EP1841964A2

EP1841964A2 - Power plant featuring thermal decoupling

Info

Publication number: EP1841964A2
Application number: EP06703820A
Authority: EP
Inventors: Jürgen K. Misselhorn
Original assignee: Misselhorn Juergen K
Current assignee: Maschinenwerk Misselhorn MWM GmbH
Priority date: 2005-01-27
Filing date: 2006-01-27
Publication date: 2007-10-10
Anticipated expiration: 2026-01-27
Also published as: EP2299097A3; US20090000294A1; ATE479833T1; DE102005013287B3; JP2008528863A; WO2006079551A3; EP2299097A2; WO2006079551A2; EP1841964B1; DE502006007773D1; US7823381B2

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

Power plant with heat extraction

Technical area

In this invention is a power unit with heat extraction, in which several of the heat engines described below, as described below and with reference to the figures 1-18, are used in series behind each other to 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 relationship to use.

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 process 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 widely used heat engines Diesel and petrol engines are used in road, ship and air transport 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. NEN. 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. These developments also include the Organic Rankine Cycle (ORC), which uses organic compounds as the working substance instead of water and steam, and whose vaporization temperatures and vapor pressures allow it to operate at low temperatures. The ORC plants can also be used to convert regenerable energy, such as geothermal heat from geothermal sources.

In order to save fossil fuels, the Stirling engine is being experimented to a greater extent, as it is immaterial in this heat engine which fuel is used. 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 changes of state: compression at constant temperature (isotherm), heat supply at constant volume (isochore), expansion at constant temperature (isotherm) and heat removal at constant volume (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 back to the high pressure stage by means of pumps (inert). Here the process starts all over again.

The Clausius Rankine process consists of 2 isobars and 2 isentropes. Reference may be made to the prior art to the documents US 4,138,847 "Heat Recursive Engine" and DE 26 49 941 A1 "Stirling engine and method for operating the same", from which a heat engine with heat exchangers is known, wherein a working gas in each case an isochoric heat. and heat dissipation, as well as an isothermal expansion and compression as a state change between two temperature levels performed. The invention is based on the object to use the heat generated in many processes waste heat through a better utilization of isochori- see changes in state, 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 (see Figs. 16 to 18 in the drawing). In order to make it possible for vaporization and liquefaction to take place, an agent is selected whose boiling point is at a correspondingly selected pressure between the two temperature levels required for the operation of the heat engine.

The heat exchangers used (closed container with large heat transfer surface) are divided into two parts. The two halves are connected together by means of an insulating layer in such a way that the heat flow through their sheath is minimized 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 changes in the state 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 freewheeling piston (i.e., the piston is not connected to a crankshaft or the like via a connecting rod), heat exchangers can 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 taken place 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 are in the following order (see Fig. 17, P-v diagram or Fig. 18, t-s 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 working cylinder and

Heat exchanger opens and further vapor of the working fluid flows, due to the compression, in the heat exchanger on, partly by the

Low 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. FIGS. 13A, 13B and 13C schematically illustrate this sequence of the various processes and their relationship to one another.

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

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

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 via the heat exchangers is then available for heating purposes in district heating or other applications.

In Organic Rankine cycle plants, part of the heat that is generated from combustion processes is diverted into a thermal oil cycle, which in turn evaporates the organic agent in the Organic Rankine Cycle plants, there in a Clausius Rankine Cycle a turbine and power generator to power. The heat generated during the condensation of the working substance is used to heat the heating water Return used or delivered 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 combined heat and power plant can be operated with full load throughout the year because electricity or heat, or both, can be generated together with almost the same efficiency. This achieves a much higher level of annual impact and efficiency. Electricity can also be coupled out of accumulating process waste heat with this invention.

Short description of the drawing

1 shows a schematic representation of the basic module of the heat engine, in which the essential components and their relationship to each other are shown in order to illustrate the realization of the Stirling cycle. Fig. 2 details of the valve control 5 and 6th

Fig. 3 shows 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 shows 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 is a schematic representation as in Fig. 5, with representation of the media flow, which simultaneously flows through opposite heat transfer medium 1.

