DE102022114439A1 - Device for compression, expansion, volume change, displacement of a fluid working medium, thermoelectric converter and computer-controlled or electronically controlled method - Google Patents

Abstract

The invention relates to a device for compression, expansion, volume change and displacement of a fluid working medium which consists at least partially of gas, the device comprising: at least one volume which comprises a liquid quantity of a liquid and a partial volume with a working medium; Volume limiting elements that limit the volume and which are designed such that one or more passages allow a maximum of a predetermined subset of the amount of liquid to flow out during a compression, expansion or displacement period. During the compression, expansion or displacement period, the amount of liquid rotates about an axis of rotation, the volume limiting elements preventing an annular flow of the amount of liquid around the axis of rotation, and the volume's overall size can be changed by displacing at least one of the volume limiting elements. The invention further relates to a thermoelectric converter with at least one of the devices and a computer-controlled or electronically controlled method for operating the thermoelectric converter.

Description

The invention relates to a device for compression, expansion, volume change and displacement of a fluid working medium according to the preamble of claim 1, a thermoelectric converter according to claim 11 and a computer-controlled or electronically controlled method according to claim 14.

State of the art

There are already devices for the compression or expansion of gases in which this is partially or largely isothermal. An example of this is the compression or expansion spaces of flat plate Stirling engines. Another example are liquid ring pumps, in which a gas is thermally coupled to a liquid during expansion or compression. Flat plate Stirling engines have the disadvantage that the heat transfer in the compression or expansion space from or to the working gas takes place via a heat exchanger, which requires a higher temperature gradient than if the working gas (i.e. the gas to be compressed or expanded) is directly thermally connected to the medium would be coupled to which the heat is to be extracted or supplied (e.g. a liquid such as water as a heat transfer medium). In addition, flat plate Stirling engines have a comparatively complex structure and only achieve low power densities. Liquid ring pumps have such a direct coupling of the working gas to a liquid as a heat transfer medium. However, they have the disadvantage that strong liquid flows occur during operation, which are caused by the eccentric rotation of the impeller and by the pressure changes in the gas to be compressed or expanded. For these flows, energy from the drive of the liquid ring pump must be applied, which ultimately does not benefit the function of compression or expansion of the working gas, but rather leads to the heating of the liquid as a flow loss and thus represents a power loss. Therefore, the efficiencies of liquid ring pumps are usually significantly lower than those of other pumps or devices for compressing or expanding gases.

Today, machines that work according to the Clausius-Rankine cycle, the Ericsson process or the Stirling process are often used to convert heat/cold or quantities of heat into mechanical/electrical energy or vice versa. A working medium is alternately compressed at a certain temperature and expanded at a certain other temperature, giving off or absorbing amounts of heat. In particular, in the Clausius-Rankine process, a phase transition of the medium between liquid and gaseous can occur; in the Stirling process and the Ericsson process, the working medium usually remains gaseous, although embodiments with at least partial phase change also exist. The Vuilleumier process is also used to convert quantities of heat at certain temperatures into quantities of heat at certain other temperatures. Other operating principles such as adsorption or absorption heat pumps are also part of the state of the art.

1. 1. Die Expansion und/oder Kompression des verwendeten Arbeitsmediums findet weitgehend adiabatisch und nicht isotherm statt
2. 2. Die Wärmetauscherflächen sind zu klein oder die Kopplung der zu-/abgeführten Wärmemengen an das Arbeitsmedium nicht ausreichend, um einen Wärmeübergang zu gewährleisten, der das Arbeitsgas in der verfügbaren Zeit weit genug erwärmt/abkühlt.
3. 3. In Stirlingmaschinen existieren Toträume, so dass sich das Arbeitsgas während der Expansion oder Kompression nicht vollständig in den vorgesehenen Expansions- bzw. Kompressionsvolumina befindet
4. 4. Beim Betrieb entstehen mechanische Reibungsverluste oder strömungsmechanische Reibungsverluste

Stirling machines and machines that implement the Clausius-Rankine cycle or the Ericsson process now have the disadvantage that their manufacturing costs are often not economical in relation to the amount of energy that can be converted. Furthermore, they usually have efficiencies that, due to the technical implementation, are far worse than the ideal Carnot efficiency for heat engines or heat pumps. This is due to, among others, the following reasons:

1. 1. The expansion and/or compression of the working medium used takes place largely adiabatic and not isothermally
2. 2. The heat exchanger surfaces are too small or the coupling of the heat supplied/removed to the working medium is not sufficient to ensure a heat transfer that heats/cools the working gas sufficiently in the available time.
3. 3. Dead spaces exist in Stirling engines, so that the working gas is not completely in the intended expansion or compression volumes during expansion or compression
4. 4. Mechanical friction losses or fluid mechanical friction losses occur during operation

In the patent EP 2 657 497 B1 describes a thermoelectric converter that largely solves the first three of the above problems by having heat exchangers that are periodically immersed in liquids. These fluids are coupled to external heat sources/sinks. The advantage of this is that this thermoelectric converter works with minimal dead spaces, that an almost isothermal compression/expansion takes place due to the position of the heat exchangers in the compression/expansion spaces and that very good heat transfer occurs due to the comparatively large heat exchanger surfaces and the periodic immersion in the liquid between the external heat sources/sinks and the working medium is guaranteed. However, this is thermoelectric The power or power density of the converter is limited: It can be operated at a maximum operating frequency at which the periodic immersion of the heat exchanger surfaces in the liquid does not result in the liquid being partially carried along when the heat exchanger surfaces are pulled out and thus “splashing around” in an uncoordinated manner in the working space “. This maximum working frequency is determined primarily by the weight of the liquid and by the amplitude of the movement of the volume change elements and heat exchanger surfaces.

