EP1017933B1 - Method and device for entropy transfer with a thermodynamic cyclic process - Google Patents

Description

Problem:

• den Aufbau der gesamten Vorrichtung oder den Betriebsablauf des gesamten Verfahrens,
• den dabei notwendigen thermischen oder mechanischen Energietransport(en),
• die dabei verwendbare(n) Verfahren oder Vorrichtungen zur mechanischen Energieumwandlung oder
• eine integrierbare Energiespeicherung

möglichst gering werden kann.When transferring entropy such as the use of solar energy or heat sources, such as the combustion of biomass, waste heat or geothermal energy, for a needs-based local supply for pump power, mechanical drive, electrical energy, heat supply, cooling, cleaning or separation, chemical or physical Modification of at least one substance through the coupling with a periodic thermodynamic cycle
to achieve that the necessary expenditure of energy sources or mechanical energy as well as the constructive, technological, economic or ecological expenditure for

• the structure of the entire device or the operating sequence of the entire method,
• the necessary thermal or mechanical energy transport (s),
• the process or devices for mechanical energy conversion or
• integrable energy storage

can be as small as possible.

The thermodynamic cycle processes previously used (Stirling engine, steam turbine) are each coupled to two heating baths with a constant temperature.
As a result, energy can only be transported optically (with parabolic mirrors or light guides) or via a material flow with a phase transition (heat pipe).
Due to the desired isothermal exchange of thermal energy, the thermal energy can only be stored in chemical stores or in latent heat stores.
As a result, the effort for concentrating the energy by the collector, transport and storage that is desirable for many applications is too often too great.
If, for example, a direct supply of cold or compressed air is desired with the least possible equipment outlay, in many known systems the route via the interface of electrical current must be chosen.

task

• den Aufbau der gesamten Vorrichtung oder den Betriebsablauf des gesamten Verfahrens,
• den dabei notwendigen thermischen oder mechanischen Energietransport(en),
• die dabei verwendbaren Verfahren oder Vorrichtungen zur mechanischen Energieumwandlung oder
• eine integrierbare Energiespeicherung

möglichst gering werden kann.The invention is based on the central object, in a method and / or in a device for transfer of entropy such as the use of solar energy or heat sources, such as the combustion of biomass, waste heat or geothermal energy, for needs-based local supply for pump power, mechanical drive , electrical energy, heat supply, cooling, cleaning or separation, chemical or physical change of at least one substance
by coupling with a periodic thermodynamic cycle, the efficiency of which is as high as possible,
to achieve that the necessary expenditure of energy sources or mechanical energy as well as the constructive, technological, economic or ecological expenditure for

• the structure of the entire device or the operating sequence of the entire method,
• the necessary thermal or mechanical energy transport (s),
• the methods or devices used for mechanical energy conversion or
• integrable energy storage

can be as small as possible.

Essence of the invention

• jeweils zumindest zwei gegeneinander abgrenzbare, vom Arbeitsfluid in einer Periode mit maximaler Menge zu durchströmende Strukturen oder Bauteile mit für den thermodynamischen Prozeß notwendig wirksamen Wärmeübergangsflächen, in welchen im Betriebszustand jeweils vom Arbeitsfluid zu durchströmende isotherme Flächen unterschiedlicher Temperatur ausgebildet werden,
• wahlweise zumindest ein oder kein dazwischen verbindend angeordnetes und weitgehend abdichtendes oder mit der Wirkung eines Regenerators ausgestattetes Element oder Bauteil wie z.B. eine (faltbare) Membrane, gefaltete, teleskopartige oder federnde Bleche, eine formveränderbare Regeneratorstruktur oder eine Flüssigkeitsgrenzfläche
• oder wenigstens ein oder kein in diesem Arbeitsvolumen bewegbarer Verdrängerkolben
• und die Begrenzung des Arbeitsfluids

zumindest ein Teilvolumen mit minimaler Größe weitgehend überschneidungsfrei zu Vergleichbarem abgrenzen und zum Teil durch daran angreifende Elemente des Steuersystems zu Bewegungen veranlaßt werden, durch die das Verhältnis von diesem Teilvolumen zu diesem Arbeitsvolumen überwiegend in den Zeitperioden des periodisch ablaufenden thermodynamischen Kreisprozesses entweder vergrößert oder verkleinert wird, während denen dieses Arbeitsvolumen nur geringer in der Größe verändert wird und je nach Druck des Arbeitsfluids in diesem Arbeitsvolumen jeweils zumindest ein bestimmtes Ventil , dessen Öffnungs- und Schließzeitpunkt den thermodynamischen Kreisprozeß entscheidend beeinflußt und welches dieses Arbeitsvolumen gegen zumindest einen äußeren Raum abgrenzen kann, welcher angefüllt ist mit zumindest einem Arbeitsmittel bei teilweise unterschiedlichen, relativ zur periodischen Druckänderung in diesem Arbeitsvolumen während diesen Zeitperioden nur geringen Schwankungen unterworfenen Drücken, vom Steuersystem oder dem Strömungsdruck überwiegend (in den oben charakterisierten Zeitperioden) offen gehalten und durchströmt wird, welches (Ventile) während zwischen diesen Zeitperioden ablaufenden anderen Zeitperjoden geschlossen gehalten wird, in denen der Druck des Arbeitsfluids in diesem Arbeitsvolumen durch die Verschiebung der oben genannten oder weiteren Komponenten oder Bauteile durch das Steuersystem und der dadurch verursachten Veränderung der mittleren Temperatur des Arbeitsfluids in diesem Arbeitsvolumen und/oder durch eine Veränderung der Größe dieses Arbeitsvolumens durch die mechanische Kompressionseinrichtung entweder steigt oder fällt und das Verhältnis jedes wie oben definierten Teilvolumens zu diesem Arbeitsvolumen nur in entscheidend geringerem Umfang verändert wird, wobei während einem relativ zur Periodendauer viel längeren Zeitintervall entweder eine Wärmeenergieaufnahme oder -abgabe zumindest einer Substanz eines kontinuierlichen oder periodisch an- und abschwellenden Massenstroms bei gleitender Temperatur oder bei mehreren Temperaturniveaus erfolgt und in diesem Arbeitsvolumen zumindest ein Arbeitsmittel zumindest teilweise als Arbeitsfluid wirkt, das den periodischen thermodynamischen Kreisprozeß durchläuft. According to the invention, this object is achieved by a device and a method for transferring entropy in which, against other rooms or the environment, at least one valve and at least one pressure housing optionally without or with a mechanical compression device, such as, for example, one or more pistons, liquid pistons or membranes, and optionally at least one liquid interface or no at least one working volume filled with working fluid is largely limited in which

• in each case at least two structures or components which can be delimited from one another and flow through by the working fluid in a period with a maximum amount and which are necessary for the thermodynamic process and in which, in the operating state, isothermal surfaces of different temperatures to be flowed through by the working fluid are formed,
• optionally at least one or no element or component that is arranged between them and is largely sealing or equipped with the effect of a regenerator, such as a (foldable) membrane, folded, telescopic or resilient sheets, a shape-changeable regenerator structure or a liquid interface
• or at least one or no displacer piston movable in this working volume
• and the limitation of the working fluid

delimit at least one partial volume with a minimal size largely without overlap with the comparable and in some cases induce movements by elements of the control system attacking it, by means of which the ratio of this partial volume to this working volume is either increased or decreased mainly in the time periods of the periodically running thermodynamic cycle, during which this working volume is only changed in size to a lesser extent and depending on the pressure of the working fluid in this working volume, at least one particular valve , the opening and closing time of which decisively influences the thermodynamic cycle and which can delimit this working volume from at least one external space which fills up is with at least one working medium with partially different, relative to the periodic pressure change in this working volume only slight fluctuations during these time periods terworfenen Press, from the control system or the flow pressure is mainly kept open (in the above specified time periods) and crosses, which (valves) during running other Zeitperjoden is kept closed between these time periods in which the pressure of the working fluid in the working volume by the displacement of The above or other components or components either increase or decrease due to the control system and the resulting change in the mean temperature of the working fluid in this working volume and / or through a change in the size of this working volume by the mechanical compression device, and the ratio of each partial volume as defined above increases this work volume is changed only to a significantly lesser extent, with either a thermal energy intake or delivery of at least one substance of a continuity during a time interval that is much longer in relation to the period mass flow or periodically rising and falling mass flow takes place at a sliding temperature or at several temperature levels and in this working volume at least one working medium acts at least partially as a working fluid which goes through the periodic thermodynamic cycle.

The entire cyclic process in a working volume can be assigned several circular processes running in parallel between two heat reservoirs with constant temperatures, if justifiable idealization is considered.
Each heat reservoir of these cycle processes can be assigned to a partial volume of the working volume which is filled with working fluid and as defined above.
At least one substance of a continuous or periodically increasing and decreasing mass flow is heated or cooled either by the absorption or release of thermal energy at a lower temperature difference relative to the overall temperature change when it comes into contact with the hotter or colder heat reservoirs of these cycles, whereby the phase or can transform chemical composition.

At least one substance is used continuously to use solar energy or periodically rising and falling mass flow thermal energy with sliding Temperature or multiple temperature levels supplied.

• optische Konzentration
• transluzente Isolation und
• Durchströmung der transluzenten Isolation

sehr effektiv kombiniert werden.
Die Wärmeenergie kann sehr effektiv und kostengünstig mit einem sensitivem Speicher, der eine große Oberfläche aufweist wie z.B. eine Kiesschüttung, bei einer Durchströmung mit Arbeitsmittel ausgetauscht werden.
Der Wärmeenergietransport kann durch eine Bewegung eines kapazitiven Arbeitsmittels, wie z.B. Luft, erfolgen.
Durch die Druckänderung zumindest eines Arbeitsmittels steht auch die Möglichkeit offen, eine sehr unproblematische Infrastruktur zum Transport der mechanischen Energie oder als Schnittstelle zum einfachen weiteren Transfer bzw. Transformation für konkretere Problemlösungen zu nützen.When building the integrable collector, the principles can change due to the temperature change over a large temperature interval

• optical concentration
• translucent insulation and
• Flow through the translucent insulation

can be combined very effectively.
The heat energy can be exchanged very effectively and inexpensively with a sensitive storage device that has a large surface area, such as a gravel fill, when the working fluid flows through it.
The heat energy can be transported by moving a capacitive working medium, such as air.
By changing the pressure of at least one work tool, there is also the possibility of using a very unproblematic infrastructure for transporting the mechanical energy or as an interface for simple further transfer or transformation for more specific problem solutions.

Some of these problems are already addressed in patent DE 3607432 A1. This patent contains a representation of the theoretical basis of a cycle. Quote: Column 3, line 45: "The present invention provides the knowledge and practical methods to achieve Carnot efficiency even with the addition of heat at a sliding temperature."
The concept for a corresponding heat engine 26 has been cited by the applicant of the patent in the Proceedings of the 6 ^th International Stirling Engine Conference 1993 - presented 28 May in Eindhoven (Netherlands) - 27th

The cited patent does not list a physical (phase) and / or chemical change due to thermal energy transformation over a wide temperature range, although these problems can be attributed to the same core problem:
In order to liquefy part of a gas mixture, thermal energy usually has to be extracted over a temperature interval due to the changeable ratio of the partial pressures.
Accordingly, when a gas mixture is vaporized, thermal energy must be supplied over a temperature interval or at several temperatures.

