JP2006522256A - Heat engine and its use for converting thermal energy to mechanical energy - Google Patents

Abstract

The present invention includes at least one vapor generator for at least partially evaporating a first liquid working medium utilizing a heat engine of supplied thermal energy and a first evaporated to generate mechanical energy. And at least one rotor that is operable around the first rotation axis relative to the at least one stator, and condenses the first working medium evaporated after the rotor is driven. In a heat engine for converting from thermal energy to mechanical energy comprising at least one condensing device for the purpose, it relates to a heat engine in which the rotor essentially completely surrounds the stator, and to the use of the heat engine according to the invention.

Description

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

  A number of heat engines are known from the prior art. For example, Patent Document 1 discloses an apparatus and method for generating flow energy in liquid from heat. The apparatus includes a casing comprising a steam inlet opening connected here to the evaporator and a steam outlet opening connected to the condenser. Furthermore, the casing has a front flow opening connected to the hydromotor and a reflux connection connected to the front flow opening. A rotor having a plurality of cells each having a piston is disposed inside the casing. Pumping of hydraulic fluid by a hydromotor is achieved by supplying steam under pressure through the steam inlet opening, discharging steam from the steam outlet opening, and rotating the rotor. However, the disadvantage of the device is that it is expensive and has a large structural space due to the multi-part structure of the device, and therefore cannot be compactly configured. More particularly, a pump is necessary to supply again the liquid condensed in the condenser to the evaporator.

  Further, Patent Document 2 discloses a steam engine for driving a generator. The steam engine includes a rotary piston engine that is incorporated into the closed steam circulation system. The steam circulation system includes a steam generator, a steam injector for injecting steam into the rotary piston engine, and a condenser for condensing the steam exiting the rotary piston engine. Combustion is performed to give a heat shock to a steam generator composed of a bundle of circular tube groups inside the steam engine. Steam exiting the steam generator is supplied to the rotary piston engine and then flows through a bundle of separate tubes that are used to preheat the combustion air. The steam partially cooled in this way is supplied to the condenser, and the water condensed in the condenser is subsequently supplied again to the steam generator via the pump. However, the shortcomings in the steam engine are compact due to the large number of necessary components including the structurally expensive structure and the pump for feeding the water condensed in the condenser in the steam generator. It is inferior to sex. Furthermore, the rotary piston engine is prone to wear, resulting in high maintenance costs.

  Furthermore, heat engines including steam turbines are known from the prior art. Steam generated in an external steam generator is supplied to the steam turbine so that a rotor having an impeller disposed in a casing is driven. The steam exiting the casing after flowing out through the impeller is condensed, and the working medium thus condensed is supplied again to the steam generator via the pump. However, a drawback with this steam turbine is that additional components, particularly valves, control elements or pumps are required to achieve the conversion of thermal energy into mechanical energy. In particular, this type of heat engine, when used in a steam turbine, has a high output weight, i.e. a weight relative to the bleedable output due to the large number of individual components.

German Patent Application Publication No. 19948128 A1 specification US Patent Application Publication No. 2002/0194848 A1

  The object of the present invention is therefore to provide a heat engine which overcomes the drawbacks of the prior art. The conversion from thermal energy to mechanical energy should be achieved by achieving a particularly low output weight, high efficiency, low emissions of harmful substances and noise, simple structure with low maintenance and wear.

  According to the invention, this object is achieved in the first configuration by at least one steam generator for at least partially evaporating the first liquid working medium using a heat engine of thermal energy supplied by the heat engine. At least one rotor capable of being driven utilizing the evaporated first working medium to generate mechanical energy and rotatable about a first axis of rotation relative to the at least one stator; At least one condensing device for condensing the first working medium evaporated after driving, the rotor essentially completely surrounding the stator, and the rotor essentially completely comprising the steam generator and the condensing device It is solved by.

  An object of the present invention, which is alternative to the above configuration, is that in the second configuration, at least one for at least partially evaporating the first liquid working medium using a heat engine of supplied thermal energy. At least one steam generator and at least one rotatable about a first axis of rotation relative to the at least one stator, and capable of being driven utilizing the vaporized first working medium to generate mechanical energy Solved by a heat engine comprising a rotor and at least one condensing device for condensing the first working medium evaporated after driving the rotor, wherein the rotor surrounds the stator at least in regions.

  In the second configuration, it can be considered that the rotor essentially completely comprises a steam generator and / or a condenser.

  In both of the above embodiments, the stator may essentially completely include a steam generator and / or a condenser according to the present invention.

  As an alternative to both of the above embodiments, the steam generator and / or the condensing device is formed at least in a split type, and the rotor is the first part of the condensing device and / or the first of the steam generating device. It can also be envisaged that the part comprises and the stator comprises the other part of the steam generator and / or the condenser.

  Here, in an advantageous embodiment according to the invention, at least one first chamber forming a steam generator, at least one second chamber forming a 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 are separated from each other by at least one, in particular thermally insulating wall, at least in each region.

  In the alternative embodiment described above, at least one comprising a first chamber for discharging the first working medium evaporated by the heat engine and the turbine chamber, preferably comprising at least one first nozzle. In the first coupling device, the shape and / or orientation of the nozzle opening is preferably adjustable and at least one first formed in at least one first tube and / or in particular a thermally insulating wall. Including an opening.

  In both alternative embodiments, the turbine chamber and the second chamber for discharging further evaporated first working medium are connected, preferably at least one first nozzle comprising at least one second nozzle. Two coupling devices, preferably a coupling device in which the shape and / or orientation of the nozzle opening is adjustable, and at least one second formed in at least one second tube and / or in particular a thermally insulating wall. Two openings may be provided.

  Also in both the above embodiments, preferably in the form of first and / or second valves, which are operatively connected to at least one first and / or second coupling device which is operatively connected to the first coupling device. At least one second flow control and / or regulating device has been proposed.

  A preferred embodiment of the heat engine according to the invention is at least one formed in a particularly preferably insulating wall connecting the first chamber and the turbine chamber for discharging the liquid first working medium. At least one third coupling device in the form of three third openings is used.

  Also, at least one in the form of at least one fourth opening connecting the turbine chamber for discharging the liquid first working medium and the second chamber, preferably formed in a particularly insulating wall. A fourth connecting device may be provided in the heat engine according to the present invention.

  In both alternative embodiments described above, according to the present invention, the first working medium flowing out of the first chamber is caused by the liquid first working medium to evaporate from the first chamber during rotation of the rotor, in particular by centrifugal force acting on the working medium. It is proposed to prevent this by a third and / or fourth coupling device and in particular to block the third and / or fourth opening.

  Furthermore, according to the invention, preferably at least one third and / or fourth coupling device operatively connected with the third coupling device, preferably in the form of a third and / or fourth valve, in particular a check valve. At least one fourth flow control and regulation device that is operatively connected has been proposed.

  In particular, it can be considered to form the second chamber and the turbine chamber as one.

  In the above embodiment of the heat engine according to the present invention, at least one flow derivative may be provided which is formed in the first chamber, the second chamber and / or the turbine chamber.

  An advantageous embodiment of the heat engine according to the invention comprises a first working medium, in particular an axis, surrounded by a stator, preferably evaporated to rotate the rotor relative to the stator via a first coupling device. It is characterized by at least one first impeller that can be supplied in a direction, radial direction and / or below a predetermined angle relative to the first axis of rotation.

  The embodiment of the heat engine according to the present invention is characterized in that the first impeller is operatively connected to the rotor, in particular capable of being reliably coupled to the rotor in a rotationally linked manner, and upstream and / or downstream of the evaporated working medium. At least one flow guide wheel arranged relative to the flow guide wheel, preferably at least per region concentrically with the first impeller, in particular within the first impeller and / or It is arranged outside. In particular, the arrangement of the flow guide ring on the upstream side of the working medium evaporated relative to the first impeller improves the efficiency.

