DE102009025401A1 - Thermal drive device i.e. linear actuator, for use in thermodynamic compound engine, has generator for generating electrical energy from displacement of piston and/or compressor for compressing coolant by performing compression process - Google Patents

Abstract

The drive device (7) has a cylindrical chamber that is outwardly closed by a movable piston. An inlet device is provided at the chamber for inletting an expansion medium. A heat exchanging medium is provided in a region of the chamber for exchanging heat between an expansion medium and an energy carrying medium. A generator (7.3a) is provided for generating electrical energy from the displacement of a piston and/or a compressor (7.3b) is provided for compressing a coolant by performing a compression process. An independent claim is also included for a thermodynamic compound engine including a heat pump arrangement.

Description

The The present invention relates to a thermal drive device, preferably in the form of a linear drive, according to claim 1. A Such drive device generally serves to thermodynamic state changes to transform a working medium into mechanical work, and more for that Applications available stands, for example for power generation.

Farther the present invention relates to a thermodynamic composite machine, which according to the claim 14 at least one thermal according to the invention Drive device and a heat pump assembly includes. It is in the said compound machine so to the combination of a right-handed Circular process, that is an engine process with a left-handed cycle, that is, a work machine process.

By a heat pump assembly becomes a primary energy source, like Air or water, deprived of heat by means of a refrigerant and subsequently from the refrigerant delivered to a heating circuit. The refrigerant evaporates at least partially and then has to be re-compressed and liquefied become one (left-turn) Realize cycle process. For compressing the refrigerant come regularly electromechanical working compressors used, which disadvantageously have a relatively high power loss, which is the efficiency of the arrangement. The invention is based on the object to give a thermal drive device to which in particular the above-mentioned refrigerant compression with improved Efficiency, that is can be passed with less power dissipation. In addition, the invention is the task is based, a thermodynamic compound machine with a heat pump assembly and to provide a thermal drive device, which is also through an elevated Efficiency distinguishes.

The Invention solves the task by means of a thermal drive device with the Features of claim 1 and by means of a thermodynamic Composite machine with the features of claim 14.

preferred Further developments are each the subject of claims, whose Wording hereby expressly Reference is included in the description to unnecessary text repetitions to avoid.

According to the invention a thermal drive device, which preferably in the form of a Linear drive can be formed, at least one cylinder chamber, closed by at least one movable piston to the outside is and which at least with a first cycle for an expansion medium and with a second circuit for an energy carrier fluid communicates. In the drive device according to the invention on the cylinder chamber at least one inlet device for the expansion medium provided, and in the area of the cylinder chamber are first heat exchange means for one Heat exchange between the expansion medium and the energy carrier fluid present. It is the expansion medium according to the invention chosen such that it in the heat exchange expands with the energy carrier fluid which is relatively warmer during operation of the drive device, preferably by evaporation, and so the piston in the cylinder chamber shifts. The piston acts according to the invention in turn with at least a means to which he transfers work. In this means can it is at least one generator means for generating electrical energy from the displacement of the piston and / or by at least one compressor means for compressing a refrigerant to act under the power of compression work. The interaction can be mechanical or otherwise (hydraulic, pneumatic) done and runs preferably linear.

With in other words, through the heat exchange between energy carrier fluid and expansion medium in or on the cylinder chamber, it comes to a Expansion of the expansion medium, which acts on the piston and does mechanical work, for example, for generating electrical energy or for compressing a refrigerant, in particular for a heat pump arrangement, is usable. For expanding the expansion medium, preferably (Liquid) Carbon dioxide, this can be injected into the energy carrier fluid.

A composite thermal engine according to the invention comprises at least one thermal drive device according to the invention and a heat pump arrangement, preferably in the form of an air-water heat pump. The latter serves for at least partial heating of the energy carrier fluid for the thermal drive device and is in thermodynamic interaction with the thermal drive device via the second circuit, which means, for example, that the energy carrier fluid at least partially heated by the heat pump arrangement then heats the expansion medium in the thermal drive device and for the latter Expansion ensures, as already described above. The energy carrier fluid may be a thermal oil circulating in a dedicated power circuit. Alternatively, it is the Energieträ gerfluid to heating water from a building heating system.

To A core idea of the present invention is based on the Recognizing that to improve the efficiency of a thermodynamic Composite machine with a thermal drive device (heat engine) and a heat pump assembly also by heat extraction lowered potential of the primary Energy suppliers (eg ambient air or groundwater) can be used to repatriate the To ensure expansion medium in its compressed initial state or at least to support, because the said lowered potential is capable of producing energy to withdraw from the expansion medium. Therefore, a preferred looks Further development of the composite machine according to the invention suggest that these second heat exchange means for cooling down and liquefying of the expansion medium after expansion has, which on the one hand from the primary energy source for the heat pump assembly after the heat has been released to the refrigerant and on the other hand flowed through by the expansion medium, to the lowered temperature of the primary energy source for cooling the To use expansion medium.

on the other hand carries however already the circumstance according to the invention, that the proposed thermal drive device for compacting of the refrigerant under the performance of compression work by the expansion medium without electromechanical agents in the manner of a conventional compressor gets along, to the improved efficiency of both the inventive thermal Drive device as well as the thermodynamic based thereon Composite machine at.

A per se known heat pump (WP) using energy, usually in electrical form, creates a "potential" over which Thermal energy flow can. This potential is then used for heating or cooling. The amount of energy that is brought into flux exceeds that usual today WP systems, the amount of energy used by 3 to 4 times. The energy is from a medium - usually air or water as a primary energy source - at one transfer other medium, which is for example a refrigerant and / or heating water is. This changes the potential of the media as follows: the supplier medium, eg. B. Air, energy is withdrawn and its potential decreases ("minus" potential; Cooling capacity). The recipient medium energy is supplied and the potential increases ("plus" potential, heating power). The result is two potentials, which is a flow of heat energy can cause. A Potential shift in the range +3 is the same as for heat pumps regularly indicated coefficient of performance. However, this coefficient of performance does not name the entire potential but only for the purpose of the WP used page. The total potential consists of the withdrawal rate (at the energy supplier) and the compaction performance (at the energy receiver).

The Previous WP systems without the thermal drive device proposed here are for designed for winter heating purposes. The HP with thermal drive device in the form of a (linear) generator can also be operated in summer and produces over the year outside the heating months a significant amount of electrical energy. Outside In the heating season, the WP also uses air as an energy source much higher performance figures as a WP with other energy suppliers (eg water).

The Potential on the "cold" side, d. H. the withdrawal side of the WP serves according to an embodiment of the invention to, on one integrated into the thermal drive device Expansion circle the repatriation of the Execute expansion medium in its initial state and through the thereby made possible Potential exchange a cycle and thus energy for the thermal To provide drive device. Required is ideal way just as much energy as usual for the Electric drive needed becomes. Since the thermal drive device compared to a mechanical compressor or an electric motor only very small Losses, thereby resulting in significant benefits, for example the coefficient of performance increases significantly. A special development of proposed composite thermal machine even provides that electrical external energy essentially only to the start of the machine is needed and can be balanced again during operation, so that the machine without the usual Comparison of used drive energy to recovered heat energy is working. The figure of merit then results from the performance of the Primary energy heat exchanger (Air-refrigerant) and the drive energy. However, the invention is by no means limited to one limited such configuration.

The conventional heat pump evolves by the integration of the expansion circuit or the thermal (linear) drive with a heat pump to said thermal compounding machine with improved efficiency, which is achieved by using the supplier-side "minus" potential. The heat energy converted with the expansion circuit is used to operate the compressor of the HP or other preferably linear actuators. The energy transformation takes place as needed and therefore without significant losses. For power production is the use a (linear) generator the optimal shape. With the same arrangement, pressure can be additionally or alternatively generated for other drive purposes. The explanations here and in the following are, however, in principle not limited to linearly working embodiments.

Of the Drive of compressor and generator can be done in different ways be combined. A needs-based coordination is on the fly accessible at any time. For The combined operation of the heat exchanger must be designed accordingly become. Ideally, the thermal linear drive is dimensioned that he has the heating needs of a building Completely and the electrical energy for covers the own operation at least proportionately. The electricity production at the expense of heating power. One more way offers operation at times (summer and / or night) in which no heating demand is present. Here then can the linear drive amplified for the linear generator in operation be taken. The operating time of the WP expands to this Way to all-season operation.

Essential is the impact on the electricity grid in this context. Of the Compressor conventional Heat pumps has a high inductive load, and the electricity suppliers leave at certain high load times an operation of the heat pump not too. This is omitted present, since the electrically driven compressor completely eliminated can. The for regulation and blowers Electricity consumption is approx. 80 kW heat output below a connected load of 2 kW. Electricity from the grid is only minor and preferably only needed to start the WP. In very cold temperatures the air-to-water heat pump must go after previous concept are electrically supported. By the present longer Running time (night reduction = buffer time) can reduce this re-heating become. An oversizing of the Heat pump ", today uneconomical, would be economically possible with self-generated drive energy, wherein primary heating produced and the rest Energy for used the electricity production and fed into the grid or itself is consumed.

The proposed power production with the linear generator is after Calculations of the applicant for already economical and not dependent on whether alone the WP in addition for heating purposes is used. The linear drive is then not only in the heating months in use. Matched systems can be characterized by their low construction volume very well on already used areas interconnected to clusters become.

energy or energy losses become a problem when this energy is purchased must be and / or comes from fossil fuels, which is environmentally harmful Immissionsen is connected. This applies to the proposed thermal linear drive not too. He uses the ambient heat of the air and thus solar Energy. The environmental balance, taken into account in production and operation be, is also positive. The plants essentially exist made of light metal. Although the extraction of light metal requires Electricity. This power requirement can be derived from the manufactured linear drives or linear generators themselves are provided.

Of the Energy transport to the expansion circle can be indirect and direct. In indirect heating, the cylinder or its wall flows around the heating water or flows through and warmed up. Here exists with simple media management the disadvantage of a relatively small heat exchanger surface, the only insufficient to ensure the supply of the expansion medium with energy. It must therefore be expected per clock with a longer heat exchange time so that the clock frequency decreases and the number to be used the cylinder rises. The resistors on the way to transformation are bigger.

The Direct heating bypasses the cylinder as an energy exchanger between Expansion circle and energy circle. Here is the expansion medium injected directly into the in-cylinder energy carrier fluid. On This ensures optimal energy conversion. The additional expenditure of components is due to a considerably higher process reliability justified. Furthermore are the possibilities the process control improved.

The Construction offers enough Scope to absorb deviations in a practical implementation to be able to. It does not rely on prerequisites or materials, their fundamentals would have to be researched with great effort. At every point of the process can Sensors and actuators integrated for control and / or control become. The "mechanical Effort "is low. this leads to at a low cost Production of a long service life and low maintenance. This is the operating noise the significant environmental impact. With appropriate noise abatement measures but these are easily manageable. Essential for the noise protection Here is the underfloor installation of the drive and the air system as well the use of noise-encapsulated Heat exchanger.

Further Features and advantages of the present invention will become apparent from the following, extensive description of exemplary embodiments based on the drawing.

1 schematically shows the overall system of a thermodynamic composite machine according to the invention, which a ther according to the invention mixing drive device comprises;

2 shows the air system of a thermodynamic composite machine according to the invention;

3 shows the refrigerant circuit of a thermodynamic composite machine according to the invention;

4 shows the heating circuit of a thermodynamic composite machine according to the invention;

5 shows the energy cycle of a thermodynamic composite machine according to the invention, which contains the energy carrier fluid;

6 shows the expansion circuit of a thermodynamic composite machine according to the invention, which contains the expansion medium;

7 to 11 show various embodiments of a thermal drive device according to the invention as part of a thermodynamic composite machine according to the invention;

12 and 13 show alternative embodiments of the thermal drive device according to the invention with external pressure generator;

14 shows the external pressure generator according to the 12 and 13 ; and

15 and 16 show further alternative embodiments of a thermal drive device according to the invention.

The overall system 1 the proposed thermal composite machine according to 1 from the air system 2 (see. 2 ), the refrigerant circuit 3 ( 3 ), the optional heating circuit 4 ( 4 ), the energy circuit 5 ( 5 ), the expansion circle 6 ( 6 ) and the thermal drive device 7 ( 7 ).

Hereinafter, the individual components of a preferred embodiment of the overall system already described above 1 discussed in more detail. The components need not necessarily be present in their entirety and / or the form shown. The description will be made without any restriction to the general public with reference to an air-water heat pump. The material specifications are to be understood as exemplary only throughout.

air system

The air system 2 forms the primary energy circuit and conveys the necessary amount of air and the potential contained therein (energy) to the heat exchangers WT1 and WT3. In WT1 the heat transfer to the refrigerant of the heat pump (refrigerant circuit 3 ). The air system is used in WT3 2 for the return of the expansion medium to the initial state. With the air system 2 Connected assemblies are the refrigerant circuit 3 the heat pump (WP) and the expansion circuit (EPK) 6 ,

• 2.1 Ansaugschacht: In regensicherer Ausführung vorwiegend unterflur angeordnet und schalloptimiert. Material: Polymerbeton, Kunststoffe, Metallgitter;
• 2.2 Zuluftrohr: leitet die Luft vom Ansaugschacht zum Wärmetauscher der Wärmepumpe (WT1) und nimmt das Axialgebläse (Bezugszeichen 2.16) auf. Material: Polymerbeton, Kunststoffe;
• 2.3 Luftverteiler (vgl. 1): Integriertes Bauteil des WT1. Verteilt die Luft unterhalb seitlich des WT1 in die Luftwärmetauscherkanäle. Material: Aluminium;
• 2.4 WT1 (vgl. 1): Im WT1 wird die Energie vom Primärenergieträger Luft an das Kältemittel übertragen. Material: Leichtmetall;
• 2.5 Luftsammler (vgl. 1): Integriertes Bauteil des WT1. Sammelt die Luft oberhalb seitlich des WT1 aus den Luftwärmetauscherkanälen. Material: Leichtmetall;
• 2.6 Luftkanal (vgl. 1): integriertes Bauteil des WT1. Von Vakuumisolierkammern umgeben; führt die Abluft in den Abluftregelkasten. Anordnung seitlich parallel zum WT1. Der Luftkanal kann alternativ in der Geräuschkapselung der WT-Einheit aus WT1 und WT2 (siehe 4) geführt werden. Material: Aluminium, Kunststoff;
• 2.7 Abluftregelkasten: Der Abluftregelkasten nimmt die Abluftregelklappe (2.18) auf. Anordnung: unterste Baugruppen im Unterflurkasten, zwischen Luftkanal, Abluftrohr und WT3. Material: Kunststoff;
• 2.8 Abluftregelklappe (ARK): Die Abluftregelklappe lenkt den Luftstrom nach Bedarf an den WT3 oder den Abluftbypass (2.12). Die Gelenke müssen gekapselt und frostsicher ausgeführt werden. Die Klappe selbst muss nicht dicht schließen, da eine Mindestkühlung des WT3 immer erforderlich ist. Material: Kunststoff;
• 2.9 Abluftsteuergruppe: Die Abluftsteuergruppe prüft mit nicht explizit dargestellten Sensoren den Druck, den Stand an flüssigem CO2-Vorrat (Expansionsmedium – EPM) und die Temperatur im Expansionskreis sowie die Ablufttemperatur und regelt über einen Stellmotor (2.10) die Abluftregelklappe 2.8.
• 2.10 Stellmotor ARK (vgl. 1): Der Stellmotor für die Abluftregelklappe verstellt die Abluftregelklappe 2.8 und verändert so die Kühlleistung am WT3. Anordnung axial zur Abluftregelklappe außerhalb der Abluft am Abluftregelkasten 2.7.
• 2.11 WT3: Die kalte Abluft kühlt das Expansionsmedium nach der Arbeitsleistung im Wärmetauscher WT3 wieder ab und verflüssigt so das Expansionsmedium. Energie wird vom Expansionsmedium an die kalte Abluft übertragen. Al ternative: Die im WT3 erwärmte, mit Energie geladene Abluft kann je nach Temperaturpotential gegenüber der Ansaugluft dem Prozess erneut zugeführt werden. Material: Leichtmetall;
• 2.12 Abluftbypass: Leitet die am WT3 nicht benötigte Luft zum Abluftsammler (2.13). Anordnung: parallel zum WT3 oder ggf. im WT3 integriert. Material: Kunststoff, Aluminium;
• 2.13 Abluftsammler: Der Abluftsammler nimmt die Abluft aus WT3 und dem Abluftbypass 2.12 auf und führt diese zum Abluftrohr. Material: Kunststoff;
• 2.14 Abluftrohr: Das Abluftrohr leitet die Luft aus dem Unterflurkasten (2.17) zum Ausströmschacht (2.15). Das Abluftrohr ist unterflur angeordnet. Es stellt zur Vermeidung von Luftkurzschluss den Abstand zwischen Einlass und Auslass sicher. Anordnung: Unterflur; Material: Polymerbeton PVC, aber auch Kanalgrundrohr (KG-Rohr) aus Abwassersystem möglich.
• 2.15 Ausströmschacht: in regensicherer Ausführung vorwiegend unterflur angeordnet und schalloptimiert. Material: Polymerbeton, Kunststoffe, Metallgitter;
• 2.16 Primärgebläse: Das Primärgebläse sorgt drehzahlgeregelt für die notwendige Luftmasse. Die Drehzahl und damit der Luftstrom wird beim Anfahren des Linearantriebs so geregelt, dass im WT3 eine möglichst hohe Kühlleistung für das EPM zur Verfügung steht. Der Luftstrom wird damit dem steigenden Temperaturpotential und der Anzahl in Betrieb befindlicher Antriebszylinder angepasst. Die Bauform ist als Axialgebläse gewählt. Es ist in das Zuluftrohr 2.2 eingesetzt und geräuschoptimiert unterflur angeordnet.
• 2.17 Unterflurkasten: Der Unterflurkasten nimmt solche Bauteile auf, die aufgrund ihrer Geräuschentwicklung im Betreib gedämmt werden müssen. Hier sind im Wesentlichen Verdichter und Luftführungsbauteile zu nennen. Auch der WT3 kann aus Gründen der Anordnung im Unterflurkasten untergebracht werden. Die Festigkeit sollte so ausgelegt werden, dass die Überfahrung mit einem PKW möglich ist. Material: Beton, Polymerbeton, faserverstärkter Kunststoff.
• 2.18 Unterflurkastendeckel: Der Unterflurkastendeckel verschließt den Unterflurkasten 2.17 regensicher. Er ist lärmdämmend ausgeführt. Seine Festigkeit vervollständigt die Anforderung an den Unterflurkasten zur Überfahrmöglichkeit mit einem PKW. Material: Leichtmetall, Metall (Riffelblech mit angeschäumter Dämmung).