The same applies to a chemical process in which thermal energy is used in several Temperatures or in a temperature interval is recorded or released.

benefits

In the devices and / or methods not cited, the mechanical work supplied (consumed) or given (won) during a period of the entire cycle to balance the energy balance is largely directly from a storage space during the transfer of at least a certain amount of at least one fluid substance moved to another storage space with different pressure.
This makes it easy to integrate other systems or processes.
Direct use of the pressure change, e.g. by replacing a mechanically driven compressor or
Decoupling the movements in the working volume from the driving shaft of a turbine or a compressor or the like. which is driven by or generates the pressure difference of the substance flowing (in the closed circuit). This means, for example, that a generator can be driven at the usual angular velocity and a flow velocity of the working fluid in the order of 1 m / s against the heat transfer surfaces and a correspondingly small temperature difference during heat transfer can be achieved, which has a positive effect on the efficiency and the accelerations occurring on the control system as well as the flow losses are reduced.
This enables a large-volume construction in which the pressure in the working volume is in the range of the atmospheric pressure and air is used as the working fluid, which alleviates many problems with regard to tightness and makes interesting applications possible. (see application examples)

The cited patent is limited to a cooling or heating of a heating or cooling medium through the thermal contact with heat exchangers of a regenerative work or heat engine compared to the more abstract formulation of the task chosen above.
This eliminates a reduction in the structural or technological outlay for heat exchangers or regenerators, which is achieved according to the invention if the heat is added to the working volume by the heating medium being taken up, for example, as hot gas in the working volume by valves and at a lower temperature again by valve ( e) is emitted, whereby the dead volume of the working volume can also be reduced, which experience has shown that it is just as favorable for achieving good efficiency as a functional replacement of the relatively small heat transfer surface of the heat exchanger by the much larger one of the regenerator.
Fresh air can flow into the working volume through one of the valves at atmospheric pressure, which can achieve decisive synergy effects in some applications.
For example, hot air can be taken up in a working volume and blown out as cooler air into a room with higher pressure, with some of the heat energy released when the air is cooled being taken up by the cooler.
If the hot fresh air has been heated at atmospheric pressure by exhaust gases from an internal combustion engine and the cooler air with higher pressure is used to charge the internal combustion engine, great synergy effects are used. (see application examples)
When using solar energy, inexpensive parabolic trough mirrors can be used, because the solar radiation can heat the working medium air and so there are no environmental and disposal problems caused by escaping thermal oil and also no widely branched absorber piping system for high-pressure steam generation, which means that thermal energy transport becomes much less problematic.
In addition, the heating of the working fluid over a large temperature interval (eg 200 ° C to 500 ° C) can be used to achieve a higher final temperature of the arthroplasty at home in the collector's absorber with relatively little effort.

For this purpose, the principles of optical concentration, translucent isolation and flow through the translucent isolation can be combined very effectively.
The incorporation of an unproblematic storage made of inexpensive materials even allows seasonal storage of the solar radiation over several months if dimensioned accordingly.
This makes an inexpensive island solution possible, such as supplying a remote village or an infirmary.

Principle of the cycle used

The formation of the temperature field in the working volume e.g. when using only one heat exchanger and the process of an entire cycle can together with the problem underlying the task by the following, executions relating to specific applications can be more easily understood.

Application of the principle of the invention

The device shown in Figure 1 can be used, among other things, as a thermal device Gas compressors (with the integrated effect as an engine) work and form due to the simple structure and the relatively easy theoretical Description of the cycle a good starting point for understanding the more complex machines also based on the principle of the invention, Devices or processes.

construction

A working volume filled with gas as the working fluid is largely enclosed by a working cylinder as the pressure housing 1, a slidingly sealed piston 2, inlet and outlet valves 3 and 4, respectively.
In this working volume, a frame 6 is slidably sealed against the cylinder wall 5, on which a heat exchanger 7 and a regenerator 8 which is unchangeable in structure or size are mounted such that the gas must flow through them.
A resilient spacer 9 is between this regenerator 8 and a structure 11 surrounded by a bellows 10 with a reversible, acting and acting as a regenerator structure 11, which consists of a fine (40 - 80 ppi) foam or comes close to this in terms of homogeneity or gaps , (e.g. several layers of embossed or bent metal fabric arranged next to one another perpendicular to the direction of flow), a flow channel 12 is formed over the entire cylinder surface, through which the gas passes the structure 11 through the opened outlet valve 4 of the volume and part 13 of the piping system to the fan 14 can reach.
This gas can flow from the fan through part 15 of the piping system and a regenerator 16 to be flowed through into a reserve space 17 which is enclosed by a bellows.
From the fan 14 or from this reserve space 17, the gas can reach the working volume after being heated in a (countercurrent) heat exchanger 18 through part of the piping system 19 through the inlet valves 3.

To buffer the pressure fluctuations, a pressure tank 20 is connected to the pipe system at 13 in front of the fan (turbine) 14.
The piston 2 and the frame 6 are moved periodically by hydraulic pistons 21, 22, 23 as is characterized in FIG. 4, FIG. 5, FIG. 6 or the subsequent description of the cycle.
By means of the hydraulic cylinders 21 and 22, the piston 2 is stabilized in the orientation with regard to the stroke direction.
The drive tube 24 of the frame 6 is guided by the piston 2 in the stroke direction through seals from the working volume. Two tubes for the cooling water run in this drive tube and are sealed against the inner wall of the drive tube in such a way that no gas exchange which interferes with the cycle can take place between the working volume and the environment.
Movable hoses 25, 26 connect these pipes to fixed connections 27, 28 of a cooled water reservoir, so that the cooling water can circulate in a closed circuit.
The liquid in the heat exchanger 7 should always have a lower pressure than the working volume, so that no liquid is pressed into the working volume, which could lead to dangerous sudden steam development, but the liquid in the heat exchanger is displaced by the inflowing working fluid.
If the hot gas to be cooled is introduced directly into the pipeline system of the entropy transfer device (see FIG. 1) at 19 and is removed again at 15, the losses and the structural outlay of the heat exchanger 18 can be eliminated.
The hydraulic pistons 21, 22 and 23 exchange mechanical power via a controlled valve system 29 of the control system via a hydraulic pump 30 with a flywheel 31 and a component 32 acting as an electric motor and / or generator.
Working fluid can be exchanged from the part of the pipeline system 19 to the flow channel 12 by a valve 33, optionally driven by a fan 34 or not by a further valve 35.

The valve 33 remains closed for the time being.
In the following, the justifiable, simplifying assumption is made that the working fluid as the ideal gas in the coolest partial volume always has the temperature T _k , ie only isothermal processes take place there.

Determination of the maximum possible delivery of work by a method according to the invention and a device according to the invention in which, by coupling with a cyclic process, a gas quantity of mass m _{A is} cooled over a temperature interval from T ₁ to T ₂ .

Upon cooling of the gas from T + dT at T, the thermal energy dQ = m _A * C _p dT is given * [a1]. If this thermal energy is absorbed isothermally at temperature T by a cycle cooled at T _k , the work can be done to the maximum dW = η -dQ η = 1 - T k / T: Carnot efficiency be performed.

verrichtet werden.
W kann [nach Stephan, Karl: Thermodynamik Grundlagen und technische Anwendungen; Band 1 Einstoffsysteme; 14. Aufl.; 1992 Springer-Verlag S. 177 ff] als die Exergie der Wärmeenergie bezeichnet werden, welche dem Gas beim Abkühlen von T₁ auf T₂ entnommen wurde, wenn die Kühlertemperatur T_k gleichgesetzt wird mit der Umgebungstemperatur T_u.

If the gas cools down from T ₁ to T ₂ , the work can be done accordingly

be performed.
W kann [according to Stephan, Karl: Thermodynamics basics and technical applications; Volume 1 single-component systems; 14th ed .; 1992 Springer-Verlag p. 177 ff] are referred to as the exergy of thermal energy, which was taken from the gas during cooling from T ₁ to T ₂ , if the cooler temperature T _{k is} equated with the ambient temperature T _u .

The hatched area under the curve of η _{c [Tk]} (T) in Fig. 2 is proportional to this work W.
The thermal energy Q = m _A - c _p - (T ₁ -T ₂ ) is fed to the cycle

For the overall efficiency of this cycle, this results in:

If the thermal energy is taken isothermally from the gas through thermal contact with four ideal heat exchangers at temperatures T _1.25 , T _1.5 , T _1.75 , T ₂ (see Fig. 3), the exergy shown above is increased by W_to the maximum usable energy W reduced.
This is shown in Fig.3. The formal description and interpretation result from the comparison with those of Fig. 2

Cyclic process that the gas goes through in the device of Fig.1

an den Kühler abgegeben.The sequence of movements is determined by the control system and is rough and sufficient for the following analysis in Fig.4, Fig.5, Fig.6 I.
With the assumption later confirmed in more detail that the regenerator system 11 has a temperature profile in the equilibrium operating state, the mean temperature T _{mg of which is} significantly higher than the cooler temperature T _k , this gives directly the temporal profile of the mean temperature in the working volume T _m (t) and is shown qualitatively in Fig.4, Fig.5, Fig.6 II. Because of the reserve space 17, the pressure P ₀ in the part of the piping system 19 in front of the inlet valves corresponds to atmospheric pressure.
The fan 14 is to work in such a way that the pressure P ₁ in the space 13 of the pipeline system adjacent to the outlet valve 4 is changed only slightly relative to the pressure difference P ₁ - P ₂ .
The valves 3 and 4 are opened or closed by the (flow) pressure of the gas.
With the corresponding reduction in the working volume from V _a to V _b by the movement of the piston 2 in the time period abc, the pressure is increased since the inlet valves 3 and outlet valves 4 due to the higher pressure P relative to P ₀ but lower relative to P ₁ (t) are closed in the work volume.
With the assumed isothermal compression in the time period abc, the cool gas in the working volume at the temperature T _k
the thermal energy

delivered to the cooler.

The work W _abc = -Q _abc must be performed on the piston by the control system in this period.
A surface hatched in FIG. 7 corresponds to this work W _abc .

In the time period cde, with a constant volume of arity, the coolest partial volume becomes smaller due to a displacement of the frame 6 with cooler 7 and regenerator 8, which leads to an increase in the average temperature of the gas in the working volume. As soon as the pressure P (t) in the working volume rises slightly above the pressure P ₁ on the other side of the outlet valve 4 at the beginning of this period, this valve is opened and the expansion of the gas associated with the rise in the mean temperature causes a gas quantity of the mass m _a of the working volume flowing through the exhaust valve, adiabatically expanded in the fan 14 while the work W performed _payload corresponding to Figure 7 in an area.