  Both of the above embodiments of the heat engine according to the invention can be characterized by at least one second impeller arranged on the downstream side of the working medium which is surrounded by the stator, in particular relative to the flow guide wheels and which has evaporated. Preferably, at least one diverting wheel that is operatively connected to the rotor relative to the second impeller and that can be reliably coupled to the rotor is preferably disposed upstream and / or downstream of the evaporated working medium. In particular, the turning wheels are arranged concentrically with the first and / or second impeller at least in each region, in particular inside and / or outside the first and / or second impeller. ing.

  In the above three alternative embodiments, the present invention particularly includes a first impeller, a flow guide wheel, a second impeller, and / or a turning wheel disposed at least partially in the turbine chamber. Consider that.

  Also, it is proposed that the second impeller has a second diameter different from the first diameter of the first impeller and / or a number or shape of blades different from the number or shape of the blades of the first impeller. Is done.

  An advantageous embodiment of the heat engine according to the invention also features a number of second impellers and / or turning wheels, which preferably have different diameters, different shapes and / or different from each other. The turning wheels have different diameters, different shapes and / or different numbers.

  Also, the shape and / or position of at least one vane of the first impeller, at least one second impeller, flow guide wheel and / or at least one turning wheel is preferably adjusted during operation of the heat engine Can be considered possible.

  Furthermore, the invention comprises a steam generator, in particular a steam generator of the first chamber, preferably in the form of a fluid heating medium, in particular in the form of a high temperature gas such as combustion gas, and with a particularly high heat transfer material and In the form of a heating source, such as in the form of at least one heating spindle incorporated into the wall of a first chamber structured for high convective heat transport and / or formed on the surface of said wall. At least one first flow device for heating fluid and / or at least one first structure and / or first formed outside the wall of the first chamber, in particular through which the heating fluid can flow. At least one heating means for applying a thermal shock in the form of at least one second structure, which is formed on the inside of the chamber wall, preferably through which the evaporated working medium can flow. To draft.

  In the above embodiment, the first flow device is integrated into the wall, the heating means of the first flow device is preferably supplied via the shaft of the stator and / or the heating means is in particular the first It can be proposed to be circulated in a preferably closed heating circulation system including a flow device.

  Furthermore, according to the invention, the condenser, in particular the second chamber, preferably in the form of a fluid refrigerant, in particular in the form of nitrogen or cooling air, particularly preferably contains a highly heat-conducting material and / or has a high convective heat transport. In the form of a cooling source, such as in the form of at least one Peltier element incorporated into the wall of a second chamber structured for and / or formed on the surface of said wall, such as nitrogen or cooling air At least one second flow device for the cooling fluid and / or at least one third structure and / or second formed outside the wall of the second chamber, in particular through which the cooling fluid can flow. At least one coolant is provided for impacting the cooling air, particularly in the form of at least one fourth structure formed inside the chamber wall, through which the working medium can flow. It is.

  Also in the above embodiment according to the present invention, the second flow device is incorporated in the wall, the refrigerant of the second flow device is preferably supplied via the shaft of the stator, and / or the refrigerant is particularly It has been proposed to be circulated in a preferably closed cooling circulation system comprising two flow devices.

  In the above four alternative embodiments, according to the present invention, the heating fluid has a flow direction extending essentially radially outward from the first axis of rotation toward the outer periphery of the rotor in the region of the heating means, And / or it is considered advantageous that the cooling fluid has a flow direction extending essentially radially in the region of the refrigerant from the outer circumference of the rotor in the direction of the first axis of rotation.

  Further, in at least one supply device for supplying at least one vaporous second working medium, a supply device preferably having the same first and second evaporated working media may be provided.

  Furthermore, an advantageous embodiment of the invention provides at least one drawing device for discharging at least part of the evaporated and / or liquid first working medium.

  Preferably at least one fifth flow control and / or regulating device and / or regulating device operatively connected to the supply device is provided. ing.

  Finally, according to the invention, a steam generator, a condenser, a first, a second, a third, a fourth, a fifth and / or a sixth flow control and / or a first and / or a second nozzle of a regulating device A first impeller, at least one second impeller, a flow guide wheel and / or at least one turning wheel, a heating means, a cooling means and / or a sensor for measuring the rotational speed of the rotor. At least one control and / or adjustment unit is proposed.

  The invention further contemplates the use of the heat engine according to the invention as a pre-turbine, exhaust turbine, back pressure turbine, bleed turbine, isobaric turbine and / or overpressure turbine.

  Thus, in the present invention, the embodiment of the steam turbine is based on the surprising recognition that a structurally simple heat engine structure can be realized in the form of an external roller in which a steam generator and a condenser are incorporated in the rotor. It has been. In particular, a heat engine can be provided which eliminates control and / or feed elements such as valves or pumps for feeding working medium from the evaporator to the condenser. By incorporating an evaporator and a condenser into a rotor that rotates around a stator having at least one impeller, the invention allows automatic feeding of the working medium from the condenser to the evaporator to act on the working medium by rotation. Achieved through centrifugal force. Further, the centrifugal force acting on the working medium along with the rotational movement of the rotor causes the working medium itself to pass through a connecting passage extending from the condenser to the evaporator, and only the steam generated in the evaporator is discharged from the evaporator. Guarantees a reachable seal in the condenser by impinging on the impeller and thereby causing rotation of the rotor. In particular, the centrifugal force acting on the working medium by the rotation of the rotor is based on the hydrostatic pressure caused by the centrifugal force relative to the pressure in the condenser even when the pressure inside the evaporator is large. It is possible that the transfer of the vapor-like working medium from is possible only after the rotation of the impeller by the above method. That is, the centrifugal sealing between the condenser and the evaporator is realized by the structure of the heat engine according to the present invention. Furthermore, this centrifugal force sealing is also used as a pump for feeding the working medium from the condenser to the evaporator. This results in that an additional supply pump or the like can be omitted. Furthermore, the structure of the steam turbine as an external roller enables high efficiency of the heat engine. For example, the heating of the machine on the evaporator side with combustion gas, for example the cooling on the condenser side with cooling air, is preferably carried out according to the invention on the convection principle, otherwise any flow direction of the refrigerant or heating medium is possible It is. The efficient use of the combustion gas is here where the hot combustion gas heats the region near the axis of the rotor, so that particularly hot steam from the steam generator is directed, in particular through the nozzles, to the stator impeller. Is achieved by This combustion gas then flows in the radial direction from the rotating shaft of the rotor toward the outer periphery of the rotor, and the liquid working medium in which the combustion gas cooled there is boiled on the outer periphery of the rotor by centrifugal force. The steam generated at that time moves in the direction of the rotor axis of rotation in the rotor and is continuously heated by the temperature of the combustion gas becoming higher in that direction, resulting in, for example, isobaric expansion. . On the condenser side, the cooling air flows from the outer periphery of the rotor in the radial direction with respect to the rotation axis of the rotor toward the outside of the rotor. In this way, it is achieved that the steam flowing radially outward from the rotary shaft inside the rotor is further cooled and condensed. Therefore, the structure of the heat engine according to the present invention enables the use of the convection principle for heating and cooling the working fluid in the form of an external roller as a steam turbine, which leads to an improvement in the efficiency of the heat engine.

  Other features and advantages of the present invention will be apparent from the following specification, in which preferred embodiments of the invention are illustrated by way of example with the aid of schematic drawings.