Fig. 7 is a schematic representation in which at certain heat exchangers 1 several modules consisting of connecting pipes 4, valves 5, working cylinder 2 and working piston 3 are connected.

Fig. 8 is 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 identified.

9A "Symbol description" and the associated FIG. 9B "Representation of clock 1 to clock 4" and FIG. 9C "Representation of clock 5 to clock 6". A representation of the process sequence on the basis of FIG. 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 is a schematic model of the basic module in an embodiment in which each 3 pieces heat exchanger 1 are connected to both sides of the working cylinder 2. Also in this model, 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. The heating and cooling sections of

Heat exchanger 1 are reported.

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

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

FIG. 13A "Symbol description" and the associated FIG. 13B "Representation of clock 1 to clock 4" and 13C "Representation of clock 5 to clock 7" a representation of the first 7 clocks of 10 clocks of the process flow based on that shown in Fig. 6 Model, however, each with 5 heat exchangers 1 on each side of the working cylinder 2.

14A "Symbol Description" and the associated FIG. 14B "Representation of clock 1 to clock 4" and 14C "Representation of clock 5 to clock 7" a schematic representation of the process flow, in which all the heat exchanger 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 is 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 CCI ₂ Fb, Frigen R12 as working substance.

Fig. 17 P-v diagram with respect to shown in Fig. 16 P-h diagram.

Fig. 18 t-s diagram based on in Fig. 16 P-h diagram shown.

Fig. 19 possible construction of a thermal power plant according to the invention, shown schematically.

Fig. 20 schematically described below in detail and shown in Figures 1 to 18 heat engine

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 "Stirlinq" 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.

The four state changes of the working gas are:

1. Heat supply at constant volume (Isochore) - valve 5 is closed.

2. Expansion at constant temperature (isotherm) (with heat input) - Valve 5 is open.

3. Heat extraction at constant volume (Isochore) - valve 5 is closed.

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 Transmitters 1, a separate cycle process instead. The individual Stirling cycle processes are coordinated with one another in such a way that, following isothermal expansion from a heat exchanger 1, isothermal compression of another heat exchanger 1 follows in the common working cylinder 2. 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 e- lectric 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 in Fig. 1, 2 and 8 is shown.

Essentially, the illustrated heat engine consists of: 1. Heat exchangers 1A, 1B and 1C, which are arranged in the shape of a star in the form of a rotor around a working cylinder 2 and rotate with it about its longitudinal axis. The heat exchangers 1A, 1B, 1C, etc. are referenced 1 in their entirety. As a result of the rotational movement, the heat exchangers 1 are each rotated by one half of the cooling medium flow (cooling section) and half by the heating medium. Current (heating section) out, 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 in one

Pipe surrounding the heat exchanger 1 on the outside and so forms an outer shell 13 (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. In a working cylinder 2, a piston 3 can move freely back and forth. For 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. A piston 3 free running 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. 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. 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 Ven- tile 5, but not their design, 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. A valve control 6 is provided for opening and closing the valves 5, at the right moment. The valve controller 6 may be mechanical (e.g., with a camshaft) 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. 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. 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. 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. A circulating air blower 10 or a circulating pump 10, which 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) is used. 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. By this regeneration process is more heat from the heating medium for heating the working gas to

Available.

11. Umlenkleitungen 11 to the heating / cooling medium of the heated heat transfer 1 to the cooled heat exchanger 1 and from there to the blower / pump 10 and back to the heated heat transferors

1, (see Fig. 11)

12. An isolated separation, which is located between the hot and the cold area (see Fig. 12), and which is formed like a tube to separate the heating medium from the cooling medium within the rotor.

