EP1623098A2

EP1623098A2 - Thermal combustion engine which converts thermal energy into mechanical energy and use thereof

Info

Publication number: EP1623098A2
Application number: EP04725274A
Authority: EP
Inventors: Wolfgang Heddrich; Hans Lautner; Lars Hein; Matthias Losch; Bernhard Renner
Original assignee: Fachhochschule Darmstadt
Current assignee: Fachhochschule Darmstadt
Priority date: 2003-04-04
Filing date: 2004-04-02
Publication date: 2006-02-08
Also published as: WO2004092547A2; US20070151246A1; WO2004092547A3; DE10315746B3; CA2521654A1; JP2006522256A

Abstract

The invention relates to a thermal combustion engine which converts thermal energy into mechanical energy, comprising at least one vapour producing device which at least partially vaporises a first liquid working medium by means of thermal energy supplied to the combustion engine, at least one rotor (11) which can be driven by means of a vaporised first working medium in order to produce mechanical energy and rotated with respect to at least one stator (3) around a first rotational axis, and at least one condensation device for condensation of the vaporised first working medium after the rotor (11) has been driven. The rotor (11) surrounds the stator in an essentially complete manner. The invention also relates to the use of the inventive thermal combustion engine.

Description

Heat engine for converting thermal energy into mechanical energy and using the same

description

The present invention relates to a heat engine for converting thermal energy into mechanical energy and the use of such a heat engine.

A large number of heat engines are known from the prior art. For example, DE 199 48 128 AI discloses a device and a method for generating flow energy in liquids from heat. The device comprises a housing with a steam inlet opening connected to an evaporator and a steam outlet opening connected with a condenser. Furthermore, the housing has a flow opening connected to a hydraulic motor and a return connection connected to the same. A rotor is arranged within the housing and has a plurality of cells, in each of which pistons are located. Pumping a hydraulic fluid through the hydraulic motor is achieved by supplying steam under pressure through the steam inlet opening, removing the steam from the steam outlet opening and rotating the rotor. However, a disadvantage of this device is that it is structurally complex and, owing to its multi-component structure, has a large installation space and therefore cannot be made compact. In addition, a pump is required in particular to feed liquid condensed in the condenser back to the evaporator.

Furthermore, US 2002/0194848 AI discloses a steam engine for driving a generator. The steam engine comprises a rotary piston engine, which is in a closed steam circuit is integrated. The steam circuit comprises a steam generator, a steam injection for injecting steam into the rotary piston engine, and a condenser for condensing the steam that emerges from the rotary piston engine. Combustion is performed within the steam engine to supply heat to a steam generator consisting of a bundle of circular tubes. The steam emerging from the steam generator is fed to the rotary piston engine and then flows through a further bundle of tubes which serve to preheat combustion air. The partially cooled steam is fed to a condenser, and the water condensed in the condenser is then returned to the steam generator via a pump. However, a disadvantage of this steam engine is also the structurally complex structure and the low compactness due to the large number of necessary components, including a pump for conveying water condensed in the condenser into the steam generator. Furthermore, the rotary piston engine is susceptible to wear, which results in high maintenance costs.

In addition, thermal turbines comprising steam turbines are known from the prior art. Steam generated in an external steam generator is fed to these steam turbines in such a way that a rotor arranged in a housing is driven by a paddle wheel. After passing through the paddle wheel, the steam emerging from the housing is condensed and the working medium thus condensed is returned to the steam generator via a pump. However, a disadvantage of these steam turbines is that additional components, in particular valves, control elements or pumps, are necessary in order to convert thermal energy into mechanical energy. In particular, such heat engines using a steam turbine have a high power to weight ratio due to the large number of individual components, i. H. Weight relative to the removable power.

The object of the present invention is therefore to provide a heat engine which overcomes the disadvantages of the prior art. In particular, the conversion of thermal energy into mechanical energy should be achieved while achieving a low power-to-weight ratio, high efficiency, low pollutant and noise emissions and a simple, low-maintenance and low-wear construction. According to the invention, this object is achieved in a first embodiment in that the heat engine has at least one steam generating device for at least partially evaporating a first liquid working medium by means of thermal energy supplied by the heat engine, at least one that can be driven by means of the evaporated first working medium to generate mechanical energy and relative to at least one Stator rotatable about a first axis of rotation and at least one condensation device for condensing the vaporized first working medium after driving the rotor, wherein the rotor substantially completely surrounds the stator, and the rotor substantially completely comprises the steam generating device and the condensing device.

As an alternative to the embodiment described, the object according to the invention is achieved in a second embodiment, by a heat engine comprising at least one steam generating device for at least partially evaporating a first liquid working medium by means of thermal energy supplied by the heat engine, at least one by means of the evaporated first working medium for generating mechanical electrical energy. Energy drivable and rotatable relative to at least one stator about a first axis of rotation and at least one condensation device for condensing the vaporized first working medium after driving the rotor, the rotor surrounding the stator at least in regions.

In the second embodiment, it can be provided that the rotor essentially completely encompasses the steam generating device and / or the condensing device.

In the two previously mentioned embodiment, the stator according to the invention can essentially completely comprise the steam generating device and / or the condensation device.

As an alternative to the two above-mentioned embodiments, it can also be provided that the steam generating device and / or the condensing device is or are at least divided into two, and the rotor comprises a first part of the condensing device and / or a first part of the steam generating device and the stator the other part of the steam generating device and / or the condensing device. According to the invention, in an advantageous embodiment, at least one first chamber forming the steam generating device, at least one second chamber forming the condensing device and at least one turbine chamber are provided, preferably the first chamber and the second chamber, the first chamber and the turbine chamber and / or the second chamber and the turbine chamber is separated from one another at least in regions by means of at least one, in particular thermally insulating, wall.

In the aforementioned alternative embodiment, it is proposed that the heat engine have at least one first connecting device connecting the first chamber and the turbine chamber for the passage of the vaporized first working medium, preferably comprising at least one first nozzle, the geometry and / or the orientation of the nozzle opening preferably being adjustable, at least one first tube and / or at least one first opening formed in particular in the thermally insulating wall.

In the two aforementioned alternative embodiments, at least one second connecting device connecting the turbine chamber and the second chamber for the passage of the vaporized first working medium, preferably comprising at least one second nozzle, wherein preferably the geometry and / or the orientation of the nozzle opening can be adjusted, at least a second one Pipe and / or at least one, in particular formed in the thermally insulating wall, second opening may be provided.

In the two aforementioned embodiments, at least one first and / or at least one second flow control and / or regulating device that is operatively connected to the first connecting device, preferably in the form of a first and / or second valve, is proposed.

Advantageous embodiments of a heat engine according to the invention have at least one third connecting device connecting the first chamber and the turbine chamber for the passage of the liquid first working medium, in particular in the form of at least one third opening, preferably formed in the thermally insulating wall. There may also be at least one fourth connecting device connecting the turbine chamber and the second chamber for the passage of the liquid first working medium, preferably in the form of at least one fourth opening, in particular formed in the thermally insulating wall, in a heat engine according to the invention.

In the case of the two aforementioned alternatives, the invention proposes that the liquid first working medium prevent the evaporated first working medium from escaping from the first chamber through the third and / or fourth connecting device during a rotation of the rotor, in particular due to the centrifugal force acting on the working medium , in particular the third and / or fourth opening blocked.

Furthermore, at least one third flow control and / or regulating device, preferably in the form of a third and / or fourth valve, in particular a non-return valve, is at least one third and / or at least one fourth flow control and / or regulating device that is operatively connected to the third connecting device. proposed.

In particular, it can also be provided that the second chamber and the turbine chamber are formed in one.

In the aforementioned embodiments of the heat engine according to the invention, at least one flow guide body formed in the first chamber, the second chamber and / or the turbine chamber can be provided.

