EP2299097A2 - Thermal engine - Google Patents

Abstract

The power source heat engine uses an enclosed working gas arranged between two temperature ranges and has three heat exchangers (1A-C) each with a single connection via a pipe (4A-C) to a working cylinder (2). Each heat exchanger is connected by a valve (5A-C) to the cylinder. The heat exchangers have hot and cold surrounding flows. The working cylinder can have a piston (3) operated by expansion and compression of the working gas.

Description

Technical area

In this invention is a power plant with heat extraction, in which several of the heat engines described below, as described below and on the basis of Figures 1-18 be used in series in order to use the available heat either largely for power generation or mostly for other purposes, such as heating, or at the same time for both in any ratio to each other.

• zwei Isobaren, zwei Isochoren, zwei Isothermen.

In dieser Wärmekraftmaschine finden mehrere des oben beschriebenen Kreisprozesses gleichzeitig, aber zeitlich versetzt, statt. Die Zustandsänderungen Expansion und Kompression der einzelnen Kreisprozesse, wirken auf einen gemeinsamen Arbeitszylinder.The heat engine used in the present invention is one having an external heat source operating on the principle of the Stirling cycle process in combination with a Clausius-Rankine cycle.
The single cycle consists of six state changes:

• two isobars, two isochores, two isotherms.

In this heat engine several of the above-described cycle process take place simultaneously but offset in time. The state changes expansion and compression of the individual cycles, act on a common working cylinder.

With the increasing cost of primary energy from fossil fuels, the need for solutions that contribute to the more effective use of primary energy is growing. By warming the atmosphere, there is a compulsion to avoid fossil fuels and to increasingly use regenerable energy. The most commonly used heat engines, diesel and petrol engines, are used in road, marine and aviation, and pollute the environment through their CO ₂ emissions. For economic reasons, these engines typically consume fuels of fossil origin, such as gasoline, diesel, kerosene or natural gas. There is increasing research to be able to replace these fossil fuels with regenerable fuels. Above all, solutions are sought to fuel z. As hydrogen, rapeseed oil, biogas or other renewable energy from biomass (eg., Using the Fischer-Tropsch process) to use.

Steam and gas turbines, combined heat and power plants and generators with diesel or gasoline engines are currently used mainly for power generation heat engines. The mentioned power generators, except for steam generation for steam turbines, can only be operated to a limited extent with regenerative fuels.

All of these heat engines have one thing in common, they can convert only a relatively small part of the energy used, about 30-40%, into mechanical work and thus also into electricity. The remaining 60-70% of the primary energy is lost as heat energy if it can not be used as heating heat.

In order to take advantage of this excess energy in the absence of heating demand, various heat engines have been developed, which operate at a low temperature with an acceptable efficiency. One of these developments is the Organic Rankine Cycle (ORC), which uses organic compounds as a working substance instead of water and water vapor, whose vaporization temperatures and vapor pressures allow it to operate at low temperatures. In the recent past, some ORC plants have been put into operation. Regenerative energy, such as geothermal heat from geothermal sources, can also be put into operation with the ORC plants.

In order to save fossil fuels, the Stirling engine is being experimented to a greater extent, since it is irrelevant which fuel is used in this heat engine. The heat generation takes place independently of the power generation. The Stirling engine is already produced as standard by several companies in various designs. It is used among other things in small combined heat and power plants (CHP).

The desire to convert solar energy into electricity has given important impulses to the development of Stirling engines.

In the Stirling thermal power plant, an enclosed gas mass is periodically heated and cooled, the pressure changes caused thereby are converted by a working piston into mechanical work. The thermodynamic process ideally consists of four state changes: constant temperature compression (isothermal), constant volume heat input (isochore), constant temperature expansion (isotherm), and constant volume heat removal (isochore). The working gas is pushed at high pressures between a warm and a cold room back and forth. Between these rooms, a regenerator is connected to improve the efficiency, to which the gas flowing to the cold side releases heat and absorbs heat during the return flow.
As a low-temperature thermal power plant, the Stirling plant is economically hardly usable, since the thermodynamic efficiency is very low. The available power is largely consumed internally by the mechanical losses.

The Stirling engine as a hot gas engine and the steam power plants (including ORC plants) according to the Clausius-Rankine comparison process are the only heat engines with external heat generation used as standard.

In the Clausius-Rankine process, water or another substance under high pressure is evaporated (isobaric). The steam relaxes isentropically via a turbine into a lower pressure level and is liquefied again at constant pressure (isobaric). The condensate is pumped by means of pumps (isentropic) back to the high pressure stage. Here the process starts all over again.

The Clausius Rankine process consists of 2 isobars and 2 isentropes.

The prior art is to the documents US 4,138,847 "Heat Recuperative Engine" and DE 26 49 941 A1 "Stirling engine and method for operating the same" pointed out, of which a heat engine with heat exchangers is known, wherein a working gas each performs an isochore Wärmezu- and heat dissipation, as well as an isothermal expansion and compression as a change of state between two temperature levels. The invention is based on the object to use the waste heat resulting from many processes and that through a better utilization of the isochoric state changes in order to achieve a lower design effort at the same time.

The heat engine used according to the present invention has a relatively high efficiency even in the low temperature range. With this heat engine, among other things, a part of the waste heat from industry or power plants, which would be lost by blowing away warm or hot air, to be recovered.
Similarly, a portion of the waste heat from liquids that would be discharged via recooling systems or the like to the environment, be recovered.
Above all, a part of the heat, which usually can not be used economically because of the low temperature level, to be converted by means of this heat engine into electricity.

The basic principle of this heat engine is based on two cycle processes (the Stirling cycle and the Clausius-Rankine cycle) which run simultaneously and complement each other. The Clausius-Rankine cycle process takes place practically within the Stirling cycle in such a way that the isentropes of the Clausius-Rankine process merge into the isotherms of the Stirling cycle. The Clausius-Rankine cycle consists in this case of two isobars and two isotherms, these isotherms being part of both cycles. (Comp. Fig.16 to 18 in the drawing)

In order to create the possibility that evaporation and liquefaction can take place, an agent is chosen whose boiling point is at a correspondingly selected pressure, between the two required for the operation of the heat engine temperature levels.

The heat exchangers used (closed container with large heat transfer surface) are divided into two parts. The two halves are connected to each other by means of an insulating layer so that the heat flow is minimized via the shell from one half to the other. However, as a liquid or gas, the working substance can flow unimpeded from one half to the other.

In a working cylinder with a free piston, the state changes of the working substance are converted into work. Via connecting pipes with integrated valves, the heat exchangers are connected to the working cylinder, via which an exchange of the working material between the heat exchanger and the working cylinder can take place. Because of the free-running piston (i.e., the piston is not connected to a crankshaft or the like via a connecting rod), heat exchangers may be connected to the cylinder on both sides of the piston.

Since several cycle processes take place simultaneously in this heat engine, several heat exchangers are required. The minimum number is 3 with one-sided connection to the working cylinder. At least 6 heat exchangers are required with two-sided connection to the working cylinder, 3 on each side. The number of heat exchangers is not limited. On each side of the working cylinder, only an odd number of heat exchangers may be connected. The number of both sides must be equal.

In each connecting pipe there is a valve which is opened by a valve control (eg cam disk or by means of electric drive) during a certain period of time. In the course of the cycle the valve is opened and closed twice, once for compression and once for expansion.

The heat exchangers are arranged in a star shape around the working cylinder and rigidly connected thereto. Together with the working cylinder, they form a rotor, which constantly turns around its own longitudinal axis. In one complete revolution, a complete cycle has expired in each heat exchanger.

The piston in the working cylinder is free-running. The circular processes act on both sides of the piston. While compression on one side, expansion on the other side takes place at the same time.

The six state changes proceed in the following order (cf. Fig. 17 , PV diagram or Fig. 18 , ts-diagram).

1. Isochoric heat extraction

The working substance is cooled at a constant volume in a heat exchanger. The heat exchanger itself consists of 2 halves, which are thermally decoupled in the middle by means of insulating layer. Only one half of the heat exchanger is cooled down to the condensation temperature of the working substance.

2. Isobaric condensation

When the condensation temperature is reached, the working fluid liquefies at constant pressure and temperature. The valve between cylinder and heat exchanger opens and further vapor of the working fluid flows, due to the compression, in the heat exchanger, partly by the negative pressure in selbigem heat exchanger, partly by external pressure on the piston in the working cylinder. Because of the continuous cooling further vapor of the working fluid is liquefied.

3. Isothermal compression

While the working gas flows from the working cylinder in the heat exchanger, heat is removed from the heat exchanger. The vapor of the working fluid does not completely condense, but is compressed with simultaneous heat removal. The valve closes.

4. Isochoric heat supply

In the heat exchanger is now due to the isothermal compression a larger mass of the working substance. During the continuous rotation, the condensate of the working fluid passes from the cooled half in the other half of the heat exchanger and is heated by the heating medium to the upper temperature level here. This temperature is higher than the boiling point of the working substance. Part of the working substance evaporates. In order to avoid simultaneous condensation in the cooled part of the heat exchanger, the connection opening between the two halves is mechanically closed or the cooled part of the heat exchanger is heated by a regeneration process.

5. Isobaric evaporation

By heating the heat exchanger to the upper temperature level, the working material evaporates. The condensate of the working material evaporates until the pressure within the heat exchanger has reached the vapor pressure of the working substance at this temperature. The valve is opened again. Because of the pressure, the working fluid flows from the heat exchanger into the working cylinder, while the heat exchanger is supplied with further heat. Due to the falling pressure and continuous heat supply, another part of the condensate evaporates at constant steam pressure.

6. Isothermal expansion

After the remaining part of the condensate has evaporated, the vapor of the working fluid continues to relax in the working cylinder with simultaneous supply of heat. The valve closes.

There are several heat exchangers each connected via a connecting pipe (4) with the working cylinder. In every heat exchanger, the same process takes place. The individual processes (shown as Stirling comparison process) of the various heat exchangers take place at different times. In Fig. 13A . 13B and 13C this sequence of the various processes and their relationship to each other is shown schematically.

In Fig. 12 is a possible model of this heat engine, in which both the Stirling and the Clausius-Rankine cycle can be realized, shown schematically.

The present invention relates to a heat engine, but more particularly to one with reference to FIGS. 19 to 21 described power plant with heat extraction.

State of the art

For the better use of energy, thermal power couplings are used in many large and small power plants. In cogeneration plants which are operated according to the Rankine cycle, the steam after leaving the turbines is first partially or completely condensed via heat exchangers, the remaining steam is then condensed in the cooling tower, air condensers or in other processes. The heat recovered through the heat exchangers is then available for heating purposes in district heating or other applications.

In Organic Rankine cycle plants, part of the heat generated from combustion processes is diverted into a thermal oil cycle, which in turn vaporizes the organic material in the Organic Rankine Cycle plant to be in a Rankine Rankine Cycle a turbine and power generator to power. The heat generated by the condensation of the working fluid heats up the heating water return used or released via an air condenser to the atmosphere.

In combined heat and power plants with internal combustion engines, the waste heat from cooling water, oil cooler and from the combustion gases is used for heating purposes or other purposes.

The state of the art is also referred to heating systems in which by means of Stirling engines, a part of the heating heat generated is converted into electricity.

If the plants described above are driven in a heat-oriented manner, i. only driven by the heat requirement, a high annual efficiency but a lower annual efficiency can be achieved. If the combined heat and power plant (CHP plant) is driven in a stream-oriented manner, losses will be lost during the time during which the residual heat can not be fully utilized and must be released to the atmosphere via cooling towers or air coolers. These losses reduce the annual impact and efficiency.

With the present invention, the cogeneration plant can be operated at full load throughout the year, because with almost the same efficiency, electricity or heat or both can be generated together. This achieves a much higher level of annual impact and efficiency. Electricity can be decoupled with this invention also from accumulating process waste heat.

Short description of the drawing

Fig. 1

eine schematische Darstellung des Grundmoduls der Wärmekraft- maschine, in der die wesentlichen Komponenten und deren Bezie- hung zueinander aufgezeigt werden, um die Realisierung des Stir- lingkreislaufes darzustellen.

Fig. 2

Einzelheiten der Ventilsteuerung 5 und 6.

Fig. 3

das Grundmodul der Fig. 1, ergänzt durch elektrische Spule 8 und Magnet 7 zur direkten Stromerzeugung.

Fig. 4

das Grundmodul der Fig. 1, ergänzt mit einem Druckausgleichsbe- hälter 9, für einen unbestimmten Betriebsdruck des Arbeitsgases.

Fig. 5

eine andere Ausführungsform des Grundmoduls, wobei der Wär- meüberträger 1, Verbindungsrohre 4, Ventile 5 und Ventilsteuerung 6 beidseitig des Arbeitszylinders 2 angeordnet sind.

Fig. 6

eine schematische Darstellung wie in Fig. 5, mit Darstellung des Medienflusses, der gleichzeitig durch gegenüberliegende Wärme- träger 1 strömt.

Fig. 7

eine schematische Darstellung, bei der an bestimmten Wärmeüber- trägern 1 mehrere Module, bestehend aus Verbindungsrohren 4, Ventilen 5, Arbeitszylinder 2 und Arbeitskolben 3 angeschlossen sind.

Fig. 8

ein schematisches Modell des Grundmoduls in einer Ausführung bei der die Wärmeüberträger 1 sternförmig um den Arbeitszylinder 2 angeordnet sind und somit einen Rotor bilden. Zusammen drehen sie um die gemeinsame Längsachse. In der Darstellung sind die Anordnung und Funktion der Verbindungsrohre 4, die Ventile 5 so- wie die Ventilsteuerung 6 hervorgehoben. Die Heiz- und Kühlstre- cken der Wärmeüberträger 1 sind ausgewiesen.

