DE19921366A1 - Arrangement for increasing energy productivity has system for converting heat into power with e.g. thermal power coupling, temporary heat storage, reverse heat transfer arrangements - Google Patents

Abstract

The arrangement has a system for converting heat into power, a working circuit-working medium-heat and power feed-transfer-extraction-circuit coupling, one or more large vol. containers with temporary storage thermal bearer liquid fillings, heat exchangers, control and transport connections, controllers, a switching center, expansion containers, a thermal bearer, thermal power and heat pump circuit, pump-compressor-engine-force transfer associations, etc. An Independent claim is also included for a method of increasing energy productivity.

Description

The invention relates to a method and devices for Execution of the method according to the preamble of Claim 1.

A known practice is that energy transfer, which enables heat to be dissipated at a high temperature a high temperature transfer point to the heat absorber part of a heat and power working group of a known type, e.g. B. Stirling / engine circuit, and transferred from the Heat supply caused expansion of the working fluid, in and via this, a heat engine (motor) is applied, in the following the working fluid in the heat emitting Part of the W-K working group transported, cooled, shrunk and with a low temperature in and over again heat-absorbing expansion circle with heat absorption the high temperature source, in the intended temperature level in Circulation fed continuously and carried out work-performing, the W-K relaxation circuit after effective use wear from this into the environment and / or partially to the building Delivered heat supply and the circuit return heat continuously returning and feeding in heat increasing again and at times a share in heat exchanging connection with a heat storage mass intermediate in a heat storage saves and is retrieved when needed.  

Disadvantage when generating electricity with partial heat loss s for a heating supply is that the essential An some thermal energy without further work as Low temperature heat is lost.

Disadvantages with W-K coupling, i. H. even when forwarding the Heat for heating supply is that the efficiency between the amount of energy supplied and released is lower, than this would be possible. Another disadvantage is that Wär meenergy from another source, e.g. B. Low temperature heat, solar use and waste heat generated by heat pumps or as Waste heat from a medium / low temperature range for the Heating supply supplied, via heat and power coupling to Workflow with effective leadership not effective assigned and cached heat from a heat store Effective with insufficient efficiency when called up can be used.

The object of the invention is to implement methods and of the method to create devices that enable Energy available from a temporary oversupply stands, e.g. B. via electricity-generating solar cells or wind power and other electricity generation processes, converted into heat entered a high temperature heat storage and if necessary with high efficiency effective for power generation and Heating supply is accessed, taking into account of waste heat recovery and heat supply z. B. about Environmental heat use. In addition, should generate heat a boiler resulting from a combustion process released heat in this, working via W-K coupling samer from high temperature level to low temperature level in Combination with energy productivity increase transmission processes coupled, can be used, as well as via controlled  Compressor and expansion processes, in association with the Heat-power cycles with temperature-raising ver sealing and lowering relaxation partial circle guides, controls the W-K cycle increasing, heat extracted and via compression processes with heat level lifting processes, Some of the heat is returned to work-related use Low temperature transmissions gained in coupled Circuits with different temperature and pressure levels managed, with different working medium assignment in the W-K conversion, expansion and shrinking processes, partially effective with the use of gravity / gravity Energy can be used to increase productivity.

The task is accomplished through procedures with the characteristics of the To Proof 1 and mentioned for the execution of the method Devices solved.

Advantages of the invention are that high-temperature, as well as with tel and low-temperature heat, such as one or more heat-emitting source, in a pressurized gas and in gaseous-liquid-gaseous working medium leading thermal power and heat transfer medium working groups used in a work-forwarding manner Forwarding of heat via heat exchangers and / or via tank walls and in and above liquid, preferably water, in appropriate heat-conducting devices via controlled gravitational processes, with effective circuit management with high pressure maintenance and metered pressure reduction and heat emission, in the coupled circuit guides with heat recovery and further processes, efficiency is increasing. Heat supplied from the outside is thus used several times to work, passed through the circuit, partly with the corresponding heating and hot water supply temperature level, temporarily stored in the water of a large-volume container chamber 5 , ( 4 ) and is available on demand via heat transfer circuits for building supply. In addition, the combined heat and power enables energy in the form of heat with a wide variety of heat levels from high to low temperature to be used to generate electrical energy.

Via the overall network of heat transfer and W-K sub-circles and Accessory controlled guided, with gravitational use in water chamber areas, with heat and power conductive processes, will not only high temperature heat multiple times for heat-power conversion processes, energy used to increase productivity, but also medium-temperature and low-temperature heat, with over Compressor and expansion processes in assigned, one Pressurized gas as the working medium leading working circuit, heat fed in or out, partly from the coupled circuits Efficiency derived derived, sometimes with higher Temperature level fed back into the circuits, as well as and environmental heat can be fed in, so that Cogeneration, programmed stored, as required derived and more extensive than before the use of environmental energy becomes possible.

Advantages of the invention are furthermore that required before directions for executing the procedures are designed in this way can that these according to the respective installation locations adapted, largely prefabricated, can be set up nen. In addition, the different temperature ranges be arranged so that the for high pressure areas required materials only for parts of the system be required, high temperature heat not just for yourself are isolated, but also by encasing low temperature areas, the inevitable heat loss in the context of Circulatory systems are immaterial. Insulation, Control circuit devices and thermal power conversion as well as compressor devices or W-K machine and heat pumps,  Heat exchangers are known, a variant of heat exchangers as well as heat to power conversion devices, however, is in partially shown variant. A warmth pump and thermal power conversion device is in special device design in a separate Patent application shown. Heat storage, solar, Control systems, pressure regulators, generators and others Accessories are available on the market.

It is also advantageous that the system is used aligned according to purpose, designed as required can.

A temperature level of approx. 180 ° C and more is assumed as the high-temperature designation,
the medium temperature designation is from approx. 100 ° C to approx. 180 ° C,
4 ° C to 99 ° C is assumed as the low-temperature designation, and in some cases minus ° C for heat pump pressure gas relaxation processes.

Example description

Embodiments of the invention are shown in the drawing and are described in more detail below.

Show it

Fig. 1 is a horizontal section through a shaft insulation and large container wall partially in the large container is arranged and partially externally assigned system device for energy productivity increase.

Heat engines with power transmission are assigned on the outside accessories, heat source compressors and feed pumps, medium Expansion and compressed gas storage tank with switching valve a working medium collecting container heat exchanger, circuit and control device, switching center and circuit Closing and / or line connection connections in and out the shaft or large-capacity container and these two classified Devices with three nested in encapsulated high-temperature water columns and steam chambers container with insulating walls and two low-temperature water columns and working medium chamber container with externally assigned Heat transfer fins, as well as a medium temperature water columns and working medium Chamber container with a steam chamber forming heat exchanger jacket with classified inside Heat exchanger fins, also a water-steam tank, a compressed gas storage tank, a compact heat exchanger as well as working medium and circuit leading lines and Lei connection in the further several in the water chamber area of the Open-plan container arranged heat exchanger chambers and pipe queued with pipe connections.

Fig. 2 is a vertical section through the open-plan container and in a modification to Fig. 1, by an arranged in this Before direction with three interlocked, self-contained high-temperature water columns and steam chamber container with insulating walls. In addition, by means of the medium-temperature water columns and working medium chamber container with the steam chamber heat exchanger border and arranged heat exchanger fins, and by a device of a low-temperature water column and working medium chamber container with heat transfer fins assigned to the outside on the upper area, as well as the compressed gas intermediate store and the interior fittings. Devices in the water columns and working medium or Dampfkammerbehäl ter with incoming and outgoing connections, as well as the heat exchanger pipe coils with line connections and in modification to Fig. 1, only the line connection connections to the compact heat exchanger and the water-steam container arranged outside in the open-top container area shown as well as the outside only the two feed pumps as well as line connections and working medium collecting tanks.

Fig. 3 shows a vertical section through a low-temperature large-volume container with assigned liquid filling, preferably water, with a modification to Fig. 2 in the large-volume container chamber shown in section several superimposed liquid or water columns and Ar beitsmedienkammern, as a closed tube - Containers with extended fins, pipe registers or container attachments as well as incoming and outgoing WK working medium, conductive connections as well as arranged heat exchangers in the two upper pipe containers and without arranged heat exchanger in the lower pipe container. In addition to Fig. 2, the lamellar tube register head portion of the tube container which is arranged in the upper open-space container chamber part, heat-accepting heat exchanger connection with the water filling, however, no steam chamber jacket with steam-heat transfer connection.

The outer tube container, the three nested ge encapsulated pipe container, also has heat accumulation in the head part Shear connection to the large-volume container chamber for water filling. In the working medium thermal power line routing in and out The three encapsulated tube containers are the connection of this to and from a compact heat exchanger, which is in bulk space container is shown classified, recognizable. in the schematic outline is outside view of the open plan container left "a heat transfer circuit with heat exchanger, circulation pump, as well as heat exchanger connections and pressure Partial gas circuit with compressor pump and expansion Container and engine connection with line connections se for W-K circuit guides and condensate feed, at Assignment of working medium "ammonia collecting container" ordered right outside of the open-plan container, with on Feed line routing, pump, switching valves, level contact sensor and heat exchanger assignments.

Fig. 4 in side view section, a compact heat exchanger from three nested, encapsulated tube containers, which each form three heat-insulated chambers, each with arranged pressure gas heat transfer pipe routing and in this associated heat exchange mass and heat exchanger surface area in the Area of the container chamber. When the pipeline of the heat transfer medium is closed and passed through the inner chamber area, it is subsequently routed through the middle and subsequently through the outer chamber area with a further conductive connection. As well as three different, separate supply and discharge thermal power steam working line routing, each in and out of one of the three chamber areas, in each of which a level tester with contact forwarding connection is assigned.

Fig. 5 in side view section in modification of Fig. 4, a pressure gas expansion tank and heat exchanger, from three nested tubular containers with insulated walls and to and from and through the expansion tank and WK working medium "ammonia" line in this, in the tube container chamber areas assigned heat exchanger solid body and heat exchanger area enlargement with closed working medium piping through and out of the inner chamber area in and through with empty to the outer chamber area and in and through this to the outside with a forwarding connection to the working medium condensate collecting tank. The expansion tank is further assigned a supply pressure gas line connection with chamber supply openings in the outer container chamber area near the bottom and flow opening from the outer to the middle chamber area in the head part and further opening in the floor area to the inner chamber and from this water to the outside pressure gas leading line to the compressor pump -Connection connection.

Fig. 6 in vertical section, a heat and pressure gas-Kraftmaschi nenkombination with several container chambers, each having a closed lower and upper chamber, where in the lower chambers in the lower half of the area preferably have a liquid water and the lower half of the chamber in the water area has a float with conductive accessories and loosely arranged float balls, so that the water surface is covered by the float mer and the floating balls and through this a chamber area for pressurized gas or gaseous heat-Ar beitsmedium z. B. Steam remains. Connecting lines to the thermal power medium steam as well as compressed gas supply and discharge lines with switching valve assignment as well as a circular line connection with flow power machine devices are assigned, likewise in the upper chamber areas piston engine and pump devices, which are partially mechanically coupled and force-transmitting-forwarding Connections to a compressor pump and other aggre garden and power conversion devices, not shown. Level tester contactors, circuits and heat exchangers as well as insulated walls and lines are assigned.

Fig. 7 In vertical section of a multi-walled outer wall, the shaft inside have a large-capacity container with classified accessories such as lines, heat exchangers, level testers and several pipe containers, z. B. as a compressed gas expansion tank, compact heat exchanger, tank chambers of an engine combination and water-oxygen extraction device are arranged, with a room with heat pump engine chamber upper area and accessories as well as safety fittings and pump and line connections are assigned to the large-capacity tank chamber. In the outside area indicated on the right-hand side solar collectors, including heating and water supply system connection with intermediate water storage, indicated below this a large-capacity container with thermal power cycle designation as arranged in Fig. 3, and top left, as arranged in Figs. 1 and 2 , including compressed gas thermal power heat transfer medium and heat pump circuit numbers, also schematic representation for heat sources, boilers and high-temperature heat storage, as well as line connections with control circuits and switch center.

Fig. 8 in a modification of Fig. 7 arranged in the open-plan container, arranged one above the other water columns and working medium chamber with working medium conducting connections-WK working circuits in a coupled connection with multi-way control devices and the gaseous working medium and liquid leading lower container chamber of an engine combination in a modification to Fig. 6 with cable routing from the bottom area of the container chamber to the piston and / or turbomachine and force-transmitting device assemblies, which are set up separately in a room, and are assigned to the engine combination.

