RS51350B - ROTOR FOR ROTATING MACHINE AND ROTATING MACHINE - Google Patents

Abstract

The rotor has a wing profile unit (3) including a convex elevation (19) on an outer mantel surface (4) and rotating in a gaseous or fluid medium. An axial hollow space (6) is enclosed in the interior of the rotor, and the rotor is connected with a chamber to supply or discharge the medium. An opening (5) is provided between the space and the mantel surface in the region of the profile units. A shaft is connected with an impeller, and the impeller and the shaft can be rotatably supported in a stator. An independent claim is also included for a fluid flow machine with a rotor.

Description

[0001] The invention relates to a rotor for a rotary machine according to the definition of patent claim 1 as well as to a rotary machine according to the definition of patent claim 11.

[0002] Rotary machines are distinguished by the fact that they produce a pressure difference in a gas or liquid medium or are driven by a pressure difference in a medium of this kind. For this reason, such rotary machines usually have one rotor, which is placed in a gas or liquid medium with the possibility of turning against the stator, and by its shape or placement produces a pressure difference or converts the pressure difference in the medium into rotation. Rotary machines of this type primarily include most types of pumps, compressors, turbo-machines, turbines or wind energy converters, which have rotors of various designs, and are mostly rotatable and placed in the housing as a stator.

[0003] A rotary machine in the form of a pump is known from DD 293 181 A5, which has

one cylindrical rotor in the shape of a cone, which is eccentrically located in the pump housing. This rotor is connected to the drive, and when it rotates, it produces a sickle-shaped circulating pump chamber, which primarily transfers oil as a liquid from the inlet port to the outlet port. This pump, which is based on the principle of hydrodynamics, produces an oil membrane during rotation in the sickle-shaped casing, which leads to an increase in pressure in the pump chamber, thus transporting the oil from the inlet to the outlet. At the same time, the rotor has a relatively smooth, round outer surface of the casing, which solely on the basis of its eccentric circulation path produces an increase in pressure in the liquid. One such eccentrically circulating rotor in a cylinder-shaped housing is poorly adjusted already on the basis of its unstructured envelope surface with the gas medium in the pump chamber.

[0004] From DE 103 19 003 Al, the rotor of the wind energy converter is admittedly known, through which wind energy is converted into electrical energy. In this case, the rotors consist of one shaft located in the stator, on which there are rotor blades protruding outwards at equal-angle intervals. The blades of the rotor are formed as a symmetrical wing of the bearing surface of an airplane, which in the direction of flow has a cylindrical envelope surface, and thus has a convex protrusion, which converges towards the rear at a sharp angle. The blades of the rotor are arranged in such a way that the wiping air acts as a gas medium according to the Bernoulli equation on the pressure difference, as a result of which the rotor embedded in the stator is switched into rotation. Since such a wing on its convergent edge at a sharp angle causes a disruptive vortex formation, depressions are provided on the profile of the wing transverse to the direction of the wind. In this way, a lower pressure is set on the upper side than on the lower side, which leads to additional pressure, which reduces the creation of vortices, and the transformation of energy should be carried out with a higher degree of useful effect. This type of rotor is intended exclusively for use in air or gas media, and due to the long blades of the rotor and the diameter of the housing required for that reason, it can hardly be used with liquid media.

[0005] From DE 42 23 965 Al, which is considered to be the closest to the state of the art, a turbo-machine rotor is admittedly known, where at least one bearing plate is mounted on the bearing shaft, on the cylindrical surface of the shell of which there are protruding short blades, which circulate in the gas medium. That rotor is housed in the stator housing, and is driven by a high-revving shaft. In doing so, the gas medium is forced from the inlet opening with a high compression effect into the outlet opening. As a rule, a turbo-machine rotor of this type is not suitable for liquid media, because they cannot be compressed, and the thin blades could easily be damaged.