The device results in a significant increase in the maximum working frequency and thus the power or power density DE 102018 212 088 B3 enabled. It works according to a similar principle, in which volume limiting elements and possible additional heat exchanger surfaces are periodically immersed in a liquid, whereby this liquid executes a rotational movement and is thus prevented from “squirting out” by centrifugal forces even at higher working frequencies, since the centrifugal forces that occur are significantly higher than that corresponding weight of the liquid. However, in the in DE 10 2018 212 088 B3 The device described causes a strong liquid flow, which leads to high fluid mechanical friction losses. This is caused primarily by the displacement of liquid from the areas between the screw blades or into these areas, which is caused, among other things, by the changes in the pressure of the working medium. This flow can take place unhindered because the liquid is not prevented from doing so by any limiting elements. For this flow, mechanical energy from the rotary movement of the rotors is applied, which is ultimately converted into frictional heat within the liquid and thus means a high power loss.

Task

The object of the invention is to provide a method and a thermoelectric converter which enable a largely isothermal compression or expansion of a working medium.

Solution

This object is achieved by the device according to claim 1, the thermoelectric converter according to claim 11 and the computer-controlled or electronically controlled method according to claim 14. Further embodiments are disclosed in the subclaims.

The invention relates to a device for a largely isothermal compression or expansion of a working medium (usually gas or gas with liquid mist) - in contrast to the widespread, largely adiabatic devices for gas compression or gas expansion such as piston compressors. In addition to the compression or expansion of the working medium, a phase transition of a component of the working medium from gaseous to liquid or from liquid to gaseous can also take place within the device. The isothermal change in the state of the gas makes it possible, for example, to achieve compression that requires less mechanical or electrical energy compared to adiabatic compression. The temperature change that occurs when the working medium is compressed or expanded can therefore be compensated for very quickly by the working medium giving off or absorbing heat energy to the liquid and thus being kept largely constant at a temperature that corresponds to that of the liquid. In other words, this means that compression or expansion of the working medium can occur largely isothermally.

Such a largely isothermal change in the state of a gas is particularly advantageous when implementing thermodynamic cycles such as the Stirling process, the Ericsson process or the Clausius-Rankine process, as it allows higher efficiencies to be achieved than in the case of largely adiabatic changes in state . In these processes, a working medium that is at least partially or temporarily gaseous goes through a thermodynamic cycle, whereby its pressure, temperature, volume and other state variables change.

• • ...von Wärmemengen (Wärmequelle und Wärmesenke mit unterschiedlichen Temperaturen) in mechanische/elektrische Energie oder ...
• • .. von mechanischer/elektrischer Energie in Wärme und Kälte oder ...
• • .. von Wärmemengen mit gewissen Temperaturen in Wärmemengen mit gewissen anderen Temperaturen verwendet werden.

Therefore, the invention may be embodied in a device/method for converting...

• • ...from amounts of heat (heat source and heat sink with different temperatures) into mechanical/electrical energy or ...
• • .. from mechanical/electrical energy in heat and cold or ...
• • .. from quantities of heat with certain temperatures to be used in quantities of heat with certain other temperatures.

The heat/cold can be coupled to this thermoelectric converter, for example, using liquids as heat carriers. Therefore, its area of application can be, for example, at temperatures and pressures at which these heat transfer media are liquid.

This application can replace conventional heat pumps, heat engines or devices for converting (waste) heat or cold or quantities of heat with certain temperature differences into useful heat and/or useful cold.

• • .. hohe Wirkungsgrade. Dies wird erstens erreicht durch die weitgehend isotherme Prozessführung, zweitens durch einen effektiven, direkten Übertrag von Wärmemengen zwischen dem verwendeten Arbeitsmedium und den Flüssigkeiten als Wärmeträger ohne einer zusätzlichen Wärmetauscherwand zwischen den Medien, und drittens durch die Vermeidung von Strömungsverlusten, wie sie bei anderen, weitgehend isothermen Vorrichtungen zur Kompression oder Expansion eines Gases (wie z.B. Flüssigkeitsringpumpen) auftreten.
• • ... und durch die Nutzbarkeit kleiner Temperaturunterschiede für den Antrieb der Vorrichtung oder durch die Möglichkeit, auch kleine Temperaturunterschiede in der Funktion als Wärmepumpe effizient erzeugen zu können. Dies ist möglich wegen der direkten Kopplung des in der Maschine verwendeten Arbeitsmediums an die Flüssigkeit als Wärmeträger ohne den Umweg über einen Wärmetauscher.