13. An outer shell 13 around the heat exchanger 1, as part of the channels with which the heating / cooling medium is deflected to the heat exchanger 1, the heat exchanger 1 wrapped. Together with the inner sleeve

Ie14 and the separator 15, the outer shell 13 forms a channel around each heat exchanger. 1 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.

The separating webs 15 are delimitations between the individual heat exchangers 1. Together with the inner shell 14 and outer shell 13, they guide the heating / cooling medium during the rotation around the respective heat transfer medium 1.

Description of the process flow at the basic module:

The process flow is shown using a model with warm air as the energy source. This model is shown schematically in FIG. 8. The process flow is shown schematically in FIGS. 9A, 9B and 9C.

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 ° in each case. 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 exchangers 1 move alternately in a region through which heating or cooling medium flows, designated in FIG. 8 as a 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 sequence in the individual heat exchangers 1 runs as shown schematically in FIGS. 9A to 9C.

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 5B opens, which connects the air space in the working cylinder 2 with that of the heat exchanger 1B. This was previously circulated 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 the valve 5B is opened, the air from the working cylinder 2 compresses into the heat exchanger 1B and the piston 3 moves back to the valve 5 due to the pressure difference. During this compression process, the heat exchanger 1B still constantly flows through cooling medium and into the working gas heat is extracted from the compression, it is an isothermal compression. Heat exchanger 1A is already partially traversed by cold air at this time.

Cycle 3: 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 heat exchanger 1 C 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, heat supplied at constant volume in the heat exchanger 1B has an overpressure generated, 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 completion of cycle 6, the process is repeated from clock 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. 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, wherein the

Working cylinder 2 is made of a non-metallic material (glass, ceramic, plastic or the like). To the working cylinder 2 is a

Coil 8 is laid with wire windings for power generation.

The freely movable piston 3 is magnetized by permanent magnets 7, o- means of 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, one-sided loading of the piston 3 by the working gas can occur 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 FIGS. 5 and 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. In this case, the sequence of valves 5 on the two sides of the working piston 3 is matched to one another such that an expansion takes place simultaneously on one side of the piston 3 and a compression on the other side.

FIG. 13 shows the process sequence for such a double unit, 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 Arbeitszy- Linders 2, are located directly behind those that are connected to the front, so that the heating / cooling medium after passing the heat exchanger 1 of the front side, those on the back also happened. In this case, the heating and cooling medium is always guided simultaneously through the directly successive heat exchanger 1. (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 exchangers 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. As is apparent from Fig. 14, the valves 5 will always connect heat exchanger 1 with different states of the working gas with the working cylinder 2. The process flow is as shown in FIG. 14.

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

The heat exchanger 1 itself, the actual envelope of the working gas, alternately heat up and cool down, requires a considerably higher energy expenditure than that which is required to heat the working gas or to cool it. 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 simultaneously cooled with the cooled by the cooled heat exchangers 1, air itself.

The regenerator consists of a fan for gaseous heating / cooling media, or a pump 10 for liquid media and Umlenkka- channels or tubes 11, the medium from one segment of the rotor directly after the heating line, directly to another segment of the rotor after the cooling section and back again.

Seventh Variant of the Basic Module with Radiation 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 in order to perform work by expansion or compression.

Eighth variant of the basic module with Strahlungsenerqie as primary energy (See Fig. 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 illustrated in FIG. 14.

Ninth variant of the basic module The Clausius-Rankine cycle

Due to 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, which is a multiple of the heat capacity of the working medium, is generated. used. Condensing or vaporizing the working substance on the heat exchanger wall requires a considerably greater flow of energy than heating or cooling the working substance. It is possible, the condensate, which has a much smaller specific volume than the gaseous aggregate to promote from the cold zone to the warm. (Like the Rankine process, 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 into the already described Stirling cycle, some changes have to be made to the heat exchangers 1.

