DE102004047896A1 - Methods and devices for using thermal energy and their applications - Google Patents

Abstract

The invention relates to a new type of methods and apparatus for the use of thermal energy using a clockwise-rotating dynamic cycle and their applications. In a dynamic cycle, the velocity of the working medium is a state variable. The device gains its useful work in an adiabatic-isobaric working process by means of a constant-pressure turbine and can be carried out without a cooler. Thus, the stored in air or water solar energy at ambient temperature can be used technically. Applications of the device are the transportation of persons and goods, the transport of liquids or gases, the change of the pressure of fluids, the generation of electric current, the desalination of seawater, the generation of hydrogen, the cooling of solid, liquid or gaseous media , the liquefaction of gases or vapors and the generation of thermal heat, wherein a device can also run multiple applications simultaneously or sequentially.

Description

The The invention relates to a new class of methods and devices for the use of heat energy with the aid of a clockwise cycle and their applications.

Known Method of using thermal energy using a clockwise clockwise process the Carnot principle or one of its derivatives, the pressure of a fluid Working medium at low temperature while consuming useful work is increased, and then after heat transfer is reduced at high temperature with release of useful work, wherein the delivered useful work is greater than the used and give their difference to an external consumer can. Finally, the temperature of the working medium is through Cool up lowered the outlet temperature, with the extracted heat energy as waste heat get lost.

Such Procedures are today the most important basis of energy technology for the production of useful work. They were considered idealized gas cycle processes (Otto, Diesel, Stirling, Joule, Ericsson, Ackeret-Keller, Seiliger) or steam cycle processes (Clausius-Rankine) described and as real processes under Use of piston machines or turbomachines realized. (Baehr: "Thermodynamics", Springer Verlag 1996, 9th edition, pages 344 ff. Or Cerbe / Hofmann: "Introduction to Thermodynamics ", Hanser Verlag 1996, 11th edition, chapters 4 and 5).

Of the Disadvantage of the known method is that the working medium in the The last step of the cyclic process must always be cooled by heat extraction to get the starting temperature again. But heat is the form of energy which only flows from "hot" to "cold" due to a temperature difference. It follows that one with a conventional one Heat engine the heat energy with ambient temperature can not turn into useful work, because the Environment can not simultaneously heat source and heat sink a heat engine be. This experience was formulated in the 2nd law of thermodynamics, which makes it impossible is, with a heat engine to gain useful work from the ambient heat according to the Carnot principle. Such a heat engine would be a Perpetuum Mobile of the 2nd kind (Stöcker: "Paperback of physics ", publisher Harri German 1998, page 643).

task In the invention, it is a new class of methods and devices to create, where the working medium in the last step of the cycle not by heat transfer chilled so must be the limitation the known heat engines to overcome from the 2nd law of thermodynamics. The invention relates also applications of these methods and devices.

The The invention will be described in 6 sections with reference to 3 figures. The formula symbols used are listed at the end.

Section 1: BASICS

The for the Invention essential theoretical foundations can be found in every standard work on thermodynamics can be found. Here were the works of Baehr and Cerbe / Hofmann used (Baehr: "Thermodynamics", Springer Verlag 1996, 9th edition, and Cerbe / Hofmann: "Introduction to Thermodynamics", Hanser Verlag 1996, 11th edition).

A cyclic process is a cyclic sequence of n different thermal states Z _i (i = 1..n) of a system with a fluid working fluid. It contains n individual open subprocesses P _i (i = 1..n), each subprocess P _i bringing the working medium from a state Z _i into the subsequent state Z _{i + 1} (P _i = Z _i → Z _{i + 1} ), and the last sub-process P _{n returns} the working medium to its initial thermal state Z ₁ .

In the following, the individual states Z _i (i = 1..n) are referred to as the "vertices" of a circular process, and the individual subprocesses P _i (i = 1..n) as its "edges". In the state space of the working medium all edges together form a closed polyline with n vertices. This polyline is called the "edge" of the cycle, and the surface enclosed by the edge is called the "surface" of the cycle.

The thermal states of the working medium in a cycle are described by state variables. For homogeneous thermodynamic systems with a fluid phase, experience has shown that two independent intensive state variables and an extensive state quantity are sufficient to unambiguously describe the system state. The equations of state of such systems are therefore generally of the form z = f (x, y) with two independent and one dependent variable, where the physical variables pressure p, temperature T and volume V are used for the state variables x, y and z , Other equations of state can be used of entropy S, enthalpy H, and internal energy U.

A subprocess P _i changes the state Z _{i of} the working medium and is therefore an "elementary component" of the cycle process In each of the subprocesses P _i , work w _i and / or heat q _{i can be} transmitted to or removed from the system are isochores, isentropes, isobars, isotherms or, more generally, polytropes, vaporization and condensation, all processes are governed by the first and second law of thermodynamics, and then the sum of all energies involved in a process is constant, and the change The entropy can not become negative (dS ≥ 0), so that entropy only remains unchanged in reversible processes and increases in all irreversible processes According to Max Planck, all natural processes are irreversible.

Because only two state variables are sufficient to To describe a homogeneous system, its state changes as continuous curves in a level. Frequently used are the representations from pressure over Volume (p, V-diagram), temperature over entropy (T, S-diagram), or enthalpy over Entropy (h, s diagram). There are also other advantageous depending on the application Representations.

In the case of a right-handed cyclic process, the sum of the useful work of all individual sub-processes is negative (Σ w _i <0) from the point of view of the system, and this amount can be given as drive to an external consumer. Examples include the gasoline or diesel process with four sub-processes and four states.

In a left-handed cyclic process, the sum of the useful work of all the sub-processes is positive (Σ w _i > 0) from the point of view of the system, and this amount must be supplied by a drive. An example of this is the heat pump, also with four sub-processes and four states.

The resulting useful work of all known cycle processes one can in the pressure-volume diagram recognize as the limited by the edge of the circular process surface. Each partial process can be carried out with unchanged kinetic and potential Energy only work when the pressure of the working medium decreases. An isobaric state change makes no contribution to external work.

A conventional cycle does not provide external work when the sum of all useful work is balanced (Σ w _i = 0). In this case, the area bordered by the edges of the process in the pressure-volume diagram degenerates into a line or a point.