The invention can enable:

• • .. high efficiencies. This is achieved firstly by the largely isothermal process control, secondly by an effective, direct transfer of heat quantities between the working medium used and the liquids as a heat transfer medium without an additional heat exchanger wall between the media, and thirdly by largely avoiding flow losses, as is the case with others isothermal devices for compressing or expanding a gas (such as liquid ring pumps) occur.
• • ... and through the use of small temperature differences to drive the device or through the possibility of being able to efficiently generate even small temperature differences when functioning as a heat pump. This is possible because of the direct coupling of the working medium used in the machine to the liquid as a heat transfer medium without the detour via a heat exchanger.

Furthermore, the invention can be used to achieve low wear and a comparatively simple and cost-effective structure.

Alternatively, the isothermal change of state can also be used in other applications in which a largely isothermal compression or expansion of a gas or a fluid containing a gas is advantageous, e.g. as a vacuum pump, as a gas compressor, for compressed air generation, compression and expansion device for compressed air energy storage, Expansion device for converting gas pressure into mechanical/electrical energy, etc. Since a phase transition of components of the working gas or the liquid used can also take place in the compression and expansion device, it is also suitable for applications such as liquefaction of gases (e.g. natural gas, Nitrogen) or the drying of gases (e.g. air).

The invention relates to a device for compression, expansion, volume change and displacement of a fluid working medium which consists at least partially of gas. The device comprises at least a volume that includes a liquid quantity of a liquid and a partial volume with a working medium, and volume limiting elements that limit the volume and that are designed such that one or more passages prevent an outflow of during a compression, expansion or displacement period allow a maximum of a predetermined subset of the liquid quantity. During the compression, expansion or displacement period, the quantity of liquid rotates about an axis of rotation. The volume limiting elements are also designed to prevent an annular flow of the amount of liquid around the axis of rotation. During the compression, expansion or displacement period, the volume's overall size can be changed by moving at least one of the volume limiting elements.

The volume limiting element can limit the volume to one or more passages (for example gaps or openings for the supply or removal of the working medium or liquid). The gaps or openings can, for example, be dimensioned or connected to other volumes in such a way that only a very small pressure loss is caused during a compression or expansion period and that the liquid flows out of the volume through these gaps or openings at a maximum of the predetermined partial amount or flows into the volume (the specified partial amount can be 5% or 10% or 15% of the amount of liquid in the volume). The direct contact of the working medium with the liquid can ensure that the working medium is very effectively thermally coupled to the liquid: quantities of heat do not first have to be transferred from the liquid to a heat exchanger wall and then transferred into the working medium or vice versa. The temperature change that occurs when the working medium is compressed or expanded can therefore be compensated for very quickly by the working medium giving off or absorbing heat energy to the liquid and thus being kept largely constant at a temperature that corresponds to that of the liquid. In other words, this means that compression or expansion of the working medium can occur largely isothermally. The liquid has a function as a “heat carrier” in that small amounts of it can escape from the volume through small openings in order to transport the resulting heat or cold out of the volume and to be able to use it outside the device or to transfer it to a heat reservoir. Likewise, liquid can enter the volume through another or the same opening in order to transport heat or cold into the volume and to replace the amount of liquid that has escaped. These openings, as well as other openings or gaps, are so small that the liquid can only flow through with considerable resistance and only very slowly, i.e As a result, the pressure in the volume only changes insignificantly and only very small flow losses (friction losses due to the flow of the liquid) occur.

For example, the device can be used for the largely isothermal compression of a gas in order to introduce it into a pressure vessel at excess pressure. Mechanical or electrical energy must be introduced into the device. The gas under excess pressure can then be used in the opposite direction from the pressure vessel to be largely isothermally expanded via the device. This releases mechanical or electrical energy that can be used for other purposes. Such a process can therefore be used as an energy storage device, in which the energy is stored in the form of the excess pressure of the gas in the pressure vessel. In contrast to the use of devices that compress the gas largely adiabatically, high efficiencies of such an energy storage device can be achieved with the device described here in such an application. In this embodiment, the gas can flow in and out of the device via pressure valves or openings that are open or closed depending on the position of the volume limiting elements.

Even when using the device described here to generate compressed air or to compress a gas or to generate a negative pressure or vacuum, high efficiencies can be achieved through the isothermal process control.

The device can include at least two of the volumes, each of which can include at least a partial volume of the working medium and amounts of liquid, wherein the at least two volumes can each be limited by the volume limiting elements, so that the amounts of liquid of different volumes cannot mix up to a maximum of the predetermined partial amount .

The specified subset can be 5% or 10% or 15%. The specified partial amount can be 5% or 10% or 15% of the amount of liquid in volume.

The volume limiting elements, which completely enclose the volume of the working medium and the liquid except for small gaps or openings or outlet/inlet openings, prevent, in contrast to conventional liquid ring pumps or in contrast to the device DE 10 2018 212 088 B3 , that the liquid is displaced or set into flow due to the changing pressure in the working medium, which means that energy would have to be applied, which would ultimately be converted into frictional heat through frictional losses in the flowing liquid and would therefore mean power loss.

