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 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 around a first rotational axis, and at least one condensation device for condensation of the vaporised first working medium after the rotor has been driven. The rotor surrounds the stator in an essentially complete manner. The invention also relates to the use of the inventive thermal combustion engine.

Description:
FIELD OF THE INVENTION  
       [0001]     The present invention relates to a thermal combustion engine which converts thermal energy into mechanical energy and the use of such a thermal combustion engine.  
       BACKGROUND OF THE INVENTION  
       [0002]     Multiple thermal combustion engines are known from the related art. Thus, for example, DE 199 48 128 A1 discloses a device and a method for generating flow energy in liquids from heat. In this case, the device comprises a housing having a vapor intake opening connected to a vaporizer and a vapor outlet opening connected to a condenser. Furthermore, the housing has a flow opening connected to a hydromotor and a return connection connected thereto. A rotor is positioned within the housing, which has multiple cells, in each of which pistons are located. By supplying vapor under pressure through the vapor intake opening, removing the vapor from the vapor outlet opening, and rotating the rotor, a hydraulic liquid is pumped through the hydromotor. However, this device has the disadvantage that it has a complex construction and, because of its multicomponent structure, has a large overall volume and may therefore not be implemented compactly. In addition, a pump is required in particular in order to return the liquid condensed in the condenser back to the vaporizer.  
         [0003]     Furthermore, US 2002/0194848 A1 discloses a vapor motor for driving a generator. In this case, the vapor motor comprises a rotary engine, which is integrated in a closed vapor loop. The vapor loop comprises a vapor generator, a vapor injector for injecting vapor into the rotary engine, and a condenser for condensing the vapor which exits out of the rotary engine. A combustion is performed within the vapor motor in order to supply heat to a vapor generator which comprises a bundle of circular pipes. The vapor exiting out of the vapor generator is applied to the rotary engine and subsequently flows through a further bundle of pipes which are used for preheating combustion air. The vapor thus partially cooled is supplied to a condenser, and the water condensed in the condenser is subsequently supplied back to the vapor generator via a pump. However, this vapor motor also has the disadvantages of a complex construction and a lack of compactness because of the multiple components necessary, including a pump for conveying water condensed in the condenser into the vapor generator. Furthermore, the rotary engine is subject to wear, because of which high maintenance costs result.  
         [0004]     In addition, thermal combustion engines comprising vapor turbines are known from the related art. Vapor generated in an external vapor generator is supplied to the vapor turbines in such a way that a rotor having a blade wheel, which is positioned in a housing, is driven. After passing through the blade wheel, the vapor coming out of the housing is condensed, and the working medium thus condensed is supplied back to the vapor generator via a pump. However, these vapor turbines have the disadvantage that additional components, particularly valves, control elements, or pumps, are necessary in order to achieve conversion of thermal energy into mechanical energy. In particular, thermal combustion engines of this type, which use a vapor turbine, have a high power to weight ratio, i.e., the weight in relation to the extractable power, because of the large number of individual components.  
       SUMMARY OF THE INVENTION  
       [0005]     As will be recognized from the description herein, embodiments of the present invention provide a thermal combustion engine which overcomes the disadvantages of the related art. In particular, the conversion of thermal energy into mechanical energy is to be attained while achieving a low power to weight ratio, a high efficiency, low pollutant and noise emissions, and a simple, low-maintenance, and low-wear construction.  
         [0006]     In one implementation, a thermal combustion engine comprises at least one vapor generation device for at least partially vaporizing a liquid first working medium using thermal energy supplied to the thermal combustion engine, at least one rotor which is drivable using a vaporized first working medium to generate mechanical energy and is rotatable in relation to at least one stator around at least one axis of rotation, and at least one condensation device for condensing the vaporized first working medium after driving the rotor, the rotor generally completely surrounding the stator, and the rotor generally completely enclosing the vapor generation device and the condensation device.  
         [0007]     In another implementation, a thermal combustion engine comprises at least one vapor generation device for at least partially vaporizing a liquid first working medium using thermal energy supplied to the thermal combustion engine, at least one rotor which is drivable using a vaporized first working medium to generate mechanical energy and is rotatable in relation to at least one stator around at least one axis of rotation, and at least one condensation device for condensing the vaporized first working medium after driving the rotor, the rotor at least partially surrounding the stator.  
         [0008]     In the foregoing implementations, a centrifugal force may be generated on the liquid first working medium by a rotational movement of the rotor, through which a centrifugal force closure may be implemented between the condensation device and the vapor generation device, and the liquid first working medium is conveyable out of the condensation device into the vapor generation device using the centrifugal force closure.  
         [0009]     Further described and claimed herein are various advantageous embodiments and features that may be implemented in connection with the foregoing implementations.  
         [0010]     In addition, disclosed herein is the use of a thermal combustion engine according to the present invention as a topping turbine, exhaust vapor turbine, back pressure turbine, extraction turbine, impulse turbine, and/or reaction turbine.  