In the upper area of the sketch Fig. 1 is indicated Darge represents a switching center 1 , including a shaft container outer wall 2 with wall insulation 3 , adjacent to this the outer wall of the low-temperature large-capacity container 4 with low-temperature chamber area 5 , arranged in this two high-temperature water columns and steam chamber device 6 and 7 , each with three self-contained water columns and steam chamber containers 8 , 9 , 10 offset in cross-section. Each water column and steam chamber container is encapsulated and has insulated wall and thermal power circuit connections in and out of the chamber area, the WK working group assignment 11 to container 8 , WK working group 12 to container 9 , WK working circle 13 to container 10 however, divided into expansion section 14 and shrinking section 15 to the WK working group 11 and expansion section 16 and shrinking section 17 to the WK working group 12 and expansion section 18 and shrinking section 19 is assigned to the WK working group 13 , the water columns and steam chamber devices 6 and 7 , these are the same and have for each water column steam chamber a circular heat-power circuit with expansion and shrinkage circuit, the expansion expansion circuit from the water columns and steam chamber container to the compact heat exchanger 20 and in these and from these to the heat engine 21 leads. From this again to the water column and steam chamber container of the high temperature water columns and steam chamber device 6 or 7 , closing the circuit. The devices 6 and 7 have coupling te connection via compact heat exchanger and engine and each with the WK circuits 11 , 12 , 13th In the area of the engine 200 , heat exchanger 24 is assigned, which has a heat-transferring connection between compressed gas working circuit 25 and the steam-carrying WK circuits 11 , 12 , 13 . The working gas 25 carrying the compressed gas as the working medium has a work process subdivision into expansion subcircuit 26 and shrinking subcircuit 27 , and in a partial area heat pump cycle function, relaxation / compression subcircuit assignment. The compressed gas circuit is associated with connection into and out of a high-temperature heat source 30 , with the transition expansion circuit 27 and shrinkage circuit 26 being the intermediate heat engine 28 which has power output accessories 29 as a transition. From the heat engine is in the conduction path of the shrinkage subcircuit 26 the heat exchanger 24 in the following the compact heat exchanger 20 further via control and bypass device 31 on the one hand with the high-temperature water column and steam chamber device 6 , 7 and on the other hand with the heat exchangers 32 , 33 which are in the water Steam container 34 are arranged and the container has an outer wall insulation 35 . In the further line path of the compressed gas leading shrinkage circuit 27 are assigned heat exchangers 36 , 37 , in a heat boosting pipe 96 , which is open at the top and bottom, in the further line path 38 is assigned a compressed gas buffer 38 , in which the shrinkage circuit input has a backflow protection and the output connection for connection to the outside and in the further route 27 from the Druckgas-Zwischenenspei cherung connection with compressed gas engine 39 , from this via pressure regulator flow valve 40 , a partial circuit line management as a relaxation part in connection with the expansion tank 41 , with connecting compressed gas Supply and discharge connections and from the discharge connection via heat exchanger 42 and compressor pump 43 , as well as these associated and nachgeordne th heat exchanger 44 as a transition area from the heat pumps Ent voltage and compressor circuit in the compressed gas working circuit 25 a part Oil circuit routing transition to expansion sub-circuit 26 with heat absorption, circuit closing by the high-temperature heat source in the cycle to the heat engine. In the pressurized gas process is in the expansion tank 41, the heat exchanger device 45 , which is assigned to the working medium gaseous-liquid-gaseous in the shrinkage pitch 47 of the WK working group 46 is assigned. The shrinking pitch circuit 47 has from the heat exchanger 45 via a distributor connection to the low-temperature water column and working medium chamber container 49 likewise with 50 and on the other hand with the working medium in the liquid state receiving the collecting container 51 and from this with the feed pump 52 and feed line and valve 63 with the medium-temperature water columns and chamber tank 54 and via feed line branch 53 with the low-temperature water column and working medium chamber tank 99 , and 50 . Inputs and discharges are assigned to the chamber containers 49 , 50 , 54 , line paths lead the WK circuits, the container chamber 54 the expansion and shrinkage partial circuit 57 with valve assignment for flow control in the WK working group 55 . The WK working groups 58 and 59 are assigned to the low-temperature container chamber 49 and 50 , respectively. About the feed line 63 and associated backflow protection in this, the Ar beitsmediumleitung for working medium supply in the liquid state to the water column container chamber 54 is given, from this via shrinkage circuit 57 and flow control into the water column container chamber 49th In addition, a connecting line with switching valve 65 from container chamber 54 to container chamber 49 , likewise a connecting line with Schaltven valve 66 for the temporary pressure transfer control of medium temperature container 54 to the container chamber 49 or to the container chamber 50 , assigned in FIG. 1, at Fig. 2 is clearly arranged in the low-temperature large container 5 not 49 and 50 but only the water column and working medium chamber container 49 , this has a thermal region delimiting preferably thermopene insulating wall from the bottom to the upper quarter, from this is recognizable a heat exchanger wall 71 with La Mellen 72 , the water column is arranged in the insulated wall part, about this up to about the lamella arrangement of the working medium liquid area chamber part, and via this lamella assignment, the boiling area 72 transition from the working medium liquid-gaseous. Above the boiling range is the exhaust port 84 and an inflow opening 65, via line switching valve 65/66 and via the latter to the upper Be rich 49th The inflow opening 77 from the shrinkage pitch circuit 61 for working medium transfer into the WK working group 46 , loading container chamber 49 via the line into the container chamber or through the water assigned to the water column 6 in the chamber area is heat sensor 74 via the outflow opening 77 . Via line path 76 from the working medium chamber container 49 with the confluence in this and line path with outflow opening in the working medium collecting container 51 , the circular connection via the motor is provided between the expansion partial circuit 46 and the shrinking partial circuit 47 in the working group 46 and in the line path 57 via heat exchanger container 92 and subordinate Heat exchanger and switching valve 78 and line away into the water column container chamber 49 through the outflow opening 77 in this, the circular connection via the machine from the boiling area 97 in the medium-temperature water column and the working medium container chamber 54 and the working medium forwarding shrinkage part 61 to the water column container chamber area 49 is given .

The condensed working medium rises in the water column via the heat absorption from it to the water surface. The liquid working medium is arranged above the water surface, approx. From liquid level "level tester" and heat sensors 98 to 74 . In the container chamber area 54 , however, the same is in this from the liquid level and temperature sensor 81 to the liquid level sensor 82 , from this level the gaseous ar is assigned to the working medium area. In the line starting from the outflow opening in the chamber area 54 is the switching valve 65 , which, via a connecting line to the container chamber 49 via the connection into the gaseous medium flowing into the gaseous medium part, leading into the outflow opening 65, a connection from the gaseous working medium-containing container part 54 to the container part 49 , Has. In the container part 49 is arranged in or on the surface of the liquid working medium in this hollow body / balls 100 as heat delimitation to the gaseous working medium, this heat delimitation insulated floating bodies in the container part 49 individually loosely arranged on the surface for the working medium are permeable. In the upper container chamber part 54, the inflow opening 99 and outflow opening thereof, and in the further conduit in the expansion part of circuit 56 via connecting links to the heat engine 62 and from this is guided back leading in Schrumpfungstei 67199 00070 552 001000280000000200012000285916708800040 0002019921366 00004 67080lkreis 57 to the reservoir chamber 49 is the working circuit 55 closed, from which the working medium absorbing heat dissipating heat is conducted, is temporarily stored in the liquid state from the collecting container 51 .

The upper region of the medium temperature water column and Ar beitsmedium container chamber 59 , has lamella border 85 and is arranged in a steam chamber forming heat exchanger jacket 86 , which has a steam supply line from the water-water steam container 34 and condensation water return line 88, a circular connection. The outflow opening 97 from the upper container chamber 54 is at the same time the inflow opening 99 into the line of the expansion partial circuit 56 . The medium-temperature water column and working medium chamber container 54 via line 56 and in this arranged heat exchanger tank 83 connected to the heat engine 62 . From this via shrinking pitch circle 57 and through the associated heat exchanger 79 , which is guided by a water-heat-up conductive jacket 96 , in the continuation via associated switching valve 78 and connection to connection with outflow opening 77 into the water column chamber area 49, the shrunk condensed working medium preferably Ammonia from the medium-temperature to low-temperature conducts the WK working group guide 55 from liquid to gaseous and condensed again, into which the water of the water column 49 in the low-temperature working group 49 is fed, FIG. 2, in FIG. 1 the WK working group 58 and the associated expansion pitch circle 60 and the shrinkage pitch circle 61 is connected to the low-temperature water columns and working medium chamber container 50 and the engine 62 in a circular manner and corresponds to the course of the working circle 46 , 47 , 48 .

Fig. 3, in a modification of the Fig. 1 and Fig. 2 medium temperature WK-working circuit 102 as well as two low-temperature working circuits 105 and 108 which, like the working circuits is lead 55 and 46, preferably ammonia in the working cycle of liquid-gas = (steam) -liquid, wherein columnar water in a modification of FIG. 1 or FIG. 2 and steam chamber device 6 no high temperature have water vapor chamber regions in association but to the associated water column chambers programmatically pressure and tem perature limited, a working medium liquid range and above the vapor region or if another working medium is assigned instead of the ammonia steam area, the gas area.

The difference in the device design when assigned to high-temperature water-steam-water working circuit management to medium temperature and low-temperature working medium z. B. ammonia-liquid-vapor-liquid working group assignment is that instead of a water suction and pressure pump 111 and the water-steam tank 34 , a working medium feed pump 52 and a working medium collecting container 51 are assigned to the outside of a low-temperature large-capacity container 4 , and instead of the condensation water return line 111, a working medium feed line 111 , from which the branch line 113 , 114 , 115 lead into the individual encapsulated water column and steam chamber containers 8 , 9 and 10 and a branch line 117 represents a filling and / or emptying line connection. The branch line 113 has in the water column chamber area 10 assigned heat exchanger 118 and in the following in the working medium chamber area 10 above the water column 10 , a flow opening with a non-return valve 119 , via the liquid working medium from the reservoir 51 with the pump 52 in the medium-temperature working circuit 102 is fed in according to the work history requirement. In this branch line 113 is a heat exchanger 123 which has a circular connection with the arrangement of the heat exchanger 124 via the associated line connection connection with expansion tank 41 and via this with the compressor pump 43 . The outflow opening opens from the branch line 114 in the water of the water column chamber 9 and from the branch line 115 in the water column chamber region 8 . When categorizing the encapsulated water column steam chambers 8 , 9 , 10 , as a high temperature water column and steam chamber area, the outflow opening 119 at the end point of the branch line 113 is also arranged in the water area. Another difference is that when assigning the high-temperature working groups in and to the water-column steam chamber device 6, the designation for the water-water vapor as the working medium leading to heat-working groups 10 , 11 , 12 and in a modification in execution Fig. 3 and assignment of ammonia steam as the working medium, the thermal power working group 102 with subdivision into expansion working section 104 and shrinking working section 103 , with assignment and assignment to water column and steam chamber container 10 . The thermal power working group 105 with subdivision into expansion working section 106 and shrinking working section 107 , with input and assignment to water column and steam chamber container 9th The thermal power working group 108 with subdivision into shrinkage working section 109 and expansion working section circle 110 , with assignment and assignment to water column and steam chamber container 8 , in which, ie in the steam chamber container area above the water column surface, the liquid working medium with boiling range and above that the steam area. The respective expansion working circuit 104 , 106 , 110 , which leads from the associated respective steam area with inflow of the working medium steam into the line, through the respectively assigned inflow opening 131 , 132 , 133 , via a line path into and out of the compact heat exchanger 20 via line connection outside of the large-capacity container 4 to the heat engine and pressed by this into the respective assigned shrinkage work circuit 103 , 107 , 109 , back into and through the upper large-capacity container area ( 5 ) the respective assigned nec in itself pressure-proof and provided with preferably thermo pene thermal insulation walls water column and steam chamber container 8 , 9 , 10 are arranged. Thermopene double wall insulation is also assigned to the pipes, insofar as they do not have heat exchange properties in the pipe routing. Also in the other chambers forming devices and nested and encapsulated pipe lines 182 , 184 , 186 from the compact heat exchanger 20 , Fig. 4, and in the expansion tank 41 , Fig. 5, the required space separating temperature isolation insulation is given, likewise in the case of the engine 200 , FIG. 6. In the water columns and working medium container chambers 161 , 162 , 163 , only a partial area has an insulating jacket 164 , the other tank wall is specified as a heat exchanger wall 165 , as are partial areas 165 of the water column steam chamber device 6 and wall parts of the low-temperature large-capacity container 4 .

The water column container chambers 161-163 in the chamber area 5 at different levels have from bottom to approx. Upper end of the insulating wall 164 , like the encapsulated chambers 8 , 9 , 10 or one above the other arranged in the container chamber 5 water columns and working medium chambers 49 , 50 , 54 , a liquid, preferably a low-oxygen heat exchange and heat buoyancy-gravitational water filling, and via this the steam area. The chambers 8 , 9 , 10 , Fig. 1, which run with high-temperature working circuit assignments working medium, ie in the water-steam-water cycle, have the boiling range in the water level and the steam chamber range over this and the one as a medium and / or Low temperature designated working medium z. B. in the cycle ammonia-liquid-vapor-liquid leading heat power groups, above the water level only the ammonia liquid area and in this the boiling area and over this the steam area.

The working medium, steam-carrying lines of the respective circuits, have a boiling and steam chamber area 97 , 72 , working medium leading out of these outflow opening 71 , 99 , 131 , with a line connection to the engine combination 200 and in this line course assigned heat-conducting heat exchangers 135 , 136 , 168 , 20 . In the piping of the heat engine, the working medium steam, heat-conducting and dissipating heat exchangers are assigned. These heat exchangers are assigned to the respective shrinking partial circular guides of the WK working groups in the respective assigned water column chambers 54 , 49 , 8 , 9 , 10 and 161 , 162 , the line path for the working medium conducting and dissipating heat as well as that Working medium as a condensate) via outflow openings 119 , 76 , in the respective nachgeord Neten chamber area z. B. from the area 161 in the loading area 162 or from the area 10 in the area 9 or from the area 54 in the area 49 or 50 are assigned to forward and corresponding to the working medium shrinkage course-cross-sectional constrictions 76 and the outflow openings backflow safety and flow-through ler 144 , 76 and / or via outwardly looped line guide, flow regulator and switching devices 145 , 156 . To the working medium, from the preceding chamber area and WK working circuit outflow openings and flow regulators 76 , 77 , are at least partially the working medium feeding line guides with switching valve assignment 116 , 65 , and feed outflow openings which, depending on the circuit assignment, open into the chamber boiling area or water column area. The shrinkage pitch circle guides of a working group 128 , which is a working medium guide with the minimum temperature level, which is fed via heat, which occurs from the lower water area of the large-volume container chamber 5 via the water columns and working medium chamber 163 , has no direct heat transferring back into the water column 163 Rather, heat-transferring partial circuit with heat exchanger 230 , 171 , in the liquid-carrying area of the engine combination 200 , and in the further shrinking and condensing partial circuit, heat-transferring connection via expansion tank 41 , with the heat pump working group. The working circuits 46 , 128 carrying heat with a higher temperature level first have heat-returning heat exchangers 157 , 138 , assigned in the respective water column chamber region 163 or 8, and heat exchangers 37 in the water filling in chamber 5 and subsequently via heat exchanger 47 with the engine in the shrinking partial circuit 200 and further with the expansion tank 41 . About expansion tank 41 , the heat-transmitting connection with the lowest temperature level circuits 47 , 47 a, 109 , 129 , from the ammonia-steam condensation working circuit in these, to the heat pump pressure gas circuit 27 is given. The ammonia liquid derivation from expansion tank 41 and feed guide, has a working medium collecting tank 51 in this level tester assigned to this working medium subcircuit 98 as well as from the collecting tank to the boiling ranges of the working groups, working medium-promoting feed pump 52 with feed line guide 63 , 110 and Backflow protection and demand control valves 78 .