Each individual heat exchanger 1 is divided into two halves (see Fig. 12). The two halves are connected in the middle with an intermediate 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 s.g. 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 transfer 1 around as inside (between heat exchanger 1 and cylinder 2) are also concentrically arranged tubes (13 and 14), which form together with the separation between the heat exchangers 1, two annular channels in which each of the "cooled" or "heated" Part of the heat transmitter 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, with a surface whose temperature is below the dew point of the working substance, condense on this surface until the pressure within the closed heat exchanger 1 corresponds to the vapor pressure of the working substance. In the present case, the entire envelope of the 'cooled' warehousing Half of meüberträger have this temperature, because the cooling medium of this half of the heat exchanger 1 constantly extracts the heat of condensation.

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. The connection opening (s) between heated and cooled half are closed mechanically.

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 is replaced by fan 10 or pump 10. This allows the heat from the heated part of the heat transfer tube to be used to heat the cooled heat transfer tube 16. Depending on the convenience of this regeneration, the amount of condensing agent can be reduced.

3. A combination of the two aforementioned methods. Taking into account the design features described, the Clausius-Rankine cyclic process can now be explained. See FIG. 12 "Design features of the" Stirling-Clausius-Rankine heat engine "and FIGS. 16 to 18" Thermodynamic comparison processes of the Stirling-Clausius-Rankine heat engine ". The working material used for this example was dichlorodifluoromethane (CbFbCH), Frigen R12. 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 area of the heat exchanger 1. Due to the rotation, the cooled above the heated half moves. 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.

In order to illustrate the sequence of the cycle process, the isochoric cooling process is initially started, with reference to FIG. 12 of the drawing. 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, the heat exchanger 1, through the cooling medium, constantly withdrawn heat. So there is an isothermal compression. (Fig. 17 point 3 to point 4) This change in state 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, heat is constantly supplied to the heat exchanger 1 (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 closed mechanically. 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 same 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 heat is continuously supplied to the heat exchanger 1, from the heating medium. There is first a continuation of the evaporation process after an isothermal expansion instead. This state change belongs both to the previously described Stirling cycle and to 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. Eg for free convection, water cooling, heat exchangers for gaseous or liquid cooling media, etc. 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 against convective 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 rotation 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 cycle. Clausius-Rankine-Keisprozess 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 majority 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 plants are used, can also be useful in this heat engine in the same way by Aggregateustandsänder- ments useful. This heat engine differs from the conventional ORC system in that condensation and vaporization 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 shown in FIG. 19 of the drawing. Here, a suitable number of heat engines A, e.g. A1, A2, A3, .... An, arranged in series. The air 22 provided for combustion is passed through the cooled part of the individual heat engines A1, A2, A3,... An one after another and, after leaving the last heat engine, fed 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 approximately shown in the diagram of Fig. 21 of the drawings. 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. It will be 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 from the heat exchangers 1, increases.

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 by a temperature control loop, consisting of a temperature sensor 31, controller and servo motor 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 ⁰ 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 uses. 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 insufficient for the heat demand, then the second-to-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.

Particularly in the first heat engines A through which the hot gases pass, the vapor pressure of the working substance located there can rise so high at too high a temperature that it can damage the construction of the heat exchangers 1, so when the heat engine A stops, the hot gases will not pass through the heat exchangers led the heat engine but by Umschaltklappen with drive 34 at this vor- and directed directly into the heat exchanger 35. There is Umschaltklappen drive 34 before each heat engine A ₁ with which 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 combined heat and power 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, are used.

Claims

claims

1. Heat engine, by four state changes, namely

1) isochoric heat supply, 2) isothermal expansion,

3) isochoric heat removal,

4) isothermal compression of an enclosed working gas between two temperature planes, and comprising: at least three heat exchangers (1A, 1B and 1C) each having only one connection, in particular a connecting tube (4A, 4B, and 4C) to a working cylinder (2) and wherein the connections are each equipped with a valve (5A, 5B or 5C) and wherein the heat exchangers (1A, 1B and 1C) are alternately flowed around by a heating medium and cooling medium.