An advantageous embodiment of a heat engine according to the invention is characterized by at least one first paddle wheel encompassed by the stator, to which the evaporated first working medium can be supplied, preferably axially, radially and / or, preferably via the first connecting device, for rotating the rotor relative to the stator at a predetermined angle relative to the first axis of rotation.

The aforementioned embodiment of a heat engine according to the invention can be characterized by at least one that is operatively connected to the rotor, in particular can be connected to it in a rotationally secure manner, and upstream and / or downstream. the vaporized working medium relative to the first impeller is arranged flow guide wheel, wherein the flow guide wheel is preferably arranged at least in regions concentrically to the first impeller, in particular inside and / or outside of the first impeller. In particular, the arrangement of the flow guide wheel upstream of the vaporized working medium relative to the first blade wheel leads to an increase in efficiency.

The two aforementioned embodiments of the heat engine according to the invention can be characterized by at least one second blade wheel, which is comprised by the stator and is arranged, in particular, downstream of the evaporated working medium relative to the degree of flow guidance, preferably at least one with the rotor upstream and / or downstream of the evaporated working medium relative to the second blade wheel a deflecting wheel that is operatively connected, in particular connectable to this in a rotationally secure manner, the deflecting wheel in particular being arranged at least in regions concentrically with the first and / or second impeller, in particular inside and / or outside the first and / or second impeller.

In the case of the three aforementioned alternative embodiments, the invention provides in particular that the first blade wheel, the flow guide wheel, the second blade wheel and / or the deflection wheel is or are at least partially arranged in the turbine chamber.

It is also proposed that the second blade wheel have a second diameter that deviates from a first diameter of the first blade wheel and / or a number or geometry of the blades that deviate from the number or geometry of the blades of the first blade wheel.

Advantageous embodiments of a heat engine according to the invention are also characterized by a plurality of second blade wheels and / or deflection wheels, the second blade wheels preferably having different diameters, different geometries and / or a different number of blades with respect to one another, and / or the deflection wheels having different diameters, different geometries and / or have a different number of blades from one another. Provision can also be made for the geometry and / or the position of at least one blade of the first blade wheel, at least one second blade wheel, of the flow guide wheel and / or at least one deflection wheel to be adjustable, preferably during operation of the heat engine.

Furthermore, the invention proposes at least one heating means for the application of heat to the steam generating device, in particular the first chamber, preferably in the form of a fluid heating medium, in particular in the form of hot gases, such as combustion gases, a heating source, such as in the form of at least one heating spindle, which is in a, in particular a material of high thermal conductivity and / or structured for a high convective heat transport, integrated wall of the first chamber and / or is formed on the surface of this wall, at least one first flow device for a heating fluid and / or at least one on an outside of the Wall of the first chamber formed, in particular through which the heating fluid can flow, and / or at least one second structure formed on an inside of the wall of the first chamber, in particular through which the preferably evaporated working medium can flow.

In the aforementioned embodiment it can be provided that the first throughflow device is integrated into the wall, the heating medium being fed to the first throughflow device preferably via a shaft of the stator and / or that heating means in particular in a preferably closed, comprising the first throughflow device. Heating circuit is circulated.

Furthermore, the invention proposes at least one coolant for applying cold to the condensation device, in particular the second chamber, preferably in the form of a fluid cooling medium, in particular in the form of nitrogen or cold air, a cooling source, such as in the form of at least one Peltier element, which in particular in a wall of the second chamber, preferably comprising a material of high thermal conductivity and / or structured for high convective heat transport, is integrated and / or formed on the surface of this wall, at least one second flow device for a cooling fluid, such as nitrogen or cold air, and / or at least one third structure formed on an outside of the wall of the second chamber, in particular through which the cooling fluid can flow, and / or at least one fourth structure formed on an inside of the wall of the second chamber, through which the working medium can flow. It is also proposed with the invention in the above-mentioned embodiment that the second flow device is integrated in the wall, the coolant being fed to the second flow device preferably via a shaft of the stator and / or the coolant in particular in a preferably comprising the second flow device closed, cooling circuit is circulated.

In the four alternative embodiments mentioned above, it is considered advantageous with the invention that the heating fluid in the area of the heating means has a flow direction that extends essentially radially outward from the first axis of rotation to the outer circumference of the rotor, and / or the cooling fluid in the area of the Coolant has a flow direction which extends substantially radially from the outer circumference of the rotor in the direction of the first axis of rotation.

At least one supply device can also be provided for supplying at least one vaporous second working medium, the first and second evaporated working medium preferably being identical.

Furthermore, an advantageous embodiment of the invention provides at least one removal device for removing at least part of the vaporized and / or liquid first working medium.

Advantageously, at least one fifth flow control and / or regulating device that is operatively connected to the supply device and / or at least one sixth flow control and / or regulating device that is operatively connected to the removal device is provided.

Finally, with the invention at least one with the steam generating device, the condensation device, the first and / or second nozzle of the first, second, third, fourth, fifth and / or sixth flow control and / or regulating device, the first impeller, at least one second impeller , the flow guide wheel and / or at least one deflection wheel, the heating means, the coolant and / or a sensor for measuring the rotational speed of the rotor are operatively connected control and / or regulating unit. The invention further provides for the use of a heat engine according to the invention as a front-end turbine, steam turbine, counter-pressure turbine, extraction turbine, constant-pressure turbine and / or positive-pressure turbine.

The invention is therefore based on the surprising finding that the design of a steam turbine in the form of an external rotor, in which a steam generating device and a condensation device are integrated in the rotor, leads to the fact that a structurally simple construction of a heat engine can be realized. In particular, a heat engine can be provided which dispenses with control and / or delivery elements, such as valves or pumps for delivering a working medium from an evaporator to a condenser. By integrating an evaporator and condenser in a rotor, which rotates around a stator having at least one impeller, an automatic conveying of working medium from the condenser to the evaporator is achieved according to the invention via the centrifugal force acting on the working medium through the rotation. In addition, the rotary movement of the rotor and thus the centrifugal force acting on the working medium ensures that the working medium itself closes a connecting channel running from the condenser to the evaporator in such a way that steam generated in the evaporator can only get into the condenser by leaving it Evaporator emerges, impacts the impeller and thus causes the rotor to rotate. In particular, the centrifugal force acting on the working medium due to the rotation of the rotor has the effect that even at higher pressures within the steam generator relative to the pressure in the condenser, due to the hydrostatic pressure caused by the centrifugal force, a transition of the vaporous working medium from the steam generator into the condenser only in the way described above is made possible after passing through the paddle wheel. That is, the construction of a heat engine according to the invention realizes a centrifugal lock between the condenser and the evaporator. This centrifugal lock also serves as a pump to convey working medium from the condenser to the evaporator. This means that there is no need for additional feed pumps, etc. In addition, the construction of the steam turbine as an external rotor enables the thermal engine to be highly efficient. Both heating of the machine on the evaporator side, for example with combustion gases, and cooling on the condenser side, for example with cooling air, are preferably carried out according to the invention in the countercurrent principle, with any other flow directions of the cooling or heating mediums are possible. Efficient utilization of the combustion gases is achieved in that high-temperature combustion gases heat the area near the axis of the rotor and thus particularly hot steam escapes from the steam generator, which is then directed in particular onto the stator's impeller via nozzles. The combustion gases then flow in the radial direction from the axis of rotation of the rotor to the outer circumference of the rotor, where the cooling combustion gases bring the liquid working medium located there due to the centrifugal force to the boil on the outer circumference of the rotor. The steam generated in the process migrates in the direction of the axis of rotation of the rotor and is continuously heated due to the temperature of the combustion gases, which is increasing in this direction, so that, for example, isobaric expansion can take place. On the condenser side, the cooling air flows from the outer circumference of the rotor in a radial direction to the axis of rotation of the rotor, outside the rotor. The result is that steam that flows radially inside the rotor from the axis of rotation to the outside is increasingly cooled and condensed. Thus, the construction of the heat engine according to the invention as a steam turbine based on the external rotor principle enables the use of a countercurrent principle both for heating a working fluid and for cooling it, which leads to an increase in the efficiency of the heat engine.