Fig. 9A

"Symbolbeschreibung" und die dazu gehörenden Fig. 9B "Darstel- lung Takt 1 bis Takt 4" und 9C "Darstellung Takt 5 bis Takt 6".eine Darstellung des Prozessablaufes auf der Basis des in Fig. 8 darge- stellten Modells. Die jeweilige Kolbenbewegung, die Ventilstellung und der Fortschritt des einzelnen Wärmeüberträgers im Stirling- Vergleichsprozess, sind schematisch dargestellt.

Fig. 10

ein schematisches Modell des Grundmoduls in einer Ausführung bei der jeweils 3 Stück Wärmeüberträger 1 an beiden Seiten des Ar- beitszylinders 2 angeschlossen sind. Auch in diesem Modell sind die Wärmeüberträger 1 sternförmig um den Arbeitszylinder 2 ange- ordnet und bilden somit einen Rotor. Zusammen drehen sie sich um die gemeinsame Längsachse. Die Heiz- und Kühlstrecken der Wärmeüberträger 1 sind ausgewiesen.

Fig. 11

Modell wie in Fig. 10 dargestellt, ergänzt mit einem Regenerator bestehend aus Umluftgebläse 10 bzw. Umwälzpumpe 10 mit Um- luftleitungen 11 bzw. Umwälzleitungen 11 (bei Flüssigkeiten).

Fig. 12

eine schematische Darstellung des Rotors mit dem kombinierten Stirling-Clausius-Rankine-Kreisprozess, mit 10 Stück Wärmeüber- trägern 1, die sternförmig um den Arbeitszylinder 2 angeordnet sind. Die Hälfte der Wärmeüberträger 1 ist an der Vorderseite und die andere Hälfte auf der Rückseite am Arbeitszylinder 2 ange- schlossen. Die Heiz-, Kühl- und Regenerationsstrecken (Umluft) sind ausgewiesen.

Fig. 13A

"Symbolbeschreibung" und die dazu gehörenden Fig. 13B "Darstel- lung Takt 1 bis Takt 4" und 13C "Darstellung Takt 5 bis Takt 7" eine Darstellung der ersten 7 Takte von 10 Takten des Prozessab- laufes auf Basis des in Fig. 6 dargestellten Modells, jedoch mit je- weils 5 Stück Wärmeüberträgern 1 auf jeder Seite des Arbeitszylin- ders 2.

Fig. 14A

"Symbolbeschreibung" und die dazu gehörenden Fig. 14B "Darstel- lung Takt 1 bis Takt 4" und 14C "Darstellung Takt 5 bis Takt 7" eine schematische Darstellung des Prozessablaufes, bei dem alle Wärmeüberträger 1 sternförmig um die Mittelachse angeordnet sind, aber abwechselnd an der einen oder anderen Seite des Ar- beitszylinders 2 angeschlossen sind.

Fig. 15

eine schematische Darstellung des Grundmoduls, mit Wärmeüber- träger 1 in Form eines Strahlungsabsorbers, wobei eine mögliche Konstruktion des Beschattungselementes und der Einhausung der bestrahlten Absorberfläche schematisch dargestellt ist.

Fig. 16.

Druck-Enthalpie-Diagramm mit CCl₂Fl₂, Frigen R12 als Arbeitsstoff.

Fig. 17

P-v-Diagramm bezogen auf in Fig. 16 dargestelltem P-h-Diagramm.

Fig. 18

t-s-Diagramm bezogen auf in Fig. 16 dargestelltem P-h-Diagramm.

Fig. 19

möglicher Aufbau einer erfindungsgemäßen Wärmekraftkopplungs- anlage, schematisch dargestellt.

Fig. 20

nachfolgend detailliert beschriebene und in den Figuren 1 bis 18 dargestellte Wärmekraftmaschine schematisch dargestellt

Fig. 21

Diagram, in dem der ungefähre Temperaturverlauf des Kühl- und Heizmediums annähernd dargestellt ist

In the drawing shows:

Fig. 1

a schematic representation of the basic module of the heat engine, in which the essential components and their relationship are shown to each other to represent the realization of the Stir- ling cycle.

Fig. 2

Details of the valve control 5 and 6.

Fig. 3

the basic module of Fig. 1 , supplemented by electric coil 8 and magnet 7 for direct power generation.

Fig. 4

the basic module of Fig. 1 , supplemented with a pressure equalization tank 9, for an indeterminate operating pressure of the working gas.

Fig. 5

another embodiment of the basic module, wherein the heat exchanger 1, connecting pipes 4, valves 5 and valve control 6 are arranged on both sides of the working cylinder 2.

Fig. 6

a schematic representation as in Fig. 5 , with representation of the media flow, which simultaneously flows through opposing heat carriers 1.

Fig. 7

a schematic representation in which at certain heat transfer 1 a plurality of modules consisting of connecting tubes 4, valves 5, cylinder 2 and working piston 3 are connected.

Fig. 8

a schematic model of the basic module in an embodiment in which the heat exchanger 1 are arranged in a star shape around the working cylinder 2 and thus form a rotor. Together they rotate around the common longitudinal axis. In the illustration, the arrangement and function of the connecting pipes 4, the valves 5 and the valve control 6 are highlighted. The heating and cooling sections of the heat exchanger 1 are shown.

Fig. 9A

"Symbol description" and the associated Fig. 9B "Display of cycle 1 to cycle 4" and 9C "Display of cycle 5 to cycle 6" .An illustration of the process flow on the basis of the Fig. 8 ones shown, set model. The respective piston movement, the valve position and the progress of the individual heat exchanger in the Stirling comparison process are shown schematically.

Fig. 10

a schematic model of the basic module in an embodiment in which each 3 pieces heat exchanger 1 on both sides of the working cylinder 2 are connected. Also in this model, the heat exchangers 1 are arranged in a star shape around the working cylinder 2 and thus form a rotor. Together they rotate around the common longitudinal axis. The heating and cooling sections of the heat exchanger 1 are identified.

Fig. 11

Model as in Fig. 10 represented, supplemented with a regenerator consisting of circulating air blower 10 and circulating pump 10 with circulating air lines 11 and Umwälzleitungen 11 (for liquids).

Fig. 12

a schematic representation of the rotor with the combined Stirling Clausius Rankine cycle, with 10 pieces of heat transfer 1, which are arranged in a star shape around the working cylinder 2. Half of the heat exchanger 1 is connected to the front side and the other half on the rear side to the working cylinder 2. The heating, cooling and regeneration sections (circulating air) are indicated.

Fig. 13A

"Symbol description" and the associated Fig. 13B "Representation of cycle 1 to cycle 4" and 13C "representation of cycle 5 to cycle 7" a representation of the first 7 cycles of 10 cycles of the process sequence on the basis of in Fig. 6 model, however, each with 5 heat exchangers 1 on each side of the working cylinder 2.

Fig. 14A

"Symbol description" and the associated Fig. 14B "Display of measure 1 to measure 4" and 14C "representation of measure 5 to measure 7" a schematic representation of the process flow, in which all heat exchangers 1 are arranged in a star shape around the central axis, but are alternately connected to one or the other side of the working cylinder 2.

Fig. 15

a schematic representation of the basic module, with heat exchanger 1 in the form of a radiation absorber, wherein a possible construction of the shading element and the housing of the irradiated absorber surface is shown schematically.

Fig. 16.

Pressure-enthalpy diagram with CCl ₂ Fl ₂ , Frigen R 12 as working substance.

Fig. 17

Pv diagram related to in Fig. 16 represented Ph diagram.

Fig. 18

ts diagram related to in Fig. 16 represented Ph diagram.

Fig. 19

Possible structure of a thermal power plant according to the invention, shown schematically.

Fig. 20

detailed below and in the FIGS. 1 to 18 shown heat engine shown schematically

Fig. 21

Diagram, in which the approximate temperature profile of the cooling and heating medium is shown approximately

definition:

In the following description, the lower temperature medium is referred to as the "cooling medium" and the higher temperature medium is referred to as the "heating medium".

The term "heat" is used in the following description for both the "warm" and "heat" operations.

Description of the cycle after the "Stirling" comparison process

The thermodynamic process consists of 4 state changes, which are similar to the Stirling comparison process.

In a closed room with a large heat exchange surface (hereinafter called heat exchanger 1) located working gas is periodically heated or cooled by a medium flowing around the closed space (liquid or gas). Also, heating of the working gas by radiant energy (e.g., solar energy) is possible. The caused by heating or cooling pressure changes are transmitted to a working piston 3, after a valve 5 between the closed heat exchanger 1 and the displacement of the working cylinder 2 is opened.

1. 1. Wärmezufuhr bei konstantem Volumen (Isochore) - Ventil 5 ist geschlossen.
2. 2. Expansion bei konstanter Temperatur (Isotherme) (mit Wärmezufuhr) - Ventil 5 ist geöffnet.
3. 3. Wärmeentzug bei konstantem Volumen (Isochore) - Ventil 5 ist geschlossen.
4. 4. Kompression bei konstanter Temperatur (Isotherme) (mit Wärmeentzug) - Ventil 5 ist geöffnet.

The four state changes of the working gas are:

1. 1. Heat supply at constant volume (Isochore) - valve 5 is closed.
2. 2. Expansion at constant temperature (isotherm) (with heat input) - Valve 5 is open.
3. 3. Heat extraction at constant volume (Isochore) - valve 5 is closed.
4. 4. Compression at constant temperature (isotherm) (with heat removal) - Valve 5 is open.

The main difference between the Stirling engine and this heat engine is that the compression stroke following the expansion stroke of the piston 3 does not occur from one and the same heat exchanger 1. At least three heat exchangers 1 are required, which are alternately and periodically warmed or cooled.

In each individual heat exchanger 1 together with the common working cylinder 2 and piston 3 takes place, offset in time to all other heat transferors 1, a separate cycle process instead. The individual Stirling cycle processes are coordinated so that an isothermal compression of another heat exchanger 1 follows in the common working cylinder 2 after an isothermal expansion from a heat exchanger 1. After this compression is followed again by an isothermal expansion of another heat exchanger 1, etc.

As with a Stirling engine, there is no internal combustion. Heat and power are generated separately. Consequently, this heat engine can also be operated with its own, external heat source and thus represent a self-sufficient system. As primary energy, everything that generates heat can be used.

Since compression and expansion take place mainly outside the displacement, no flywheel or the like is required. A fraught with friction losses mechanical linkage, which affects the efficiency of the machine is not required. Contrary to conventional heat engines, the movement of the piston 3 can be converted directly into electrical energy. For this purpose, electrical windings are required around a working cylinder 2 made of non-metal and a magnetized piston 3.

Plant structure of the basic module

Schematically, the heat engine is in Fig. 1, 2 and 8th shown.