The air system 2 includes in the embodiment according to 2 following components:

• 2.1 Intake shaft: In rain-proof design, mainly arranged underfloor and sound-optimized. Material: polymer concrete, plastics, metal mesh;
• 2.2 Supply pipe: directs the air from the intake duct to the heat exchanger of the heat pump (WT1) and takes the axial fan (reference numeral 2.16 ) on. Material: polymer concrete, plastics;
• 2.3 Air distributor (cf. 1 ): Integrated component of the WT1. Distributes the air below the side of the WT1 into the air heat exchange channels. Material: aluminum;
• 2.4 WT1 (cf. 1 ): In WT1, the energy from the primary energy carrier air is transferred to the refrigerant. Material: Alloy;
• 2.5 Air collector (cf. 1 ): Integrated component of the WT1. Collects the air above the side of the WT1 from the air heat exchanger channels. Material: Alloy;
• 2.6 Air duct (see. 1 ): integrated component of the WT1. Surrounded by Vakuumisolierkammern; guides the exhaust air into the exhaust air control box. Arrangement laterally parallel to the WT1. The air duct may alternatively be included in the noise enclosure of the WT unit from WT1 and WT2 (see 4 ). Material: aluminum, plastic;
• 2.7 Exhaust air control box: The exhaust air control box takes the exhaust air control flap ( 2.18 ) on. Arrangement: lowest modules in the underfloor box, between air duct, exhaust duct and WT3. Material: Plastic;
• 2.8 Exhaust air control flap (ARK): The exhaust air control flap directs the air flow as required to the WT3 or the exhaust air bypass ( 2.12 ). The joints must be encapsulated and executed frost-proof. The flap itself does not have to close tightly, as a minimum cooling of the WT3 is always required. Material: Plastic;
• 2.9 Exhaust air control group: The exhaust air control group checks the pressure, the level of liquid CO2 supply (expansion medium - EPM) and the temperature in the expansion circuit as well as the exhaust air temperature by means of sensors that are not explicitly shown. 2.10 ) the exhaust air flap 2.8 ,
• 2.10 Actuator ARK (cf. 1 ): The actuator for the exhaust air damper adjusts the exhaust air damper 2.8 and thus changes the cooling capacity at the WT3. Arrangement axially to the exhaust air control flap outside the exhaust air at the exhaust air control box 2.7 ,
• 2.11 WT3: The cold exhaust air cools down the expansion medium after the work in heat exchanger WT3 and liquefies the expansion medium. Energy is absorbed by the expansion medium transfer the cold exhaust air. Alternative: The energy-laden exhaust air heated in the WT3 can be fed back to the process depending on the temperature potential compared to the intake air. Material: Alloy;
• 2.12 Exhaust air bypass: directs the air not required on the WT3 to the exhaust air collector ( 2.13 ). Arrangement: parallel to the WT3 or possibly integrated in the WT3. Material: plastic, aluminum;
• 2.13 Exhaust air collector: The exhaust air collector takes the exhaust air from WT3 and the exhaust air bypass 2.12 and leads them to the exhaust pipe. Material: Plastic;
• 2.14 Exhaust pipe: The exhaust pipe directs the air from the underfloor box ( 2.17 ) to the discharge shaft ( 2.15 ). The exhaust pipe is arranged below ground. It ensures the distance between inlet and outlet to avoid air short circuit. Arrangement: underfloor; Material: Polymer concrete PVC, but also sewer pipe (KG pipe) possible from sewage system.
• 2.15 Outflow shaft: rainproof design, mainly arranged underfloor and sound-optimized. Material: polymer concrete, plastics, metal mesh;
• 2.16 Primary fan: The primary fan provides speed-controlled for the necessary air mass. The speed and thus the air flow is controlled during start-up of the linear drive in such a way that in the WT3 the highest possible cooling capacity is available for the EPM. The air flow is thus adapted to the increasing temperature potential and the number of operating drive cylinders in operation. The design is chosen as axial fan. It is in the supply air pipe 2.2 inserted and noise-optimized underfloor arranged.
• 2.17 Underfloor box: The underfloor box accommodates such components that have to be insulated in operation due to their noise development. Here are mainly compressors and air duct components to call. The WT3 can also be accommodated in the underfloor box for reasons of arrangement. The strength should be designed so that the passage over with a car is possible. Material: concrete, polymer concrete, fiber reinforced plastic.
• 2.18 Underfloor box lid: The underfloor box lid closes the underfloor box 2.17 rainproof. It is noise-insulating. Its strength completes the requirement of the underfloor box for driving over with a car. Material: light metal, metal (corrugated sheet with foamed insulation).

To keep the entry of rainwater as low as possible, the system should be on the side of the house facing away from the weather 4 ' be attached. The air shafts 2.1 . 2.15 are also equipped with water deflectors and can penetrate the water to the drainage 2.19 derived. The cables to the underfloor box are laid in ascending order, so that water always drains to the air shaft. In the derivation of the duct system a float device should be installed. It prevents the intake of air from the duct system. This duct air can contain corrosive components and thus damage the components of the system.

The Introduction and discharge of the air is designed according to aerodynamic principles. By the shape of the air shafts can the noise level be significantly influenced. High air speeds at the discharge shaft for example by dividing the airflow and then running against each other the air flows without Energy consumption be braked. The shafts are in one Depth up to approx. 50 cm. The housing are sound-absorbing executed. The Air duct with deflectors and baffles provides by reflection and absorption a low noise level the plant sure. The sheath of the WT unit (WT3) will not only the heat-insulating Requirements, but also meets the sound insulation requirements of the air system.

A further soundproofing measure represents the control of the primary blower. Depending on the power requirement while the speed of the fan is controlled. Measured by the heating operation, the maximum temperature becomes, for example at 75 ° C Set flow temperature. Depending on the air temperature and the heating load can be the required power of different huge Airflows be provided. When the flow temperature is reached, the blower speed becomes reduced.

The Speed control of the primary blower is continues to make sense to the airflow during startup of the plant in terms of performance and number of cylinders used. One too big Airflow across a small cylinder power causes a proportionally low Energy deprivation, and the temperature of the air flow does not decrease sufficiently in WT3 the return of the To perform expansion medium in the initial state.

Refrigerant circuit

The refrigerant circuit (also called "compressor circuit") 3 extracts a part of their heat energy from the ambient air and gives it to the heating water in the heating circuit 4 ( 4 ) or alternatively directly to the power circuit ( 5 ). He thus largely corresponds to its function in known heat pumps. The functional in the refrigerant circuit 3 included compressors 7.3b is due to thermal expansion of the EPM in the drive device (also "drive"; 7 ). The refrigerant circuit 3 is with the air system 2 and the heating circuit 4 connected.

• 3.1 Kältemittel: Das Kältemittel, beispielsweise Tetrafluorethan (R134a), nimmt durch Expansion im WT1 (3.2) Energie aus der Umgebungsluft auf und gibt sie auf einem höheren Temperaturniveau über den WT2 an das Heizwasser ab (vgl. 4). Je nach Konfiguration wird die Energie an den Heizkreis abgegeben oder ohne Pufferung direkt an den Expansionszylinder bzw. das Energieträgerfluid ETF. Material: Gase, z. B. R134a, bzw. allgemein als Kältemittel dienliche Medien (Fluide, Gase, Gasgemische);
• 3.2 WT1: Der erste Wärmetauscher (WT1) übernimmt die Übertragung der Energie aus dem Primärenergieträger, z. B. Luft, an das Kältemittel 3.1. Die Führung der Medien erfolgt im Gegenstromverfahren. Er ist kombiniert mit dem WT2 des Heizkreises (4) zu der bereits erwähnten WT-Einheit. Die Bauteile Luftverteiler, Luftsammler, Luftkanal sind integriert (vgl. Bezugszeichen 2.3, 2.5 und 2.6 in 2). Aus dem Kältemittelkreis sind ein erster Kältemittelverteiler, die Kältemitteldüsen und der Kältemittelsammler integriert (vgl. Bezugszeichen 3.3–3.5). Die gesamte WT-Einheit ist nach außen wärme- und schallisoliert, beispielsweise durch eine Vakuumisolierung. Interne thermische Trennungen werden mit Vakuumkammern hergestellt. Anordnung: Der WT1 ist senkrecht oberirdisch aufgestellt. Material: Leichtmetall;
• 3.3 (erster) Kältemittelverteiler: Der Kältemittelverteiler übernimmt das flüssige Kältemittel aus dem Kältemittelkondensator (3.12). Im Kältemittelverteiler wird das flüssige Kältemittel zu den Kältemitteldüsen (3.4) geleitet. Anordnung: oberhalb des WT1. Material Aluminium.
• 3.4 Kältemitteldüsen: Die Kältemitteldüsen sprühen das Kältemittel 3.1 in zerstäubter Form in die Rohre des WT1. Anordnung: eingepresst in die Kältemittelrohre des WT2 oder im Übergang von WT2 zu WT1. Material: Edelstahl;
• 3.5 Kältemittelsammler: Der Kältemittelsammler sammelt das expandierte und mit Wärmeenergie geladene Kältemittel 3.1 und führt es über die Saugleitung (3.6) an die Verdichter. Der Kältemittelsammler ist unterhalb des WT1 angeordnet. Material Leichtmetall;
• 3.6 Saugleitung: Die Saugleitung verbindet den Kältemittelsammler 3.5 mit dem Verdichter (7.3b). Eine Bohrung im Zylinderblock versorgt die Kältemitteleinlassventile (3.7). Material: Leichtmetall;
• 3.7 Kältemitteleinlassventil: Das Kältemitteleinlassventil regelt den Kältemittelstrom zum Verdichter (7.3b). Es ist elektromagnetisch betätigt und sorgt für eine Begrenzung des Kältemittelzulaufs bei Fehlfunktionen entsprechend einem zu hohen Druck im Kältemittelkreislauf. Stoppt die WP durch Schließen. 7.3b Verdichter: Hat die Aufgabe, das expandierte, mit Energie geladene Kältemittel 3.1 zu verdichten und damit die Temperatur zu heben. Der Verdichter wird vom Expansionszylinder der thermischen Antriebsvorrichtung (7) angetrieben. Material: Leichtmetall;
• 3.9 Kältemittelauslassventil: Das Kältemittelauslassventil ist vorzugsweise elektromagnetisch und/oder druckgesteuert betrieben. Das Ventil lässt beim Erreichen eines Drucks höher als der Druck der Hochdruckseite des Kältemittelkondensators (3.12) das verdichtete Kältemittel 3.1 in den Kältemittelkreis (KMK) überströmen. Das Ventil wird aufgrund der Druckdifferenz gesteuert und kann auch als einfaches federbelastetes Kugelventil ausgeführt sein. Anordnung: in der Druckleitung (3.10) in der Nähe des Verdichterzylinders.
• 3.10 Druckleitung: Die Druckleitung verbindet den Verdichterzylinder mit dem Kältemittelverteiler 3.2. Material Leichtmetall;
• 3.11 (zweiter) Kältemittelverteiler: Der zweite Kältemittelverteiler 3.11 verteilt das Kältemittel 3.1 an die Kältemittelrohre des WT2. Er ist unterhalb des WT2 angeordnet. Material: Leichtmetall;
• 3.12 Kältemittelkondensator: Im Kältemittelkondensator wird das Kältemittel 3.1 aus dem WT2 verflüssigt und an den Kältemittelverteiler des WT1 geleitet. Anordnung oberhalb des WT2. Material: Leichtmetall;
• 3.13 Kältemittelsteuergruppe: Die Kältemittelsteuergruppe wirkt auf die Einlass- und Auslassventile des Verdichters.
• 3.14 Sensoren (nur angedeutet): ermitteln die Temperatur des Energieträgerfluids (ETF), die Temperatur des CO2 und die Temperatur der Luft sowie den Expansionsdruck und den Druck im Kältemittelkreis.

The refrigerant circuit 3 includes in the according to 3 following components:

• 3.1 Refrigerant: The refrigerant, such as tetrafluoroethane (R134a), decreases due to expansion in WT1 ( 3.2 ) Energy from the ambient air and gives it at a higher temperature level via the WT2 to the heating water (see. 4 ). Depending on the configuration, the energy is delivered to the heating circuit or without buffering directly to the expansion cylinder or the energy carrier fluid ETF. Material: gases, eg. B. R134a, or generally as a refrigerant media (fluids, gases, gas mixtures);
• 3.2 WT1: The first heat exchanger (WT1) takes over the transmission of the energy from the primary energy source, eg. As air, to the refrigerant 3.1 , The leadership of the media takes place in countercurrent process. It is combined with the WT2 of the heating circuit ( 4 ) to the already mentioned WT unit. The components air distributor, air collector, air duct are integrated (see reference numeral 2.3 . 2.5 and 2.6 in 2 ). From the refrigerant circuit, a first refrigerant distributor, the refrigerant nozzles and the refrigerant collector integrated (see reference numeral 3.3 - 3.5 ). The entire WT unit is heat and sound insulated to the outside, for example by a vacuum insulation. Internal thermal separations are made with vacuum chambers. Arrangement: The WT1 is installed vertically above ground. Material: Alloy;
• 3.3 (first) refrigerant distributor: The refrigerant distributor takes over the liquid refrigerant from the refrigerant condenser ( 3.12 ). In the refrigerant distributor, the liquid refrigerant is added to the refrigerant nozzles ( 3.4 ). Arrangement: above the WT1. Material aluminum.
• 3.4 Refrigerant nozzles: The refrigerant nozzles spray the refrigerant 3.1 in atomised form into the tubes of the WT1. Arrangement: pressed into the refrigerant tubes of the WT2 or in the transition from WT2 to WT1. Material: stainless steel;
• 3.5 Refrigerant collector: The refrigerant collector collects the expanded and charged with thermal energy refrigerant 3.1 and leads it over the suction line ( 3.6 ) to the compressors. The refrigerant collector is located below the WT1. Material light metal;
• 3.6 Suction line: The suction line connects the refrigerant collector 3.5 with the compressor ( 7.3b ). A bore in the cylinder block supplies the refrigerant inlet valves ( 3.7 ). Material: Alloy;
• 3.7 Refrigerant inlet valve: The refrigerant inlet valve regulates the refrigerant flow to the compressor ( 7.3b ). It is electromagnetically actuated and ensures a limitation of the refrigerant supply in case of malfunction corresponding to a high pressure in the refrigerant circuit. Stop the HP by closing. 7.3b Compressor: Has the task of expanding, charged with energy refrigerant 3.1 to condense and thus raise the temperature. The compressor is driven by the expansion cylinder of the thermal drive device ( 7 ). Material: Alloy;
• 3.9 Refrigerant outlet valve: The refrigerant outlet valve is preferably operated electromagnetically and / or pressure-controlled. The valve leaves on reaching a pressure higher than the pressure of the high pressure side of the refrigerant condenser ( 3.12 ) the compressed refrigerant 3.1 into the refrigerant circuit (KMK). The valve is controlled due to the pressure difference and can also be designed as a simple spring-loaded ball valve. Arrangement: in the pressure line ( 3.10 ) near the compressor cylinder.
• 3.10 Pressure line: The pressure line connects the compressor cylinder with the refrigerant distributor 3.2 , Material light metal;
• 3.11 (second) refrigerant distributor: The second refrigerant distributor 3.11 distributes the refrigerant 3.1 to the refrigerant pipes of the WT2. It is located below the WT2. Material: Alloy;
• 3.12 Refrigerant condenser: The refrigerant in the refrigerant condenser becomes the refrigerant 3.1 liquefied from the WT2 and directed to the refrigerant distributor of the WT1. Arrangement above the WT2. Material: Alloy;
• 3.13 Refrigerant Control Group: The refrigerant control group acts on the inlet and outlet valves of the compressor.
• 3.14 Sensors (indicated only): determine the temperature of the energy carrier fluid (ETF), the temperature of the CO2 and the temperature of the air as well as the expansion pressure and the pressure in the refrigerant circuit.

In the lower part of the 3 is an alternative embodiment with reference to the 12 which will be discussed in more detail below.

The pressure generation is a continuous process, ie the necessary pressure is not only at a certain piston position in the cylinder (see. 7 ) but progressively reached during the stroke. In order to avoid unnecessary energy-intensive overpressure, a spring-loaded differential pressure valve (refrigerant outlet valve) opens during normal operation 3.9 ) and allows the higher compression pressure to flow into the KMK. This valve is integrated in the electromagnetic exhaust valve and can be controlled higher-level at the start of operation.