Further features and advantages of the invention result from the following description, in which preferred embodiments of the invention are explained by way of example with reference to schematic drawings. It shows:

Figure 1 is a sectional view of a first embodiment of an inventive

Heat engine;

Figure 2 is a sectional view of the heat engine of Figure 1 along the plane A-

A of Figure 1;

Figure 3 is a sectional view of a second embodiment of an inventive

Heat engine;

FIG. 4 shows a sectional view of the heat engine of FIG. 3 along the plane B -

B of Figure 3; Figure 5 is a sectional view of a third embodiment of an inventive

Heat engine;

FIG. 6 shows a sectional view of the heat engine of FIG. 5 along the plane B -

B of Figure 5;

Figure 7 is a sectional view of a fourth embodiment of an inventive

heat engine;

Figure 8a is a sectional view of a fifth embodiment of an inventive

Heat engine;

Figure 8b is a sectional view of a modification of the fifth embodiment of a heat engine according to the invention according to Figure 8a;

Figure 9 is a sectional view of a sixth embodiment of an inventive

Heat engine;

Figure 10 is a sectional view of a seventh embodiment of an inventive

Heat engine; and

Figure 11 is a sectional view of an eighth embodiment of an inventive

Heat engine.

FIGS. 1 and 2 show a first embodiment of a heat engine according to the invention in the form of a steam turbine 1, or rather a compact steam turbine, with an integrated steam generation zone. The steam turbine 1 comprises a stator 3, which in turn comprises a fixed shaft 5 and a blade wheel 7 connected to the shaft 5. Via a bearing 9 and a seal 10, a rotor 11 with end walls 11a, 11c and a peripheral wall 11b is rotatably mounted relative to the stator 3 in such a way that the interior of the rotor 11 is sealed. The rotor 11 essentially consists of a first chamber 13 and a second chamber 15. The chambers 13, 15 are separated from one another by a thermally insulating wall 17, apart from openings 19 in the wall 17 in the region of the peripheral wall 11b of the rotor 11 Openings 19 can be a working medium 21, preferably Water flow from the second chamber 15 into the first chamber 13 as described in detail later. Due to the centrifugal forces acting on the working medium 21 when the rotor 11 rotates, the working medium 21 collects on the peripheral wall 11b of the rotor 11, as shown in FIGS. 1 and 2. The first chamber 13 is further separated by a partition 23 from a turbine chamber 25 in which the impeller 7 is arranged. Openings in the form of nozzles 27 are formed within the partition 23. The mode of operation of the steam turbine 1 is now explained below:

Combustion gases 29 of a heating device (not shown) are fed to the rotor 11 on the first end wall 11a arranged on the side facing the first chamber 13. As can be seen in FIG. 1, the combustion gases 29 are fed in such a way that they are guided radially outward along the rotor 11 from the axis of rotation thereof. The combustion gases 29 heat the first end wall 11a of the rotor 11, which causes the working medium 21 in the region of the first chamber 13 to heat up, which ultimately leads to at least partial evaporation of the working medium 21 in the first chamber 13 leads. The first chamber 13 thus acts as a steam generation chamber. By regulating the heat supply by means of regulating or regulating the amount of combustion gas 29 supplied or its temperature, the power output or the speed of the steam turbine 1 can be controlled or regulated.

In order to enable efficient heat exchange between the combustion gases 29 and the interior of the first chamber 13 or steam generation chamber, are located on the first end wall 11a of the rotor 11 in the region of the first chamber 13, preferably both on the side facing the combustion gases 29 and on that side the side facing the first chamber 13, not shown heat exchanger elements through which the combustion gases 29 or the working medium 21 evaporated in the first chamber 13 flow. In particular, the first end wall 11a of the rotor 11 comprises a material with high thermal conductivity.

The evaporated working medium 21 travels within the first chamber 13 from the peripheral wall 11b to the axis of rotation of the rotor 11. A counterflow principle is thus implemented in the steam turbine 1. This leads to an efficient use of the energy of the combustion gases 29. The combustion gases 29 of high temperature meet that of the rotary Axis of the rotor 11 facing the first chamber 13, so that particularly hot steam is generated in this area. The combustion gases 29 migrating in the radial direction of the rotor 11 then cool further and bring the working medium 21 to a boil in the region of the peripheral wall 11b of the rotor 11. An efficient use of the thermal energy of the combustion gases 29 is thus achieved.

The working medium 21 which is heated in the region of the peripheral wall 11b of the rotor 11 flows through the first chamber 13 or steam generation chamber in the direction of the partition wall 23, whereby it expands isobarically. An increased internal pressure thus arises within the first chamber 13, which is noticeable in that the level of the working medium 21 in the region of the first chamber 13 is lower than that in the second chamber 15. The steam generated in this way in the first chamber 13 flows through the nozzles 27 and is expanded adiabatically. As can be seen in particular in FIG. 2, the nozzles 27 are not aligned radially, but rather inclined, so that an optimal angle of inclination of the nozzles 27 can be set. The steam therefore strikes the impeller 7 in such a way that the rotor 11 recoils relative to the stator 3, which produces or maintains a rotary movement of the rotor 11.

After passing through the impeller 7, the steam from the turbine chamber 25 enters the second chamber 15, which serves as a condensation chamber. There, the steam cools down and thus the working medium 21 condenses out in the region of the second chamber 15.

Due to the rotation of the rotor 11, condensed working medium 21 collects on the peripheral wall 11b of the rotor 11. In order to cool the vaporous working medium 21 in the second chamber 15, which acts as a condensation chamber, cooling air 31 becomes the second end face 11c of the rotor 11 fed. This supply also takes place in the counterflow principle. Cold air flows as cooling air from the outside of the rotor 11 in the radial direction to the axis of rotation of the rotor 11. The cooling air 31 is heated. In contrast, the vaporous working medium 21, which flows radially away from the axis of rotation of the rotor 11 in the interior of the second chamber 15, is increasingly cooled and condenses in the process. Since the already heated cooling air 31 can thus absorb further thermal energy in the region of the axis of rotation of the rotor 11, a convective heat exchange between the working medium 21 and the cooling medium 31 being supported by a structuring of the wall 11c, not shown, preferably in the form of heat exchanger elements ensures efficient heat dissipation from the second chamber 15. The working medium 21 condensed out in the second chamber 15 then flows through the openings 19 in the wall 17 into the first chamber 13, where it is in turn evaporated.

Due to the centrifugal force acting on the working medium 21, the latter is accelerated to the outside and thus closes the openings 19, so that steam from the first chamber 13 can only enter the second chamber 15 through the nozzles 27. Even with a higher pressure in the first chamber 13 relative to the pressure in the second chamber 15, a secure closure of the openings 19 for steam generated in the first chamber 13 of the working medium 21 is ensured, because due to the hydrostatic pressure caused by the centrifugal force, the Openings 19 are kept closed by the working medium 21.

In order to ensure that the steam turbine 1 can start up independently, check valves 19 can be arranged within the openings. These have the effect that steam, which is initially generated in the first chamber 13, causes the rotor 11 to rotate through the outlet through nozzles 27, so that the openings 19 are sealed by the working medium 21 after the start of the rotation. In addition, closure devices, such as valves, can also be provided in the nozzles 27 in order to achieve control of the rotational speed of the rotor 11. It can in particular be provided that the valves in the openings 19 and the nozzles 27 are connected to a control and regulating device, not shown. Furthermore, speed control or regulation of the steam turbine 1 is possible by varying the amount of thermal energy supplied by means of the combustion gases 29 and / or by varying the angle of inclination of the nozzles 27.