At least a first volume limiting element of the volume limiting elements can perform a rotational movement in a housing that can include the at least one volume, wherein a rotation axis of the first volume limiting element can be different from a central axis of the housing and / or the at least one first volume limiting element of the volume limiting elements can perform a first rotational movement carry out and at least one second volume limiting element can carry out a second rotational movement, wherein a first axis of rotation of the first rotational movement and a second axis of rotation of the second rotational movement can be different from one another. The housing can be circular cylindrical or shaped differently.

A first volume limiting element of the volume limiting elements can carry out a rotational movement, wherein this first volume limiting element can comprise movable limiting elements which can periodically change their position relative to the first volume limiting element during the rotation of the first volume limiting element.

A first volume limiting element of the volume limiting elements can perform a movement, which can include a rotational movement about a first axis and a rotational movement about a second axis.

At least a first volume limiting element of the volume limiting elements can comprise a piston or hollow piston, which can carry out a rotational movement which can be superimposed by a periodic translational movement.

In addition to its function as a heat transfer medium, the liquid can also fulfill a sealing function by preventing the at least partially gaseous working medium from unintentionally escaping from the volume through gaps or openings. Gaps or openings are therefore preferably surrounded by the liquid and not by the working medium.

The function of the device to expand, compress, change the volume or displace the working medium is accomplished by the volume limiting elements shifting in position relative to the liquid (or the liquid relative to the volume limiting elements elements), so that the partial volume that contains the working medium changes (this partial volume is limited on the one hand by the volume limiting elements and on the other hand by the liquid). The working medium is continuously in contact with the liquid and correspondingly thermally coupled to it, so that the compression, expansion, volume change or displacement occurs largely isothermally.

In order to prevent the liquid from being dragged along by the volume limiting elements when moving relative to them and mixing with the working medium in large quantities or causing flow losses, the force that holds the liquid in its preferred position must be at least greater as the forces that would separate the fluid from its preferred position. In a device like in EP 2 657 497 B1 described, this force is the earth's gravity. In this case, the acceleration due to gravity must be at least greater than the maximum acceleration of the movement of the volume limiting elements relative to the liquid. In order to be able to operate the present invention at higher speeds (or working frequencies of the periodic movements) and thus higher maximum accelerations of the relative movement of the volume change elements relative to the liquid, the liquid is set into a rotational movement. In addition to the force of gravity, additional, significantly larger centrifugal forces act on the liquid, which keep it in its preferred position and prevent partial quantities of the liquid from being transported out by the movement of the volume limiting elements relative to the liquid, even at higher speeds of this relative movement.

At least one of the liquid quantities can move in the volume relative to other volume limiting elements caused by inertial forces or by movement of at least one of the volume limiting elements and thereby change a size of at least one of the partial volumes.

The device can further comprise heat transfer elements which periodically dip into and out of the liquid in the volume, wherein the heat transfer elements can comprise, for example, plates, grids and/or rods. The plates, nets, grids or bars can include metal, for example.

A further advantage of the device described here may be that the heat transfer between the working medium and the liquid occurs quickly and therefore effectively compared to devices in which the heat is transferred via a conventional heat exchanger. This is because the working medium can equalize its temperature with the liquid directly at the interface between the working medium and the liquid, and the corresponding transfer of heat quantities does not have to take place indirectly via the wall of a heat exchanger, in which quantities of heat are initially transferred from the working medium to the heat exchangers and in the second step from the heat exchanger to the liquid (or vice versa). This advantage can be enhanced by the heat transfer elements. During exchange into the liquid, they are thermally coupled to it and largely assume the temperature of the liquid. While they are pulled out of the liquid, they are then thermally coupled to the working medium and a temperature equalization takes place between them and the working medium. In this way, you increase the contact surface of the working medium with elements that have virtually the same temperature as the liquid, so that the transfer of heat quantities and thus the temperature equalization is accelerated. These heat transfer elements can additionally serve to reduce flows of liquid quantities within the volume, for example by arranging plates such that their surfaces are perpendicular to the flow direction they are intended to reduce. For example, plates can be arranged in the volumes in such a way that their surfaces are arranged largely perpendicular to the rotational movement of the amounts of liquid about their axis of rotation in order to reduce the back and forth fluctuation of the amounts of liquid within their respective volume.

A thermoelectric converter for converting quantities of heat into mechanical or electrical energy or for converting mechanical or electrical energy into heat/cold or for converting quantities of heat at first temperatures into quantities of heat at second temperatures comprises at least one device as described above or below.

With the thermoelectric converter, a thermodynamic cycle can be realized, for example a Stirling process, an Ericsson process, a Clausius-Rankine process or a Stirling process, in which, in addition to the compression and expansion or displacement of the working gas, condensation and / or Evaporation of a component of the working medium or liquid can take place.

Thermodynamic cycle processes in which a working medium undergoes a cyclical change of state (change in volume,... Pressure, temperature, state of aggregation, etc. in a certain sequence that is repeated cyclically) often have a high degree of efficiency if certain changes in state - for example compression or expansion processes - occur largely isothermally instead of adiabatic. Examples of such cycle processes are the Stirling process, the Vuilleumier process, the Ericsson process or the Clausius-Rankine process. Therefore, the device described here can be suitable for implementing such a process with high efficiency.