         [0011]     Embodiments of the present invention are based on the surprising recognition that the implementation of a vapor turbine in the form of an external rotor motor, in which a vapor generation device and a condensation device are integrated in the rotor, results in a constructively simpler construction of a thermal combustion engine. In particular, a thermal combustion engine may be provided which dispenses with control elements and/or impellers, such as valves or pumps for conveying a working medium from a vaporizer to a condenser. Through the integration of a vaporizer and condenser in a rotor which rotates around at least one stator having a blade wheel, automatic conveyance of working medium from the condenser to the vaporizer is achieved via the centrifugal force acting on the working medium through the rotation.  
         [0012]     In addition, the rotational movement of the rotor and therefore the centrifugal force acting on the working medium ensures that the working medium itself closes a connection channel running from the condenser to the vaporizer in such a way that vapor generated in the vaporizer may only reach the condenser by exiting the vaporizer, hitting the blade wheel, and therefore causing rotation of the rotor. In particular, the centrifugal force acting on the working medium due to the rotation of the rotor causes a transition of the vaporized working medium from the vapor generator into the condenser to be possible only in the way described above after passing through the blade wheel, even at higher pressures within the vapor generator in relation to the pressure in the condenser, because of the hydrostatic pressure caused by the centrifugal force. This means that a centrifugal force closure between the condenser and the vaporizer is implemented according to the present invention. This centrifugal force closure is also used as a pump for conveying the working medium from the condenser into the vaporizer. This results in additional feed pumps, etc. being able to be dispensed with.  
         [0013]     In addition, the construction of the vapor turbine as an external rotor motor achieves a higher efficiency of the thermal combustion engine. Both heating of the machine on the vaporizer side, using combustion gases, for example, and also cooling on the condenser side, using cold air, for example, may be performed using a countercurrent principle according to the present invention, arbitrary flow directions of the cooling and/or heating medium otherwise being possible. Efficient excitation of the combustion gases is achieved in this case in that combustion gases of higher temperature heat the area in proximity to the axis of the rotor and therefore especially hot vapor exits out of the vapor generator, which is then particularly directed onto the blade wheel of the stator via nozzles.  
         [0014]     The combustion gases then flow in a radial direction from the axis of rotation of the rotor outward to the external circumference of the rotor, where the cooling combustion gases bring to a boil the liquid working medium, which is located there at the external circumference of the rotor because of centrifugal force. The vapor generated in this case travels in the rotor in the direction of the axis of rotation of the rotor and is continuously heated because of the temperature of the combustion gases, which becomes higher and higher in this direction, so that an isobaric expansion may occur, for example.  
         [0015]     On the condenser side, the cooling air flows from the external circumference of the rotor in the radial direction toward the axis of rotation of the rotor, outside the rotor. Thus, vapor which flows radially outward from the axis of rotation in the interior of the rotor is increasingly cooled and condensed. Therefore, the construction of a thermal combustion engine according to the present invention as a vapor turbine in an external rotor motor allows the use of a countercurrent principle both for heating a working liquid and also for cooling it, which results in an increase of the efficiency of the thermal combustion engine. 
     
    
     BRIEF DESCRIPTION OF THE DRAWINGS  
       [0016]     Further features and advantages of the present invention result from the following description, in which preferred embodiments of the present invention are explained for exemplary purposes on the basis of schematic figures.  
         [0017]      FIG. 1  shows a sectional view of a first embodiment of a thermal combustion engine according to the present invention;  
         [0018]      FIG. 2  shows a sectional view of the thermal combustion engine of  FIG. 1  along the plane A-A of  FIG. 1 ;  
         [0019]      FIG. 3  shows a sectional view of a second embodiment of a thermal combustion engine according to the present invention;  
         [0020]      FIG. 4  shows a sectional view of the thermal combustion engine of  FIG. 3  along the plane B-B of  FIG. 3 ;  
         [0021]      FIG. 5  shows a sectional view of a third embodiment of a thermal combustion engine according to the present invention;  
         [0022]      FIG. 6  shows a sectional view of the thermal combustion engine of  FIG. 5  along the plane B-B of  FIG. 5 ;  
         [0023]      FIG. 7  shows a sectional view of a fourth embodiment of a thermal combustion engine according to the present invention;  
         [0024]      FIG. 8   a  shows a sectional view of a fifth embodiment of a thermal combustion engine according to the present invention;  
         [0025]      FIG. 8   b  shows a sectional view of an alteration of the fifth embodiment of a thermal combustion engine according to  FIG. 8   a;    
         [0026]      FIG. 9  shows a sectional view of a sixth embodiment of a thermal combustion engine according to the present invention;  
         [0027]      FIG. 10  shows a sectional view of a seventh embodiment of a thermal combustion engine according to the present invention; and  
         [0028]      FIG. 11  shows a sectional view of an eighth embodiment of a thermal combustion engine according to the present invention. 
     
    
     DETAILED DESCRIPTION  
       [0029]     A first embodiment of a thermal combustion engine is illustrated in  FIGS. 1 and 2  in the form of a vapor turbine  1 , or rather a compact vapor turbine, having an integrated vapor generation zone. The vapor turbine  1  comprises a stator  3 , which in turn comprises a fixed shaft  5  and a blade wheel  7  connected to the shaft  5 . A rotor  11  having front walls  11   a ,  11   c  and a peripheral wall  11   b  is mounted so it is rotatable in relation to the stator  3  via a bearing  9  and a seal  10  in such a way that the interior of the rotor  11  is sealed. The rotor  11  essentially comprises a first chamber  13  and a second chamber  15 . The chambers  13 ,  15  are separated from one another by a thermally insulating wall  17 , except for openings  19  of the wall  17  in the area of the peripheral wall  11   b  of the rotor  11 . A working medium  21 , preferably water, may flow through the openings  19  from the second chamber  15  into the first chamber  13 , as will be described later in detail.  