[0006] From DE 197 19 692 Al, a rotor-pump with a rotor that has internal teeth is known, and which has a powerful performance of a rotor with internal teeth. The pump consists of a housing in which there is a rotating eccentric ring in which one outer and one inner turbine wheel are rotatably mounted. At the same time, the internal turbine circuit represents an internal rotor with a greater number of teeth on its outer surface of the casing, which is placed in an external rotor with the possibility of rotation. The outer rotor wraps around the inner rotor with its inner casing surface, which also has inwardly directed teeth. At the same time, both the inner and outer teeth extend along the entire length of the surface casing, and mainly consist of one convex elevation, with six convex elevations on the outer surface of the inner rotor casing, and seven convex elevations on the inner surface of the outer rotor. The inner hollow space of the outer rotor is connected to the inlet and outlet openings, which are opposite each other. The rotation of the inner rotor causes the rotation of the outer rotor in the eccentric ring, whereby a whole series of chambers with variable volume is created between the teeth of the inner and outer rotor. Thus, the fluid in the chambers is sucked into the expanding chambers and expelled from the decreasing chambers. A hydraulic fluid is provided as a fluid, which is pushed from the inlet opening to the outlet opening through the pressure differences thus produced. Since the rotor of this type consists of two parts that are coaxially located to each other, which also have different numbers of teeth and fit into each other in the most accurate design, such a rotor arrangement is very expensive to manufacture, and it is also equipped with a number of parts coated with a friction layer, which are subject to wear.

[0007] This invention had the task of making a universally applicable rotor for many types of rotary machines, which is strong and does not need to be maintained, and is therefore easy to manufacture.

[0008] This task is solved through the invention specified in patent claims 1 and 11. Further forms and examples of the invention, which prove its advantage, are specified in the subclaims.

[0009] Inventions for the advantage that through the profile of the bearing surface at once from the envelope of the rotor based on the Bernoulli effect, due to the movement of the rotor or the flow of gas or liquid medium, the effect of underpressure is created above the profile of the bearing surface, so that the rotor of this type can be used in rotary machines for liquid but also for gas media. Since the pressure action or the suction action is not produced by the creation of circulating compression chambers, the medium that is moved with solid substances can be primarily transported in this way, so rotors of this type are also very suitable for the continuous transport of spreading material or dispersions.

[0010] The invention has at the same time the advantage that through the circulation favorable profile of the bearing surface only a small vortex is created in the used medium, and apart from storage there will be no contact with the stator or other parts of the rotor, so that rotary machines, which are equipped with such a rotor, operate with particularly low noise and have almost no losses in flow or friction. Since the rotor of the invention is hollow inside and produces a pressure difference only through the flat profile of the bearing surface on one of the envelope surfaces, it is made with a particularly low weight, so that only small masses have to be accelerated, through which overall and in connection with low friction and low turbulence of the flow, a rotary machine with high performance can be achieved.

[0011] Due to the small mass of the rotor and its fairly symmetrical construction, as well as the centric rotation, there are only slight effects of centrifugal force, so the advantage of a rotor of this type is that it starts with a high number of revolutions. As a result, large differences in pressure can be produced with high flow velocities, which has the advantage that at the same time high performance of the transfer of the intended gas or liquid medium or the solids it contains can be achieved.

[0012] Since the producible pressure difference with such a profiled casing of the rotor of the invention grows almost proportionally to the number of revolutions, the advantage is that, with the same number of revolutions of the rotor, it is hardly possible for oscillations in pressure or volume to occur. Through the profile of the bearing surface on the surface of the casing, there is always a difference in pressure when the rotor is in operation, which is independent of the surrounding pressure of the medium, thus giving an advantage in that even high-density gas media can be transported or liquids from a great depth can be pumped to the upper surface under static pressure.

[0013] The rotor according to the invention and the rotary machine that is equipped with it can not only be used in the operating state for the transmission or production of pressure, but it is also useful when introducing the correct flow of medium under steam pressure and for the production of revolutions, in order to produce, for example, electricity from the energy of water power or wind.