1. 1. Wärmeüberträgern 1A, 1B und 1C, die sternförmig in Form eines Rotors um einen Arbeitszylinder 2 angeordnet sind und sich mit diesem um seine Längsachse drehen. Auf die Wärmeüberträger 1A, 1B, 1C usw. wird insgesamt mit 1 Bezug genommen. Durch die Drehbewegung werden die Wärmeüberträger 1 jeweils zur Hälfte einer Umdrehung durch den Kühlmedium-Strom (Kühlstrecke) und zur Hälfte durch den Heizmedium-Strom (Heizstrecke) geführt, so dass sie abwechselnd mit Kühl- und Heizmedium umströmt werden.
   Wärmeüberträger 1 sind geschlossene Räume mit einer Verbindung zu dem Arbeitszylinder 2. Die Wärmeüberträger 1 befinden sich in einem Rohr, das die Wärmeüberträger 1 außen herum umgibt und so eine äußere Hülle13 (Fig. 10) bildet. Ebenso ist innen zwischen Wärmeüberträger 1 und Arbeitszylinder 2 ein Rohr vorgesehen, dass eine innere Hülle 14 bildet. Diese Hüllen 13 und 14 sind so lang wie die Wärmeüberträger 1. Sie bilden einen kreisringförmigen Kanal, in dem sich die Wärmeberträger 1 befinden. Zwischen den einzelnen Wärmeüberträgern 1 sind Trennstege 15 vorgesehen, die von der äußeren bis zur inneren Hülle reichen. Somit befindet sich jeder Wärmeüberträger 1 in einem Kanal, durch den das Heiz- und Kühlmedium hindurch geführt wird und somit den einzelnen Wärmeüberträger 1 umspült.
   Jeder Wärmeüberträger 1 ist, bis auf eine Öffnung innen, geschlossen. Die Öffnung ist mit einem Verbindungsrohr 4 und über ein Ventil 5 mit dem Arbeitszylinder 2 verbunden, durch welches das eingeschlossene Arbeitsgas aus- und einströmen kann.
   Die Wärmeüberträger 1 sind aus einem Material mit sehr guter Wärmeleitfähigkeit (z. B. Ag, Cu oder Al) hergestellt.
2. 2. In einem Arbeitszylinder 2 kann sich ein Kolben 3 frei hin und her bewegen. Für einen guten Wirkungsgrad ist auf der Innenseite eine Oberfläche mit niedriger Wärmekapazität und schlechter Wärmeleitfähigkeit sowie guter Gleiteigenschaft (z. B. Teflon) erforderlich. (Es soll möglichst wenig Wärme vom Arbeitsgas auf den Arbeitszylinder 2 oder umgekehrt übertragen werden).
   Um den Arbeitszylinder 2 ist eine elektrische Spule 8 zur Stromerzeugung gelegt. Der Arbeitszylinder 2 ist aus einem nicht metallischen Material (Glas, Keramik, Kunststoff oder Ähnlichem) hergestellt.
   An einer oder an beiden Seiten sind Öffnungen, an denen die Verbindungsrohre 4 mit dem Hubraum des Arbeitszylinders 2 verbunden sind.
3. 3. Ein Kolben 3 frei laufend ohne Pleuel oder sonstige mechanische Verbindung. Er kann sich frei im Arbeitszylinder 2 hin und her bewegen. Ähnlich wie bei einem Benzinmotor ist der Kolben 3 gegenüber den Arbeitszylinderwänden 2 abgedichtet.
   Um den Wirkungsgrad zu verbessern sind Flächen des Kolbens 3, die mit dem Arbeitsgas in Berührung kommen, mit einer Oberfläche niedriger Wärmekapazität und schlechter Wärmeleitfähigkeit zu versehen.
   Es ist vorteilhaft die Masse des Kolbens 3 so gering wie möglich zu halten, um Beschleunigungsarbeit zu minimieren.
   Um direkt aus der Kolbenbewegung elektrischen Strom erzeugen zu können, muss der Kolben 3 magnetisiert sein. Diese Magnetisierung ist unter Ziffer 7 beschrieben.
4. 4. Verbindungen insbesondere Verbindungsrohre 4A, 4B und 4C sind Verbindungen welche die einzelnen Wärmeüberträger 1A, 1B und 1C und Arbeitszylinder 2 räumlich verbinden. Auf Verbindungen 4A, 4B, 4C usw. wird insgesamt mit 4 Bezug genommen. Diese Verbindungsrohre 4 werden, um unnötigen Todraum zu vermeiden, so kurz wie möglich gehalten. Soweit möglich haben die Verbindungsrohre 4 eine geringe Wärmekapazität und Wärmeleitfähigkeit. Dort, wo diese Verbindungsrohre 4 nicht von Kühl-/Heizmedium umströmt werden, sind sie gegen Wärmeaustausch mit der Umwelt isoliert. In diesen Verbindungsrohren 4 sind Steuerventile 5 eingebaut, soweit sie nicht im Arbeitzylinder 2 integriert sind.
5. 5. Steuerventile 5, bestehend aus einzelnen Ventilen 5, die sich jeweils im Verbindungsrohr 4 zwischen Wärmeüberträger 1 und Arbeitszylinder 2 befinden und den eigentlichen Prozess steuern. Der Einsatz dieser Ventile 5, nicht aber ihre Ausführung, ist ein wesentliches Merkmal dieser Wärmekraftmaschine.
   Für jeden Wärmeüberträger 1A,1B und 1C ist ein Ventil 5A, 5B und 5C vorgesehen. Auf Ventile 5A, 5B, 5C usw. wird insgesamt mit 5 Bezug genommen. Die Ventile 5 werden abwechselnd geöffnet und geschlossen, um den in den einzelnen Wärmeüberträgern 1 eingeschlossenen Raum mit dem Arbeitszylinder 2 zu verbinden oder zu trennen. Der Raum in jedem Wärmeüberträger 1 ist bei geöffnetem Ventil 5 direkt mit dem Arbeitszylinder 2 verbunden.
   Die Ventile 5 sind dichtschließend und sind für die maximale Druckdifferenz zwischen Wärmeüberträger 1 und Arbeitszylinder 2 ausgelegt.
6. 6. Eine Ventilsteuerung 6 wird zum Öffnen und Schließen der Ventile 5, im richtigen Moment, vorgesehen. Die Ventilsteuerung 6 kann mechanisch (z.B. mit einer Nockenwelle/ -scheibe) oder elektrisch/elektronisch erfolgen.
   Die Ventile 5 werden im gleichen Rhythmus, wie das Erwärmen und Kühlen der Wärmeüberträger 1 erfolgt, geöffnet und geschlossen. Am Ende eines Heiz- oder Kühlvorganges an einem Wärmeüberträger 1 öffnet das dem Wärmeüberträger 1 zugeordnete Ventil 5 und löst damit die Expansion bzw. Kompression aus. Das Ventil 5 schließt nach erfolgter Expansion bzw. Kompression, aber bevor der Wärmeüberträger 1 vom Heizauf das Kühlmedium, oder umgekehrt, wechselt.
7. 7. Eine Magnetisierung des Arbeitskolbens 3 mit Permanentmagneten 7 oder mit erregter Spule. Der Erregerstrom wird mittels Schleifkontakten vom Zylinder 2 an den Kolben 3 übertragen.
8. 8. Eine elektrische Spule 8, welche um den Arbeitszylinder 2 gelegt ist, in der, durch die Bewegung des magnetisierten Kolbens 3, Strom erzeugt wird.
9. 9. Ein Druckausgleichsbehälter 9, welcher nur bei solchen Arbeitzylindern 2 angewendet wird, an denen nur auf einer Seite Wärmeüberträger 1 angeschlossen sind. Ein druckbeständiger Behälter in dem sich Arbeitsgas befindet und der dem Druckausgleich dient, wenn der Ruhedruck in den Wärmeüberträgern 1 vom atmosphärischen Druck abweicht.
10. 10. Ein Umluftgebläse 10 oder eine Umwälzpumpe 10, welche zum Umwälzen des Mediums von den aufgeheizten Wärmeüberträgern 1, unmittelbar nach dem Expansionsvorgang (nach Schließen des Ventils 5) zu den gekühlten Wärmeüberträgern 1 am Ende des Kompressionsvorganges (nach Schließen des Ventils 5) eingesetzt wird. Mit dieser Umwälzung wird ein Teil der Wärme, die in den Wärmeüberträgerhüllen gespeichert ist, ausgetauscht, um die gekühlten Wärmeüberträger 1 aufzuheizen und die beheizten abzukühlen. Durch diesen Regenerationsprozess steht mehr Wärme aus dem Heizmedium zur Aufheizung des Arbeitsgases zur Verfügung.
11. 11. Umlenkleitungen 11, um das Heiz-/Kühlmedium von den aufgeheizten Wärmüberträgern 1 zu den gekühlten Wärmeüberträgern 1 und von dort zum Gebläse/Pumpe 10 und zurück zu den geheizten Wärmeüberträgern 1 zu lenken. (vergleiche Fig. 11)
12. 12. Eine isolierte Trennung, welche sich zwischen dem warmen und dem kalten Bereich befindet (vergleiche Fig. 12), und welche rohrartig ausgebildet ist, um das Heizmedium vom Kühlmedium innerhalb des Rotors zu trennen.
13. 13. Eine äußere Hülle 13 um die Wärmeüberträger 1, als Bestandteil der Kanäle mit denen das Heiz-/Kühlmedium um die Wärmeüberträger 1 gelenkt wird, die Wärmeüberträger 1 umhüllt. Zusammen mit der Innenhülle14 und dem Trennstege 15 bildet die äußere Hülle 13 einen Kanal um jeden einzelnen Wärmeüberträger 1.
14. 14. Eine innere Hülle 14 um eine rohrförmige Abgrenzung des Medienkanals zum Arbeitszylinder 2 herzustellen. Die Innenhülle bildet zusammen mit der Außenhülle13 und dem Trennsteg 15 einen Kanal um jeden einzelnen Wärmeüberträger 1.
15. 15. Die Trennstege 15 sind Abgrenzungen zwischen den einzelnen Wärmeüberträgern 1. Zusammen mit der Innenhülle 14 und Außenhülle 13 lenken sie das Heiz-/Kühlmedium während der Rotation um die jeweiligen Wärmeüberträger 1.

In essence, the illustrated heat engine consists of:

1. 1. heat exchangers 1A, 1B and 1C, which are arranged in a star shape in the form of a rotor about a working cylinder 2 and rotate with this about its longitudinal axis. The heat exchangers 1A, 1B, 1C, etc. are referenced 1 in their entirety. By the rotational movement, the heat exchanger 1 are each half of a revolution by the cooling medium flow (cooling section) and half by the heating medium flow (Heating) led, so that they are alternately flows around with cooling and heating medium.
   Heat exchanger 1 are closed spaces with a connection to the working cylinder 2. The heat exchanger 1 are located in a tube surrounding the heat exchanger 1 outside and so an outer shell 13 (Fig. Fig. 10 ). Likewise, a tube is provided internally between the heat exchanger 1 and the working cylinder 2 that forms an inner shell 14. These shells 13 and 14 are as long as the heat exchanger 1. They form an annular channel in which the heat carrier 1 are located. Between the individual heat exchangers 1 dividers 15 are provided which extend from the outer to the inner shell. Thus, each heat exchanger 1 is located in a channel through which the heating and cooling medium is passed and thus flows around the individual heat exchanger 1.
   Each heat exchanger 1 is closed, except for an opening inside. The opening is connected to a connecting pipe 4 and via a valve 5 to the working cylinder 2, through which the trapped working gas can flow out and in.
   The heat exchangers 1 are made of a material with very good thermal conductivity (eg Ag, Cu or Al).
2. 2. In a working cylinder 2, a piston 3 can move freely back and forth. For a good efficiency on the inside of a surface with low heat capacity and poor thermal conductivity and good sliding property (eg Teflon) is required. (As little heat as possible should be transferred from the working gas to the working cylinder 2 or vice versa).
   To the working cylinder 2, an electric coil 8 is set to generate electricity. The working cylinder 2 is made of a non-metallic material (glass, ceramic, plastic or the like).
   On one or both sides are openings at which the connecting pipes 4 are connected to the displacement of the working cylinder 2.
3. 3. A piston 3 running freely without connecting rod or other mechanical connection. He can move freely in the working cylinder 2 back and forth. Similar to a gasoline engine, the piston 3 is sealed against the working cylinder walls 2.
   In order to improve the efficiency surfaces of the piston 3, which come into contact with the working gas, to be provided with a surface of low heat capacity and poor thermal conductivity.
   It is advantageous to keep the mass of the piston 3 as low as possible in order to minimize acceleration work.
   In order to generate electrical current directly from the piston movement, the piston 3 must be magnetized. This magnetization is described under point 7.
4. 4. Connections in particular connecting pipes 4A, 4B and 4C are connections which spatially connect the individual heat exchangers 1A, 1B and 1C and working cylinder 2. 4A, 4B, 4C, etc. are referenced 4 in their entirety. These connecting pipes 4 are kept as short as possible in order to avoid unnecessary dead space. As far as possible, the connecting pipes 4 have a low heat capacity and thermal conductivity. Where these connecting pipes 4 are not flowed around by cooling / heating medium, they are isolated from heat exchange with the environment. In these connecting tubes 4 control valves 5 are installed, as far as they are not integrated in the working cylinder 2.
5. 5. control valves 5, consisting of individual valves 5, which are located in the connecting pipe 4 between the heat exchanger 1 and cylinder 2 and control the actual process. The use of these valves 5, but not their execution, is an essential feature of this heat engine.
   For each heat exchanger 1A, 1B and 1C, a valve 5A, 5B and 5C is provided. Valves 5A, 5B, 5C, etc. are referenced 5 in their entirety. The valves 5 are alternately opened and closed in order to connect or separate the space enclosed in the individual heat exchangers 1 with the working cylinder 2. The space in each heat exchanger 1 is connected directly to the working cylinder 2 when the valve 5 is open.
   The valves 5 are sealed and are designed for the maximum pressure difference between the heat exchanger 1 and cylinder 2.
6. 6. A valve control 6 is provided for opening and closing the valves 5, at the right moment. The valve control 6 can be done mechanically (eg with a camshaft / disc) or electrically / electronically.
   The valves 5 are opened and closed in the same rhythm as the heating and cooling of the heat exchanger 1 takes place. At the end of a heating or cooling process on a heat exchanger 1 opens the heat exchanger 1 associated valve 5 and thus triggers the expansion or compression. The valve 5 closes after expansion or compression, but before the heat exchanger 1 from Heizauf the cooling medium, or vice versa, changes.
7. 7. A magnetization of the working piston 3 with permanent magnets 7 or excited coil. The field current is transmitted by means of sliding contacts from the cylinder 2 to the piston 3.
8. 8. An electric coil 8, which is placed around the working cylinder 2, in which, by the movement of the magnetized piston 3, power is generated.
9. 9. A pressure equalization tank 9, which is used only in such work cylinders 2, where only one side heat exchanger 1 are connected. A pressure-resistant container in which working gas is located and which serves to equalize the pressure when the static pressure in the heat exchangers 1 deviates from the atmospheric pressure.
10. 10. A circulating air blower 10 or a circulating pump 10, which is used for circulating the medium of the heated heat exchangers 1, immediately after the expansion process (after closing the valve 5) to the cooled heat exchangers 1 at the end of the compression process (after closing the valve 5) , With this circulation, a part of the heat stored in the heat exchanger shells is exchanged to heat the cooled heat exchangers 1 and to cool the heated ones. Through this regeneration process is more heat from the heating medium for heating the working gas available.
11. 11 deflecting lines 11 to direct the heating / cooling medium of the heated heat exchanger 1 to the cooled heat exchanger 1 and from there to the blower / pump 10 and back to the heated heat exchanger 1. (see Fig. 11 )
12. 12. An isolated separation, which is located between the warm and the cold area (cf. Fig. 12 ), and which is tube-shaped to separate the heating medium from the cooling medium within the rotor.
13. 13. An outer shell 13 to the heat exchanger 1, as part of the channels with which the heating / cooling medium is directed to the heat exchanger 1, the heat exchanger 1 wrapped. Together with the inner shell 14 and the separating web 15, the outer shell 13 forms a channel around each individual heat exchanger 1.
14. 14. An inner shell 14 to produce a tubular boundary of the media channel to the working cylinder 2. The inner shell, together with the outer shell 13 and the separating web 15, forms a channel around each individual heat exchanger 1.
15. 15. The dividers 15 are delimitations between the individual heat exchangers 1. Together with the inner shell 14 and outer shell 13, they steer the heating / cooling medium during rotation about the respective heat exchanger. 1

Description of the process flow at the basic module:

The process flow is represented by a model with warm air as an energy source. This model is schematic in Fig. 8 shown. The process flow is schematic in Fig. 9A . 9B and 9C shown.