2. Heat engine according to claim 1, wherein the heat exchanger (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 free movable piston (3), which performs work by the expansion and compression of the working gas.

3. Heat engine according to claims 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 at sustained heat input into the working cylinder (2) can expand and perform work there, after completion of the expansion process same valve (5A) closes again and subsequently the first heat exchanger (1A) with the valve closed (5A) from the external source to the lower

Temperature level is cooled.

4. Heat engine according to claims 1 to 3 wherein the working gas is cooled in a different second heat exchanger (1B) offset in time relative to the first heat exchanger to the lower temperature level and compressed after opening this heat exchanger (1B) associated 2.Ventils (5B) is, with simultaneous heat dissipation, wherein the previously expanded working gas flows from the working cylinder (2) in the second heat exchanger (1B), and in turn doing work on the working piston (3), wherein at the conclusion of the compression process in the heat exchanger (1B) that this heat transfer carrier (1 B) associated second valve (5B) closes, and with closed second valve (5B) of the heat exchanger (1B) is heated in the further course to the upper temperature level.

5. A heat engine according to claims 1 to 4, wherein the working gas in a further third heat exchanger (1C) is raised in time from the external source to the upper temperature level and after opening the heat exchanger (1C) associated third valve (5C), expanded at simultaneous supply of heat, wherein the previously compressed working gas from the third heat exchanger (1C) in the working cylinder (2) flows and performs work and then the third heat exchanger (1C) is cooled with the third closed valve (5C) from the external source to the lower temperature level ,

6. Heat engine according to claims 1-5, wherein the ein¬ Ssen 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) is compressed and heat is dissipated by the first heat exchanger (1A) during the compression process, wherein work is performed in the working cylinder (2) by the compression, and after

Closing of the first valve (5A), the first heat exchanger (1A) is reheated, in the same way when opening the corresponding second valve (5B), from the now warmed up second heat exchanger (1B) an expansion of the working gas followed by a compression in the meantime cooled third heat exchanger (1C) takes place.

7. Heat engine according to claim 1, wherein for warming and cooling of the working medium for the particular heating or cooling medium suitable heat exchanger (1) are used.

8. A heat engine according to claims 1 to 7, wherein the valves (5A, 5B and 5C) via a camshaft (6), electric drive or similar valve control (6) are opened and closed in a certain order and a certain rhythm.

9. A heat engine according to any one of claims 2 to 8, wherein, however, for transmitting the work, the working piston (3) with permanent or energized magnet (7) is magnetized and the working cylinder (2) in such a manner with an electric coil (8) is enclosed, that by the movements of the working piston (3) electricity is generated, ie the work of the piston (3) is converted directly into electricity.

10. Heat engine according to claims 1 to 9, wherein a pressure equalization tank (9) on the working cylinder (2) is connected, on the opposite side to terminals of the working cylinder.

11. Heat engine according to claim 10, wherein the surge tank (9) is filled with the same working gas as the heat exchanger (1).

12. Heat engine according to claim 10, wherein the pressure in the expansion tank (9) is adapted to the static pressure in the heat exchangers (1A, 1B, 1 C).

13. A heat engine according to claim 10, wherein the heat engine at each suitable pressure of the working gas, regardless of the atmospheric pressure, can be operated.

14. Heat engine according to claim 1, with an arbitrary odd number of heat exchangers, which are connected with connecting tubes (4) together with valves (5) to the same working cylinder (2).

15. Heat engine according to one or more of claims 1 to 14, wherein with the same odd number of heat exchangers (1),

Valves (5) and connecting pipes (4) are connected to 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 one side and one at the same time

Expansion on the other side takes place.

16. A heat engine according to claim 15, with an arbitrary odd number of heat exchangers (1), compounds in particular connecting tubes (4) and associated valves (5), at both

Pages are connected to the same cylinder (2).

17. Heat engine according to claim 1, wherein, however, the heating and cooling medium flows through the, the working cylinder (2) exactly opposite, the heat exchanger (1) simultaneously.