[0014] With the multi-stage formation of the rotor according to the invention and the rotary machine equipped with it, the advantage is that higher pressures can be produced in the case of axial stages and a constant amount of flow, or in the case of coaxial stages, due to the increase in the profile surface, larger flow amounts can be transmitted with the same pressure difference.

[0015] The invention is described in more detail by means of an exemplary embodiment, which is shown in the drawing. This is how they show: Fig. 1: perspective view of a pump with a single-stage pump rotor; Fig. 2: front view of pump with pump rotor; Fig. 3: view of the pump with pump rotor; Fig. 4: lamella ring of the turbine circuit for the pump rotor; Fig. 5; arrangement of lamellar elements of the turbine circuit for the pump rotor; Fig. 6: section of a pump with a multi-stage pump rotor; Fig. 7: section of the drive turbine;

[0016] In Fig. 1 of the drawing shows the perspective 1 of the pump as a rotary machine, which contains a single-stage hollow rotor 2 as a pump rotor, which on the outer surface of the casing 4 has nine profile elements of the bearing surface 3, between which the flow openings 5 towards the inner hollow space 6 are located.

[0017] With the pump shown, it is a design that is mainly driven by water as a liquid medium. Pump 2 consists mainly of one stationary housing 7 as a stator, in which the pump rotor is located. The rotor is rotatably housed in the casing 7 in two bearings 8, and in its center it has one shaft 9, which is connected to the not shown drive motor 9. The casing 7 is generally cylindrical in shape and contains on the outer surface of the casing an outlet opening 11 for draining the water to be pumped. An inlet opening 10 is provided on the left front or casing surface 7 for admitting water that is pumped towards the hollow space 6, which can be connected to a supply water which is not shown. The inlet opening 10 is connected to the hollow space 8 of the rotor 2, and forms an inlet chamber 12 with it. Basically, all liquid media such as e.g. water, oil and the like as well as all liquids, which are mixed with solids, e.g. dispersions.

[0018] In Fig. 2 of the drawing shows the previously described pump 1 with a front view, from which the placement and formation of the rotor 2 can be seen. The rotor 2 consists mainly of a cylindrical turbine wheel 20, which has a cylindrical hollow space 6 inside, which forms the inlet chamber 12 in the case of the pump 1 shown. On the outer surface of the casing 4 of the rotor 2, there are nine convex elevations 3 at the same angular intervals, which form one axial profile of the bearing surface on the outer tangential surface of the casing 4 of the rotor 2. Since the rotor 2 on its outer tangential surface 4 has several profile elements of the bearing surface 3, which during rotation according to the Bernoulli effect create an area of low pressure and in gas media, such as air, all gas media as well as gas media moved with bulk material can be transported, compressed or sucked in this way.

[0019] In the end area of the profile of the bearing surface 3, passage openings 5 are provided towards the inner hollow space 6 or the inlet chamber 12 of the pump 1, in which there is a medium for pumping, such as water. The axial formation of pump 1 is shown individually in Fig. 3 drawings. From Fig. 3 drawing is visible, that the rotor 2 is made in the axial direction in the form of lamellae. These slats are made of sheet metal and for the profile of the bearing surface 3 they are cut or processed best with a laser. The rotor 2 consists mainly of lamellar rings 13 and distributed lamellar elements 14, which form the turbine wheel (20).