The ammonia feed line routing is assigned to heat exchangers 101 , 173 . The pressure gas line guide 27 from the pressure gas intermediate store 38 to the engine 200 via reusable circuit connection 176 are assigned heat exchangers 123 , 123 a. The compressed gas expansion partial circuit guide 27 , after the engine 200 flows through the pressure regulator 40, a compressed gas working medium branch guide with connection to and from the heat exchanger 124 , and via this and line routing in the expansion tank 41 with branch guide 196 a, and flow line 194 , 195 in the chamber area 181-183 in this, with line guide 25 , 27 in and out of this to the heat exchanger compressor ter heat pump 43rd

In Fig. 6, the compressor pump 43 of the multi-purpose power machine combination 200 is directly assigned, with force via the load-bearing connection 204 , 22 , and supply and discharge connections z. B. 210 , 47 , 50 , 110 , 48 , 102 , of the WK-Ar beitskreisführung and connection connections of the pressure gas leading heat transfer, thermal power and heat pump circuit 25th The engine combination 200 has two pairs, each pair in the liquid filling, which is preferably water, connected tube-container chambers 62 and 62 a and 39 and 39 a. Each chamber has a section above the liquid for pressurized gas supply and discharge with line connection and switching valves, connection 210 in association with chamber 62 or 62 a supplying and forwarding connection for low temperature ammonia vapor leading WK working groups. The chambers 39 and 39 a have inlet and outlet connection connection via reusable Schaltven valve 176 with the pressurized gas-carrying working group 25 or partial circuit guide 27th The liquid leading coupled chamber areas 62 , 62 a, have line connection 220 and 219 with the flow machine device 215 , the chamber areas 39 , 39 a via line connection 218 , 217 with the flow machine device 214 . The pressurized gas chambers 39 , 39 a, have line connection with the fluid machine device 213 . In connection with the water filling, heat exchangers are assigned to the chambers, as well as floating devices 225 and loose float balls 100 in the water level range. Above the chamber areas with the float devices are encapsulated chamber sub-areas 62 b, 39 b, in which there is a transmission connection from the float, in the chamber sub-area 62 b, piston machine devices 201 , 202 , with connection to the WK working group management and each transmission - Power connection and forwarding devices 203 as well as pump or compressed gas or a forwarding device 149 , 146 acting on a liquid. The chambers 39 b also have force-transmitting devices arranged and piston machine device 28 , 21 , with Ver connection connecting line to the working gas leading circuit 25th The chamber sections 62 b and 39 b each have a line connection with switching valve 235 , 234 . All chamber areas have a contactor level tester 224 assigned. A large-capacity container 4 b, Fig. 7, in this are shown schematically arranged Kammerbe containers 39 a and 62 a of an engine device 200 , with these in and out connecting line connections to the compressor pump 43 and engine 200 connections pneumatic and / or hydraulic as well as in the accessory area 22 , 23 , mechanical power transmission of a known type with a corresponding device connection z. B. generator, compressor, pump. Compressors and other pumps with pistons and flow machine area 200 is indicated with line connection 245 and engine connection 22 and heat exchanger-heat intermediate storage 44 assignment. In the chamber area 5 is also arranged - shown in outline - a compact heat exchanger 20 , Fig. 4, as well as an expansion tank 41 , Fig. 5 and a water-oxygen-withdrawal device 241 , which is in elevation to the chamber area in the sem the iron filling 242 , and lines 241-243 with assigned level tester 199 and coupled connection to the outside of the container 4 b arranged circulation pump 238 and multi-way switching device 239 with line connection connection in and out of the container chambers 5 and the water-oxygen withdrawal container 241 in this and line connection connection Extension 244 to a control safety valve filling and venting device 240 , which has connection in the connected line system 244 , 236 , 237 , 245 , not shown, likewise in a system with a plurality of shaft or large-capacity containers 4 , 4 a, 4 b with water-heat transfer pipe coupling and WK-system supplies arranged in the tanks chungen that are partially filled with water and in the container ter 4 , 4 a, 4 b in the water filling entered here, a set. The large-capacity containers can also be silo-like, but preferably shaft compartments embedded in the ground, depending on the system orientation, one or more. The liquid filling in this is preferably water, which has heat transfer medium, heat exchanger and heat storage mass function. In Fig. 7 are indicated on the outside, heat source solar collector 232 , line connections 236 , 237 with Wärmeab delivery points of the heating and hot water supply system 233 , and entered in container 4 a, the designation of the thermal power circuits 102-108 and 120-128 as assigned to Fig. 3 and the indicated container 4 , entered the designation of thermal power and compressed gas circuits 11-13 , 55-46 and 25 , as well as line approaches to the switching center 1 and heat source high and medium temperature heat storage 30 and heat source boiler 155 , as well as heat pump 43 and accessories room.

Absorbing heat with different temperature levels and lower-level W-K working medium circuit running tours, is in with different heat and Pressure level in two or more working groups, the same Working medium z. B. with partial temperature supply above 100 ° C and below 100 ° C, mostly low temperature Use of heat with ammonia as the working medium, which flows in the river condition, over each of the heat and working medium conductive, encapsulated water column level in the water column Working medium container chamber area, over the course of the work Supply and supplied with heat in the specified evaporator Fer boiling and pressure level for ongoing steam generation chert and conducted as a steam in a circular manner is, the working medium in the cycle with the heat supply expands and shrinks with heat removal and over one that Circular course each remaining pressure and temperature level, in Cycle condensed.

If a high-temperature heat source is assigned to the heat supply, the low-temperature working groups are preceded by several WK working group tours that guide water, steam and water, and in these, the water column level is the boiling range. Water is controlled according to the switching program, in the water column area according to the steam consumption, fed in during the work process. The heat and pressure level gradations of the water vapor-conducting WK circuits 13 , 12 , 11 are, based on the highest possible or, according to the device design, pressure-compatible, most appropriate temperature level in the circuit 13 and in this associated encapsulated water columns and working medium container boiling and steam chamber area z. B. about 310 ° C, 100 bar, and about M 55 kg / m ³ in the pressure level curve z. B. from 100 bar to 50 bar.

The circuit 12 subsequently assigned to the circuit 13 could then have an assigned level of approximately 265 ° C., 50 bar, in the boiling and steam chamber area, with a chamber size in the ratio of the steam volume then resulting to M 55 kg. Corresponding to that is entered for the following circuit 11 if the water is then halved again in the pressure level, ie programmed to approx. 25 bar and the water vapor continuation of the circuit 11 is reduced in the pressure level from 25 bar to approx. 3 bar, ie controlled by flow regulator 145 , The pressure drop occurs so that the water vapor in the water vapor container chamber to the programmed temperature level z. B. 150 ° C-160 ° C as for heat transfer to the as Ar preferably Arits ammonia leading medium-temperature working group 55 , the z. B. for the steam-carrying area approx. 140 ° C and for a boiling temperature range of approx. 125 ° C and a WK cycle with pressure difference to the subsequent from approx. 90 bar to 40 bar or up to 50 bar as appropriately aligned and programmed is arranged and the heat-transmitting course from the water-water vapor chamber via heat exchanger 83 and in the water vapor chamber heat exchanger jacket 86 , the majority of the heat in the ammonia vapor-conducting partial circuit 56 takes place, the steam energy level being increased as it flows through. The heat-supplying transfer profile at high-temperature heat supply and water vapor as the working medium-carrying WK working circuit 13 also takes place mainly with heat being fed into the steam via the steam-carrying subcircuit 14 , 177 , 186 , in the compact heat exchanger 20 , chamber area 180 , FIG. 4, the heat supply via compressed gas circuit partial circuit 27-27 a essentially via the heat exchanger assignment 183 in the chamber area 180 . The initial heat feed, ie until a predetermined temperature level in the liquid z. B. water column in the chamber area 10 is given via heat exchanger 124 and controller 31st The heat input into the water vapor working groups 12 and 11 , which is subordinate to the WK working group 13 , takes place only to a small extent via the compact heat exchanger from the heat supply through the pressurized gas working circuit 25 by the steam in the WK circuit 12 in the chamber 181 and the steam in the WK circuit 11 in the chamber 182 is reheated, ie the energy level in the steam is raised from the boiling temperature level without increasing the pressure.

From the compact heat exchanger 20 , the water vapor is passed through the respective circulation system 13 , 12 , 11 in a work-effective manner through the engine device 21 , FIG. 1, or FIG. 6 through one of the unit assignments, engine 200 , with a movable wall back and forth in the cycle moving, with the inflow into the piston unit simultaneously on the opposite wall z. B. piston side of the steam is pressed into the shrinking pitch circle and guided over this in the respectively assigned water columns and working medium container, pressed into this by the respectively assigned heat exchanger 137 , 138 , 139 and accordingly the remaining pressure level heat with a corresponding temperature level, in the water column is fed in and a high proportion of it is transported to the boiling range by means of heat buoyancy. Corresponding to the heat output via the heat exchanger in the water of the water column, the water vapor condenses in the respective shrinkage sub-circuit 15 , 17 , 19th The condensation water from the circuit guide 13 , shrinkage partial circuit 15 , is conveyed via outflow and backflow protection 143 , FIG. 2, into which you are controlled in the area of the circuit 12 , chamber 9 . The condensation water after effective steam circuit management 12 and condensation drain via shrinkage circuit 17 , in the boiling range of the circuit 11 , chamber 8 , transported. The condensation water from the circuit 11 , is conveyed via the shrinking partial circuit 19 and out or in a flow and flow regulator device into the water-water vapor container chamber 34 .

The condensation flow through the heat exchanger with heat transfer level, is controlled by cross-section through flow allocation and pipe constriction 140 , 80 , in accordance with the intended shrinkage flow and through flow control device 145 , 156 . The heat build-up in the respective water column area is conducted by means of a partition or pipe duct 96 , 152 , which conducts gravity, so that the water portion which decreases after the evaporator heat is emitted does not simply mix with the heat build-up, but rather via the outflow inlet openings 153 in the lift / Water of the gravity cycle is controlled in the highest temperature heat exchanger level, so that the evaporator heat in circuit 13 is largely via the heat recirculation and in the subsequent circuits 12 , 11 , the heat retransmissions in addition to the heat supply from the respective upstream circuit takes place with the supplementary Heat supply in the partial circuit 14 , 16 , 18 leading the steam, via the heat feed in the compact heat exchanger 20 . In the variant of medium and low temperature z. B. ammonia as the working medium leading working groups 102 , 105 , 108 , Fig. 3, zen to steam also the heat exchanger 20 is arranged.

The heat energy inflow into the steam-conducting sub-circles, the pressure specification as specified above the boiling point in the boiling range not being raised, however, the energy level in the steam being raised via the compact heat exchanger 20 and the z. B. plus 5% to 30%. After effective and heat-returning circulating energy flow in the WK circuit 13 is with temperature reduction to about 5-10% above the boiling temperature level of the ordered circuit, via the condensation of circuit 13 in the circuit 12 , and further from this in the circuit 11 , and the respective residual energy z. B. from the feed into the circuit 13 via the heat exchanger and gravity circuit 150 and the associated inlet and outlet openings 151 , in the heat-exchanging gravity water circuit, heat from the lower water column area of the chamber 10 in the upper water column area of the chamber 9 and the portion continuously Energy from the lower area in this gravity heat transfer process to the upper area, that is to say in the boiler area of the chamber 8 , and passed on, whereby from the lower water column area in chamber 8 via the heat exchanger wall area 165 into the water filling of the associated chamber separating casing 152 here with the water vapor formation in this and the water vapor heat transfer to the heat exchanger 83, heat is passed on and to this and the steam condensate recirculation, the heat supplied from the outside is continuously dissipated in the low-temperature working circuit. The condensate is returned to the water-water vapor-water working groups, controlled by level tester pulse generators 154 , 199 and control center 1 , line 111 and pump 159 from the water-water vapor container 34 in the order that a proportion of water from the water column area 8 in the water column area 9 and from this into the water column area 10 is pumped in the cycle of condensation delivery with programmed controlled mass / kg.

The required temperature difference for the heat emitting Condensation flow in heat retransmission and heat layers tion in the water column of the respective circuit assignment is through this condensate recovery with the never lower temperature, effectively promoted and heat supply and feed through approximately to the heating of the mass in the condensate level to the releasing level and the difference between evaporator heat regenerative processes and pre-programmed Heat transfer including the Power retransmission portion from the engine and the Timings between returning press the steam into the respective shrinking pitch circle Heat emission in these and the condensation emission in the after following working group boiling range.

In the case of the WK working circuit guides with ammonia steam as the working medium, a variation to the water-water vapor is the WK working circuit guide, so that the last, ie with the lowest temperature level assignment in the working medium, shrinkage process, heat to the water filling in the large-volume container chamber 5 , forwards via outer wall part 165 in the lower chamber area 8 and via the water-heat-gravity-conducting wall partition 152 into the upper water area in the container chamber 5 .

Heat from the water area of the container chamber 5 is fed from the area with the higher heat level into the expansion partial circuit guides carrying ammonia steam. Heat is fed in via heat exchangers 101 , 173 into the ammonia liquid subcircuit, from the water filling in the container chamber 5 , heat from the circuits or the thermal power of ammonia steam, is partly as in the water-steam circuits in the assigned water column with the conducted buoyancy-gravity heat retransmission processes in its own boiling range, the ammonia own evaporator heat in condensation has a preferably high heat retransfer approximately similar to the water vapor-water cycles. In some cases, the heat conduction through the working circuit runs like water vapor circulation through ammonia heat transfer from the higher heat level and pressure level leading working group z. B. 102 to 105 or 120 to 125 , 55 to 46 , and from the lowest heat management working group z. B. 46 , 108 , 128 , after work on the engine 200 , on heat-emitting course via the heat exchanger 47 and on heat dissipation in the shrinkage condensation drain via heat exchanger in the expansion tank 41 , with heat removal from the gaseous ammonia steam to condensation lead the working group , with heat transfer to the nitrogen-carrying pressure-gas expansion partial circuit 26 , the heat transfer medium and heat pump working circuit 25 .

The ammonia steam liquefaction process with controlled high Condensation heat is released into the water vapor condensers sation under specified pressure level and heat dissipation.  

The temperature level difference between the supply of heat in the boiling range and the removal of heat in the condensation process, taking into account the shrinkage time and the minimum pressure level retention, results in the work-effective pressure difference, which is transferred into force via a heat engine 200 and accessories. About the nested arrangement of the encapsulated chambers 8 , 9 , 10 , a better use of heat is made possible at high and medium temperature heat with pressure compensation.