Section 2: STATIC AND DYNAMIC CIRCULAR PROCESSES

As The experience shows is the theory of thermodynamics with the development the steam engine, the forerunner of all today's heat engines. The essential for the delivery of labor constructive element of the steam engine is the movable piston in a cylinder, which the decreasing Pressure of steam converts into work. In the textbooks of Thermodynamics are therefore the concepts for energy conversion as well mediated by means of a piston movable in a cylinder.

all but oscillating piston engines is common that the piston at the upper and lower turning point of his movement for one Moment stands still, its speed thus reaches the value "0" Volume of working fluid in a piston engine through the piston is changed, is the working medium in the cylinder at the top and bottom Turning point also at rest. Furthermore, the state change the working medium between the two turning points of the piston movement always a quasi-static event when the piston speed small is opposite the propagation velocity of a pressure disturbance in the working medium (at Gases is the speed of sound).

These constructive characteristics of the piston engine can be found in the theory of circular processes again, because in the vertices of all known ideal cycles is the working medium at rest. The constructive low piston speed of the steam engine is found in the theory of the subprocesses of all known cycle processes again, because their subprocesses are quasistatic state changes, where the working medium is not only in the corners but even while the entire state change between the corner points at rest.

Historical conditionally, all known cycle processes are based on the implicit ones Assumption that the working medium is always at rest and the Speed of the working medium is NOT an independent state variable. This assumption is constructive for all oscillating piston machines also correct, whose pistons at the upper and lower turning point of the Movement is at rest, and its speed is small compared to the Propagation speed of pressure disturbances in the fluid working medium.

• • Bei einem STATISCHEN KREISPROZESS ist die Geschwindigkeit des Arbeitsmediums KEINE unabhängige Zustandvariable zur Beschreibung eines Prozesszustandes. Diese Definition gilt für alle bekannten Kreisprozesse.
• • Bei einem DYNAMISCHEN KREISPROZESS ist die Geschwindigkeit des Arbeitsmediums eine unabhängige Zustandsvariable zur Beschreibung eines Prozesszustandes. Diese Definition gilt für alle nachfolgend beschriebenen erfindungsgemäßen Verfahren und Vorrichtungen.

To delimit the invention against al Therefore, two types of cycle processes are now defined according to known methods:

• • In a STATIC CIRCULAR PROCESS, the velocity of the working medium is NOT an independent state variable for describing a process condition. This definition applies to all known cycle processes.
• • In a DYNAMIC CIRCULATION PROCESS, the velocity of the working medium is an independent state variable used to describe a process condition. This definition applies to all methods and devices according to the invention described below.

• 1. Alle realisierten Wärmekraftmaschinen basieren heute noch auf statischen Kreisprozessen, sogar wenn sie ihre Nutzarbeit mit Hilfe einer Turbine gewinnen. In diesem Sinne werden Dampf- und Gasturbinen thermodynamisch betrachtet heute nur als „simulierte Kolbenmaschinen" eingesetzt.
• 2. Es ist unmöglich, einen dynamischen Kreisprozess mit Hilfe einer Kolbenmaschine zu realisieren, solange die Nutzarbeit des Prozesses mit Hilfe eines beweglichen Kolbens gewonnen wird. In einem dynamischen Kreisprozess kann die Nutzarbeit nur mit Hilfe einer Strömungsmaschine gewonnen werden.
• 3. Die Zustandsgleichungen zur Beschreibung dynamischer Kreisprozesse enthalten die Geschwindigkeit des Arbeitsmediums als unabhängige Zustandsvariable. Mit drei möglichen Freiheitsgraden für Rotation und Translation sind bis zu sechs weitere Zustandsvariablen möglich.
• 4. Die Eckpunkte von statischen Teilprozessen liegen im Zustandsraum des Arbeitsmediums auf einer Fläche mit gleicher Geschwindigkeit (Isotache). Die Eckpunkte von dynamischen Teilprozessen liegen auf verschiedenen Isotachen. Ein dynamischer Teilprozess ist immer auch eine Polytache.
• 5. Alle denkbaren statischen Kreisprozesse liegen auf einer Isotachen. Alle denkbaren dynamischen Kreisprozesse werden von zwei verschiedenen Isotachen begrenzt und enthalten mindestens einen dynamischen Teilprozess.

The following definitions emerge from the two definitions:

• 1. All realized heat engines are still based on static cycle processes, even if they gain their useful work with the help of a turbine. In this sense, steam and gas turbines thermodynamically considered today only as "simulated piston engines" used.
• 2. It is impossible to realize a dynamic cycle with the aid of a reciprocating machine, as long as the useful work of the process is obtained by means of a movable piston. In a dynamic cycle process, the useful work can only be obtained with the help of a turbomachine.
• 3. The equations of state for describing dynamic cycle processes contain the velocity of the working medium as an independent state variable. With three possible degrees of freedom for rotation and translation, up to six other state variables are possible.
• 4. The vertices of static subprocesses lie in the state space of the working medium on an area with the same velocity (isotache). The cornerstones of dynamic subprocesses are on different isotacts. A dynamic subprocess is always a polytache.
• 5. All conceivable static cycles lie on an isotache. All conceivable dynamic cycle processes are limited by two different isotachines and contain at least one dynamic subprocess.

Out this consideration It becomes clear that the previously realized static cycles a subset of all possible ones Circular processes represent because they are in the state space of all conceivable Circular processes are each defined on an isotache. All methods of the invention and devices unlike the known methods and devices a dynamic cycle. Every dynamic Circular process contains at least a dynamic sub-process between two isotachs.

Section 3: DYNAMIC PART PROCESSES

• 1. Jeder dynamische Prozesszustand Z⁺ mit der Totalenthalpie h⁺ und einer Geschwindigkeit c > 0 besitzt einen korrespondierenden Ruhezustand Z° mit der Enthalpie h° und der Geschwindigkeit i = 0 und es gilt h° = h⁺ (Energieerhaltung).
• 2. Es gibt einen adiabaten Prozess P⁺ mit dem sich der Bewegungszustand aus dem Ruhezustand erreichen lässt (P⁺ = Z° → Z⁺), d.h. eine Masse lässt sich ohne Wärmeübertragung unter Einsatz von Arbeit beschleunigen.
• 3. Es gibt einen adiabaten Prozess P° mit dem sich der Ruhezustand aus dem Bewegungszustand erreichen lässt (P° = Z⁺ → Z°), d.h. eine Masse lässt sich ohne Wärmeübertragung unter Gewinnung von Arbeit verzögern.
• 4. Die Enthalpie h des dynamischen Prozesszustandes unterscheidet sich von der Enthalpie des korrespondierenden Ruhezustandes h° durch die kinetische Energie e des strömenden Arbeitsmediums und es gilt h° = h⁺ = h + e.
• 5. Jeder mögliche dynamische Teilprozess lässt sich durch einen zweiteiligen Ersatzprozess mit einem statischen und einem dynamischen Prozessanteil darstellen, wobei der statische Prozessanteil auf einer Isotachen verläuft und der dynamische Anteil isobar zwischen zwei Isotachen abläuft.