         [0030]     Because of the centrifugal forces acting on the working medium  21  during rotation of the rotor  11 , the working medium  21  collects at the peripheral wall  11   b  of the rotor  11 , as shown in  FIGS. 1 and 2 . The first chamber  13  is also separated by a partition wall  23  from a turbine chamber  25 , in which the blade wheel  7  is positioned. Openings in the form of nozzles  27  are implemented within the partition wall  23 . In the following, the mode of operation of the vapor turbine  1  will now be explained.  
         [0031]     Combustion gases  29  of a heating device (not shown) are supplied to the rotor  11  on the front wall  11   a  positioned on the side facing toward the first chamber  13 . As may be seen in  FIG. 1 , the combustion gases  29  are supplied in such a way that they are guided along the rotor  11  from its axis of rotation radially outward. In this case, the first front wall  11   a  of the rotor  11  is heated by the combustion gases  29 , because of which the working medium  21  located in area of the first chamber  13  is heated, which finally results in at least partial vaporization of the working medium  21  in the first chamber  13 . The first chamber  13  thus acts as a vapor generation chamber. By regulating the heat supplied using control and/or regulation of the quantity of supplied combustion gas  29  and/or its temperature, the power output by the vapor turbine  1  and/or the speed thereof may be controlled and/or regulated.  
         [0032]     In order to allow sufficient heat exchange between the combustion gases  29  and the interior of the first chamber  13  or vapor generation chamber, heat exchanger elements (not shown) are located on the first front wall  11   a  of the rotor  11  in area of the first chamber  13 , preferably both on the side facing toward the combustion gases  29  and also on the side facing toward the first chamber  13 , which the combustion gases  29  and/or the working medium  21  vaporized in the first chamber  13  flow through. In particular, the first front wall  11   a  of the rotor  11  comprises a material having high thermal conductivity.  
         [0033]     The vaporized working medium  21  travels within the first chamber  13  from the peripheral wall  11   b  to the axis of rotation of the rotor  11 . A countercurrent principle is thus implemented in the vapor turbine  1 . This results in efficient exploitation of the energy of the combustion gases  29 . The combustion gases  29  of higher temperature are incident on the area of the first chamber  13  facing toward the axis of rotation of the rotor  11 , so that especially hot vapor arises in this area. The combustion gases  29  traveling in the radial direction of the rotor  11  then cool down again and bring to a boil the working medium  21  in area of the peripheral wall  11   b  of the rotor  11 . Efficient exploitation of the thermal energy of the combustion gases  29  is thus achieved.  
         [0034]     The working medium  21  heated in area of the peripheral wall  11   b  of the rotor  11  flows through the first chamber  13  and/or vapor generation chamber in the direction toward the partition wall  23 , while expanding in an isobaric way. Therefore, an increased internal pressure arises within the first chamber  13 , which is noticeable in that the level of the working medium  21  in the area of the first chamber  13  is lower than that in the second chamber  15 . The vapor thus generated in the first chamber  13  flows through the nozzles  27  and is expanded adiabatically at the same time. As may be seen in  FIG. 2  in particular, the nozzles  27  are not oriented radially, but rather are inclined, so that an optimum angle of inclination of the nozzles  27  is settable. The vapor thus hits the blade wheel  7  in such a way that there is a recoil of the rotor  11  in relation to the stator  3 , which generates and/or maintains a rotational movement of the rotor  11 .  
         [0035]     After the passage through the blade wheel  7 , the vapor exits from the turbine chamber  25  into the second chamber  15 , which is used as the condensation chamber. The vapor cools there and the working medium  21  therefore condenses out in the area of the second chamber  15 .  
         [0036]     Because of the rotation of the rotor  11 , condensed working medium  21  collects on the peripheral wall  11   b  of the rotor  11 . In order to achieve cooling of the vaporized working medium  21  in the second chamber  15 , which acts as a condensation chamber, cooling air  31  is applied to the second front face  11   c  of the rotor  11 . This supply is also performed in accordance with the countercurrent principle. Cold air flows as cooling air from the outside of the rotor  11  in a radial direction toward the axis of rotation of the rotor  11 . The cooling air  31  is heated at the same time. In contrast, the vaporized 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 condensed in this case. Since therefore the already heated cooling air  31  may absorb further heat energy in area of the axis of rotation of the rotor  11 , a conductive heat exchange between the working medium  21  and the cooling medium  31  being supported by structuring of the wall  11   c  (not shown), preferably in the form of heat exchanger elements, efficient heat dissipation from the second chamber  15  is ensured. The working medium  21  condensed in the second chamber  15  then flows through the openings  19  in the wall  17  into the first chamber  13 , where it is again vaporized.  