FIGS. 3 and 4 show a second embodiment of a heat engine according to the invention in the form of a steam turbine 1 ', or rather a compact steam turbine, with an integrated steam generation zone. The basic structure of the steam turbine 1 'corresponds essentially to the structure of the steam turbine 1 shown in FIGS. 1 and 2. In contrast to the steam turbine 1, the corresponding elements in the steam turbine 1' are denoted by the same reference numerals, but deleted once. The steam turbine 1 'essentially differs from the steam turbine 1 in that the flow of the vaporized or liquid working medium 21' is different. Similar to the steam turbine 1, combustion gases 29 'are supplied to the rotor 11' of the steam turbine 1 'on the side of the first end wall 11a' arranged on the side facing the first chamber 13 '. leads. As can be seen in FIG. 3, this feed also takes place in the counterflow principle. The combustion gases 29 'cause the working medium 21' present in the first chamber 13 'to heat up. In contrast to the steam turbine 1, however, this evaporated working medium 21 'only flows after a deflection by almost 180 ° by means of a flow guide body 14' through nozzles 27 'into the turbine chamber 25' or the second chamber 15 '. This deflection around the flow guide body 14 'offers the particular advantage that entrained droplets of the working medium 21' cannot follow the steam flow around the flow guide body 14 'and thus do not reach the turbine chamber 25' or the second chamber 15 'via the nozzle 27' can. The entrained droplets flow with the steam flow in the direction of the axis of rotation of the rotor 11 ', but continue to move in the radial direction and hit the flow body 14', as a result of which they are accelerated in the direction of the peripheral wall 11b 'due to the acting centrifugal force. It is also achieved by the flow guide body 14 'that the evaporated working medium 21' can flow essentially up to the axis of rotation of the rotor 11 'within the first chamber 13', and thus a maximum heat transfer of the energy of the combustion gases 29 'to the working medium 21 'can be done.

After the vaporous working medium 21 'has been deflected, it flows through nozzles 27' in the radial direction onto the impeller 7 '. The vaporous working medium 21 'then flows within the second chamber 15' in the vicinity of the shaft 5 'in the direction of the end wall 11c'. This flow guidance is achieved in particular by a flow guidance body 16 'arranged in the second chamber 15' in the region of the impeller 7 '. This flow control ensures that the vaporous working medium 21 'flows in the counterflow principle relative to the cooling air 31' on the inside of the end wall 11c 'in the direction of the peripheral wall 11b'. In addition, the flow guidance within the steam turbine 1 'has the advantage that, in comparison to the steam turbine 1, a blade wheel 7' can be used which has a larger diameter than the blade wheel 7 of the steam turbine 1. The steam turbine 1 'can thus be operated at lower speeds.

The working medium 21 'condensed out in the second chamber 15' collects due to the rotational forces on the peripheral wall 11b 'and flows back through channels 20' into the first chamber 13 '. The channels 20 'are formed by the circumferential wall 11b' on the one hand and an essentially cylindrical partition wall 24 ', which in particular comprises the guide guide bodies 14' and 16 '. The partition 24 'is in particular in the area of Channels 20 'are designed to be thermally insulating in order to avoid heating of the working medium 21' within the channels 20 '.

FIGS. 5 and 6 show a third embodiment of a heat engine according to the invention in the form of a steam turbine 1 ″, or rather a compact steam turbine. The basic structure of the steam turbine 1 ″ essentially corresponds to the construction of the steam turbine 1 ′ shown in FIGS. 3 and 4. , The elements of the steam turbine 1 "which correspond to those of the steam turbine 1 'have the same reference numerals. The steam turbine 1" differs from the steam turbine 1' essentially in that a paddle wheel 7 "is provided which is connected to at least one connecting member 6" a shaft 5 "of the stator 3" is connected. As can be seen in particular from FIG. 6, the paddle wheel 7 "concentrically surrounds a flow guide wheel 8" which is connected to the wall 17 "and thus to the rotor 11" via connecting members 18 ", as can be seen in particular from FIG 6, the impeller 7 has "blades 28", while the flow guide wheel 8 comprises "blades 30". This arrangement of the flow guide wheel 8 "relative to the blade wheel 7" results in a further increase in the efficiency of the steam turbine 1 "compared to the steam turbine 1 'achieved. The working medium 21 'emerging from the nozzle 27 "first strikes the blades 28" of the impeller 7 ", which leads to a drive of the rotor 11" relative to the stator 3 "with which the impeller 7" is connected. The working medium emerging from the paddle wheel 7 "strikes the blades 30" of the flow guide wheel 8 ", which is connected to the rotor 11". The flow guide wheel 8 "thus also converts the remaining energy present in the working medium, at least partially, into kinetic energy of the rotor 11".

The steam turbines 1, 1 ', 1 "shown in FIGS. 1 to 6 are single-stage radial turbines, since only one paddle wheel 7, 7', 7" is provided in each case, and the steam also radially onto the paddle wheel 7 "7 ', 7". In contrast to this, FIG. 7 shows a fourth embodiment of a heat engine according to the invention in the form of a steam turbine 51, or better, multi-stage axial turbine, which is constructed as a constant pressure turbine, that is to say working according to the Curtis principle. Constant pressure turbines are steam turbines in which the inlet and outlet pressure of the vapor of a working medium into or out of the rotor blades of a paddle wheel is the same. Reduced steam driven in the blades. In particular, it is provided that the steam turbine has 51 speed levels, that is, the speed of the steam is used in stages. In order to achieve a higher thermodynamic efficiency, it is also provided in such constant pressure turbines that pressure stages are generated, that is to say a pressure drop is divided into several stages. This has the advantage that excessive steam speeds can be avoided.

The steam turbine 51 has a stator 53 which comprises a shaft 55. Paddle wheels 57a and 57b are spaced apart from one another on the shaft 55. A rotor 61 is provided in the steam turbine 51 rotatably relative to the stator 53 via a bearing 59 and seals 60. The rotor 61 has a first end wall 61a, a conversion wall 61b and a second end wall 61c. Furthermore, a first chamber 63, which serves as a steam generation chamber, and a second chamber 65, which serves as a condensation chamber, are formed within the rotor 61. In addition, the steam turbine 51, in contrast to the steam turbine 1, has an equalizing chamber 67 for collecting liquid working medium 73. The first chamber 63 and the compensation chamber 67 are separated from one another by a thermally insulating wall 69.

Similar to the steam turbines 1, 1 ', 1 ", combustion gases 71 are fed in the steam turbine 51 to the first end wall 61a of the rotor 61 in a countercurrent principle. This causes at least part of the working medium 73 to evaporate within the first chamber 63. The working medium 73 thus evaporated is first fed to the first impeller 57a via lines 75, at the end of which nozzles 77 are arranged, because of the expansion of the steam in the region of the nozzles 77 and the impact of the steam on the first impeller 57a, the rotor 61 rotates.

In order to be able to fully utilize the energy inherent in the vaporous working medium, it is provided in the steam turbine 51 that the steam directed axially onto the first blade wheel 57a enters a deflection wheel 79a which also rotates with the rotor 61 after passing through the first blade wheel 57a , This deflection wheel acts in particular as an impeller and converts the energy inherent in the steam into working energy. In the deflection wheel 79a there is then also a deflection of the steam flow, before it then essentially hits again in the axial direction with respect to the axis of rotation of the rotor 61 on a second paddle wheel 57b, which is also connected to the shaft 55. After passing through The steam passes through the second paddle wheel 57b into a second deflection wheel 79b, which is also used in particular as an impeller and which is also connected to the rotor 61. The steam then enters the second chamber 65, where it is cooled and condensed out by means of cooling air 81 due to the cooling of the second end wall 61c of the rotor 61. The condensed working medium 73 then flows from the second chamber 65 via the equalization chamber 67 into the first chamber 63. The working medium 73 flows through channels 83 which are formed between the peripheral wall 61b and a substantially cylindrical partition 85. The partition wall 85 serves for thermal insulation of the area in which the paddle wheels 57a, 57b and the deflection wheels 79a, 79b are located, on the one hand, and the peripheral wall 61b or the channels 83, on the other hand. For this purpose, the partition 85 has a low thermal conductivity. In particular, it can be provided that the partition 85 is hollow, in particular comprises an insulating material.