On the refrigerant circuit and the refrigerant comes at low temperatures a very special importance. The refrigerant circuit must be adapted to these temperatures become. Alternatively you can also special gas mixtures the tasks of the known refrigerant gases and the CO2 in the expansion cycle.

By multiple compression and / or by the operation for power generation can also at previously unavailable temperatures collected energy and converted into a usable form.

heating circuit

The heating circuit 4 has the task of heat energy from the refrigerant 3.1 ( 3 ) and take these to the heating points of a building 4 ' and to transfer to the energy carrier fluid. For this purpose, the heating circuit with the refrigerant circuit 4 , the energy circuit 5 (see. 5 ) and connected to a provided there intermediate heat storage.

• 4.1 Wärmetauscher 2 (WT2): Der Wärmetauscher 2 überträgt die Wärmeenergie vom Kältemittel 3.1 an das Heizwasser. Anordnung: in der Wärmetauschereinheit (WT-Einheit). Material Aluminium;
• 4.2 Heizsystem: dem Wunsch des Benutzers und dem Wärmebedarf des Gebäudes entsprechend angepasst. Die Vorlauftemperatur von 75°C ist für eine Radiatorenheizung und eine Flächenheizung geeignet.
• 4.3 Zusatzkreis: Der Zusatzkreis sorgt mit Ventilen im Heizungsvorlauf und Heizungsrücklauf für die Beheizung des ETF über den Zwischenwärmespeicher
• 5.1 (5) oder einen Koaxialwärmetauscher. Die Anbindung erfolgt parallel zum Zwischenwärmespeicher/Koaxialwärmetauscher oder in Reihe mit diesem.
• 4.4 Umwälzpumpe: Optionale Baugruppe; wälzt im Parallelbetrieb bedarfsgerecht das Heizwasser zwischen WT2 und ETF-Beheizung um.
• 4.5 Heizkreissteuerung: Die Heizkreissteuerung arbeitet wie bei allen Warmwasserheizsystemen mit der zusätzlichen Aufgabe, vorrangig das ETF mit Energie zu versorgen.
• 4.6 Sensoren (nur angedeutet): für die ETF-Temperatur sowie weitere gebäudespezifische Sensoren.

The heating circuit 4 includes in the embodiment according to 4 following components:

• 4.1 heat exchangers 2 (WT2): The heat exchanger 2 transfers the heat energy from the refrigerant 3.1 to the heating water. Arrangement: in the heat exchanger unit (WT unit). Material aluminum;
• 4.2 Heating system: adapted to the user's request and the heat demand of the building. The flow temperature of 75 ° C is suitable for radiator heating and surface heating.
• 4.3 Additional circuit: The additional circuit with valves in the heating flow and heating return for the heating of the ETF via the intermediate heat storage
• 5.1 ( 5 ) or a coaxial heat exchanger. The connection is parallel to the intermediate heat storage / coaxial heat exchanger or in series with this.
• 4.4 Circulation pump: optional assembly; In parallel operation, the heating water circulates as required between WT2 and ETF heating.
• 4.5 Heating circuit control: As with all hot water heating systems, the heating circuit control has the additional task of providing energy primarily to the ETF.
• 4.6 Sensors (indicated only): for the ETF temperature and other building-specific sensors.

The heating circuit 4 largely corresponds to the heating circuits of conventional heat pump systems and requires no further adjustments on the building side. Only branches with priority for energy transfer to the energy carrier fluid ETF are integrated. The integration of the energy transfer can be carried out in series or in parallel, as shown in each case. The heating circuit can be used for indirect heating of the cylinder ( 7 ) by heating. Direct heating via the energy carrier fluid and an intermediate heat store 5.1 however, is the optimal variant in terms of energy transfer from the ETF to the EPM, as discussed in more detail below. In a variant for the exclusive production of electricity, the heating circuit can be omitted. Its function is then taken over directly by the refrigerant circuit.

energy circuit

The energy circuit 5 removes the heating circuit 4 or the refrigerant circuit 3 The energy required for the thermal drive device by means of the energy carrier fluid ETF, preferably a synthetic thermal or thermal oil and transmits them in the drive cylinder ( 7 ) to the expansion circle ( 6 ). For this purpose, the energy circuit on the one hand with the drive device and on the other hand with the expansion circuit (see. 6 ) as well as the heating circuit 4 and possibly directly with the refrigerant circuit 3 connected.

• 5.1 Zwischenwärmespeicher: Der Zwischenwärmespeicher dient zur Energieübertragung der im Heizwasser oder im Kältemittel gespeicherten Energie an das Energieträgerfluid ETF. Er muss im Druckbereich des ETF druckfest gebaut sein, da hier ein Druckausgleich zum Expansionskreis erforderlich ist. Er puffert und speichert die Energie für den Betriebsstart. Er tauscht im Kombibetrieb Stromerzeugung-Heizen bis zu 90% der Energie an das ETF zum Betrieb der Linearantriebe für Verdichter und Lineargenerator. Die Bauform ist ähnlich einem hocheffektiven Warmwasserspeicher mit bestmöglicher Wärmeisolierung und einem leistungsfähigen Rohrwärmetauscher. Anordnung: parallel zum oder in Reihe mit dem Heizkreislauf 4 eingebunden. Aufstellung im Gebäude. Material: Leichtmetall;
• Ein Koaxialrohrwärmetauscher stellt eine nicht gezeigte Alternative zum Zwischenwärmespeicher 5.1 dar und übernimmt dann im laufenden Betrieb die kontinuierliche Energieübertragung vom Heizkreis 4 oder Kältemittelkreis 3 an das Energieträgerfluid ETF (Wärmeträgeröl) im Energiekreis. Seine Wirkungsweise ähnelt der eines Durchlauferhitzers.
• 5.3 Heizstab: Der Elektroheizstab heizt bei einem Kaltstart das ETF im Zwischenwärmespeicher auf, um ein für den Betriebsstart notwendiges Temperaturpotential zu gewährleisten. Er kommt vorteilhafter Weise und im Zuge einer besonderen Ausgestaltung der Erfindung nur nach langen Betriebsstillständen, z. B. nach Reparaturmaßnahmen, zum Einsatz. Im normalen Betrieb wird bei der genannten Ausgestaltung bei Stillstand der Energieverlust im Zwischenwärmespeicher von der Anlage selbsttätig nachgeladen. Alternativ kann der Heizstab auch dauerhaft bzw. regelmäßig zum Ausgleichen von Verlusten und zur Aufrechterhaltung des erforderlichen thermischen Betriebspotential eingesetzt werden. Anordnung: eingesetzt in den Zwischenwärmespeicher 5.1; Bauform: handelsüblich.
• 5.4 Entgasungsstufe: dem Zwischenwärmespeicher 5.1 nachgeschaltete Entgasungsstufe. Die Entgasungsstufe scheidet im ETF befindliches Expansionsgas an den Expansionskreis ab. Es ist nur ein geringes Gasvolumen zu erwarten. Die Entgasungsstufe sorgt durch die Entgasung für einen guten Energieübergang im Zwischenwärmespeicher 5.1 und für ein gleich bleibendes Volumen des ETF im Zwischenwärmespeicher. Für den CO2-Übergang ist ggf. eine (nicht gezeigte) Hilfspumpe erforderlich. Anordnung: oberhalb des Zwischenwärmespeichers 5.1 mit Anschluss an den Expansionskreis 6.
• 5.5 ETF-Vorlaufleitung: Die ETF-Vorlaufleitung verbindet den Zwischenwärmespeicher 5.1 mit der thermischen Antriebsvorrichtung (7) und dem ETF-Einlassventil (5.7) mit Mengenregelung und Rückströmsicherung. (ETF-EMR);
• 5.6 Membrandruckregler: Der Membrandruckregler stellt außerhalb des Zylinders der Antriebsvorrichtung den Druckausgleich zwischen dem Expansionskreis 6 und dem ETF-Kreis oder Energiekreis 5 her. Er trennt die beiden Kreise 5, 6 physisch und thermisch. Der Druckausgleich ist während des ETF Wechsels oder -Austausches erforderlich. Eine mögliche Bauform ist ein Gummibalg in einem Zweikammergefäß.
• 5.7 ETF-Einlassventil: Hierbei handelt es sich vorzugsweise um ein elektromagnetisch gesteuertes Ventil. Es stellt den ETF-Wechsel in der für die Betriebsphase notwendigen Menge durch eine Regelung der Öffnungszeit sicher. Es verschließt den Zylinder der Antriebsvorrichtung 7 während des Expansi onsvorgangs. Anordnung: direkt an dem genannten Zylinder.
• 5.8 ETF-Auslassventil: Das ETF-Auslassventil öffnet beim ETF-Wechsel den Expansionsraum im Zylinder der Antriebsvorrichtung 7 und lässt das ETF zum Gastrenner (5.10) ausströmen. Das Ventil wird elektromagnetisch betätigt. Anordnung: direkt am Zylinder.
• 5.9 (erste) ETF-Rücklaufleitung: Die erste ETF Rücklaufleitung 5.9 verbindet den Expansionszylinder mit dem Gastrenner (5.10).
• 5.10 Gastrenner: Der Gastrenner trennt mitgerissenes Expansionsmedium EPM vom ETF und führt dieses wieder dem Expansionskreis 6 zu. Seine Funktion ist rein physikalisch. Die Trennung erfolgt aufgrund verschiedener Dichte der Medien. Das getrennte EPM-Gas wird entweder vom Expansionskreis 6 durch „Strömungsunterdruck” mitgerissen oder über ein Zweikammersystem und eine Druckerhöhung aus der Restenergie an den Expansionskreis 6 abgegeben. Alternativ kann auch mithilfe einer (nicht gezeigten) Pumpe das EPM-Gas abgesaugt und dem Expansionskreis 6 zugeleitet werden. Anordnung: parallel zwischen Expansionskreis 6 und Energiekreis 5.
• 5.11 (zweite) Rücklaufleitung: Die zweite Rücklaufleitung 5.11 verbindet den Gastrenner 5.10 mit der Umwälzpumpe (5.12) und dem Zwischenwärmespeicher 5.1.
• 5.12 Umwälzpumpe: Die Umwälzpumpe fördert das ETF im Energiekreis 5. Sie entspricht in der Bauform und Volumenanforderung einer kleinen Heizungsumwälzpumpe, jedoch mit einer höheren Druckfestigkeit gemäß dem Betriebsdruck. Anordnung: in der zweiten Rücklaufleitung 5.11;
• 5.13 Energiekreis-Steuergruppe: Steuert die Magnetventile für Einlass 5.7 und Auslass 5.8 des ETF und regelt die Drehzahl der Umwälzpumpe 5.12. Überwacht den Entgasungsvorgang im Gastrenner 5.10 und der Entgasungsstufe 5.4. Enthaltene Sensoren (nicht gezeigt): Sensor für Kolbenstellung sowie Temperatursensoren für Luft, CO2 und ETF; Drucksensor für Verdichtungsdruck.

The energy circuit 5 includes in the embodiment according to 5 following components:

• 5.1 Intermediate heat storage: The intermediate heat storage is used to transfer energy stored in the heating water or refrigerant energy to the energy carrier fluid ETF. It must be pressure-resistant in the pressure area of the ETF, as it requires pressure equalization to the expansion circuit. It buffers and stores the energy for the start of operation. In combined operation, it exchanges power generation heating for up to 90% of the energy to the ETF for operation of the linear drives for compressors and linear generators. The design is similar to a highly effective hot water tank with the best possible heat insulation and a powerful tube heat exchanger. Arrangement: parallel to or in series with the heating circuit 4 involved. Posing in the building. Material: Alloy;
• A coaxial tube heat exchanger provides an alternative to the intermediate heat store, not shown 5.1 and then takes over the continuous energy transfer from the heating circuit during operation 4 or refrigerant circuit 3 to the energy carrier fluid ETF (thermal oil) in the energy circuit. Its effect is similar to that of a water heater.
• 5.3 Heating element: The electric heating element heats up the ETF in the intermediate heat storage during a cold start in order to ensure a temperature potential necessary for the start of operation. He comes advantageously and in the course of a particular embodiment of the invention only after long shutdowns, z. B. after repairs, for use. In normal operation, the energy loss in the intermediate heat storage is automatically recharged by the system in the above configuration at standstill. Alternatively, the heating element can also be used permanently or regularly to compensate for losses and to maintain the required thermal operating potential. Arrangement: used in the intermediate heat storage 5.1 ; Type: commercially available.
• 5.4 Degassing stage: the intermediate heat store 5.1 downstream degassing stage. The degassing stage separates expansion gas in the ETF to the expansion circuit. It is expected only a small volume of gas. The degassing stage ensures through the degassing for a good energy transition in the intermediate heat storage 5.1 and for a constant volume of the ETF in the intermediate heat storage. For the CO2 transition, an auxiliary pump (not shown) may be required. Arrangement: above the intermediate heat store 5.1 with connection to the expansion circuit 6 ,
• 5.5 ETF feed line: The ETF feed line connects the intermediate heat store 5.1 with the thermal drive device ( 7 ) and the ETF inlet valve ( 5.7 ) with flow control and backflow protection. (ETF-EMR);
• 5.6 Diaphragm pressure regulator: The diaphragm pressure regulator sets the pressure balance between the expansion circuit outside the cylinder of the drive device 6 and the ETF circle or energy circle 5 ago. He separates the two circles 5 . 6 physically and thermally. Pressure equalization is required during ETF replacement or replacement. One possible design is a rubber bellows in a two-chamber vessel.
• 5.7 ETF inlet valve: This is preferably an electromagnetically controlled valve. It ensures the ETF change in the quantity required for the operating phase by regulating the opening time. It closes the cylinder of the drive device 7 during the expansion process. Arrangement: directly on the mentioned cylinder.
• 5.8 ETF outlet valve: The ETF outlet valve opens the expansion space in the cylinder of the drive device during the ETF change 7 and lets the ETF become a gas separator ( 5.10 ). The valve is actuated electromagnetically. Arrangement: directly on the cylinder.
• 5.9 (first) ETF return line: The first ETF return line 5.9 connects the expansion cylinder with the gas separator ( 5.10 ).
• 5.10 Gas separator: The gas separator separates entrained expansion medium EPM from the ETF and leads it back to the expansion circuit 6 to. Its function is purely physical. The separation is due to different density of the media. The separated EPM gas is either from the expansion circuit 6 entrained by "flow vacuum" or via a two-chamber system and an increase in pressure from the residual energy to the expansion circuit 6 issued. Alternatively, by means of a pump (not shown), the EPM gas can be sucked off and the expansion circuit 6 be forwarded. Arrangement: parallel between expansion circle 6 and energy circle 5 ,
• 5.11 (second) return line: The second return line 5.11 connects the gas separator 5.10 with the circulation pump ( 5.12 ) and the intermediate heat storage 5.1 ,
• 5.12 Circulation pump: The circulation pump feeds the ETF in the energy circuit 5 , It corresponds in design and volume requirement of a small heating circulation pump, but with a higher pressure resistance according to the operating pressure. Arrangement: in the second return line 5.11 ;
• 5.13 Power circuit control group: Controls the inlet solenoid valves 5.7 and outlet 5.8 of the ETF and regulates the speed of the circulation pump 5.12 , Monitors the degassing process in the gas separator 5.10 and the degassing stage 5.4 , Sensors included (not shown): piston position sensor and temperature sensors for air, CO2 and ETF; Pressure sensor for compaction pressure.

The energy circuit 5 has - as already mentioned - the main task to transport energy into the drive cylinder (the cylinder of the thermal drive device). He takes the energy from the heating circuit 4 or the refrigerant circuit 3 , In the thermal drive device 7 the energy is released to the expansion medium. This can be carried out directly in the drive cylinder or in a separate assembly (pressure generator) or indirectly by heating a heat exchanger surface (for example the jacket surface of the cylinder of the thermal drive device) which is in direct contact with the drive cylinder.

In the power circuit, the module also uses intermediate heat storage 5.1 stored the energy required for a cold start. If the cached heat energy is too low, in particular after a longer standstill, the intermediate heat store is brought to the required operating temperature by an electric heating element or held there.

The Energy carrier fluid (ETF) of the energy circuit is charged by heating with energy. The Energy is released in the drive cylinder to the expansion medium. The ETF takes over In addition, the lubrication of the drive cylinder and the downstream Assemblies, namely of the linear generator and the compressor.

The heating water of higher temperature (eg 75 ° C = 348 K) charged in WT2 with energy is transferred via the intermediate heat storage tank 5.1 directed. Alternatively, the charge can also be directly through the refrigerant 3.1 respectively. In the intermediate heat storage 5.1 it gives its energy to the ETF. This process can be carried out both in parallel operation and in series operation. The removal of energy from the heating water is always dependent on the energy consumption by the working or expansion cylinder of the thermal drive device, and only the amount of energy removed is crucial for the recharging of energy. The parallel operation offers the advantage that it is possible after the start, only the intermediate heat storage 5.1 to provide energy. In normal operation, by dividing the heating water flow on the one hand, the intermediate heat storage 5.1 and on the other hand the heating system with the maximum temperature ver be worried. The heat exchanger surface of the intermediate heat store 5.1 must supply the ETF with the highest possible energy in combined operation or in pure power generation operation and charge the ETF with energy. This is necessary in order to power the linear drives (linearly operating thermal working devices) for the linear generators during operation without heating requirement.

The drive of the power circuit 5 done by the electric circulation pump 5.12 , The power requirement for the circulation pump is low and comparable to that of a conventional small Heizkreisumwälzpumpe. The ETF change is made by the electromagnetic valves 5.7 . 5.8 carried out.