  1 and 2 show a first embodiment of a heat engine according to the present invention in the form of a steam turbine 1 or a compact steam turbine comprising a steam generation zone. The steam turbine 1 includes a stator 32. The stator 32 includes a fixed shaft 5 and an impeller 7 connected to the shaft 5. The rotor 11 is pivotally supported by the front walls 11a and 11c and the peripheral wall 11b so as to be relatively rotatable with respect to the stator 3 via the bearing 9 and the seal 10 so that the inside of the rotor 11 is sealed. The rotor 11 basically includes a first chamber (combustion chamber) 13 and a second chamber 15. The chambers 13 and 15 are partitioned from each other by the heat insulating wall 17 up to the opening 19 of the wall 17 in the region of the peripheral wall 11 b of the rotor 11. A working medium 21, preferably water, may flow through the opening 19 from the second chamber 15 into the first chamber 13 as will be described in detail below. As shown in FIGS. 1 and 2, the working medium 21 gathers on the peripheral wall 11 b of the rotor 11 by the centrifugal force acting on the working medium 21 when the rotor 11 rotates. Further, the first chamber 13 is separated by a partition wall 23 from a turbine chamber 25 in which the impeller 7 is disposed. An opening is formed in the form of a nozzle 27 inside the partition wall 23. Here, the mode of operation of the steam turbine 1 will be described below.

  The combustion gas 29 of a heating device (not shown) is supplied to the rotor 11. The rotor 11 exists on the first front wall 11 a located on the side facing the first chamber 13. As can be seen from FIG. 1, the combustion gas 29 is supplied so that the combustion gas is guided along the rotor 11 radially outward from the rotation axis of the rotor. Since the working medium 21 existing in the region of the first chamber 13 is heated, the first front wall 11a of the rotor 11 is heated by the combustion gas 29, and finally in the first first chamber 13. At least partial evaporation of the working medium 21 occurs. The first chamber 13 thereby acts as a steam generation chamber. By adjusting the heat supply by controlling or adjusting the amount of the combustion gas 29 to be supplied or its temperature, the output delivered from the steam turbine 1 or its rotational speed can be controlled or adjusted.

  In order to enable efficient heat exchange between the combustion gas 29 and the interior of the first chamber 13 or the steam generation chamber, there are a plurality of heat engine elements not shown. These heat engine elements are present on the first front wall 11 a of the rotor 11 in the region of the first chamber 13, preferably on the side facing the combustion gas 29 and on the side facing the first chamber 13. To do. The combustion medium 29 or the working medium 21 that evaporates in the first chamber 13 flows through the heat engine element. In particular, the front wall 11a of the rotor 11 includes a highly heat conductive material.

  The working medium 21 that evaporates moves from the peripheral wall 11 b toward the rotation axis of the rotor 11 inside the first chamber 13. Thereby the convection principle is realized in the steam turbine 1. This results in an efficient utilization of the energy of the combustion gas 29. The high-temperature combustion gas 29 collides with the region of the first chamber 13 facing the rotation axis of the rotor 11, and as a result, particularly high steam is generated in the region. The combustion gas 29 moving in the radial direction of the rotor 11 is then cooled again, and the working medium 21 is boiled in the region of the peripheral wall 11 b of the rotor 11. Thereby, efficient use of the thermal energy of the combustion gas 29 is achieved.

  The working medium 21 heated in the region of the peripheral wall 11b of the rotor 11 flows in the direction of the partition wall 23 through the first chamber 13 or the steam generation chamber, and the working medium expands to an equal pressure. As a result, a high internal pressure is generated inside the first chamber 13, and the level of the working medium 21 is recognized in the region of the first chamber 13 and lower than that of the second chamber 15. Thus, the steam generated in the first chamber 13 flows through the nozzle 27, where it expands in an adiabatic manner. In particular, as can be seen from FIG. 2, the nozzle 27 is oriented in a tilted manner rather than in the radial direction, so that a suitable tilt angle of the nozzle 27 can be adjusted. Therefore, the steam collides with the impeller 7 so as to cause a reaction of the rotor 11 relative to the stator 3, and the rotational motion of the rotor 11 is generated or maintained.

  After being discharged through the impeller 7, the steam flows from the turbine chamber 25 into the second chamber 15 which is used as a condensation chamber. Therefore, condensation of the working medium 21 occurs in the region of the second chamber 15 together with the cooling of the steam.

  Due to the rotation of the rotor 11, the condensed working medium 21 gathers on the peripheral wall 11 b of the rotor 11. In order to achieve cooling of the vapor-like working medium 21 in the second chamber 15 acting as a condensation chamber, a cooling gas 31 is supplied to the second front face 11 c of the rotor 11. This supply is performed on the convection principle. The cold air flows as cooling air from the outside of the rotor 11 in the radial direction toward the rotation axis of the rotor 11. At that time, the cooling gas 31 is heated. On the other hand, the vapor-like working medium 21 flowing away from the rotating shaft of the rotor 11 in the radial direction inside the second chamber 15 is gradually cooled and condensed there. Thereby, the already heated cooling gas 31 can receive another heat energy in the region of the rotating shaft of the rotor 11, and the convective heat exchange between the working medium 21 and the refrigerant 31 provides a wall 11 c (not shown). Thus, preferably supported in the form of a heat exchanger element, it ensures efficient exhaust heat from the second chamber 15. The working medium 21 that is condensed in the second chamber 15 then flows into the first chamber 13 through the opening 19 in the wall 17 where it is evaporated again.

  Centrifugal force acting on the working medium 21 accelerates the working medium outward, thereby closing the opening 19, so that the vapor passes from the first chamber 13 exclusively through the nozzle 27 in the second chamber 15. Can be reached. Even when the pressure in the first chamber 13 is relatively large with respect to the pressure in the second chamber 15, the opening 19 is sealed by the working medium 21 due to the hydrostatic pressure and limited to the centrifugal force. As a result, the opening 19 is reliably closed to the vapor of the working medium 21 generated in the first chamber 13.

  A check valve may be provided inside the opening 19 for automatic start of the steam turbine 1. This check valve causes the steam initially generated in the first chamber 13 to rotate the rotor 11 by means of the nozzle 27 through the outlet, so that after the start of rotation, the opening 19 is sealed. Guaranteed by medium 21. Furthermore, in order to achieve control of the rotational speed of the rotor 11 among the nozzles 27, a sealing device such as a valve can be provided. In this case, it can be considered in particular that the valve is connected in the opening 19 and the nozzle 27 with a control and regulating device not shown. Furthermore, the rotational speed control or adjustment of the steam turbine 1 is made possible by changes in the thermal energy supplied by the combustion gas 29 and / or by changes in the tilt angle of the nozzles 27.

  3 and 4 show a second embodiment of the heat engine according to the present invention. The second embodiment is in the form of a steam turbine 1 'or a compact steam turbine having the generation zone. The steam turbine 1 ′ essentially corresponds to the structure of the steam turbine 1 shown in FIGS. 1 and 2 from its basic structure. Unlike the steam turbine 1, in the case of the steam turbine 1 ′, the corresponding elements are represented by the same reference, but with one apostrophe. The steam turbine 1 'is essentially distinguished from the steam turbine 1 by various flow derivatives of the evaporated or liquid working medium 21'. Similar to the steam turbine 1, the combustion gas 29 ′ is supplied to the first front wall 11 a ′ which is disposed on the rotor 11 ′ of the steam turbine 1 ′ on the side facing the first chamber 13 ′. This supply is also performed on the convection principle, as can be seen from FIG. The working gas 21 ′ inside the first chamber 13 ′ is heated by the combustion gas 29 ′. However, unlike the steam turbine 1, the evaporated working medium 21 'passes through the nozzle 27' using the flow derivative 14 'for the first time after turning about 180 ° and enters the turbine chamber 25' or the second chamber 15 '. Flows in. This turning around the flow derivative 14 ′ is in particular not possible because the entrained (entrained, entrained) droplets of the working medium 21 ′ cannot follow the vapor flow around the flow derivative 14 ′, thus the nozzle 27. It provides the advantage that it cannot be reached through the turbine chamber 25 'or the second chamber 15'. The entrained droplets flow in the direction of the rotation axis of the rotor 11 ′ together with the steam flow, but also move in the radial direction and collide with the flow derivative 14 ′, whereby the droplets are caused by the centrifugal force to act on the peripheral wall 11b. It is accelerated in the direction of '. Furthermore, the flow derivative 14 ′ allows the evaporated working medium 21 ′ to flow inside the first chamber 13 ′ essentially up to the axis of rotation of the rotor 11 ′, whereby the combustion gas 29 ′ in the working medium 21 ′. It is achieved that the maximum heat transfer of the energy can be carried out.