The following applies:

aufgeteilt werden, daß für V_i ohne eine effektive Verfälschung der thermodynamischen Beschreibung angesetzt werden kann: P*V i = N i * kB * Ti ; N i = P * 1 kB * 1 Ti * Vi ; k_B: Boltzmannkonstante; T_i : Temperatur in V_i ; N_i· Anzahl von Gas-Molekülen in V_i Note: For a given pressure ratio P ₁ / P ₀ , T _{2 is} independent of m _A W nutz = C p * m A * (T 1 - T 2 ) * η ges Each volume V can be divided into partial volumes V _i by a corresponding, possibly very small, division

be divided so that V _{i can be applied} without an effective falsification of the thermodynamic description: P * V i = N i * k B * T i ; N i = P * 1 k B * 1 T i * V i ; k _B : Boltzmann constant; T _i : temperature in V _i ; N _i · number of gas molecules in V _i

Mathematical reasoning:

Due to the heat conduction, a continuously differentiable temperature field can be assumed. see. Riemann - integrals
The following then generally applies:

Number of gas molecules exchanged with the aridity volume per period:

m_c : Masse des Gases im Arbeitsvolumen zum Zeitpunkt c
für die Zeitperiode c-d-e gilt:

Note: the letters in the index, for example c in N _c, indicate a point in time of the cycle defined in Fig. 4, Fig. 5, Fig. 6.
Determination of the mass of the amount of gas exchanged

m _c : mass of the gas in the working volume at time c
for the time period cde:

m_Agha = m_Acde
m_a : Masse des Gases im Arbeitsvolumen zum Zeitpunkt aIn the time period efg, the working volume is increased by the piston movement.
The gas should not flow relative to the heat transfer surfaces which are necessary for the thermodynamic cycle.
Since the gas in the entire working volume is in direct contact with heat transfer areas during this period of time to large thermal capacities, which are necessary for the thermodynamic cycle and due to their special movement, the gas is not moved relative to it, this period of the cycle can be described by an isothermal expansion the same formulas apply to the exchanged thermal energy or work as for the time period abc.
This makes it possible to store this energy in a vibrating system and to release it again for compression (e.g. by a vibrating water column in a U-shaped tube, possibly with a cavity acting as an air spring as a limitation. The quantity of gas absorbed in the period gha applies : (see cde)

m _Agha = m _Acde
m _a : mass of the gas in the working volume at time a

The temperature profile, the temperature field T (r) in the device of FIG. 1. In the time period efg, the largely homogeneous regenerator structure 11 fills the entire working volume with the heat capacity that is very large in relation to the gas, hereinafter assumed to be infinite, and largely the entire working volume expanded by the displacement of the piston.
Due to the special movement, only isothermal processes take place in the arity volume.

Approach:

Let the working volume be divided into sub-volumes of equal size by E - 1 planes arranged perpendicular to the stroke. Due to the symmetry, the temperature is ideally constant at these levels.
The heat energy Q _i = 1 / E ₊ Q _{efg is} taken from the regenerator structure 11 in each of these partial volumes by the isothermal expansion of the gas. i ∈ [1; E ] During the time period gha, the regenerator structure 11 is effectively supplied with energy by the cooling of the hot gas quantity of the mass m _A flowing through the inlet valves 3 at each period, since as a result a larger quantity of gas flows from the hot part into the colder part of the regenerator structure 11 than in the reverse flow direction.

The jth of these partial volumes is limited (see above) by the isothermal levels of the temperature T _j and T _{j + 1} . The gas flow during a period leads to this partial volume
the thermal energy Q _j = m _A * C _p * (T _j - T _{j + 1} ).
The following must apply to the formation of an operating state in equilibrium: Q j = m A * c p * (T j -T j + 1 ) = Q i = 1 / E * Q efg From (T _j - T _{j + 1} ) = (m _A * c _p * E) ^-1 * Q _efg , a linear temperature _{curve in the stroke direction} follows for T (r).

If a greater pressure ratio P ₁ / P _{0 is to be} achieved in the system when the exchanged gas is cooled by a certain temperature difference, then the gas quantity of mass m _{B must be passed} through a further (controlled) outlet valve 35 from the flow channel 12 in the period gha be sucked by a fan 34 which. ideally, by means of adjustable elements, the necessary pressure difference relative to P ₁ - P ₀ can only be applied in this time period. This amount of gas is supplied to the space 15 of the piping system.
Ie open valve 33.
If four such working volumes are phase-shifted by 90 °, a commercially available fan can run evenly, ie only the outlet valves 35 have to be controlled with a little effort and energy.
With unchanged T ₁ , T ₂ , P ₀ , the exchanged and cooled gas quantity m _A is thereby increased by m _B and the regenerator system 11 is supplied with a larger quantity of thermal energy during a period.
This greater thermal energy is partially withdrawn from the regenerator system 11 in the time period efg during the effectively isothermal expansion of the gas from P ₁ to P ₀ , a larger pressure ratio P ₁ / P ₀ being able to be achieved and thus more energy being converted per period overall, whereby the total heat energy exchanged at the regenerator 8 or at the regenerator system 11 as well as the associated thermal losses are increased in a much lower ratio.
Overall, this results in better efficiency.
If the mass flow through the adjustable fan can be set in 3 stages (off, medium, large) and the large stage is always switched on by a thermostat when the temperature falls below a certain temperature, the temperature T _{2 can} thus be sufficient at a relatively low cost Value to be stabilized.

Use of the device characterized in Fig.1 as a refrigerator

The device shown in FIG. 1 can also be operated as a refrigerator, which cools a quantity of gas over a large temperature interval.
For this purpose, the then driven fan (turbine) 14 must press the gas from the part of the piping system 19 with the pressure P ₀ into the part 13 with P ₁ .
The direction of flow of the gas is reversed (everywhere in the working volume), the structure of the device and the speed of movement remain as in Fig. 1 and Fig. 4. Fig.5, Fig.6 obtained.
The outlet valve 4 becomes an inlet valve in that it is kept open against the flow pressure with an unchanged stop direction in the time period cde, for example by an attacking spring connected to the control system.
The gas then flowing in with the pressure P ₁ releases thermal energy to the regenerator system 11 during cooling.
The regenerator is efg during the time period in which effective isothermal expansion of the gas (such as front, home gas compressor; engine) from P ₁ to P ₀ withdrawn heat energy. As shown above in the description of the engine, a temperature field T (r) which is linear in the stroke direction is also formed in the regenerator structure 11 in the refrigeration machine by the interaction of the sub-processes in the time periods cde and efg, the mean temperature T _{m of which} in the refrigeration machine is below the Radiator temperature T _k is. (Development over time of T _m (t) in Fig. 4, Fig. 5, Fig. 6: replace max. T _m (t) by min. T (t).
As a result, the average temperature in the working volume when the regenerator system 11 is pushed together is increased in the time period gha.
The inlet valves of the engine 3 can act as outlet valves in the refrigerator if they are kept open against the flow pressure in this time period gha, for example by an attacking spring connected to the control system, and gas due to the increase in the mean temperature in the constant working volume at a constant pressure Pressure P _{0 flows out} into the part of the piping system 19.
Before this gas is compressed again by the fan (turbine), it absorbs the heat energy from the cooling of the other gas stream in the heat exchanger 18.
If the gas to be cooled is introduced directly into the pipeline system of the refrigeration machine at 15 (cf. FIG. 1) and is removed again at 19, the losses and the structural outlay of the heat exchanger 18 can be dispensed with.
In the time period cde, with a constant working volume, the average temperature of the gas in the working volume is reduced by the expansion of the regenerator system 11, which due to the valve 4 being kept open at a constant pressure P ₁ leads to an inflow of warmer gas, an additional supply of thermal energy to the regenerator structure 11 and the like Closure of the cycle leads.

Reaching a larger temperature difference T ₁ - T ₂ when using the device characterized in Fig.1 as a refrigerator

The device shown in FIG. 1 and already described as an engine can, as already largely shown at the front, also be operated as a refrigerator. As with the engine, with the valve 33 open and the fan 34 stopped, a greater temperature difference in the amount of gas of the mass m _A taken up and given off by the working volume can be achieved if in the period gha a gas amount of the mass m _H by in this case at the same stop as Exhaust valve acting valve 35 flows into space 15, which is kept open during this period gha by the control system against the flow pressure.

Reaching a smaller temperature difference T ₁ - T ₂ when using the device characterized in Fig.1 as a refrigerator

The motor machine shown in FIG. 1 can also be operated as a refrigeration machine, as already shown above. If, as with the engine, a larger pressure difference P ₁ -P ₀ is also to be used for the cooling machine for a certain cooling, this can be achieved if, in the period gha, the gas quantity of the mass m _{B is passed} through a further (controlled) inlet valve 35 is blown into the flow channel 12 from the room 15 with a fan 34.

Effect as a heat pump

If in the chillers described above, the control system by reversing all directions of motion so that the moving parts are in their position according to Fig. 4, Fig.5, Fig.6 in the reverse order h-g-f-e-d-c-b-a h change and fan working directions remain unchanged relative to Fig.1, so these devices work than heat pumps, which the injected gas over comparable Heat temperature intervals at comparable pressure ratios instead cool.

The cycle when using a device according to Fig.1 as a heat pump

In the period gfe, thermal energy is supplied to the regenerator system 11 during the isothermal compression (with closed valves) of the gas from P ₀ to P ₁ .
When the regenerator system 11 is pushed together in the time period edc, the valve T is taken up by the turbine gas at the temperature T _{H of} the working volume at the pressure P ₁ , since the mean temperature is lowered.

hot gas + cool gas gives warm gas with higher pressure

a.) am Kolben 2 sind Ventile der Art 3 angebracht, durch welche das kalte Gas aus einem relativ zur Änderung des Arbeitsvolumen großen mit dem Zylinder 1 gebildeten Pufferraum in das Arbeitsvolumen einströmen kann. Zwischen diesen Ventilen und dem angetriebenen flachen Rahmen 6 des Regenerators 8 ist ein zu 11 analoges Regeneratorsystem angeordnet. Der Wärmetauscher 7 kann entfallen. Der Bewegungsablauf, sowie die Änderung der mittleren Temperatur T_m(t) oder der Druck im Arbeitsvolumen P(t) entsprechen dennoch weitgehend den qualitativen

Darstellungen in Fig.4, Fig.5, Fig.6. In der Zeitperiode g-h-a wird durch die jeweiligen Ventile Gas mit der Temperatur T₁, bzw. T₂ eingesaugt. Bei einer entsprechenden Einstellung des Verhältnisses der Massen der eingesaugten Gasmengen m₁ (T₁) und m₂, ergibt sich in Hubrichtung ein linearer Temperaturverlauf. Dies müßte sich für den Wirkungsgrad als ideal erweisen.
Durch Ventile müssen die in das Arbeitsvolumen einströmenden Gasmengen entsprechend reguliert werden.
Soll das kühlere Gas nur eine geringere Temperaturänderung erfahren, so wird wie vorne beschrieben während dessen Einströmvorgang durch ein weiteres Ventil (vgl. 35) mit einem Ventilator Gas aus dem Arbeitsvolumen gesaugt.
Zum Strömungskanl 12 kommt ein weiterer spiegelbildlich zum Regenertor 8 angeordneter Strömungskanal für das aus dem Arbeitsvolumen strömende Gas.
An jeden dieser Strömungskanäle grenzen jeweils die Ventile 4 und 35 bzw. entsprechende Venile an, durch die die Temperaturintervalle für die ausgetauschten Gasmengen über weite Bereiche (vgl. zu Fig.1b, 1c) variiert werden können.
Insgesamt ist dieser Entropietransformator evtl. einfacher aufzubauen; da kein Wärmetauscher (z.B. Autokühler) notwendig ist.
Außerdem kann keine plötzliche Dampfentwicklung durch entwichenes Kühlwasser auftretenIn order to be able to take up two gas quantities of masses m ₁ , m ₂ with temperatures T ₁ and T ₂ in a working volume and to be able to release a temperature T ₃ between T ₁ and T ₂ at higher pressure, compared to the The entropy transformers shown in FIG. 1 can be modified as follows:

a.) on the piston 2, valves of type 3 are attached, through which the cold gas can flow into the working volume from a large buffer space formed with the cylinder 1 relative to the change in the working volume. A regenerator system analogous to 11 is arranged between these valves and the driven flat frame 6 of the regenerator 8. The heat exchanger 7 can be omitted. The movement sequence, as well as the change in the average temperature T _m (t) or the pressure in the working volume P (t), however, largely correspond to the qualitative ones