The vertices of dynamic subprocesses lie on two different isotacts, and the working medium has a different flow velocity at the beginning and at the end. It is obvious that there are infinitely many possible dynamic subprocesses, but all possible dynamic subprocesses have the following in common:

• 1. Each dynamic process state Z ⁺ with the total enthalpy h ⁺ and a velocity c> 0 has a corresponding rest state Z ° with the enthalpy h ° and the velocity i = 0 and h ° = h ⁺ (conservation of energy).
• 2. There is an adiabatic process P ⁺ with which the state of motion can be reached from the resting state (P ⁺ = Z ° → Z ⁺ ), ie a mass can be accelerated without heat transfer by using work.
• 3. There is an adiabatic process P ° with which the resting state can be reached from the state of motion (P ° = Z ⁺ → Z °), ie a mass can be delayed without heat transfer to gain work.
• 4. The enthalpy h of the dynamic process state differs from the enthalpy of the corresponding rest state h ° by the kinetic energy e of the flowing working medium and h ° = h ⁺ = h + e.
• 5. Each possible dynamic part process can be represented by a two-part replacement process with one static and one dynamic process part, whereby the static process part runs on one isotache and the dynamic part isobaric between two isotacts.

From all possible dynamic subprocesses will only be used for the following discussion examines two special processes: the isobar-adiabatic working process and the adiabatic acceleration in a convergent vortex. Both Processes are elementary, because with the working process the useful work from a flow can be obtained, which was generated with the acceleration process.

to Simplification will reduce the potential energy between two process states the following representation is considered constant (Δz = 0).

Section 3.1: ISOBAR ADIABATERS WORK PROCESS

An isobar-adiabatic working process does not change the pressure or the temperature of the working medium, but only reduces the flow velocity and provides work. Such a process is not possible with a static sub-process, because static sub-processes only at pressure can give away work.

Of the isobar-adiabate work process is known and will for example realized by means of a wind turbine. An "ideal wind turbine" does not change the pressure is still the temperature of the air. It reduces the flow velocity of the Wind on 1/3 and can according to the theoretical derivation of Betz a maximum of 16/27 of the wind energy contained in the wind (Gasch: "wind turbines", B.G. Teubner Stuttgart 1996, 3rd edition, page 120).

For the thermodynamic analysis of this working process, the temperature difference of the corresponding quiescent states of the wind in front of and behind a wind turbine is determined, these are the states Z ° ₁ and Z ° ₂ . To do this, one thinks of a sequence of three dynamic subprocesses, in which static air is first accelerated and wind is created, the wind is then deprived of kinetic energy by a wind turbine, and finally the air is put back into hibernation. The process flow is Z ° ₁ → Z ⁺ ₁ → Z ⁺ ₂ → Z ° ₂ . The actual work process Z ⁺ ₁ → Z ⁺ ₂ is isobaric and adiabatic, ie pressure and temperature do not change - just as the pressure and temperature of the air remain at a sufficient distance in front of and behind a real existing wind turbine.

Because kinetic energy is removed from the wind, the total enthalpy h ^{+ of} the air changes and decreases by the amount of extracted wind energy. Consequently, the enthalpies of the corresponding resting states of the air h ° ₁ and h ° ₂ differ by exactly the amount of kinetic energy taken from the wind. The enthalpy of the still air is only a function of the temperature, because air behaves at atmospheric pressure with sufficient accuracy as an ideal gas. Consequently, the enthalpies h ° ₁ and h ° _{2 of} the corresponding idle states of the air in front of and behind the wind turbine differ only in temperature. The idle state of the air behind the wind turbine is thus colder by the amount: ΔT = T ° 2 - T ° 1 = (h ° 2 - h ° 1 ) / C p and therefore ΔT <0 (3.1.1)

The deceleration of the wind in the dynamic isobaric-adiabatic working process thus has the same effect as a cooler in a static cyclic process: it reduces the internal energy of the working medium and thus lowers the temperature of the corresponding resting state. The entropy change of this process sequence can be determined from the temperatures of the corresponding rest states: Δs = s ° 2 - s ° 1 = c p ln (T ° 2 / T ° 1 ) / and therefore Δs <0 (3.1.2)

• • Ein adiabat-isobarer Arbeitsprozess senkt die Entropie des Arbeitsmediums ohne Wärmeübertragung, oder
• • eine Windkraftanlage, welche nur die Geschwindigkeit des Windes reduziert, mindert die Entropie der Luft.

Because the first and the third sub-process can theoretically always be carried out as an adiabatic process by exchanging work without heat transfer, the entropy change thus comes only from the second sub-process, the adiabatic-isobaric work process, and the following applies:

• • An adiabatic-isobaric work process reduces the entropy of the working medium without heat transfer, or
• • A wind turbine, which only reduces the speed of the wind, reduces the entropy of the air.

This Result is easy to understand in the context of kinetic gas theory, because "wind" is a state of movement the air in the all air molecules statistically averaged with a proportion of their kinetic energy move in the same direction at the same time. When the speed of the wind isobar and adiabat is lowered, then one reduces at the same time the mean kinetic energy of ALL participants molecules the air and thus their inner energy in the corresponding state of rest. at but an ideal gas, the internal energy is only a function the temperature, which inevitably has to decrease, considering the mean kinetic energy of the particles reduced in gas - and That's exactly what a wind turbine does. The temperature change but is measurable only in the corresponding idle state of the air and not within the flow of the wind, because the current remains isothermal.

The result can also be transferred to incompressible working media because entropy is generally defined as: dS = (dU - pdV) / T (3.1.3) or after introduction of the enthalpy differential dH: dS = (dH - Vdp) / T (3.1.4)

at There is no change in an adiabatic-isobaric work process of pressure or temperature, consequently dp = 0 and dS = dH / T. Because Enthalpy of the corresponding resting state of any flow through the adiabatic-isobaric Decreases the entropy of the working medium in the working process decreases Hibernation, and the result applies to both gases and liquids.

• • Weil jeder mögliche dynamische Teilprozess in einen isotachen statischen Anteil und einen polytachen dynamischen Anteil zerlegt werden kann, und statische Teilprozesse nach dem 2. Hauptsatz der Thermodynamik immer die Entropie erhöhen, ist der adiabat-isobare Arbeitsprozess der besondere Prozess mit der maximal möglichen Entropieminderung aller möglichen dynamischen Arbeitsprozesse.
• • Ein adiabat-isobarer Arbeitsprozess kann nur mit einer Gleichdruckturbine realisiert werden, denn es gibt keine Kolbenmaschine, die ohne Druckänderung Nutzarbeit liefern kann.
• • Die Gleichdruckturbine ist die bestmögliche Vorrichtung zur Umsetzung eines dynamischen Arbeitsprozesses, denn der dynamische Arbeitsprozess einer Überdruckturbine enthält einen statischen Prozessanteil, der nach dem 2. Hauptsatz der Thermodynamik die Entropie erhöht.