FIG. 8a shows a fifth embodiment of a heat engine according to the invention in the form of a multi-stage steam turbine 51 '. The basic structure of the steam turbine 51 'essentially corresponds to that of the steam turbine 51 shown in FIG. 7. Therefore, essentially identical components of the steam turbine 51' bear the same reference numerals, but deleted once, as that of the steam turbine 51. In contrast to the steam turbine 51, the steam turbine 51 ' Steam turbine 51 'three paddle wheels 57a', 57b 'and 57c'. Accordingly, the steam turbine 51 'also has three deflection wheels 79a', 79b 'and 79c', which are each connected to the rotor 61 '. Furthermore, the steam turbine 51 'differs from the steam turbine 51 in that it is an overpressure turbine due to the geometry of the nozzles 77', the paddle wheels 57a ', 57b', 57c 'and the deflection wheels 79a', 79b 'and 79c'. Since the steam flows through the paddle wheels 57a ', 57b', 57d 'at an inclined angle relative to the axis of rotation of the rotor 61', the steam turbine 51 'is also a diagonal turbine. The design as an overpressure turbine means that the steam emerges from the nozzles 77 'at a relatively high pressure, and there is a pressure drop in the steam pressure in the blades of the blade wheels 57a', 57b 'and 57c'. This results in an energy conversion of the steam in the blades of the paddle wheels 57a ', 57b', 57c ', which is composed of the speed conversion of the steam and additionally the back pressure that occurs when the steam relaxes. Therefore, a plurality of pressure stages are formed within the steam turbine 51 ′, which have a low stage pressure gradient and thus achieve a favorable flow design and a good dynamic efficiency. 8b shows a modification of the steam turbine 51 'shown in FIG. 8a in the form of the steam turbine 51 ". The basic structure of the steam turbine 51" essentially corresponds to that of the steam turbine 51' and identical elements of the steam turbine 51 "compared to the steam turbine 51 ' bear identical reference numerals. The steam turbine 51 "essentially differs from the steam turbine 51 'in that it has a geometrically different configuration of the impellers 57a", 57b ", 57c", the deflection wheels 79a ", 79b" and 79c "and the partition 85" Paddle wheels 57a ", 57b", 57c "each differ from one another by different diameters. In addition, the geometry of the blades of the blade wheels 57a ", 57b", 57c "differs in order to form speed or pressure stages within the steam turbine 51". Accordingly, the shape of the partition 85 "and the shape of the second chamber 65" are adapted to these different diameters. In addition, the lines 75 "and the nozzles 77" are also adapted in comparison to the steam turbine 51 'to the different geometry of the impeller 57a ". Finally, the deflection wheels 79a", 79b "and 79c" are designed such that by They included blades to guide the working medium 73 "flowing through the blade wheels 57a", 57b ", 57c" diagonally relative to the axis of rotation of the rotor 61 ".

The embodiments of a heat engine according to the invention shown in FIGS. 1 to 8b are characterized jointly in that the rotor essentially completely the steam generating device in the form of the chambers 13, 13 ', 63, 63' and the condensation device in the form of the chambers 15, 15 ' , 65, 65 '. Embodiments of a heat engine according to the invention are now described with reference to FIGS. 9 to 11, in which the steam generating device or the condensing device are essentially completely or partially encompassed by the stator. These heat engines also have the advantages that they have a low power-to-weight ratio, high efficiency, low pollutant and noise emissions as well as a simple, low-maintenance and low-wear construction. In particular, these heat engines constructed as external rotors also have the advantage that the centrifugal force has the effect that a centrifugal force lock is implemented between the condenser and the evaporator, so that additional feed pumps can also be dispensed with. FIG. 9 shows a sixth embodiment of a heat engine according to the invention in the form of a steam turbine 101, or rather a compact steam turbine, with an integrated steam generation zone. The construction of the steam turbine 101 is similar to that of the steam turbine 1 ″ shown in FIGS. 5 and 6. The steam turbine 101 thus comprises a stator 103, which in turn comprises a fixed shaft 105. In contrast to the embodiments according to the invention shown in FIGS. 1 to 8a an end wall 107 of the steam turbine 101 is connected to the shaft 105, and thus forms part of the stator 103. Via the end wall 107, the shaft 105 is also connected to a first impeller 109 and a second impeller 111. In contrast, a circumferential wall 113 and an end wall 115 rotatably mounted relative to the stator 103. These walls 113, 115 thus form a rotor 117. Partition walls 119, 121 and 123 are also connected to the rotor so as to be secured against rotation, and a flow guide wheel 125 is also arranged on the partition wall 121. This flow guide wheel 125 is connected via a Bearing 127 is rotatably supported on shaft 105. However, the flow guide is supported gsrades 125 on shaft 105 not absolutely necessary. In particular, the rotor 117 can be adequately supported by the sealing devices 133, so that the bearing 127 can be dispensed with. The interior of the steam turbine 101 is divided into a first chamber 129 and a second chamber 131 by means of the, preferably thermally insulating, wall 121. Chamber 129 acts as a steam generation chamber, while chamber 131 serves as a condensation chamber. The second chamber 131 is sealed in the region of the transition from the end wall 107 to the peripheral wall 113 by a sealing device 133. This sealing device 133 can be designed in a form which is generally known to the person skilled in the art. The sealing device 133 can in particular comprise sealing elements, such as in the form of O-rings and / or a labyrinth system. It is important for the functioning of the steam turbine 101 that the sealing device 133 ensures a seal of the second chamber 131 and at the same time enables the rotor 117 to rotate relative to the stator 103. It is thus achieved in the steam turbine 101 that the steam generating device in the form of the chamber 129 is essentially completely surrounded by the rotor 117, while the condensation device in the form of the second chamber 131 with the end wall 107 is essentially completely surrounded by the stator 103.