[0020] Lamellar rings 13 are shown in more detail in Fig. 4 drawings, and lamellar elements 14 in Fig. 5 of the drawing, and they as an axial lamellar package form a turbine circuit 20 with tangential surfaces of the casing 4. The rotor 1 shown in Fig. 3 of the drawing consists of three arrangements of lamellar elements 14, on the outer side surfaces of which one lamellar ring 13 is attached. The lamellar ring 13 consists of a flat steel sheet, which is protected from corrosion due to liquids containing water or consists of stainless steel. The lamellar rings 13 as well as the lamellar elements 14 consist mainly of the same material, which, depending on the medium used, can also consist of other metals, hard plastics, synthetic fibers or ceramics. Each lamellar ring 13 has an internally drilled hole 23 in the shape of a circle, for example with a diameter of 250 mm and a smallest outer diameter of ca. 360 mm. At the same time, the lamellar ring 13 contains mainly nine of the same angular regions of 40° each, on the outer tangential surface of the casing 4 there is one convex elevation 19, which, opposite to the direction of rotation 18, passes straight down into the exit area 24 and forms the profile of the bearing surface 3. The convex elevation 19 has one elevation 19 of approx. 45 mm and has a radius of ca. 20 mm. The profile part 24 that comes out against the direction of rotation has a concave bend with a radius of 167 mm and extends for a length of approx. 70 mm. The convex elevation 19 with the decreasing concave exit region 24 thus forms on the surface of the envelope 4 a profile of the bearing surface of the aircraft wing. The profile of the bearing surface 3 thus ends in a slightly rising tip 25, which looks like a spoiler and prevents the formation of vortices on the trailing edge.

[0021] After the tip 25, which prevents the creation of vortices, a tangential flat surface follows opposite to the direction of rotation 18, which has the smallest distance to the axis of rotation 26 and goes tangentially towards it in a length of ca. 5 mm. This flat surface borders the flow openings 5 in the axial direction and ends each individual profile of the bearing surface 3 on the tangential outer surface of the casing 4 of the rotor 2. At the same time, each lamellar ring 13 consists of related profiles of the bearing surface 3, which are located at the same distance from the axis of rotation 26.

[0022] Between the two outer lamellar rings 13 there are three lamellar layers of all nine lamellar elements 14 for the design of the shown pump rotor 2, which on their outer radial edges have the same profile of the bearing surface 3 as the lamellar rings 13. To make the turbine circuit 20 of the rotor 2, individual lamellar elements 14 are connected congruently coaxially with the profile of the bearing surface 3 with lamellar ring 13 or with other lamellar arrangements and thus represent one axial turbine circuit or part of a turbine circuit, which on its external tangential surface of the casing 4 forms an equal axially straightened profile of the bearing surface 3. In this case, the lamellar elements 14 are tangentially offset from each other and connected together with the lamellar rings 13, whereby the gap between the lamellar elements creates one passage opening 5, through which outside, it sucks in the intended medium through the internal one of the cylindrical hollow space 6 due to underpressure along the decreasing profile of the bearing surface 3, based on the Bernoulli effect.

[0023] For favorable circulation formation of those passage openings 5, individual lamellar elements 14 have in their rear region a convex bend 15 and in their front region a concave bend 16, which during rotation enable a vortex-free flow. At the same time, the convex bend 15 on the inner edge also turns into a concave bend, which corresponds to a radius of, for example, 125 mm of the drilled opening 23 of the lamellar ring 13. In this way, the rotor 2 forms a passing through cylindrical hollow space 6 as an intake chamber 12.

[0024] To attach the turbine circuit 20 to the drive shaft 9, connecting elements in the form of stars, not shown, are provided in the first place, which are torsionally rigidly connected to the guide shaft 9 and primarily to at least one of the lamellar rings 13. In another embodiment of the invention, the profile of the bearing surface 3 can also be placed on the inner tangential surface of the casing 4, whereby the rotor 2 then has a circular surface of the casing on the outside 4, as a result of which the flow direction returns and the outlet chamber 21 is created in the hollow space 6 of the turbine circuit 20, i.e. rotor 2.