For the low-temperature use of heat, the arrangement of the water columns and working medium chamber areas Fig. 3, 163 , 162 , 161 , one above the other in the water of a large-volume container chamber 4 , increasing efficiency. It is accordingly the heat stratification, the heat feed from the water filling of the large-volume container chamber in several temperature stages in the thermal power working groups, with a larger working medium mass required in the assigned in the lower water area assigned WK working group according to the thermal expansion, the additional need that not fed in from the preceding circuit, is pump 52 and feed line guide 111 , 116 , absorbing heat through heat exchanger 173 and outlet opening 65 in and through the water of the water column in chamber 163 and in FIG. 2 as a variant with a temporary compressor pump-like pressure increase in the water column container chamber 49 , via line routing with switching valve 65 and outflow opening via boiling area 74 in chamber 49 and condensate supply via inflow-outflow opening 77 in the lower water column area, balanced from time to time. According to the program allocation, the different temperature utilization of the heat and power cycles with heat feed via lamella wall 89 , 72 and heat exchanger 90 , 91 , as well as partly with retransmission processes via heat exchanger 158 and the water column container walls 165 to different water levels in the large container 5 in the switching center and level tester pulses, so that a work-effective temperature stratification and thus the highest possible heat utilization and low heat level z. B. + 25 ° C and temperature difference to z. B. -5 ° C over expansion partial circuit of a heat pump circuit 25 with energy productivity increasing use for thermal power efficiency, are given. The pressure level to be classified Differences according to the heat level in the variant of FIG. 2 from the ammonia-leading working group 55 to the condensing pressure level up to the working group 46 , can be adjusted with a corresponding heat level layer specification, for. B. be about 40 bar to 70 bar, and from the pressure level in the circuit 46 to the subsequent condensate collector z. B. approx. 10 bar to 30 bar for the subsequent, the Druckab gradations will be smaller in the variant Fig. 3 with at least three superimposed thermal power cycles, z. B. from 75 bar to 35 bar and from 35 bar to about 10 bar and to the condensate collector z. B. from 10 bar to 3 bar, the temperature level reduction being controlled by the pressure gas expansion in the expansion tank 41 and the pressure difference correspondingly. In or with the connection, heat engine combination 200 and compressor heat pump 43 and associated pressure gas circuit running guide 25 , as well as switching center control program via contactors and multi-way switching valves 210 , 27 , 40 , and force-coupling accessories 29 , 22 , 23 , a demand control with heat supply and energy transfer is carried out.

If the compressed gas circuit 25 is also classified as a high-temperature heat carrier and thermal power cycle, on the one hand, heat absorption from the minus range and with subdivision of the circuit as expansion subcircuit 26 in accordance with the effective temperature level, heat supply in a circuit, heat-absorbing via heat exchanger and shrinking sub-circuit 27 , emitting heat, the cycle can be controlled as a thermal power heat transfer medium and heat pump working group.

High temperature heat from a heat source e.g. B. Hochtem temperature-heat storage 30 and / or boiler 155 is at a temperature level, which is preprogrammed for the work-effective and classification and system classification from runs at about 400 ° C a compressed gas z. B. nitrogen or compressed air leading working circuit 25 is fed. Compressed gas z. B. with programmed pressure level z. B. m ³ / mass 60 kg / approx. 80 bar, 400 ° C, work effectively over combustion engine 21/200, ge passes pressed from this in the heat-emitting part of the expansion circuit 27, in this heat conducting performed with such through-flow pressure gradient. B. from 80 bar to 75 bar, and temperature gradient from 400 ° C to 10 ° C controlled, whereby to maintain the pre-programmed pressure gradient congestion cross-sectional changes in the line path according to the compressed gas shrinkage, ie volume decrease according to heat emission, and metered pressure gas transmission from - from the compressed gas buffer 38 via pressure regulator control device 40 is that the preprogrammed pressure in the pressure gas intermediate storage 38 and pressure difference in the chambers 39 , 39 a of the engine 200 is maintained. A partial pressure reduction takes place via engine 200 / container 39 , 39 a. From the pressure regulator control device 40 with inflows into the compressed gas expansion tank 41 , the substantial pressure reduction takes place, according to demand control, which is done by correspondingly pumping off and on via the downstream compressor pump 43 . The temperature reduction is via compressed gas expansion according to the cooling effect requirement for heat removal from the WK shrinkage sub-working group 47 or 50 or 109 , pumping over the compressed gas and compressing ge controls via heat pump. The work efficiency of the pressurized gas working group 25 is controlled according to the program call via control center 1 so that when no heat at an elevated temperature is required for a work-effective flow, but only a heat flow for a work-effective heat feed for an ammonia-leading work group z. B. between about 100 ° C and 160 ° C from a heat source z. B. 43 , and heat output via heat exchanger 36 a, 32 , 31 , partially in the WK working groups 120 , 102 with interposition of a heat transfer medium z. B. water vapor / water, container chamber 34 .

With programmed pressure level maintenance such as with compressed gas circulation with supply of heat approx. 400 ° C and difference to 10 ° C in the heat-emitting course, less mass is required in the cycle, as with a heat difference of 160 ° C to 110 ° C. The difference in mass of pressurized gas is fed as required from the pressurized gas storage bottles 231 into the circuit 25 or is pumped back out of this via the compressor pump 141 by the engine 200 when the program is controlled. Flowing with compressed gas at the heat difference of z. B. 160 ° C to 10 ° C, the WK working group 25 with the heat difference curve and compressed gas flow "on-off", heat engine 200 , 28 , only little heat-power work efficiency.

The effectiveness of the work consists essentially in the heat transfer, refrigeration and heat pump effects. With flows with high-temperature heat absorption and effective pressure gas flow in the cycle on-off by the heat engine 200 with subsequent temperature level, decreasing work flow z. B. from approx. 400 ° C to approx. 10 ° C, results from the current pressure gas volume change in the circuit, a pressure gas volume mass difference z. B. 1 m ³ pressurized gas approx. M 60 kg / 400 ° C to approx. 0.33 m ³ pressurized gas M approx. 99 kg / 10 ° C, this difference of 67% to 33% corresponds to the assumed flow pressure resp Flow pressure loss of z. B. 80 bar to 75 bar, a 60% pressure difference to be used in a work-effective manner with a working group management that correspondingly drops in the pressure level. For the pressure received in the circuit 25 , which is necessary for the efficiency or heat transfer processes with a corresponding temperature level, a substantial proportion of thermal power is delivered via the engine 28 , 200 for the circuit pressure maintenance. e.g. B. assumed necessary with appropriate heat transfer time sequences 50% for the circuit stop and 50% for power delivery via engine 200 and accessories 22 , 203 , transmitted to the compressor pump 43 as the driving force, likewise the power output via the pressure difference according to relaxation flow pattern from the compressed gas intermediate storage 38 to the expansion tank 41 via engine 200 z. B. the pressure difference power of 75 bar from buffer 38 and z. B. 20 bar in the compressed gas expansion tank 41st Further driving force transmission for the compressor / heat pump via the work-effective pressure difference of a WK circuit via WK machine 200 and accessories 22 are transmitted, whereby by the generation of refrigeration in the compressed gas expansion tank 41 , the temperature reduction and condensation of a gaseous working medium in the working circuit 47 or 50 or 128 or 108 takes place and thus the work-effective pressure difference in these is considerably increased. The possibility of lowering the temperature in the compressed gas and in the gaseous, preferably steam, working medium of the WK relaxation partial circuit of the WK working circuits, with liquefaction of the gaseous working medium and again via heat absorption, with a transition from the liquid to a gaseous state. With heat-absorbing expansion partial circuit, both in the compressed gas and via the gaseous working medium expansion partial circuit, low-temperature heat from a wide variety of environments and / or heat-exhibiting areas, for. B. heat exchanger subcircuit 160 , Fig. 7, withdrawn and stored in the respective classified working medium and work efficiency and / or gaining heat from low temperature ranges, increasing efficiency, arranged in the WK work cycle guides via control circuit management with pressure differentiated work flow.

For the recognizable sequence classification, the are approximate Called data, pressure, temperature, working medium, mass and Volume that is variably controlled and / or specified can and should not be regarded as mandatory are.

For the pressurized gas, preferably nitrogen or compressed air, circuit 25 leading as a heat transfer and thermal power circuit are, for. B. accepted as data. Retrieval from high temperature heat source 30 or 155 with approx. 400 ° C, 80 bar in the expansion partial circuit via engines 200 , partial area 28 , used in a work-effective manner, from this with pressure by heat exchanger 46 , FIGS. 1 and 2, or 20, FIG , assigned in the direct or indirect engine area 200 , so that a predetermined amount of heat is given to the steam-carrying circuits 12 , 13 or 102 . At the boiling temperature, the steam is led from the boiling range, passed into the compact heat exchanger 20 , in which heat is transferred to the working medium steam, and heat is transferred for reheating. With flow through the heat exchanger in the guide run, the heat transfer medium pressurized gas with decreasing temperature, through the compact heat exchanger 20 , details Fig. 4 z. B. from the initial temperature level z. B. 400 ° C to about 320 ° C after heat in the expansion circuit 16 to about 265 ° C in the following after heat in the medium water vapor as a heat source to the circuits 55 or 120 to about 160 ° C via heat exchanger 32 , in downstream via heat exchanger 36 , feeding heat into the medium of water in the steam and water tank 34 , releasing heat to approx. 130 ° C. and further via heat exchanger 31 releasing heat in the water area of the low-temperature tank chamber 5 , the large-volume tank 4 . Via heat conduction is further heat in the water in container 5 , z. B. 99 ° C and the lower region of the intermediate storage 38 z. B. passed down to about 10 ° C in temperature level.

The working medium stored in the compressed gas intermediate store 38 at approx. 10 ° C./75 bar is then used to absorb heat from another circuit, which is effective in terms of work, via heat engine 200 at approx. 10 ° C./75 bar.

The gaseous working medium of a shrinkage pitch course z. B. 47 or 128 , in particular, heat is removed, so that the working medium preferably ammonia vapor condenses at a predetermined pressure level, the relaxed pressure gas in the expansion tank 41 is fed accordingly heat. In the further pipeline, z. B. 175 and / or 170 and 169 and this associated heat transfer connection to a heat transfer circuit z. B. 160 or from chamber 5 , further heat in the compressed gas to the heat level z. B. 10 ° C with environmental heat absorption and up to approx. 30 ° C with heat absorption from the water in the lower region of the container chamber 5 of a large-capacity container 4 .

The compressed gas is via compressor pump 43 at a pre-programmed pressure level, e.g. B. compresses 80 bar and compressor heat from the heat transfer medium to the specified application, passed from.

Compressor pump 43 can, depending on the program assignment / system orientation, have the medium-temperature heat source function, that is to say compression gas increasing at the heat-temperature level above water boiling temperature, so that the heat exchanger 44 , as from the water-steam container 34 , FIG. Water vapor routing to the WK circuit 55 through the water-steam chamber 86 for feeding heat into the gaseous working medium with a medium-temperature functional sequence, likewise in the case of heat-transferring assignment of the compact heat exchanger 20 in connection with compressed gas heat carrier functional sequence of the shrinking partial circuit 21 and heat feed into the WK Working circuits 102 , 105 , 108 , Fig. 3.

As a program function, the compressor heat pump 43 dissipates heat below 100 ° C and is also not assigned a high-medium temperature heat source 155 or 30 , but is only assigned to waste heat or a thermal solar system 232 as an essential heat source, as well as several low-temperature large-capacity containers 4 , 4 a, 4 b with water filling as heat storage mass, the program heat stratification takes place in the large-capacity container with associated low-temperature WK cycles z. B. 46 , 120 , 125 , 128 , corresponding to the heat exchanger output and retransfer, ie in the water near the surface z. B. about 90 ° C-95 ° C near the ground z. B. 10 ° C. With priority assignment of heat storage function and only classification of devices as heat engines container assignment 62-62 a and / or 39-39 a with engine combination 200 are shown as a container device the same as the expansion tank 41 and the compact heat exchanger 20 in FIG. 7 Filed water tank 4 and have shielding insulation to the water area. For the heat transfer processes through closed heat carrier circuit management, is preferably associated with frost protection in the water-carrying circuit at solar system 232 , as is well known, via heat exchangers 70 , 68 , likewise with heat exchanger connection for heating supply and hot water with demand switching and heat exchanger coupling 233 via associated closed heat carrier circuit management in a network with heat exchanger 69-169 .

The heat requirement redistribution from and in the water fillings, controlled by several large containers 4 , 4 a, 4 b via level tester contacts, switching center 1 and reusable circuit 239 , pump 238 , line connection connections 243 , is carried out by the staggered arrangement of the inlet and outlet openings in the water filling. The water filling is expediently kept low in oxygen, this by predetermined corrosion processes with controlled water flow through a container 241 , the corrosion-resistant additives z. B. 242 has achieved. Venting and unwanted gas suction as required is controlled by filling and venting and control and safety valve device 240 . The thermal power conversion processes, with heat output from low-temperature thermal power cycle with heat transfer into the heat pump relaxation sub-circuit via expansion tank 41 , takes place after work-effective use, preferably via water displacing in the cycle, whereby water displacement cycle management of engine sub-area 39 a and 39 b and / or 61 a, 62 b, the transmission of force through the flow or piston machines with force-transmitting devices, assignment 21 , 212 and engine accessories 23 takes place. Assigning the spatial device subdivision to different large-capacity containers 4 , 4 a, 4 b, as well as compressor 43 and engine subdivision, in the water in the container chamber area 5 and in a machine room above this, Fig. 7, arranged part areas, is about Line connection connections 245 pneumatically and / or hydraulically, with the assignment of engine accessories 22 , 23 power transmission for predetermined use, for. B. heat pumps and / or generator drive controlled by switching program assignment in the switching center 1 , take place.