Representations in Fig. 4, Fig. 5, Fig. 6. In the period gha, gas with the temperature T ₁ or T _{2 is} sucked in through the respective valves. With a corresponding setting of the ratio of the masses of the sucked-in gas quantities m ₁ (T ₁ ) and m ₂ , a linear temperature curve results in the stroke direction. This should prove to be ideal for efficiency.
Valves must be used to regulate the amount of gas flowing into the working volume.
If the cooler gas is only to experience a smaller change in temperature, gas is sucked out of the working volume with a fan as described above during its inflow process by means of a further valve (cf. 35).
In addition to the flow channel 12 there is a further flow channel arranged in mirror image to the rain gate 8 for the gas flowing out of the working volume.
The valves 4 and 35 or corresponding valves adjoin each of these flow channels, by means of which the temperature intervals for the gas quantities exchanged can be varied over wide ranges (cf. FIGS. 1b, 1c).
Overall, this entropy transformer may be easier to set up; since no heat exchanger (e.g. car cooler) is necessary.
In addition, there can be no sudden steam generation from escaped cooling water

As already shown at the front of the gas compressor, this construction can do the same operated that lukewarm gas at a higher pressure through a turbine in the Working volume pressed and thereby the flow direction but not the periodic movement sequence (see Fig.4, Fig.5, Fig.6) is changed and from the Flush out working volume of hot and cold gas at lower pressure.

Combination of chiller and engine

If hot gas and cool gas or cooling water of temperature T _k are available, gas can be cooled below the cooling water temperature T _k by an entropy transformer with 2 working volumes.
In principle, in one of the refrigeration machines described above, the driven fan 14 is replaced by one of the devices described above with the effect of a gas compressor; the hot gas is taken up by the working volume, which can be assigned to the gas compressor, and is discharged at higher pressure through the outlet valve 4 of this working volume into a space of the piping system, to which a buffering pressure vessel can be connected and from where the gas may be after a previous cooling to about T _{k flows} through the valve 4 acting as an inlet valve into the working volume, which can be assigned to the refrigerator.
From this working volume, the gas cooled under T _k flows out through the valves 3 and possibly 35.
For the coordination of pressure and temperature differences, the periodic flow through the valves 35 of the two unit volumes can be set accordingly (as shown above).
If the movements shown in FIG. 4, FIG. 5, FIG. 6 I run simultaneously in a work volume, the buffering pressure vessel can be dimensioned smaller or can be omitted.
It is also interesting to use this combination as a heat pump for liquids.
Other interesting combinations serve to increase the heating number to a value above 1.
Thus, a hot and cold gas quantity is absorbed by a first working volume as described above and released again as a cool gas quantity at higher pressure, and absorbed by a second working volume which it releases as a warm gas quantity at the outlet pressure. The liquid of a heat exchanger or an additional amount of gas was cooled in the second working volume.

Constant work volume

Described function: part of a gas compressor (engine)
The working volume of an entropy transformer shown in FIG. 8, FIG. 9 or FIG. 10 shows, for example, as part of an engine in comparison with the two that are decisive for thermodynamics in comparison with FIG. 1 or FIG. 4, FIG Differences in:
First, the work volume is not changed in size.
Second, instead of the relatively homogeneous regenerator system 11 shown in FIG. 1, four discrete, rigidly constructed regenerators 36, 37, 38, 39 act on the working volume of FIG. 8, FIG. 9 or FIG. 10, on which, as on the two further regenerators 40 and 41 are each attached to four tubes, each of which is part of one of the four concentric arrangements of tubes 42 of the control system.
These components 36 - 41 as well as the frame with the heat exchanger 43 acting as a cooler are sealed with V2A sealing brushes on bronze cylinder wall plates 44 as well as the pipes for the heat exchanger liquid 45, 46 in such a way that they are at a minimal (less than 10%) ) Leakage flow between the seal and the cylinder wall can be flowed through.
The periodic movement of these components is qualitatively shown in Fig. 9 I or Fig. 10 I with the designations H: for stroke and t: for time.
The regenerators are made of a lower V2A perforated plate with as little metal surface as possible, with U-profiles made of V2A welded on for reinforcement and open parallel to the perforated plate, in which metal fibers are sheathed with V2A fabric (wire diameter approx. 0.1 mm) (center of gravity of the diameter at 40 micrometers ) are inserted, which are clamped and enclosed by another perforated plate.
The two perforated sheets are held together by a wire winding where the perforated sheets have been deformed in such a way that the outer surfaces of these regenerators have no local elevation despite the wire winding.
At the edge, the perforated plate turns into a plate without holes, whereby the seals are held and sealed to the metal fibers so that they flow through.
Otherwise, similar to the engine as in FIG. 1, FIG. 4, FIG. 5, FIG. 6, a working volume filled with gas as working fluid is largely enclosed by a pressure housing 47, inlet 48 and outlet valves 49. The gas can flow through the inlet valves from a space of the piping system corresponding to FIG. 1 in FIG. 1 into the partial volume between the cylinder cover and the regenerator 36 and from a space between the regenerators 39 and 40 through

Flowing out pipe 50, in which a pipe 45 concentrically and in firm connection the line 46 for the heat exchanger liquid and periodically in one of the pipes 5 which limit the working volume and are not moved periodically Brushes 52 retracted sealed. From this tube 51, the gas through the Exhaust valves 49 enter a space in the gas piping system which is shown in FIG 13 corresponds.

The guide, drive and control unit for the Realization of what is characterized in FIGS. 9 and 10 Movement sequence of the elements with the reference numbers 36 - 41 and 43 are referenced 42, 53-60, 63-98 designated in Figures 8, 11 to 14 and 17 to 19.

The heat exchanger is in a closed circuit with Liquid from the elements with the reference number 45, 46, 102-106.

In the partial volume, which is delimited from the working volume only by the regenerator 41, grating planes 108 to be flowed through by the gas and arranged perpendicular to the direction of rotation are characterized by the control system as in FIG. 9 I, so that they move to this regenerator 41 or the neighboring one , either move the grating plane that is already moving, maintain a certain distance (e.g. 20% of the total stroke) or remain as close as possible to the boundary surface of the pressure vessel. For driving the grating planes 109 in the partial volume of the working volume, which is only delimited by the regenerator 36, the same largely applies. In the case of this periodic movement sequence, gas with a constant temperature flows through these grating planes in the operating state to a large extent and the formation of eddy currents is severely hampered, as a result of which gas quantities can mix with the maximum temperature differences in these partial volumes.
Drive: See claim 99, 100.
The working volume shown in Fig.8 is connected to the piping system like the working volume in Fig.1 and integrated into the surrounding system.

Cyclic process of the gas shown in Fig.8 constant work volume

The fundamental considerations which were made for the system characterized in FIG. 1 or 3 used, inter alia, as a gas compressor also apply to this system characterized in FIG. 8 or 9 and used as a gas compressor.
It can also be assumed that the regenerators 36 - 40 have a temperature profile in the equilibrium operating state, the mean temperature T _{mg of which is} significantly above the temperature T _{k of} the cooler.
The qualitative time profile of the mean temperature in the working volume T _m (t) results directly from this and is shown qualitatively in FIG. 9 II.
As shown in FIG. 1, the inlet and outlet valves should be connected to the surrounding systems, ie, due to the reserve space 17, the pressure P ₀ corresponds to that
Part of the piping system upstream of the inlet valves 48 atmospheric pressure.
The turbine 14 in FIG. 1 is intended to work in such a way that the pressure P _{1 is changed} only slightly relative to the pressure difference P ₁ - P ₀ by the interaction with an upstream compensating pressure vessel in the space of the pipeline system adjacent to the outlet valve 13.
The valves 49 and 48 are opened and / or closed by the (flow) pressure of the gas.
In the equilibrium operating state, the gas has its lowest mean temperature T _m (t) in the working volume cf. Fig.9 I reached at time a.
Immediately thereafter, the inlet valve is closed by the flow pressure of gas flowing from the working volume due to the increase in the average gas temperature T _m in the working volume.
As long as the pressure in the working volume remains lower than the pressure P ₁ on the other side of the exhaust valve 49, this is also closed.
As the mean gas temperature T _m (t) in the working volume increases, the pressure in the time period abc increases from P ₀ to P ₁ :

The compressed gas emits thermal energy to the cooler. At time e, the gas in the working volume has reached the highest average temperature T _m (t).
During the subsequent lowering of T _m (t) in the time period efg, the outlet valve is closed again by the pressure in the working volume which is lower than that of P ₁ . The pressure in the working volume is still too great for the inlet valves to open, so that the reduction in T _m (t) leads to a reduction in the pressure P (t) in the working volume. Thereby 37 - 40 heat energy is taken from the regenerators; (cf. Q _efg ) because the gas flowing through it is expanded again between two regenerators.

With a further increase in T _m (t) in the time period cde, the outlet valve is opened by the somewhat higher pressure in the working volume and a gas quantity of mass m _{A flows} out.

At time e, the maximum average temperature of the gas in the aridity volume is reached.
In the subsequent time period efg, the mass of the gas in the working volume is smaller than in the time period abc.
The pressure difference from P ₁ - P ₀ is already reached after a smaller decrease in T _m (t).
When T _m (t) is further reduced, the gas quantity of the mass m _{A is} absorbed by the working volume through the inlet valve at a constant pressure P ₀ until the point in time
j = a the smallest value for T _m (t) is reached again.
The amount of gas that flows in is cooled by the release of thermal energy to the regenerators 36-40 and by mixing with cooler gas. In general, a partial volume divided by the components characterized in claim 1 from the working volume is withdrawn from thermal energy during a full period if it is (significantly) smaller during the time period of the pressure increase than during that of the pressure decrease.
If all valves on this machine are suddenly closed while the equilibrium is in operation, a process takes place that comes very close to that of a Vuilleumier heat pump. In this case, thermal energy is taken from the partial volumes of the working volume between the regenerators 36-40 and partially released to the cooler.
This partial cycle process drives a second partial cycle process which pumps from the partial volume of the working volume, which is only delimited by regenerator 41, into the partial volume which is only delimited from the working volume by regenerator 36.