The circular cylindrical or differently shaped housing can be mounted so that it can rotate freely about the central axis of the housing.

A computer-controlled or electronically controlled method for operating a thermoelectric converter, as described above or below, is provided.

The volume change elements can be controlled in such a way that the working medium condenses at least partially during compression and evaporates during a subsequent expansion. The working medium can also completely condense during compression.

The thermoelectric converter can convert mechanical/electrical energy into amounts of heat at certain temperatures (function as a heat pump), or can convert amounts of heat at certain temperatures into electrical/mechanical energy (function as a heat engine), or can convert amounts of heat at certain temperatures into amounts of heat at certain other temperatures convert (function like a combination of heat pump with heat engine or like a Vuilleumier machine). By using the device, as described above or below, high efficiencies can be achieved, and the efficient use or generation of even small temperature differences is possible because of the good and direct coupling of the working medium to the liquid as a heat transfer medium or heat transport medium.

The function of such a process is explained below using the example of the Stirling process in the function of a heat pump. The working medium used in the process, here a gas, is largely isothermally compressed in a first volume in a first step. This releases quantities of heat into a first quantity of liquid, which consequently heats up.

In a second step, the working medium is displaced from the partial volume, which is located in the first volume together with this first amount of liquid. It flows through a (gas-tight) connection into a second volume that contains a second amount of liquid. During this flow into the second volume, the working medium largely assumes the temperature of the liquid and volume-limiting elements of the second volume by giving off amounts of heat to or absorbing them from the wall of the connection. This temperature adjustment of the working medium during the change from one volume to the other, which is important for achieving good efficiency, can be improved if a so-called regenerator is used in the connection, which has the largest possible surface area with which the working medium can interact during the flow through can be in contact (and thus in thermal coupling). As the working medium flows through the regenerator, it releases quantities of heat in one direction to the regenerator, which essentially stores it temporarily. When flowing through in the other direction, the working medium then absorbs quantities of heat from the regenerator. Consequently, a temperature gradient is formed in the regenerator along its length and the regenerator reaches a temperature on the sides adjacent to the two volumes that largely corresponds to the temperatures prevailing in the volumes.

In a third step, the working medium in the second volume is expanded largely isothermally. It absorbs amounts of heat from the liquid that is in the second volume and thus keeps its temperature largely constant at a level that largely corresponds to the temperature of the liquid in the second volume.

In a fourth step, the working medium is displaced from the second volume and flows back into the first volume via the same connection as in step two, whereby as it flows through the connection and through the possible regenerator it again largely assumes the temperature that in the first volume prevails.

The cycle then starts again from the beginning with the first step. For this function as a heat pump, mechanical energy must be applied in order to maintain this cycle and to supply appropriate amounts of heat to one liquid and to remove it from the other liquid. This can be done, for example, by an electric drive.

This cycle can also be carried out in the opposite direction, so that the Stirling process is used to create a heat engine. In this case, the expansion of the working medium takes place in a first Volume in contact with a first liquid, and the compression of the working medium takes place in a second volume in contact with a second liquid, the first liquid being warmer than the second.

If the method of the present invention is implemented in the form of the Stirling process, it can be an alpha, beta or gamma Stirling process. Different variants of process management are also possible when implemented in the form of another circular process such as the Ericsson process or the Clausius-Rankine process. In contrast to the Stirling process, in the Clausius-Rankine process a phase transition also takes place in the working medium (change of the aggregate state from gaseous to liquid and vice versa). In the present invention, mixed forms of the processes are also possible, for example a Stirling process in which part of the working medium evaporates or condenses during compression and expansion.

Short character description

• 1 eine 3D-Ansicht einer ersten Ausführungsform eines thermodynamischen Wandlers,
• 2 einen Längsschnitt der Vorrichtung der 1,
• 3 einen Querschnitt (Schnitt A-A) durch die erste Hauptkammer,
• 4 einen Querschnitt (Schnitt B-B) durch die zweite Hauptkammer,
• 5 eine 3D-Ansicht des ersten Rotors zusammen mit den Verbindungselementen,
• 6 eine alternative Ausführungsform des ersten Rotors mit zusätzlichen Wärmetauscherelementen,
• 7 eine zweite Ausführungsform eines thermodynamischen Wandlers,
• 8 einen ersten Querschnitt (Schnitt A-A) durch die erste Hauptkammer,
• 9 einen zweiten Querschnitt (Schnitt B-B) durch die erste Hauptkammer,
• 10 eine dreidimensionale Ansicht der Rotoren zusammen mit den gasdurchlässigen Verbindungselementen,
• 11 einen Längsschnitt durch eine dritte Ausführungsform eines thermodynamischen Wandlers,
• 12 einen ersten Querschnitt (Schnitt A-A) durch die erste Hauptkammer,
• 13 einen zweiten Querschnitt (Schnitt B-B) durch die zweite Hauptkammer,
• 14 einen Drehkolben einer alternativen Ausführungsform,
• 15 den Drehkolben der 14 in einer dreidimensionalen Ansicht,
• 16 eine weitere Ausführungsform eines thermodynamischen Wandlers und
• 17 eine dreidimensionale Ansicht der Hubkolben, Verdrängerkolben, der Verbindungselemente, des Exzenters und des Kugellagers.