  After changing the direction of the vapor-like working medium 21 ', the working medium flows through the nozzle 27' in the radial direction of the impeller 7 '. The vapor-like working medium 21 'then flows in the second chamber 15' in the vicinity of the shaft 5 'in the direction of the front wall 11c'. This flow derivative is achieved in particular by a flow derivative 16 'arranged in the region of the impeller 7' in the second chamber 15 '. This flow derivative ensures that the vapor-like working medium 21 ′ flows in the direction of the peripheral wall 11 b ′ inside the front wall 11 c ′ relative to the cooling air 31 ′ on the convection principle. Furthermore, this flow guidance inside the steam turbine 1 ′ provides the advantage that an impeller 7 ′ having a larger diameter than the impeller 7 of the steam turbine 1 can be used compared to the steam turbine 1. Accordingly, the steam turbine 1 'can be operated at a lower rotational speed.

  The working medium 21 ′ condensed in the second chamber 15 ′ collects on the peripheral wall 11 b ′ by the rotational force and flows back into the first chamber 13 ′ through the passage 20 ′. The passage 20 'is here formed on the one hand by a peripheral wall 11b' and a partition wall 24 'which is essentially cylindrical and in particular contains flow derivatives 14' and 16 '. Here, the partition wall 24 ′ is formed to be thermally insulated in order to prevent the working medium 21 ′ from being heated inside the passage 20 ′, particularly in the region of the passage 20 ′.

  FIGS. 5 and 6 show a third embodiment of the heat engine according to the invention in the form of a steam turbine 1 ″ or a compact steam turbine. The steam turbine 1 ″ essentially consists of its basic structure in FIGS. This corresponds to the structure of the steam turbine 1 ′ shown. The elements of the steam turbine 1 "corresponding to the structure of the steam turbine 1 'are labeled with the same reference. The steam turbine 1" is essentially connected to the shaft 5 "of the stator 3" via at least one connecting member 6 ". By providing a connected impeller 7 ", it is distinguished from the steam turbine 1 '. As can be seen in particular in FIG. 6, the impeller 7 ″ surrounds the flow guide wheel 8 ″ which is concentrically connected to the rotor 11 ″ together with the wall 17 ″ via the connecting member 18 ″ as can be seen in particular from FIG. As is apparent from Fig. 6, the impeller 7 "has vanes 28", while the flow guide wheel 8 "includes the blade 30". This of the flow guide wheel 8 "relative to the impeller 7". The arrangement achieves a further improvement in the efficiency of the steam turbine 1 ″ compared to the steam turbine 1 ′. The working medium 21 'coming out of the nozzle 27 "first collides with the blade 28" of the impeller 7 ", thereby driving the rotor 11" relative to the stator 3 "to which the impeller 7" is connected. The working medium exiting from the impeller 7 "collides with the vane 30" of the flow guide wheel 8 "connected to the rotor 11". As a result, the remaining energy present in the working medium is also at least partly converted into the kinetic energy of the rotor 11 ″ by the flow guide wheels 8 ″.

  The steam turbines 1, 1 ′, 1 ″ shown in FIGS. 1 to 6 are single-stage radial turbines, which are simply provided with impellers 7, 7 ′, 7 ″, respectively, and the steam is impeller in the radial direction. 7, 7 ′, and 7 ″. In contrast, FIG. 7 shows a fourth embodiment of the heat engine according to the present invention as a steam turbine 51 or an isobaric turbine. That is, it is shown in the form of a multi-stage axial (shaft) turbine that operates according to the Curtis principle, which is a steam turbine in which the inflow and outflow pressures of the steam of the working medium in or from the impeller blades are equal. Thereby, the blades of the isobaric turbine are driven using the energy from the deceleration of the steam in the blades, in particular the steam turbine 51 has a speed stage, i.e. the speed of the steam is used stepwise. In order to achieve higher thermodynamic efficiency, in this type of isobaric turbine, a pressure stage is also generated, i.e. the pressure gradient is divided into several stages. This provides the advantage of avoiding excessive steam speeds.

  The steam turbine 51 has a stator 53 including a shaft 55. Impellers 57a and 57b are disposed on the shaft 55 so as to be separated from each other. A rotor 61 is located in the steam turbine 51 so as to be rotatable relative to the stator 53 via a bearing 59 and a seal 60. The rotor 61 has a first front wall 61a, a peripheral wall 61b, and a second front wall 61c. Further, a first chamber 63 used as a steam generation chamber and a second chamber 65 used as a condensation chamber are formed in the rotor 61. In particular, the steam turbine 51, unlike the steam turbine 1, has a compensation chamber 67 for collecting the liquid working medium 73. The first chamber 63 and the compensation chamber 67 are separated from each other via a heat insulating wall 69.

  Similar to the steam turbines 1, 1 ′, 1 ″, the combustion gas 71 is fed into the steam turbine 51 on the first front wall 61 a of the rotor 61 by the convection principle. Evaporation occurs inside the first chamber 63. The working medium 73 thus evaporated is first supplied to the impeller 57a via a pipe 75 in which a nozzle 77 is disposed at the end. The rotation of the rotor 61 is caused by the expansion of the steam in the region and the collision of the steam with the first impeller 57a.

  In order to make the energy inherent in the steam-like working medium completely available, in the steam turbine 51, the steam directed toward the first impeller 57a in the axial direction is discharged by the impeller 57a together with the rotor 61. It is considered to flow into the rotating turning wheel 79a. This turning wheel acts in particular as a rotor blade disk, and the energy inherent in the steam is converted into operating energy. Further, in the turning wheel 79a, the steam flow essentially before again impinges on the second impeller 57b, which is likewise connected to the shaft 55 in the axial direction with respect to the rotational axis of the rotor 61, before the steam flow. Cause a change of direction. After being discharged through the second impeller 57b, the steam reaches a second turning wheel 79b, which is also used as a rotor blade disk, which is also connected to the rotor 61. Thereafter, the steam flows into the second chamber 65, where the steam is cooled and condensed by using the cooling air 81 by cooling the second front wall 61c of the rotor 61. The condensed working medium 73 then flows from the second chamber 65 through the compensation chamber 67 into the first chamber 63. In this case, the working medium 73 flows through a passage 83 formed between the peripheral wall 61 b and the essentially cylindrical partition wall 85. The partition wall 85 is used for heat insulation of the peripheral wall 61b or the passage 83 on the other hand in the region where the impellers 57a and 57b and the turning wheels 79a and 79b are present. For this purpose, the partition wall 85 becomes less heat conductive. In particular, it may be considered that the partition wall 85 is formed in a hollow shape and particularly includes a heat 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 the structure of the steam turbine 51 shown in FIG. For this reason, essentially the same components of the steam turbine 51 'have the same reference numerals as the steam turbine 51, but are indicated by a single apostrophe. Unlike the steam turbine 51, the steam turbine 51 'has three impellers 57a', 57b 'and 57c'. Correspondingly, the steam turbine 51 ′ also has three turning wheels 79 a ′, 79 b ′ and 79 c ′ each connected to the rotor 61 ′. Further, the steam turbine 51 ′ is distinguished from the steam turbine 51 by being an overpressure turbine based on the shape of the nozzle 77 ′, the impellers 57a ′, 57b ′, and 57c ′ and the turning wheels 79a′79b ′ and 79c ′. . Since steam flows through the impellers 57a ', 57b', 57d 'at an angle inclined relative to the rotation axis of the rotor 61', the steam turbine 51 'is particularly a mixed flow turbine. This overpressure turbine configuration means that the steam exits the nozzle 77 'at a relatively high pressure, causing a drop in steam pressure in the blades of the impellers 57a', 57b 'and 57c'. Therefore, steam energy conversion occurs in the blades of the impellers 57a ', 57b', 57c 'composed of steam speed conversion and additionally back pressure generated when the steam relaxes. Thus, a plurality of pressure steps are formed which have a low step pressure gradient inside the steam turbine 51 'and achieve good flow formation as well as good dynamic efficiency.