The model consists of 3 heat exchangers 1, which are arranged in a star shape around the working cylinder 2. The angle between the adjacent heat exchangers 1 is 120 °. The heat exchanger 1 are rigidly connected to the working cylinder 2 and rotate with this, as well as with the outer shell 13 and inner shell 14, about its longitudinal axis.
The heat exchanger 1 move alternately in a flow-through with heating or cooling medium area, in Fig. 8 referred to as heating and cooling section. Cooling and heating medium leading lines are connected to the inlet and outlet of the heat exchanger 1. Each of the two types of media occupies half of the annular channel in which the heat exchanger 1 are located.

The valve control 6 is shown in this model as a cam and is arranged so that the plungers of the valves 5 follow the contours of the cam 6 during rotation. The cam itself is fixed. The cam has two opposed cams. They are arranged that the valves 5 are opened when the associated heat exchanger 1 has covered about 2/3 of the respective cooling or heating distance. The valve 5 closes shortly before the heat exchanger 1 from the cooling medium in the heating medium (or vice versa) passes.
The process flow in the individual heat exchangers 1 runs as in Figs. 9A to 9C shown schematically.
In this model it is assumed that the rotation of the heat exchanger 1 and cylinder 2 is performed by an external drive.

Clock 1:

The heat exchanger 1A is already flowed through with hot air and the trapped working gas is already heated. Due to the heating and the limited volume, the pressure in the heat exchanger 1A has increased at the same volume (Isochore). By rotating over the cam plate 6, the valve 5A opens and the pressurized working gas expands into the working cylinder 2 and performs work with the piston 3. During the expansion of the heat exchanger 1A is still flowing around with hot air. There is thus an isothermal expansion.

Bar 2:

As the piston 3 moves away from the valve 5A, the power cylinder 2 and heat exchanger 1 continue to rotate and valve 5A closes. At the same time another valve 5 B opens, which connects the air space in the working cylinder 2 with that of the heat exchanger 1 B. This was previously flowed around with cooling medium. In the affected heat exchanger 1 B, the trapped gas was cooled, at a constant volume, and there was thus a negative pressure. When opening the valve 5B, the air from the working cylinder 2, compressed in the heat exchanger 1 B and the piston 3 moves through the pressure difference back to the valve 5. Since during this compression process, the heat exchanger 1B still constantly flows through the cooling medium and the working gas in the Compression heat is extracted, it is an isothermal compression.
Heat exchanger 1A is already partially traversed by cold air at this time.

Clock 3:

By the rotation of the third heat exchanger 1 C, in the time during which the piston 3 moved back and forth, flowed through with heating medium. With a constant volume, the pressure of the working medium in the heat exchanger 1C increased. With opening of the valve 5C, the working gas expands isothermally from the heat exchanger 1C in the working cylinder 2 and pushes the piston 3 away from the valve 5 again.

Clock 4:

While the piston 3 moves away, was through the rotation of the heat exchanger 1A this time traversed with cooling medium. Since the valve 5A is closed, heat was extracted from the working gas in the closed space (isochore). This created a negative pressure of the working gas in the heat exchanger 1A. After further rotation, the valve 5A opens and the piston 3 is brought back by the negative pressure.

Clock 5:

The, by the heating medium to the working gas in the heat exchanger 1 B, supplied heat at constant volume in the heat exchanger 1 B has generated an overpressure, which can relax when opening the valve 5 B in the working cylinder 2. By this (isothermal) expansion of the piston 3 is pushed away again.

Bar 6:

The, by this time cold air flow to the working gas in the heat exchanger 1C, dissipated heat has generated a negative pressure at constant volume in the heat exchanger 1C. When opening the valve 5C, the working gas from the working cylinder 2 will compress into the heat exchanger 1C. By this (isothermal) compression of the piston 3 is brought back again.

After completing bar 6, the process repeats from bar 1.
For each complete revolution of the rotor, each heat exchanger 1 must be connected twice via the valves 5 to the working cylinder 2, ie once for the expansion and once for the compression.

Due to the external drive of the rotor, a speed control is possible to optimize the performance of the individual cycle processes, for. B. with changed parameters of the heating or cooling medium.

First variant of the basic module (See Fig.3)

Heat engine as described for the basic module, in which the working cylinder 2 is made of a non-metallic material (glass, ceramic, plastic or the like). To the working cylinder 2, a coil 8 is placed with wire windings for power generation.

The freely movable piston 3 is magnetized by permanent magnets 7, or by excitation current. By the reciprocation of the piston 3 2 power is generated in the coil 8 to the working cylinder.

Second variant of the basic module (See Fig. 4)

If the working cylinder 2 is open to the atmosphere, a one-sided loading of the piston 3 by the working gas can arise as soon as the static pressure of the working gas deviates from the atmospheric pressure. This considerably restricts the choice of the working gas. Should it be necessary to work with pressures that deviate from the atmospheric pressure, a surge tank 9 is connected to the open side of the piston 3, which applies the required back pressure.

Third variant of the basic module (See Fig. 5 and Fig. 13)

It makes sense, instead of the previously described pressure equalization tank 9, 2 heat exchanger 1, connecting pipes 4 and valves 5 symmetrically build on both sides of the working cylinder. Here, the sequence of valves 5 on the two sides of the working piston 3 is adjusted to each other, that at the same time on one side of the piston 3 an expansion, on the other side takes place a compression.
In the Fig. 13 the process flow for such a double unit is shown, but with 5 heat exchangers on each side of the working cylinder. 2

Fourth variant of the basic module (See Fig. 6, and Fig. 13)

This variant corresponds essentially to the third variant with the difference that the heat exchanger 1, which are connected to the back of the working cylinder 2, are located directly behind those which are connected to the front, so that the heating / cooling medium after passing the heat exchanger 1 the front side, those on the back also happened. In this case, the heating and cooling medium is always performed simultaneously through the heat transfer medium 1 directly behind one another. ( Fig. 13 )

Fifth variant of the basic module (See Figs. 10 and 14)

With respect to the working cylinder 2 and piston 3, including the connections of the heat exchanger 1, this variant corresponds to those of the third and fourth. In this variant, all heat exchangers 1 are arranged in a star shape around the working cylinder 2. On each side of the working cylinder 2, a valve control 6 is required. The heat exchanger 1 are connected alternately times on the front, sometimes on the rear side of the working cylinder 2. If half of the sum of all heat exchangers 1 corresponds to an odd number, at each angle of rotation of the rotor always a heat exchanger 1 with the one side of the working cylinder 2 and another heat exchanger 1 with the opposite side to the working cylinder 2 connected. How out Fig. 14 shows, the valves 5 are always heat exchanger 1 with different states of the working gas to the working cylinder 2 connect. The process takes place as in Fig. 14 shown.

Sixth Variant of the Basic Module (See Fig. 11)

The heat exchanger 1 itself, the actual envelope of the working gas, alternately heat and cool, requires a significantly higher energy expenditure than that which is required to heat or cool the working gas. So much of the energy that should be recovered is lost. In order to reduce this loss, a regenerator is provided in a module as described in the fifth variant. The regenerator is a circulation system which, by circulating the cooling / heating medium, uses the heat of the heated heat exchanger 1 to heat the cooled heat exchanger 1 and at the same time to be cooled by the cooled by the cooled heat exchanger 1, air itself.
The regenerator consists of a fan for gaseous heating / cooling media, or a pump 10 for liquid media and deflection channels or tubes 11, the medium from one segment of the rotor directly after the heating line, to another segment of the rotor directly after the cooling section and lead back again.

Seventh variant of the basic module with radiant energy as primary energy (See Fig. 15)

The principle of the basic module is retained. Instead of the channels for heating and cooling media, the heat exchanger 1 are formed as a radiation absorber. Working cylinder 2, piston 3 and valves 5 retain their function, as described for the basic module.
The heat exchanger 1 (as absorber) are aligned so that the available radiant heat can be optimally absorbed. They have a flat shape and are coated with an absorbent surface. As the heat absorbed back to the environment must be a construction that allows for optimized convection.
Similar to the basic module only half the absorber surface of the heat exchanger 1 is exposed to radiation. The other half is shadowed. Half of the heat exchanger 1, which is exposed to the radiation should absorb as much of the heat and therefore be protected against loss by convection
The heat exchanger 1 with working cylinder 2, connecting pipes 4 and valves 5 rotate about the longitudinal axis of the working cylinder 2 as described in the basic module. As a result, the heat exchanger 1 are alternately heated by the radiation and, by releasing the heat to the environment, cooled again.
The valves 5, as described in the basic module are operated so that alternately a cooled and heated heat exchanger 1 are connected to the working cylinder 2 to perform work by expansion or compression.

Eighth variant of the basic module with radiation energy as the primary energy (See Figs. 14 and 15)

Heat engine as described in variant seven only that each half of the heat exchanger 1 are connected to one, the other half on the other sides of the working cylinder 2. The heat exchanger 1 are all located on the same side of the working cylinder 2 and are arranged in a star shape in the form of a disc. The process flow corresponds to that described in variant five and in Fig. 14 is shown.

Ninth variant of the basic module The Clausius-Rankine cycle

Because of the considerably larger amount of energy compared to the working substance, which is required to heat up or cool down the working substance envelope, heat of evaporation becomes many times the heat capacity of the working substance represents used. Condensing or vaporizing the working substance on the heat exchanger wall requires a considerably greater energy flow than heating or cooling the working substance.
It is possible to convey the condensate, which has a much smaller specific volume than the gaseous aggregate, from the cold zone into the warm one (as in the Rankine cycle, where the condensate is pumped into the high-pressure zone).
In the high pressure area, the volume increase is used by the evaporation to do work.
In order to integrate the Clausius-Rankine process in the already described Stirling cycle, some changes to the heat exchangers 1 must be made.
Each individual heat exchanger 1 is divided into two halves (see Fig. 12 ). The two halves are connected in the middle with an interposed insulating layer. The insulating layer forms a thermal decoupling of the two halves, so that the heat is not transferred via the metal wall of the heat exchanger from one half to the other.
The heat exchanger 1, as described in the sixth variant, arranged in a star shape around the working cylinder 2 and alternately connected to the front and back of the working cylinder 2.
Also in this variant, the heat exchanger 1 rotate together with the working cylinder 2 about the longitudinal axis and thus form a so-called rotor. Just as described in the sixth variant, a compression and an expansion by means of valve control 6 is triggered alternately on each side. Likewise, if there is compression on the front, expansion on the back, or vice versa.
The used in this variant, split heat exchanger 1 are installed so that the outer half of the individual heat exchanger 1 the cold media flow, the inner (the working cylinder 2 facing) half are exposed to the warm media flow.
In the spaces between the heat exchangers 1 is a cylindrical separation 12, with which the heating medium from the cooling medium, is separated within the rotor inserted. Outside around the heat carrier 1 around as well inside (between heat exchanger 1 and cylinder 2) are also concentrically arranged tubes (13 and 14), which together with the separation between the heat exchangers 1, two annular channels form, in each of which is the "cooled" or "heated" part of the heat exchanger is located. In the drawing, these tubes are referred to as outer13 and inner14 sheaths.

Each individual heat exchanger 1 is also separated from the adjacent heat exchangers 1 by means of a separating web 15 which extends from the outer casing 13 to the inner casing 14. By means of these dividers 15, the heating and cooling medium is channeled within the rotor. In each segment between two dividers 15 there is only a single heat exchanger. 1

On both faces of the rotor, the heating or cooling media conveying lines are connected. The heating medium lines are connected to the upper semicircle of the inner annular channel, the cooling medium lines are connected to the lower semicircle of the outer annular channel. Only half of the respective circular rings is flowed through with heating or cooling medium, since the heating and cooling take place alternately.

The cooling section begins after closing the valve 5 at the end of an expansion process within the heating section. The heating section begins after closing the valve 5 at the end of the compression process within the cooling section.

The working substance in the closed heat exchanger 1 is, with a surface whose temperature is below the dew point of the working fluid, as long as condense on this surface until the pressure within the closed heat exchanger 1, the, corresponds to the vapor pressure of the working fluid. In the present case, the entire shell of the "cooled" heat exchanger half have this temperature, because the cooling medium of this half of the heat exchanger 1 constantly extracts the heat of condensation.

1. 1. Die Verbindungsöffnung(en) zwischen geheizter und gekühlter Hälfte wird (werden) mechanisch geschlossen.
2. 2. Es erfolgt eine Art Regeneration, ähnlich wie vorher in der "Sechsten Variante" beschrieben, bei der Kühl/Heizmedium zwischen dem beheizten Segment des inneren Kreisringes, welches direkt nach Schließung des "Expansionsventils" 5 folgt, mit dem gekühlten Segment, welches direkt dem "Kompressionsventil" 5 folgt mittels Ventilator 10 oder Pumpe 10, ausgetauscht wird. Hierdurch kann die Wärme aus dem geheizten Teil der Wärmeüberträgerhülle genutzt werden, die gekühlte Wärmeüberträgerhülle zu erwärmen. Je nach Zweckmäßigkeit dieser Regeneration kann die Menge des kondensierenden Arbeitsstoffes reduziert werden.
3. 3. Eine Kombination der beiden vorgenannten Methoden.