This discussion is followed by three important insights:

• • Because every possible dynamic subprocess can be decomposed into an isotactical static part and a polytaching dynamic part, and static subprocesses after the 2nd main part Thermodynamics always increase the entropy, the adiabatic-isobaric work process is the special process with the maximum possible entropy reduction of all possible dynamic work processes.
• • An adiabatic-isobaric work process can only be realized with a constant-pressure turbine, because there is no piston engine that can deliver useful work without pressure change.
• • The constant pressure turbine is the best possible device for implementing a dynamic working process, because the dynamic working process of an overpressure turbine contains a static process component, which increases the entropy according to the second law of thermodynamics.

Out This discussion makes it clear that the best possible device or machine to implement a dynamic cycle their useful work with Help win a constant pressure turbine.

Section 3.2: ADIABATE ACCELERATION IN THE SPIRIT

Of the second dynamic subprocess to be examined here is the adiabatic acceleration of a fluid with the help of a convergent Vortex flow.

Vortex flows are known in nature as two-dimensional or three-dimensional flow processes, in which air or water spiral flowing around a vortex center and the flow velocity grows against the vortex center. A dynamic subprocess that changes the state of the working medium from the edge of the vortex to the center, needed in the two-dimensional vortex a second, and in the three-dimensional vortex a third speed variable.

To simplify the following discussion, only the planar vortex flow of an incompressible working medium is to be represented here, as can be found, for example, in parallel-walled rotary cavities of hydraulic machines. In this case, pressure p, temperature T, peripheral speed c _u and meridional speed c _{m are} selected as state variables. These are four state variables, three of which are independent. With incompressible media, the specific volume remains constant.

The vortex flow begins at an outer edge of the vortex with the larger distance r ₁ from the vortex center and ends at the inner edge with the smaller distance r ₂ from the vortex center. Let k = r ₁ / r _{2 be the} ratio of the distances between the outer and inner edges of the flow, and k> 1 for a convergent eddy flow. In a plane frictionless vortex flow, the ratio between the meridional velocity c _m and the peripheral velocity c _{u is} constant c _m / c _u = tan α = const, so that the flow follows a logarithmic spiral with the inclination angle α. The web speed c results from the vector addition of meridian and peripheral speed.

In all adiabatic flow processes, the total enthalpy remains unchanged. In a convergent eddy currents, the angular momentum is retained. In rotating flows a centrifugal force acts, which has to be compensated by an inner pressure gradient towards the center. The pressure gradient is given in the radial pressure equation by the centrifugal acceleration a _z with dp / dr = ρ a _z (Siekmann: "fluid dynamics", Springer Verlag 2000, page 48).

Out leaves these constraints the state change determine the adiabatic acceleration in the convergent vortex.

The change in velocity and thus the change in the kinetic energy Δe results from the angular momentum conservation set with the entrance velocity c for the radii ratio k with: Δe = c 2 (k 2 - 1) / 2> 0 (3.2.1)

The pressure change Δp results from integration of the radial pressure equation in the limits r ₁ and r ₂ with the centrifugal acceleration a _z = c _u ² / r for the entry velocity c and the helix angle α with: Δp / ρ = -c 2 cos 2 α (k 1 - 1) / 2 <0 (3.2.2)

The pressure change is negative and the pressure to the vortex center naturally decreases. The total enthalpy is preserved and the following applies: .delta.h + = Δu + Δp / ρ + Δe = 0 (3.2.3)

This results in the change of the internal energy Δu of the flowing working medium with: Δu = -Δe - Δp / ρ = -c 2 sin 2 α (k 2 - 1) / 2 ≤ 0 (3.2.4)

The internal energy thus sinks in the convergent vortex flow in favor of the flow energy. Since the internal energy is only a function of the temperature, one can calculate the temperature decrease in the convergent vortex flow for an incompressible fluid working medium with the specific heat capacity c _v with: ΔT = -c 2 sin 2 α (k 2 - 1) / (2c v ) <0 (3.2.5)

For flowing water with a vortex gangsgeschwindigkeit c = 6 m / s and a radii ratio k = 3 results from this equation at a helix angle of α = 30 ° a temperature change ΔT = -0.0086 ° C or ΔT = -8.6 mK. Temperature changes of this magnitude have so far been neglected.

Since the flow velocity c in the inflow of the vortex flow depends on the pressure difference Δp between inflow and outflow, the following also applies: ΔT = Δp tan 2 α / (pc of v ) <0 (3.2.6)

The convergent vortex flow So, on the one hand, it has an accelerating effect because it increases the speed a flow elevated, and cooling off to another, because it lowers the temperature of the medium. This dynamic subprocess in turn has the same effect as a cooler in part a static cycle.

The Derivation took place here for an incompressible working medium, such as e.g. Water, but it can be analog for this compressible media, such as e.g. Air. It only has to the density change considered become.

With a convergent vortex flow Consequently, one can the internal energy of a fluid working medium in favor of the flow energy convert, whereby the temperature of the medium decreases. A drop in the Temperature also means a reduction in entropy - but without Heat transfer.

Out This discussion makes it clear that the best possible implementation device a dynamic cycle process the flow velocity with the help of create a convergent vortex flow got to.