A valve that is controlled by the temperature of the endangered sub-volume can prevent that this process is not started unintentionally by a sticking valve and that it is destroyed by overheating, which valve causes a constant pressure in the working volume in an emergency.
If the outlet valve is opened by a correspondingly lower selection of the pressure P ₁ a small fraction of the time period abc after the point in time a at which the lowest average gas temperature prevails in the working volume, the pressure in the working volume is increased in this cycle process in particular , if the partial volume delimited only by regenerator 41 and the partial volume adjacent to the cooler largely have the maximum size and the partial volume only delimited by regenerator 36 and the partial volumes between two regenerators largely have their minimum size.
The other extreme size ratio prevails while the pressure in the working volume is reduced.
As a result, the thermal energy with respect to these partial volumes is converted in the opposite direction through this entire cycle process than with closed valves (see above)

Between these two extremes, the pressure P _{1 can} be selected such that on average no heat energy is removed or supplied to the partial volume of the working volume which is only delimited by the regenerator 36 by the cyclic process.

The thermal energy which is supplied to the partial volume of the working volume, which is only delimited by the regenerator 41, due to irreversibilities such as the shuttle effect, heat conduction and the unfavorable efficiency of the regenerator, is at this pressure P ₁ by the special one shown in FIG Movement sequence of the regenerator 41 withdrawn and fed to the cooler.

The movement sequence characterized in FIG. 10 has the advantage that the flow channels for gas exchange are covered to a lesser extent by the moving regenerators or are better designed.
In contrast to the representations in FIG. 8, the lower lifting frame 90 must be connected to the lowest regenerator 41.
For this sequence of movements in the working volume, too, the pressure P1 can be set so that an analog one for the corresponding partial volumes
Thermal energy balance results.

The partial volume of the working volume between two of the regenerators 36-40 is reduced by the fact that the gas flowing through is further expanded in the time period efg between two regenerators.
These partial volumes are supplied with thermal energy during a period by virtue of the fact that, due to the gas quantity of the mass m _A, which is hotly taken up into the working volume by the inlet valve 48 and coolly discharged through the outlet valves 49, the regenerators 36-39 flow through the hottest side with one around them Gas quantity of mass m _A larger gas volume is flowed through than from the cooler side.
A temperature profile with a larger gradient in the flow direction is formed on the cooler side of one of these homogeneously assumed regenerators.
Given the assumed uniform quality of the regenerators, one of the partial volumes defined above is supplied with more thermal energy than is extracted by the periodic flow.
The heat energy given off during the cooling of the gas quantity m _A flowing into the working volume, which flows periodically hot and cooler again, is absorbed in part by the circular processes running parallel between the partial volumes with largely isothermal heat energy absorption and delivery.
As a result, a linear temperature profile is formed in the working volume, as generally shown in the front of Fig. 4, Fig. 5, Fig. 6.
As a result, the average temperatures of adjacent partial volumes of the working volume range between two? the regenerators 36-40 with the same size and temporal order of magnitude the same difference as shown in the front to Fig.4, Fig.5, Fig.6 generally.
The work that can be done to a maximum is reduced by W_ compared to the exergy (T _u = T _k ) as explained for FIG. 3.

The losses at regenerators 36-39 are partially reduced by W_. Due to the irreversibility, such as heat conduction or the losses of the regenerators, only a smaller pressure ratio P ₁ / P _{2 is} achieved and the gas quantity m _A must enter the working volume with a temperature greater than T, especially in a device constructed as in FIG ₁ is.

One of the valves 49 in FIG. 8 can be used like the valve 35 in FIG. 1 in order to achieve the described changes in the temperature differences when cooling or heating a portion of the exchanged gas at the same ratio of the pressures P ₁ / P ₀ .

Cooling of the gas over a smaller temperature difference T ₁ - T ₂

If, in the system shown in FIG. 8, a larger pressure ratio P ₁ / P _{0 is to be} achieved when the exchanged gas is cooled by a certain temperature difference, then in the period gha the gas quantity of mass m _B is controlled by the (controlled) valve 49, 1 corresponds to the outlet valve 35, sucked from the partial volume between the regenerators 39 and 40 with a fan which, in the ideal case, only uses adjustable elements in this time period to apply the necessary small pressure difference to P ₀ relative to P ₁ - P ₀ and this amount of gas is supplied to the space 15 of the piping system.
Four working volumes work 90 ° out of phase, ie a special fan can run through evenly, only the outlet valves 35 have to be controlled with some effort and energy.
With unchanged T ₁ , T ₂ , P ₀ , the exchanged and cooled gas quantity m _A is thereby increased by m _B and the regenerators 36 to 39 are supplied with a larger quantity of thermal energy during this period.
This greater thermal energy is partially withdrawn from the regenerators 36 to 39 in the time period efg during the effectively isothermal expansion of the gas from P ₁ to P ₀ , a larger pressure ratio P ₁ / P ₀ being able to be achieved and thus more energy being implemented per period is, whereby the total heat energy exchanged at the regenerators 36 to 41 as well as the associated thermal losses are increased in a much lower ratio.
Overall, this results in better efficiency.

Application as a chiller

The system described above, which acts as an engine and has the working volume shown in FIG. 8, can, after a few changes, also be operated as a refrigeration machine which cools a gas quantity over a large temperature interval. For this purpose, the then driven fan (turbine) 14 must press the gas from the part of the piping system 15 with the pressure P ₀ into the part 13 with P ₁ . The movement sequence shown qualitatively in FIG. 9 I or FIG. 10 I is carried out in the reverse chronological order. The outlet valve 49 becomes an inlet valve in that it is kept open by the control system against the flow pressure in the time period ahg with the stop direction unchanged.
In this time period ahg, the partial volumes between these regenerators are increased and the average temperature of the gas in the working volume is lowered from the maximum value.
The gas then flowing in with the pressure P ₁ releases thermal energy to the regenerators 36 to 39 during cooling.

Thermal energy is withdrawn from these regenerators during the subsequent period of time by the expansion of the gas between two regenerators (cf. front: engines).
With closed valves, the pressure in the working volume is reduced due to the lowering of the average temperature of the gas to the minimum value by a shift at constant relative distances of the regenerators 36 to 41.
As shown above in the description of the engine, also in the refrigeration machine through the interaction of the sub-processes in the time periods ahg and gfe, a linearly stepped temperature field T (r) is formed in the regenerators 36 to 39, whose average temperature T _m at the Chiller is below the cooler temperature T _k .
The temporal development of T _m (t) corresponds to the reversal of the chronological sequence and the replacement of max. T _m (t) by min. T _m (t) of the qualitative representation in Fig. 9 II.
The average temperature of the gas in the working volume is increased when the regenerators 36 to 39 are pushed together in the subsequent time period edc.
The inlet valve 48 of the engine in FIG. 8 acts as an outlet valve in the refrigerator if it is kept open by the control system against the flow pressure during this period of time edc with the stop direction unchanged and gas and, inter alia, due to the increase in the mean temperature in the constant working volume at constant pressure P. _{0 flows out} into the part of the piping system 15.
Before this gas is compressed again by the fan (turbine), it absorbs the heat energy from the cooling of the other gas stream in the heat exchanger 18.
If the gas to be cooled is introduced directly into the piping system of the refrigeration machine at 15 (cf. FIG. 1) and is removed again at 15, the losses and the structural outlay of the heat exchanger 18 can be eliminated.
In the subsequent time period cba, the average temperature of the gas in the working volume is increased to the maximum value by the displacement of the regenerators 36 to 39, which leads to a pressure increase and the closing of the cycle due to the closed valves.
From the partial volume of the working volume, which is divided only by the regenerator 36, (additional) thermal energy is removed by opening the valve 48 or a valve acting in parallel with it with a smaller cross-sectional area before the pressure difference is completely equalized.
Analogously, the partial volume of the working volume, which is only delimited by regenerator 41, is supplied with thermal energy in that a valve acting in parallel with one of the valves 49 is already opened before the pressure difference is completely equalized.

Cooling of the gas over a larger temperature difference T ₁ - T ₂

As in the case of use as a power machine, a greater temperature difference in the amount of gas of mass m _A taken up and given off by the working volume can be achieved in the device shown in FIG. 1 if, in the time period edc, a gas amount of mass m _H is in this case relative to Fig. 8 modified stop as an outlet valve as valve 35 in Fig. 1 acting valve 49 flows into space 15, which is kept open in this time period edc by the control system against the flow pressure.

Function of a gas compressor according to the invention: hot gas + cool gas gives warm gas with higher pressure

Into a working volume of two gas volumes of the masses m _1, m _k with the temperatures T _1, and T take _k and _k at between T ₁ and T lying temperatures T _3, T to be able to leave at higher pressure again _1, must compared For the working volume shown in Fig. 8 as shown in Fig. 24, the following can be changed:
The regenerator 41 is omitted and the heat exchanger 43 is replaced by the regenerator 207.
The regenerators 39 and 207 are therefore connected to each other at a fixed distance and the regenerator 40 is temporarily applied.
Analogously, the regenerator 208 which is temporarily applied to the regenerator 207 with the regenerator 38 which is occasionally applied to the regenerator 39, the regenerator 209 which is occasionally applied to the regenerator 208 with the regenerator 37 which is occasionally applied to the regenerator 38 and the regenerator 210 which is occasionally applied to the regenerator 209 with the temporarily Regenerator 37 adjacent regenerator 36 firmly connected.
The air exchange through the air guide tubes 205 and 211 takes place predominantly simultaneously, as does the air exchange through the air guide tubes 50 and 212.
One of the valves 49 or one of the valves 213, through which the air flows out of or into the air guide tube 212, is used with a changed stop direction like the valve 35 in FIG. 1.

The sequence of movements and the change in the mean temperature T _m (t) or the pressure in the working volume P (t) nevertheless largely correspond to the qualitative representations in FIG. 9. In the period gha, gas with the temperature T ₁ or T _{k is} sucked in through valves. As shown above, there is a linear, stepped temperature curve in the regenerators between the valves in the stroke direction.
Valves must be used to regulate the amount of gas flowing into the working volume in order to maintain a certain temperature difference during cooling or heating of the periodically exchanged amounts of gas.
If the cooler gas is to experience only a minor change in temperature, gas is sucked out of the working volume through a valve 49 acting like valve 35 as described above during its inflow process.
Since the gas from two different partial volumes, which are separated from one another by a regenerator 40, can flow out of the working volume through different valves 49 and 213 into different spaces of the pipeline system, (together with a valve which acts like valve 35), the two Temperature changes occurring temperature differences can be varied over a wide range.
Overall, this type of entropy transformer is easier to set up, since no heat exchanger (eg car cooler) is necessary.
In addition, there can be no sudden steam generation from escaped cooling water.
As already shown above, a system that acts as a gas compressor with minor changes can also act as a heat pump or refrigerator.
This construction can also be operated in such a way that lukewarm gas at higher pressure is periodically pressed into the working volume by a turbine and hot and cold gas periodically flow out of the working volume at a lower pressure.
Both the cycle shown at the front of the heat pump and the one at the chiller can be used.

The respective temperature differences can additionally with a valve that like that Valve 35 acts to be adjusted.