Since the heated half of the heat exchanger 1 is communicatively connected to the cooled half, the condensate would evaporate in this part as far as it could flow there. However, since the (previously) heated part of the heat exchanger 1 is located above the cooled half during the cooling process, it is not physically possible.
The situation is different in the heated part of the heat exchanger 1. If the working material evaporates with constant supply of heat, the steam will condense again when the connection to the (previously) cooled part communicates. This process will take place until the heat transfer tube (now without heat removal) has reached the vapor pressure temperature of the working material. To prevent this, three options are considered here:

1. 1. The connection opening (s) between heated and cooled half are closed mechanically.
2. 2. There is a kind of regeneration, similar to that described previously in the "Sixth Variant", in the cooling / heating medium between the heated segment of the inner annulus, which follows immediately after closure of the "expansion valve" 5, with the cooled segment directly the "compression valve" 5 follows by means of fan 10 or pump 10, is replaced. As a result, the heat from the heated part of the heat transfer tube shell can be used to heat the cooled heat transfer tube shell. Depending on the desirability of this regeneration, the amount of condensing agent can be reduced.
3. 3. A combination of the two aforementioned methods.

Taking into account the design features described, the Clausius-Rankine cyclic process can now be explained. Compare to this Fig. 12 "Design features of the" Stirling-Clausius-Rankine heat engine "and Fig. 16 to 18 "Thermodynamic comparison processes of the Stirling-Clausius-Rankine heat engine". The working material used for this example was dichlorodifluoromethane (Cl ₂ Fl ₂ CH), Frigen R 12. The reference temperatures for this example were 60 ° C as the upper temperature level and 20 ° C as the lower temperature level.

By the rotation of the rotor is the outer, the cooled half of a heat exchanger 1, times below the heated half times over. It is therefore useful to choose the cooling section so that the cooled half of the heat exchanger 1 is located at the bottom during the cooling process. The resulting condensate then collects in the lower and thus in the outer region of the heat exchanger 1. Due to the rotation, the cooled moves over the heated half. From a certain position, the condensate will flow from the cooled to the heated half. (This process replaces the feed pump in the classical Clausius-Rankine process.) Now, the largest mass of the working substance is on the heated side of the heat exchanger 1. The evaporation process begins. To avoid simultaneous condensation on the cooled half, the connection openings between the heated and cooled halves are mechanically closed.

To illustrate the sequence of the cycle, is, with the involvement of Fig. 12 the drawing, initially started with the isochoric cooling process. The, in consideration, heat exchanger 1 is located in the cooling section directly after the closure of the expansion valve 5. The heat exchanger 1 is continuously withdrawn heat on this route. The working material condenses until the vapor pressure (of the working substance) is reached at cooling medium temperature. Since the valve 5 is closed during this process, the total volume within the heat exchanger 1 remains constant.

By the rotation of the point at which the valve 5 is opened to the working cylinder 2, is reached. The valve 5 opens and now connects the space in the heat exchanger 1 with that of the working cylinder 2. The working gas flows because of the negative pressure in the heat exchanger 1 and because of the simultaneous expansion process on the other side of the working piston 3, from the working cylinder 2 in the heat exchanger 1 inside. During this process and in the time after the closing of the (compression) valve 5, the working material condenses again until the, corresponding to the temperature, vapor pressure is reached. ( Fig. 17 , Point 2 to point 3) During the compression of the working gas heat is withdrawn from the heat exchanger 1, through the cooling medium, constantly. So there is an isothermal compression. ( Fig. 17 Point 3 to Point 4) This state change belongs both to the previously described Stirling cycle process and to the Clausius-Rankine cycle process described here. Due to the isothermal and non-isentropic compression of the working gas, the Clausius-Rankine cyclic process described here deviates from the classical one

When the valve 5 is closed, the heat exchanger 1 is constantly supplied with heat ( Fig. 17 , Point 4 to point 5).

By the rotation of the rotor, the point is reached at which the cooled half of the heat exchanger 1 moves over the heated half and wherein the condensate of the working fluid flows into the heated half. The connection openings between the cooled and heated half are mechanically closed. While in the heated half, by the heating medium, constantly heat is supplied, the condensate evaporates. The evaporation takes place until the vapor pressure of the working medium, now at the upper temperature level is reached. ( Fig. 17 , Point 5 to point 5 ').

Upon further rotation, the point is reached at which the valve 5 to the working cylinder 2, the second time during the cycle process, is opened. The valve 5 opens and now connects the space in the heat exchanger 1 with the Space of the working cylinder 2. The pressure in the heat exchanger 1 and the simultaneously taking place on the other side of the working piston 3 compression, urge the gaseous working fluid from the heat exchanger 1 in the working cylinder 2. During this expansion process the heat exchanger 1, from the heating medium constantly supplied heat. There is first a continuation of the evaporation process after an isothermal expansion instead. This state change belongs to both the previously described Stirling cycle and the Clausius-Rankine cycle described here. Due to the isothermal and non-isentropic expansion of the working gas, the Clausius-Rankine cyclic process described here deviates from the classical one.

The connection between the heated and the cooled half is mechanically opened again.

After closing the valve 5, the process starts again.

Tenth variant of the basic module

Heat engine as described in the ninth variant with the difference that the heatable part of the heat exchanger 1 is constructed not as a heat exchanger, but as an absorber for radiant energy. The cooled part may be used for any form of heat transfer, e.g. B. for free convection, water cooling, heat exchangers for gaseous or liquid cooling media u.s.w. be constructed. Working cylinder 2, piston 3, connecting pipes 4, valve 5, valve controls 6, etc. have the same function as described in the ninth variant, they rotate together with the heat exchangers 1 about a common axis. In this variant, the connections between the heated and the cooled part of the heat exchanger 1 are closed during the heating process.

According to the description of the variant seven, the radiation-exposed, absorbent surface of the heat exchanger 1 is protected from convection losses. For this purpose, a glass cover 19 on the front and an enclosure (20 to 22), with reflective surface to the absorber behind it. The cooled part of the heat exchanger 1 is shaded analogously, as described in the variant seven, against the radiation energy.

Eleventh variant

In this variant, a rotor with heat exchangers 1, connecting pipes 4, valves 5 and valve control 6 is used as described in the Ninth Variant but without working cylinder 2 and piston 3. Thus, there are not two valve controls 6, (on both sides of the working cylinder are arranged) but compression and expansion of all heat exchanger 1 take place at the same valve control 6.
Instead of the working piston 3, a rotary engine is used, such. Example, a rotary piston machine, reverse screw compressor, reversed Vielzellverdichter, turbine or the like over which the expanding working gas can relax. Since in the rotor described, consisting of heat exchanger 1, connecting pipes 4, working cylinder 2, etc., the valves 5 always open for expansion in the same place, can be introduced with a suitable valve construction, the expanding working gas in a fixed line. This initiates the working gas in the high pressure side of the rotary engine. Similarly, for compression, a line from the low-pressure side of the rotary engine to the point at which the valves 5 open for the compression process, return the working gas to the heat exchangers 1 again.
In such a machine, a rotating shaft is provided with which a power generator or other machine can be driven.
The rotational movement can also be used to drive the heat exchanger rotor. By carefully adjusting the rotational speeds of the rotor and rotary machine, it is ensured that the correct amount of working gas is present in the rotary engine.
In this variant, an isotropic expansion takes place, thus it has a lower thermodynamic efficiency compared to the other variants.

Deviations of this heat engine of the prior art

The heat engine of this heat engine is operated with an external heat source, therefore it is different from all heat engines with internal combustion.

In a variant of this heat engine, the Stirling cycle process is connected to a Rankine cycle process, resulting in 6 state changes. As a result, this heat engine differs from conventional machines, which run either only with a Stirling cycle or only with a Rankine cycle.

The most important difference to the conventional techniques consists in the interaction of different cycle processes on a common working cylinder 2. In a complete process sequence of this heat engine, the working gas or agent in each heat exchanger 1 has a complete Stirling cycle process with four state changes or a complete Stirling Clausius Rankine key process with 6 state changes go through d. H. Each valve 5 between the individual heat exchangers 1 and common cylinder 2 has opened and closed twice. This means for each heat exchanger 1 in each case an expansion and a compression.

It is a heat engine that has very low internal losses compared to other heat engines, with few moving parts and little dead space. The moving parts are a freely movable working piston 3 in a working cylinder 2 and a rotating rotor consisting of: heat exchanger 1, connecting pipes 4, valves 5, inner 14 and outer 13 sheaths and partitions 15.

Through the use of valves 5, this heat engine differs from the classic Stirling engine. The state changes can therefore be exploited almost completely. By careful design of the components, the actual efficiency can be brought very close to the theoretically possible. The valve 5 is opened only when the warm-up or cool down process is completed. Over the shortest path, the working gas can expand into the working cylinder 2 or compressed from the working cylinder 2.

A difference of this heat engine to the conventional thermal power plants lies in the fact that in conventional systems, the working gas or agent, eg. B. in steam power plants, from the warm heat exchanger 1 to the cold heat exchanger 1 and moved back again, in this heat engine, however, the largest part of the working gas in the same heat exchanger 1 remains there alternately warmed or cooled.

The piston 3 of this free-piston engine is magnetized by permanent magnets 7 or exciting current and runs in a non-metallic working cylinder 2, around which an electric coil 8 is mounted. This converts the mechanical work directly into electrical current without detours. In addition to the friction losses of the free piston 3 occur when power generation, no further mechanical losses.

Organic compounds such. B. ammonia and Frigene, which in heat engines such. B. ORC systems are used, can also be used meaningfully in this heat engine in the same way by aggregate state changes. This heat engine differs from the conventional ORC system in that condensation and evaporation take place alternately at the same place, within a heat exchanger 1.

Although the invention also relates to a heat engine of the type described above, the invention is directed in particular to a power plant with heat extraction described below.

A possible construction of a thermal power plant according to the invention is in Fig. 19 the drawing shown. Here are a suitable number of heat engines A, for example, A1, A2, A3, .... An, arranged in series. The intended for combustion air 22 is as a cooling medium the cooled part of the individual heat engines A1, A2, A3, ... An succession flow through and fed after leaving the last heat engine to a combustion process in the combustion chamber 25 as combustion air.

The combustion gases 30 from the combustion process in the combustion chamber 25 flows through the heated part of the individual heat engines An ... A2, A1 in the opposite direction and in the reverse order as the cooling medium 22 with a similar temperature difference but with each different temperature level at each heat engine A, as in the diagram Fig. 21 the drawing is shown. The working substance in each heat engine A is selected so that it is adapted to the respective temperatures occurring there.

The fuel is stored in a fuel tank 26. The fuel container 26 may be designed for solids (eg wood chips) as a funnel or for liquids or gases as a tank. The fuel is introduced into the combustion chamber 25 by means of a conveyor 27 (as a cell sluice or screw in the case of solid substances or a pump in the case of liquids). For solids, a combustion grate 28 is provided which is designed so that the fuel as optimally distributed over the surface.

The cooling and combustion air 22 may be pure ambient air but also cooled air or air emerging from other processes, which are suitable for burning the fuel used. She is using a blower 21 through the heat exchanger 1 of the individual heat engines A up to the combustion chamber 25 promoted.

As it flows through each heat exchanger 1 of the individual heat engines A, the temperature of the air, because of the heat absorption of the heat exchangers 1, to.

The warmed up air is used after leaving the heat exchanger 1 of the last heat engine An as combustion air. Here, through the use of control valves 23, a portion of the cooling air through the combustion chamber 25 and a part passed to the combustion chamber 25 over. After combustion, the two air streams are brought together again and mixed. The flaps 23 are controlled via a temperature control loop, consisting of a temperature sensor 31, controller and actuator 24, so that a constant temperature of the combustion gases 30 is achieved. These combustion gases 30 are hereinafter referred to as hot gases.

The hot gases 30 are introduced into the heat exchangers 1 of the heat engine An, through which the cooling air 22 was last carried out. Further, the hot gases flow through all the other heat engines A in the reverse order and direction as the cooling air. By discharging the heat to the heat exchanger 1, the temperature in each heat exchanger 1 decreases. Since the temperature decreases in the opposite direction as the cooling air increases in each heat engine A, more or less, same temperature differences occur which are required to implement the heat in work.

The outlet temperature of the hot gases depends on the selected number of heat engines A, the working materials, especially in the last stages and the construction of the heat engines A. It can be similar to a condensing boiler at about 50 ° C. This means that the heat of vaporization of the water in the combustion gases 30 also contributes to power generation. The upper calorific value of the fuel is used. Also, the heat of evaporation that is consumed to evaporate the water in wet fuels is not lost.

For the resulting condensate from the heat engines A neutralization 39 is provided.

In order to use the residual heat of the hot gases after leaving the last heat engine A1 for heating purposes, it is passed through the primary side of a heat exchanger 35. Heating water for district heating 36 is circulated through the secondary side of the heat exchanger. If more heat is needed for heating purposes than the residual heat in the hot gases 30 after the last heat engine An, the last heat engine A1 can be stopped, so that the heat can pass unused. If this is not sufficient for the heat demand, then the second-last thermal engine A2 can be stopped. This can be continued until the heat engine is stopped on and the entire heat is used only for heating purposes.

Especially in the first of the hot gases flowed through heat engines A, the vapor pressure of the working material located there can rise so high at too high temperatures that it can damage the construction of the heat exchanger 1, therefore, when stopping the heat engine A, the hot gases are not through the heat exchanger of the heat engine led but by Umschaltklappen with drive 34 to these past and directed directly into the heat exchanger 35. There is Umschaltklappen with drive 34 before each heat engine A, whereby the hot gases can be passed to the subsequent heat engines A to use the heat for other purposes.

The hot gases are finally fed to a chimney 38. If necessary, a flue gas cleaning 37 between the cogeneration plant and chimney 38 can be provided.