         [0037]     Because of the centrifugal force acting on the working medium  21 , it is accelerated outward and therefore closes the openings  19 , so that the vapor from the first chamber  13  may reach the second chamber  15  exclusively through the nozzles  27 . Even in the event of a larger pressure in the first chamber  13  than the pressure in the second chamber  15 , a secure closure of the openings  19  is ensured for the vapor of the working medium  21  generated in the first chamber  13 , since the openings  19  are held closed by the working medium  21  because of the hydrostatic pressure caused by the centrifugal force.  
         [0038]     In order to allow the vapor turbine  1  to start up automatically, check valves may be positioned within the openings  19 . These cause vapor which is initially generated in the first chamber  13  to ensure rotation of the rotor  11  by exiting through nozzles  27 , so that after beginning the rotation, closure of the openings  19  by the working medium  21  is ensured. In addition, closure devices, such as valves, may also be provided in the nozzles  27  in order to achieve control of the rotational velocity of the rotor  11 . The valves in the openings  19  and the nozzles  27  may particularly be connected to a control and regulation device (not shown) in this case. Furthermore, speed control and/or regulation of the vapor turbine  1  is possible through variation of the quantity of heat energy supplied using the combustion gases  29  and/or through variation of the angle of inclination of the nozzles  27 .  
         [0039]     A second embodiment of a thermal combustion engine according to the present invention is shown in  FIGS. 3 and 4  in the form of a vapor turbine  1 ′, or rather a compact vapor turbine, having an integrated vapor generation zone. The vapor turbine  1 ′ essentially corresponds in its basic construction to the construction of the vapor turbine  1  illustrated in  FIGS. 1 and 2 . In contrast to the vapor turbine  1 , in the vapor turbine  1 ′, the corresponding elements are provided with the identical reference numbers, but with an apostrophe. The vapor turbine  1 ′ essentially differs from the vapor turbine  1  through a different flow guide of the vaporized and/or liquid working medium  21 ′.  
         [0040]     Similar to the operation of the vapor turbine  1 , combustion gases  29 ′ are supplied to the rotor  11  ′ of the vapor turbine  1 ′ on the first wall  111   a ′ positioned on the side facing toward the first chamber  13 ′. This supply is also performed, as may be inferred from  FIG. 3 , in accordance with the countercurrent principle. Working medium  21 ′ provided inside the first chamber  13 ′ is heated by the combustion gases  29 ′. In contrast to the operation of the vapor turbine  1 , this vaporized working medium  21 ′ only flows through nozzles  27 ′ into the turbine chamber  25 ′ and/or the second chamber  15 ′ after a deflection by nearly 180° using a flow guiding body  14 ′. This deflection around the flow guiding body  14 ′ particularly offers the advantage that entrained droplets of the working medium  21 ′ may not follow the vapor flow around the flow guiding body  14 ′ and thus may not reach the turbine chamber  25 ′ and/or the second chamber  15 ′ via the nozzles  27 ′. The entrained droplets flow with the vapor flow in the direction of the axis of rotation of the rotor  11 ′, but move further in the radial direction and hit the flow body  14 ′, where they are accelerated in the direction of the peripheral wall  11   b ′ because of the acting centrifugal force. Furthermore, due to the flow guiding body  14 ′, the vaporized working medium  21 ′ may flow up to the axis of rotation of the rotor  11 ′ within the first chamber  13 ′, and therefore maximum heat transfer of the energy of the combustion gases  29 ′ to the working medium  21 ′ may occur.  
         [0041]     After deflection, the vaporized working medium  21 ′ flows through nozzles  27 ′ in the radial direction to the blade wheel  7 ′. The vaporized working medium  21 ′ then flows within the second chamber  15 ′ in proximity to the shaft  5 ′ in the direction of the front wall  11   c ′. This flow guiding is particularly achieved by a flow guiding body  16 ′ positioned in the second chamber  15 ′ in the area of the blade wheel  7 ′. This flow guiding ensures that the vaporized working medium  21 ′ flows in accordance with the countercurrent principle in relation to the cooling air  31 ′ on the inside of the front wall  11   c ′ in the direction of the peripheral wall  11   b ′. In addition, the flow guiding within the vapor turbine  1 ′ offers the advantage that, in comparison to the vapor turbine  1 , a blade wheel  7 ′ may be used which has a larger diameter than the blade wheel  7  of the vapor turbine  1 . The vapor turbine  1 ′ may therefore be operated at lower speeds.  
         [0042]     The working medium  21 ′ condensed in the second chamber  15 ′ collects on the peripheral wall  11   b ′ because of the rotational forces and flows through channels  20 ′ back into the first chamber  13 ′. The channels  20 ′ are formed in this case by the peripheral wall  11   b ′ and a generally cylindrical partition wall  24 ′, which particularly comprises the flow guiding bodies  14 ′ and  16 ′. In this case, the partition wall  24 ′ is implemented as thermally insulating particularly in the area of the channels  20 ′ in order to avoid heating of the working medium  21 ′ within the channels  20 ′.  