The intermediate heat store 5.1 has the already mentioned task to store the energy for the start of operation or by means of the electric heating element 5.3 especially after a prolonged shutdown to provide or keep. It resembles a hot water tank, but must be pressure resistant to withstand the operating pressure. The included heat exchanger, with which the energy from the heating water or the refrigerant is transferred to the ETF, must be adapted to the intended use of the system. The heat exchanger must have at least one power at which the energy for the operation of the compressors and / or for power generation is transmitted to the ETF.

meaningful is an interpretation that allows energy, not for Heating purposes needed is to be used to drive linear generators (combined operation or summer operation). For this purpose, the heat exchanger capacity is up to designed to 100% of the performance of the WT1. In the design is too consider, that in the months when mainly electricity is produced, the overall performance of the plant due to higher temperatures of the primary energy increases. This factor leads needed to a smaller one heat exchangers and thus lower investment costs. However, if you keep the size of the heat exchanger at, the excess power can used in the summer beyond the base calculation Energy with other thermal drive devices for power production to use. The size of the heat exchanger has no influence on the heat output, as not removed energy also does not need to be reloaded.

Of the Between heat storage can - as well already addressed - on two types are integrated into the heating circuit. The integration "inline" or in Row means that the heat exchanger always flows through the heating water and that this behind the heat exchanger is a fundamentally lower Temperature for the heating circuit of the building having.

in the parallel operation, the heating water can always with the highest possible Temperature are delivered to the heating circuit of the building. It offer There are also more control options and hydraulics the intermediate heat store independently and to supply them with energy as needed. The volume of the intermediate heat store is chosen that on the one hand to the heat exchanger surface and to the operating conditions (electricity, heating requirements) of the user fits and on the other hand has at least the size that is necessary to enable a start of operation after a short downtime again or at least support.

The Involvement via the heating water causes over the ETF volume going out larger energy buffer through the heating water volume available is provided. The energy transfer This is done more continuously. In a plant that is the exclusive Electricity production is used, does not apply the heating circuit. Here is the intermediate heat storage directly from the refrigerant loaded.

The term "intermediate heat storage" includes in the context of the present description that the maximum possible is performed for the thermal insulation. Best results can be achieved by using vacuum insulation. This complex type of insulation is only an optimization. It is not absolutely necessary from a technical and economic point of view. The built-in electric heater 5.3 may be designed to be very low in performance, as long as it is required or used only after prolonged shutdown. However, the invention is not limited thereto. Decreases during a standstill, the temperature / energy in the intermediate heat storage, and a start could then no longer be performed, the system starts automatically, if necessary using the heating element, and the intermediate heat storage is recharged. The use of external energy is thus minimized.

In The cost balance is therefore ideally only wear and tear a criterion. In the profitability calculation is the benefit through the production of Electricity is a major factor in the cost balance. It is therefore assume that the proposed equipment or compound machines have no or hardly any downtime.

As The person skilled in the art can recognize the additional external heating power also in other ways than by using a heating rod and / or elsewhere in the energy circuit or in another circuit take the plant, for example by external heating of the Heating medium.

The intermediate heat store 5.1 is in the pri the best area in the basement of the house 4 ' established. The determined size of 1851 × 645 mm plus insulation with a thickness of 100 mm can be easily accommodated in most existing buildings. Alternative locations to outdoor installation are also possible.

A not illustrated variant provides, the power circuit instead of an intermediate heat store with heat exchanger segments equip. In the heat exchanger segments gets the energy from refrigerant transferred directly to the ETF. The advantage of this design variant is a fast heating of the ETF in a relatively small cycle. The constructive integration is easily solvable. The intermediate heat store deleted in favor of a simple, well-insulated tank that merely as energy storage for the start serves. The heating circuit is no longer with the power circuit connected. The thermal inertia conditioned by the heating circuit and the associated multiple Energy exchange is eliminated.

Around Also, to produce electricity, more energy must be available from the heating area to the preferably designed as a linear drives thermal Drive devices are routed. This can be done by intrusion further heat exchanger segments in the interface area refrigerant ETF and simultaneous shutdown of heat exchanger segments in the interface area Refrigerant heating water to be performed. The disadvantage opposite the variant with intermediate heat storage consists in only a gradual combination possibility between power generation and heating and a more elaborate Heat exchanger design.

Of the Starting energy storage is integrated here in parallel and during the Operation reloaded. The energy storage is here at least for one Cold start first electrically pre-heated or continuously reheated. On the fly, as well constantly After a short-term standstill, the machine ideally runs automatically to load the energy storage, without the invention thereto limited would. there This variant is in the basic concept for the predominant heating operation designed.

expansion loop

The expansion circle 6 has the task in the cylinder of the thermal drive device ( 7 ) to transform energy introduced by thermal reaction into expansion by evaporation of the EPM and subsequently to work. In particular CO2 is suitable as an expansion medium EPM. Other gases are also possible by adjusting the operating conditions (pressure, temperature, quantities used, ...). In particular, taking into account the ambient temperature, other gases can be used. The expansion circle 6 is with the assemblies air system 2 and energy circle 5 connected and includes functionally also the cylinder of the thermal drive device together with the corresponding supply and discharge devices or the entire thermal drive device according to the invention (see. 7 ).

• 7.2 Expansionszylinder mit Kolben 7.4: Der Expansionszylinder 7.2 mit Zylinderkammer und Kolben 7.4 ist konstruktiv eigentlich ein Teil der der thermi schen Antriebsvorrichtung 7 (7) und umschließt das expandierende Gas (Expansionsmedium – EPM). Er wird im Rahmen der vorliegenden Beschreibung deshalb auch als „Antriebszylinder” oder „Arbeitszylinder” (7.2a; vgl. 7) bezeichnet.
• 6.2 Expansionsmedium: Das EPM, vorzugsweise CO2, nimmt durch Wärmefluss die Energie des ETF auf und expandiert/verdampft. Es treibt damit den Kolben 7.4 im Zylinder 7.2 an.
• 6.3 Expansionsmedium-Auslassventil (EPMAV): Das EPMAV lässt das expandierte EPM an den Wärmetauscher WT3 ausströmen. Anordnung: im oberen Bereich direkt am Zylinder 7.2. Elektromagnetisch betätigt.
• 6.4 (erste) EPM-Ableitung: Die erste EPM-Ableitung verbindet das EPMAV 6.3 mit dem Membrandruckregler (5.6; 5) und dem Wärmetauscher WT3. Der Membrandruckregler (vgl. Bezugszeichen 5.6 in 5) stellt außerhalb des Zylinders 7.2 den Druckausgleich zwischen dem Expansionskreis 6 und dem Energiekreis 5 her. Er trennt die beiden Kreise physisch und thermisch. Der Druckausgleich ist während des ETF-Wechsels erforderlich. Eine mögliche Bauform ist ein Gummibalg in einem Zweikammergefäß. Anordnung: beispielsweise wie dargestellt. Die Volumina und Flächen sind so ausgelegt, dass in allen Betriebsphasen – also auch bei Stillstand – der Druckausgleich sichergestellt ist. Bei Produktion und Wartung müssen beide Kreise gleichzeitig gefüllt werden.
• 6.6 (zweite) EPM-Ableitung: Die zweite EPM-Ableitung verbindet den Membrandruckregler 5.6 und die Entgasungsstufe 5.4 im Zwischenwärmespeicher (5.1).
• 6.8 (dritte) EPM-Ableitung: Die dritte EPM-Ableitung verbindet den Gastrenner 5.10 (5) mit dem Wärmetauscher WT3. Der Gastrenner trennt mitgerissenes Expansionsmedium EPM vom ETF und führt dieses wieder dem Expansionskreis zu. Seine Funktion ist rein physikalisch. Die Trennung erfolgt aufgrund der verschiedenen Dichte der Medien. Das getrennte Gas wird entweder vom Expansionskreis durch „Strömungsunterdruck” mitgerissen oder über ein Zweikammersystem und eine Druckerhöhung aus der Restenergie des ETF an den Expansionskreis abgegeben. Anordnung: parallel zwischen Expansionskreis und Energiekreis.
• Wärmetauscher WT3: Der Wärmetauscher WT3 führt die kalte Abluft an den Expansionskreis 6 und sorgt damit für die Rückführung des EPM in dessen Anfangszustand (vorzugsweise flüssig). Er stellt so flüssiges EPM für die Einspritzung zur Verfügung. Er fungiert als Ausdehnungsraum für das expandierte EPM zur Druckabsenkung nach dem Ablassen aus dem Zylinder 7.2. Anordnung: nach dem Abluftregelkasten 2.7 vor dem Abluftsammler 2.13 (2). Der Wärmetauscher WT3 kann konstruktiv baugleich mit der WT-Einheit aus WT1 und WT2 sein. Material: Aluminium;
• 6.10 (erste) EPM-Zuleitung: Die erste EPM-Zuleitung führt das flüssige EPM vom Wärmetauscher WT3 zu dem CO2-Speicher (6.11).
• 6.10' (zweite) EPM-Zuleitung: Die zweite EPM-Zuleitung führt das flüssige EPM vom CO2-Speicher (6.11) zu den Einspritzdüsen (6.13).
• 6.11 CO2-Speicher: Der CO2-Speicher sammelt das flüssige CO2. Durch seinen Einbauort unterflur übersteigt die Temperatur des CO2 auch bei Betriebsstillstand eine Temperatur von 25°C nicht. Für den Betriebsstart steht somit immer genügend flüssiges CO2 zur Verfügung.
• 6.12 Einspritzpumpe: Die Einspritzpumpe versorgt die Einspritzdüsen (6.13) mit dem flüssigen EPM und dem notwendigen Einspritzdruck. Sie ist elektrisch angetrieben und druckgeregelt. Anordnung: zwischen CO2-Speicher 6.11 und der zweiten EPM-Zuleitung 6.10'.
• 6.13 Einspritzdüse mit Injektor 6.13': Die Einspritzdüse 6.13 wird elektromagnetisch betätigt und spritzt das EPM fein vernebelt direkt in das ETF im Zylinder 6.1 ein. Der Injektor 6.13' taucht dabei zur Abgabe des EPM in das ETF ein und bildet so zumindest teilweise die Wärmeaustauschmittel der thermischen Antriebsvorrichtung.
• 6.14 EPM-Steuergruppe: Die EPM-Steuergruppe überwacht den Betriebsdruck im Expansionskreis, steuert die Einspritzpumpe 6.12, die zugeordneten Magnetventile und überwacht die Entgasung am Zwischenwärmespeicher 5.1 und am Gastrenner 5.10.
• 6.15 Sensoren (nur angedeutet): für Kolbenstellung, Ablufttemperatur, Verdichtungsdruck, ETF-Temperatur, EPM-Temperatur und Flüssigvorrat an EPM.
• 7.7 Vorspannmittel für den Kolben 7.4 in Form einer Spiralfeder oder dergleichen zum Vermitteln einer Rückstellkraft gegen den Druck des EPM; vorzugsweise einstellbar.

The expansion circle 6 includes in the embodiment according to 6 Total of the following components:

• 7.2 Expansion cylinder with piston 7.4 : The expansion cylinder 7.2 with cylinder chamber and piston 7.4 is structurally actually a part of the thermal drive device rule 7 ( 7 ) and encloses the expanding gas (expansion medium - EPM). It is therefore in the context of the present description also as "drive cylinder" or "working cylinder" ( 7.2a ; see. 7 ) designated.
• 6.2 Expansion medium: The EPM, preferably CO2, absorbs the energy of the ETF through heat flow and expands / vaporizes. It drives the piston 7.4 in the cylinder 7.2 at.
• 6.3 Expansion Media Outlet Valve (EPMAV): The EPMAV allows the expanded EPM to flow out to the WT3 heat exchanger. Arrangement: in the upper area directly on the cylinder 7.2 , Electromagnetically actuated.
• 6.4 (first) EPM derivative: The first EPM derivative connects the EPMAV 6.3 with the diaphragm pressure regulator ( 5.6 ; 5 ) and the heat exchanger WT3. The diaphragm pressure regulator (see reference numeral 5.6 in 5 ) places outside of the cylinder 7.2 the pressure balance between the expansion circuit 6 and the energy circuit 5 ago. He separates the two circles physically and thermally. Pressure equalization is required during the ETF change. One possible design is a rubber bellows in a two-chamber vessel. Arrangement: for example, as shown. The volumes and surfaces are designed so that pressure equalization is ensured in all operating phases - even at standstill. During production and maintenance, both circuits must be filled at the same time.
• 6.6 (second) EPM drain: The second EPM drain connects the diaphragm pressure regulator 5.6 and the degassing stage 5.4 in the intermediate heat store ( 5.1 ).
• 6.8 (third) EPM derivative: The third EPM derivative connects the gas separator 5.10 ( 5 ) with the heat exchanger WT3. The gas separator separates entrained expansion medium EPM from the ETF and leads it back to the expansion circuit. Its function is purely physical. The separation is due to the different density of the media. The separated gas is either entrained by the expansion circuit by "flow vacuum" or delivered via a two-chamber system and a pressure increase from the residual energy of the ETF to the expansion circuit. Arrangement: parallel between expansions circle and energy circle.
• Heat exchanger WT3: The heat exchanger WT3 feeds the cold exhaust air to the expansion circuit 6 and thus provides for the return of the EPM in its initial state (preferably liquid). It thus provides liquid EPM for injection. It acts as an expansion chamber for the expanded EPM for pressure reduction after discharge from the cylinder 7.2 , Arrangement: according to the exhaust air control box 2.7 in front of the exhaust collector 2.13 ( 2 ). The WT3 heat exchanger can be structurally identical to the WT unit made of WT1 and WT2. Material: aluminum;
• 6.10 (first) EPM feed line: The first EPM feed line carries the liquid EPM from the WT3 heat exchanger to the CO2 store ( 6.11 ).
• 6.10 ' (second) EPM supply line: The second EPM supply leads the liquid EPM from the CO2 storage ( 6.11 ) to the injectors ( 6.13 ).
• 6.11 CO2 storage: The CO2 storage collects the liquid CO2. Due to its location below ground, the temperature of the CO2 does not exceed a temperature of 25 ° C even when the machine is at a standstill. For the start of operation is thus always enough liquid CO2 available.
• 6.12 Injection pump: The injection pump supplies the injectors ( 6.13 ) with the liquid EPM and the necessary injection pressure. It is electrically driven and pressure controlled. Arrangement: between CO2 storage 6.11 and the second EPM feed line 6.10 ' ,
• 6.13 Injector with injector 6.13 ' : The injector 6.13 is electromagnetically actuated and injects the EPM finely atomized directly into the ETF in the cylinder 6.1 one. The injector 6.13 ' dips into the ETF for delivery of the EPM and so at least partially forms the heat exchange means of the thermal drive device.
• 6.14 EPM control group: The EPM control group monitors the operating pressure in the expansion circuit, controls the injection pump 6.12 , the associated solenoid valves and monitors the degassing of the intermediate heat storage 5.1 and at the gas separator 5.10 ,
• 6.15 Sensors (indicated only): for piston position, exhaust air temperature, compression pressure, ETF temperature, EPM temperature and liquid reservoir to EPM.
• 7.7 Biasing means for the piston 7.4 in the form of a coil spring or the like for imparting a restoring force against the pressure of the EPM; preferably adjustable.

The design of the control of the expansion circuit 6 has a significant influence on the energy balance of the entire system. The controller should therefore not run according to a rigid program, but primarily by the sensors 6.15 determined operating state be influenced. An essential feature for the control is the process result. The controller recognizes the work performed by the linear drive on the basis of the compressor power or the power production and uses these parameters to regulate the energy input and the associated modules. It affects the volumes of ETF and EPM used.

The operating pressure of the expansion circuit 6 is crucial for the operation of the machine 1 , It must be selected in such a way that a stock of expansion medium in a liquid state, which is necessary for the start of the system, is present at the time of machine or machine standstill and the expected ambient temperatures. During operation, the expansion medium in the WT3 is cooled by the exhaust air and energy is released to the exhaust air. As a result, the expansion medium liquefies. In the liquid state, the expansion medium can then be in the drive cylinder 7.2a be injected. The properties of CO2 are suitable here. The corresponding phase diagram shows that it is possible at a normal ambient temperature of about 20 ° C, by appropriate pressure in the expansion circuit 6 to obtain a liquid supply. The arrangement is mounted underfloor and thermally insulated for this purpose. As a result, the temperature does not rise above the earth's temperature and thus remains well below the value critical for CO2. At a pre-pressure of approx. 60 bar, operation is possible up to a CO2 temperature of 25 ° C.

The CO2 storage 6.11 with the liquid supply is expediently at the lowest point in the underfloor box 2.17 arranged. Alternatively, this can also be arranged in a separate underfloor box or as Erdlagertank. A deep cold cellar is also a suitable place. This avoids that the CO2 is heated up by radiant heat of other assemblies or by solar radiation. The supply of WT3 should be done in descending order, so that the CO2 easily by gravity the storage tank 6.11 can flow.

The operating pressure results from the temperature at standstill and the used, matching the ambient temperature gas EPM. The operating pressure is with the diaphragm pressure regulator 5.6 to the energy circuit 5 transfer. The pressure transmission is for the exchange of the ETF in the drive cylinder 7 respectively. 7.2a advantageous. The exchange of the ETF can at the same pressure of expansion circle 6 and energy circle 5 , ie at a relative pressure of 0 bar, be carried out as a simple recirculation process. The calculations of the operating pressure start from the worst to the expected variant. It can be assumed that the mentioned pressure of 60 bar can be undercut by cooling effects during operation. The storage temperature in the earth area will not exceed a temperature of 10 ° C even in summer. These conditions significantly affect the construction costs of the entire system in terms of compressive strength. The on the piston 7.4 in the cylinder 7.2 acting restoring force can then be substantially reduced, since it is essentially determined by the operating pressure. The operating pressure will have a possibly significant difference between plant downtime and operation. The restoring force in this case would have to be adjusted to the operating pressure by adjusting. Constructively, this can be realized in the case of a coil spring or the like. By a hydraulic adjustment of the spring counter. If the hydraulics are operated by the ETF, there is a direct connection between the operating condition and the restoring force / preload. Alternatively, the biasing means 7.7 be designed as such pneumatically, hydraulically or electromagnetically adjustable.