[0025] To drive the pump 1, the rotor 2 is started with a given number of revolutions and direction of rotation 18, so that on the outer surface of the casing 4 in the direction of rotation 18 behind the convex elevation 19, a negative pressure is created according to the Bernoulli effect, i.e. pressure difference to the surrounding gas or liquid medium, as a result of which the medium is sucked outwards from the inner space 6 with a higher pressure. At the same time, the pressure difference depends mainly on the number of revolutions, i.e. the speed of the turbine circuit 20. The pressure difference increases linearly until, while the creation of vortices on the breaking edge or in other vortex elements increases so much, that it results in a nominal back pressure. It can be reduced, however, primarily by forming a special tear edge and creating circular intake 12 and exhaust chambers 21, so that at a speed of at least 10,000 U/min. there is a linear increase in pressure.

[0026] The high differential pressure can simultaneously increase the amount of flow per unit of time, which is however limited by the cross-sectional area of the flow openings 5. In any case, the amount of flow, that is, the volume of flow can be increased in a simple way and by increasing the upper surface of the profile of the bearing surface 3. Basically, the pressure difference can already be produced with only one profile of the bearing surface 3 on the circumference of the rotor 2, i.e. turbine circuit 20. In order to increase the quantity and to improve the rotating ratio, mainly nine profiles of the bearing surface 3 are located in a circle around the tangential outer casing of the rotor 4, whereby a larger number of profile surfaces is also possible. The rotor 2 of this type with at least one profile of the bearing surface 3 does not have to be cylindrical, but can also have the outer surface of the envelope 4 in the shape of a ball or cone. At the same time, the rotor 4 of this type does not need the final intake 12 and exhaust chambers 21, since the rotation inside the gas or liquid medium without the housing produces a pressure difference, which is useful only through the drain or supply line, which must be connected to only one of the inlet 12 or outlet chambers 21. The possibility of using pressure equalization is mainly determined by the way the rotary machine is made. Thus, a rotary machine with a closed inlet chamber to which it is connected via lines can be formed both as a suction machine and for gaseous media, i.e. like a vacuum cleaner. In contrast, the rotor 2 with the closed outlet chamber 21 can be usefully applied as a compressor or blower for gas medium or as a pump for transporting or equalizing the pressure of liquid media. A rotor of this type 2 can be used for the production of revolutions at the existing pressure difference of the surrounding medium as well as for the production of energy at the existing pressure differences of water or air.

[0027] In the embodiment of the invention shown in Fig. 6, several turbine circuits 20 are located axially next to each other, and they are separated from each other by special outlet chambers 21. At the same time, the four shown turbine wheels 20 are placed on a common drive shaft 9, which is placed in two bearings 8 on a stator and part of the housing. All turbine wheels 20 are surrounded by one multi-part casing 7, which has three intermediate walls 22 and thus forms four outlet chambers 21, in which there is a rotating turbine wheel 20 of the same type.

[0028] Each turbine circuit is formed like the turbine circuit 20 shown in FIG

Fig. 1 to 5 of the drawing and basically consists of nine profiles of the bearing surface 3 located on the outer surface of the casing 4, between which are provided flow openings 5 to the inner hollow space 6. In the case of the first turbine circuit 20, a first inlet opening 10 is provided to the outer region of the housing 7, in the form of a circular groove, which establishes a connection to the hollow space 6 of the first turbine circuit 20 as an inlet chamber 12. supplies the intended gas or liquid medium, so that it reaches the first, formed as a hollow space 6, the inlet chamber 12 of the first turbine wheel 20. If the rotor 2 is started with the prescribed number of revolutions, then a pressure difference occurs on the profile of the supporting wing 3 in the area of the flow opening 5, whereby the medium is sucked outward into the outlet chamber 21 that surrounds the turbine wheel 20. As a result, an elevated pressure, which acts through the second inlet opening 27 in the hollow space, i.e. the inlet chamber of the second turbine circuit 28. Through that rotating second turbine circuit 28, a pressure difference is again produced, so that the medium reaches the second outlet chamber 29 by increasing the pressure. Since the inlet opening towards the third turbine circuit is also provided in the second outlet chamber 29, a further equally large increase in pressure occurs in the next two outlet chambers, so that a four-stage pump of this type leads to a four-fold increase in pressure, as with the single-stage pump 1 with only one turbine circuit 20. One such multi-stage pump as a rotary machine can be equipped with multiple degrees of pressure increase, so that almost the desired pressure increases can be produced according to the predicted number of revolutions.