         [0043]     A third embodiment of a thermal combustion engine according to the present invention is shown in  FIGS. 5 and 6  in the form of a vapor turbine  1 ″, or rather a compact vapor turbine. The vapor turbine  1 ″ generally corresponds in its basic construction to the construction of the vapor turbine  1 ′ illustrated in  FIGS. 3 and 4 . The elements of the vapor turbine  1 ″ which correspond to those of the vapor turbine  1 ′ have identical reference numbers. The vapor turbine  1 ″ differs from the vapor turbine  1 ′ generally in that a blade wheel  7 ″ is provided, which is connected via at least one connection element  6 ″ to a shaft  5 ″ of the stator  3 ″. As may be seen in  FIG. 6  in particular, the blade wheel  7 ″ concentrically encloses a flow guiding wheel  8 ″, which is connected via connection elements  18 ″ to the wall  17 ″ and therefore to the rotor  11 ″, as may be seen from  FIG. 5  in particular.  
         [0044]     As shown in  FIG. 6 , the blade wheel  7 ″ has blades  28 ″, while the flow guiding wheel  8 ″ comprises blades  30 ″. Through this arrangement of the flow guiding wheel  8 ″ in relation to the blade wheel  7 ″, a further increase of the efficiency of the vapor turbine  1 ″ is achieved in comparison to the vapor turbine  1 ′. The working medium  21 ′ exiting out of the nozzles  27 ″ first hits the blades  28 ″ of the blade wheel  7 ″, through which the rotor  11 ″ is driven in relation to the stator  3 ″ to which the blade wheel  7 ″ is connected. The working medium exiting out of the blade wheel  7 ″ hits the blades  30 ″ of the flow guiding wheel  8 ″, which is connected to the rotor  11 ″. Therefore, the remaining energy present in the working medium is also at least partially converted into movement energy of the rotor  11 ″ by the flow guiding wheel  8 ″.  
         [0045]     The vapor turbines  1 ,  1 ′,  1 ″ illustrated in  FIGS. 1 through 6  are single-stage radial turbines, since only one blade wheel  7 ,  7 ′,  7 ″ is provided in each case and, in addition, the vapor hits the blade wheels  7 ,  7 ′,  7 ″ in the radial direction. In contrast to this, a fourth embodiment of a thermal combustion engine according to the present invention is illustrated in  FIG. 7  in the form of the vapor turbine  51 , or rather a multistage axial turbine, which is constructed as an impulse turbine, i.e., according to the Curtis principle.  
         [0046]     Impulse turbines are understood as vapor turbines in which the intake and outlet pressure of the vapor of a working medium into and/or out of the running blades of a blade wheel are equal. Therefore, the blades of an impulse turbine are driven using the energy from the velocity reduction of the vapor in the running blades. In particular, the vapor turbine  51  has velocity stages, i.e., the velocity of the vapor is exploited in stages. In order to achieve higher thermodynamic efficiency, it is also provided in impulse turbines of this type that pressure stages are generated, i.e., a pressure gradient is divided into multiple stages. This offers the advantage that vapor velocities which are too large may be avoided.  
         [0047]     The vapor turbine  51  has a stator  53  which surrounds a shaft  55 . Blade wheels  57   a  and  57   b  are positioned spaced apart from one another on the shaft  55 . A rotor  61  is provided in the vapor turbine  51  so it is rotatable in relation to the stator  53  via a bearing  59  and seals  60 . The rotor  61  has a first front wall  61   a , a peripheral wall  61   b , and a second front wall  61   c . Furthermore, a first chamber  63 , which is used as a vapor generation chamber, and a second chamber  65 , which is used as a condensation chamber, are implemented inside the rotor  61 . In addition, the vapor turbine  51 , in contrast to the vapor turbine  1 , has an equalizing chamber  67  for collecting liquid working medium  73 . The first chamber  63  and the equalizing chamber  67  are separated from one another via a thermally insulating wall  69 .  
         [0048]     Similar to the operation of the vapor turbines  1 ,  1 ′,  1 ″, in the vapor turbine  51 , combustion gases  71  are supplied to the first front wall  61   a  of the rotor  61  in accordance with the countercurrent principle. At least a part of the working medium  73  is thus vaporized within the first chamber  63 . The working medium  73  thus vaporized is firstly supplied via lines  75 , at the ends of which nozzles  77  are positioned, to the first blade wheel  57   a . Because of the expansion of the vapor in the area of the nozzle  77  and the incidence of the vapor on the first blade wheel  57   a , there is a rotational movement of the rotor  61 .  
         [0049]     In order to be able to completely exploit the energy residing in the vaporized working medium, in the vapor turbine  51 , the vapor directed axially to the first blade wheel  57   a  enters a deflection wheel  79   a , which rotates together with the rotor  61 , after the passage through the blade wheel  57   a . This deflection wheel particularly acts as a running wheel and converts the energy residing in the vapor into work energy. Furthermore, the vapor flow is deflected in the deflection wheel  79   a  before this flow is incident on a second blade wheel  57   b , which is also connected to the shaft  55 , again generally in the axial direction in relation to the axis of rotation of the rotor  61 .  