Combination of chiller and engine

If hot gas and cooling water of temperature T _k are available, gas can be cooled below the cooling water temperature T _k by an entropy transformer with 2 working volumes.
In principle, in the refrigeration machine described above, the driven fan 14 is replaced by an engine described above, the hot gas being taken up by the working volume which can be assigned to the engine and, at higher pressure, through the outlet valve 49 or 4 into a space of the piping system is delivered, to which a buffering pressure vessel can be connected and from where the gas, possibly after a previous cooling to approx. T _{k, flows} through the valve 49 acting as an inlet valve into the working volume which can be assigned to the refrigerator.
From this working volume, the gas cooled under T _k flows out through valves 48 and possibly valve 49, which acts like valve 35.
For the coordination of pressure and temperature differences, as shown above, the periodic flow through these valves of the two working volumes can be set accordingly.
If the movements shown in Fig. 4, Fig. 5, Fig. 6 I occur simultaneously in a working volume, the buffering pressure vessel can be dimensioned smaller or can be omitted.

This combination can also be used as a heat pump to heat a liquid be used.

Other interesting combinations serve to increase the heating number to a value above 1
Thus, a hot and cold gas quantity is absorbed by a first working volume as described above and released again as a cool gas quantity at higher pressure, and absorbed by a second working volume which it releases as a warm gas quantity at the outlet pressure. The liquid of a heat exchanger or an additional amount of gas was cooled in the second working volume.

If an isothermal heat source and an isothermal heat sink are available, so it is interesting for heating or cooling, gas, in the front described systems (with the effect of a chiller or heat pump) the Compressor by a known thermal compressor with isothermal To replace thermal energy absorption and heat energy output.

additional change in work volume

Due to the flow through the regenerators when the pressure drops in Working volume, the gas is expanded almost isothermally.

The gas temperature is changed only relatively slightly, since the gas volume flowing through in one period is significantly larger compared to the size of the partial volume of the working volume between two regenerators.
This reduces the irreversibility of gas and heat transfer surfaces of the regenerators.
These advantages can be used particularly well if, in the case of the machine in FIG. 8, in the time period in which the pressure in the working volume would increase even with the working volume unchanged, the working volume is reduced by a piston which is moved periodically by the control system.
In this device it is particularly important that, as shown above, above the regenerator 36 and below 41 grid levels 108 and 109 obstruct vortices and are moved by the control system so that they are largely only flowed through by gas of constant temperature.
Due to the effect described above that a valve acts like the valve 35 in FIG. 1, the temperature interval in which the exchanged gas is cooled or heated can also be set in this construction.

If the gas volume is changed without flowing through the regenerators, the gas between two regenerators is expanded or compressed adiabatically from P ₁ to P ₀ and cooled or heated.
The periodic sequence of movements is similar to that in Fig. 4, Fig. 5, Fig. 6.
The irreversibility of a subsequent flow through one of the adjacent regenerators has a greater effect in terms of efficiency, the greater the temperature change that occurred.
Since this effect also occurs in the known Stirling engines, a structurally simple structure is also interesting, which, except for the regenerator system 11, largely corresponds to FIG. 1 with the change that the regenerator system 11 by the regenerators 37-40 and the associated control system 42-55 from Fig. 8 are replaced.
The periodic sequence of movements can be seen in Fig. 4, Fig. 5, Fig. 6.

Flow around the displacer

In the machine shown in FIG. 21, the working volume largely enclosed by a cylinder as the pressure housing 110, the valves 111, 112 and the slidingly sealed piston 113 is divided into partial volumes by cylindrical displacers 114:
The working fluid can flow around these displacers 114, the gap between the displacer and the cylinder wall acting as a regenerator, in the direction of the cylinder axis they are 3 to 10 times larger than their maximum length of movement against the pressure housing.
When used as an engine, cooling lines 115 cool outside the pressure housing.
A single displacer 114 acts like one of the corresponding regenerators 36-40 in FIG. 8.
For a constant working volume (ie immobile piston in Fig. 21), the argumentation to Fig. 9 can be adopted directly with a transferable movement sequence.

Valves 111 and 112 correspond to valves 49 and 48, respectively.
As with the regenerators in FIG. 8, the displacers 114 are driven by a bundle of concentric tubes 109, the tube with the largest diameter slidingly sealing against the piston 113 and any other tube to the two tubes with the next smaller or next larger diameter becomes.
Outside of the working volume, the drive can then take place with only a relatively small change in the working volume (up to 10%) by means of the piston 113 by means of a lever construction 117 as in FIG. The corresponding connecting rods of the chain drive described in FIG. 8 can act directly on the corresponding tubes of the tube bundle 109.
This structure is all the more interesting the smaller the ratio of the working volume to the cylinder surface, since in this case the heat exchange with the cylinder surface acts constructively like a regenerator.
In order to intensify this effect, this active area must be enlarged by fine slits in the (stroke direction) for working fluids with lower thermal conductivity.
If an even larger heat transfer surface is required to achieve good efficiency, a regenerator to be flowed through must be arranged inside the displacer and the flow resistance in the gap between the cylinder wall and displacer must be of the same order of magnitude as the regenerator at a comparable flow rate. This may require an additional seal.
The heat transfer surface for cooling through the cylinder wall 115 is enlarged by slots in the stroke direction, the working fluid flows around the displacer in this area and must also flow through a regenerator in this displacer.

This machine can also be used for operation with a liquid as a working fluid Working volume can be designed.

The technological problems that occurred (pressure resistance, temperature, stability, seals) were solved by Malone in 1931 for water as the working fluid in machines that are similar in construction to a Stirling engine.
Sources: Malone: A new prime mover-J. of the Royal Society of Arts, Vol 97 1931, No. 4099, p.680-708 or: The development of the hot air motor by Ivo Kolin Professor of Thermodynamics translated into German by Dr. C. Forster page 54, 55 c E. Schmitt, D-6370 Oberursel, Postfach 2006, Tel: (06171) 3364, Fax: (06171) 59518
As shown in Fig. 1, this working volume can be coupled to surrounding systems if they are designed for the corresponding pressures and pressure differences for liquids. eg: instead of gas fan or - turbine:
high pressure pump
As already shown by Malone, the use of a liquid as a working fluid enables the construction of compact machines with high mechanical performance.

Displacer sealed

The working volumes of the entropy transformers in Fig. 22 can be described thermodynamically by the same models that can be connected to Fig. 4, Fig. 5, Fig. 6 or Fig. 9.
The construction shown in Fig. 22, however, looks very different.
The working volume is largely delimited by a pressure housing 128, inlet and outlet valves 130 and 129a, b. In this working volume, the regenerators 131-136, which are stationary relative to the pressure housing, the partition walls 137-141 connected to the regenerators 131-135, walls of the pressure housing and displacers 142-146 slidingly sealed on these walls, delimit partial volumes.
In the operating state, the periodic change in size of these partial volumes corresponds to the periodically changed stroke difference of the corresponding regenerators in FIG.
In order to achieve this periodic movement sequence, the displacers 142-145 can be periodically moved simultaneously.
The racks 146-149 attached to these displacers are driven by gears on a shaft 150a.
This shaft is sealed by the pressure housing out of the working volume and on it the ends of a chain 150 are wound up or unwound, which is stretched over two sprockets 151 and on which the connecting rod 152 engages such a chain transmission control, which in FIG Regenerator 36 drives.
With this chain transmission through the shaft 154 driven by an electric motor, another similar chain transmission 155, which moves the displacer 146 in the same way, is connected in such a way that there is a phase shift of approximately a quarter period with the movement of the other displacers.

In contrast to the displacers in FIG. 21, each of the displacers 142-145 in FIG. 22 adjoins one of the partial volumes between two of the regenerators 131-135 and the partial volume adjacent to the cooler 156.
The displacers 142-145 may practically no longer be flowed around, otherwise the desired balance will not be formed.
To ensure that the flow through the regenerators 131-135 in the time period abc, def, ghj (see FIG. 9) is as uniform as possible, the displacers have slots in the region which is inserted between two regenerators, from one regenerator to the other and in the stroke direction ,
The resulting dead volume can have a very unfavorable effect in some applications.
Another valve 129 can be used like valve 35 in FIG.

As shown in FIG. 8, the construction of FIG. 22 as an engine, Chiller, heat pump, ... are trained or used.

Liquid displacer

For another construction, the construction shown in Fig. 22 is modified as shown in Fig. 23.
The displacement pistons are designed as a vibrating liquid column with a float in a U-shaped container.
The movement of the liquid displacement piston is controlled and driven by a belt 159 which is tensioned on a shaft 158 and which is attached to the float 157.
Since the liquid displacement pistons perform largely the same periodic movements, as explained for FIG. 22 with FIG. 9, several of the liquid displacement pistons corresponding to the displacement pistons 142-145 can also be driven from a shaft 158 corresponding to 150 a in the operating state with this construction.
The periodic movement of this shaft 158 can be controlled and / or driven as described in FIG. 22.

min two heat exchangers in a pressure housing according to the invention:

If a liquid is to experience a temperature change over a large interval through contact with a cyclic process, each of the regenerators 131-134 in FIG. 22 must be provided with a heat exchanger on the same side with regard to the flow as in regenerator 135.
The liquid can then flow through these heat exchangers in sequence and thereby exchange thermal energy at several temperature levels (see Fig. 3).

Integration of motor + thermal gas compressor

The thermal energy given off by the exhaust gas of a gasoline or diesel engine during cooling can be used to generate additional mechanical or electrical energy or to charge the engine with filtered fresh air at a higher pressure, thereby avoiding the need to use mechanical energy for a turbocharger or compressor. whereby, compared to an engine without this supercharging, a better output volume and in any case a better efficiency can be achieved.
Compared to an engine without charging, a cheaper engine power volume with an improved efficiency is possible, since when the engine is charged by a compressor or turbocharger, the compression of the air takes place with a less efficient efficiency.
Further synergy effects are achieved in that no turbine and no additional generator are required to convert the energy of the compressed air into electrical energy.

Integration of gas turbine and thermal gas compressor

Largely analogous to the front of the internal combustion engine, the thermal energy emitted by the exhaust gas of a gas turbine during cooling can be used to supply the cool gas with filtered, cool fresh air at higher pressure.
The compressor of the gas turbine used can be designed so that it requires less drive energy with unchanged pressure in the combustion chamber and with unchanged gas flow, which leads directly to a greater useful output with the same fuel consumption and better efficiency.
The efficiency in this case is greater due to a synergy effect than the sum of the efficiency of the original gas turbine and the efficiency of the thermal compressor (gas compressor), since the power applied by the thermal compressor for gas partial compression from the original compressor of the gas turbine only with less favorable Efficiency can be achieved, driven by the branching of mechanical shaft power.
Possibly. it is also possible to use a conventional gas turbine. A relative pressure increase in the gas turbine can then be expected, which decreases continuously from the fresh air inlet to the exhaust gas outlet, as a result of which the power density and efficiency are increased.

In order to achieve high outputs of several 100 kW at atmospheric pressure ratios, the area of the regenerators 274 - 277 through which flow is required must be increased accordingly.
In order to achieve a compact housing shape 278, the stationary regenerators 274-277 are folded several times at a substantially constant distance along parallels 278 and enclose at least one disk-shaped displacer element 279, which is periodically moved parallel to it, up to the area of the central axis of the displacer element parallel to the folded edges on both sides.
The other half of the displacement element is surrounded by the adjacent regenerator.
In the case of a round car construction, the folded edges of the regenerator are accordingly on concentric circles.

At least one of the regenerators is optionally available with one in the stroke direction movable hydraulic or pneumatic pistons or diaphragm bellows connected by Liquid or gas from the room around the corresponding work area removed liquid surface of the coupled vibrating liquid column is filled or filled via control valves.