A rapid expansion of the expansion medium can be achieved by the widest possible temperature difference between ETF and EPM. The EPM goes directly to the high pressure injection pump 6.12 finely atomized into the ETF "injected". This would result in unregulated operation that consumes more energy from the EPM than necessary. Due to the work done, the energy absorption is stopped here by the expansion medium being discharged at this time. Further energy absorption beyond the operating point is thus avoided. Next determines the amount of EPM in the cylinder 7.2 the effective process.

The work is done by overcoming the restoring force of the biasing or spring means 7.7 provided. Any power greater than the restoring force can be delivered as work. The restoring force is already structurally stored by the bias of the spring. Energetically, the force is equal to a variant in which restoring force is "generated", z. B. by a gas spring. The restoring force is determined by the force required to expose the expanded EPM to pressure equalization from the cylinder 7.2 eject.

The volume to be moved out and thus the mass to be moved by the restoring force corresponds to the cylinder volume in relation to the cylinder pressure, which at this time equals the pressure of the expansion circuit 6 is. Next, the restoring force must be the weight of the piston 7.4 , the ETF and the frictional resistance are overcome. After-flowing refrigerant on the back of the piston (compressor side) reduces the restoring force of the spring. When starting the system, the piston is always in the upper position and can deliver the maximum power immediately. The maximum power is determined by the ETF charge and temperature and the potential difference to the EPM and its mass. A small residual amount of expansion medium in a damping chamber 6.18 (upper area of the cylinder chamber; 7 ) prevents the piston 7.4 in operation is pushed to the stop. Mechanically knocking noises and increased wear can be avoided. At a standstill is a stop 7.4a required in the cylinder chamber, hence the ETF outlet 6.3 not from the piston 7.4 is covered. At the start of operation, the ETF is replaced several times before the first drive cycle and thus the cylinder 7.2 preheated.

The change or exchange process begins after the cylinder pressure of the expansion medium by overflow into the expansion circuit 6 was balanced and the EPM drain valve 6.3 closed again. The piston 7.4 has been pushed by the restoring force in the upper position. It is held there until re-injection and until the end of the change process by the spring force. An injection of expansion medium takes place only after the end of the ETF change.

By a sensor, not shown, (for example, a photocell), the piston position is detected and to the control group 6.14 reported. The ETF outlet valve 5.8 ( 5 ) opens. The residual pressure in the cylinder pushes a subset of ETF into the energy circuit 5 in the direction of Gastrenner 5.10 , There is now pressure balance between the drive cylinder 7.2 , Energy circle 5 and expansion circle 6 , The ETF inlet valve 5.7 opens, and charged ETF flows into the cylinder 7.2 , After the change, the ETF valves close 5.7 . 5.8 , The closing time can be programmatically depending on the volume flow and / or sensor by temperature measurement in the outlet 5.8a ( 7 ) be determined. Comes loaded, recognizable at its relatively high temperature ETF on the exhaust valve 5.8 This will be closed. By increasing the pump power in the power circuit 5 the time span is shortened. By differently long opening times of the valves 5.7 . 5.8 can the amount of ETF in the cylinder 7.2 to be changed.

By releasing the expansion pressure and the diaphragm pressure regulator 5.6 will ensure that pressure equalization between expansion circuit 6 and energy circle 5 is present. The pressure compensation causes significantly the performance of the circulation pump 5.12 and the valve control 6.14 specify the ETF change quantity and that this is not the pressure in the cylinder 7.2 being affected. No energy needs to be expended under these conditions to get one in the cylinder 7.2 overcome higher pressure.

Optional noise screens 7.5 ( 7 ) prevent too much spatial distribution of the ETF cylinder 7.2 and regulate the exchange. Loaded ETF and unloaded ETF are "stratified". The viscosity of the ETF and the mesh size of the screens 7.5 must be coordinated with each other, which the expert easily succeeds.

The exchange can be carried out in surplus. Energetically, there is only a small loss corresponding to the energy required to circulate. Is a multiple quantity in the cylinder 7.2 , so this is heated continuously. An overfilling of the cylinder with ETF also ensures a permanently gas-tight "Ablasseparation", which ensures that when changing little EPM gas is entrained. As a further effect, the enlargement of the "heat exchanger surface" for the energy transfer from the ETF to the expansion medium occurs. The electronically controlled valves specify the changeover process and regulate the ETF change quantity over the opening time, regardless of the stroke rate of the piston. At the start of operation, due to the initially small potential or temperature differences between ETF and EPM, larger amounts of ETF are required to overcome the inertia of the system with "excess energy".

The diaphragm pressure regulator 5.6 is preferably - as already mentioned - a simple component consisting of two chambers, which are separated by a membrane. In this way, the pressure balance between the power circuit 5 and the expansion circle 6 carried out. This component is necessary when ETF change, so there is no relative pressure over the expansion circuit must be overcome. The pressure of the expansion circle 6 is equal to the pressure in the cylinder 7.2 during the ETF change. He separates expansion circle 6 and energy circle 5 physical and thermal, transmitting the pressure of the circles.

The expansion medium and the ETF are separated in two stages. The first separation already takes place in the cylinder 7.2 , The expanded gas is located above the ETF and is transmitted via the EPMAV 6.3 headed straight back to the WT3.

Incomplete gas, on the other hand, is carried along by the ETF when changing it. Therefore, between energy circuit 5 and expansion circle 6 a gas separation integrated (gas separator 5.10 ). This gas separation takes care of outside the cylinder 7.2 for the removal of the expansion medium from the ETF. The function of gas separation is essentially physical, due to the different densities of ETF and expansion medium. The size of the gas separator 5.10 depends on the length of stay of the ETF for degassing. The gas separation can also in the intermediate heat storage 5.1 Success - as described above. Here, however, there are conflicts with a flawless revolution and energy transfer.

During the stay of the ETF in the Gastrenner 5.10 In addition, a small amount of energy is absorbed by the expansion medium. The resulting increase in pressure or the gasification of the EPM ensure the transition of the expansion medium in the expansion circuit 6 , The transition takes place in the low-pressure region of the expansion circuit 6 instead of. The ETF is powered by the circulation pump 5.12 "Sucked" and in the intermediate heat storage 5.1 pumped back.

Also essential is the selection of the energy carrier fluid ETF. Here it must be noted that it must not enter into a chemical connection with the expansion medium EPM. The downstream degassing stage 5.4 at the intermediate heat storage 5.1 Eliminates small residual amounts of EPM and redirects them to the expansion circuit 6 ,

Small amounts of mixing are harmful to the process only if they significantly change the mass of the required medium in certain components. If the amount of foreign matter accumulates in a medium, there is the possibility of malfunctioning. When changing the mass of the ETF in the intermediate heat storage 5.1 is to be assumed by an insufficient energy transfer. He is therefore again separately "degassed". A compensation by an increase in volume is structurally simple to manufacture. Likewise, after a period of operation could follow a regular downtime in which the expansion medium can outgas.

One variant involves the use of two gas separators analogous to element 5.10 , While one is being charged, the other can outgas. The system thus achieves a 100% operating time.

For the best possible energy absorption with the lowest "resistance", the direct route is preferably chosen by the ETF to implement the energy transport in the EPM. For this purpose - as already mentioned - the EPM directly in the drive cylinder 7.2 . 7.2a injected into the ETF. In this way, the largest possible "heat exchanger surface" is guaranteed. This construction is referred to herein as "internal" (linear) drive. In contrast to the "external" (linear) drive, in which ETF and EPM interact only indirectly, ie without material contact or mixing, the already mentioned gas separation has to be interposed as a further step in the internal (linear) drive in order to recover the two media to separate.

For energy transport, a synthetic oil is preferably used as the energy carrier fluid used in the field of refrigeration oils / heat transfer oils. As a means of expansion, CO2 is the cheapest substance available. On the one hand, carbon dioxide is harmful to the climate but on the other hand it is also a natural gas and a necessary component in nature. The CO2 used here can be taken from the atmosphere. It is not "produced" in this plant because there is no burning of fossil fuels. The proposed use of CO2 is therefore not harmful to the climate. It is run in a closed circuit, only with defects there is a risk of release. However, the release is climate-neutral, as no more CO2 is released than was previously taken from nature.

Generally holds that ETF and EPM have no chemical or physical connection allowed to enter. The energy exchange should take place in a short period of time. The separation should be carried out without significant additional energy expenditure can. A purely physical separation due to the different Density is to be striven for.

Constructive is the already mentioned use of Schwallsieben 7.5 in the cylinder 7.2 limited a spatial distribution of the ETF in the cylinder. The flood screens 7.5 Keep the ETF back to prevent over the EPM exhaust valve 6.3 too large amounts in the expansion circle 6 be carried away. The grid structure and overall shape as well as the number of screens 7.5 will be adapted to the characteristics of the ETF, as has already been pointed out.

Furthermore, it is envisaged that the substantial amounts of ETF and EPM via two different ways out of the cylinder 7.2 be directed. The expanded CO2 is located above the ETF and can be routed directly to the WT3. Small amounts of CO2 are carried along by the ETF. These CO2 levels need to be further separated to maintain the respective masses of the ETF and EPM in the circuits and to limit mixing. The ETF is passed over the gas separator in the manner already described 5.10 guided. The gas separator 5.10 has the function of a "settling basin". The ETF will be "stored" there for a certain period of time and may outgas during that period. The intermediate storage takes place in layers, with the ETF molecules sinking. The CO2 absorbs energy from the ETF and gasses across the ETF. To further optimize the process, the gas separation can be operated with two alternately charged gas separators. Degassing with a short degassing phase during a program-controlled downtime is also a possibility, as already mentioned.

The transition of CO2 from the gas separator 5.10 in the expansion cycle 6 can be done in several ways:
The simplest and desired variant is based on the fact that the pressure in the two circles (expansion circle 6 and energy circle 5 ) is almost the same. This is due to the fact that the energy removal of the expansion medium in the WT3 and the appropriate pipe dimensioning create a low-pressure area ("suction area") in the inlet of the WT3. The CO2 can be sucked in by this relative negative pressure. A second effect is the suction due to the flow similar to a water jet pump.

A Electrically operated pump is the more expensive variant. she offers the possibility, precisely controlled the process and adapted to the operating situation perform. Sensors and solenoid valves complete this variant.

In a gas separator with a second chamber are the two chambers separated by a differential pressure valve. Increases by the outgassing in the first chamber the pressure, the CO2 flows into the second chamber. If the pressure in the second chamber rises above the pressure of the expansion circuit, then it opens another differential pressure valve, and the CO2 can overflow. advantage This method is the low construction costs with less prone technology.

The degassing is a necessary process, since gases the energy transfer in the intermediate heat storage 5.1 hinder. For process safety should therefore also in the intermediate heat storage 5.1 a gas zone will be set up. This gas can then pass through an auxiliary pump as needed to the expansion circuit 6 be promoted back. It is only to be expected with a small amount, since this is already the third separation point in the cycle.

In WT3 no deposition takes place. The liquefied CO2 and the ETF flow to the CO2 storage due to gravity 6.11 , A separation is also possible there. The ETF will do this in CO2 storage 6.11 collected below and sporadically pumped out. To control in this area, a photosensory evaluation can be carried out inexpensively. The fact that CO2 is a colorless gas and that the ETF is in a dark color leads to a clear visual identity.

The exhaust operation from the drive cylinder 7.2 can be controlled so that no significant amount of ETF in the expansion circle 6 so that during operation there is no cumulation of the ETF quantity in the expansion circle 6 one occurs. This means that a residual volume of CO2 in the cylinder 7.2 is left. The amount of ETF in the CO2 that reaches the bottom of the CO2 storage 6.11 flows, is immediately sucked again. Injection quantity control is designed to be "ETF-tolerant". This means that the injection quantity is adjusted based on the output power supplied. The larger the relative amount of ETF in the injection volume, the lower the power. The injection quantity is then increased according to the requirements. No separate components are required for this process.

A small amount of ETF in the expansion circle 6 can also be beneficial. The components of the expansion circuit are then lubricated by the ETF.

drive

The thermal drive device (also referred to herein simply as a "drive" or due to its exemplary embodiment also referred to as a "linear drive") represents the heart of the composite machine described and is denoted by the reference numeral 7 Mistake. Its special construction will therefore be described below with reference to the 7 to 11 more detail:
The drive 7 has the task of energy transfer from the energy circuit 5 to the expansion circle 6 , In addition, he is to convert the subsequent expansion of the EPM into linear kinetic energy. It transfers with a piston-cylinder arrangement, the energy from a so-called. Drive range in the so-called. Power range and outputs it to a compressor, a generator and / or to another preferably linear, ie moving rectilinear application. The compressor can itself be part of the refrigerant circuit 3 be (see above). The drive 7 is with the expansion circle 6 , the energy circuit 5 , optionally with the refrigerant circuit 3 and further optionally connected to a power supply circuit, the latter comprising said generator.

• 7.1 Zylinderblock: Hauptbestandteil dieser Baugruppe; nimmt praktisch alle anderen Baugruppen auf und verteilt über integrierte Bohrungen die Medien an die Ventile des Zylinders. Angeordnet ist der Zylinderblock unterhalb der WT-Einheit im Unterflurkasten 2.17. Material: Leichtmetall.
• 7.1a Zylinderkopf: Der Zylinderkopf ist Bestandteil des Zylinderblocks 7.1 und verschließt den Expansionsbereich. Er nimmt die Ein- und Auslassventile des EPM auf. Er nimmt den ETF-Raum und den Dämpfungsraum auf. Material: Leichtmetall;
• 7.1b Zylinderfußplatte: Die Zylinderfußplatte verschließt den Leistungsbereich des Verdichters (7.3b) gasdicht. Sie nimmt Lecköl auf und führt es der Leckölpumpe (7.21) zu. Nimmt in der Stromerzeugungsversion ggf. die Abnahmewicklung auf und führt die Stromstange (siehe unten). Stützt die Rückstellfeder (7.7) und hält die Vorspannung. Material: Leichtmetall;
• 7.2 Zylinder: Der Zylinder nimmt die Baugruppen Antrieb und Arbeitsmittel (Generator- und/oder Verdichtermittel) auf. Ein Anschlag 7.4a für den Kolben 7.4 spart im oberen Bereich einen ETF-Raum und einen Dämpfungsraum aus. Der Anschlag 7.4a kann Bestandteil des Zylinderblocks oder als Einzelbauteil eingesetzt sein. In der Bauform als Einzelbauteil nimmt der Zylinderkopf (7.1a) den ETF-Raum und den Dämpfungsraum auf. Eine Ausführung aus technischer Keramik erhöht die Verschleißfestigkeit. Angeordnet ist der Zylinder im Zylinderblock 7.1. Material: Leichtmetall;
• 7.3a Lineargenerator: Der Lineargenerator umfasst alle Bauteile, die der Stromerzeugung dienen. Er ist unterhalb des Expansionsbereiches (11) oder integriert im Expansionsbereich (8 bis 10) angebracht.
• 7.3b Verdichter: Der Verdichter ist im Leistungsbereich unter dem Kolben (7.4) angebracht und Bestandteil des Zylinders 7.2.
• 7.4 Kolben: Der Kolben ist im Zylinder als Freikolben mit Rückstellfeder integriert. Er trennt den Expansionsraum vom Leistungsbereich und überträgt die Energie linear, d. h. mittels einer geradlinigen Bewegung. Material: Leichtmetall oder Keramik.
• 7.5 Schwallsiebe: Die Schwallsiebe sind vorzugsweise ein Bestandteil des Kolbens 7.4. Sie steuern die Schichtung des ETF beim Wechsel. Sie vermindern nach der Expansion und beim Ablassen des Expansionsmittels EPM das Mitreißen von ETF in den Expansionskreis 6. Im Zentrum der Schwallsiebe befindet sich jeweils ein Durchbruch für die Injektordüse (7.10). Material: Leichtmetall;
• 7.7 Rückstellfeder: Die Rückstellfeder übernimmt die Rückstellung des Kolbens 7.4 nach der Arbeit und schiebt expandiertes restliches EPM aus. Anordnung: im Zylinder 7.2 unterhalb des Kolbens 7.4. Stellt den Kolben 7.4 bei Betriebsstillstand in die Startstellung. Material: Federstahl;
• 3.7a, 3.9a, 5.7a, 5.8a, 6.3a, 6.9a Zulauf- und Ablaufbohrungen: Führen im Zy linderblock 7.1 die Medien an die entsprechenden Ventile des Zylinders 7.2. Ausführung in Guss mit mechanischer Nachbearbeitung. In die Bohrungen sind Rückschlagventile eingesetzt, die verhindern sollen, dass bei sich überschneidenden Vorgängen Medien vom Zylinderdruck in die „falsche Richtung” entgegen dem Kreisprozess gefördert werden.
• 3.7, 3.9, 5.7, 5.8, 6.3, 6.9 Magnetventile: Die Magnetventile regeln den Zulauf der Medien zum Zylinder 7.2. Alle Magnetventile sind vorzugsweise baugleich. 6.13a Injektordüse (vgl. 6): Die Injektordüse ist in den Zylinderkopf 7.1a eingeschraubt und dem EPM-Ventil nachgeschaltet. Sie taucht in das im Zylinder 7.2 befindliche ETF ein. Durch die Düse 6.13a wird das EPM optimal im ETF verteilt.
• 7.13 Permanentmagnet: Der Permanentmagnet ist ein möglicher Bestandteil des Lineargenerators 7.3a und unterhalb des Kolbens 7.4 angebaut (8) oder in diesen integriert.
• 7.14 Erregerwicklung: Die Erregerwicklung gemäß den 9 bis 11 ist Bestandteil des Lineargenerators 7.3a. Sie ist eine Alternative zum Permanentmagnet 7.13 (8). Sie kann an den Kolben 7.4 angebaut oder in diesen integriert sein (9 und 10). Sie hat den Vorteil der Regelbarkeit der Stromproduktion.
• 7.15 Abnahmewicklung: Auch Stator genannt; ist um die Erregerwicklung 7.14 herum angeordnet. Sie ist im Zylinder 7.2 oder außerhalb des Zylinders, beispielsweise um den Zylinder herum, angeordnet.
• 7.16 Stromstange: Die Stromstange versorgt die Erregerwicklung 7.14 mit Spannung. Sie ist beispielsweise unterhalb der Erregerwicklung 7.14 angeordnet (8 bis 10). Sie wird von der Zylinderfußplatte 7.1b geführt und nimmt die Kontaktbahnen (7.19) auf.
• 7.17 Führungsnut: Die Führungsnut verhindert, dass sich die Stromstange 7.16 dreht. Sie dient dazu, die Polarität der Kontaktbahnen (7.19) radial zu fixieren. Sie ist ein Bestandteil der Stromstange 7.16 und der Zylinderfußplatte 7.1b.
• 7.18 ovaler Querschnitt (der Stromstange 7.16): alternative Lösung zur radialen Fixierung der Stromstange 7.16. Der ovale Querschnitt oder ein beliebiger anderer Querschnitt mit Vorzugsrichtung verhindert bei Vorsehen eines komplementären Durchbruchs in der Zylinderfußplatte 7.1b, dass sich die Stromstange 7.16 dreht, so dass die Kontaktbahnen (7.19) immer an den Schleifkohlen (7.20) anliegen (axiale Fixierung).
• 7.19, 7.19' Kontaktbahnen: Die Kontaktbahnen sind ein Bestandteil der Stromstange 7.16. Sie sind elektrisch getrennt und verbinden die Schleifkohlen (7.20) mit der Erregerwicklung 7.14.
• 7.20 Schleifkohlen: Die Schleifkohlen übertragen die elektrische Spannung an die Kontaktbahnen 7.19.
• 7.21 Leckölpumpe: Die Leckölpumpe fördert sporadisch aufgefangenes Lecköl (ETF) in den Energiekreis 5 zurück. Sie ist ein Anbauteil des Zylinderblocks 7.1. Das Lecköl läuft der Leckölpumpe allein aufgrund der Schwerkraft zu. Alternativ kann ein nicht gezeigter ETF-Sammelbehälter vom Anlagendruck ventilgesteuert in den Energiekreis 5 entleert werden (Ausblasen).
• 7.22 Sensorik (nur in 7 angedeutet): zur Überwachung des Verdichtungsdrucks, des Expansionsdrucks, der ETF-Temperatur, der Kolbenstellung und des Leckölstands.
• 7.23 Steuerung (nur in 7 angedeutet): Die Steuerung erfolgt gemäß der Beschreibung zu den 5 und 6 (Energiekreis bzw. Expansionskreis). Eine Leckölsteuerung steuert bei Bedarf die Leckölpumpe oder den Entleervorgang des Sammelbehälters. Die Leckölsteuerung erfolgt autark über Flüssigkeitserkennung und kann in die Leckölpumpe oder den Sammelbehälter integriert sein.