         [0050]     After passing through the second blade wheel  57   b , the vapor reaches a second deflection wheel  79   b , also particularly used as a running wheel, which is also connected to the rotor  61 . The vapor then enters the second chamber  65 , where it is cooled and condensed because of the cooling of the second front wall  61   c  of the rotor  61  using cooling air  81 . The condensed working medium  73  than then flows out of the second chamber  65  via the equalization chamber  67  into the first chamber  63 . In this case, the working medium  73  flows through channels  83  which are implemented between the peripheral wall  61   b  and a generally cylindrical partition wall  85 . The partition wall  85  is used for thermal insulation of the area in which the blade wheels  57   a ,  57   b  and the deflection wheels  79   a ,  79   b  are located and, in addition, the peripheral wall  61   b  and/or the channels  83 . For this purpose, the partition wall  85  has a generally low thermal conductivity. In particular, the partition wall  85  may be implemented as hollow, and may particularly comprise an insulation material.  
         [0051]     A fifth embodiment of a thermal combustion engine according to the present invention is illustrated in  FIG. 8   a  in the form of a multistage vapor turbine  51 ′. The basic construction of the vapor turbine  51 ′ generally corresponds to that of the vapor turbine  51  illustrated in  FIG. 7 . Therefore, essentially identical components of the vapor turbine  51 ′ have identical reference numbers as those of the vapor turbine  51 , but with an apostrophe.  
         [0052]     In contrast to the vapor turbine  51 , the vapor turbine  51 ′ has three blade wheels  57   a ′,  57   b ′, and  57   c ′. Accordingly, the vapor turbine  51 ′ also has three deflection wheels  79   a ′,  79   b ′, and  79   c ′, which are each connected to the rotor  61 ′. Furthermore, the vapor turbine  51 ′ differs from the vapor turbine  51  in that, because of the geometry of the nozzle  77 ′, the blade wheels  57   a ′,  57   b ′,  57   c ′, and deflection wheel  79   a ′,  79   b ′, and  79   c ′, it is a reaction turbine.  
         [0053]     Since the vapor flows through the blade wheels  57   a ′,  57   b ′,  57   c ′ at an inclined angle in relation to the axis of rotation of the rotor  61 ′, the vapor turbine  51 ′ is additionally a diagonal turbine. The construction as a reaction turbine means that the vapor exits out of the nozzle  77 ′ at a relatively high pressure, and the vapor pressure is reduced in the blades of the blade wheels  57   a ′,  57   b ′, and  57   c ′. Therefore, there is an energy conversion of the vapor in the blades of the blade wheels  57   a ′,  57   b ′,  57   c ′, which is composed of the velocity conversion of the vapor and, in addition, the back pressure occurring upon relaxation of the vapor. Therefore, multiple pressure stages are implemented within the vapor turbine  51 ′, which have a low staged pressure gradient and therefore achieve a favorable flow design and a good dynamic efficiency.  
         [0054]     Furthermore, an alteration of the vapor turbine  51 ′ illustrated in  FIG. 8   a  is shown in  FIG. 8   b  in the form of the vapor turbine  51 ″. The basic construction of the vapor turbine  51 ″ generally corresponds to that of the vapor turbine  51 ′ and identical elements of the vapor turbine  51 ″ in comparison to the vapor turbine  51 ′ have identical reference numbers. The vapor turbine  51 ″ generally differs from the vapor turbine  51 ′ through a different geometric design of the blade wheels  57   a ″,  57   b ″,  57   c ″, the deflection wheels  79   a ″,  79   b ″, and  79   c ″, and the partition wall  85 ″. The blade wheels  57   a ″,  57   b ″,  57   c ″ each differ from one another through different diameters.  
         [0055]     In addition, the geometry of the blades of the blade wheels  57   a ″,  57   b ″,  57   c ″ differs to produce velocity and/or pressure stages within the vapor turbine  51 ″.  
         [0056]     Correspondingly, the shape of the partition wall  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 to the different geometry of the blade wheel  57   a ″ in comparison to the vapor turbine  51 ′. Finally, the deflection wheels  79   a ″,  79   b ″, and  79   c ″ are implemented in such a way that the blades which they comprise guide the working medium  73 ″ flowing through the blade wheels  57   a ″,  57   b ″,  57   c ″ diagonally in relation to the axis of rotation of the rotor  61 ″.  
         [0057]     The embodiments of a thermal combustion engine according to the present invention illustrated in  FIGS. 1 through 8   b  are jointly distinguished in that the rotor generally completely surrounds the vapor generation 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 according to the present invention of a thermal combustion engine will now be described on the basis of  FIGS. 9 through 11 , in which the vapor generation device and/or the condensation device is generally completely and/or partially surrounded by the stator. These thermal combustion engines also have the advantages that they have a relatively low power to weight ratio, a high efficiency, low pollutant and noise emissions, and a simple, low-maintenance, and low-wear construction. In particular, these thermal combustion engines, which are constructed as external rotor motors, also have the advantage that the centrifugal force causes a centrifugal force closure to be implemented between the condenser and the vaporizer, so that additional feed pumps may be dispensed with.  
         [0058]     A sixth embodiment of a thermal combustion engine is illustrated in  FIG. 9  in the form of a vapor turbine  101 , or rather a compact vapor turbine, having an integrated vapor generation zone. The construction of the vapor turbine  101  is similar to that of the vapor turbine  1 ″ illustrated in  FIGS. 5 and 6 . Thus, the vapor turbine  101  comprises a stator  103 , which in turn comprises a fixed shaft  105 .  