[0029] One such multistage pump as a rotary machine can also be formed with radial stages. There, several turbine wheels 20 with different outer diameters are placed coaxially one inside the other, and are set in rotation by means of a common drive shaft 9. With a rotary machine of such a coaxial structure, not only can very high pressures be produced, but also high volumes of passages per time unit are transported by the high effective upper surface of the bearing surface profile.

[0030] In Fig. 9 drawings showing a further embodiment of the invention, which shows a drive turbine primarily for a liquid medium. A single-stage cylindrical rotor 2 with bearing surface profiles 3 located on its outer surface and flow openings 5 to its hollow space, which is located in a cylindrical housing, is provided for this purpose. The housing 7 contains an inlet opening 10 at one of its axial ends and an exhaust opening 11 at one of its axial ends, which are formed in the shape of a bottle neck. The rotor 2 located in the housing 7 drives the shaft 9 through its inlet opening 10, through which the liquid medium is supplied in the first place, such as e.g. water. By rotation, the water is sucked into the surrounding housing as an outlet chamber 21, so that an overpressure is created in it, which exits from the narrow, rotationally favorable outlet opening 11 in the shape of the neck of the bottle, into the surrounding medium. Already according to the number of revolutions of the drive and the cross-sectional area of the outlet opening 22, the water circulates at a certain flow rate into the surrounding water, which produces a turbine-like kickback effect. In this way, water vehicles can be started in the first place or liquids with high pressure can be emitted depending on the direction into media of the same type or other media.

Claims (20)