The individual heat engines A - compare Fig. 20 - Are equipped with a magnetized Koben 3 and the cylinder 2 is enclosed with an electric coil 8 such that the piston 3, an electric current is generated by induction. As a result, each machine A produces a type of alternating current, each with different frequencies. This current is converted into direct current via rectifier 40 and stored in accumulators 42 while at the same time the direct current is also converted via an inverter 43 into alternating current at mains frequency. For each machine A own power drainage 41 is provided.

Since the heat engine A described above is listed in several variants, different variants of the heat engine A can be used in this type of cogeneration. It would be z. B. advantageous if at very high temperatures heat engines, which are operated according to the Stirling cycle, and at low temperatures heat engines which are operated with combined Stirling Clausius Rankine cycle can be used.

1. 1. Wärmekraftmaschine, die durch vier Zustandsänderungen, nämlich
   1. 1) isochorische Wärmezufuhr,
   2. 2) isothermische Expansion,
   3. 3) isochorische Wärmeabfuhr,
   4. 4) isothermische Kompression
   eines eingeschlossenen Arbeitsgases zwischen zwei Temperaturebenen Arbeit verrichtet, und folgendes aufweist: mindestens drei Wärmeüberträger 1A, 1B und 1C, die jeweils nur eine Verbindung insbesondere ein Verbindungsrohr 4A, 4B, und 4C zu einem Arbeitszylinder 2 aufweisen und wobei die Verbindungen jeweils mit einem Ventil 5A, 5B oder 5C ausgestattet sind und wobei die Wärmeüberträger 1A, 1B und 1C abwechselnd von einem Heizmedium und Kühlmedium umströmt werden.
2. 2. Wärmekraftmaschine nach Punkt 1, wobei die Wärmeüberträger 1A, 1B und 1C, die Verbindungsrohre 4A, 4B, und 4C und der Arbeitszylinder 2 mit einem Arbeitsgas gefüllt sind und im Arbeitszylinder 2 sich ein frei beweglicher Kolben 3 befindet, der durch die Expansion und Kompression des Arbeitsgases Arbeit verrichtet.
3. 3. Wärmekraftmaschine nach den Punkten 1 bis 3 wobei das Arbeitsgas in einem ersten der Wärmeüberträger 1A von einer externern Quelle auf die obere Temperaturebene aufgewärmt wird und durch Öffnen des zugehörigen ersten Ventils 5A das Gas bei anhaltender Wärmezufuhr in den Arbeitszylinder 2 expandieren kann und dort Arbeit verrichtet, wobei nach Abschluss des Expansionsvorganges selbiges Ventil 5A wieder schließt und nachfolgend der erste Wärmeüberträger 1A bei geschlossenem Ventil 5A von der externen Quelle auf die untere Temperaturebene abgekühlt wird.
4. 4. Wärmekraftmaschine nach den Punkten 1 bis 3 wobei das Arbeitsgas in einem anderen zweiten Wärmeüberträger 1 B zeitlich versetzt gegenüber dem ersten Wärmeüberträger auf die untere Temperaturebene abgekühlt wird und nach Öffnen diesem Wärmeüberträger 1 B zugeordneten 2.Ventils 5B, komprimiert wird, bei gleichzeitiger Wärmeabfuhr, wobei das vorher expandierte Arbeitsgas aus dem Arbeitszylinder 2 in den zweiten Wärmeüberträger 1B strömt und dabei wiederum Arbeit am Arbeitskolben 3 verrichtet, wobei bei Abschluss des Kompressionsvorganges im Wärmeüberträger 1 B das diesem Wärmeüberträger 1 B zugeordnete zweite Ventil 5B schließt, und bei geschlossenem zweiten Ventil 5B der Wärmeüberträger 1 B im weiteren Verlauf auf die obere Temperaturebene aufgewärmt wird.
5. 5. Wärmekraftmaschine nach den Punkten 1 bis 4, wobei das Arbeitsgas in einem weiteren dritten Wärmeüberträger 1C von der externen Quelle auf die obere Temperaturebene zeitlich versetzt angehoben wird und nach Öffnen dem Wärmeüberträger 1C zugeordneten dritten Ventils 5C, expandiert, bei gleichzeitiger Wärmezufuhr, wobei das vorher komprimierte Arbeitsgas aus dem dritten Wärmeüberträger 1C in den Arbeitszylinder 2 fließt und Arbeit verrichtet und nachfolgend der dritte Wärmeüberträger 1C bei geschlossenem dritten Ventil 5C von der externen Quelle auf die untere Temperaturebene abgekühlt wird.
6. 6. Wärmekraftmaschine nach den Punkten 1 - 5, wobei das eingeschlossene Arbeitsgas im ersten Wärmeüberträger 1A inzwischen auf die niedere Temperaturebene abgekühlt ist und beim Öffnen des ersten Ventils, welches dem ersten Wärmeüberträger 1A zugeordnet ist, 5A sich komprimiert und während des Kompressionsvorganges vom ersten Wärmeüberträger 1A Wärme abgeführt wird, wobei im Arbeitszylinder 2 durch die Kompression Arbeit verrichtet wird, und nach Schließen des ersten Ventils 5A der erste Wärmeüberträger 1A wieder aufgewärmt wird, wobei in gleicher Weise beim Öffnen des entsprechenden zweiten Ventils 5B, aus dem inzwischen aufgewärmten zweiten Wärmeüberträger 1 B eine Expansion des Arbeitsgases gefolgt von einer Kompression im inzwischen gekühlten dritten Wärmeüberträger 1C erfolgt.
7. 7. Wärmekraftmaschine nach Punkt 1, wobei zum Aufwärmen und Abkühlen des Arbeitsmediums für das bestimmte Heiz- oder Kühlmedium geeignete Wärmeüberträger 1 eingesetzt werden.
8. 8. Wärmekraftmaschine nach den Punkten 1 bis 7, wobei die Ventile 5A, 5B und 5C über eine Nockenwelle 6, einen elektrischen Antrieb oder eine ähnliche Ventilsteuerung 6 in bestimmter Reihenfolge und bestimmtem Rhythmus geöffnet und geschlossen werden.
9. 9. Wärmekraftmaschine nach einem der Punkte 2 bis 8, wobei jedoch zur Übertragung der Arbeit, der Arbeitskolben 3 mit permanent oder erregten Magneten 7 magnetisiert ist und der Arbeitszylinder 2 in einer solchen Weise mit einer elektrischen Spule 8 umschlossen wird, dass durch die Bewegungen des Arbeitskolbens 3 Strom erzeugt wird, d.h. die Arbeit des Kolbens 3 wird direkt in elektrischen Strom umgesetzt.
10. 10. Wärmekraftmaschine nach den Punkten 1 bis 9, wobei ein Druckausgleichsbehälter 9 am Arbeitszylinder 2 angeschlossen ist, und zwar auf der gegenüberliegenden Seite zu Anschlüssen der Arbeitszylinder.
11. 11. Wärmekraftmaschine nach Punkt 10, wobei der Druckausgleichbehälter 9 mit dem gleichen Arbeitsgas gefüllt ist wie die Wärmeüberträger 1.
12. 12. Wärmekraftmaschine nach Punkt 10, wobei der Druck im Ausgleichsbehälter 9 dem Ruhedruck in den Wärmeüberträgern 1A, 1B, 1C angeglichen wird.
13. 13. Wärmekraftmaschine nach Punkt 10, wobei die Wärmekraftmaschine bei jedem geeigneten Druck des Arbeitsgases, unabhängig vom atmosphärischen Druck, betrieben werden kann.
14. 14. Wärmekraftmaschine nach Punkt 1 mit einer beliebigen ungeraden Anzahl von Wärmeüberträgern, die mit Verbindungsrohren 4 nebst Ventilen 5, an denselben Arbeitszylinder 2 angeschlossen sind.
15. 15. Wärmekraftmaschine nach einem oder mehreren der Punkte 1 bis 14, wobei mit gleiche ungerade Anzahl von Wärmeüberträgern 1, Ventilen 5 und Verbindungen bzw. Verbindungsrohren 4 an beiden Seiten des Arbeitszylinders 2 angeschlossen sind, und wobei die Periode eines Kreislaufes auf beiden Arbeitszylinderseiten identisch ist und die beiderseits angeordneten Ventile 5 so gesteuert werden, dass eine Kompression auf der einen Seite und zur gleichen Zeit eine Expansion auf der anderen Seite erfolgt.
16. 16. Wärmekraftmaschine nach Punkt 15 mit einer beliebigen ungeraden Anzahl von Wärmeüberträgern 1, Verbindungen insbesondere Verbindungsrohren 4 und dazu gehörenden Ventilen 5, die an beiden Seiten an denselben Arbeitszylinder 2 angeschlossen sind.
17. 17. Wärmekraftmaschine nach Punkt 1 bei der jedoch das Heiz- und Kühlmedium die dem Arbeitszylinder 2 genau gegenüberliegenden Wärmeüberträger 1 gleichzeitig durchströmt.
18. 18. Wärmekraftmaschine nach einem der Punkte 1 bis 16, wobei eine Anordnung aus mehreren Arbeitszylindern 2, Kolben 3, Verbindungen 4, Ventilen 5 und Ventilsteuerungen 6 besteht, die alle parallel an eine beliebige Anzahl gemeinsamer Wärmeüberträger 1 geschaltet sind.
19. 19. Wärmekraftmaschine nach Punkt 15, wobei ein Arbeitsgas eingesetzt wird, dessen Siedepunkt bei entsprechend gewähltem Druck zwischen dem unteren und oberen Temperaturniveau liegt, damit eine Kondensation während der isochorischen Wärmeentnahme und Kompression und eine Verdampfung während der isochorischen Wärmezuführung und Expansion, stattfindet.
20. 20. Wärmekraftmaschine nach Punkt 15 bei der die Wärmeüberträger 1 alle sternförmig um die Längsachse des Arbeitszylinders 2 angeordnet sind und die Verbindungsrohre 4 abwechselnd an beiden Seiten des Arbeitszylinders 2 angeschlossen sind, wobei die Wärmeüberträger 1 starr mit dem Arbeitszylinder 2 verbunden sind und sich mit demselben um die gemeinsame Längsachse drehen, sodass die einzelnen Wärmeüberträger 1 während einer Hälfte der Umdrehung durch das Kühlmedium und während der anderen Hälfte der Umdrehung durch das Heizmedium geführt werden.
21. 21. Wärmekraftmaschine nach Punkt 20 wobei die Wärmeüberträger 1 als Strahlungsabsorber flach ausgebildet sind und die Form eines Scheibensegmentes haben und kranzförmig so um die Längsachse des Arbeitszylinders 2 ausgerichtet sind, dass eine Scheibe entsteht, wobei sie mit einer strahlungsabsorbierenden Oberfläche ausgestattet sind und wobei sie auch für Kühlung durch Konvektion ausgebildet sind, da die aufgenommene Wärme wieder an die Umgebung abgegeben werden muss, wobei Wärmeüberträger 1, Verbindungsrohre 4 und Ventile 5 starr mit dem Arbeitszylinder 2 verbunden sind und sich mit demselben um die gemeinsame Mittelachse drehen.
22. 22. Wärmekraftmaschine nach Punkt 21, wobei die Hälfte der Wärmeüberträger 1 der Strahlung ausgesetzt werden, während die andere Hälfte der Wärmeüberträger 1 beschattet wird.
23. 23. Wärmekraftmaschine nach Punkt 21, wobei die Beschattung aus verschiedenen Schichten aufgebaut ist, und die der Strahlungsquelle zugewandte Seite eine reflektierende Oberfläche 23 z.B. Spiegel erhält, wobei danach eine Isolierschicht 21 und auf der Rückseite eine Schicht 24 mit grauer oder dunkler Oberfläche folgt, welche die Abstrahlung der Wärmeüberträger 1 nach Beschattung absorbiert und zu der Abführung der Wärme durch Konvektion beiträgt.
24. 24. Wärmekraftmaschine nach Punkt 21, wobei die Wärmeüberträger 1, welche der Strahlung ausgesetzt sind, durch eine Einhausung vor Verlust durch Konvektion und Strahlung geschützt sind, und wobei die Einhausung von vorne der Strahlungsquelle zugewandten Seite mit einem Glas 19, seitlich und hinten mit einer mehrschichtigen Abdeckung 20 bis 22 ausgeführt ist, wobei ferner die innere, den Wärmeüberträgern 1 zugewandte Schicht 22 dieser Abdeckung gewellt und reflektierend ist, während die mittlere 21 Schicht eine Isolierschicht und die nach außen gewandte Schicht 20 eine Wetterschutzschicht ist.
