion engine according to one or more of claims 16-23, characterized in that the flow-through opening between the second chamber B and the cylindrical housing has an extent that corresponds mainly to all or part of the angle of rotation that the helical groove (2, 3, 4) in the screw shaft (1) extends above. 25. Combustion engine according to one or more of claims 16-24, characterized in that the flow opening between the third chamber C and the cylindrical housing has an extent that corresponds mainly to a smaller part of the angle of rotation that the helical groove (2, 3, 4) in the screw shaft (1) extends above and the flow opening is placed mainly upstream in the chamber in relation to the direction of rotation of the screw shaft (1). 26. Combustion engine according to one or more of claims 16-25, characterized in that the flow opening between the fourth chamber D and the cylindrical housing is slit-shaped with an extent that corresponds mainly to a large part of the angle of rotation as the helical groove (2, 3, 4 ) in the screw shaft (1) extends above. 27. Combustion engine according to one or more of claims 16-26, characterized in that chamber parts (10, 20) which are placed on opposite sides of the longitudinal direction of the screw shaft (1) are counter-rotating. 28. Combustion engine according to one or more of claims 16-27, characterized in that the number of helical grooves (2, 3, 4) in the screw shaft (1) corresponds to the number of chamber divider blades (12, 13, 14, 22, 23, 24) on the chamber divider bodies ( 10, 20). 29. Internal combustion engine according to one or more of claims 16-27, characterized in that the number of helical grooves (2, 3, 4) in the screw shaft (1) is different from the number of chamber dividing blades (12, 13, 14, 22, 23, 24) on the chamber dividing bodies (10, 20). 30. Combustion engine according to one or more of claims 16-29, characterized in that the profile of each chamber section blade (12, 13, 14, 22, 23, 24) is complementary to the internal shape of the helical screw groove (1). 31. Combustion engine according to one or more of claims 16-30, characterized in that the rotation of the chamber dividing bodies (10, 20) is synchronized with the rotation of the screw shaft (1) through a gear transmission. 32. Combustion engine according to one or more of claims 16-30, characterized in that the rotation of the chamber dividing bodies (10, 20) is synchronized with the rotation of the screw shaft (1) through an electrical transmission and electronic control to a motor that drives each of or more of the chamber dividing bodies (10, 20). 33. Combustion engine according to one or more of claims 16-32, characterized in that sealing devices are placed at the outer edge of the screw shaft (1) against the cylindrical housing. 34. Combustion engine according to one or more of claims 16-33, characterized in that a sealing device is placed at the outer edge of the screw shaft (1) against the cylindrical housing. 35. Combustion engine according to one or more of claims 16-34, characterized in that a sealing device is placed at the passage of the screw shaft (1) in the housing. 36. Combustion engine according to one or more of claims 16-35, characterized in that a sealing device is placed at the edge of the chamber dividing body (10, 20) towards the inside of the helical groove (2, 3, 4). 37. Combustion engine according to one or more of claims 16-36, characterized in that the screw shaft (1) is designed with a shaft pin or a recess in at least one end for fixed or detachable connection with an engine or a drive unit.