  8b shows a variant of the steam turbine 51 ′ shown in FIG. 8a in the form of a steam turbine 51 ″. The basic structure of the steam turbine 51 ″ essentially corresponds to the structure of the steam turbine 51 ′. The same elements of 51 "have the same reference numbers as compared to the steam turbine 51 '. The steam turbine 51" is essentially impellers 57a ", 57b", 57c "turning wheels 79a", 79b "and 79c". As well as different from the steam turbine 51 'by the geometrically different embodiments of the partition wall 85 ". The impellers 57a", 57b ", 57c" are distinguished from each other by their different diameters. Furthermore, the blade shapes of the impellers 57a ", 57b", 57c "are distinguished in order to form a speed or pressure step inside the steam turbine 51". Correspondingly, the shape of the partition wall 85 "as well as the shape of the second chamber 65" is adapted to these different diameters. Furthermore, the tube 75 "and the nozzle 77" are likewise adapted to the different shapes of the impeller 57a "as compared to the steam turbine 51 '. Finally the turning wheels 79a", 79b "and 79c" are encompassed by them. It is formed so that the guidance of the working medium 73 "flowing through the impellers 57a", 57b ", 57c" is achieved diagonally relative to the rotational axis of the rotor 61 ".

  The embodiment shown in FIGS. 1 to 8b of the heat engine according to the invention has in common a steam generator whose rotor is essentially completely in the shape of chambers 13, 13 ′, 63, 63 ′ and chamber 15, And a condensing device having a shape of 15 ', 65, 65'. With reference to FIGS. 9 to 11, an embodiment according to the invention of a heat engine in which the steam generator or condenser is essentially entirely or partially surrounded by a stator will now be described. The heat engine also has the advantage that the heat engine has a simple structure with low output weight, high efficiency, low emissions of harmful substances and noise, and less maintenance and wear. In particular, the heat engine configured as this external roller has the advantage that it produces a centrifugal force and a centrifugal sealing between the condenser and the evaporator is realized, so that an additional supply can be omitted.

  FIG. 9 shows a sixth embodiment of the heat engine according to the present invention in the form of a steam turbine 101 or a compact steam turbine having a steam generation zone. The structure of the steam turbine 101 is similar to the structure of the steam turbine 1 ″ shown in FIGS. 5 and 6. Thus, the steam turbine 101 again includes a stator 103 including a fixed shaft 105. As shown in FIGS. 1 to 8a. Unlike the embodiment according to the present invention, the front wall 107 of the steam turbine 101 is connected to the shaft 105, thereby forming a part of the stator 103. Further, the shaft 105 is connected to the first impeller 109 via the front wall 107. It is connected to the second impeller 111. On the other hand, the peripheral wall 113 and the front wall 115 are rotatably supported relative to the stator 103. The walls 113 and 115 thereby support the rotor 117. Furthermore, the partition walls 119, 121 and 123 are securely connected to the rotor in conjunction with the rotation. The flow guide ring 125 is rotatably supported by the shaft 105 via a bearing 127. However, the support of the flow guide ring 125 is not necessarily required for the shaft 105. In particular, sufficient support of the rotor 117 is possible via the sealing device 133, so that the bearing 127 may be omitted, the interior of the steam turbine 101 is preferably the first using the insulating wall 121. The chamber 129 is partitioned into a chamber 129 and a second chamber 131. Here, the chamber 129 acts as a steam generation chamber, while the chamber 131 is used as a condensing chamber, and the sealing of the second chamber 131 is performed by the sealing device 133 on the peripheral wall 113. And in the transition region of the front wall 107. This sealing device 133 is generally known to those skilled in the art. Thus, the sealing device 133 may include a sealing member such as an O-ring and / or a labyrinth system, but it is important to the operation mode of the steam turbine 101 that the sealing device 133 is important. Guarantees the sealing of the second chamber 131 and at the same time allows rotation of the rotor 117 relative to the stator 103. In the steam turbine 101, the steam generator is essentially in the form of a chamber 129. Is completely enclosed by the rotor 117, on the other hand, the condenser is essentially completely enclosed by the stator 103 in the form of a second chamber 131 having a front wall 107.

  Hereinafter, the operation method of the steam turbine 101 will be described. Similar to the above embodiment, the combustion gas 135 collides with the front wall 115 on the convection principle. This causes heating of the first chamber 129 and causes the working medium 137 to evaporate. The working medium 137 flows into the second chamber 131 through the partition walls 121 and 123 and the nozzle 139. Then, the working medium that evaporates collides with the first impeller 109 and causes the rotor 117 to be driven relative to the stator 103. After being discharged by the first impeller 109 connected to the stator 103, the evaporated working medium collides with the flow guide wheel 125 connected to the rotor 117, whereby the rotor 117 is continuously driven. After flowing out of the flow guide wheel 125, the working medium finally collides with the second impeller 111 connected to the stator 103 at least partially via the front wall 107. In order to achieve the condensation of the working medium in the region of the second chamber 131, the cooling air 141 flows along the convection principle on the side of the front wall 107 that is remote from the chamber 131. The condensed working medium is collected in the region of the peripheral wall 113 by the rotational movement of the rotor 117, and in the region between the front wall 107 and the partition wall 119, a driving element (not shown) is preferably rotated together with the rotor 117, in particular Arranged in the form of vanes attached to the rotor. However, this driving element is not always necessary, but the operational safety of the centrifugal sealing with the working medium 137 is improved. In response to this, the working medium 137 returns to the first chamber 129 again between the peripheral wall 113 and the partition wall 119. The working medium 137 ensures that a seal between the first chamber 129 and the second chamber 131 is achieved in the region of the partition wall 119 and the peripheral wall 113 in the steam turbine 101, and as a result The medium 137 must always travel through the nozzle 139 through the passage from the first chamber 129 to the second chamber 131. The steam turbine 101 provides the advantage that the front wall 107 does not perform a rotational movement, whereby a particularly laminar flow of the cooling air 141 occurs along the front wall 107. This improves the efficiency of the steam turbine 101 as well as the efficiency of the condensing device in the form of the second chamber 131. Furthermore, the structure of the steam turbine 101 facilitates the supply of refrigerant to the front wall 107. Thus, it can be considered that the front wall 107 is realized in the form of a passage by a flow device (not shown). This passage can in particular be part of a closed cooling circulation system in which a cooling fluid such as water circulates. By connecting the front wall 107 to the shaft 105 of the stator 103, the refrigerant can be supplied through a passage disposed in or passing through the shaft 105. This another cooling method can further improve the efficiency of the steam turbine 101.