The drive 7 comprises in the embodiment according to the 7 to 11 at least some of the following components, some of which already based on 6 were described:

• 7.1 Cylinder block: main component of this assembly; Adopts virtually all other components and distributes the media to the valves of the cylinder via integrated bores. The cylinder block is arranged below the WT unit in the underfloor box 2.17 , Material: light metal.
• 7.1a Cylinder head: The cylinder head is part of the cylinder block 7.1 and closes the expansion area. He picks up the inlet and outlet valves of the EPM. He picks up the ETF room and the muffling room. Material: Alloy;
• 7.1b Cylinder base plate: The cylinder base plate closes the power range of the compressor ( 7.3b ) gas-tight. It picks up leak oil and leads it to the leak oil pump ( 7.21 ) too. If applicable, picks up the pickup coil in the power generation version and runs the power bar (see below). Supports the return spring ( 7.7 ) and holds the bias. Material: Alloy;
• 7.2 Cylinder: The cylinder accommodates the components drive and working means (generator and / or compressor means). An attack 7.4a for the piston 7.4 Saves in the upper part of an ETF room and a damping room. The stop 7.4a can be part of the cylinder block or used as a single component. In the design as a single component takes the cylinder head ( 7.1a ) the ETF room and the damper room. A version made of technical ceramics increases wear resistance. Arranged is the cylinder in the cylinder block 7.1 , Material: Alloy;
• 7.3a Linear generator: The linear generator includes all components that are used to generate electricity. He is below the expansion area ( 11 ) or integrated in the expansion area ( 8th to 10 ) appropriate.
• 7.3b Compressor: The compressor is in the power range below the piston ( 7.4 ) and part of the cylinder 7.2 ,
• 7.4 Piston: The piston is integrated in the cylinder as a free piston with return spring. It separates the expansion space from the power range and transmits the energy linearly, ie by means of a linear movement. Material: light metal or ceramic.
• 7.5 Sweep screens: The screens are preferably part of the piston 7.4 , They control the stratification of the ETF when switching. They reduce the entrainment of ETF into the expansion circuit after expansion and release of the EPM expansion agent 6 , In the center of the flood screens is in each case a breakthrough for the injector nozzle ( 7.10 ). Material: Alloy;
• 7.7 Return spring: The return spring takes over the return of the piston 7.4 after work and expands expanded residual EPM. Arrangement: in the cylinder 7.2 below the piston 7.4 , Represents the piston 7.4 at standstill in the starting position. Material: spring steel;
• 3.7a . 3.9a . 5.7a . 5.8a . 6.3a . 6.9a Inlet and drain holes: Guide in the cylinder block 7.1 the media to the corresponding valves of the cylinder 7.2 , Cast version with mechanical finishing. In the holes check valves are used to prevent that in intersecting processes media from the cylinder pressure in the "wrong direction" are promoted contrary to the cycle.
• 3.7 . 3.9 . 5.7 . 5.8 . 6.3 . 6.9 Solenoid valves: The solenoid valves regulate the supply of media to the cylinder 7.2 , All solenoid valves are preferably identical. 6.13a Injector nozzle (cf. 6 ): The injector nozzle is in the cylinder head 7.1a screwed in and the Downstream EPM valve. She dives into the cylinder 7.2 one ETF. Through the nozzle 6.13a the EPM is distributed optimally in the ETF.
• 7.13 Permanent magnet: The permanent magnet is a possible component of the linear generator 7.3a and below the piston 7.4 grown ( 8th ) or integrated into it.
• 7.14 Excitation winding: The exciter winding according to the 9 to 11 is part of the linear generator 7.3a , It is an alternative to the permanent magnet 7.13 ( 8th ). She can attach to the piston 7.4 grown or integrated into these ( 9 and 10 ). It has the advantage of controllability of electricity production.
• 7.15 Acceptance winding: also called stator; is about the excitation winding 7.14 arranged around. She is in the cylinder 7.2 or outside the cylinder, for example around the cylinder.
• 7.16 Power bar: The power bar supplies the excitation winding 7.14 with tension. It is below the excitation winding, for example 7.14 arranged ( 8th to 10 ). It is from the cylinder base plate 7.1b guided and takes the contact tracks ( 7.19 ) on.
• 7.17 Guide groove: The guide groove prevents the power bar 7.16 rotates. It serves to increase the polarity of the contact tracks ( 7.19 ) to fix radially. It is part of the power bar 7.16 and the cylinder foot plate 7.1b ,
• 7.18 oval cross section (the power bar 7.16 ): alternative solution for radial fixation of the power bar 7.16 , The oval cross-section, or any other preferred-directional cross-section, prevents provision for complementary breakthrough in the cylinder foot plate 7.1b that is the power bar 7.16 turns so that the contact tracks ( 7.19 ) always on the carbon brushes ( 7.20 ) abut (axial fixation).
• 7.19 . 7.19 ' Contact tracks: The contact tracks are a component of the power bar 7.16 , They are electrically isolated and connect the carbon brushes ( 7.20 ) with the exciter winding 7.14 ,
• 7.20 Carbon brushes: The carbon brushes transmit the electrical voltage to the contact tracks 7.19 ,
• 7.21 Leak oil pump: The leak oil pump sporadically pumps collected oil (ETF) into the energy circuit 5 back. It is an attachment to the cylinder block 7.1 , The leak oil flows to the leak oil pump solely by gravity. Alternatively, an ETF sump, not shown, can be valve-controlled by the system pressure into the energy circuit 5 be emptied (blow out).
• 7.22 Sensor technology (only in 7 indicated): to monitor the compression pressure, the expansion pressure, the ETF temperature, the piston position and the leakage oil level.
• 7.23 Control (only in 7 indicated): The control is carried out according to the description of the 5 and 6 (Energy circuit or expansion circuit). If necessary, a leak oil control controls the leak oil pump or the emptying process of the collection container. The leakage oil control is self-sufficient via liquid detection and can be integrated into the leak oil pump or the collecting tank.

The drive 7 is advantageously in the underfloor box 2.17 ( 2 ) appropriate. His cylinder 7.2 preferably consists of a light metal cast block. The main production steps are carried out mechanically. Cylinder head and cylinder are preferably made in one piece. The cylinder 7.2 can also be used as a separate component in the associated drive block. The cylinder inner wall can be equipped with a wear protection, as it is known from the construction of internal combustion engines. The load is compared to a combustion engine, however, comparatively low. The insertion of a ceramic bushing in conjunction with a ceramic piston can further increase the wear resistance with lower lubricant requirement.

The cylinder block contains the inlet and outlet bores already mentioned above for connecting the power circuit 5 , the expansion circle 6 and the refrigerant circuit 3 , In the cylinder 7.2 is the piston 7.4 with smoke screens 7.5 and possibly the return spring 7.7 , The cylinder 7.2 has two areas, namely the expansion area, where thermal energy is converted to linear motion, and the power range, which converts the energy of linear motion into the desired power. In the present case, the use for compression offers 7.3b of the refrigerant 3.1 or for the production of electrical energy with a (linear) generator 7.3a at ( 8th to 11 ).

For the pure compressor version ( 7 ) a thermal insulation must be inserted between the drive area and the compressor area. This prevents energy from flowing from the ETF to the refrigerant to be compressed. The reverse case occurs after compression; Here, the compressed refrigerant has a higher temperature. The training of the piston 7.4 in ceramics offers the best conditions for this. Controlled feeding of media into the cylinder 7.2 takes place via the mentioned solenoid valves. The solenoid valves are in the cylinder block 7.1 screwed in and sealed the said holes to the outside. About an inserted valve seat, the connection of the holes with the cylinder is prepared in a conventional manner. The cylinder block 7.1 is in the power range through the cylinder base plate 7.1b tightly closed. The cylinder base plate captures oil leakage (ETF) from the lubrication of the piston 7.4 on. About the leak oil pump 7.21 the leak oil is then the power circuit 5 fed again.

In the upper area of the cylinder 7.2 there is a damping room 6.18 , The damping chamber is filled with a residual amount of expansion agent. This residual quantity has the function of a gas damper or gas cushion. The gas damper brakes the piston 7.4 and prevents during operation a striking of the piston in the upper cylinder area.

The damping chamber 6.18 should be as small as possible, so that no pressure can build up when the system is shut down, the piston 7.4 moved from the upper position. Optionally, shortly before the start, "pressure is released". During a longer standstill with the result of equipotential bonding / cooling, the influence on the piston position due to the change in volume is only slight. Opening the ETF valves during system standstill allows the residual pressure to drain into the energy circuit 5 ,

In the variants for electricity production ( 8th to 11 ), the area of the compressor against a linear generator 7.3a be exchanged. To the piston 7.4 is according to 8th in the lower part of the permanent magnet 7.13 or alternatively arranged a field winding. The foot plate 7.1b carries the acceptance winding 7.15 and leads them into the cylinder 7.2 , The excitation winding 7.14 ( 9 to 11 ) is via a power bar 7.16 coming out of the cylinder 7.2 out, supplied with excitation voltage. The power bar 7.16 is mounted against rotation. The rotation is done for example via a in 11 shown guide groove 7.17 or an oval or otherwise provided with a preferred direction cross-section of the power bar 7.16 , The carbon brushes 7.20 transmit the voltage to two electrically isolated contact tracks 7.19 . 7.19 ' ,

According to 10 can basically be combined in one cylinder power generation and compression in one power range. If only heat load is requested, the linear generators will run 7.3a , Especially in the case of variants with permanent magnet 7.13 ( 8th ), but constantly with. There are thus at least no-load losses. For those drives, which are provided for self-supply of the system, there are no conflicts here, because a power demand for the electrically driven components, such as fans and pumps, is always and can be covered so cost-effectively, at least partially.

The Construction of the cylinder with internal energy transfer (injection EPM in ETF) has the advantage that the cylinder materials in terms of function and wear optimally can be tuned, because the other property, heat energy transfer to have to, eliminated. Another advantage lies in the simplified geometric shape and the cheaper Production.

The exemplary return spring shown 7.7 or alternatively used return means should have a design that has a linear force curve over the entire piston stroke. This means that the piston does not require much more than the preload force to perform the stroke.

In operation for power generation, the drive power is practically doubled, because here, in contrast to the compressor operation, the return path to the energy conversion can be used. The energy in this case is during expansion in the return spring 7.7 saved and returned by this on the way back. The amount of ETF, the amount of EPM and the restoring force of the spring 7.7 are suitably adapted to this condition. Being on an energy conversion during the return of the piston 7.4 waived, the restoring force of the spring 7.7 be sized so that the generator reactive power can be overcome.

Alternatively, the linear drive 7 deviating from the embodiment according to 7 also be combined with an external pressure generator or generator. This is in 12 respectively. 13 in the context of a double piston arrangement of drive 12 and compressors 12.5 with separate pressure generator 14 which will be discussed in more detail below (cf. 14 ).

Of the primary Advantage of such an arrangement is that the processes expansion work on the one hand and pressure generation or power generation on the other the ETF change in spatially separate modules take place and run parallel in time can. By separating the processes in their own assemblies, the optimal (geometric) Form chosen become. In particular, the shape of the expansion cylinder is no longer by the (now no longer required) recording of ETF charged. In consequence, can in the pressure generator optimizes the pre-pressure zone and the loading zone become.

In a separate pressure generator 14 can hold a large volume of ETF. As a result, the energy transfer is carried out with only a small temperature change of the ETF. The nearly constant temperature level of the ETF with respect to the EPM during the energy transfer leads to a rapid and process-reliable evaporation of the EPM and the generation of pressure. A preferred embodiment of the separate pressure generator 14 is below based on 14 described in more detail.

With reference to 12 can ever drive cylinder 12b several pressure generators 14 be provided. The number is determined by the Period of time from injection to pressure generation in the admission pressure zone (cf. 14 ). Another influence is the desired number of cycles and thus the power per cylinder. Increases the number of pressure generators 14 , depending on the size of the system, a cylinder may be saved or the number of cycles increased.

Already With a power cylinder can be flexible on the conditions of Load or plant size received become. The power adjustment of the cylinder is in a wide range Range possible. It can identical cylinder for different load cases be used.

The separation of EPM and ETF is in the design with external pressure generator 14 preferably already carried out in the pressure generator. Residual amounts of ETF accumulate in the EPM storage tank and are then pumped back into the energy circuit with an auxiliary pump ETFP. Residual amounts of EPM accumulate in the ETF memory are deposited there (pumping agent EPMP).

The energy circuit 5 is pressurized by the expansion circle 6 separated. The energy circuit 5 does not have to be built pressure resistant, so that the related effort is reduced.

Furthermore, on the cylinders 12b . 12.5b according to 12 No additional piston reset assembly required. The working stroke of the opposite side of the drive double piston 12a takes over the provision. The control of the provision goes into the control of the work of the opposite side. There are no separate components required. By means of a load-oriented control, the required restoring force is automatically included.

Every cylinder 12b . 12.5b is thus used twice. Two working strokes offset by 180 ° ensure uniform performance in both directions. In particular, this "regular" motion course has a positive effect on a properly connected linear generator 7.3a ( 13 ) out. The effort to process the generated electricity decreases. In addition, the efficiency is increased.