The attached figures represent aspects and/or exemplary embodiments of the invention for better understanding and illustration. It shows:

• 1 a 3D view of a first embodiment of a thermodynamic converter,
• 2 a longitudinal section of the device 1 ,
• 3 a cross section (section AA) through the first main chamber,
• 4 a cross section (section BB) through the second main chamber,
• 5 a 3D view of the first rotor together with the connecting elements,
• 6 an alternative embodiment of the first rotor with additional heat exchanger elements,
• 7 a second embodiment of a thermodynamic converter,
• 8th a first cross section (section AA) through the first main chamber,
• 9 a second cross section (section BB) through the first main chamber,
• 10 a three-dimensional view of the rotors together with the gas-permeable connecting elements,
• 11 a longitudinal section through a third embodiment of a thermodynamic converter,
• 12 a first cross section (section AA) through the first main chamber,
• 13 a second cross section (section BB) through the second main chamber,
• 14 a rotary piston of an alternative embodiment,
• 15 the rotary piston of the 14 in a three-dimensional view,
• 16 another embodiment of a thermodynamic converter and
• 17 a three-dimensional view of the reciprocating pistons, displacer pistons, the connecting elements, the eccentric and the ball bearing.

Detailed character description

The 1 shows a 3D view of a first embodiment of a thermodynamic converter, which includes devices for compression, expansion, volume change and / or displacement of a fluid containing a gas. A housing 2 is mounted on a frame 1 and is freely rotatable via ball bearings (not shown). A first liquid can flow into the interior of the housing 2 or flow out again through a first inlet line 3 and a first outlet line 4. A motor 7, which is firmly connected to the frame 1, can drive rotors located inside the housing 2, referred to as the first and second rotors. Alternatively, the motor 7 can also be operated as a generator to convert mechanical energy from the rotation of the rotors into electrical energy.

The 2 shows a longitudinal section of the device 1 . The motor 7 is mechanically firmly connected to the first rotor 8 and the second rotor 9 via an axis 10. The axis 10 is rotatably mounted via two ball bearings 11, 12. The ball bearings 11, 12 are each held by a bearing block 13, 14, which is firmly connected to the frame 1.

A second liquid 16 can flow into the interior of the housing 2 or flow out again through a second inlet line 5 and a second outlet line 6. The bearing blocks 13, 14 also serve to accommodate the first and second inlet and outlet lines 3, 4, 5, 6 for the first and second liquid 15, 16. The two ball bearings 17, 18 are also shown in longitudinal section, above which the housing 2 is rotatably mounted, the axis of rotation of the rotors 8, 9 being parallel, but not congruent, with the axis of rotation of the housing 2. The rotors 8, 9 are therefore mounted eccentrically to the axis of rotation of the housing 2. The housing 2 is divided inside into six chambers 20, 21, 22, 23, 24, 25, each of which is rotationally symmetrical. In one In the inner chamber 20, which is also referred to as the first main chamber 20, is the first rotor 8, which is mounted eccentrically to the housing 2, and in the other inner chamber 21, which is also referred to as the second main chamber 21, is the second, which is mounted eccentrically to the housing 2 Rotor 9. The rotors 8, 9 are not connected to the housing 2 and can rotate within the chambers 20, 21.

Movable limiting elements are arranged in the first main chamber 20, two of which 41, 44 can be seen, and their function in the 3 is explained in more detail.

In the 2 Sections of gas-permeable connecting elements 57 can also be seen. The gas-permeable connecting elements 57 each connect a volume from the first main chamber 20 with a different volume from the second main chamber 21.

Via the first inlet line 3, the chamber 22 and first openings 80, the first liquid 15 can be continuously fed into the first main chamber 20 and thus into its volumes (see 3 ) and flow out again via second openings 81, the chamber 23 and the first drain line 4.

The second liquid 16 can flow into the second main chamber 21 via the second inlet line 5, the chamber 24 and third openings 83 and can flow out again via fourth openings 84, the chamber 25 and the second outlet line 6.

The rotors 8, 9 have a conical profile on the inside, so that liquid that gets into the interior of the rotors 8, 9 can flow away via narrow, external first and second gaps 85, 86.

The 3 shows a cross section (section AA) through the first main chamber 20, within which the first rotor 8 is located.

The first rotor 8 divides the first main chamber 20 into six volumes 31, 32, 33, 34, 35, 36, each of which is formed by a part of the housing 2 and the first rotor 8 and limiting elements 41, 42, 43 that are movable relative to the first rotor 8 , 44, 45, 46 are limited, which together form so-called volume limiting elements.