  FIG. 10 shows a seventh embodiment of a heat engine according to the invention in the form of a steam turbine 101 ′ or in the form of a compact steam turbine with a steam generation zone. The structure of the steam turbine 101 'essentially corresponds to the structure of the steam turbine 101 shown in FIG. In particular, the steam turbine 101 ′ may be provided with the drive device described for the steam turbine 101 in the region of the partition wall 119 and the front wall 107. Elements of the steam turbine 101 'that are the same as the steam turbine 101 have the same reference numerals, while the different elements have the same reference but are simply represented by apostrophes. The structure of the steam turbine 101 ′ is essentially distinguished from the structure of the steam turbine 101 by the fact that both the condenser and the steam generator are essentially completely surrounded by the stator 103 ′. Stator 103 'includes a shaft 105' that is coupled to both front wall 107 and front wall 115 '. Thereby, the front wall 115 'is not surrounded by the rotor 117'. The rotor 117 ′ includes a peripheral wall 113 ′ that is essentially connected to the partition walls 119, 121, and 123. Further, a flow guide ring 125 is attached to the partition wall 123. For sealing the first chamber 129 ′ used as a steam generator, the peripheral wall 113 ′ is connected to the front wall 115 ′ via the sealing device 143 ′. With this structural configuration of the steam turbine 101 ′, a state in which the front wall 115 ′ along with the front wall 107 remains stationary during the operation of the steam turbine 101 ′ is achieved. Thereby, the combustion gas 135 supplied to the front wall 115 'does not become a turbulent flow, so that the efficiency of the steam generator 129' is improved. Thereby, a good heat exchange with the first chamber 129 'is achieved, thereby further improving the efficiency of the whole steam turbine 101'. A further increase in the efficiency of the steam turbine 101 ′ is in the form of a passage where the front wall 115 ′ exits the front wall 115 ′ through another flow device, preferably through which a heating medium supplied via the shaft 105 ′ is circulated. Can be achieved by including. In a similar manner, the flow device may be provided in the form of a passage in the front wall 107 as described using the steam turbine 101 above.

  Finally, FIG. 11 shows an eighth embodiment of the heat engine according to the present invention in the form of a steam turbine 101 ″. The structure of the steam turbine 101 ″ is compared with the structure of the steam turbine 101 ′ shown in FIG. it can. The same elements of the steam turbine 101 ″ have the same reference numerals as the elements of the steam turbine 101 ′, while the different elements have the same reference numerals, but are indicated by two apostrophes. Both steam turbines 101 ′ and 101 "is essentially distinguished from each other by the front walls 107" and 115 "being essentially split. Thus, the front wall 107 "is composed of the portions 107a" and 107b ". Here, the front wall 107b" is connected to the shaft 105 ", while the front wall 107a" is connected to the peripheral wall 113 ". This provides the advantage that the sealing device 133 "is not arranged in the region of the working medium 137, so that an easy sealing can be achieved. In a similar manner, the front wall 115 "is formed in a divided form in the form of a first front wall 115a" and a second front wall 115b ". The front wall 115a" is connected to the peripheral wall 113 ". On the other hand, the front wall 115b ″ is connected to the shaft 105 ″. Based on this structure, the first chamber 129 ″ is used together with the front wall 115 ″ used as a steam generator, and the second chamber 131 is also used. "Is also surrounded by the rotor 117" and the stator 103 "together with the front wall 107" used as a condenser.

  In another, not shown embodiment of the present invention, the evaporated working medium exiting the first chamber is initially connected to the rotor to impinge on the impeller or group of impellers by intermediate connection of the flow guide wheels. Can be considered. In particular, when using individual impellers, it is considered that the impeller is connected to a rotor, in particular to act as an external roller, in order to use the energy inherent in the working medium that evaporates. it can. Further, the arrangement of turning wheels, flow guide wheels and / or impellers is not limited to relative axial arrangement. In order to realize the high compactness of the heat engine of the present invention, it is considered in particular that the turning wheels are arranged radially relative to each other at least in each region.

  In another, not shown embodiment of the present invention, it is contemplated that the heat engine is formed in the form of a back pressure or bleed turbine that can bleed steam generated from the steam turbine into the steam generation chamber by an additional bleed device. it can.

  In addition, the use of the heat engine according to the present invention can be implemented in the form of a front or exhaust turbine that can supply additional steam in addition to the steam generated inside the heat engine. .

  Regarding the embodiment according to the above example of the present invention, the working medium is adapted to the respective needs of the heat engine inside the heat engine, as particularly identified by the steam turbine 1 ′ shown in FIGS. Note that it may have a flow transition. In this way, in particular, it is possible for the working medium to flow axially, radially or laterally from section to section, in particular both radially with respect to the axis of the heat engine and away from said axis. That is, the present invention is not particularly limited to the exemplified flow path of the working medium.

  The features of the invention disclosed in the above specification, drawings and claims can be the essence for implementing the invention in its various embodiments both individually and in any combination.

1 is a cross-sectional view of a first embodiment of a heat engine according to the present invention. 2 is a cross-sectional view of the heat engine of FIG. 1 along the plane AA of FIG. It is sectional drawing of 2nd Embodiment of the heat engine which concerns on this invention. FIG. 4 is a cross-sectional view of the heat engine of FIG. 3 along the plane BB of FIG. 3. It is sectional drawing of 3rd Embodiment of the heat engine which concerns on this invention. FIG. 6 is a cross-sectional view of the heat engine of FIG. 5 along the plane AA of FIG. It is sectional drawing of 4th Embodiment of the heat engine which concerns on this invention. It is sectional drawing of 5th Embodiment of the heat engine which concerns on this invention. It is sectional drawing of the deformation | transformation aspect of 5th Embodiment of the heat engine which concerns on this invention of FIG. 8a. It is sectional drawing of 6th Embodiment of the heat engine which concerns on this invention. It is sectional drawing of 7th Embodiment of the heat engine which concerns on this invention. It is sectional drawing of 8th Embodiment of the heat engine which concerns on this invention.

Explanation of symbols

1, 1 ', 1 "steam turbine 3, 3', 3" stator 5, 5 ', 5 "shaft 6" connecting member 7, 7', 7 "impeller 8" flow guide wheel 9, 9 'bearing 10, 10 'seal 11, 11', 11 "rotor 11a, 11c, 11a ', 11c', 11a", 11c "front wall 11b, 11b ', 11b" peripheral wall 13, 13' chamber 14 'flow derivative 15, 15' chamber 16 'flow derivative 17, 17', 17 "wall 18" connecting member 19 opening 20 'passage 21, 21' working medium 23 partition wall 24 'partition wall 25, 25' turbine chamber 27, 27 ', 27 "nozzle 28' , 28 "blades 29, 29 'combustion gas 30" blades 31, 31' cooling air 51, 51 ', 51 "steam turbines 53, 53', 53" stators 55, 55 'shafts 57a, 57b, 57a', 57b ' , 57c '
57a ″, 57b ″, 57c ″ impeller 59, 59 ′ bearing 60, 60 ′ seal 61, 61 ′, 61 ″ rotor 61a, 61c, 61a ′, 61c ′ front 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" tube 77, 77 ', 77 "nozzle 79a, 79b, 79a ', 79b', 79c '
79a ", 79b", 79c "Turning wheels 81, 81 'Cooling air 83, 83' Passage 85, 85 ', 85" Partition walls 101, 101', 101 "Steam turbine 103, 103 ', 103" Stator 105, 105 ', 105 "shaft 107, 107" front wall 107a ", 107b" front wall 109 impeller 111 impeller 113, 113', 113 "peripheral wall 115, 115 ', 115" front wall 115a ", 115b" front wall 117, 117 ′, 117 ″ rotor 119, 121, 123 Partition wall 125 Flow guide wheel 127, 127 ′ Bearing 129, 129 ′, 129 ″ Chamber 131, 131 ′, 131 ″ Chamber 133, 133 ″ Seal 135 Combustion gas 137 Operation Medium 139 Nozzle 141 Cooling air 143 ', 143 "Sealing element

Claims (32)