18. Heat engine according to one of claims 1 to 16, wherein an arrangement of a plurality of working cylinders (2), piston (3), connections (4), valves (5) and valve controls (6), all of which are parallel to any number of common Heat exchanger (1) are connected.

19. A heat engine according to claim 15, wherein a working gas is used, the boiling point is at a correspondingly selected pressure between the lower and upper temperature level, so that a condensation during isochoric heat extraction and compression and evaporation during the isochoric heat supply and expansion, takes place.

20. A heat engine according to claim 15, wherein 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) alternately on both sides of the working cylinder (2) are connected wherein the heat exchanger (1 ) are rigidly connected to the working cylinder (2) and rotate with the same about 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 through the heating medium.

21. Heat engine according to claim (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 ring around the longitudinal axis of the working cylinder (2), that a disc is formed, wherein they are absorbed by a radiation Where they are also designed for cooling by convection, since the absorbed heat must be returned to the environment, wherein the heat exchanger (1), connecting pipes (4) and valves (5) rigidly connected to the working cylinder (2) are connected and rotate with the same about the common center axis.

22 heat engine according to claim 21, wherein the half of the heat transfer (1) of the radiation are exposed, while the other

Half of the heat exchanger (1) is shaded.

23 heat engine according to claim 21, wherein the shading is constructed of different layers, and the, the radiation source facing side receives a reflective surface (23) (eg mirror), wherein thereafter an insulating layer (21) and on the back of a ne (24) follows with gray or dark surface, which the

Radiation of the heat exchanger (1) absorbed after shading and contributes to the dissipation of heat by convection.

24. Heat engine according to claim 21, wherein the heat exchanger (1), which are exposed to the radiation, through an enclosure before

Loss are protected by convection and radiation, and wherein the housing from the front (the radiation source facing side) with a glass (19), laterally and in the back with a multi-layer cover (20 to 22) is executed, in which further the inner, the heat Transducers 1 facing layer (22) of this cover is corrugated and reflective, while the middle (21) layer is an insulating layer and the outwardly facing layer (20) is a weatherproof layer.

25. Heat engine according to claim 21, wherein the heat exchanger (1) rotate about the center of the absorber ring, and each heat exchanger (1) alternately passes the shading and enclosure, thereby alternately heated by the radiation and, during shading, by delivery the heat to the environment, to be cooled again.

A heat engine according to claim 21, wherein the valves (5) are controlled to alternately connect a cooled and heated heat exchanger (1) to the power cylinder (2) to perform work by expansion or compression.

27. Heat engine according to claim 15 and claim 21, with an odd number of heat exchangers 1, each alternately on the one and the other side of the working cylinder (2) are connected.

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 is) isochoric heat supply, 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 expansion from a heated heat exchanger (1 ) in the working cylinder (2) is followed by a compression in another cooled heat exchanger (1), and expansion and compression means

Valves between individual heat exchangers (1) and working cylinder (2) are triggered depending on the heating / cooling process.

29. Heat engine with at least 3 or more closed heat transfer 1, the work together with a common cylinder (2) and working piston (3), wherein in each heat exchanger (1) with working cylinder (2) and working piston (3), a own Stirlingkreisprozess, offset in time compared to the other heat exchanger, (1) takes place.

30. Heat engine according to claim 28, wherein the individual cycle processes by the use of valves (5) are separated from each other.