A volume can contain both the working medium (a gas, a gas mixture or a mixture of gas(es) with liquid mist) and a liquid and can be limited by the volume limiting elements except for gaps or openings for the inflow or outflow of the working medium or liquid . These gaps or openings can be sized or connected to other volumes in such a way that during a compression or expansion process only a very small pressure loss is caused by the liquid flowing out of the volume or flowing into the volume through these gaps or openings (< 10% of the amount of liquid in volume). The direct contact of the working medium with the liquid ensures that the working medium is thermally coupled to the liquid very effectively.

Within each volume 31-36 there is a partial volume 51, 52, 53, 54, 55, 56, which is filled with a working medium (e.g. air), as well as a part of the first liquid 15. The first liquid 15 is created by the centrifugal forces each accelerated outwards. The limiting elements 41-46 are guided by slots in the first rotor 8 and are freely movable radially therein. As soon as the first rotor 8 rotates at sufficient speed, the limiting elements 41-46 are pushed radially outwards by the centrifugal force until they reach the outer wall of the housing 2. In this way, they prevent the first liquid 15 from flowing from one volume (e.g. 31) into an adjacent volume (e.g. 32).

Alternatively, it is also conceivable to use springs or the like to press the limiting elements 41-46 against the housing 2 from the inside.

The 4 shows a cross section (section BB) through the second main chamber 21, within which the second rotor 9 is located.

The second rotor 9 in the second main chamber 21 is constructed identically to the first rotor 8. In comparison to the first rotor 8, the second rotor 9 is attached to the axis 10 and rotated by a certain angle.

The second rotor 9 divides the second main chamber 21 into six volumes 61, 62, 63, 64, 65, 66, each of which is formed by a part of the housing 2 and the second rotor 9 and limiting elements 47, 48, 49 movable relative to the second rotor 9 , 50, 60, 70 are limited, which together form so-called volume limiting elements.

Within each volume 61-66 there is a partial volume 71, 72, 73, 74, 75, 76, which is filled with a working medium (e.g. air), as well as a part of the second liquid 16. The second liquid 16 is created by the centrifugal forces each accelerated outwards. The limiting elements 47, 48, 49, 50, 60, 70 are guided by slots in the second rotor 9 and are freely movable radially therein. As soon as the second rotor 9 rotates at sufficient speed, the limits are tongue elements 47, 48, 49, 50, 60, 70 are pressed radially outwards by the centrifugal force until they reach the outer wall of the housing 2. In this way they prevent second liquid 16 from flowing from one volume (eg 61) into an adjacent volume (eg 62).

Alternatively, the use of springs or the like is also conceivable in order to press the limiting elements 47, 48, 49, 50, 60, 70 against the housing 2 from the inside.

Each volume (e.g. 31) from the first main chamber 20 is connected to each volume (e.g. 63) from the second main chamber 21 by means of one of the gas-permeable connecting elements 57, so that through the working medium from the partial volume (e.g. 51) of the first main chamber 20 in the partial volume (e.g. 73) of the second main chamber 21 continuously equalizes pressure. These connecting elements 57 can be filled with a regenerator material, e.g. steel wool or another material (preferably metal) that is gas-permeable and has a large surface area so that it can very quickly exchange quantities of heat with the fluid flowing past.

Based on 3 and 4 the implementation of the Stirling cycle process can be explained.

The four steps of the cycle will now be explained below using the two volumes 31 and 63 of the first main chamber 20 and the second main chamber 21, respectively. In the other volumes (32 with 64, 33 with 65, 34 with 66, 35 with 61, 36 with 62) the circular process runs analogously, but out of phase compared to volumes 31 and 63. This is therefore a sixfold process Alpha Stirling process.

In the in the 3 and 4 In the starting position shown, the working medium of the volumes 31 and 63 is largely in the partial volume 73; like in the 3 can be seen, the partial volume 51 is small in comparison to the partial volume 73. If the two rotors 8, 9 now continue to rotate clockwise (for example by 60 ° to the position of the volumes 32 and 64 shown), the sum of the partial volumes increases 51 and 73. The working medium is therefore expanded. It barely cools down because it can absorb heat energy primarily from the second liquid 16, to which most of the working medium adjoins - the expansion therefore takes place largely isothermally. When the rotors 8, 9 rotate further, the partial volume 73 is reduced and the partial volume 51 is increased. The working medium therefore flows from the partial volume 73 into the partial volume 51 through the connecting element 57 and through the regenerator located therein. It largely assumes the temperature of the first liquid 15 to which the side of the connecting element 57 and the regenerator facing the partial volume 51 was previously heated. Now the partial volume 51 is approximately at the in 3 shown position of the partial volume 54 and the partial volume 73 at the in 4 shown position of the partial volume 76 and the majority of the working medium is in partial volume 51. When the rotors 8, 9 rotate further clockwise, the sum of the partial volumes 51 and 73 is reduced and the working medium is compressed - again largely isothermally. In this case, quantities of heat are given off primarily to the first liquid 15, since the majority of the working medium is located in the volume 31 and is thermally coupled to the first liquid 15 there. When the rotors 8, 9 rotate further into the in 3 and 4 In the starting position shown, the partial volume 51 is reduced and the partial volume 73 is enlarged, so that the working medium flows again through the connecting element 57 and the regenerator into the partial volume 73 and thereby largely assumes the temperature of the second liquid 16.