14 shows an embodiment of the already mentioned several times pressure generator 14 which basically has a mirror-symmetrical arrangement with two pressure generating cylinders. During the injection of the EPM into the pressure generator 14 are the ETF valves 5.7 . 5.8 and the overflow valve 14.5 closed. The isolation valve 14.1 and the injection valve 6.13 are opened. The amount of EPM required for the power stroke is set and injected by the controller based on the pressures and the temperature potential. In the loading zone, the EPM flows through the ETF and absorbs energy. After energy absorption, the EPM passes through the separation area / isolation valve 14.1 and flows through the ETF separator 14.2 ,

The isolation valve 14.1 will be closed now. It closes the loading zone in the wet area. This avoids pressure being built up by trapped EPM in the loading zone. The energy circuit 5 is characterized by the pressure of the loading zone and the expansion circuit 6 separated. The energy stored in the pre-pressure zone in the form of pressure can now open the opened overflow valve 14.5 happen and the butt of the in 14 Driving cylinder not shown, the invention in this context not on the double piston assembly 12 . 12.5 according to 12 or 13 is limited. At the same time, the ETF can be changed or replaced in the loading zone. When the work has been done, the piston has reached the lower point or generally at the reversal point of its movement, the EPM outlet valve on the working cylinder opens. The working pressure escapes from the pre-pressure zone and the working cylinder into the expansion circuit. After pressure equalization, the overflow valve becomes 14.5 on the pressure generator 14 closed. The isolation valve 14.1 and the EPM injector 6.13 to open. The energy transfer begins again. The EPM outlet valve 6.3 on the working cylinder (cf. 12 and 13 ) closes before the piston has arrived in its upper position, ie the other reversal point of its movement. The EPM residual volume forms a gas cushion for impact damping, as already described above.

to cushioning Also a variant with a "premature start of work" can be realized. For this purpose, the overflow valve even before reaching the reversal point and thus the striking of the piston opened. The incoming EPM, the primary intended to perform work, brakes the piston and urges this with the for the following work necessary pressure.

In the course of emptying the working cylinder, an intermediate step (intermediate cycle or standstill cycle) may alternatively be provided. For this purpose, the start of work on the opposite side must be delayed accordingly. In the double piston arrangement according to 12 or 13 is alternately per piston always with two pressure generators 14 according to 14 Pressure provided.

Hereinafter, preferred embodiments of the arrangements according to the 12 to 14 more detail:
A drive rod 12.1 connects the two pistons 12a . 12.5A the double piston arrangement 12 . 12.5 according to 12 , The pistons and the drive rod are preferably made of technical ceramic. High wear resistance, chemical and thermal stability and low lubrication requirements are the reasons for choosing this material. Between drive and compressor ( 12 ) is a ceramic insulating plate 12.2 , This insulating plate guides the drive rod and seals the drive against the load. The piston is guided on the wall of the associated cylinder and seals ge against this. Manufacturing tolerances between the guides can be compensated for by an optional "slidable eccentric arrangement" of the cylinders relative to the insulating plate. The sealing surface 12.3 between insulating plate and drive rod is dimensioned so that a wide overlap area is given. The drive rod can be made with one of the pistons in one piece. The second piston ( 12 ) or the excitation winding 7.14 of the generator 7.3a ( 13 ) are fastened to the drive rod with a cross bolt (not shown). Alternatively, a combination of metal and ceramic can be used for the drive rod. In this case, a tubular ceramic drive rod is preferably reinforced in the interior by a metal rod. The ceramic cladding takes over the leadership and shear forces, the metal rod takes over the tensile forces. The metal bar should be made of an elastic alloy, so that thermal expansion problems are avoided by appropriate bias. To screw the metal rod, the appropriate fasteners, z. B. nuts, complete with the piston crown plan.

During operation, it is necessary - as already described above, the piston before striking the valve plates 12.4 the double piston arrangement 12 the latter, in accordance with the 12 and 13 the overflow channels 12.6 for the EPM. High running noise and wear would otherwise be the result. In the compressor drive ( 12 ) there is already a damping by the compression work, since the piston is braked by the load case. Precise control over the valves and the gas exchange, in which a remaining gas cushion takes over the stop damping, increases the efficiency and requires no separate components. A gas cushion can be realized both in the compressor and in the drive cylinder (see above). The pressure difference between the cylinder and the compressor circuit or expansion circuit serves to control the process. The gas cushion can also be influenced by an opening time of the EPM exhaust valve calculated by the control.

When using a linear generator ( 13 ), additional damping may be realized in an electromagnetic manner. In this case, the voltage of the excitation winding is briefly increased sharply when He reach the stroke end, so that the piston is braked and a striking is prevented. Separate components are not required here. Another way of damping is to increase each at the stroke end, the effective number of windings by appropriate switching of turns so that the desired braking effect occurs. At the start of work, there is a high cylinder pressure in the expansion cylinder, which can overcome the braking range. A short-term disconnection of the excitation voltage is another option for releasing the "brake".

The energy absorption of the EPM is on the loading zone in the pressure generator ( 14 ) limited. Therefore, before the overflow of the EPM into the drive cylinder, it must be charged with energy as much as possible. The pressure generator is preferably constructed in an elongated form for this purpose, whereby the EPM travels a relatively long distance therein. This path lengthens the energy transfer time in the pressure generator, and the EPM optimally absorbs the energy. The separation of the pressure generator from the working cylinder also offers the advantage that the ETF change in the pressure generator for the next power stroke can already take place during the ejection process for the EPM in the drive cylinder.

advantageously, the arrangement further comprises a sensor, not shown, for the piston position in the working cylinder. The sensor can be designed in an optical design and provides a signal as the piston advances. The signal can be used to control the drive as a function of the piston position be used. additionally or alternatively, the piston position also on the pressure conditions be determined in the cylinder relative to the EPM circle. The pressure control has a lower construction cost and is less prone to failure. There may be other sensors, z. B. Reed contacts or inductive sensors are used.

The EPM must be in the pre-pressure zone of the pressure generator 14 be kept in a small volume at high pressure. The pre-pressure and the volume are determined by the necessary working pressure. This is achieved at the end of the working cycle in the lower piston position of the piston in the working cylinder. In the calculation of the working energy, the energy required for pushing out the EPM in the opposite cylinder must be included in the load case. This energy is determined by the pressure in the expansion circuit. Since this pressure varies according to the ambient temperature and the operating phase, the EPM injection quantity must be adjusted accordingly. After pushing out is located in the cylinder only the gas cushion for the stop damping. The pressure of the gas cushion is determined by the volume and the Pressure of the piston at the end of the working stroke of the opposite side. This pressure or this amount of energy is used again in the next cycle, but must be overcome by the form with. The energy of the gas cushion is therefore neutral in the balance and does not include effective work. Therefore, the gas cushion should be kept as small as possible.

For the load case, it must be considered that not the entire length of the cylinder can be used, but that the gas cushion must be taken into account. The gas cushion and thus the stroke will fluctuate within a tolerance. In any case, the compressor (in particular according to 12 ) have already delivered the necessary power to the compressor circuit before the end of the stroke. A linear generator can be adapted by appropriate execution of the winding.

As already noted, the injection amount of EPM is dependent on the temperature difference between EPM and ETF. The higher the difference, the smaller the required injection quantity. The injection quantity is metered according to the load case, as already stated. The injection quantity is program-controlled according to the temperature values for ETF and EPM and is corrected by the pressure in the admission pressure zone as well as the performance result in the load case. Deviating from the other systems is in the embodiments according to the 12 to 14 a premature termination of the energy transition is not provided. A pressure sensor in the pre-pressure zone of the pressure generator can be included for monitoring and controlling the injection quantity. A premature termination would cause the inclusion of EPM in the loading zone. As a result, the loading zone would be under pressure during the ETF change. This pressure would be delivered to the ETF circuit, so that it would have to be laboriously built pressure-resistant, which is just to be avoided. Furthermore, a large amount of EPM would circulate in the ETF cycle and would have to be laboriously separated.

The injection pressure is determined by the pressure in the admission pressure zone with the separating valve open 14.1 certainly. The pressure in the pre-pressure zone corresponds to the mentioned suction pressure / low pressure in the expansion circuit 6 , The injection pressure must substantially exceed this pressure to prevent ETF from the loading zone into the expansion circuit 6 penetrates. Since the pressure in the expansion circuit varies according to the operating phase and the ambient temperature, the pressure difference in the expansion circuit can be used only to a limited extent for injection. Therefore, a high pressure pump HDP (see. 12 or 13 ), with which a constantly high optimum injection pressure is generated. Here, the back pressure in the pressure generator control technology can be considered.

When calculating the injection quantity and the amount of energy, the expansion volume must be taken into account. The expansion volume consists of the cylinder volume and the pre-pressure zone and the overflow channels (behind 14.5 ) in the valve plate 12.4 ( 12 . 13 ), see. reference numeral 12.6 , When the full expansion volume is reached, the piston is in the lower stroke end and there is working pressure.

The Volume of the transfer ports should as low as possible being held. Located in the overflow channels after the overflowing the same specific amount of energy as in the cylinder. This volume is an additional Expansion area. The piping volumes of possible different pressure generators or pre-pressure zones to the respective cylinder should be as possible be equal. Alternatively you can different volumes with an adjusted injection quantity be equalized at EPM.

For each cylinder - as already mentioned - at least two pressure generators 14 be provided. The chronological sequence requires that at the time of starting work, at which the working piston is at the upper end of the stroke, ie at 0 ° stroke, from a pressure generator, which was just involved in the previous power stroke, still no pressure can be removed because the available time for pressure generation is insufficient. Therefore, two pressure generators alternately provide the form. For the generation of pressure therefore applies: Time span for the pressure generation = cycle / number of pressure generators. The volume of the ETF in the charging zone is chosen so that the necessary amount of energy can be delivered to the EPM for one working cycle even with a slight excess temperature of the ETF and normal operating temperature.

In The loading zone will be the energy of the ETF in the described way submitted to the EPM. The EPM is thus loaded. To this process to ensure, it is necessary to give the EPM one possible large "heat exchanger surface" and a high temperature difference between ETF and EPM available put. The final temperature of the EPM should be chosen to be safe in the gaseous Condition is transferable and due to its density according to the energy absorption in the Form pressure zone is located at the top of the cylinder. The size and design of the loading zone should offer the EPM a long way to make it sufficiently there can absorb thermal energy.

The viscosity of the ETF and the structure of the ETF ETF separators prevent ETF from entering the pre-compression zone and the working cylinder in larger quantities. The ETF separator is preferably similar to a ball filter. By separating the pressure generation from the working cylinder is basically for the separation of any period of time available. This period of time is used to overcome the constructive high volume resistance of the separator. At the same time, the high volume resistance prolongs the time span of the energy transfer in the charging zone. This has a positive effect on the charging process. ETF and EPM should split as completely as possible. The entrainment of a small amount of ETF in the EPM is required to lubricate the working cylinder. Another assembly for media separation is therefore no longer provided in the present embodiment.

The isolation valve 14.1 for the ETF change or exchange is in the pressure generator ( 14 ), as already stated. It separates the loading zone and the pre-pressure zone. The closing area is arranged to be below the ETF level and below the ETF separator. As a result, the pressure of the pre-compression zone is separated from the loading zone. It is exploited here that a (incompressible) liquid can not store pressure. The entire power circuit can thereby be operated at low pressure. It can be assumed that the pressure in the energy circuit does not rise above 3 bar due to the low amounts of EPM entrained. For the ETF change, a commercially available circulation pump can be used. During injection, the isolation valve is opened. If the power consumption of the EPM in the charging zone is too low, the charging time may need to be extended. For this purpose, the separating valve is always closed and opened and allows only EPM with sufficient charge, ie overflow correspondingly high pressure in the pre-pressure zone.

The level of the ETF in the loading zone must be maintained exactly. If the level is too high, the pre-pressure zone decreases. If the level is too low, the separation of the pre-pressure zone, ie the described separation of the gas pressure is not guaranteed. To control the level, a sensor, not shown, can be used in accordance with the principle of the communicating tubes connected to a low pressure in the energy circuit. In an ETF reservoir, for example, a second chamber is installed for this purpose. This is connected to the actual ETF supply via an adjustable pressure maintenance valve. It uses the pressure of the entrained EPM in the ETF or an EPM supply deliberately created when the system is started. This pressure causes ETF to be pressed to the level. During assembly, the pressure is adjusted so that the vent 14.3 the loading zone is just leaving some ETF. During operation, the level will be adjusted by a sensor 14.4 monitored and readjusted by the controller. During operation, entrained EPM is allowed to pass through said pressure holding valve into said second chamber. This is constantly emptied by an auxiliary pump. In this way, an adaptation to differences in height of the ETF container relative to the level level can be carried out in the system design. A parallel-connected diaphragm pressure equalization vessel (not shown) further secures the level if necessary.

The EPM overflow lets the stored pressure from the pre-pressure zone in the working cylinder overflow. It stays almost while of the entire work cycle over about 355 ° open. Only during the Formation of the gas cushion is closed. From this point the pressure build-up in the pre-pressure zone can begin. During the injection and the pressure build-up, the EPM overflow valve is closed. Thereby prevents ETF from being blown into the working cylinder.

A special embodiment of the present machine described sees that external starting energy is required only for drives with compressor load is. Ideally, it is only in the state of equipotential bonding at the start of operation external energy needed to heat the ETF, the heating preferably performed electrically becomes. Electrical components such as pumps and fans are supplied with mains power. Such a start of operation (cold start) is necessary only in rare cases. The machine stops in usually without a supply of external energy a bootable state by appropriately heated, charged ETF upright. With increasing Energy in the plant, the linear generators are put into operation, and the power supply is turned off. As already emphasized several times However, the invention is not limited to such an embodiment limited, but also includes embodiments in which continuously external (electric) energy has to be expended to complete the process or keep the corresponding thermal compound machine running.

The addressed heating can basically at least three Species performed 1) installation of a water heater in the power circuit; 2) heating up an ETF supply that needs to be large enough, at least to ensure the (cold) start; and 3) direct heating of the charging zone (glow plug), during which Heating no ETF change is performed.

To the storage tank for the EPM is according to 12 or 13 in the lower area an auxiliary pump ETFP connected to the ETF. It promotes the ETF collected there due to the physical properties (density) back into the energy circuit 5 ,

Analog is according to 12 above the intermediate heat storage or the ETF supply or alternatively, depending on the system configuration, an auxiliary pump EPMP for the EPM is installed at the uppermost point of the energy circuit. Here, due to the physical property (density), the EPM accumulates and is returned to the expansion circuit by the auxiliary pump 6 pumped.

The 15 and 16 show a further variant of the proposed compound machine in the form of a so-called. Thermal reciprocating compressor, the EPM alone, ie without ETF in a working cylinder 7.2a introduced or injected and evaporated there. The cylinder 7.2a is thermally to the heating circuit 4 is connected and is heated accordingly, so that this compound machine works without additional energy circuit or without additional energy carrier fluid, which is generally possible:

15 shows left a working cylinder 7.2a with a piston 7.4 , which takes on one side of the expansion work of the EPM after injection into the cylinder chamber and this on the other side as compression work to the refrigerant of a primary energy circuit (PEK, here for a heat pump) again. The EPM circuit represents a secondary energy circuit (SEK). The piston 7.4 separates PEK and SEK and transfers the pressure. However, this does not require a translation.

to Adaptation of different pressures of secondary energy circuit (SEK) and primary energy circuit (PEK), the compressor element with a hydraulic transmission will be realized. Furthermore can be a hydraulic translation be realized in the aforementioned embodiments.

With a graduated in diameter piston or two pistons with rigid pipe joint and matching cylinders, it is possible with little effort different pressures or To move volume. The suitable material is preferably highly thermally conductive and made of metal. Preferably, a light metal is used. Of the Cylinder block can be produced inexpensively in the die casting process. in the Range of the cylinder wall is due to the required gas tightness a precise one Fine machining required. The surface should also be with a wear protection be provided. The burden and effort are but in comparison low to a cylinder of an internal combustion engine.

The size of the working cylinder 7.2a is arbitrary. It can be optimally adapted to the environment and the operating conditions. The behavior of the expansion medium, the heat flow, the heat exchanger surface, and the inertia of the piston are requirements that must be considered. For example, the medium is in the center of an oversized cylinder u. U. no sufficient heat exchanger surface available.

The construction can according to 16 several such cylinders 7.2a to limit pulsations in the PEK and always have a pressure drop in the condenser for the EPM available. As the cost per compressor 7.8 is not very high, inertia in the system can be compensated by the number of drives. A longer time during pressure build-up is compared with a corresponding number of drives to compensate. Especially in the phase shortly after the start is expected by a low temperature gradient greater inertia.

In the working cylinder 7.2a For lubrication purposes, a suitable fluid should be entered. This lubricating fluid 16.1 (eg oil) takes over the fine sealing and lubrication. This is according to 16 between the compressor side and working side a lubrication groove 16.2 in the pistons 7.4 incorporated. This lubrication groove is connected in a certain piston position outside the gas range (expansion range) with an oil reservoir and is supplied from there or thermally balanced. It is possible to pressurize the oil supply by heating a gas bubble acting as an accumulator. As a result, the sealing operations are further improved. A valve controlled by oil pressure 16.3 regulates the heating 16.4 and thus the oil pressure. During operation, the oil is depressurised. In order to achieve rapid pressure reduction and pressure build-up, a small pressure relief cylinder (not shown) may be beneficial. This relief cylinder releases a volume without current and presses its oil volume back into the oil system during a cold start.

The compressor side determines the point of maximum performance. If the intended pressure is reached on the compressor side, then the required work has been done and transferred on the working side. The energy for this was taken from the heating circuit. The adjustment or control of the compressor valve is essential for the entire process. Quantity and temperature of the injected working fluid or expansion medium lose influence. Only the expanded amount of EPM absorbs energy and drives the piston 7.4 ,

If the heating water temperature drops due to high heat load or during the start phase, extended the heat-up time. The goal should be to have an always constant heating water temperature on the drive. A suitable thermostatic control in Heizwasszulauf is easy to implement.

Since the pressure generation and transmission of energy takes place in a closed system, a very high efficiency can be assumed. The heat energy is converted into pressure and transmitted as such. Unconverted energy remains in the system or is released into the case as heat. If one introduces the supply air for the PEK (top left in 15 ) through the housing, so this energy is supplied to the system again. The achievable increase in the supply air temperature leads to an improvement in the efficiency.