The mode of operation of the steam turbine 101 is now explained below. Similar to the previously illustrated embodiments, combustion gases 135 hit the end wall 115 in the countercurrent principle. This causes the first chamber 129 to heat up, which is why leads to a working medium 137 being evaporated. The working medium 137 enters between the partitions 121, 123 and through the nozzles 139 into the second chamber 131. There, the evaporated working medium strikes the first impeller 109, which leads to a drive of the rotor 117 relative to the stator 103. After passing through the first vane wheel 109 connected to the stator 103, the evaporated working medium strikes the flow guide wheel 125 connected to the rotor 117, as a result of which the rotor 117 is driven further. After exiting the flow guide wheel 125, the working medium finally at least partially meets the second paddle wheel 111, which is connected to the stator 103 via the end wall 107. In order to achieve condensation of the working medium in the region of the second chamber 131, the side facing away from the chamber 131 flows Front wall 107 cooling air 141 along the counterflow principle. The condensed working medium collects due to the rotational movement of the rotor 117 in the region of the peripheral wall 113, in the region between the end wall 107 and the partition wall 119 driving elements, not shown, are preferably arranged in the form of blades that rotate with the rotor 117, in particular are attached to this. However, these entrainment elements are not absolutely necessary, but they increase the operational safety of the centrifugal lock by the working medium 137. The working medium 137 then flows back between the peripheral wall 113 and the partition wall 119 into the first chamber 129. The working medium 137 also ensures in the steam turbine 101 that a seal is achieved between the first chamber 129 and the second chamber 131 in the region of the partition wall 119 and the peripheral wall 113, so that the working medium 137 is always the way out of the nozzle 139 must go first chamber 129 into the second chamber 131. The steam turbine 101 offers the advantage that the end wall 107 does not perform any rotational movement, which leads to a particularly laminar flow of the cooling air 141 along the end wall 107. Thus, the efficiency of the condensation device in the form of the second chamber 131 and thus the efficiency of the steam turbine 101 is increased. Furthermore, this construction of the steam turbine 101 facilitates the supply of a cooling medium into the end wall 107. It can thus be provided that the end wall 107 is penetrated by flow devices, not shown, in the form of channels. These channels can in particular be part of a closed cooling circuit in which a cooling fluid, such as water, is circulated. Because the end wall 107 is connected to the shaft 105 of the stator 103, this cooling medium can be supplied through a channel arranged on or passing through the shaft 105. The efficiency of the steam turbine 101 can be increased further by this further cooling possibility. FIG. 10 shows a seventh embodiment of a heat engine according to the invention in the form of a steam turbine 101 ', or rather a compact steam turbine, with an integrated steam generation zone. The structure of the steam turbine 101 'essentially corresponds to that of the steam turbine 101, which is shown in FIG. 9. In particular, the steam turbine 101 ′ can have the entrainment devices described in relation to the steam turbine 101 in the region of the dividing wall 119 and the end wall 107. Elements of the steam turbine 101 'which are identical to the steam turbine 101 have the same reference numerals, while different elements are simply denoted by the same reference number. The structure of the steam turbine 101 'essentially differs from the structure of the steam turbine 101 in that both the condensation device and the steam generating device are essentially completely comprised by a stator 103'. The stator 103 'comprises a shaft 105' which is connected both to the end wall 107 and to an end wall 115 '. The end wall 115 'is therefore not encompassed by the rotor 117'. The rotor 117 'essentially comprises the peripheral wall 113', which is connected to the partition walls 119, 121, 123. The flow guide wheel 125 is also attached to the partition 123. To seal the first chamber 129 ', which serves as a steam generating device, the peripheral wall 113' is connected to the end wall 115 'via a sealing device 143'. This structural design of the steam turbine 101 'ensures that, in addition to the end wall 107, the end wall 115' also remains stationary when the steam turbine 101 'is in operation. This increases the efficiency of the steam generating device 129 'since the combustion gases 135 supplied to the end wall 115' are not swirled. A better heat exchange with the first chamber 129 'is thus achieved and the efficiency of the entire steam turbine 101' is further increased. A further increase in the efficiency of the steam turbine 101 'can be achieved in that the end wall 115' comprises a further throughflow device in the form of channels penetrating the end wall 115 ', through which a heating medium, preferably supplied via the shaft 105', is circulated. Flow devices in the form of channels can be provided in an analogous manner in the end wall 107, as previously described with the aid of the steam turbine 101.

Finally, an eighth embodiment of a heat engine according to the invention is shown in the form of a steam turbine 101 "in FIG. 11. The structure of the steam turbine 101" is comparable to that of the steam turbine 101 'shown in FIG. Identical elements of the steam turbine 101 "have the same reference numerals as the elements of the steam turbine 101 ', while the different elements bear the same reference numbers, albeit with two lines. The two steam turbines 101 'and 101 "essentially differ from one another in that the end walls 107" and 115 "are essentially in two parts. The end wall 107" consists of the parts 107a "and 107b". The end wall part 107b "is connected to the shaft 105", while the end wall part 107a "is connected to the peripheral wall 113". This offers the advantage that the sealing devices 133 "are not arranged in the area of the working medium 137, and thus a easier sealing can be achieved. In an analogous manner, the end wall 115" is formed in two parts in the form of the first end wall part 115a "and the second end wall part 115b ". The end wall part 115a "is connected to the peripheral wall 113", while the end wall part 115b "is connected to the shaft 105". Due to this construction, both the first chamber 129 "with the end wall 115", which serves as a steam generating device, and the second chamber 131 "with the end wall 107", which serves as a condensation device, are both partially from the rotor 117 "and the Stator 103 "includes.

In further embodiments of the invention, not shown, it can be provided that the evaporated working medium emerging from the first chamber initially hits the blade wheel or wheels with the interposition of a flow guide wheel that is operatively connected to the rotor. In particular when using a single paddle wheel, it can be provided that, in order to utilize the energy inherent in the vaporized working medium, a flow guide wheel that is operatively connected to the rotor and in particular acts as an impeller is connected downstream of this paddle wheel. In addition, the arrangement of the deflection wheel, the flow guide wheel and / or the paddle wheel is not limited to an axial relative arrangement to one another. In order to achieve a high degree of compactness of the heat engine of the invention, it is provided in particular that these wheels are arranged at least in regions radially relative to one another.

In further embodiments of the invention, not shown, it can be provided that the heat engine is designed in the form of counter-pressure or extraction turbines, from which steam generated by additional extraction devices in the steam-generating chambers can be extracted.

The use of the heat engine according to the invention can also be carried out in the form of a ballast or steam turbine, in that the heat engine is external, in addition to the internal Steam generated within the heat engine, additional steam can be supplied.

With regard to the exemplary embodiments of the invention mentioned above, it should be noted that, as can be seen in particular from the steam turbine 1 ′ shown in FIGS. 3 and 4, the working medium within the heat engine can have a flow pattern that is adapted to the respective requirements of the heat engine , In particular, it is possible for the working medium to flow in sections in the axial, radial or also transverse direction, in particular both in the radial direction towards an axis of the heat engine and away from it. The invention is therefore in particular not limited to the flow paths of the working medium shown as examples.

The features of the invention disclosed in the above description, in the drawings and in the claims can be essential both individually and in any combination for realizing the invention in its various embodiments.

LIST OF REFERENCE NUMBERS

, i ', i "steam turbine, 3', 3" stator, 5 ', 5 "shaft" connecting link, 7 *, 7 "paddle wheel" flow guide wheel, 9' bearing 0, 10 'seal 1, 11', 11 "rotor 1a , 11c, 11a ', 11c', 11a ", 11c" end wall 1b, 11b ', 11b "peripheral wall 3, 13' chamber 4 'flow guide body 5, 15' chamber 6 'flow guide body 7, 17', 17" wall 8 "connecting link 9 opening 0 'duct 1, 21' working medium 3 partition 4 'partition 5, 25' turbine chamber 7, 27 ', 27 "nozzle 8', 28" blade 9, 29 'combustion gas 0 "blade 1, 31' cooling air 1, 51 ', 51 "steam turbine 3, 53', 53" stator 5, 55 'shaft 57a, 57b, 57a ', 57b', 57c ',