Section 3.3: CONCLUSIONS

• 1. Die bekannte Theorie der Thermodynamik ist UNVOLLSTÄNDIG im Hinblick auf die Existenz dynamischer Kreisprozesse. Die bekannte Theorie beschreibt nur statische Kreisprozesse und auch nur solche wurden bisher technisch realisiert.
• 2. Der 2. Hauptsatz der Thermodynamik in seiner bekannten Form gilt nur für statische Kreisprozesse, bei denen die Geschwindigkeit des Arbeitsmediums KEINE Zustandsvariable ist. Für dynamische Kreisprozesse muss der 2. Hauptsatz der Thermodynamik neu formuliert werden.
• 3. Die Aussage des 2. Hauptsatzes der Thermodynamik bezüglich der Wärmeübertragung gilt unverändert für alle statischen und dynamischen Teilprozesse. Danach ist Wärme eine Energieform, und sie fließt „von selbst" nur in Richtung geringerer Temperatur, also nur von „heiß" nach „kalt".
• 4. Die Aussage des 2. Hauptsatzes der Thermodynamik bezüglich der positiven Entropieänderung (dS ≥ 0) gilt nur für statische Teilprozesse, bei denen die Strömungsgeschwindigkeit des Arbeitsmedium KEINE Zustandsvariable ist. Die einschränkende Entropiebedingung (dS ≥ 0) gilt nicht für alle dynamischen Teilprozesse.
• 5. Es gibt mindestens zwei dynamische Teilprozesse, bei denen die Geschwindigkeit des Arbeitsmediums eine Zustandsvariable ist, welche die innere Energie des Arbeitsmediums ohne Wärmeübertragung senken und darum seine Entropie mindern können (dS < 0). Folglich ist es möglich einen rechtslaufenden dynamischen Kreisprozess zu definieren, der ohne Kühler funktioniert, und der, ohne Abwärme abzuführen, trotzdem Nutzarbeit an einen externen Verbraucher liefern kann.
• 6. Weil die innere Energie eines strömenden Arbeitsmediums mit Hilfe eines dynamischen Prozesses technisch genutzt werden kann, ist diejenige Wärmeenergie zugänglich, die zeitlich VOR Beginn des Prozessablaufes an das Arbeitsmedium übertragen wurde.
• 7. Mit einem dynamischen Kreisprozess ist es möglich, die innere Energie des Wassers und der Luft bei Umgebungstemperatur technisch zu nutzen. Die innere Energie von Wasser und Luft stammt aus Wärmeübertragung der Sonne. Wasser und Luft enthalten „historische" Solarenergie.

The preceding discussion shows that there are at least two dynamic subprocesses that reduce the entropy of a medium without heat transfer. It also shows that a dynamic sub-process can only be realized if the speed of the working medium is a state variable. In this case, at least one entropy-reducing sub-process exists for both a compressible and an incompressible working medium. This has far-reaching consequences for the theory of thermodynamics, for the existence of possible energy conversion processes and for the theory of possible machines for energy conversion:

• 1. The well-known theory of thermodynamics is INCOMPLETE in terms of the existence of dynamic cycles. The known theory describes only static cycles and only such have been technically realized.
• 2. The 2nd law of thermodynamics in its known form applies only to static cycles in which the velocity of the working medium is NOT a state variable. For dynamic cycle processes the 2nd law of thermodynamics has to be reformulated.
• 3. The statement of the 2nd law of thermodynamics with regard to heat transfer applies unchanged to all static and dynamic sub-processes. Thereafter, heat is an energy form, and it flows "by itself" only in the direction of lower temperature, ie only from "hot" to "cold".
• 4. The statement of the 2nd law of thermodynamics with respect to the positive entropy change (dS ≥ 0) applies only to static sub-processes in which the flow velocity of the working medium is NOT a state variable. The limiting entropy condition (dS ≥ 0) does not apply to all dynamic subprocesses.
• 5. There are at least two dynamic subprocesses in which the velocity of the working medium is a state variable which can lower the internal energy of the working medium without heat transfer and therefore reduce its entropy (dS <0). Consequently, it is possible to define a right-handed dynamic cycle that works without a cooler, and which, without dissipating waste heat, can still provide useful work to an external consumer.
• 6. Because the internal energy of a flowing working medium can be used technically with the help of a dynamic process, that heat energy is accessible, which was transferred temporally BEFORE the beginning of the process flow to the working medium.
• 7. With a dynamic cycle it is possible to use the internal energy of the water and the air at ambient temperature technically. The internal energy of water and air comes from the heat transfer of the sun. Water and air contain "historical" solar energy.

In order to it is clear that with a dynamic cycle the time the operation of a machine from the time of heat transfer are decoupled can, as long as lowering the entropy of the working medium with a dynamic work or acceleration process and NOT with one cooler he follows. In this case, the working medium of the dynamic Circular process itself to the energy source, from whose internal energy the Useful work and no other source of energy is required.

If the internal energy of the working medium is used technically, its temperature must be sink in the dynamic cycle. Consequently, there is at least one dynamic cycle that provides useful work and can be used to generate cold at the same time. Such processes can replace left-handed static cycles in heat pumps and chillers.

Section 4: RIGHTS DYNAMIC CIRCULAR PROCESSES

Clockwise Ideal dynamic cycle processes provide useful work and are model processes for presentation and derivation of possible Machinery. Thus, the well-known Carnot process is a model process that as a reference and comparison process to evaluate real static Processes is used. Because a cycle can be any number of times Subprocesses can contain, there are infinitely many possible dynamic Cycles. Because those enclosed by the edge of the cycle state area a clockwise cycle is a measure of the useful work generated, have to such cycles at least three different states and Include subprocesses, at least one of which is a polytacher Process is.

As an example of possible dynamic cycle processes, only two ideal processes, each with five sub-processes, are presented here, the first for a compressible working medium, such as air, and the second for an incompressible working medium, such as water. The processes are in the 1 and 2 described. The representations there are only qualitatively correct and should clarify the principles of dynamic circular processes.

• 1. Druck über Volumen (p,V-Diagramm),
• 2. Druck über Strömungsenergie, das ist die spezifische kinetische Energie der Strömung und ermittelt sich aus e = c²/2 (p,e-Diagramm),
• 3. Temperatur über Entropie (T,S-Diagramm),
• 4. Drallenergie über Transportenergie, das ist die spezifische Energie der Strömung in Umfangs- und Meridianrichtung und kann aus den Komponenten c_u, und c_m ermittelt werden (e_u,e_m-Diagramm).

The variables for describing the process states here are pressure p, temperature T, volume V, peripheral speed c _u and meridian speed c _m , which are five variables, four of which are independent for compressible media, three for incompressible media. Consequently, to complete the process, four or three different diagrams are needed. Here were selected:

• 1. pressure over volume (p, V-diagram),
• 2. pressure across the flow energy, which is the specific kinetic energy of the flow and is determined by e = c ^2/2 (p, e) plot,
• 3. temperature over entropy (T, S-diagram),
• 4. Spin energy via transport energy, which is the specific energy of the flow in the circumferential and meridian directions and can be determined from the components c _u , and c _m (e _u , e _m diagram).

In In both cycles, the working medium becomes convergent Vortex accelerates, and the useful work is won with a constant pressure turbine. In the downflow of the turbine becomes from the remaining flow energy recovered static pressure, so that the required Reduced compression or pumping work in the cycle.

The highest pressure in the cycle is p _hi , the lowest is p _lo and the pressure after recovery of the flow energy in the downflow of the turbine is p _mid . Only the change of state to increase the pressure from p _mid to p _hi consumes useful work. The decrease in temperature is compensated by heat transfer.