         [0059]     In contrast to the embodiments according to the present invention illustrated in  FIGS. 1 through 8   a , a front wall  107  of the vapor turbine  101  is connected to the shaft  105 , and thus forms a part of the stator  103 . Furthermore, the shaft  105  is connected via the front wall  107  to a first blade wheel  109  and a second blade wheel  111 . In contrast, a peripheral wall  113  and a front wall  115  are mounted so they are rotatable in relation to the stator  103 . These walls  113 ,  115  thus form a rotor  117 . Furthermore, partition walls  119 ,  121 , and  123  are connected to the rotor for secure rotational driving.  
         [0060]     Furthermore, a flow guiding wheel  125  is positioned on the partition wall  121 . This flow guiding wheel  125  is mounted so that it is rotatable on the shaft  105  via a bearing  127 . However, mounting the flow guiding wheel  125  on the shaft  105  is not absolutely necessary. In particular, the rotor  117  may be mounted sufficiently via the sealing devices  133 , so that the bearing  127  may be dispensed with.  
         [0061]     The interior of the vapor turbine  101  is subdivided using the preferably thermally insulating wall  121  into a first chamber  129  and a second chamber  131 . In this case, the first chamber  129  acts as a vapor generation chamber, while the second chamber  131  acts as a condensation chamber. The second chamber  131  is sealed in the area of the transition of the front wall  107  to the peripheral wall  113  by a sealing device  133 . The sealing device  133  may be implemented in a form generally known to those skilled in the art. Thus, the sealing device  133  may particularly comprise sealing elements, in the form of O-rings and/or a labyrinth system, for example. However, it is important for the mode of operation of the vapor turbine  101  that the sealing device  133  ensures a seal of the second chamber  131  and simultaneously allows a rotation of the rotor  117  in relation to the stator  103 . Therefore, in the vapor turbine  101 , the vapor generation device in the form of the first chamber  129  is generally completely surrounded by the rotor  117 , while the condensation device in the form of the second chamber  131  having the front wall  107  is generally completely surrounded by the stator  103 .  
         [0062]     In the following, the mode of operation of the vapor turbine  101  will be explained. Similar to the embodiments described above, combustion gases  135  are incident on the front wall  115  in accordance with the countercurrent principle. This causes heating of the first chamber  129 , which results in a working medium  137  being vaporized. The working medium  137  enters the second chamber  131  between the partition walls  121 ,  123  and through the nozzles  139 . The vaporized working medium hits the first blade wheel  109  there, which results in driving of the rotor  117  in relation to the stator  103 .  
         [0063]     After passing through the first blade wheel  109  connected to the stator  103 , the vaporized working medium hits the flow guiding wheel  125  connected to the rotor  117 , through which the rotor  117  is driven further. After exiting the flow guiding wheel  125 , the working medium finally at least partially hits the second blade wheel  111  connected to the stator  103  via the front wall  107 . In order to achieve condensation of the working medium in the area of the second chamber  131 , cooling air  141  flows along the side of the front wall  107  facing away from the chamber  131  in accordance with the countercurrent principle.  
         [0064]     The condensed working medium collects in the area of the peripheral wall  113  because of the rotational movement of the rotor  117 , dog elements, preferably in the form of blades, being positioned in the area between the front wall  107  and the partition wall  119 , which rotate together with the rotor  117 , and are particularly attached thereto. These dog elements are not absolutely necessary, however, but elevate the operational reliability of the centrifugal force closure by the working medium  137 .  
         [0065]     The working medium  137  then flows back into the first chamber  129  between peripheral wall  113  and partition wall  119 . The working medium  137  also ensures in the vapor turbine  101  that a closure is achieved between the first chamber  129  and the second chamber  131  in the area of the partition wall  119  and the peripheral wall  113 , so that the working medium  137  must always go from the first chamber  129  into the second chamber  131  by the path via the nozzle  139 . The vapor turbine  101  offers the advantage that the front wall  107  does not execute a rotational movement, because of which there is particularly laminar flow of the cooling air  141  along the front wall  107 . Therefore, the efficiency of the condensation device in the form of the second chamber  131 , and thus the efficiency of the vapor turbine  101 , are increased.  
         [0066]     Furthermore, this construction of the vapor turbine  101  makes the supply of a cooling medium into the front wall  107  easier. Thus, the front wall  107  may be permeated by flow devices (not shown) in the form of channels. These channels may particularly be part of a closed cooling loop, in which a cooling fluid, such as water, is circulated. Because the front wall  107  is connected to the shaft  105  of the stator  103 , this cooling medium may be supplied through a channel positioned on the shaft  105  or permeating the shaft. Through this further cooling possibility, the efficiency of the vapor turbine  101  may be increased further.  
         [0067]     A seventh embodiment of a thermal combustion engine according to the present invention is illustrated in  FIG. 10  in the form of a vapor turbine  101 ′, or rather a compact vapor turbine, having an integrated vapor generation zone. The construction of the vapor turbine  101  ′ generally corresponds to that of the vapor turbine  101 , which is illustrated in  FIG. 9 . In particular, the vapor turbine  101 ′ may have the dog devices in the area of the partition wall  119  and the front wall  107  described in regard to the vapor turbine  101 . Elements of the vapor turbine  101 ′ identical to the vapor turbine  101  have identical reference numbers, while different elements are provided with identical reference numbers and a single apostrophe.  