1. A rotor for a rotating machine, which circulates in a gaseous or liquid medium and which has a profile (3) on at least one of its envelope surfaces (4) with at least one convex elevation (19) for producing a pressure difference, wherein the convex elevation (19) is formed as a profile of the bearing surface (3), and the rotor (2) is connected to at least one chamber (12,21) for the supply or removal of the medium, indicated that the rotor (2) has an axial hollow space (6) inside and provides at least one through opening (5) between the hollow space (6) of the outer casing (4) in the area of the bearing surface profile (3). 2. The rotor according to claim 1, characterized by the fact that it contains at least one turbine wheel (20) and one shaft (9), torsionally rigidly connected to it and which can be rotatably placed in a stator (7). 3. The rotor according to claim 1 or 2, characterized in that the turbine wheel (20) is formed mainly in the form of a cylinder and shows a cylindrical hollow space (6) inside, wherein the profile of the bearing surface (3) is located either on the outer surface of the casing (4) or on the inner surface of the casing. 4. The rotor according to one of the previous requirements, indicated by the fact that at least one profile of the bearing surface (3) is located axially and tangentially on one of the surfaces of the casing (4) of the turbine wheel (20), wherein the profile of the bearing surface (3) has at least one radial convex elevation (19), which, contrary to the direction of rotation (18), passes into a longitudinal falling off exit region (24) whose distance from the rotating shaft (26) decreases with the outer of the surface of the casing (4) and increases at the inner surface of the casing, whereby at least one flow opening (5) towards the inner hollow space (6) is placed on or in its end area. 5. A rotor according to one of the preceding claims, characterized in that the turbine wheel (20) consists of metal, plastic, glass fibers or ceramics. 6. The rotor according to one of the previous claims, characterized in that the turbine wheel (20) has a lamellar structure and consists of at least one lamellar ring (13), with at least one profile of the bearing surface (3) and one arrangement of at least one lamellar element (14) with one profile of the bearing surface (3), which are axially equally connected to each other, wherein the lamellar elements (14) are tangentially spaced so far from each other, that they form at least one flow opening (5). 7. The rotor according to one of the previous claims, indicated by the fact that the convex elevation (19) describes a partially circular surface with a given radius, which, contrary to the direction of rotation (18), passes into the waste outlet region (24), which flows in a straight line, slightly convex or slightly concave and in whose area or at the end of which the flow opening (5) is located. 8. The rotor according to one of the previous claims, characterized by the fact that the waste outlet region (24) is shaped slightly concave and at the end of which there is a tip (25) in the form of a modulator directed radially outwards as a breaking edge. 9. The rotor according to one of the previous claims, indicated by the fact that the turbine wheel (29) is shaped axially and multi-stage, and in the direction of the rotating shaft (26) there are several spaced turbine wheels (20,28) located axially one after the other, which act as a separate turbine wheel (20,28), and they are torsionally rigidly connected to each other or to the shaft (9). 10. The rotor according to one of claims 1 to 8, characterized in that the turbine wheel (20) is formed in a radially multi-stage manner, whereby several turbine wheels (20) of different diameters are placed coaxially with each other and symmetrically to the axis of rotation (26), and are rigidly connected to each other and/or to the shaft (9). 11. A rotating machine with a rotor according to one of claims 1 to 10, characterized in that it has a casing (7) as a stator in which the rotor is placed, which either with the outer surface casing (4) and/or the inner casing of the rotor (2) forms at least one chamber (12, 21), which during rotation shows a pressure difference to the surrounding gas or liquid medium. 12. A rotating machine according to claim 11, characterized in that the housing (7) as a chamber (12, 21) in which the medium is supplied forms an inlet chamber (12) and as a chamber in which the medium is removed forms an exhaust chamber (21). 13. A rotating machine according to claim 11 or 12, characterized by the fact that it contains at least one rotor (2), whose outer surface of the casing (4) is surrounded by a part of the housing (7) which together with it forms an inlet (12) or exhaust chamber (21) on the rotor (2) and has at least one inlet (10) and/or outlet opening (11). 14. The rotating machine according to claim 11 or 12, characterized in that it has at least one rotor (2), whose inner space (6) is covered by at least one part of the housing (7) and with the hollow space (6) forms one inlet (12) or exhaust chamber (21) and has at least one inlet (10) and/or outlet opening (11). 15. A rotating machine according to claim 11 or 14, characterized in that it has at least one inlet (12) or exhaust chamber (21), wherein each chamber (12,21) has one inlet (10) or outlet (11). 16. A rotating machine according to claim 11 or 15, characterized in that it contains at least one rotor (2) with one axial multi-stage turbine circuit (20, 28) and whose outer surfaces of the casing (4) are surrounded by a special part of the housing (7, 22), which always has an inlet opening towards the next stage with another part of the turbine circuit (28) or has an inlet (10) or an outlet opening (11). 17. A rotating machine according to one of claims 11 to 15, characterized in that it contains at least one rotor (2) with one radially multistage turbine circuit, which is surrounded by a common part of the housing (7) and/or whose hollow spaces (6) are covered by at least one part of the housing (7), wherein at least one part of the housing (7) is provided with one inlet (10) or outlet opening (11). 18. A rotating machine according to one of claims 11 to 17, characterized in that it is formed as a drive turbine and contains at least one rotor (2) with a turbine wheel (20), which is surrounded by a cylindrical part of the housing (7) and includes the rotor (2), and contains one axial inlet opening (10) for the supply of gas or liquid medium and for the introduction of the shaft (9) and at the opposite axial end of which there is one outlet opening in the shape of a bottle neck (11). 19. A rotating machine according to one of claims 11 to 17, characterized in that it is formed as a pump, compressor, condenser, turbine, turbo-machine or pressure neutralizer. 20. A rotating machine according to one of claims 11 to 17, characterized in that it is made for the production of revolutions using a gas or liquid medium, which contains an inlet chamber (12) for a directed supply under pressure of a gas or liquid medium, which is formed in such a way that the flow direction is directed towards the convex elevation (19) of the rotating rotor (2).