To make even more special movements, such as for a direct drive of the Described below with liquid in the work area and moving regenerators two-part displacement structure is necessary to be able to realize the movement either by means of a rod or a tensioned tension element (such as a rope or chain) a flexible connection from an endless traction element like a closed chain or toothed belt, tapped, which non-positively over several, with relative even angular speed rotating wheels is so tense that the angle between the two elements in time periods of the operating state in which the driven element in the working space (regenerator, displacer) only slightly should be moved about 90 ° and the smaller the faster the movement of the driven element in the work space.

A pipeline system with negative pressure like the boiler via a heater is coupled to the inlet valve of a heat engine according to the invention.
This system is used as a vacuum cleaner.

The effort for the housing 280 around the workspace can be significantly reduced if curved shapes are used.
The moving regenerators 281-284, constructed in the form of a cone shell, have good dimensional stability, can be produced with reasonable effort and can only be driven in the area of the cone tips.
For sealing purposes, each regenerator is connected to a sheet metal cylinder jacket 285 or a comparable jacket of a pointed truncated cone, which is continuously immersed in a liquid 286 at the lower end and thus prevents flow around the regenerator during stroke movements parallel to the cylinder axis of the sheet metal jacket.
Truncated cones, which become narrower at the top, are favorable and unproblematic as a shape for the sealing element 285 immersed in the liquid and the side housing 280, since the upper region is expanded due to the temperature increase.
The cone-obtuse angle must be relatively acute so that the gap between two sealing elements 285 does not widen too much when they are moved apart, since irreversible processes take place in this gap due to the heat transfer.
Concentric tubes 286 are used to drive and guide the regenerators and sealing cylinders, which are guided on an unmoved tube 287 on the common axis of the cylinders and are connected to the regenerators 281-285 in the region of the cone tips.
In this area, the tubes 286 are provided with at least one slot in the axial direction, through which the internal tubes are connected to the corresponding regenerators 281-284.
The tubes 287 protrude decisively upwards over the uppermost regenerator 281 into a special bulge 288 of the work space enclosed by the housing and are slidably guided there on an unmoved tube 287.
Below the liquid surface 288, the cylinders 285 are also each connected to one of the tubes 286, which are also slidably guided in this area.
The space between the liquid surface 288 and the lowermost regenerator 284 at its lowest position in the operating state is largely filled by an at least two-part displacer structure 289, which is moved apart during an upward movement and releases flow channels for the working gas at the separating surfaces which run at an angle to the direction of movement.
This displacer structure 289 is also guided in the region of the cylinder axis and either moved via a separate drive or by springs between the regenerator 284 and individual displacement elements and a spring-loaded stop for the stop at the liquid interface 288.
If, alternatively, this displacer 289 is permanently connected in one piece form to the lowest regenerator 284, then two parts have to be moved less.
For this, the dead space becomes larger because of the necessary permanent air channels through the displacer 289 or on its surface.
The heat exchanger 290 is either attached directly below the lowermost regenerator 284 and flows through a heat exchange medium, or it is attached to the cylinder 285 and / or the corresponding pipe 286 with the lowest regenerator 284 and immersed in the lowest position in the liquid 286, whereby the heat energy is exchanged, which is compensated for in continuous operation by a stationary heat exchanger, which is connected, for example, to the hot water supply of the building.
Working gas is exchanged periodically by at least one valve 291 in the housing above the uppermost regenerator 281. This exchange is compensated for by the exchange of working gas, which takes place from the partial space above the lowermost regenerator 284 through at least one piercing tube attached directly to one end in the stroke direction, which is always immersed in the liquid 286.
A tube 293, which projects beyond the liquid level 288 and from which the gas exchange takes place through at least one valve 294, is arranged in a concentric manner in a sealed manner with the housing.

If the lower regenerator moves too quickly or becomes blocked, liquid can flow into this tube.
If this has to be avoided due to a disturbing or critical steam development, at least one further tube is arranged in it, the upper edge of which extends even further beyond the liquid level.
The space is connected by a separate valve, which is controlled together with the gas valve, to a space which is also connected to the space with which the working space exchanges gas through the adjacent pipe.
Depending on the design of these valves, it can alternatively be simpler, see the water level via an additional corresponding pipe arrangement. 295 to check, in which the pipe for gas exchange is omitted.
This pipe cf. 295 is also supplied with water via a further pipe cf. 296 which is used as an overflow and which is arranged largely in the stroke direction within the liquid with an opening at the level of the largely immobile liquid level without penetrating a regenerator.
A porous structure (see 297) is integrated into the lower area of the overflow (see 296) so that the lowest regenerator cannot be flowed through by this tube arrangement.

Intermediate levers are movably attached to a plurality of regenerators 281 - 284 or elements rigidly connected to them, which are each movably connected at the other end to different locations of at least one further main lever, which is movably connected either directly or via a lever to the housing.
The top regenerator 281 directly or indirectly movably engages the main lever at a location that is closest to the location where the direct or indirect movable connection to the housing occurs.
The mirror symmetry of this lifting arrangement to a plane in which the stroke direction lies also means that no lateral forces are transmitted to the regenerator structure, in particular if the lever arrangement takes place below the centroids.

One of the lowest regenerators is movably connected via connecting rods 298 to two driven crankshafts 299, which are arranged and moved mirror-symmetrically to a plane in which the stationary guide element 287 lies in the stroke direction.
Lower regenerative forces relative to the stroke direction, which would have to be absorbed by the guides 300 and lead to additional wear, are transmitted to the regenerator arrangement 281-285, in particular if the connecting rods 298 run below the center of gravity of the regenerators 281-284
Masses are attached to the crankshaft 299 opposite the connecting rod bearing, which at least partially compensate for the weight of the regenerator arrangement due to their weight.
Optionally, as an alternative to the drive system of the regenerators, several regenerators are at least each movably connected to one of the connecting rods, which are supported at the other ends on axles of at least one crankshaft, all of which can be cut by a line through the axis of rotation of the crankshaft parallel to it, whereby the bearing for a connecting rod of the lowest regenerator is furthest from the axis of rotation of the crankshaft and the bearing of the highest regenerator is closest.

As with a comparable Stirling engine, at least one regenerator is driven with a phase shift of a quarter (25%) of a period in relation to the change in volume.
In the time period with the lowest pressure in the work area (work area = work volume) with a periodically changed volume, when operating as a power machine, the periodic intake takes place and when operating as a heat pump or refrigeration machine, the working fluid is periodically released through a valve 291, which is activated in the work area adjoins a partial space 301 with constant volume, which is completely enclosed by two regenerators 302-303, one of these regenerators 302 being relatively directly adjacent to the housing.
Optionally, as an alternative to the drive described above, at least one guide element in the stroke direction 287 is at least partially designed as a threaded rod or recirculating ball screw, and by means of an element engaging therein, at least one regenerator connected to it is moved in the lifting direction by rotating the threaded rod or Kubelumlspindel.
Optionally, as a more special alternative, the threaded rod or ball screw has areas with different pitches, in which the connecting elements of the regenerators moving at different speeds engage, so that when the threaded rod or ball screw rotates at different speeds they are moved in the stroke direction, so the number of movable Parts can be significantly reduced.
A heat engine according to the invention can thus be constructed with only five moving parts and the necessary valves.

In these alternatives, the regenerators are periodically moved up and down in the direction of stroke when the ball screw rotates at a constant speed, or at least one threaded rod or ball screw is rotated periodically in different directions by using a cube screw and interlocking connecting elements, each with a closed, intersecting threaded path either by a mechanical control system or directly by an appropriately controlled motor
For a construction that can be realized with commercially available parts, the bottom regenerator engages in a ball screw with a closed path and at least a part of the other regenerators in rather ordinary thread paths whose paths are not closed.
This prevents the bottom regenerator from hitting the liquid surface.
The guide tube is flowed through periodically or continuously in the middle of working gas from the coolest part.
A radial fan is connected to the pipe with thread or ball screw and the pipe in this area is opened laterally as well as in the coolest part on the other side of the pipe center.
A separate pipeline for working gas leads from the space adjacent to one opening of the guide tube to the space adjacent to the other opening in the area of the liquid surface.
It has already been shown that periodic compression increases the energy turnover by periodically changing the volume of the work space.
This is most effectively achieved by coupling a pipe 304 with a water column 305 vibrating in the operating state to the coldest area in the work area.

For this purpose, a tube 306 is stirred in the stroke direction with an opening above the liquid surface 288 from the housing 280.
In a system with a single work space, the other end of the coupled pipe 304 of the periodically resonating liquid column 305 is connected to a pressure vessel 306.
There is optionally a connection 307 of the two rooms 308, 309 adjoining the ends of the liquid column 305 at the level of the desired central liquid surface 310 with a reducing valve 311, so that only a negligible amount of liquid can flow through periodically for pressure compensation, but a significant amount of gas or a small portion of the working gas is fed to the pressure vessel per period through a pipe system with a non-return valve from the work area and another pipe with a non-return valve is connected to the pressure vessel at the desired mean height of the liquid surface, which leads into the space that leads to the other end of the Liquid column adjoins, whereby only a negligible amount of liquid flows periodically, but a significant gas atom.
This stabilizes the amount of gas in the pressure vessel.
A valve 312 is attached to the connection from the working space to the tube with the vibrating liquid column, which has a stop in the flow direction to the working space, against which the valve plate 313 is pressed in a sealed manner as soon as the liquid column has moved too far in the direction of the working space.
When this valve is closed, the excess pressure which builds up in front of it can pass through a pressure relief valve leading from this space 308 to the pipe system of the vibrating water column and a special pipe (into the pressure vessel) to the other end 309 of the vibrating liquid column 305.

Another pressure relief valve 315, coupled to the same space 308, leads to an external container 316 instead of the pressure vessel 309.
The liquid level in this container is kept constant at the highest possible level.
It is connected to a further check valve with one end of the pipe system around the vibrating water column, through which a small amount of the liquid can flow back again in certain time periods.
A tube 295a extending in the stroke direction is fastened to the lowest periodically moving regenerator, into which gas can flow in and out unhindered from the part space above it and the bottom end of which is always immersed in the liquid.
A pipe 295b is arranged concentrically in this pipe 295a, sealingly connected to the housing, the upper edge of which corresponds to the height of the maximum liquid surface 288 applied to the sealing cylinder 285 of the regenerator and that in an area in the working space above the safety valve 313 at the access to the vibrating water column 305 leads from which the possibly overflowing liquid reaches the liquid of the vibrating liquid column 305.
A tube 299, the upper edge of which ends in the lowermost subspace at the level of the desired liquid surface 288 in the working space, is connected as far as possible to the previously described tube 295, which leads to the vibrating liquid column 305.
If the liquid level in the working space 288 is higher than the connection of the associated tube end to the shrinking liquid column at the valve 313, then a porous structure 297 is integrated from the confluence into the previously described pipe system, which cannot be flowed around.
A valve supplies the machine with a certain amount (eg 3l) of liquid each time the machine is rigid.
The rest of the management of the different amounts of liquid in the machine is done automatically with the construction described above and the functional relationships.