  Utilizing a heat engine (1, 1 ′, 1 ″, 51, 51 ′, 51 ″) of the supplied thermal energy, the first liquid working medium (21, 21 ′, 73, 73 ′) is at least partially At least one steam generator (11a, 11a ′, 11a ″, 13, 13 ′, 61a, 61a ′, 63, 63 ′) for evaporating and a first operation evaporated to generate mechanical energy First rotation relative to at least one stator (3, 3 ′, 3 ″, 53, 53 ′, 53 ″) that can be driven using the medium (21, 21 ′, 73, 73 ′) After driving at least one rotor (11, 11 ′, 11 ″, 61, 61 ′, 61 ″) rotatable around the axis and the rotor (11, 11 ′, 11 ″, 61, 61 ′, 61 ″) Evaporated first working medium (21, 21 ′, 73, 7 Converting thermal energy to mechanical energy including at least one condensing device (11c, 11c ', 11c ", 15, 15', 61c, 61c ', 65, 65', 65") for condensing ') Heat engine (1, 1 ′, 1 ″, 51, 51 ′, 51 ″) for which the rotor (11, 11 ′, 11 ″, 61, 61 ′, 61 ″) is the stator (3, 3 ′). , 53, 53 ′, 53 ″) and the rotor (11, 11 ′, 11 ″, 61, 61 ′, 61 ″) is essentially completely surrounded by the steam generators (11a, 11a ′, 11a ″, 13 ”). 13 ', 61a, 61a', 63, 63 ') and the condenser (11c, 11c', 11c ", 15, 15 ', 61c, 61c', 65, 65 ', 65") essentially completely Including heat engine.   The first liquid working medium (21, 21 ′, 73) using the heat engine (1, 1 ′, 1 ″, 51, 51 ′, 51 ″, 101, 101 ′, 101 ″) of the supplied thermal energy. 73 ′, 137) at least one vapor generator (11a, 11a ′, 11a ″, 13, 13 ′, 61a, 61a ′, 63, 63 ′, 115, 115 ′, 115 ″) and at least one stator (3, 3 ′) that can be driven using the first working medium (21, 21 ′, 73, 73 ′, 137) evaporated to generate mechanical energy. 3 ″, 53, 53 ′, 53 ″, 103, 103 ′, 103 ″) and at least one rotor (11, 11 ′, 11 ″, 61, 61) rotatable around the first rotation axis. ', 61 ", 117, 117 117 ″) and the first working medium (21, 21 ′, 73, evaporating after driving the rotor (11, 11 ′, 11 ″, 61, 61 ′, 61 ″, 117, 117 ′, 117 ″)) 73 ′, 137) at least one condensing device (11c, 11c ′, 11c ″, 15, 15 ′, 61c, 61c ′, 65, 65 ′, 65 ″, 107, 107 ′, 107 ″) A heat engine (1, 1 ′, 1 ″, 51, 51 ′, 51 ″, 101, 101 ′, 101 ″) for converting heat energy including the rotor (11, 11 ′) 11 ″, 61, 61 ′, 61 ″, 117, 117 ′, 117 ″) surrounds the stator (3, 3 ′, 53, 53 ′, 53 ″, 103, 103 ′, 103 ″) at least in each region. Heat engine.   Rotor (11, 11 ′, 11 ″, 61, 61 ′, 61 ″, 117) is a steam generator (11a, 11a ′, 11a ″, 13, 13 ′, 61a, 61a ′, 63, 63 ′, 115) 3. and / or a condenser (11c, 11c ′, 11c ″, 15, 15 ′, 61c, 61c ′, 65, 65 ′, 65 ″) essentially completely. Heat engine.   Heat engine according to claim 2 or 3, characterized in that the stator (103, 103 ") essentially completely comprises a steam generator (115) and / or a condenser (107, 107 ').   The steam generator (115 ") and / or the condensing device (107") are formed at least in a split type, and the rotor (117 ") is a first part of the condensing device (107a") and / or the steam generating device ( 115a ") and the stator (103") includes the other part of the steam generator (115b ") and / or the condenser (107b"). Heat engine.   At least one first chamber (13, 13 ′, 63, 63 ′, 129, 129 ′, 129 ″) forming a steam generator and at least one second chamber (15, 15) forming a condenser. ', 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 at least one second chamber and turbine chamber per region, in particular thermally insulating walls (17, 17 ′, 17 ″, 23, 24 ′, 69, 69 ′, 85, 85 ′, 85 " Characterized in that it is separated from each other by 121), according to claim 1 to a heat engine according to any one claim of 5.   The first chamber (13, 13 ′, 63, 63 ′) for discharging the evaporated first working medium (21, 21 ′, 73, 73 ′) and the turbine chamber (25, 25 ′) are connected. , Preferably in at least one first coupling device comprising at least one first nozzle (27, 27 ′, 27 ″, 77, 77 ′, 77 ″, 139), preferably the shape of the nozzle opening and / or Featuring a coupling device with adjustable orientation and at least one first tube (75, 75 ′, 75 ″) and / or at least one first opening formed in a particularly insulating wall. The heat engine according to claim 6.   In at least one second coupling device, preferably including at least one second nozzle, which couples the turbine chamber and the second chamber for discharging the evaporated first working medium, preferably the shape of the nozzle opening And / or a coupling device with adjustable orientation and at least one second opening formed in at least one second tube and / or in particular a thermally insulating wall. Or the heat engine of 7.   At least one second, preferably in the form of a first and / or second valve, operatively connected to at least one first and / or second coupling device operatively connected to the first coupling device. The heat engine according to claim 7 or 8, wherein the heat engine is a flow control and / or regulation device.   The first chamber (13, 13 ′) for discharging the liquid first working medium (21, 21 ′) and the turbine chamber (25, 25 ′) are connected to each other, and particularly preferably an insulating wall (17). , 17 '), characterized in that at least one third coupling device in the form of at least one third opening (19, 20') is formed. Heat engine.   At least one in the form of at least one fourth opening connecting the turbine chamber and the second chamber for discharging the liquid first working medium, preferably formed in a particularly heat-insulating wall The heat engine according to any one of claims 6 to 10, characterized by a fourth connecting device.   During the rotation of the rotor (11, 11 ′, 11 ″, 61, 61 ′, 61 ″, 117, 117 ′, 117 ″) the liquid first working medium (21, 21 ′, 73, 73 ′) In particular, due to centrifugal force acting on the working medium (21, 21 ′, 73, 73 ′, 137), the first chamber (13, 13 ′, 63, 63 ′, 129, 129 ′, 129 ″) evaporated One working medium (21, 21 ′, 73, 73 ′) is prevented from flowing out by the third and / or fourth coupling device, in particular the third and / or fourth opening (19, 20 ′) is blocked. The heat engine according to claim 10 or 11, characterized in that:   Preferably in the form of a third and / or fourth valve, in particular a check valve, at least one operatively connected to at least one third and / or fourth linking device connected to the third linking device. 13. A heat engine according to any one of claims 10 to 12, characterized by one fourth flow control and adjustment device.   14. A heat engine according to any one of claims 6 to 13, characterized in that the second chamber (15, 15 ') and the turbine chamber (25, 25') are formed as one.   Characterized by at least one flow derivative (14 ', 16') formed in a first chamber (13 '), a second chamber (15') and / or a turbine chamber (25 ') Item 15. The heat engine according to any one of Items 6 to 14.   Preferably, the first coupling device (27, 27 ', 27 ", 75, 75' surrounded by the stator (3, 3 ', 3", 53, 53', 53 ", 103, 103 ', 103") , 75 ″, 77, 77 ′, 77 ″, 139) and the rotor (11, 3 ′, 3 ″, 53, 53 ′, 53 ″, 103, 103 ′, 103 ″) relative to the stator (11). , 11 ′, 11 ″, 61, 61 ′, 61 ″, 117, 117 ′, 117 ″), the first working medium (21, 21 ′, 73, 73 ′, 137) evaporated to rotate, In particular, at least one first impeller (7, 7 ′, 7 ″, 57a, 57a ′, 57a which can be supplied axially, radially and / or below a predetermined angle relative to the first axis of rotation. ”, 109) according to any one of the preceding claims. Heat engine.   