57a ", 57b", 57c "paddle wheel

59, 59 'bearings

60, 60 'seal

61, 61 ', 61 "rotor

61a, 61c, 61a ', 61c' end wall

61b, 61b 'peripheral wall

63, 63 'chamber

65, 65 ', 65 "chamber

67, 67 'compensation chamber

69, 69 'wall

71, 71 'combustion gas

73, 73 'working medium

75, 75 ', 75 "line

77, 77 ', 77 "nozzle

79a, 79b, 79a *, 79b ', 79c',

79a ", 79b", 79c "deflection wheel

81, 81 'cooling air

83, 83 'channel

85, 85 ', 85 "partition

101, 101 ', 101 "steam turbine

103, 103 ', 103 "stator

105, 105 ', 105 "shaft

107, 107 "end wall

107a ", 107b" end wall part

109 paddle wheel

111 paddle wheel

113, 113 ', 113 "peripheral wall

115, 115 ', 115 "end wall

115a ", 115b" end wall part

117, 117, 117 "rotor

119, 121, 123 partition

125 flow guide wheel

127, 127 'bearings 129, 129 ', 129 "chamber

131, 131 ', 131 "chamber

133, 133 "seal

135 combustion gas

137 working medium

139 nozzle

141 cooling air

143 '. , 143 "r sealing element

Claims

Expectations

1. Heat engine (1, 1 ', 1 ", 51, 51', 51") for converting thermal energy into mechanical energy, comprising at least one steam generating device (11a, 11a ', 11a ", 13, 13', 61a, 61a ', 63, 63') for at least partially evaporating a first liquid working medium (21, 21 ', 73, 73') by means of thermal energy supplied by the heat engine (1, 1 ', 1 ", 51, 51', 51"), at least one that can be driven by means of the vaporized first working medium (21, 21 ', 73, 73') to generate mechanical energy and relative to at least one stator (3, 3 ', 3 ", 53, 53', 53") around a first one Rotatable rotor (11, 11 ', 11 ", 61, 61', 61") and at least one condensation device (11c, 1 lc ', 1 lc ", 15, 15', 61c, 61c ', 65, 65', 65 ") for condensing the evaporated first working medium (21, 21 ', 73, 73') after driving the rotor (11, 11 ', 11", 61, 61', 61 "), the rotor (11, 11 ' , 11 ", 61, 61 ', 61") the stator (3, 3', 53, 53 ', 53 ") essentially completely and and there are the rotor (11, 11 ', 11 ", 61, 61', 61") the steam generating device (11a, 11a ', 11a ", 13, 13', 61a, 61a ', 63, 63') and the Condensation device (11c, 11c ', 11c ", 15, 15', 61c, 61c '65, 65', 65") substantially completely comprises.

2. Heat engine (1, 1 ', 1 ", 51, 51', 51", 101, 101 ', 101 ") for converting thermal energy into mechanical energy, comprising at least one steam generating device (11a, 11a', 11a", 13, 13 ', 61a, 61a', 63, 63 *, 115, 115 ', 115 ") for at least partially evaporating a first liquid working medium (21, 21', 73, 73 ', 137) by means of the heat engine (1, 1 ', 1 ", 51, 51 *, 51", 101, 101', 101 ") of thermal energy supplied, at least one by means of the vaporized first working medium (21, 21 ', 73, 73', 137) for the generation of mechanical Energy drivable and rotatable relative to at least one stator (3, 3 ', 3 ", 53, 53', 53", 103, 103 ', 103 ") about a first axis of rotation (11, 11', 11", 61, 61 ', 61 ", 117, 117', 117") and at least one condensing device (11c, 11c ', 11c ", 15, 15', 61c, 61c ', 65, 65', 65", 107, 107 ', 107 ") for condensing the evaporated first working medium (21, 21', 73, 73 ', 137) after driving the rotor (11, IT, 11", 61, 61 *, 61 ", 117, 117 ', 117"), the rotor (11, 11', 11 ", 61, 61 ', 61", 117, 117', 117 ") the stator (3, 3 ', 53, 53 ', 53 ", 103, 103', 103") at least in some areas.

3. Heat engine according to claim 2, characterized in that the rotor (11, 11 ', 11 ", 61, 61', 61", 117) the steam generating device (11a, 11a ', 11a ", 13, 13', 61a, 61a ', 63, 63', 115) and / or the condensation device (11c, 11c ', 1 lc ", 15, 15', 61c, 61c ', 65, 65', 65") essentially completely.

4. Heat engine according to claim 2 or 3, characterized in that the stator (103, 103 ") comprises the steam generating device (l 15) and / or the condensation device (107, 107 ') substantially completely.

5. Heat engine according to claim 2, characterized in that the steam generating device (l 15 ") and / or the condensation device (107") is or are formed at least in two parts and the rotor (117 ") is a first part of the condensation device (107a") and / or comprises a first part of the steam generating device (115a ") and the stator (103") comprises the other part of the steam generating device (115b ") and / or the condensing device (107b").

6. Heat engine according to one of claims 1 to 5, characterized by at least one first chamber forming the steam generating device (13, 13 ', 63, 63', 129, 129 ', 129 "), at least one second chamber forming the condensing device (15, 15 ', 65, 65', 65 ", 131, 131 ', 131") and at least one turbine chamber (25), preferably the first chamber (13, 13', 63, 63 ', 129, 129', 129 " ) and the second chamber (15, 15 ', 65, 65', 65 ", 131, 131 ', 131"), the first chamber (13, 13') and the turbine chamber (25, 25 ') and / or the second chamber and the turbine chamber are separated from one another at least in regions by means of at least one, in particular thermally insulating, wall (17, 17 ', 17 ", 23, 24', 69, 69 ', 85, 85 *, 85", 121).

7. Heat engine according to claim 6, characterized by at least one of the first chamber (13, 13 ', 63, 63') and the turbine chamber (25, 25 ') for passage of the vaporized first working medium (21, 21', 73, 73 ' ) connecting first connecting device, preferably comprising at least one first nozzle (27, 27 ', 27 ", 77, 77', 77", 139), preferably the geometry and / or the orientation of the nozzle opening being adjustable, at least one first tube ( 75, 75 ', 75 ") and / or at least one first opening formed in particular in the thermally insulating wall.

8. Heat engine according to claim 6 or 7, characterized by at least one second connecting device connecting the turbine chamber and the second chamber for the passage of the vaporized first working medium, preferably comprising at least one second nozzle, preferably the geometry and / or the orientation of the nozzle opening being adjustable, at least one second tube and / or at least one second opening, in particular formed in the thermally insulating wall.

9. Heat engine according to claim 7 or 8, characterized by at least one first and / or at least one second flow control and / or regulating device operatively connected to the first connecting device, preferably in the form of a first and / or second valve.

10. Heat engine according to one of claims 6 to 9, characterized by at least one connecting the first chamber (13, 13 ') and the turbine chamber (25, 25') for the passage of the liquid first working medium (21, 21 '), in particular in the form of at least one third opening (19, 20 '), preferably formed in the thermally insulating wall (17, 17').

11. Heat engine according to one of claims 6 to 10, characterized by at least one connecting the turbine chamber and the second chamber for the passage of the liquid first working medium fourth connecting device, preferably in the form of at least one, in particular in the thermally insulating wall formed, fourth opening.

12. Heat engine according to claim 10 or 11, characterized in that the liquid first working medium (21, 21 ', 73, 73') during a rotation of the rotor (11, 11 ', 11 ", 61, 61', 61", 117, 117 ', 117 "), in particular due to the centrifugal force acting on the working medium (21, 21', 73, 73 ', 137), an escape of the vaporized first working medium (21, 21', 73, 73 ') from the first chamber (13, 13 ', 63, 63', 129, 129 ', 129 ") prevented by the third and / or fourth connecting device, in particular the third and / or fourth opening (19, 20') blocked.

13. Heat engine according to one of claims 10 to 12, characterized by at least one third and / or at least one fourth flow control and / or regulating device that is operatively connected to the third connecting device, preferably in the form of a third and / or or fourth valve, in particular a check valve.

14. Heat engine according to one of claims 6 to 13, characterized in that the second chamber (15, 15 ') and the turbine chamber (25, 25') are formed in one.

15. Heat engine according to one of claims 6 to 14, characterized by at least one in the first chamber (13 '), the second chamber (15 *) and / or the turbine chamber (25') formed flow guide body (14 ', 16').

16. Heat engine according to one of the preceding claims, characterized by at least one of the stator (3, 3 ', 3 ", 53, 53', 53", 103, 103 ', 103 ") comprising a first blade wheel (7, 7' , 7 ", 57a, 57a ', 57a", 109), preferably via the first connecting device (27, 27', 27 ", 75, 75 ', 75", 77, 77', 77 ", 139), for rotating the rotor (11, 11 ', 11 ", 61, 61 *, 61", 117, 117', 117 ") relative to the stator (3, 3 ', 3", 53, 53', 53 ", 103, 103 ', 103 ") the evaporated first working medium (21, 21', 73, 73 ', 137) can be supplied, in particular axially, radially and / or at a predetermined angle relative to the first axis of rotation.