         [0068]     The construction of the vapor turbine  101 ′ generally differs from the construction of the vapor turbine  101  in that both the condensation device and also the vapor generation device are generally completely surrounded by a stator  103 ′. The stator  103 ′ comprises a shaft  105 ′ which is connected to both the front wall  107  and also a front wall  115 ′. The front wall  115 ′ is therefore not surrounded by the rotor  117 ′. The rotor  117 ′ generally comprises the peripheral wall  113 ′ which is connected to the partition walls  119 ,  121 ,  123 . Furthermore, the flow guiding wheel  125  is attached to the partition wall  123 .  
         [0069]     To seal the first chamber  129 ′, which is used as the vapor generation device, the peripheral wall  113 ′ is connected via sealing device  143 ′ to the front wall  115 ′. Through this construction of the vapor turbine  101 ′, in addition to the front wall  107 , the front wall  115 ′ also remains fixed during operation of the vapor turbine  101  ′. The efficiency of the vapor generation device  129 ′ is thus increased, since the combustion gases  135  supplied to the front wall  115 ′ are not eddied. Therefore, better heat exchange with the first chamber  129 ′ is achieved and thus the efficiency of the entire vapor turbine  101  ′ is further increased.  
         [0070]     A further increase of the efficiency of the vapor turbine  101 ′ may be achieved in that the front wall  115 ′ may have a further flow device in the form of channels permeating the front wall  115 ′, through which a heating medium, preferably supplied via the shaft  105 ′, is circulated. Flow devices in the form of channels may be provided in the front wall  107  analogously as described previously on the basis of the vapor turbine  101 .  
         [0071]     Finally, an eighth embodiment of a thermal combustion engine according to the present invention in the form of a vapor turbine  101  ″ is illustrated in  FIG. 11 . The construction of the vapor turbine  101  ″ is comparable to that of the vapor turbine  101 ′ illustrated in  FIG. 10 . Identical elements of the vapor turbine  101 ″ have identical reference numbers as the elements of the vapor turbine  101 ′, while differing elements have identical reference numbers, but with a double apostrophe.  
         [0072]     The two vapor turbines  101 ′ and  101 ″ differ from one another essentially in that the front walls  107 ″ and  115 ″ are generally implemented in two parts. Thus, the front wall  107 ″ comprises the parts  107   a ″ and  107   b ″. In this case, the front wall part  107   b ″ is connected to the shaft  105 ″, while the front wall part  107   a ″ is connected to the peripheral wall  113 ″. This offers the advantage that the sealing devices  133 ″ are not positioned in the area of the working medium  137 , and a seal may thus be achieved more easily.  
         [0073]     Analogously, the front wall  115 ″ is implemented in two parts, in the form of the first front wall part  115   a ″ and the second front wall part  115   b ″. The front wall part  115   a ″ is connected to the peripheral wall  113 ″, while the front wall part  115   b ″ is connected to the shaft  105 ″. Because of this construction, both the first chamber  129 ″, having the front wall  115 ″, which is used as the vapor generation device, and also the second chamber  131 ″, having the front wall  107 ″, which is used as the condensation device, are surrounded partially by both the rotor  117 ″ and also the stator  103 ″.  
         [0074]     In further embodiments of the present invention (not shown), the vaporized working medium exiting out of the first chamber may first hit the blade wheel(s), with a flow guiding wheel operationally linked to the rotor interposed. Particularly if a single blade wheel is used to exploit the energy residing in the vaporized working medium, a flow guiding wheel operationally linked to the rotor, which particularly acts as a blade wheel, may be downstream from this blade wheel. In addition, the arrangement of the deflection wheel, the flow guiding wheel, and/or the blade wheel is not restricted to an axial arrangement in relation to one another. In order to implement high compactness of the thermal combustion engine of the present invention, these wheels may particularly be positioned at least partially radially in relation to one another.  
         [0075]     In further embodiments of the present invention (not shown), the thermal combustion engine may be implemented in the form of back pressure turbines and/or extraction turbines, in which vapor generated through additional extraction devices in the vapor generation chambers may be taken from the vapor turbines.  
         [0076]     A use of the thermal combustion engine according to the present invention in the form of a topping and/or exhaust vapor turbine may also be performed, in that additional vapor may be supplied to the thermal combustion engine externally, in addition to the vapor generated within the thermal combustion engine.  
         [0077]     In regard to the exemplary embodiments of the present invention described above, it is to be noted that, as may be seen in particular on the basis of the vapor turbine  1 ′ illustrated in  FIGS. 3 and 4 , the working medium may have a flow course within the thermal combustion engine that is tailored to the particular requirements of the thermal combustion engine. Thus, it is possible in particular that the working medium may flow axially, radially, or even transversely in sections, particularly both radially toward an axis of the thermal combustion engine and also away from this axis. The present invention is thus particularly not restricted to the flow paths of the working medium illustrated as examples.  
         [0078]     The features of the present invention disclosed in the above description, in the figures, and in the claims are exemplary only and may be used to implement the present invention in various embodiments both individually and in any arbitrary combination.