Reference list

1

Control center

2nd

Manhole container outer wall

3rd

Wall insulation

4

Low-temperature large-capacity container

5

Low temperature chamber area

6

Water column and steam chamber device

7

as before

8th

Liquid column and working medium container or water column and steam chamber container

9

as before

10th

as before

11

Heat-power working group water-water vapor

12th

as before

13

as before

14

Expansion pitch circle too

11

15

Shrink pitch circle too

11

16

Expansion pitch circle too

12th

17th

Shrink pitch circle too

12th

18th

Expansion pitch circle too

13

19th

Shrink pitch circle too

13

20-20

a compact heat exchanger

21-21

a heat engine

22

Heat engine accessories

23

Engine device with accessory connection

24th

Heat exchanger

25th

Pressurized gas leading working group

26

Expansion pitch circle

27

Shrink pitch circle

28

Engine thermal power and / or compressed gas

29

Power delivery accessories

30th

Heat source z. B. High-temperature medium-temperature heat storage

31

Control and bypass device

32

Heat exchanger, compressed gas water vapor

33

Heat exchanger, pressurized gas water

34

Water-steam container

35

External wall insulation

36

Heat exchanger

37

as before

38

Pressurized gas buffer

39

Pressurized gas engine

40

Pressure regulator flow valve

41

Expansion tank

42

Heat exchanger

43

Multi-stage compressor pump, with heat exchanger (heat pump)

44

Heat exchanger-heat pump-heat buffer

45-45

b Negative heat exchanger area Assignment of sub-circuit to cooling circuit wall

46

Heat and power working group "low temperature"

47

Shrink pitch circle

48

Expansion pitch circle

49

Low temperature water column and working medium chamber container

50

as before

51

Working medium collecting container

52

Feed pump

53

Heat exchanger and feed line branch and line

54

Medium temperature water column and working medium container chamber

55

Heat and power working group (zu

54

)

56

Expansion pitch circle

57

Shrink pitch circle

58

Heat and power working group

59

as before

60

Expansion pitch circle

61

Shrink pitch circle

62

Heat engine

63

Feed line with non-return valve

64

Line with switching valve

65

Connection line with changeover valve from Container chamber opening (

49

) (

50

)

66-66

a Reversing switching valve

67

Heat exchanger

68

as before

69

as before

70

as before

71

Container chamber area with heat exchanger wall

72

Boiling range of heat exchanger fins

73

Insulating wall "Thermopen"

74

Liquid level and heat sensor in the boiling range

75

Cable route with cross-sectional constriction and / or with backflow protection

76

Heat exchanger

77

To-outflow opening

78

Switching valve

79

Heat exchanger

80

Cross-sectional constriction / pitot nozzle

81

Liquid level and temperature sensor

82

Liquid level sensor in the boiling range

83

Heat exchanger tank

84

Inflow opening

85

Slat borders

86

Heat exchanger jacket forming water vapor chamber

87

Steam supply line

88

Return of condensed water

89

Slat border

90

Heat exchanger

91

as before

92

Heat exchanger tank

93

Switching valve

94

Heat exchanger

95

Feed line opening

96

Heat exchanger in the jacket / duct forming heat-water buoyancy

97

Boiling range in the medium temperature chamber

98

The most up-to-date pressure-heat-liquid level

99

Inflow opening

100

Floating bodies, preferably spheres, which are hollow on the inside

101

Heat exchanger

102

Medium temperature working group

103

Shrink pitch circle

104

Expansion pitch circle

105

Low temperature working group

106

Expansion pitch circle

107

Shrink pitch circle

108

Low temperature working group

109

Shrink pitch circle

110

Expansion pitch circle

111

Line for feeding, filling and emptying

112

Working medium feed pump

113

Branch line with switching valve assignment

114

as before

115

as before

116

as before

117

as before

118

Heat exchanger

119

Inflow opening with backflow protection

120

Heat-power working group "medium temperature"

121

Shrink pitch circle

122

Expansion pitch circle

123-123

a heat exchanger

124

Heat exchanger in the cooling circuit expansion circuit

125

Heat and power working group "low temperature"

126

Expansion pitch circle

127

Shrink pitch circle

128

Heat and power working group "low temperature"

129

Shrink pitch circle

130

Expansion pitch circle

131

Inflow opening

132

as before

133

as before

134

Heat exchanger

135

as before

136

as before

137

as before

138

as before

139

as before

140

Pipe narrowing / change in cross section

141

as before

142

as before

143

Outflow, inflow, backflow protection device

144

as before

145

Outflow, inflow and pressure flow control device

146

pneumatic or hydraulic power transmission device

147

as before

148

as before

149

pump

150

Heat exchanger gravity circuit

151

Inflow and outflow opening

152

Heat-gravity conducting / separating pipe shaft or wall assignment

153

Outflow and / or inflow opening in water / on drive / gravity-conducting partition

154

Level boiling range

155

Heat source / boiler

156

Reusable switching valve

157

Heat exchanger

158

as before

159

pump

160

Water-carrying heat transfer heat exchanger circuit connection

161

Water columns, working medium container chamber with boiling area

162

as before

163

as before

164

Insulated area / insulated casing

165

Heat exchanger wall, heat transfer wall area

166

Chamber area

167

Cable routing with backflow protection

168

Heat exchanger

169

as before

170

as before

171

as before

172

as before

173

as before

174

as before friction heat-waste heat

175

Heat exchanger

176

Multi-way circuit

177-177

a Inlet line with opening

178-178

a as before

179-179

a as before

180

Heat exchanger chamber area

181

as before

182

as before

183

Heat exchanger solid mass with lamella assignment or heat exchanger area enlargement

184

as before

185

as before

186-186

a Outflow opening with line routing

187-187

a as before

188-188

a as before

189

Pressurized gas flow divider

190

as before

191

as before

192

Flow direction regulator

193

as before

194

Inflow opening

195

Outflow opening

196

Guide branching work medium

197

Leading work medium

198

as before

199

Level test temperature sensor / contactor

200

Multi-purpose engine combination

201

Piston engine device

202

as before

203

Gear ratio and power transmission device

204

as before

205

Fluid machine

206

as before

207

as before

208

as before

209

Reusable switching valve

210

as before

211

as before

212

Directional control valve mapping

213

Fluid machine device

214

as before

215

as before

216

as before

217

Route

218

as before

219

management

220

management

221

Power transmission device / pull rope

222

Power transmission device / thrust and tie rod with rack section and piston end

223

Guide bar with support suspension and piston chamber

224

Pressure and heat level testers and contactors

225

Ballast float device

226

Rack

227

Piston and connecting rod

228

Pipe connections

229

Flow control and bypass switch valve

230

Heat exchanger

231

High pressure compressed gas storage bottle

232

Solar collector

233

Hot water and heating supply system

234

Pipe connection with switching valve

235

as before

236

Control and power transmission lines

237

Heat transfer pipe connections

238

Circulation pump

239

Multi-way switching

240

Control safety valve filling and venting device

241

Water-oxygen withdrawal container

242

Elevation chamber area / iron filling

243

Incoming and outgoing lines

244

Line connection connections in and out of the water leading containers

4

,

4

a,

4

b

245

Line connection connections as before and device connection connections

246

Engine room

Claims (29)