25. 25. Wärmekraftmaschine nach Punkt 21, wobei die Wärmeüberträger 1 um den Mittelpunkt des Absorberkranzes rotieren, und jeder Wärmeüberträger 1 dabei abwechselnd die Beschattung und Einhausung passiert, wobei sie dadurch abwechselnd durch die Strahlung aufgeheizt und, während der Beschattung, durch Abgabe der Wärme an die Umgebung wieder abgekühlt werden.
26. 26. Wärmekraftmaschine nach Punkt 21, wobei die Ventile 5 so gesteuert werden, dass abwechselnd ein gekühlter und erwärmter Wärmeüberträger 1 mit dem Arbeitszylinder 2 verbunden werden, um durch Expansion oder Kompression Arbeit zu verrichten.
27. 27. Wärmekraftmaschine nach Punkt 15 und Punkt 21 mit ungerader Anzahl Wärmeüberträgern 1, die jeweils abwechselnd auf der einen und anderen Seite des Arbeitszylinders 2 angeschlossen sind.
28. 28. Wärmekraftmaschine mit externer Wärmequelle und mindestens 3 Wärmeüberträgern 1 mit eingeschlossenem Arbeitsgas, welche abwechselnd gekühlt und beheizt werden, wobei die thermodynamischen Zustandsänderungen in jedem Wärmeüberträger 1 in Zusammenhang mit einem Arbeitszylinder 2 und Ventilsteuerung 5 und 6 a) isochorische Wärmezufuhr, b) isothermische Expansion, c) isochorische Wärmeabfuhr und d) isothermische Kompression sind, und wobei die nacheinander folgenden Zustandsänderungen: Expansion und Kompression nicht mit ein demselben Arbeitsgas stattfinden, und wobei nach der Expansion aus einem gewärmten Wärmeüberträger 1 in den Arbeitszylinder 2 eine Kompression in einem anderen gekühlten Wärmeüberträger 1 folgt, und Expansion und Kompression mittels Ventilen zwischen einzelnen Wärmeüberträgern 1 und Arbeitszylinder 2 in Abhängigkeit vom Heiz-/Kühlvorgang ausgelöst werden.
29. 29. Wärmekraftmaschine mit mindestens 3 oder mehr geschlossenen Wärmeüberträgern 1, die zusammen mit einem gemeinsamen Zylinder 2 und Arbeitskolben 3 Arbeit verrichten, wobei in jedem Wärmeüberträger 1 mit Arbeitszylinder 2 und Arbeitskolben 3, ein eigener Stirlingkreisprozess, zeitlich versetzt gegenüber dem anderen Wärmeüberträger 1, stattfindet.
30. 30. Wärmekraftmaschine nach Punkt 28, wobei die einzelnen Kreisprozesse durch den Einsatz von Ventilen 5 voneinander getrennt werden.
31. 31. Wärmekraftmaschine nach Punkt 28 bei der der Wärmeüberträger 1 einen geschlossenen Raum bildet in dem sich ein Arbeitsstoff befindet, der weiterhin für einen optimierten Wärmeaustausch zwischen Arbeitsstoff und Umgebung konstruiert ist, wobei ein Teil des Wärmeüberträgers 1 von dem anderen Teil thermisch, durch eine dazwischen eingebaute Isolierschischicht 25, entkoppelt ist, wobei ein Teil gekühlt und der andere beheizt wird, wobei eine mechanische Schließvorrichtung 26 zwischen dem gekühlten und beheizten Teil eingebaut ist, um den eingeschlossenen Raum des Wärmeüberträgers 1 bei Bedarf in zwei Räume zu unterteilen, wobei eine Anschlussöffnung in der Wand des gewärmten Teiles des Wärmüberträgers 1 existiert, durch welche der Arbeitsstoff ein- und ausströmen kann.
32. 32. Wärmekraftmaschine nach Punkt 31 bei der eine beliebige Anzahl Wärmeüberträger 1 sternförmig und symmetrisch um einen Arbeitszylinder 2 angeordnet und starr mit ihm verbunden sind, wobei die Anschlussöffnungen der Wärmeüberträger 1 mit dem Arbeitszylinder 2 über Verbindungen bzw. Verbindungsrohre 4 verbunden sind, damit ein Austausch des Arbeitsgases zwischen beiden möglich ist, wobei eine Hälfte der Wärmeüberträger 1 an der Stirnseite des Arbeitszylinders 2, die andere Hälfte an der anderen, der Stirnseite gegenüberliegenden Seite angeschlossen sind, wobei immer abwechselnd ein Wärmeüberträger 1 an der einen der nächste an der anderen Seite angeschlossen ist, wobei sich Ventile 5 in den Verbindungen 4 zwischen Wärmeüberträger 1 und Arbeitszylinder 2 befinden, die über eine Ventilsteuerung 6 nach Punkt 2 geöffnet und geschlossen werden, während sich Arbeitszylinder 2, Wärmeüberträger 1, Verbindungsrohre 4 und Ventile um die Längsachse des Arbeitszylinders 2 als Rotor drehen.
33. 33. Wärmekraftmaschine nach Punkt 32, wobei ein Arbeitsgas eingesetzt wird, dessen Siedepunkt bei entsprechend gewähltem Druck zwischen dem unteren und oberen Temperaturniveau liegt, damit eine Kondensation während der isochorischen Wärmeentnahme und Kompression und eine Verdampfung während der isochorischen Wärmezuführung und Expansion stattfindet.
34. 34. Wärmekraftmaschine mit Wärmeüberträgern 1 nach Punkt 32, wobei der gekühlte Teil der Wärmeüberträger 1 sich auf der Außenseite während der beheizte Teil sich auf der Innenseite zum Arbeitszylinder 2 hin befindet, wobei der gekühlte Teil über die Hälfte des Umfanges mit einem Kühlmedium gekühlt und der beheizte Teil über die gegenüberliegende Hälfte des Umfanges beheizt wird, während der Rotor bestehend aus Wärmeüberträger 1, Arbeitszylinder 2 mit Kolben 3, Verbindungsrohren 4 und Ventilen 5 rotiert.
35. 35. Wärmekraftmaschine nach Punkt 32 bei der das Ventil 5 zwischen jedem Wärmeüberträger 1 und Arbeitszylinder 2 während einer Umdrehung des Rotors zweimal geöffnet und geschlossen wird, und zwar einmal während des Kühlvorganges und einmal während des Heizvorganges.
36. 36. Wärmekraftmaschine nach Punkt 32 bei der die Verbindungen zwischen den gekühlten und beheizten Teilen der Wärmeüberträger 1 mit einer Schließvorrichtung 26 während des Heizvorganges geschlossen werden.
37. 37. Wärmekraftmaschine nach den Punkten 31 bis 36 bei der mittels Umwälzung des Heiz- und Kühlmediums die innere Wärme des Materials des beheizten Teils der Wärmeüberträger 1 innerhalb eines Segmentes kurz nach Abschluss des Heizvorganges genutzt wird, um den gekühlten Teil der Wärmeüberträger 1 innerhalb eines Segmentes kurz nach Abschluss des Kühlvorganges aufzuwärmen, um eine Kondensation im gekühlten Teil während der Beheizung des beheizten Teiles zu minimieren.
38. 38. Wärmekraftmaschine nach den Punkten 31 bis 37, jedoch ohne Arbeitszylinder 2 und Kolben 3, wobei die Ventile 5 aller Wärmeüberträger 1 von einer einzigen Ventilsteuerung 6 angesteuert werden, wobei die Wärmeüberträger 1 beim Öffnen der ihnen zugeordneten Ventile 5 mit einer Rotationskraftmaschine verbunden sind, welche die Druckdifferenz zwischen zwei Druckebenen eines Gases nutzt um Arbeit zu verrichten, wobei die Verbindung in der die Expansion stattfindet mit der Hochdruckseite und die Verbindung in der die Kompression stattfinden mit der Niederdruckseite der Rotationskraftmaschine verbunden ist, wobei ein Teil der Rotationsenergie der Rotationskraftmaschine über ein Getriebe als Antrieb dieser Wärmekraftmaschine genutzt werden kann.
39. 39. Wärmekraftmaschine nach den Punkten 31 bis 37, wobei die beheizten Teile der Wärmeüberträger 1 als Strahlungsabsorber ausgebildet sind, wobei die beheizten Teile der Wärmeüberträger 1 flach sind und die Form eines Scheibensegmentes haben, und kranzförmig so um einen Mittelpunkt ausgerichtet, dass eine Scheibe gebildet wird, wobei sie mit einer strahlungsabsorbierenden Oberfläche ausgestattet sind, wobei diese Strahlungsabsorber gegen Verluste durch Konvektion und Abstrahlung mittels geeignete Maßnahmen gemäß Anspruch 24 geschützt sind.
40. 40. Wärmekraftmaschine nach den Punkten 31 bis 36 mit mindestens drei oder mehr geschlossenen Wärmeüberträgern 1, die zusammen mit einem gemeinsamen Arbeitszylinder 2 und Arbeitskolben 3 Arbeit verrichten, wobei in jedem Wärmeüberträger 1 mit Arbeitszylinder 2 und Arbeitskolben 3 ein eigener Stirlingkreisprozess, kombiniert mit einen Clausius-Rankine-ähnlichem Kreisprozess, zeitlich versetzt gegenüber den anderen Wärmeüberträgern 1, stattfindet.
41. 41. Wärmekraftmaschine nach den Punkten 31 bis 36 deren Wirkungsweise auf folgenden Zustandsänderungen in einem Kreisprozess beruht: 1. isochorischer Wärmeentzug, 2. isobarische Verflüssigung, 3. isothermischer Kompression, 4. isochorische Wärmezuführung, 5. isobarische Verdampfung und 6. isothermische Expansion.
42. 42. Kraftanlage mit Wärmeauskopplung bei der eine beliebige Anzahl Wärmekraftmaschinen A gemäß den obigen Punkten in Reihe hintereinander geschaltet sind, wobei das Heizmedium 30, welches aus Verbrennungsgasen 30 eines Verbrennungsprozesses besteht, die einzelnen Wärmekraftmaschinen A kaskadenartig nacheinander durchströmt, wobei die Temperatur des Heizmediums 30 beim Durchströmen der Wärmeüberträger 1 der Wärmekraftmaschinen An bis A1 abnimmt und wobei das Kühlmedium 22, welches aus Umgebungsluft oder sonstiger Luft besteht, dieselben Wärmekraftmaschinen A1 bis An in entgegengesetzter Richtung und in umgekehrter Reihenfolge kaskadenartig durchströmt, wobei die Kühlmediumtemperatur beim Durchströmen der Wärmeüberträger 1 der Wärmekraftmaschinen A zunimmt, wobei eine Temperaturdifferenz zwischen dem Heiz und Kühlmedium mehr oder weniger erhalten bleibt und jede Wärmekraftmaschine A Arbeit verrichtet und durch sie elektrischen Strom erzeugt, wobei das Kühlmedium nach Austreten aus der letzten Wärmekraftmaschine A der Kaskade als Verbrennungsluft 30 in einem Verbrennungsprozess verwendet wird und wobei das Heizmedium 30 nach Austritt aus der letzten Wärmekraftmaschine An in der Kaskade für Heizungszwecke oder sonstige Wärmeverbraucher genutzt wird.
43. 43. Kraftwärmekopplungsanlage, nach Punkt 42, jedoch ohne Verbrennungsprozess, bei der die Abwärme aus anderen Prozessen benutzt wird.
44. 44. Kraftwärmekopplungsanlage nach Punkt 42 bei der verschiedene Varianten der unter den Punkten 1 bis 41 beschriebenen Wärmekraftmaschine A eingesetzt werden.
45. 45. Kraftanlage mit Wärmeauskopplung bei welcher der Strom mit einer beliebigen Anzahl, der oben beschriebenen und in den Figuren 1 bis 18 dargestellten Wärmekraftmaschinen A erzeugt wird, wobei die Wärmekraftmaschinen A in Reihe geschaltet sind und mit dem Kühlmedium 22 und Heizmedium 30 im Gegenstromprinzip durchströmt werden, wobei das aufgewärmte Kühlmedium 22 nach Austreten aus der letzten Wärmekraftmaschine als Verbrennungsluft genutzt wird, und wobei das aus der in der Gegenrichtung letzten Wärmekraftmaschine A austretende Heizmedium 30 weiter für Heizungszwecke oder andere Wärmeverbraucher genutzt werden kann.