The pressure vessel can optionally be replaced by another work space, in which the thermodynamic cycle with an identical period by half Period is staggered

A bulk material storage works well thermodynamically and becomes bearable Effort built up by flowing through the heat transfer medium (e.g. air) Bulk material 348 through at least one insulating, non-flowable intermediate layer 349 in concentric shells with cylindrical mantle with vertical axis and after outside vaulted floor and top surfaces is divided and the flowable Transitions 350 from an inner, filled with Schürgut to the adjacent outer shell through openings in the insulating cylinder jacket 349, which are arranged on both sides in the area of a plane through the cylinder axis and the flow through non-flow bores running in the area of this plane Connections are made so that the shells only in one direction of rotation can flow through the vertical cylinder axis.

A transition between two half-shells filled with bulk material is only possible when flowing through a vertical shaft 351, via which the heat transfer medium can also be exchanged.
As a result, the flow can be controlled by reducing the inflow channel in places so that only heat transfer medium flows in a narrow temperature range in the shaft.

One of the outermost insulation layers 352 becomes a bed layer flowed through others. This creates a decisive curvature of the Temperature profile out, which due to the smaller slope on the cooler Side only a lower loss of heat energy flow than without the flow through the temperature gradient occurs.

In the horizontally running bulk material layers 353, in particular in the area of the cylinder axis 354, the flow paths are lengthened by additional smaller impermeable barriers 355.
As a result, flow through these layers of bulk material 353 is relatively uniform, the flow paths are approximately the same length as in the cylinder jacket 356, and there is no unfavorable mixing of the heat transfer medium at different temperatures.

For seasonal storage, the bulk material storage becomes hot when it cools down Incoming and coolly flowing air heated to well over 100 ° C and the Bulk storage is removed a few weeks later by air, which flows into the outer storage area at approx. 50 ° C and through one of the Air channels at 120 ° C - 150 ° C is removed and then cooled by a heat exchanger, which heats water from approx. 40 ° C to 100 ° C isolated water storage in the lower area and in the upper area is fed.

The waste heat from the heat engine operated as a hot gas engine is used in houses to supply energy for heating and hot water.
A memory is interposed to decouple the operation of the machine from the heat requirement.
A high synergy effect is achieved if the storage is not filled with pure water, but with organic waste and faeces.
Especially when seasonal heat storage is sought, the faeces in the summer are too hot for decomposition reactions or the generation of biogas to take place to a significant extent.
This effect is used in a similar way when preserving fruit.
If this storage facility is cooled in late autumn or winter, biogas production can begin.
This not only saves heat energy seasonally, it also indirectly stores biogas

Claims (26)

1. A method for entropy transfer via an open periodic thermodynamic cyclic process, with
      at least one working volume filled with a working fluid,
      at least one central partial volume in the working volume, which is located between two isothermal sectional areas and is periodically modified in size,
      wherein a flow of working fluid through the central partial volume takes place from one isothermal sectional area to the other one,
      wherein an exchange of working fluid takes place at different pressure levels and at different time periods (c-d-e, g-h-a) from the working volume to at least one volume having a largely constant pressure and/or from at least one volume having a largely constant pressure into the working volume,
      wherein a modification of the working fluid temperature averaged through the working volume is concurrently brought about by the periodic modification of size of the at least one central partial volume,
      wherein at least one central partial volume is modified in size during the exchange of working fluid at a largely constant pressure,
      wherein the size of the at least one central partial volume, or the ratio of its size relative to that of the working volume, is largely kept constant when (a-b-c, e-f-g) the pressure in the working volume is modified without exchange of working fluid,
      wherein heat is input and/or output in the range of the at least two isothermal sectional areas,
      wherein one respective further partial volume borders on each of the flow section isothermal areas delimiting the at least one central partial volume, the working fluid in the partial volumes presents different temperatures, and the sizes of the partial volumes are modified periodically,
      wherein, during a time interval much longer in comparison with the duration of one period of the cyclic process, either intake of heat energy to or discharge of heat energy from the working fluid in the working volume takes place with the aid of at least one substance of at least one continuously or periodically increasing and decreasing mass flow at a sliding temperature or at several temperature levels.
2. The method according to claim 1, characterized in that the intake of working fluid into the working volume and the discharge of working fluid from the working volume each take place starting out from partial volumes having different temperatures and being separated by one of the isothermal sectional areas in the range of which heat energy is taken in by and/or discharged from the working fluid.
3. The method according to claim 1 or 2, characterized in that a further exchange of working fluid takes place at identical time periods and at approximately identical pressure levels.
4. The method according to any one of the preceding claims, characterized in that the size of the at least one working volume is modified periodically.
5. The method according to any one of the preceding claims, characterized in that the size of the at least one working volume is modified periodically, primarily in those time periods (a-b-c, e-f-g, cp. Figs. 4-6) during which no intake or discharge of working fluid into or from the working volume takes place.
6. The method according to any one of the preceding claims, characterized in that at least one substance is the working fluid.
7. The method according to any one of the preceding claims, characterized in that the open periodic cyclic process is powered by solar energy, geothermal energy, combustion energy, in particular from regenerative renewable raw materials, waste heat, or nuclear power.
8. The method according to any one of the preceding claims, characterized in that the drive energy is intermediately stored in a storage flowed through by the substance, which storage in particular has the form of a bulk material.
9. A device for implementing the method according to any one of the preceding claims, comprising:

   at least one working volume (11, 8, 36-41, 43, 114, 131-135, 156, 207-210, 281-284, 275-277) filled with a working fluid (301, 310) in a pressure vessel (1, 128, 302, 288, 107),

   at least two flow passage devices (11, 8, 36-41, 43, 114, 131-135, 156, 207-210, 281-284, 275-277) for confining at least one central partial volume (11, 36-41, 131-135, 207-210, 281-284, 275-277) periodically modified in size in the working volume,

   at least one means (21-24, 29-32, 55-991, 117, 150-155, 298-300) for periodically modifying the size of the at least one central partial volume, so that a modification of the temperature of the working fluid averaged through the working volume is concurrently brought about thereby during the working fluid exchange at a largely constant pressure, and the size of the at least one central partial volume, or the ratio of its size relative to that of the working volume, is largely kept constant when the pressure in the working volume is modified without exchange of working fluid,

   at least one means (146, 2, 22, 29-32, 113, 304-316, 11, 36-41, 131-135, 207-210, 281-284, 275-277) for modifying the pressure in the working volume,

   at least one means (18, 8, 11, 36-41, 131-135, 207-210, 281-284, 275-277, 7, 43, 115, 156, 290) for intake of heat energy to or discharge of heat energy from the working fluid in the working volume with the aid of at least one substance of at least one continuously or periodically increasing and decreasing mass flow at sliding temperature or at several temperature levels during a time interval much longer in comparison with the duration of a period of the cyclic process,

      wherein at least one valve (3, 4, 48, 49, 111, 112, 130, 129a, 129b, 291, 294) is opened for the intake of working fluid or discharge of working fluid from at least one or into at least one space (13, 20, 19, 17) having a substantially constant pressure for the purpose of the exchange of working fluid at different pressure levels,
      wherein heat energy is taken in by and/or discharged from the working fluid and respective isothermal sectional areas interconnected via seal means (285, 288, 101, cp. Fig. 13) or the delimitation of the working volume (1, 44) extend in the range of the at least two flow passage devices (11, 8, 36-41, 43, 114, 131-135, 156, 207-210, 281-284, 275-277),
      wherein in the range of the flow passage devices (11, 8, 36-41, 43, 114, 131-135, 156, 207-210, 281-284, 275-277) one partial volume each periodically modified in size and having a different temperature borders on the side of the isothermal sectional areas facing away to the central partial volume.
10. The device according to claim 9, characterized in that a regenerator (8, 11, 36-41, 131-135, 207-210, 281-284, 275-277) is arranged in the range of the isothermal sectional area where heat energy exchange takes place.
11. The device according to any one of preceding claims 9 to 10, characterized in that a heat exchanger (7, 43, 115, 156, 290) is arranged in the range of the isothermal sectional area where the heat energy exchange takes place.
12. The device according to any one of preceding claims 9 to 11, characterized    by a control system (21-24, 29-32, 55-91, 117, 150-155, 298-300) for periodically moving the at least two flow passage devices (11, 8, 36-41, 43, 114, 207-210, 281-284) against each other, to reduce the central partial volume between the flow passage devices (11, 8, 36-41, 43, 114, 207-210, 281-284) to the clearance volume during at least one time period.
13. The device according to any one of preceding claims 9 to 12, characterized in that
       the at least two flow passage devices (114, 131-135, 156, 274-277) are fixedly mounted in the working volume, and the intermediately positioned, central partial volume is reduced to the clearance volume during at least one time period with the aid of at least one displacement member (279, 114, 142-145) periodically interposed by the control system (117, 150-155).
14. The device according to any one of preceding claims 9 to 12, characterized in that the at least two flow passage devices have the form of displacement pistons (114) movable against each other, with the central partial volume being located between two respective displacement pistons (114).
15. The device according to one of preceding claims 9 to 14, characterized by a compressing device (2, 22, 29-32, 113, 304-316) for periodically modifying the size of the working volume.
16. The device according to claim 15, characterized in that the compressing device comprises at least one movable liquid column (304).
17. The device according to claim 15 or 16, characterized in that the compressing device is a resonant oscillating system (304-316) synchronized with the other periodical movements.
18. The device according to any one of preceding claims 15 to 17, characterized in that the control system is designed for control and feedback control of the compressing device (2, 22, 29-32, 113).
19. The device according to any one of preceding claims 15 to 18, characterized in that the flow passage devices (11, 8, 36-41, 43, 114, 131-135, 156, 207-210, 281-284, 275-277) capable of containing a flow of working fluid therethrough serve the purpose of separating, purifying, or physically or chemically modifying the substances contained in the working fluid.
20. The device according to any one of preceding claims 12 to 19, characterized in that the direction of movement and the axis of symmetry of the flow passage devices (11, 8, 36-41, 43, 114, 207-210, 281-284) is vertical, and the flow passages in particular are conical in shape.
21. The device according to any one of preceding claims 12 to 20, characterized in that two respective, not immediately neighbouring flow passage devices (11, 8, 36-41, 43, 114, 131-135, 156, 207-210, 281-284, 275-277) each are coupled to each other at fixed spacings in a direction of movement via members, and two respective, immediately neighbouring flow passage devices each periodically move towards each other and away from each other again.
22. The device according to any one of preceding claims 9 to 21, characterized by a turbine (14) connected to two spaces (13, 15) having different pressures,
    wherein the two spaces (13, 15) are connected with the working volume through the intermediary of the at least one valve (3, 4, 48, 49, 111, 112, 130, 29a, 129b, 291, 294).
23. A device characterized by serial arrangement of a plurality of devices according to any one of preceding claims 9 to 22.
24. A device characterized by parallel arrangement of a plurality of devices according to any one of preceding claims 9 to 22.
25. The device according to according to any one of claims 15 to 24, characterized in that at least one of the flow passage devices (11, 8, 36-41, 43, 114, 131-135, 156, 207-210, 281-284, 275-277) is driven at a phase difference of one quarter (25%) relative to the compressing device (2, 22, 29-32, 113, 304-316).
26. The device according to any one of preceding claims 15 to 24, characterized by use in the framework of combined heat and power generation, in particular in short-distance and long-distance heat energy networks

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