31. Heat engine according to claim 28, in which the heat exchanger (1) forms a closed space in which a working substance is, which is further designed for an optimized heat exchange between the working substance and the environment, wherein a part of the heat Transducer (1) is thermally decoupled from the other part by an insulating layer (25) built in between, one part cooled and the other heated, with a mechanical closing device (26) installed between the cooled and heated part to enclose the enclosed one Divide space of the heat exchanger (1), if necessary, into two spaces, with 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. A heat engine according to claim 31, in which any number of heat exchangers (1) are arranged in a star shape and symmetrically about a working cylinder (2) and rigidly connected to it, wherein the connection openings of the heat exchangers (1) to the working cylinder (2) via connections or Connecting pipes (4) are connected so that an exchange of the working gas between the two is possible, wherein one half of the heat exchanger (1) on the front side of the working cylinder (2), the other half are connected to the other, the front side opposite side, wherein always alternately a heat exchanger (1) is connected to one of the next on the other side, wherein valves (5) in the connections (4) between the heat exchanger (1) and working cylinder (2) are located, which via a valve control (6) can be opened and closed according to claim 2, while working cylinder (2) heat exchanger, (1) connecting pipes (4) and Ven Tile around the longitudinal axis of the working cylinder (2) rotate as a rotor.

33. A heat engine according to claim 32, 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 isochoric heat extraction and compression and evaporation takes place during the isochoric heat supply and expansion.

34. Heat engine with heat exchangers (1) according to claim 32, wherein the cooled part of the heat exchanger (1) is on the outside while the heated part on the inside (to the working cylinder (2) out), wherein the cooled part over half cooled with a cooling medium and heated the heated part 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 valves (5 )).

35. A heat engine according to claim 32, wherein the valve (5) between each heat exchanger (1) and working cylinder (2) during a revolution of the rotor is opened and closed twice, once during the cooling process and once during the heating process.

36. A heat engine according to claim 32, wherein the connections between the cooled and heated parts of the heat exchanger (1), with a closing device (26) during the heating process, are closed.

37. A heat engine according to claims 31 to 36, wherein 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), within a segment shortly after completion of the heating process is used to the cooled Heat part of the heat exchanger (1), within a segment shortly after completion of the cooling process, to minimize condensation in the cooled part during heating of the heated part.

38. Heat engine, according to claims 31 to 37, but without working cylinder (2) and piston (3), wherein the valves (5) of all heat exchangers (1) by a single valve control (6) are driven, wherein the heat exchanger (1) during Opening their assigned venues Tile (5) are connected to a rotary engine, which uses the pressure difference between two pressure planes of a gas to do work, the connection in which the expansion takes place with the high pressure side and the connection in which the compression takes place connected to the low pressure side of the rotary engine wherein a part of the rotational energy of the rotary engine can be used via a transmission as a drive of this heat engine.

39. Heat engine, according to claims 31 to 37 wherein the heated parts of the heat exchanger (1) are designed as radiation absorbers, wherein the heated parts of the heat exchanger (1) are flat and have the shape of a disk segment, and aligned in a ring around a center that a disc is formed, wherein they are 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. The heat engine according to claims 31 to 36 with at least 3 o more closed heat exchangers 1, which perform work together with a common working cylinder (2) and working piston (3), wherein in each heat exchanger (1) with working cylinder (2) and working piston (3) a separate Stirling cycle, combined with a Clausius-Rankine similar cycle, with a time offset from the other heat exchangers (1) takes place.

41. The heat engine according to claims 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. Power plant with heat extraction in the any number of heat engines (A) according to the above description, which 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 successively flows through, wherein the temperature of the heating medium (30) when 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) in opposite Direction and in the reverse sequence flows through a cascade, wherein 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 after exiting the last heat engine (A) of the cascade as combustion air (30) in a combustion process is used 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 combined heat and power plant, according to claim 42, but without combustion process in which the waste heat from other processes is used.

44. Combined heat and power plant, according to claim 42, in which different variants of the heat engine (A) described in claims 1 to 41 are used.

45. A power plant with heat extraction, in which the power is generated with any number of heat engines (A) described above and shown in Figures 1 to 18 is shown. The heat engines (A) are connected in series and with the cooling medium (22) and heating medium (30) flows through in countercurrent principle. The warmed cooling medium (22) is used after exiting the last heat engine as combustion air. The heating medium (30) emerging from the last heat engine (A) in the opposite direction can continue to be used for heating purposes or other heat consumers.