The Pressure difference between the condenser for the EPM and the working cylinder should be low at the time of injection. The corresponding electromagnetic Injector is designed to be energy efficient with less pressure increase injected, with 0.5 bar are sufficient.

The cooling of the SEK for the re - liquefaction of the evaporated EPM is carried out by the exhaust air of the PEK in the condenser. The Exhaust air supply is equipped with a control flap, as too much cooling with Energy loss is connected. The condenser is designed to that he was during the startup phase due to its volume without cooling briefly the EPM gas record and liquid EPM or work equipment available can make.

By the overall simple and therefore cost-effective design can be realize multi-level variants, as mentioned. First, within the primary circuit, by matching to the temperature and the properties of the working medium the compressor valve is controlled accordingly or by the number the currently used compressor is adjusted. As a second variant can be a second primary circuit be involved. The third variant is a small primary circuit, the exclusively for the compressor drive is used. He then drives a large primary circuit for the heating load. The advantage is a higher one Flow temperature for the heating circuit.

aim An advantageous development of the invention is the startup process for longer Downtime without a mechanical compressor with electrical Drive to perform. The problem is that at this time at no point of the systems enough greater Potential difference available stands.

Around in particular the lack of exhaust air cooling (too low "minus" potential) while To compensate for the startup phase, the condenser becomes a large volume fitted. The lack of pressure gradient during the gas exchange can be short Time to be bridged, because the pressure does not rise immediately until the cooling starts. At the same time there is a sufficient supply in the condenser liquid Work equipment. The system pressure of the working fluid is corresponding to set the standstill temperatures. The power of the working cylinder is while of the startup process. The injection quantity must be adjusted accordingly become.

The Temperature potential is at least for the start of electrical Heating elements applied, which are housed directly in the working cylinder can. The power for this can be removed at least temporarily from batteries.

Of the Boot process can be done by an additional small heating circuit (not shown) will be shortened. This small heating circuit acts only on the thermal compressor and heat it up quickly. The large heating circuit with the heating load of the building is then controlled slowly controlled temperature.

Important is a precise one Control, which for it ensures that just enough energy is taken from the heating system, as necessary. About printing and temperature detection are the control information appropriate to disposal, which are then converted into control commands.

Of the System pressure of the working fluid must be selected so that at standstill liquid at ambient temperature Work equipment for the boot process available stands. In the chosen Working medium CO2 applies at a pressure of approx. 60 bar, which has already been pointed out.

Below is detailed again on the function of the thermal piston compressor according to the 15 and 16 received:
The thermal piston compressor removes part of the heat energy from the heating water and transmits it as a compression capacity to the primary energy circuit (PEK). The piston compressor is driven by the secondary energy circuit (SEK). The SEK is brought from the exhaust air of the PEK in the condenser to a potential which is below that of the heating water. The energy required for this is ideally neutral, as the cold exhaust air is sufficiently available due to the process. However, the invention is not limited thereto. As a result of the removal of heat, the working medium EPM changes into the liquid state. Pressure, temperature and volume decrease. The result is a pressure gradient between the working cylinder and condenser, which after work, the gas exchange, ie the EPM exchange in Ar supported working cylinder.

in the liquid Condition is running the working fluid by gravity in the electromagnetic injection valve. The pressure in the valve is the same as in the condenser. This pressure is below the pressure in the working cylinder. To do that now Be able to inject working fluid, the pressure must be slight be increased, as already mentioned, with about 0.5 bar pressure difference suffice. The energy expenditure for the injection is kept low. The valve can as Be designed differential pressure valve. This is the shutter kept closed by the working cylinder pressure and a spring means. The surfaces of the closure give the necessary pressure difference to the Open valve. Of the Operation adapts automatically to the operating conditions.

The electronic control recognizes over a sensor the position of the piston and triggers the injection process. About the amperage the injection quantity can be regulated. The working cylinder becomes at least during the starting phase electrically heated. During the operating phase is he at least partially heated by the heating water. The injected work equipment heated itself, evaporates and deprives the heating water energy. The pressure and that Volume increases. The intake valve of the compressor cylinder closes. Of the Working piston is against the return spring force and the Pressure of the refrigerant pushed down in the PEK.

These processes run in the second cylinder 7.2a . 15.4 according to 15 (right), which via a hydraulic circuit 15 for operating a generator 15.2 is used, largely parallel. In the two, preferably identical cylinders 7.2a the pressure increases. The respective piston 7.4 will be pushed further down. When the necessary compression pressure has been reached, the compressor valve opens 3.7 on the left (compressor) cylinder 7.2b , The refrigerant is in the corresponding circuit PEK (refrigerant circle 3 ). The compressor valve closes, exhaust valve for working cylinder 7.2a and inlet valve for compressor cylinder 7.2b to open. The piston 7.4 , which is formed as a free piston within the cylinder and so working cylinder 7.2a and compressor cylinder 7.2b separates or spatially defined, is pushed upwards. The same applies to the right cylinder.

The working fluid EPM flows in accordance with the pressure difference and the spring force of the working piston and the inflowing refrigerant in the circuit PEK in the condenser. The piston 7.4 reaches its uppermost position, closing the exhaust valve and the intake valve of the compressor cylinder. In the condenser, the EPM is cooled down again. The process is re-initiated with the injection of EPM.

The Performance and thus the energy withdrawal are from the compaction pressure dependent. This in turn is regulated by the compressor valve. The energy transition is initiated by a thermal process. Unconverted Energy stays in the system. The potential difference can be regulate exactly as needed.

The volume and pressure conditions in the two cylinders 7.2a can be different. By grading piston and cylinder as well as by separation into two opposite cylinder banks, a hydraulic adaptation to the characteristics of the circuits (refrigerant circuit 3 or hydraulic circuit 15 ) be performed. The design of the cylinder sizes should already lead to full function at about 40 ° C heating water temperature.

at higher Heating water temperatures, the injection quantity is withdrawn, because too big Injection quantities extract more energy from the heating water than necessary.

To avoid excessive cooling of the working fluid, the exhaust air flow is controlled by a control flap 2.8 if necessary, bypass the condenser. The condenser is preferably as a counterflow layer heat exchanger with attached reservoir 2.8a executed for the liquid working fluid. The reservoir 2.8a also ensures the necessary volume for pressure reduction.

hereupon has already been pointed out.

The pressure generation for the power generation by means of the second (right) cylinder 7.2 . 15.4 over the hydraulic circuit 15 works in a similar way. As a pressure transmission medium, a (hydraulic) liquid can be used, which then via a pressure accumulator 15.3 to the generator 15.2 is directed. If no electricity can be produced, it will not be injected into the cylinder in question. There is no idle loss.

Essential is the energy transfer and thus the energy from the heating medium (refrigerant and / or heating water) to the cylinder 7.2a is delivered. The heating time is determined by the temperature difference between the working fluid EPM in the SEK and the heating medium and by the heat exchanger surface on the respective cylinder 7.2a dependent. The heating time determines the cycle time. The EPM and the refrigerant are in the cylinders 7.2a , b loaded. It is heated up or transferred energy until the necessary work has been done.

The heating medium heats the EPM which expands, putting pressure on the respective one piston 7.4 exerts, so that this the refrigerant in the respective compressor cylinder 7.2b compacted. The refrigerant flows into the refrigerant circuit when the pressure is reached 3 above. Has the piston 7.4 his stroke ends, the EPM is drained, and the piston 7.4 is pushed back by the spring, whereupon the process starts again.

2

air system

2.1

intake shaft

2.2

supply air duct

2.3

air distributor in WT1

2.5

plenum in WT1

2.6

air duct in WT1

2.7

Exhaust rule box

2.8

Exhaust air damper (ARK)

2.8a

grown reservoir

2.9

Exhaust air control group

2.10

servomotor ARK

2.12

exhaust air bypass

2.13

exhaust collector

2.14

exhaust pipe

2.15

Ausströmschacht

2.16

axial fan

2.17

Subsurface enclosure

2.18

Underfloor box cover

2.19

drainage

3

Refrigerant circuit

3.1

refrigerant (KM)

3.3

first KM-distribution

3.4

Refrigerant nozzles

3.5

Refrigerant collector

3.6

suction

3.7

Refrigerant inlet valve

3.7a

inlet bore KM

3.9

Kältemitteleauslassventil

3.9a

drain hole KM

3.10

pressure line

3.11

second KM-distribution

3.12

Refrigerant condenser

3.13

Refrigerant control group

3.14

sensors

4

heating circuit

4 '

building

4.2

heating system

4.3

auxiliary circuit

4.4

circulating pump

4.5

Heating circuit

4.6

sensors

5

energy circuit

5.1

Between heat storage

5.2

coaxial heat

5.3

heater

5.4

degassing

5.5

ETF-flow pipe

5.6

Diaphragm pressure regulator

5.7

ETF inlet valve

5.7a

inlet bore ETF

5.8

ETF outlet

5.8 '

ETF outlet

5.8a

drain hole ETF

5.9

first ETF return

5.10

gas separators

5.11

second ETF return

5.12

circulating pump

5.13

Energy circuit control group

5.14

auxiliary pump deposition

6

expansion loop

6.2

expansion medium

6.3

EPMAV outlet valve

6.3a

drain hole EPM

6.4

first EPM-derivative

6.6

second EPM-derivative

6.8

third EPM-derivative

6.9

intake valve EPM

6.9a

inlet bore EPM

6.10

first EPM-lead

6.10 '

second EPM-lead

6.11

Storage

6.12

Injection pump

6.13

Injector EPM

6.13a

Injector nozzle EPM

6.14

EPM control group

6.15

sensors

6.18

damping space

7

drive

7.1

cylinder block

7.1a

cylinder head

7.1b

Zylinderfußplatte

7.2

cylinder

7.2a

drive cylinder

7.2b

compression cylinder

7.3a

linear generator

7.3b

compressor

7.4

piston

7.4

working piston

7.4a

attack for pistons

7.5

Schwall screens

7.7

Return spring

7.13

permanent magnet

7.14

excitation winding

7.15

stator

7.15

decrease winding

7.16

power rod

7.17

guide

7.18

oval cross-section

7.19

contact track 1

7.19 '

contact track 2

7.20

carbon brush

7.21

Leak oil pump

7.22

sensors

7.23

control

12

drive double piston

12.b

drive cylinder

12a

Double piston drive

12.1

drive rod

12.2

insulation

12.3

sealing surface

12.4

valve plates

12.5

compressor

12.5A

Double-piston compressor

12.5b

compression cylinder

12.6

overflow

14

pressure generator

14.1

isolation valve

14.2

separator

14.3

vent

14.4

sensor

14.5

overflow

15

generator hydraulic drive

15.2

generator

15.3

accumulator

15.4

hydraulic cylinders

16

lubrication

16.1

lubricating fluid

16.2

Ölschmiernut

16.3

Oil pressure regulating valve

16.4

heating heat exchangers

WT1

heat exchangers 1

WT2

heat exchangers 2

WT 3

heat exchangers 3

Claims (23)

Thermal drive device ( 7 ), preferably in the form of a linear drive, with at least one cylinder chamber, which is defined by at least one movable piston ( 7.4 ) is closed to the outside and which at least with a first circuit ( 6 ) for an expansion medium and with a second circuit ( 6 ) is in communication with an energy carrier fluid, wherein at least one inlet device ( 6.9 . 6.9a ) is provided for the expansion medium, and further in the region of the cylinder chamber first heat exchange means for heat exchange between the expansion medium and the energy carrier fluid are provided, wherein the expansion medium is selected such that it expands during the heat exchange with the relatively warmer in the operation energy carrier fluid, preferably by evaporation, and the piston ( 7.4 ) is displaced in the cylinder chamber, wherein the piston for transmitting work is formed on at least one means operatively connected to it, preferably at least one generator means ( 7.3a ) for generating electrical energy from the displacement of the piston and / or at least one compressor means ( 7.3b ) for compressing a refrigerant under the performance of compression work. Thermal drive device ( 7 ) according to claim 1, characterized in that on the cylinder chamber at least one inlet device ( 5.7 . 5.7a ) is provided for the energy carrier fluid, and that the first heat exchange means are realized in that in the cylinder chamber when supplying the energy carrier fluid and the expansion medium, a mixture of the energy carrier fluid and the expansion medium is formed, preferably by injecting the expansion medium in liquid form in the energy carrier fluid. Thermal drive device ( 7 ) according to claim 1 or 2, characterized in that on the cylinder chamber separate outlet devices ( 5.8 . 5.8a ; 6.3 . 6.3a ) are present for the energy carrier fluid and for the expansion medium and / or that in the cylinder chamber or in fluidly active connection with this at least one separating device ( 7.5 ; 5.6 ) is present for preferably physically separating the energy carrier fluid and the expansion medium. Thermal drive device ( 7 ) according to one of claims 1 to 3, characterized in that the first heat exchange means have physically separate media guides for the energy carrier fluid and the expansion medium, wherein the energy carrier fluid is preferably guided in a wall of the cylinder chamber. Thermal drive device ( 7 ) according to one of claims 1 to 4, characterized in that the expansion medium is a gas, preferably carbon dioxide, which is most preferably in liquid form when introduced into the cylinder chamber. Thermal drive device ( 7 ) according to one of claims 1 to 5, characterized in that the energy carrier fluid is a liquid, preferably water or a thermal oil, most preferably a synthetic thermal oil. Thermal drive device ( 7 ) according to one of claims 1 to 6, characterized in that in the cylinder chamber at least one braking device ( 6.18 ) is present for the piston at the end of its stroke movement, preferably in the form of a fluid cushion, most preferably in the form of a gas cushion, or in the form of an electro-magnetic brake, which most preferably in the generator means ( 7.3a ) is integrated. Thermal drive device ( 7 ) according to one of claims 1 to 7, characterized in that the piston ( 7.4 ) is biased against the pressure of the expansion medium and according to claim 2 optionally against the pressure of the energy carrier fluid in the cylinder chamber, preferably using adjustable spring means ( 7.7 ), wherein the bias voltage is highly preferably controlled and / or regulated depending on an operating state of the drive device. Thermal drive device ( 7 ) according to claim 8, characterized in that the Vor controlled by introducing a certain amount of a pressure medium, preferably of the expansion medium, into one of the pistons ( 7.4 ) acting cylinder cylinder is effected. Thermal drive device ( 7 ) according to one of claims 1 to 9, characterized in that the inlet quantity of the expansion medium in dependence on an operating state of the drive device is controllable and / or controllable, preferably in dependence on the temperature difference between the expansion medium and energy carrier fluid, most preferably in response to a drive load. Thermal drive device ( 7 ) according to one of claims 1 to 10, characterized in that the drive device for selectively generating electrical energy and / or for performing mechanical work, preferably of compression work on said refrigerant, is formed depending on the load case. Thermal drive device ( 7 ) according to one of claims 1 to 11, characterized by at least one spatially separate from the cylinder chamber pressure generator ( 14 ), which is set up for the thermal interaction of the energy carrier fluid and the expansion medium and for pressurizing the piston ( 7.4 ) is technically connected to the cylinder chamber pressure. Thermal drive device ( 7 ) according to one of claims 1 to 12, characterized in that the piston as a double piston ( 12a . 12.5A ) is formed, which is acted upon on both sides with the expansion pressure of the expansion medium, preferably by means of at least one respective pressure generator ( 14 ) according to claim 12. Thermodynamic compound machine ( 1 ) comprising at least one thermal drive device ( 7 ) according to one of claims 1 to 13 and a heat pump arrangement, preferably in the form of an air-water heat pump, which is set up for the at least partial heating of the energy carrier fluid for the thermal drive device and via the second circuit ( 5 ) is in thermodynamic operative connection with the thermal drive device. Thermodynamic compound machine ( 1 ) according to claim 14, characterized in that said refrigerant in the refrigerant circuit ( 3 ) of the heat pump assembly is included. Thermodynamic compound machine ( 1 ) according to claim 14 or 15, characterized by a heating device ( 5.3 ) for the energy carrier fluid, preferably an electric heater, which most preferably in the second circuit ( 5 ) is arranged. Thermodynamic compound machine ( 1 ) according to one of claims 14 to 16, characterized by second heat exchange means (WT3) for cooling and liquefying the expansion medium after expansion, which on the one hand flows through the primary energy source for the heat pump assembly, preferably air, after heat release to the refrigerant and on the other hand from the expansion medium are to make the lowered temperature of the primary energy source for cooling the expansion medium available. Thermodynamic compound machine ( 1 ) according to one of claims 14 to 17, characterized in that the heat pump arrangement is arranged for direct heating of the energy carrier fluid via the refrigerant and via third heat exchanger means. Thermodynamic compound machine ( 1 ) according to one of claims 14 to 18, characterized in that the heat pump arrangement for indirect heating of the energy carrier fluid by means of an additional heating medium and fourth heat exchange means ( 5.1 ), wherein the additional heating medium is preferably the heat transfer medium of a building heating system ( 4 . 4.2 ), most preferably heating water. Thermodynamic compound machine ( 1 ) according to claim 19, characterized in that the building heating system ( 4 . 4.2 ) and the thermal drive device ( 7 ) are thermally connected in series. Thermodynamic compound machine ( 1 ) according to claim 19, characterized in that the building heating system ( 4 . 4.2 ) and the thermal drive device ( 7 ) are connected in parallel thermally. Thermodynamic compound machine ( 1 ) according to one of claims 14 to 21, characterized by a plurality of parallel connected thermal drive devices ( 7 ), each of which is designed according to one of claims 1 to 13. Thermodynamic compound machine ( 1 ) according to one of claims 14 to 22, characterized in that the thermal drive device ( 7 ) for selectively generating electrical energy and / or performing mechanical work, preferably compression work on the refrigerant of the heat pump assembly, as appropriate Load case is formed.