1. Method for increasing energy productivity with combined heat and power and intermediate storage by heat transfer processes in and from a closed heat and power cycle with liquid and / or gaseous working medium in the by heat transfer in the expansion circuit working medium through the heat exchanger and pipe wall Heat supplied from a high-temperature heat source, the working fluid expanding through heat absorption, effective for work via the WK machine, conveyed from this into the heat-power-relaxation circuit via the wall of the line guide and heat exchanger, heat to the working medium, which shrinks it Pipe wall and / or heat exchanger in the temperature gradient to a heat transfer medium, this heat transferring and continuously dissipating a portion of heat in a buffer storage, whereby in the heat-conducting WK working group continuously receive a heat portion to the heat source in the cycle s as well as with heat transfer coupling from the heat buffer storage heat, when required, the working medium in the circuit is fed back into the renewed heat absorption processes temporarily, in the case of temperature, is carried out in a work-effective manner, heat is continuously converted into power for electrical energy generation in the work, or is passed on, characterized in that on demand with specifications from the switching program via the switching center ( 1 ), heat from a heat source ( 43 ) ( 44 ) and / or ( 30 ) ( 155 ) with an elevated temperature level in controlled transmission processes to the working medium at least one closed WK working group ( 13 ) ( 55 ) ( 25 ) ( 102 ) and / or heat transfer medium ( 25 ) ( 5 '), heat from this through one or more heat exchangers ( 20 ) ( 24 ) ( 36 ) ( 124 ) ( 83 ) guided over the heat exchanger walls in the thermal power expansion partial circular guides ( 27 ) and / or ( 19 ) leading a gaseous working medium ( 57 ) ( 103 ) with a programmed temperature level, fed in and with this thermal energy the specified energy level, as specified from the respective boiling range in the working medium, is also fed into the respective gaseous working medium leading expansion circuit, the working medium without increasing the pressure level with heat enriched with tem energy level work effective controlled by thermal engine ( 200 ) and / or ( 28 ) ( 21 ) ( 62 ) directed by and / or via this with proportional heat-power output in the assigned working group pressure pump-like the gaseous working medium transported in the respective assigned th Pressed-in shrinkage circle, in which heat and heat conduction and / or condensing with temperature level increasing controlled pressure and heat profile with dross rarely pressure reduction processes through or over pipe cross-section constrictions ( 80 ) ( 140 ) ( 141 ) ( 143 ) and / or backflow protection and Flow controller ( 76 ) ( 145 ) in the respective shrinking partial circuit ( 19 ) or ( 103 ) or ( 57 ) heat at the boiling temperature level according to evaporator heat requirement via the heat exchanger ( 137 ) ( 138 ) ( 139 ) fed into the surrounding liquid medium with heat buoyancy in the liquid-carrying area controlled by gravity-separating conductive wall shaft and / or pipe arrangements ( 96 ) ( 152 ) in the liquid-carrying, column-like area, with heat retransmission processes of the evaporator heat demand controlled to the boiling range, excess heat, ie the thermal energy difference between the energy supply via the heating of the gaseous working medium and energy-returning circuit via the evaporator heat energy preservation, passed on in a lower-level working group at a given pressure and temperature level, partly via the condensed working medium and partially via heat exchanger wall and this assigned heat-transferring working media flow continuously fed to the respective working group heat, which is continuously passed with heat-returning partial circuit runs and the heat energy supplied from outside is passed on in a work-related manner. 2. The method according to claim 1, characterized in that supplying heat from a pre-connected a predetermined pressure and heat level to the pointing heat-power working group ( 13 ) or ( 12 ) or ( 102 ) or ( 105 ), this from the outside Is fed in, after work-effective flows, of this externally stored thermal energy, this with a programmed reduced temperature level proportionately via the heat exchanger wall ( 165 ) ( 151 ) ( 150 ) and heat-conducting liquids, at least partially controlled, guided by heat / gravity leading heat exchanger and pipe shaft - Assignments ( 150 ) ( 165 ) heat to and into a subordinate WK work boiling area transferred into this, whereby further proportional heat energy via largely shrinked condensate working medium with heat and working medium transferring discharge from the upstream working circuit via line outflow opening from this or Inflow opening ( 144 ) ( 145 ) passed on to the downstream WK working group in the boiling range assigned to them and to the heat transferred from the upstream working circuit to the boiling range, the boiling range via heat feedback via its own shrinking sub-circuit and heat buoyancy and gravity drains, so that the required heat of vaporization given continuously and this over boiling process cycle from liquid to gaseous working medium transferred thermal energy via the respective assigned expansion partial circuit in and through compact heat exchanger ( 20 ) and the upstream or downstream heat exchanger via wall in this, by a heat transfer medium and / or Circulation, further heat with a higher temperature level is fed to the gaseous working medium in the leading expansion partial circuit, the working medium is raised in energy level, guided to the heat engine, with or after effective work WK machine use, the gaseous working medium, via the heat engine a portion of force energy with pressing the working medium into the respective shrinking pitch circle z. B. ( 15 ) ( 19 ) ( 103 ) ( 57 ) ( 27 ) and via this assigned in the partial circuit heat exchanger and liquid area, preferably water aligned as a water column with gravity use, the evaporator energy largely required feedback, and partially supplemented, which continuously the cycle of previous heat via load-bearing processes with a high level of energy fed in, with a lower level of heat and pressure level, is passed on in a controlled manner. 3. The method according to claim 1 and 2, characterized in that heat from a thermal power and / or heat transfer circuit ( 11 ) ( 25 ) derived via shrinkage partial circuit ( 15 ) and / or ( 27 ) and heat exchanger ( 36 ) ( 32 ) and ( 83 ) heat exchanger wall ( 165 ) in a liquid heat transfer medium, preferably water and / or in water vapor, in a container chamber or chamber area ( 34 ) ( 166 ) with preprogrammed boiling temperature and pressure water vapor via line in and / or through a heat exchanger ( 83 ) heat exchanger chamber ( 86 ) via the heat exchanger wall, transferring heat into a liquid and / or gaseous working medium, preferably ammonia / steam, feeding into a thermal power working group, the heat transfer medium water vapor with heat and pressure level specification continuously flowed in and condensed with heat emission flowing through piping ( 88 ) ( 167 ) due to height offset and gravity and / or via Pu pumping action ( 157 ) is pumped in the circuit to the heat exchanger / water boiling area and is returned again. 4. The method according to claim 1 to 3, characterized in that in a columnar, encapsulated th device, referred to as a medium-temperature water column, and steam chamber ( 54 ) and / or low-temperature liquid column and working medium chamber ( 49 ) or ( 50 ). Liquid arranged in the water column chamber area, preferably low-oxygen water, and liquid working medium, preferably ammonia, arranged above the water level ( 82 ) ( 81 ) or ( 74 ), with continuous heat supply to the pressure and boiling temperature level in the liquid working medium and also via the Ammonia liquid area, ie over the boiling area, by continuously supplying heat from the outside, in part via the chamber container lamella heat exchanger wall ( 82 ) ( 72 ) beyond the boiling temperature, to the working medium steam, supplied with thermal energy, via heat transfer from the tank area ( 4 ) External heat supply, e.g. B. from the downstream heat exchanger ( 90 ) ( 83 ) ( 136 ) and / or via water vapor heat transfer medium through the steam-conducting chamber and heat exchanger area ( 86 ) ( 83 ) the working medium steam, increasing energy level, heat is fed, a heat retransmission in the liquid working medium by isolating floats, small part inserts, in front of loose float balls, obstructed, or heat absorption from the gaseous working medium / steam into the liquid working medium largely slowed down, however, the heat-induced buoyancy of the supplied working medium into the water filling of the container chamber ( 49 ) or ( 50 ), the working medium increases work efficiency and heat is transferred back and enriched with heat energy from different temperature level levels. 5. The method according to claim 1 to 4, characterized in that at predetermined time intervals and / or temperature level contact transmitter pulses signaling tem heat level stratification in the large container ( 4 ) via switching program of the switching center ( 1 ), the switching valves ( 53 ) ( 156 ) ( 66 ) ( 66 a) each controls the working media inlet and return flow direction alternating between the working medium water column chamber area ( 54 ) to the chamber area ( 49 ) and to the chamber area ( 50 ) and back or to the heat engine ( 62 ) ( 200 ) or from chamber region (54) machine to the Wärmekraftma (62) (200) work effectively these forwarded by flowing white, gesteu with predetermined interruption times ert with superior heat level in the exchange line via connecting and switching valve (65) of gaseous working medium with a high pressure level from the reservoir chamber (54) Line and inflow opening ( 84 ) into the container chamber ( 49 ) or ( 50 ) alternately in this r the high-pressure transmission compressor pump effect, with the resulting temperature rises in the working medium and water column area, with heat boost in it, and partly via the outer wall of the column tank in the upper area to transfer heat to the water from the open-air tank ( 4 ), storing and partially transferring heat forwarding with the working medium, whereby heat is temporarily withdrawn from the lower and middle area and in the upper area of the container chamber ( 4 ) corresponding to the heat pump-like pressure increase and reduction in the column container chamber area ( 49 ) ( 50 ) via container wall and working medium guidance. 6. The method according to claim 1 to 5, characterized in that via heat transfer medium heat at an elevated temperature level via the heat exchanger wall in the boiling range ( 82 ) of the heat-power working group ( 55 ) in the liquid working medium, which is preferably ammonia, fed into this , where heat is conducted over the wall of the container chamber area ( 97 ) from a water-steam as a partial circle ( 86 ) ( 88 ) which carries the heat transfer medium and which converts the working medium ammonia from the liquid to the vapor state. Via heat exchanging the heat transfer medium leading chamber region (86) (82) and the steam-carrying expansion part circuit (56) receptive via heat exchanger chamber (83) and or (20) further heat the working medium vapor with increased energy level above the engine (62) (200) work effectively conducted in pressed the shrinking pitch circle ( 57 ), via this heat exchanger ( 92 ) heat in the subsequent heat-power working circuit ( 46 ) and heat exchanger ( 79 ) in the water in the water column Kammerbe container ( 54 ) in this partially with water heat - Buoyancy, the buoyancy via the wall ( 96 ) of water-sinking gravity drains after heat release separating ge conducts heat back to the boiling area ( 82 ) and heat partially in the water filling of the Großraumbe container ( 4 ) via wall in the lower water column area ( 54 ) derived and in the further shrinking pitch circle ( 57 ) ( 57 a) gest According to the program specification, multi-way circuit ( 156 ) alternately via line ( 57 ) ( 57 a), a portion of heat with the largely condensed working medium in the water column chamber ( 49 ) or ( 50 ) via outflow opening ( 77 ) for transmission with heat boost in the each boiling area ( 74 ) and heat-absorbing heat via the outer wall / lamella border ( 89 ) from the surrounding water area from the open-air tank ( 4 ), the working medium in the boiling area ( 74 ) from liquid to gaseous state with temperature and pressure level corresponding to Heat supply in and out of the boiling range, the working medium changing from the liquid to a gaseous state, via line inflow opening ( 84 ) in the expansion expansion circuit ( 48 ) further heat via heat exchangers ( 90 ) ( 91 ) from the upper water area in the large-capacity container ( 4 ) withdrawal and heat in the further expansion part of the circuit he heat exchanger ( 92 ) from a heat with a higher level shrinking partial circuit ( 57 ) or via compact heat exchanger ( 20 ) from a circuit associated therewith, the gaseous working medium steam controlled by switching valve ( 93 ) in a programmed change from / over low temperature water column Chamber container ( 49 ) or ( 50 ) directly or indirectly via heat exchangers from the previous working group absorbing heat at an elevated level to the heat engine ( 62 ) ( 200 ) and after using it alternately via switching valve and shrinking partial circuit ( 47 ) or ( 47 a ) passed via heat exchangers with heat transfer transfers via heat build-up / gravity drains in the chambers and in the further shrinkage partial heat cycle via heat exchangers in the lowered temperature level into the water in the large-capacity tank ( 4 ) and / or flowing through the expansion tank ( 41 ) , the ammonia da mpf condensed again in the heat-giving shrinkage process and the working medium ammonia with predetermined pressure in the condensate-working medium-collecting container ( 51 ) here via the heat exchanger ( 124 ) and / or ( 45 ) shrinking sub-circuit assigned in the minus area, heat removed and the liquefied Working medium via pump ( 52 ) and feed line via switching valve ( 78 ) metered as required, which is fed back into the heat-power cycle. 7. The method according to claim 1 to 6, characterized in that in the Großraumkammerkam mer ( 5 ), in the associated liquid, which preferably consists of low-oxygen water, with heat, via height-offset in the liquid arranged heat exchanger ( 70 ) ( 69 ) Heat from solar collector ( 230 ) or waste heat z. B. from a heat-emitting heat source z. B. ( 43 ) ( 30 ) and heat extraction and heat retransmission processes via ( 68 ) in conjunction with hot water and / or heating system ( 233 ) and heat exchanger-heat exchanger wall ( 169 ) ( 160 ) ( 170 ) in connection with heat pump heat transfer circuit and Heat exchanger wall ( 72 ) ( 165 ) ( 71 ) of the water column container chamber in the water of the large-capacity container ( 5 ) with and over the circuit guides of the assigned or in the heat flow level raising and / or lowering heat force z. B. ( 55 ) ( 96 ) and / or heat transfer circuits ( 25 ) ( 160 ) via assigned heat exchangers ( 37 ) ( 158 ), at least partially with heat buoyancy / gravity-conducting wall shaft ( 152 ) or heat exchanger jacket ( 96 ) with appropriate flow distance and openings ( 153 ) for the heat conduction lift / gravity for temperature level stratification in and out of the water filling of the container chamber ( 5 ), with heat transfer processes from the different temperature level areas of the container chamber ( 5 ), in the chambers ( 50 ) ( 49 ) or ( 161 ) ( 162 ) ( 163 ) carrying water columns and working medium are fed into the assigned liquid working medium with heat feed into the respectively assigned boiling temperature level range ( 166 ) via wall ( 165 ) and fins ( 72 ) and heat is withdrawn from the container chamber ( 5 ), in the further heat and transition from the liquid to the gaseous state, in which the working medium is conducted the respective WK circuit ( 46 ) ( 120 ) ( 128 ) or the steam-carrying subcircuit, after the work medium has been used via the WK machine, the working medium at least partially heat via heat exchanger ( 158 ) ( 37 ) and / or container wall ( 165 ) is returned to the water in the large-capacity container ( 5 ) and stratified heat is returned from the working groups. 8. The method according to claim 1 to 7, characterized in that heat from the water in the large space container ( 4 ) corresponding to the different temperature level stratification in this from the upper region to the lower container region ( 4 ) from the water in this via heat exchanger wall in the one above the other from the upper to the lower area arranged in self-contained water columns working medium container chambers ( 161 ) ( 162 ) ( 163 ) with the temperature level, as in the heat stratification in container ( 4 ) makes it possible in the respective boiling range of the working medium container chambers to be fed into the working medium in the working medium the liquid working medium in this continuously in the gaseous state in the heat-power expansion partial circuit continues to heat at least partially out of the water in the container ( 4 ) to take up, work-effective via heat-power machine ( 62 ) ( 200 ), guided by this leading shrinkage rates in the respective working medium Ilkreis pressed, retransferring this heat and forwarding via heat exchanger and water-heat-buoyancy gravity processes in and through the respective assigned water columns of the chamber areas controlled with heat-retransfer processes and with heat and working medium transfer in at least partially condensed state, of which in Upper water area of the container chamber ( 4 ) arranged circuit boiling area, from this with the highest temperature level heat feed and pressure level having heat and power working circuit management ( 120 ) with working medium and heat transfer after work, to the downstream WK working group ( 125 ) via this assigned thermal power -Circle with reduced temperature and pressure level as well as further heat absorption with transfer into this and transmission of this when heat is absorbed from the water in the central region of the large-volume container ( 4 ) with a corresponding heat temperature level, the work eitsmedium in the circuit ( 125 ) and according to the heat level and the corresponding lower pressure level after work and subsequent heat retransmission processes via the water / gravity processes in and over the own water column area as well as heat and working medium transfer to the working medium container ( 163 ) Heat exchange in the lower water area of the container chamber ( 4 ), heat-absorbing arranged heat-power circuit ( 128 ) and in this via working medium evaporation processes and further heat supply into the steam in the expansion sub-circuit ( 130 ) with working cycle management via heat engine ( 62 ) ( 200 ) conveys the working medium into the associated shrinking circuit ( 129 ), via this and via heat exchanger ( 169 ) and / or ( 158 ) heat into the water of the container ( 4 ) and via the further circuit via heat exchanger ( 171 ) ( 172 ) and ( 45 ), heat from the heat Force-shrinking pitch circle in the compressed gas expansion cooling pitch circuit, and in the further line management the condensed working medium preferably ammonia in and out of the condensate collector ( 51 ) via pump ( 52 ) and feed line routing ( 111 ) controlled by switching valve ( 116 ) and again via the heat exchanger ( 173 ) absorbing water from the container ( 4 ), the working medium absorbing further heat in the liquid state, into the liquid column chamber region ( 165 ), flowing through it, controlled according to the quantity required, the circuit ( 128 ) working medium to which from the preceding circuit ( 125 ) or via this from the circuit ( 128 ) transferred to ammonia, fed and the circuit ( 120 ) continuously from these from the upper water columns and working medium container chamber ( 161 ) continuously after work input derived working medium Pump ( 52 ) and line routing ( 145 ) with heat absorption from container Elder ( 4 ) signaled via heat exchanger ( 173 ) as required via contact transmitter ( 154 ), fed via assigned switching valves in the line routing ( 111 ) ( 116 ) or ( 145 ) controlled by the switching center ( 1 ) according to program sequences, the working medium in Circulation routing guided and returned, continuously absorbing heat with different heat levels in the cycle, releasing and partially returning repeatedly expanded and shrinking controlled, multiple work effective from a high low temperature level to a programmed minus range via coupled circuits continuously used in a work-effective manner. 