Section 4.1: A CIRCULAR PROCESS FOR COMPRESSIBLE FLUIDS

• 1. Z₁ → Z₂: Adiabat-verzögerte Kompression von p_mid auf p_hi unter Verbrauch von Arbeit. Die Strömung wird verzögert, der Druck gesteigert und die Strömung erhält einen Drall. Die Temperatur steigt bei konstanter Entropie.
• 2. Z₂ → Z₃: Isobare Wärmeübertragung beim oberen Druck p_hi. Das spezifische Volumen nimmt zu, Entropie und Temperatur steigen. Der Strömungszustand bleibt unverändert. Im p,e-Diagramm und e_u,e_m-Diagramm sind die Zustände 2 und 3 identisch.
• 3. Z₃ → Z₄: Adiabat-beschleunigende Expansion von p_hi auf p_lo innerhalb einer konvergenten Wirbelströmung. Druck und Temperatur sinken bei abnehmender Entropie. Die Strömungsgeschwindigkeit wächst, Drallenergie und Transportenergie der Strömung nehmen zu.
• 4. Z₄ → Z₅: Gewinnung von Nutzarbeit mit Hilfe einer Gleichdruckturbine. Im p,V-Diagramm sind die Zustände 4 und 5 identisch. Der Strömungszustand wandelt sich von drallbehafteter in drallfreie Strömung, und die Strömungsenergie sinkt bei konstantem Druck, die Entropie sinkt bei konstanter Temperatur (Anmerkung: Wie in einem Kühler).
• 5. Z₅ → Z₁: Adiabat-verzögerte Kompression von p_lo auf p_mid in einem Diffusor ohne Verbrauch von Arbeit. Der Diffusor wandelt einen Teil der im Abstrom der Turbine befindlichen Strömungsenergie zurück in statischen Druck. Die Temperatur steigt mit dem Druck, die drallfreie Strömung verliert an Geschwindigkeit.

A clockwise cyclic process for compressible fluids is in 1 shown. It contains five states and sub-processes. The sub-processes are in detail:

• 1. Z ₁ → Z ₂ : Adiabatic delayed compression of p _mid to p _hi with consumption of labor. The flow is delayed, the pressure increased and the flow receives a twist. The temperature increases with constant entropy.
• 2. Z ₂ → Z ₃ : Isobaric heat transfer at the upper pressure p _hi . The specific volume increases, entropy and temperature increase. The flow state remains unchanged. In the p, e diagram and e _u , e _m diagram, states 2 and 3 are identical.
• 3. Z ₃ → Z ₄ : Adiabatic-accelerating expansion from p _hi to p _lo within a convergent vortex. Pressure and temperature decrease with decreasing entropy. The flow velocity increases, swirl energy and transport energy of the flow increase.
• 4. Z ₄ → Z ₅ : Extraction of useful work with the help of a constant pressure turbine. In the p, V diagram, states 4 and 5 are identical. The flow state changes from swirling to swirl-free flow, and the flow energy decreases at constant pressure, the entropy decreases at a constant temperature (note: as in a cooler).
• 5. Z ₅ → Z ₁ : Adiabatic-delayed compression of p _lo to p _mid in a diffuser without consumption of labor. The diffuser converts part of the flow energy downstream of the turbine back into static pressure. The temperature increases with the pressure, the swirl-free flow loses speed.

From the p, V diagram alone, it can be seen that the cyclic process is able to give useful work to a consumer because it is visible clockwise and part of its area is visible in the p, V diagram. However, the actual isobaric work process can not be seen in the pV diagram because states 4 and 5 in the p, V diagram are identical. Without the representation of the dynamic quantities in the p, e-slide gram and e _u , e _m diagram can not be seen that and why the process is able to provide useful work, because two edges of this cycle process are perpendicular to each other in the state space, and the surface of the cycle is twisted in the state space in itself.

Section 4.2: A CIRCULAR PROCESS FOR INCOMPRESSIBLE FLUIDS

• 1. Z₁ → Z₂: Adiabat-verzögerte Kompression von p_mid auf p_hi unter Verbrauch von Arbeit. Die Strömung wird verzögert, der Druck gesteigert und die Strömung erhält einen Drall. Temperatur und Entropie bleiben konstant.
• 2. Z₂ → Z₃: Isobare Wärmeübertragung beim oberen Druck p_hi. Das Volumen bleibt (fast) gleich, Entropie und Temperatur steigen. Der Strömungszustand bleibt unverändert. Im p,e-Diagramm und e_u,e_m-Diagramm sind die Zustände 2 und 3 identisch.
• 3. Z₃ → Z₄: Adiabat-beschleunigende Expansion von p_hi auf p_lo innerhalb einer konvergenten Wirbelströmung. Druck und Temperatur sinken bei abnehmender Entropie. Die Temperaturänderung ist aber sehr, sehr klein. Die Strömungsgeschwindigkeit wächst, Drallenergie und Transportenergie der Strömung nehmen zu.
• 4. Z₄ → Z₅: Gewinnung von Nutzarbeit mit Hilfe einer Gleichdruckturbine. Im p,V-Diagramm sind die Zustände 4 und 5 identisch. Der Strömungszustand wandelt sich von drallbehafteter in drallfreie Strömung, und die Strömungsenergie sinkt bei konstantem Druck, die Entropie sinkt bei konstanter Temperatur (Anmerkung: Wie in einem Kühler).
• 5. Z₅ → Z₁: Adiabat-verzögerte Kompression von p_lo auf p_mid in einem Diffusor ohne Verbrauch von Arbeit. Der Diffusor wandelt einen Teil der im Abstrom der Turbine befindlichen Strömungsenergie zurück in statischen Druck. Die Temperatur bleibt gleich, die drallfreie Strömung verliert Geschwindigkeit.

A clockwise circulating process for incompressible fluids is in 2 shown. It contains five states and sub-processes. Because the volume is constant, the area of this process in the p, V diagram degenerates into a vertical line. A static cycle process can not deliver useful work in this case, but it is possible with a dynamic process. The sub-processes are in detail:

• 1. Z ₁ → Z ₂ : Adiabatic delayed compression of p _mid to p _hi with consumption of labor. The flow is delayed, the pressure increased and the flow receives a twist. Temperature and entropy remain constant.
• 2. Z ₂ → Z ₃ : Isobaric heat transfer at the upper pressure p _hi . The volume remains (almost) the same, entropy and temperature increase. The flow state remains unchanged. In the p, e diagram and e _u , e _m diagram, states 2 and 3 are identical.
• 3. Z ₃ → Z ₄ : Adiabatic-accelerating expansion from p _hi to p _lo within a convergent vortex. Pressure and temperature decrease with decreasing entropy. The temperature change is very, very small. The flow velocity increases, swirl energy and transport energy of the flow increase.
• 4. Z ₄ → Z ₅ : Extraction of useful work with the help of a constant pressure turbine. In the p, V diagram, states 4 and 5 are identical. The flow state changes from swirling to swirl-free flow, and the flow energy decreases at constant pressure, the entropy decreases at a constant temperature (note: as in a cooler).
• 5. Z ₅ → Z ₁ : Adiabatic-delayed compression of p _lo to p _mid in a diffuser without consumption of labor. The diffuser converts part of the flow energy downstream of the turbine back into static pressure. The temperature remains the same, the swirl-free flow loses speed.

in the Comparison to the cycle for Compressible fluids degenerate this cycle in the p, V diagram to a line on an isochore V = const. Degenerated in the T, S-diagram the process becomes a triangle, but the representations of the dynamic State variables remain unchanged.