The following points summarize some basic and preferred embodiments of the heat engine and the power plant:

1. 1. Heat engine, by four state changes, namely
   1. 1) isochoric heat supply,
   2. 2) isothermal expansion,
   3. 3) isochoric heat removal,
   4. 4) isothermal compression
   of at least three heat exchangers 1A, 1B and 1C, each having only one connection, in particular a connecting pipe 4A, 4B, and 4C to a working cylinder 2, and the connections each with a valve 5A 5B or 5C, and wherein the heat exchangers 1A, 1B and 1C alternately flows around a heating medium and cooling medium.
2. 2. Heat engine according to item 1, wherein the heat exchangers 1A, 1B and 1C, the connecting pipes 4A, 4B, and 4C and the working cylinder 2 are filled with a working gas and in the working cylinder 2 is a freely movable piston 3, by the expansion and Compression of the working gas done work.
3. 3. Heat engine according to the items 1 to 3 wherein the working gas is warmed in a first of the heat exchanger 1A from an external source to the upper temperature level and by opening the associated first valve 5A, the gas can expand in sustained heat supply into the working cylinder 2 and work there performs, after completion of the expansion process same valve 5A closes again and then the first heat exchanger 1A is cooled with the valve 5A closed from the external source to the lower temperature level.
4. 4. Heat engine according to points 1 to 3 wherein the working gas is cooled in a different second heat exchanger 1 B offset from the first heat exchanger to the lower temperature level and after opening this heat exchanger 1 B associated second valve 5 B, is compressed, with simultaneous heat dissipation , wherein the previously expanded working gas from the working cylinder 2 flows into the second heat exchanger 1B and in turn performs work on the working piston 3, at the conclusion of the compression process in the heat exchanger 1 B, the heat exchanger 1 B associated second valve 5B closes, and the second valve is closed 5B of the heat exchanger 1 B is heated in the further course to the upper temperature level.
5. 5. Heat engine according to the items 1 to 4, wherein the working gas is raised in a further third heat exchanger 1C from the external source to the upper temperature plane offset in time and after opening the heat exchanger 1C associated third valve 5C, expanded, with simultaneous heat, wherein the previously compressed working gas from the third heat exchanger 1C flows into the working cylinder 2 and performs work, and subsequently the third heat exchanger 1C is cooled from the external source to the lower temperature level with the third valve 5C closed.
6. 6. Heat engine according to points 1-5, wherein the trapped working gas in the first heat exchanger 1A is now cooled to the lower temperature level and when opening the first valve, which is associated with the first heat exchanger 1A, 5A compressed and during the compression process of the first heat exchanger 1A heat is dissipated, being performed in the working cylinder 2 by the compression work, and after closing the first valve 5A, the first heat exchanger 1A is reheated, in the same way when opening the corresponding second valve 5B, from the meantime reheated second heat exchanger. 1 B is carried out an expansion of the working gas followed by compression in the meantime cooled third heat exchanger 1C.
7. 7. Heat engine according to item 1, wherein for heating and cooling of the working medium for the particular heating or cooling medium suitable heat exchanger 1 are used.
8. 8. Heat engine according to the items 1 to 7, wherein the valves 5A, 5B and 5C are opened and closed via a camshaft 6, an electric drive or a similar valve control 6 in a certain order and a certain rhythm.
9. 9. Heat engine according to any one of items 2 to 8, wherein, however, for transmitting the work, the working piston 3 is magnetized with permanent or energized magnet 7 and the working cylinder 2 is enclosed in such a manner with an electric coil 8 that by the movements of the Working piston 3 power is generated, ie the work of the piston 3 is converted directly into electricity.
10. 10. Heat engine according to the items 1 to 9, wherein a pressure equalization tank 9 is connected to the working cylinder 2, on the opposite side to terminals of the working cylinder.
11. 11. Heat engine according to item 10, wherein the surge tank 9 is filled with the same working gas as the heat exchanger. 1
12. 12. Heat engine according to item 10, wherein the pressure in the expansion tank 9 is equalized to the static pressure in the heat exchangers 1A, 1B, 1C.
13. 13. Heat engine according to item 10, wherein the heat engine at each suitable pressure of the working gas, regardless of the atmospheric pressure, can be operated.
14. 14. Heat engine according to item 1 with an arbitrary odd number of heat exchangers, which are connected with connecting pipes 4 together with valves 5, to the same working cylinder 2.
15. 15, heat engine according to one or more of the items 1 to 14, being connected with the same odd number of heat exchangers 1, valves 5 and connections or connecting pipes 4 on both sides of the working cylinder 2, and wherein the period of a cycle on both sides of the working cylinder is identical and the valves 5 arranged on both sides are controlled so that a compression on the one hand and at the same time an expansion on the other hand takes place.
16. 16. Heat engine according to item 15 with an arbitrary odd number of heat exchangers 1, compounds in particular connecting pipes 4 and associated valves 5, which are connected on both sides to the same working cylinder 2.
17. 17 heat engine according to item 1 in which, however, the heating and cooling medium flows through the working cylinder 2 exactly opposite heat exchanger 1 at the same time.
18. 18. Heat engine according to any one of items 1 to 16, wherein an arrangement of a plurality of working cylinders 2, piston 3, connections 4, valves 5 and valve controls 6, which are all connected in parallel to any number of common heat exchanger 1.
19. 19. A heat engine according to item 15, wherein a working gas is used, the boiling point is at a correspondingly selected pressure between the lower and upper temperature levels, so that condensation during the isochoric heat extraction and compression and evaporation during the isochoric heat supply and expansion, takes place.
20. 20. Heat engine according to item 15 in which the heat exchanger 1 are all arranged in a star shape around the longitudinal axis of the working cylinder 2 and the connecting pipes 4 are alternately connected to both sides of the working cylinder 2, wherein the heat exchanger 1 are rigidly connected to the working cylinder 2 and with the same rotate around the common longitudinal axis, so that the individual heat exchanger 1 during one half of the rotation through the cooling medium and during the other half of the rotation are passed through the heating medium.
21. 21. Heat engine according to item 20 wherein the heat exchanger 1 are formed as a radiation absorber flat and have the shape of a disk segment and are aligned in a circle around the longitudinal axis of the working cylinder 2, that a disc is formed, wherein they are equipped with a radiation-absorbing surface and where they also are designed for cooling by convection, since the heat absorbed must be returned to the environment, wherein the heat exchanger 1, connecting pipes 4 and valves 5 are rigidly connected to the working cylinder 2 and rotate with the same about the common center axis.
22. 22. Heat engine according to item 21, wherein half of the heat exchanger 1 of the radiation are exposed, while the other half of the heat exchanger 1 is shaded.
23. 23. Heat engine according to item 21, wherein the shading is composed of different layers, and the radiation source facing side receives a reflective surface 23 such as mirrors, followed by an insulating layer 21 and on the back of a layer 24 follows with gray or dark surface, which absorbs the radiation of the heat exchanger 1 after shading and contributes to the dissipation of heat by convection.
24. 24. Heat engine according to item 21, wherein the heat exchanger 1, which are exposed to the radiation, are protected by a housing against loss by convection and radiation, and wherein the housing from the front of the radiation source side facing a glass 19, laterally and rear with a multi-layer cover 20 to 22 is executed, further wherein the inner, the heat transfer 1 facing layer 22 of this cover is corrugated and reflective, while the middle layer 21 is an insulating layer and the outward-facing layer 20 is a weatherproof layer.
25. 25. Heat engine according to item 21, wherein the heat exchanger 1 rotate about the center of the absorber ring, and each heat exchanger 1 while alternately the shading and housing happens, thereby alternately heated by the radiation and, during shading, by delivering the heat to the Environment to be cooled down again.
26. 26. A heat engine according to item 21, wherein the valves 5 are controlled so that alternately a cooled and heated heat exchanger 1 are connected to the working cylinder 2 to perform work by expansion or compression.
27. 27. Heat engine according to item 15 and item 21 with an odd number of heat exchangers 1, which are each connected alternately on one and the other side of the working cylinder 2.
28. 28. Heat engine with external heat source and at least 3 heat exchangers 1 with trapped working gas, which are alternately cooled and heated, the thermodynamic state changes in each heat exchanger 1 in connection with a working cylinder 2 and valve control 5 and 6 a) isochoric heat, b) isothermal expansion , c) isochoric heat removal and d) isothermal compression, and wherein the successive state changes: expansion and compression do not take place with a same working gas, and wherein after the expansion from a heated heat exchanger 1 into the working cylinder 2, a compression in another cooled heat exchanger 1 follows, and expansion and compression are triggered by means of valves between each heat exchanger 1 and cylinder 2 in response to the heating / cooling process.
29. 29. Heat engine with at least 3 or more closed heat exchangers 1, which perform work together with a common cylinder 2 and working piston 3, wherein in each heat exchanger 1 with working cylinder 2 and piston 3, a separate Stirling cycle, offset in time from the other heat exchanger 1, takes place ,
30. 30. Heat engine according to item 28, wherein the individual cycles are separated by the use of valves 5 from each other.
31. 31. Heat engine according to item 28, wherein the heat exchanger 1 forms a closed space in which there is a working substance, which is further designed for optimized heat exchange between working fluid and the environment, wherein a part of the heat exchanger 1 of the other part thermally, by an intermediate insulating insulating layer 25 is decoupled, one part is cooled and the other is heated, wherein a mechanical closing device 26 is installed between the cooled and heated part to divide the enclosed space of the heat exchanger 1, if necessary, into two spaces, wherein a connection opening in the wall of the heated part of the heat exchanger 1 exists through which the working fluid can flow in and out.
32. 32. Heat engine according to item 31 in which any number of heat exchangers 1 arranged in a star shape and symmetrical about a working cylinder 2 and are rigidly connected to it, wherein the connection openings of the heat exchanger 1 are connected to the working cylinder 2 via connections or connecting pipes 4, so an exchange the working gas between the two is possible, wherein one half of the heat exchanger 1 at the end face of the working cylinder 2, the other half are connected to the other, the front side opposite side, always alternately connected to a heat exchanger 1 at one of the next on the other side is, with valves 5 are in the connections 4 between the heat exchanger 1 and cylinder 2, which are opened and closed via a valve control 6 to point 2, while working cylinder 2, heat exchanger 1, connecting pipes 4 and valves about the longitudinal axis of the working cylinder 2 as Turn the rotor.
33. 33. The heat engine according to item 32, wherein a working gas is used whose boiling point is at a correspondingly selected pressure between the lower and upper temperature level, so that condensation takes place during the isochoric heat extraction and compression and evaporation during the isochoric heat supply and expansion.
34. 34. Heat engine with heat exchangers 1 according to item 32, wherein the cooled part of the heat exchanger 1 is on the outside while the heated part is on the inside to the working cylinder 2 out, the cooled part over half of the circumference cooled with a cooling medium and the heated part is heated over the opposite half of the circumference, while the rotor consisting of heat exchanger 1, working cylinder 2 with piston 3, connecting tubes 4 and 5 valves rotates.
35. 35. A heat engine according to item 32, wherein the valve 5 is opened and closed twice between each heat exchanger 1 and working cylinder 2 during one revolution of the rotor, once during the cooling process and once during the heating process.
36. 36. Heat engine according to item 32 in which the connections between the cooled and heated parts of the heat exchanger 1 are closed with a closing device 26 during the heating process.
37. 37. Heat engine according to items 31 to 36 in which by means of circulation of the heating and cooling medium, the internal heat of the material of the heated part of the heat exchanger 1 is used within a segment shortly after completion of the heating process to the cooled part of the heat exchanger 1 within a segment warm up shortly after completion of the cooling process to minimize condensation in the cooled part during heating of the heated part.
38. 38. Heat engine according to points 31 to 37, but without working cylinder 2 and piston 3, wherein the valves 5 of all heat exchangers 1 are driven by a single valve control 6, the heat exchangers 1 are connected when opening their associated valves 5 with a rotary engine, which uses the pressure difference between two pressure planes of a gas to perform work, wherein the connection in which the expansion takes place with the high pressure side and the connection in which the compression take place is connected to the low pressure side of the rotary engine, wherein part of the rotational energy of the rotary engine via a Transmission can be used as a drive of this heat engine.
39. 39. Heat engine according to items 31 to 37, wherein the heated parts of the heat exchanger 1 are formed as a radiation absorber, wherein the heated parts of the heat exchanger 1 are flat and have the shape of a disk segment, and annularly aligned around a center that a disc formed is equipped with a radiation-absorbing surface, these radiation absorbers are protected against losses by convection and radiation by means of suitable measures according to claim 24.
40. 40. Heat engine according to the items 31 to 36 with at least three or more closed heat exchangers 1, 3 work together with a common cylinder 2 and working piston, in each heat exchanger 1 with working cylinder 2 and 3 working piston own Stirlingkreisprozess, combined with a Clausius -Rankine-like cycle process, offset in time compared to the other heat exchangers 1, takes place.
41. 41. The heat engine according to points 31 to 36 whose operation is based on the following state changes in a cyclic process: 1. isochoric heat extraction, 2. isobaric liquefaction, 3. isothermal compression, 4. isochoric heat supply, 5. isobaric evaporation and 6. isothermal expansion.
42. 42. Power plant with heat extraction in which any number of heat engines A according to the above points are connected in series, wherein the heating medium 30, which consists of combustion gases 30 of a combustion process, the individual heat engines A cascade flows through successively, the temperature of the heating medium 30 during Flowing through the heat exchanger 1 of the heat engines to A1 decreases and wherein the cooling medium 22, which consists of ambient air or other air, the same heat engines A1 to An flows through in the opposite direction and in the reverse cascade, the cooling medium temperature when flowing through the heat exchanger 1 of the heat engine A. increases, with a temperature difference between the heating and cooling medium is more or less maintained and each heat engine A performs work and generated by them electrical power, the cooling medium na Ch leakage from the last heat engine A of the cascade is used as combustion air 30 in a combustion process and wherein the heating medium 30 after exiting the last heat engine An is used in the cascade for heating purposes or other heat consumers.
43. 43. Combined heat and power plant, according to point 42, but without a combustion process using waste heat from other processes.
44. 44. Combined heat and power plant according to item 42, in which different variants of the heat engine A described under points 1 to 41 are used.
45. 45. power plant with heat extraction in which the power with any number, the above and in the FIGS. 1 to 18 shown, with the heat engines A are connected in series and are flowed through with the cooling medium 22 and heating medium 30 in the countercurrent principle, wherein the heated cooling medium 22 is used after exiting the last heat engine as combustion air, and wherein from the in the Opposite direction last heat engine A exiting heating medium 30 can be used for heating purposes or other heat consumers.

Claims (11)

Heat process in which, in a cycle, four changes in state of an entrapped agent occur between two temperature levels in the following order: isochoric heat, isothermal expansion, isochoric heat dissipation, isothermal compression. Heat process in which, in a cycle, four changes in state of an entrapped agent occur between two temperature levels in the following order: isochoric heat, isotropic expansion, isochoric heat dissipation, isothermal compression. A heating process according to claim 1 or 2, further comprising an isobaric evaporation of the working material after the isochoric heat supply; and
after isochoric heat removal has an isobaric liquefaction of the working material. Heat process according to claim 3, wherein after the isobaric liquefaction, the working fluid is conveyed by a pump or by valves lying one behind the other. A heating process according to claim 1, wherein the isothermal expansion takes place in a working cylinder. A heating process according to claim 2, wherein the isotropic expansion takes place in a rotary engine. A heating process comprising simultaneously and staggered carrying out a plurality of heating processes as claimed in any one of claims 1 to 6, wherein the total working fluid is divided among the plurality of heating processes A heating process according to claim 7, wherein part of the total agent involved in a first heat process is transferred to a second heat process during the course of the first heat process. A heat engine with an interior closed to the outside, in which a total amount of working substance is contained, wherein in the heat engine, a plurality of heat processes according to one of claims 1 to 6 simultaneously and temporally offset from each other. Heat engine according to claim 9, wherein in the plurality of heating processes each part of the total agent is involved in a heat process. Heat engine according to claim 10, wherein the part of the total working substance, which is involved in a first heat process, is transferred during the course of the first heat process in a second heat process.

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