9. The method according to any one of the preceding claims, characterized in that in a compressed gas intermediate store ( 38 ) from a gas with high pressure preference as compressed air or nitrogen as the working medium lead the thermal power heat transfer medium ( 25 ) and heat pump working circuit with compressor part circular guide (26) and for drinks-voltage part circular guide (27) and shrinkage of the pitch circle (27) receiving with programmed heat and donating recycling, the compressed gas after heat release latched via line guide (27) from the latch (38) through heat exchanger (123) (41 ) ( 42 ) as well as heat-absorbing and partially heat-dissipated guided with multi-way circuit ( 176 ) controlled in and through the compact flow and piston engine ( 200 ) ( 39 ), via this work-effective with controlled pressure reduction via pressure regulator flow valve ( 40 ) the compressed gas with a substantial, pressure-reducing a minus temperature level e generating relaxation, passed into and through the expansion tank ( 41 ), in this case via heat exchanger wall ( 45 ) ( 45 a) ( 45 b) in this from at least one thermal power working group ( 46 ) ( 128 ) or the associated shrinkage partial circular course ( 47 ) ( 129 ) extracting heat, storing in the compressed gas, in the compressed gas transmission with further heat absorption via heat exchangers ( 42 ) from at least one heat carrier circuit ( 160 ) and / or ( 175 ) the compressed gas with low-temperature waste and / or environmental heat increasing heat level curve, compressed via multi-stage compressors ( 43 ) to a programmed pressure level, thereby compressing heat with a high heat level partly fed into an intermediate heat store ( 44 ), from which sem partly directly into the WK working groups ( 55 ) or via heat exchangers in the container chamber ( 34 ) ( 32 ) and partly in the continuing compressed gas expansion partial circuit ( 26 ) via a circuit guide tion and flow and piston engine ( 200 ) ( 28 ) and when heat source ( 30 ) or ( 155 ) is assigned, heat is then carried through it, raising the compressed gas heat level to a pre-programmed level, via heat engine ( 28 ) ( 200 ) directed to work, from this in the compressed gas shrinking part circle ( 26 ) pressed in shrinking part circle guide via heat exchanger ( 24 ) ( 20 ) and / or control and bypass device ( 31 ) via heat exchanger ( 32 ) ( 33 ) heat in the The respective assigned working medium water / water vapor or ammonia / steam and via the heat exchangers or heat exchanger tanks ( 135 ) ( 136 ) or ( 137 ) arranged in the heat-transferring compressed gas course partially emitting heat into the tank ( 4 ), the compressed gas giving off heat shrinking with a reduced temperature level in the shrinkage part of the circuit is guided, further giving off heat at an almost constant pressure level i n the compressed gas intermediate storage ( 38 ) returned and continuously controlled by this with the circuit guide ( 25 ) and associated expansion ( 26 ) compressor expansion ( 27 ) and shrinkage partial circuit guide ( 26 ) heat transfer and work effective according to the program specification is directed. 10. The method according to any one of the preceding claims, characterized in that one or more boiling temperature ranges, the WK working groups ( 13 ) ( 13 a) ( 12 ) ( 12 a) ( 11 ) ( 11 a) or ( 102 ) ( 102 a) ( 105 ) ( 105 a) ( 108 ) ( 108 a) are assigned, the gaseous working medium / steam flows out of them via the expansion sub-circuit guides assigned to the respective WK-Ar working circuit into the compact heat exchanger ( 20 ), the working medium medium from the WK working circuit ( 13 ) or ( 102 ) receiving the highest pressure level via the inflow line with opening ( 177 ) ( 177 a) into the heat exchanger chamber area ( 180 ), the working medium with the mean pressure level in the WK -Working group ( 12 ) or ( 105 ) via a flow lines with an opening ( 178 ) ( 178 a) in the centrally arranged heat exchanger chamber area ( 181 ) and the working medium with the lowest temperature and pressure level from the WK working group ( 11 ) or ( 108 ) in the outer Ren heat exchanger chamber area ( 182 ) flowing in the floor area in each chamber area, the flowing working medium vapor from the floor area to the ceiling area via the heat exchanger ( 183 ) ( 184 ) ( 185 ) arranged in the chamber area, absorbing heat, from the heat exchanger chambers, the steam with increased heat level via the respective outflow openings and line guides ( 186 ) to ( 188 a) is continuously passed on to work, with the ongoing heat feed into the working medium steam via the heat exchanger ( 183 ) ( 184 ) ( 185 ) leading from the compressed gas Working group ( 25 ) or compressed gas shrinkage circuit with inflow via line connection ( 27 ) and after heat emitting by flowing the compact heat exchanger ( 20 ) via the shrinking circuit section line connection ( 27 a) the compressed gas is passed on at a reduced temperature level, the temperature-reducing heat exchanger course major ch the compact heat exchanger ( 20 ) via the flow profile distributors ( 189 ) ( 190 ) ( 191 ) controlled in the closed pressure gas guide path first heat via heat exchanger ( 183 ) in the chamber area ( 180 ) in the steam circuit ( 13 ) or ( 102 ) in following via heat exchanger ( 184 ) in the chamber area ( 181 ) to the steam supply circuit ( 12 ) or ( 105 ) and in the following section via heat exchanger ( 185 ) in the chamber area ( 182 ) to the steam-carrying work cycle ( 11 ) or ( 108 ) transferred, the compressed gas continuously from the engine ( 28 ) giving off heat from the ceiling area to the floor area through the compact heat exchanger ( 20 ) and via a conduit from the shrinkage circuit ( 27 ) to the compressed gas buffer ( 38 ) and the working medium Steam running from the WK cycle boiling areas into the compact heat exchanger ( 20 ) and in the opposite direction, heat absorbing to the heat e emitting compressed gas controlled flowing through the heat exchanger chamber and conveyed from and guided by this to the heat engine. 11. The method according to any one of the preceding claims, characterized in that a pressurized gas, preferably nitrogen or compressed air from a pressurized gas-conducting working circuit ( 25 ) partial circuit ( 27 ) via pressure gas flow controller ( 40 ) and flow course-Untertei ler ( 189 ) controlled, from an engine ( 200 ) ( 28 ) after work via the line ( 27 ) into the chambers ( 182 ) ( 181 ) ( 180 ) of the expansion tank ( 41 ), with large pressure drop through the inflow opening ( 194 ), the chambers through the Flow regulator ( 192 ) ( 193 ) from the bottom area of the outer chamber ( 182 ) to the ceiling area, the middle chamber ( 181 ) from the ceiling area to the floor area and the inner chamber ( 180 ) from the floor area to the ceiling area and further via the outflow openings ( 195 ) and subcircuit ( 26 ) passed on, the compressed gas with flow through the expansion tank ( 41 ) over the expansion and thus v tied lowering of the temperature level, from which gaseous working medium dissipates heat via the supply part-circle connection ( 46 ) ( 128 ) and line routing through the chambers ( 182 ) ( 181 ) ( 180 ) in the expansion tank via the heat exchanger ( 185 ) ( 184 ) ( 183 ) and condensed, the working medium shrunk to condensate via the work circuit circuit ( 127 ) in the thermal power circuit to a collection container and the expanded compressed gas via line ( 26 ) in the heat transfer heat pump circuit, to a compressor ( 43 ) . 12. The method according to any one of the preceding claims, characterized in that in and from a, as a piston and fluid power machine combination ( 200 ), one or more, a gaseous working medium preferably steam leading WK working group, and at least one of a compressed gas preferably nitrogen-carrying WK compressor and expansion Ar work circle, effective for the engine, as a working medium steam and / or compressed gas with high pressure and / or temperature level via line connection in one or more engine piston devices ( 21 ) ( 28 ) when the pressure flows in, it acts in a cycle on a movable room divider or piston side / 201 ), so that on the opposite side ( 202 ) the working medium is squeezed out and shrinking over line connection and subsequent heat-releasing line routing in certain time sequences generating the pressure difference and correspondingly Difference in pressure e Power delivery partly as a working medium, and the power difference via the gear ratio and power forwarding device ( 203 ) and ( 204 ) to the central power delivery accessories ( 22 ) and ( 29 ) and via this with further power supply via turbo machines -Device ( 205 ) ( 206 ) ( 207 ) ( 208 ) of the compressed gas compressor device ( 43 ) to drive power and the moreover available to another work performance, in particular for power in electrical energy conversion is derived. 13. The method according to any one of the preceding claims, characterized in that controlled via line connection and multi-way switching valve ( 176 ), the working medium compressed gas in a cycle times in the chamber ( 39 ) times in the chamber ( 39 a) and gaseous from a compressed gas working circuit Working medium z. B. steam in the cycle in the chambers ( 62 ) ( 62 a) of the multi-purpose engine combination ( 200 ) flows, with inflow of compressed gas z. B. in the chamber ( 39 a), the liquid, preferably oxygen-poor water, in this displaced via conduit ( 217 ) leads to the flow machine device ( 214 ) ge, the flow machine device flowing through work, via directional control valve assignment ( 212 ) rotating in the same direction, conveyed via the cycle path in the chamber ( 39 ) and simultaneously with the inflow of the working medium steam via reusable switching valve ( 210 ) times into the chamber ( 62 ) times into the chamber ( 62 a), the liquid in and from these, via line ( 219 ) and in the cycle via line ( 220 ) and from the fluid machine device ( 213 ) in a work-effective, pressed manner, the steam also working medium alternatingly via multi-way switching valves ( 210 ) each from the container chamber with inflows of liquid through this with steam pressure from the opposite side te pressed out via line connection ( 109 ) or ( 97 ) z around shrinking partial circuit ( 47 ) via heat exchanger ( 175 ) ( 171 ) and for condensation with heat emission to the compressed gas circuit in and through the expansion tank ( 41 ) Fig. 5, the work-effective pressure difference in the steam circuit corresponding to heat absorption and heat output generated with Thermal power conversion processes passed on, the compressed gas from the chamber ( 39 ) and via multi-way circuit ( 176 ) and line ( 217 ) ( 219 ) in and through the fluid machine device ( 213 ) driving the se work effectively, the compressed gas with increased pressure drop over controlled the flow controller ( 40 ) and on the connecting line, passed into the expansion tank ( 41 ) Fig. 5, and the cyclic compressed gas supply and discharge processes with the corresponding cyclic liquid displacement and return into and out of the chambers ( 39 ) ( 39 a) and related liquid level changes in the cycle in the chambers, the float devices n ( 225 ) into this, sometimes lifting, sometimes lowering, with the effect of gravity and force transmission processes via device ( 221 ) and translating force-transmitting device ( 204 ) controlling and transferring a portion of force, and with the associated isolated floating balls, the liquid surface towards the gaseous working medium, causes heat delimitation, and via the cyclical liquid movements with flows through the heat exchangers ( 175 ) ( 171 ) controlled by multi-way switching valve ( 209 ) and level tester contact ( 224 ) as well as in the subsequent compressed gas flow and steam condensation course after multiple work-effective use, heat circulating from gaseous working medium steam is transferred directly or indirectly to the pressure gas-carrying working group, is passed on. 14. The method according to any one of the preceding claims, characterized in that a gaseous Arbeitsme medium, preferably steam, with the predetermined assigned temperature and pressure level, via multi-way switching device ( 210 ) and thermal power partial circuit line connection ( 47 ) or ( 109 ) in the cycle in and out of the chambers ( 62 ) ( 62 a) of the multi-purpose engine combination ( 200 ) with inflows, the steam controlled times from the pitch circle ( 109 ) times from with pitch circle ( 47 ) the liquid in the presses the respective chamber acted upon with the steam, presses the liquid into the chamber connected in a work-effective manner, through the liquid the working medium steam pressurized in it via a multipurpose switching valve ( 219 ) controlled by the connecting circuit ( 109 ) or ( 47 ) due to the shrinkage -Teilkreis and by the associated heat exchanger ( 230 ) and ( 171 ) controlled by flow regulator and bypass switch valve ( 229 ) Heat in the liquid, in the chambers ( 62 ) ( 62 a) ( 39 ) ( 39 a) with programmed demand transfer via heat exchanger flow control, the steam condenses with more or less pressure reduction in the shrinking sub-circuit, the pressure difference - and flow-through sequences with heat-transferring temperature levels in the liquid and the chambers ( 62 ) ( 62 a) and ( 39 ) ( 39 a) with a programmed minimum level in the respective engine area via controlled steam supply via ( 210 ) from at least temporarily different heat and Pressure level steam leading expansion sub-circuits ( 109 ) and ( 47 ) or ( 50 ) as well as with force coupling of float-buoyancy-gravity cycle and mechanically ( 203 ) ( 221 ) ( 226 ) ( 22 ) as well as pneumatically and / or hydraulically coupled conversions and translations ( 146 ) ( 148 ) ( 215 ) ( 147 ) ( 149 ) ( 219 ) and forwarding power transmission processes, according to power and heat demand controls, from the thermal power ( 102 ) ( 109 ) ( 47 ) ( 28 ) and heat pump ( 43 ) ( 49 ) ( 25 ) working circuit guides ( 28 ) ( 126 ) (coupled to the multi-purpose engine ( 200 )). 29 ) ( 22 ). 15. An apparatus for performing the method according to claim 1 to 14, characterized in that an energy productivity increase heat to power conversion plant, a work circuit-working medium heat and power supply transmission-transfer-circuit coupling, one or more large-capacity containers ( 4 ) with intermediate storage heat-carrier liquid filling in the chamber area ( 5 ) as well as wholly or partially in this self-contained liquid columns and working medium container chambers ( 54 ) ( 49 ) and / or ( 161 ) ( 162 ) ( 163 ) and / or Water column and steam chamber device ( 6 ) ( 7 ) with line connection of the working medium leading expansion subcircuits and routing of the WK working circuits inside and outside of the chamber area ( 5 ) with one or more heat exchangers ( 20 ) and / or ( 136 ) ( 135 ) ( 90 ) ( 91 ) in the respective thermal power cycle to the associated WK machine device ( 39-39 a) ( 62-62 a) u nd / or ( 21 ) ( 28 ), with arranged switch-reusable line control device in the line guides and connection circuit connection of working medium shrinkage circuit connection of the WK circuits, from the engine combination ( 200 ) with heat exchange as well as level testers and Contact sensor assignment, in the liquid filling and the engine device ( 39-39 a) ( 62-62 a) as well as in the large-volume container chamber area ( 5 ) as well as in the respective liquid columns and working medium chambers and in the WK cycles arranged working media intermediate storage ( 34 ) and / or ( 51 ) with control and line connections ( 236 ) of the contactors, pumps and control switching devices to and from the switching center ( 1 ) when assigning at least one heat source connection ( 232 ), ( 30 ), and / or heat pumps ( 43 ) with assignment expansion tank ( 41 ) and heat exchanger integration with heat transfer thermal power W heat pump circuit ( 25 ) as well as heat transfer medium heat exchanger ( 160 ) ( 42 ) ( 68 ) ( 169 ) integration and pump-compressor-engine-power transmission accessory assignments ( 22 ) ( 23 ) ( 212-216 ) and / or ( 21 ) ( 28 ) ( 146 ) ( 197 ). 16. Devices for carrying out the method according to claim 15, characterized in that a liquid column and working medium container or water column and steam chamber container ( 54 ) ( 49 ) ( 161 ) ( 162 ) ( 8-10 ) at least one column-like tubular container chamber part with arranged liquid filling, preferably oxygen-poor water with arranged level tester ( 81 ) ( 98 ) ( 154 ) and above the water filling in the level range - also called water level and / or boiling range ( 74 ) ( 72 ) ( 97 ) - a working medium steam chamber area ( 71 ) ( 161-162 ) ( 166 ) with classified working medium filling, liquid and gaseous or steam, at high temperature leading WK working cycles ( 13 ) ( 12 ) ( 11 ) water-water vapor and in medium and / or low temperature leading WK -Working circuits ( 54 ) ( 46 ) or ( 102-108 ) and ( 120-128 ) a liquid-gaseous working medium, preferably an ammonia liquid-steam filling in the Water column-steam chamber container above the water column level with one or more working working circles, which protrude into the steam chamber area and are sealed by the wall of the container, with line inlet or outlet openings ( 77 ) ( 131-139 ) ( 84 ) ( 99 ) assigned in the chamber area Backflow preventer ( 144 ) ( 143 ) ( 119 ) and / or through flow control device ( 65 ) ( 145 ) ( 76 ) ( 156 ) or in an outwardly looped line with switching valve assignment as well as heat exchanger in the shrinking partial circuit guides in the water column area in Assignment with lead-through and line routing through the water column chamber container with a classification of cross-sectional change-pipe constriction ( 76 ) ( 140-142 ) in the heat exchanger ( 132 ) ( 157 ) ( 137 ) ( 139 ) and water column lead-through shrinkage partial circle guides vertical room divider wall ( 152 ) the column-like tube container chamber part and / or around the heat exchanger e shaft-like casing ( 96 ) with vertically offset inflow-outflow-gravity guide openings ( 153 ). 