With Thus, static cycle processes make it impossible to do useful work without the Gas phase alone from incompressible fluids to win, because the area of the circular process in the p, V diagram then degenerates to a line. Here, the essential advantage of dynamic cycles becomes visible, because with them it is possible the internal energy of liquid water technically usable directly.

The Heat transfer shown in both cycles can be omitted, when the fluid is exchanged directly with the environment, and the renewal the internal energy of the working medium outside the cycle by heat transfer done in the area.

Section 4.3: SYSTEM ENVIRONMENT

• 1. Der tiefste Druck des Kreisprozesses liegt über dem Umgebungsdruck. Dieses ist ein Hochdruckprozess, der nur in einem Druckbehälter ausgeführt werden kann. Ein Austausch des Mediums mit der Umgebung ist nur mit einer zusätzlichen Pumpe möglich. Bei kompressiblen Medien kann die Energiedichte und damit die Leistung einer Maschine gesteigert werden. Bei inkompressiblen Medien kann die Kavitationsgefahr vermindert werden. Solche Maschinen können aber auch im Vakuum oder im Weltraum eingesetzt werden.
• 2. Der tiefste Druck des Kreisprozesses ist gleich dem Umgebungsdruck. Dieses ist ein Überdruckprozess, der ebenfalls einen Druckbehälter erfordert. Allerdings kann eine Maschine offen ausgeführt werden und stets Arbeitsmedium mit der Umgebung austauschen. Die Wärmeübertragung kann dann außerhalb der Maschine in der Umgebung erfolgen.
• 3. Der mittlere Druck des Kreisprozesses ist gleich dem Umgebungsdruck. Dieses ist ein neutraler Prozess und die Maschine kann stets Arbeitsmedium mit der Umgebung austauschen. Eine offene Maschine mit Luft als Arbeitsmedium kann dann prinzipiell unbegrenzt lange laufen. Bei einer offenen Maschine mit Wasser als Arbeitsmedium steigt die Kavitationsgefahr.
• 4. Der obere Druck des Kreisprozesses ist gleich dem Umgebungsdruck. Dieses ist ein Unterdruckprozess, der besonders zur Förderung von Flüssigkeiten und Gasen geeignet ist.
• 5. Der obere Druck des Kreisprozesses liegt unter dem Umgebungsdruck. Dieses ist ein Tiefdruckprozess, mit dem man ein Vakuum aufbauen und aufrechterhalten kann. Ein Austausch des Arbeitsmediums mit der Umgebung ist nur mit einer zusätzlichen Pumpe möglich.

The system environment is important for the planning of dynamic cycle processes and the design of machines. In addition to the decision on the type of working medium, the position of the ambient pressure p ₀ in comparison to the pressure values of the cycle processes is essential. As in 3 In principle, five different variants can be distinguished:

• 1. The lowest pressure of the cycle is above ambient pressure. This is a high pressure process that can only be done in a pressure vessel. An exchange of the medium with the environment is only possible with an additional pump. With compressible media, the energy density and thus the performance of a machine can be increased. Incompressible media can reduce the risk of cavitation. Such machines can also be used in vacuum or space.
• 2. The lowest pressure of the cycle is equal to the ambient pressure. This is an overpressure process that also requires a pressure vessel. However, a machine can be run open and always exchange working fluid with the environment. The heat transfer can then take place outside the machine in the environment.
• 3. The mean pressure of the cycle is equal to the ambient pressure. This is a neutral process and the machine can always exchange working fluid with the environment. An open machine with air as the working medium can then in principle run indefinitely. An open machine with water as the working medium increases the risk of cavitation.
• 4. The upper pressure of the cycle is equal to the ambient pressure. This is a vacuum process, which is particularly suitable for the conveyance of liquids and gases.
• 5. The upper pressure of the cyclic process is below the ambient pressure. This is a gravure process that allows you to build a vacuum and can sustain. An exchange of the working medium with the environment is only possible with an additional pump.

Section 5: DEVICES

• 1. Die erfindungsgemäßen Vorrichtungen müssen die Nutzarbeit mittels einer Gleichdruckturbine in einem adiabat-isobaren Arbeitsprozess gewinnen. Bei einer Gleichdruckturbine ist die Umfangsgeschwindigkeit der Strömung an der Druckkante des Laufrades doppelt so groß wie die Umfangsgeschwindigkeit der Druckkante, und der Reaktionsgrad der Turbine ist null (Sigloch: „Strömungsmaschinen", Hanser Verlag 1993, 2. Auflage, Seite 95).
• 2. Die Beschleunigung des Arbeitsmediums vor der Turbine muss in einer Düse erfolgen, vorzugsweise mittels einer konvergenten Wirbelströmung.
• 3. Im Abstrom der Turbine muss eine Druckrückgewinnung mittels eines Diffusors erfolgen.
• 4. Zwischen dem Austritt aus dem Diffusor und dem Eintritt in die Düse muss das Arbeitsmedium durch eine Pumpe gefördert werden, deren Antriebsarbeit direkt oder indirekt aus der Turbinenarbeit stammt.
• 5. Die Differenz aus Turbinenarbeit und Pumpenarbeit wird an einen externen Verbraucher gegeben.
• 6. Das Arbeitsmedium wird innerhalb oder außerhalb der Vorrichtung während ihres Betriebes oder nach Beendigung wieder erwärmt.
• 7. Das Arbeitsmedium zirkuliert in der Vorrichtung oder es wird regelmäßig mit der Umgebung ausgetauscht und so erneuert.

The possibilities for realizing devices for the implementation of dynamic cycle processes are as diverse as the possibilities of designing these cycle processes per se. Nevertheless, "optimal" devices according to the invention for implementing the method according to the invention must have few common features.