The upstream side and / or the downstream side of the evaporated working medium (21 ', 137), which is operatively connected to the rotor (11 ", 117, 117', 117"), in particular capable of being reliably coupled with the rotor in a rotationally linked manner. In at least one flow guide wheel (8 ", 125) disposed relative to the first impeller (7", 109), the flow guide wheel (8 ", 125) is preferably at least per region A flow guide wheel arranged concentrically with the first impeller (7 ", 109), in particular inside and / or outside the first impeller (7", 109). 16. Heat engine according to 16.   At least one second impeller (disposed in particular downstream of the working medium evaporated relative to the flow guide wheels surrounded by the stator (53, 53 ', 53 ", 103, 103', 103") 57b, 57b ′, 57c ′, 57b ″, 57c ″, 111), the second impeller (57b, 57b ′, 111b) preferably upstream and / or downstream of the evaporated working medium (73, 73 ′). 57b ″, 57c ′, 57c ″) and relative to the rotor (61, 61 ′, 61 ″), in particular at least one turning wheel (79a, 79b, 79b, 79b, 79a ′, 79b ′, 79c ′, 79a ″, 79b ″, 79c ″), in particular, the turning wheel is concentric with the first and / or second impeller at least in each region, First and / or wherein the impeller is disposed inside and / or outside of the second impeller, claim 16 or 17 thermal engine according to.   First impeller (7, 7 ', 57a, 57a', 57a "), flow guide wheel, second impeller (57b, 57b ', 57c', 57b", 57c ") and / or turning wheel ( 79a, 79b, 79a ′, 79b ′, 79c ′, 79a ″, 79b ″, 79c ″) are arranged at least partly in the turbine chamber (25, 25 ′). The heat engine according to any one of 16 to 18.   The second impeller has a second diameter different from the first diameter of the first impeller and / or a number or shape of blades different from the number or shape of the blades of the first impeller. The heat engine according to claim 18 or 19.   In a number of second impellers (57b ′, 57c ′, 57b ″, 57c ″) and / or turning wheels (79a, 79b, 79a ′, 79b ′, 79c ′, 79a ″, 79b ″, 79c ″), The second impellers (57b ', 57c') preferably have different diameters, different shapes and / or different numbers of blades and / or turning wheels (79a ', 79b', 79c '). 21. A heat engine according to any one of claims 18 to 20, characterized in that the second impeller and the turning wheels have different diameters, different shapes and / or different numbers.   The shape and / or position of the at least one blade of the first impeller, the at least one second impeller, the flow guide wheel and / or the at least one turning wheel is preferably adjustable during operation of the heat engine. 22. A heat engine according to any one of claims 16 to 21, characterized in that it is.   Steam generators (11a, 11a ′, 11a ″, 13, 13 ′, 61a, 61a ′, 63, 63 ′, 115, 115 ′, 115 ″, 129, 129 ′, 129 ″), particularly the first chamber ( 13, 13 ′, 63, 63 ′, 129, 129 ′, 129 ″), preferably in the form of a fluid heating medium, in particular in the form of combustion gases (29, 29 ′, 71, 71 ′, 135). At least one incorporated in and / or formed on the surface of the first chamber comprising a particularly highly heat-conducting material and / or structured for high convective heat transport In the form of a heating source, such as in the form of one heating spindle, in the form of at least one first flow device for the heating fluid (29, 29 ′, 71, 71 ′, 135), the first chamber (13 , 13 ', 63, 63 129, 129 ′, 129 ″), especially formed on the outside of the walls (11a, 11a ′, 11a ″, 61a, 61a ′, 115, 115 ′, 115 ″), heated fluids (29, 29 ′, 71). , 71 ′, 135) through which at least one first structure and / or the wall (11a, 11a) of the first chamber (13, 13 ′, 63, 63 ′, 129, 129 ′, 129 ″) can flow. ′, 11a ″, 61a, 61a ′, 115, 115 ′, 115 ″), particularly preferably the evaporated working medium (21, 21 ′, 73, 73 ′, 137) is at least capable of flowing therethrough. A heat engine according to any one of the preceding claims, characterized in that it comprises at least one heating means for applying a thermal shock in the form of one second structure.   A first flow device is integrated in the wall, the heating means of the first flow device is preferably supplied via the shaft of the stator, and / or the heating means comprises in particular the first flow device. 24. A heat engine according to claim 23, characterized in that it is circulated in a closed heating circulation system.   Condensing devices (11c, 11c ′, 11c ″, 15, 15 ′, 61c, 61c ′, 65, 65 ′, 65 ″, 107, 107 ′, 107 ″, 131, 131 ′, 131 ″), especially the second The chamber (15, 15 ′, 65, 65 ′, 65 ″, 131, 131 ′, 131 ″) is preferably in the form of a fluid refrigerant, in particular nitrogen or cooling air (31, 31 ′, 81, 81 ′, 141). ) In the form of a second chamber, particularly preferably comprising a highly heat-conducting material and / or structured for high convective heat transport and / or on the surface of said wall At least one second for a cooling fluid (31, 31 ', 81, 81', 141) such as nitrogen or cooling air in the form of a cooling source, such as in the form of at least one Peltier element formed Flow device shape And the walls (11c, 11c ′, 11c ″, 61c, 61c′m 107, 107 ′, 107 ″) of the second chamber (15, 15 ′, 65, 65 ′, 65 ″, 131, 131 ′, 131 ″). ) At least one third structure and / or second chamber (15, 15 ′, 65, in particular) through which cooling fluid (31, 31 ′, 81, 81 ′, 141) can flow. 65 ′, 65 ″, 131, 131 ′, 131 ″), which is formed inside the walls (11c, 11c ′, 11c ″, 61c, 61c ′, 107, 107 ′, 107 ″), in particular a working medium (21 21 ', 137) in the form of at least one fourth structure capable of flowing through, characterized by at least one refrigerant for giving an impact by cooling air .   A second flow device is integrated in the wall, preferably the refrigerant of the second flow device is preferably supplied via the shaft of the stator and / or the refrigerant comprises in particular the second flow device, 26. A heat engine according to claim 25, wherein the heat engine is circulated in a closed cooling circulation system.   The heating fluid (29, 29 ', 71, 71') is essentially radially outward from the first axis of rotation in the region of the heating means (11, 11 ', 11 ", 61, 61', 61"). And / or the cooling fluid (31, 31 ′, 81, 81 ′) has an essentially radial rotor (11, 11 ′, 11 ″, The heat engine according to any one of claims 23 to 26, characterized in that it has a flow direction extending from the outer periphery of 61, 61 ') in the direction of the first axis of rotation.   The at least one supply device for supplying at least one vaporous second working medium, preferably characterized in that the first and second evaporated working media are identical. A heat engine according to any one of the above.   A heat engine according to any one of the preceding claims, characterized by at least one drawing device for discharging at least part of the evaporated and / or liquid first working medium.   At least one fifth flow rate control and / or regulating device and / or at least one sixth flow rate control and / or regulating device operatively connected to the supply device, 30. A heat engine according to claim 28 or 29.   Steam generator, condenser, first, second, third, fourth, fifth and / or sixth flow control and / or regulator first and / or second nozzle, first vane At least one control operatively connected to a sensor for measuring the rotational speed of the vehicle, at least one second impeller, flow guide wheel and / or at least one turning wheel, heating means, cooling means and / or rotor A heat engine according to any one of the preceding claims, characterized in that-and / or a regulating unit.   Use of a heat engine according to any one of the preceding claims as a pre-turbine, exhaust turbine, back pressure turbine, bleed turbine, isobaric turbine and / or overpressure turbine.

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