17. The device for carrying out the method according to claim 15 to 16, characterized in that a WK working group ( 46 ) and / or ( 58 ) and ( 55 ) with a circuit-dividing arrangement in expansion part circle guide ( 48 ) and shrinking part circle ( 47 ) to the working group ( 46 ) and and expansion part circle ( 60 ) and shrinkage part circle ( 61 ) to the circuit ( 58 ) and expansion part circle ( 56 ) and shrinkage part circle ( 57 ) to the circuit ( 55 ) with each arranged in the subdivided assignment a water column and working medium loading container chamber ( 49 ) to the circuit ( 46 ), working medium container chamber ( 50 ) to the circuit ( 58 ) and working medium container chamber ( 54 ) to the circuit ( 55 ) with line management of the expansion subcircuit with connection of working media container chambers to the WK machine device ( 62-62 a) and returning from this line ti connection of the shrinkage partial circuit to the water columns working medium container, where in the line management switching devices, as well as heat exchanger with direct heat exchanger connection in the surrounding water area and heat exchanger with chamber and heat transfer circuit connection assignments. 18. Devices for carrying out the method according to one of the preceding claims, characterized in that a water column and steam chamber container ( 54 ) has a pipe register steam chamber container with lamella assignment as the upper part and a pipe container / water column chamber lower part with partial insulating wall ( 73 ) and around Heat exchanger pipe register area a chamber ( 86 ) forming this enclosing chamber with water vapor heat transfer line connection ( 87 ) to and from the water / steam tank ( 34 ) and circuit closing condensation water return line ( 88 ) with connection to working medium pump connecting line ( 111 ) , having. 19. Devices for performing the method according to one of the preceding claims, characterized in that water columns working medium container chamber ( 161 ) ( 162 ) ( 153 ) ( 49 ) ( 50 ) ( 54 ) heat exchanger wall areas ( 71 ) ( 72 ) ( 165 ) and insulated partial wall areas ( 73 ) and line connections with an inflow or outflow opening ( 76 ) ( 71 ) ( 77 ) ( 131 ) in the water column and / or working medium chamber area and circuit line connections from these to and from a working medium collecting container ( 51 ) and Circuit line connection to and from device connections ( 47 ) ( 102 ) ( 110 ) ( 210 ) of a heat engine ( 200 ) and line connection with heat exchanger ( 47 ) ( 91 ) ( 158 ) ( 173 ) in heat exchange integration in the water in Container chamber ( 5 ) and heat exchanger ( 157 ) ( 79 ) ( 139 ) ( 137 ) with heat exchange integration in the water of the water column working media container chambers in the circuit guides. 20. Devices for carrying out the method according to one of the preceding claims, characterized in that water column working medium container chambers in the water filling a container chamber ( 5 ), an offset arrangement, with different heights from working medium chamber ( 161 ) to ( 162 ) and from this to ( 163 ) and / or from working medium chamber ( 54 ) to working medium chamber ( 49 ) ( 50 ), with shrinkage circuit of the WK working circuit ( 120 ) or ( 55 ), through the water in the water column chamber area ( 161 ) or . ( 54 ) with cable routing from these, into the water column container chambers ( 162 ) or ( 49 ) or ( 50 ) and the shrinkage partial circuit from the WK working circuit ( 125 ) through the water column container chamber ( 162 ) and the shrinkage - Partial circuit routing from the WK circuit ( 46 ) or ( 55 ) through the water column container chamber ( 49 ) or ( 50 ) and from this the forwarding line routing into and through the downstream En container chambers ( 161 ) and / or heat exchanger expansion tank ( 41 ) and line connection from this to the working medium collecting container ( 51 ) and from this a circuit connection with connection to working medium container chambers ( 161-163 ) or ( 54 ) with additional working medium guide -Leitungsver connection with changeover valve ( 65 ) connection connection from the container chamber ( 54 ) to the container chamber ( 49 ) or ( 50 ). 21. Devices for carrying out the method according to any one of the preceding claims, characterized in that a plurality of encapsulated water columns working media chambers ( 8 ) ( 9 ) ( 10 ), each with thermo pen insulating wall, nested as a water column steam chamber device ( 6 ) or ( 7 ), with each water column and working media chamber assigned WK circuit, z. B. WK circuit ( 13 ) to the water column chamber area ( 10 ), WK circuit ( 12 ) to the water column chamber area ( 9 ) and WK circuit ( 11 ) to the water column chamber area ( 8 ), each with associated WK Circuit subdivision into expansion sub-circuit and shrinkage sub-circuit with connection of the sub-circuits to heat engine ( 200 ), as well as heat exchanger assignment in the sub-circuits with heat transfer connection ( 135 ) ( 136 ), or circuit heat transfer ( 25 ) connection from and to one Heat source ( 46 ) and / or ( 30 ) as well as compact heat exchanger ( 20 ) and heat circuit integration management of expansion partial circuits ( 18 ) ( 16 ) ( 14 ) or ( 104 ) ( 106 ) ( 110 ) and routing of these with partial shrink circuits z. B. from the circuit ( 13 ) or ( 102 ) through the chamber area ( 10 ) to the chamber area ( 9 ) via the circuit shrinkage cycle from the WK circuit ( 12 ) or ( 105 ) through the chamber area ( 9 ) to the chamber area ( 8 ) and via a circuit from the chamber area ( 8 ) to the water-water vapor container ( 34 ), or in the case of ammonia working medium circuit management, expansion tank ( 41 ) heat exchanger arrangement and line connection in the collecting container ( 51 ). 22. Devices for performing the method according to any one of the preceding claims, characterized in that water columns and Dampfkam mer device ( 6 ) ( 7 ) to the arranged container chambers ( 8 ) ( 9 ) ( 10 ), heat-gravity circuit conduit with arranged heat exchangers ( 150 ) in the chamber areas ( 8-10 ) with heat exchanger water-gravity inflow and outflow opening assignment in the water level area of the subsequent water column working medium chamber tank from ( 10 ) to ( 9 ) and ( 9 ) to ( 8 ) and heat exchanger wall sections ( 165 ) in the insulated outer jacket area of the water column chamber container ( 8 ) with chamber-forming pipe or jacket assignment ( 152 ) and this water vapor line connection ( 87 ) connected to the upper area to the heat exchanger ( 83 ) and Kondenzrück flow line ( 167 ) ( 88 ) from this, also heat transfer circularly working medium-heat transfer medium shrink Fungkreiskreis connection with flow controller device ( 145 ) and line routing in and out of what water steam tank ( 34 ) and line connection of this with pump arrangement and switching valves in the line routing ( 111 ) with branch line ( 113 ) in the chamber area ( 10 ) and Cable routing ( 114 ) in the chamber area ( 9 ) and cable routing ( 115 ) in the chamber area ( 8 ), also level tester contactor and working medium-heat carrier-WK working circuit with heat exchanger arrangement in the water column-Ar working medium chamber areas ( 8-10 ) with water-heat-buoyancy gravity leading shaft allocation to the shrinking pitch circle through the water column chamber areas, as well as heat-water-gravity cycle allocation ( 150 ) from chamber area ( 10 ) to ( 9 ) from ( 9 ) to chamber area ( 8 ) , Has. 23. Devices for carrying out the method according to one of the preceding claims, characterized in that the expansion working part circuits and the shrinking working part circuits of several WK working circuits ( 120 ) ( 125 ) ( 128 ) these per working group at least one connection of the expansion s Pitch circle to a water column and working media chamber ( 161-163 ) ( Fig. 8) with line connection of the expansion partial circuit guides and assignment of at least one heat exchanger ( 135-137 ) arranged in liquid filling in a large-capacity container chamber ( 5 ) with each of the expansion Partial circuit guides, as well as forwarding line connection via switching device ( 210 ) with coupled connection ( 220 ) from switching valve ( 210 ) to switching valve ( 209 ) via this with the shrinking partial circuit guides, and from switching valve ( 210 ) into the engine chamber devices ( 62 ) and ( 62 a) via protruding and protruding line Guides with associated inflow and outflow opening ( 151 ) also near the bottom area in the chambers ( 62 ) and ( 62 a), inflow and outflow openings ( 77 ) in line routing ( 217 ) ( 218 ) with connection via this to a piston or turbomachine device ( 215 ) of an engine combination ( 200 ), moreover via line connections from switching valve ( 209 ), shrinkage working circuit connections of the WK working groups through and in respective assigned water column working medium chambers ( 161 ) ( 162 ) ( 163 ) , In the shrinkage circuit connection assignment a working medium feed connection to the working medium collecting container ter ( 51 ) with line routing through the heat exchanger chamber area ( 41 ) and / or ( 44 ) in the heat exchanger assignment a heat transfer line connection coupling a heat transfer medium circuit ( 25 ) and / or ( 160 ) also a shrinkage partial circuit (heat exchanger chamber areas ( 41 )) 129 ) with line routing with valve assignment ( 76 ) into and out of the working medium collecting container ( 51 ) via flow control device ( 145 ) and pumps ( 52 ) with feed line routing ( 111 ) ( 115 ), each with a connection assignment in the water column working medium chambers ( 161 ) ( 162 ) ( 163 ). 24. Devices for carrying out the method according to one of the preceding claims, characterized in that a water column working medium container device ( 161 ) a closed at the foot end of the tubular body with partially insulated wall ( 73 ) and partial heat exchanger wall ( 65 ) with applied tem Firmly connected, extended head section, preferably in the form of a tube register with heat exchanger fins ( 72 ), where the tubular body with the head section forms a closed chamber with assignment of several line connections to a WK circuit, including feed and level contactors ( 81 ) ( 154 ) ( 82 ) Line connection connection, whereby a shrinkage partial line routing with assigned heat exchangers ( 139 ) ( 157 ) ( 79 ) from the WK shrinkage pitch circle in the water column chamber area separates these into water-gravity buoyancy and case separating chamber area subdivision ( 152 ) with upper and lower flow opening ( 96 ) ( 153 ) as well as height replaced in the wall associated inflow or outflow openings ( 153 ) likewise a heat-boosting pipe jacket ( 96 ) with throughflow openings on the outside around the tubular water column chamber area with lamella assignment. 25. Devices for carrying out the method according to one of the preceding claims, characterized in that a compact heat exchanger ( 20 ) ( Fig. 4) a plurality of nested, closed, all around provided with insulating wall chamber areas che ( 182 ) ( 181 ) ( 180 ) forming, tube-like container with supply connection ( 27 ) and heat transfer pipe routing from the inner chamber area ( 180 ) to the outer chamber area ( 182 ) with heat exchanger wall surfaces and solid mass assignment ( 183 ) for pipe routing ( 27 ) through the chamber areas and discharge connection ( 27 a) from the outer chamber area ( 182 ) with level tester contactor arrangement in the chambers as well as inlet ( 177 ) and discharge ( 186 ) connection with at least one WK expansion subcircuit working medium steam duct in and out of the chamber area ( 180 ), as well as inlet ( 178 ) and outlet connection ( 187 ) with at least one WK expansion part-circle steam guide in and out of de r chamber ( 181 ) and inlet ( 179 ) and outlet ( 188 ) connection with at least one WK expansion subcircuit steam duct in and out of the chamber region ( 182 ), the duct routing outside of the chamber region insulating walls ( 73 ) , Has. 26. Devices for carrying out the method according to any one of the preceding claims, characterized in that a compressed gas expansion container ( 41 ) ( Fig. 5) a plurality of nested, ge closed tube container with at least the outer tube container and the working medium supply and discharge duct insulated Wall and in the chamber areas ( 180-183 ) heat exchanger wall surfaces and solid mass allocation ( 183-185 ) to the working medium-ammonia heat exchanger line guide ( 46 ) ( 128 ) ( 108 ) of one or more coupled WK shrinkage partial circular guides with ge closed line routing in, through and out of the chamber areas, from the outer ( 182 ) to the inner chamber area ( 180 ) with a further line connection ( 127 ) as well as supply line connection ( 196 a) ( 25-27 ) with compressed gas connection ( 194 ) to the outer chamber area ( 182 ) and flow connection with backflow protection assignment to the chamber area ( 181 ) and flow ömverbin extension ( 193 ) of these to the chamber area ( 180 ) and from line connection ( 25-26 ) from this, same level tester in the chamber area with contactor connection ( 199 ). 27. Devices for carrying out the method according to one of the preceding claims, characterized in that line connections ( 102 ) ( 110 ) ( 47 ) ( 56 ) of a plurality of WK working circuits, the same line connection ( 27 ) of at least one pressurized gas heat carrier and thermal power Compressor heat pump working group ( 25 ) with control switching valve and connection to thermal power machine device assignments ( 21 ) ( 28 ) or ( 62-62 a) and ( 39-39 a) of an engine combination ( 200 ) ( Fig. 6 ) with power transmission connection ( 22 ) ( 29 ) ( 213 ) ( 214 ) and connection to the compressor heat pump ( 44 ), with associated heat transfer connections and heat exchangers ( 44 ), the machine-device assignment ( 62 ) and ( 62 a) the same ( 39 ) and ( 39 a) in each case two ge with pipe connections coupled tubular or cylindrical closed container chambers arranged directly or indirectly via pipe connections above it e piston and / or flow engine and force-transmitting devices, the individual liquid - preferably water-carrying chambers ( 62-62 a) ( 39-39 a), with float ( 225 ) and / or float ball ( 100 ) in the chambers, dividing this lower container chamber area, which leads in water or liquid, and gaseous working medium, dividing the upper chamber area, with level contactors ( 224 ) in the chamber areas and line connections ( 217-218 ) of the chambers ( 62-62 a) with the chamber areas connected flow engine device ( 215 ) and line connections ( 217-219 ) of the chambers ( 39-39 a) with engine device ( 214 ) and the compressed gas line connection ( 27 ) via control switching device ( 176 ) with line connection via this to the compressed gas chamber areas ( 39 ) and ( 39 a) with line guidance in a flow or piston engine machine ( 213 ) with this Pressurized gas forwarding connection ( 27 ) through flow controller ( 40 ) and branch line assignment ( 196 ) with connection connection of compressed gas working group ( 25 ) leading lines, have. 28. Devices for carrying out the method according to any one of the preceding claims, characterized in that a pressurized gas - preferably nitrogen - as the working medium leading working circuit ( 25 ) in a circuit piping an expansion-WK working section ( 26 ) with connection to heat pump / Ver denser ( 46 ) and routing of this with heat exchanger assignment ( 44 ) ( 169 ) with control device arrangement ( 40 ) ( 27 ) with direct line connection or indirect via heat transfer circuit to one or more heat sources, e.g. B. solar collector ( 232 ) and / or high-temperature heat accumulator ( 30 ) and / or heating source ( 155 ) and expansion partial circuit connection to Kraftmaschi NEN device ( 28 ) ( Fig. 1 / Fig. 6) and by this in the line path as shrinkage -Working part circuit guide ( 27 ) with compact heat exchanger ( 20 ) and / or heat exchanger ( 124 ) ( 36 ) ( 37 ) as well as compressed gas buffer store ( 38 ) with circuit-leading line ( 27 ) and compact heat engine connection ( 200 ) via Schaltvor direction ( 176 ) and from this continuing line with pressure regulator valve 40 and connection line with expansion tank ( 41 ) classification in the circuit management and heat exchanger assignment ( 171 ) ( 160 ) ( 44 ) with circuit line connection to the Verdichtervor direction ( 43 ). 29. Devices for carrying out the method according to any one of the preceding claims, characterized in that a large-capacity container ( 4 b) in the container chamber ( 5 ) stored heat transfer heat storage fluid, with in this height-displaced heat exchanger ( 79 ) ( 69 ) ( 68 ) ( 68 ) ( 159 ) with circuit-connecting line assignments ( 237 ) ( 236 ) to solar collector ( 232 ) as well as hot water and heating supply systems ( 233 ) and switching center ( 1 ) connection with arranged height-shifted level sensor contact ( 199 ) and from the liquid filling the container chamber ( 5 ) leading lines also vertically offset inflow and outflow openings in the container chamber ( 5 ) with cable guides ( 243-245 ) in and out of the container chamber with a multi-way circuit ( 239 ) and pump ( 238 ) and control line assigned outside the container chamber - Guide with integration of cable guides arranged in the chamber area ( 5 ) with over Cable routing ( 245 ) ( 237 ) WK circuit assignments in containers ( 4 ) and / or ( 4 a) in the circuit network coupled thermal power circuits with in the container chamber ( 5 ) of the container ( 4 b) arranged compact heat exchanger ( 20 ) and Expansion tank ( 41 ) and engine combination container devices ( 62 ) ( 62 a) and / or ( 39 ) ( 39 a) with line connection connections and assignment of control and safety valve filling and venting device ( 240 ) and line connection connections ( 245 ) to and from the compressor ( 43 ) and the heat exchanger ( 44 ) of the same engine, power-transmitting connection with a forwarding device assignment ( 22 ) ( 23 ) ( 212 ) ( 213 ) and thermal power-heat transfer circuit connections with heat sources ( 232 ) ( 30 ) and / or ( 55 ) with circuit couplings via switching valve assignments ( 239 ) ( 256 ).