• 1. The devices of the invention must gain the useful work by means of a constant pressure turbine in an adiabatic-isobaric work process. In a constant pressure turbine, the peripheral speed of the flow at the pressure edge of the impeller is twice as large as the peripheral speed of the pressure edge, and the degree of reaction of the turbine is zero (Sigloch: "Turbomachinery", Hanser Verlag 1993, 2nd edition, page 95).
• 2. The acceleration of the working medium in front of the turbine must be done in a nozzle, preferably by means of a convergent vortex flow.
• 3. In the downstream of the turbine, a pressure recovery must be done by means of a diffuser.
• 4. Between the outlet from the diffuser and the inlet to the nozzle, the working medium must be pumped by a pump whose drive is directly or indirectly from the turbine work.
• 5. The difference between turbine work and pump work is given to an external consumer.
• 6. The working fluid is reheated inside or outside the device during its operation or after completion.
• 7. The working fluid circulates in the device or it is regularly exchanged with the environment and so renewed.

Section 6: APPLICATIONS

• (1) Antrieb für den Transport von Personen und/oder Gütern,
• (2) Antrieb für den Transport von Gasen und/oder Flüssigkeiten,
• (3) Antrieb für die Änderung des Drucks von Fluiden,
• (4) Antrieb zur Erzeugung von elektrischem Strom,
• (5) Antrieb zur Entsalzung von Meerwasser,
• (6) Antrieb zur Erzeugung von Wasserstoff,
• (7) Erzeugung von Kälte zur Kühlung von Gasen, Flüssigkeiten oder Festkörpern,
• (8) Erzeugung von Kälte zur Verflüssigung von Gasen oder Dämpfen,
• (9) Erzeugung von Wärme zur Erwärmung von Gasen, Flüssigkeiten oder Festkörpern.

The applications of the methods and devices according to the invention are manifold:

• (1) drive for the transport of persons and / or goods,
• (2) drive for the transport of gases and / or liquids,
• (3) drive for changing the pressure of fluids,
• (4) drive for generating electric power,
• (5) drive for desalination of seawater,
• (6) drive to generate hydrogen,
• (7) generation of cold for cooling gases, liquids or solids,
• (8) generating cold for liquefying gases or vapors
• (9) Generation of heat to heat gases, liquids or solids.

Symbols:

a _z

centrifugal acceleration

c

Amount of absolute flow rate

c _u

circumferential speed

c _m

Meridian speed

const

constant

c _p

specific heat capacity at constant print

c _v

specific heat capacity at constant volume

e

specific kinetic Energy: e = E / m

e _u

specific twist energy of a planar flow: e c _u = _u ^2/2

e _m

specific transport energy of a planar flow: e _m = _m c ^2/2

H

specific enthalpy h = u + pv

h ⁺

specific total enthalpy

h °

specific enthalpy of the corresponding resting state (h ° = h ⁺ ; c = 0)

k

Radial ratio of a plane turbulent flow: k = r ₁ / r ₂

m

Dimensions

p

print

p ₀

ambient pressure

q

Specific heat

r

Radius or distance from the turning center

s

specific entropy

u

specific inner energy

v

specific volume

w

specific work

z

geodesic height

e

kinetic energy

H

enthalpy

P _i

Sub-process of a cycle between the states Z _i and Z _{i + 1}

P ⁺

adiabatic process for generating a state of motion from rest

P °

adiabatic process for generating the resting state from the movement

S

entropy

T

temperature

U

Inner energy

V

volume

Z _i

Condition of a cycle process at the beginning of the ith sub-process

Z ⁺

Movement state of a Working medium with c> 0

Z °

Hibernation of a Working medium with c = 0

α

Absolute flow angle

ρ

specific density

indices:

0

environmental condition

1

first state or swirl edge

2

second state or vortex center

i

Counting index i = 1..n

m

Meridian direction

u

circumferentially

°

Idle state with c = 0

+

Movement state with c> 0

Hi

Process state with highest Pressure in the cycle process

lo

Process state with lowest pressure in the cycle

mid

Process state after reclamation of pressure in the effluent of a turbine

Functions, operators and other characters:

ln

naturally logarithm

sin

Sine

cos

cosine

tan

tangent

→

Sub-process between two states P _i = Z _i → Z _{i + 1}

=

equal sign

/

division

>

greater than

<

less than

≥

greater or equal

Σ x _i

Sum of all values x _i , i = 1..n

x ⁿ

x high exponent n

dx

Differential of size x

dx / dy

Derivation of the size x after the size y

Ax

Difference of size x between two states 1 and 2: dr = x ₂ - x ₁

Claims (20)

Method for using thermal energy by means of a clockwise cyclic process in which a fluid working fluid is cyclically repeatedly performed by a number n excellent process states, which mark the vertices of the cycle, and the circular process gives useful work, characterized in that the n excellent process states of the cycle through more than two independent state variables are described, where the velocity of the working medium is a state variable, and at least two of the n process states have different velocities. Method according to claim 1, characterized in that that the cycle with a compressible fluid, or a incompressible fluid or a mixture is performed. Method according to claim 2, characterized in that that the cycle process without heat transfer works to the environment, so without waste heat. Apparatus for carrying out the method according to one the claims 1 to 3, characterized in that the useful work of the cycle in an adiabatic-isobaric Gained working process with one or more constant pressure turbines becomes. Device according to claim 4, characterized in that that the pressure of the working medium in the cyclic process by one or more pumps is increased, their drive work directly or indirectly the turbine work comes. Device according to claims 4 and 5, characterized in that that they are not coolers for the removal of heat owns to the environment. Device according to one or more of claims 4 to 6, characterized in that the working medium in front of each turbine is accelerated, preferably in a convergent vortex flow. Device according to one or more of claims 4 to 7, characterized in that the heat transfer to the working medium either done inside the device or already outside is done in the vicinity of the device. Device according to one or more of claims 4 to 8, characterized in that the working medium in the device circulated or exchanged with the environment. Device according to one or more of claims 4 to 9, characterized in that it is used stationary or mobile. Device according to claim 10, characterized in that that it is used to transport people or goods. Device according to claim 10, characterized in that that they are transporting liquids or gases is used. Device according to claim 10, characterized in that that they change the pressure of liquids or gases is used. Device according to claim 10, characterized in that that it is used to generate electricity. Device according to claim 10, characterized in that that it is used for the desalination of seawater. Apparatus according to claim 10, characterized in that it is for the production of water fabric is used. Device according to claim 10, characterized in that that they are for cooling of solid, liquid or gaseous Media is used. Device according to claim 10, characterized in that that they liquefy of gases or vapors is used. Device according to claim 10, characterized in that that they use to generate thermal heat is used. Device according to one or more claims 11 to 19, characterized in that they each have a single or Run multiple applications simultaneously or sequentially.