17. Heat engine according to claim 16, characterized by at least one with the rotor (11 ", 117, 117 ', 117") that is operatively connected, in particular connectable to this in a rotationally secure manner, and upstream and / or downstream of the vaporized working medium (21', 137 ) Relative to the first paddle wheel (7 ", 109) arranged flow guide wheel (8", 125), the flow guide wheel (8 ", 125) preferably at least in regions concentric to the first Paddle wheel (7 ", 109) is arranged, in particular inside and / or outside of the first paddle wheel (7", 109).

18. Heat engine according to claim 16 or 17, characterized by at least one of the stator (53, 53 ', 53 ", 103, 103', 103"), in particular arranged downstream of the vaporized working medium relative to the degree of flow, second paddle wheel (57b, 57b ', 57c', 57b ", 57c", 111), preferably upstream and / or downstream of the vaporized working medium (73, 73 ') relative to the second paddle wheel (57b, 57b', 57b ", 57c ', 57c" ) at least one deflection wheel (79a, 79b, 79a ', 79b', 79c ', 79a ", 79b", 79c "), which is operatively connected to the rotor (61, 61', 61") and in particular can be connected to it in a rotationally secure manner , in particular the deflection wheel is arranged at least in regions concentrically with the first and / or second impeller, in particular inside and / or outside the first and / or second impeller.

19. Heat engine according to one of claims 16 to 18, characterized in that the first blade wheel (7, 7 ', 57a, 57a', 57a "), the flow guide wheel, the second blade wheel (57b, 57b ', 57c', 57b" , 57c ") and / or the deflection wheel (79a, 79b, 79a *, 79b ', 79c', 79a", 79b ", 79c") is or are at least partially arranged in the turbine chamber (25, 25 ').

20. Heat engine according to claim 18 or 19, characterized in that the second impeller has a second diameter deviating from a first diameter of the first impeller and / or a number or geometry of the blades deviating from the number or geometry of the blades of the first impeller having.

21. Heat engine according to one of claims 18 to 20, characterized by a plurality of second paddle wheels (57b ', 57c', 57b ", 57c") and / or deflection wheels (79a, 79b, 79a ', 79b', 79c ' , 79a ", 79b", 79c "), the second vane wheels (57b ', 57c') preferably having different diameters, different geometries and / or a different number of vanes relative to one another and / or the deflection wheels (79a ', 79b', 79c ') different diameters, different Have geometries and / or a different number of blades from one another.

22. Heat engine according to one of claims 16 to 21, characterized in that the geometry and / or the position of at least one blade of the first blade wheel, at least one second blade wheel, of the flow control wheel and / or at least one deflection wheel, preferably during operation of the heat engine, is or are adjustable.

23. Heat engine according to one of the preceding claims, characterized by at least one heating means for acting on the steam generating device (11a, 11a ', 11a ", 13, 13', 61a, 61a ', 63, 63', 115, 115 ', 115", 129, 129 ', 129 "), in particular the first chamber (13, 13', 63, 63 ', 129, 129', 129"), with heat, preferably in the form of a fluid heating medium, in particular in the form of hot gases, such as Combustion gases (29, 29 ', 71, 71', 135), a heating source, such as in the form of at least one heating spindle, which is integrated in a wall of the first chamber, which comprises in particular a material with high thermal conductivity and / or is structured for high convective heat transport and or is formed on the surface of this wall, at least one first flow device for a heating fluid (29, 29 ', 71, 71', 135), at least one on an outside of the wall (11a, 11a ', 1 la ", 61a, 61a ', 115, 115', 115 ") of the first chamber (13, 13 *, 63, 63 ', 129, 129', 129") formed, in particular by the heating fluid (29, 29 ', 71, 71', 135), first structure and / or at least one on an inside of the wall (11a, 11a ', 11a ", 61a, 61a', 115, 115 ', 115 ") of the first chamber (13, 13', 63, 63 ', 129, 129', 129"), which can be flowed through, in particular, by the preferably vaporized working medium (21, 21 ', 73, 73', 137) , second structure.

24. Heat engine according to claim 23, characterized in that the first throughflow device is integrated in the wall, the heating means being fed to the first throughflow device preferably via a shaft of the stator and / or that heating means in particular in a preferably closed, comprising the first throughflow device, Heating circuit is circulated.

25. Heat engine according to one of the preceding claims, characterized by at least one coolant for acting on the condensation device (11c, 11c *, 11c ", 15, 15 ', 61c, 61c', 65, 65 ', 65", 107, 107', 107 ", 131, 131 ', 131"), in particular the second chamber (15, 15', 65, 65 ', 65 ", 131, 131', 131"), with cold, preferably in the form of a fluid cooling medium, in particular in the form of nitrogen or cold air (31, 31 ', 81, 81', 141), a cooling source, such as in the form of at least one Peltier element, which in particular comprises a material which preferably has a high thermal conductivity and / or for a high convective Structured heat transport, integrated wall of the second chamber and / or is formed on the surface of this wall, at least one second flow device for a cooling fluid (31, 31 ', 81, 81', 141), such as nitrogen or cold air, at least one on an outside the wall (11c, 11c *, 11c ", 61c, 61c'm 107, 107 ', 107") of the two th chamber (15, 15 ', 65, 65', 65 ", 131, 131 ', 131") formed, in particular by the cooling fluid (31, 31', 81, 81 ', 141), third structure and / or at least one on an inside of the wall (11c, 11c ', 11c ", 61c, 61c', 107, 107 ', 107") of the second chamber (15, 15', 65, 65 ', 65 ", 131, 131' , 131 "), fourth structure through which the working medium (21, 21 ', 137) can flow.

26. Heat engine according to claim 25, characterized in that the second flow device is integrated in the wall, the coolant of the second flow device preferably being supplied via a shaft of the stator and / or the coolant in particular in a preferably closed, comprising the second flow device, Cooling circuit is circulated.

27. Heat engine according to one of claims 23 to 26, characterized in that the heating fluid (29, 29 ', 71, 71') has a flow direction in the region of the heating medium, which essentially radially outwards from the first axis of rotation to the outer circumference of the rotor (11, 11 ', 11 ", 61, 61', 61"), and / or the cooling fluid (31, 31 ', 81, 81') has a flow direction in the region of the coolant which is essentially radial from the outer circumference of the Rotor (11, 11 ', 11 ", 61, 61') runs in the direction of the first axis of rotation.

28. Heat engine according to one of the preceding claims, characterized by at least one supply device for supplying at least one vaporous second working medium, preferably the first and second evaporated working medium being identical.

29. Heat engine according to one of the preceding claims, characterized by at least one removal device for removing at least part of the evaporated and or liquid first working medium.

30. Heat engine according to claim 28 or 29, characterized by at least one fifth flow control and / or regulating device that is operatively connected to the feed device and / or at least one sixth flow control and / or regulating device that is operatively connected to the removal device.

31. Heat engine according to one of the preceding claims, characterized by at least one with the steam generating device, the condensation device, the first and / or second nozzle of the first, second, third, fourth, fifth and / or sixth flow control and / or regulating device, the first Paddle wheel, at least one second paddle wheel, the flow guide wheel and / or at least one deflection wheel, the heating medium, the coolant and / or a sensor for measuring the rotational speed of the rotor, the control and / or regulating unit being operatively connected.

32. Use of a heat engine according to one of the preceding claims as a front-end turbine, steam turbine, counter-pressure turbine, extraction turbine, constant-pressure turbine and / or positive-pressure turbine.