In this process, the first liquid 15 is heated and the second liquid 16 is cooled. For the compression, mechanical energy must be used via the rotation of the rotors 8, 9, whereby the rotors are braked, and the expansion drives the rotors 8, 9 and thus accelerates them.

If the second liquid 16 is warmer than the first liquid 15, the rotors are accelerated more strongly by the expansion of the working medium than they are slowed down by the compression of the working medium. If this energy difference is greater than the mechanical friction in the system, including the flow losses of the liquids, the motor 7 can be driven and generate electrical energy.

If the first liquid 15 is warmer than the second liquid 16, the motor 7 must apply mechanical energy to drive the rotors 8, 9 - but this allows the first liquid 15 to be heated further and the second liquid 16 to be cooled further, so that the method how a heat pump works. Via the first inlet line 3, the chamber 22 and the openings 80 (see 2 ) first liquid 15 can flow continuously into the first main chamber 20 and thus into the volumes 31-36 and flow out again via the openings 81, the chamber 23 and the first drain line 4. Liquid rings form in the chambers 22 and 23. Likewise, the second liquid 16 can flow into the second main chamber 21 via the second inlet line 5, the chamber 24 and the openings 83 and flow out again via the openings 84, the chamber 25 and the second outlet line 6, here in the chamber form 24 and 25 liquid rings. The first and second liquids 15, 16 can thus be coupled to external heat reservoirs or useful heat and cold can be removed from the system or drive heat and drive cold can be added to the system. The height of the liquid rings in the chambers 23 and 25 is controlled via the length of the first and second drain lines 4, 6 and thus also the height of the rotating amounts of liquid in the volumes 31-36 of the first main chamber 20 and the volumes 61-66 of the second Main chamber 21. Since the rotors 8, 9 have a conical profile on the inside, liquid that gets into the interior of the rotors 8, 9 can flow out through the narrow, outer gaps 85, 86. The housing 2 is rotatably mounted via the ball bearings 17, 18 so that it can rotate during operation. Thus, the movement of the housing 2 relative to the rotors 8, 9, to the first and second liquids 15, 16 and to the movable limiting elements 41-46, 47, 48, 49, 50, 60, 70 is minimized and friction losses are accordingly minimized .

The 5 shows a three-dimensional oblique view of the first rotor 8 together with the connecting elements 57, which connect the partial volumes 51-56 of the first main chamber 20 with the partial volumes 71, 72, 73, 74, 75, 76 of the second main chamber and can contain a regenerator material. The movable limiting elements 41-46 of the first rotor 8 can also be seen. The connecting elements 57 can be provided in such a way that the following assignment of the partial volumes is achieved: 51 with 73, 52 with 74, 53 with 75, 54 with 76, 55 with 71, 56 with 72.

The 6 shows an alternative embodiment of the first rotor 8, which has the same elements as in the 5 includes and in which additional heat exchanger elements 90 are provided, which are immersed at different depths in the first liquid 15 during the rotation of the first rotor 8, ie there are areas of them which are located inside the first liquid 15 at certain times and outside at other times the first liquid 15 and thus within the working medium in one of the partial volumes 51-56. While the heat exchanger elements 90 are immersed in the first liquid 15, they are thermally coupled to it and can largely assume the temperature of the first liquid 15. While the heat exchanger elements 90 are not immersed in the first liquid 15, they are thermally coupled to the working medium and can largely transfer their temperature to it. These additional heat exchanger elements 90 thus contribute to improving or accelerating the exchange of heat quantities between the working medium and the first liquid 15.

The 7 shows a longitudinal section of a second embodiment of a thermodynamic converter, which includes devices for compression, expansion, volume change and / or displacement of a fluid containing a gas.

A housing 102 is mounted on a frame 101 and is freely rotatable and mounted concentrically to the axis 110 via ball bearings 111, 112. A motor 107, which is firmly connected to the frame 101, can drive the housing 102 and rotors 108, 109 located inside the housing 102, referred to as the first and second rotors 108, 109. Alternatively, the motor 107 can also be operated as a generator in order to convert mechanical energy from the rotation of the rotors 108, 109 into electrical energy.

The axis 110 is fixed and non-rotatably connected to the frame 101. Two eccentrics 193, 194 are firmly mounted on this axis 110, which ensure that the ball bearings 197, 198 have a position that is eccentric to the axis 110. The two rotors 108, 109 are rotatably mounted via these two ball bearings 197, 198, so that they can carry out a rotational movement eccentrically to the axis 110 and thus also eccentrically to the housing 102.

The rotors 108, 109 are mechanically coupled to the housing 102 via gears 200, 202, which are firmly connected to the rotors 108, 109, and via internal gears 201, 203, which are firmly connected to the housing 102, in such a way that the rotation speeds of the Rotors 108, 109 are in a fixed relationship to the rotation speed of the housing 102.

The axis of rotation 218 of the motor 107 is firmly connected to the housing 102 and can cause it to rotate or absorb rotational energy from it in order to convert it into electrical energy. The rotational movement of the rotation axis 218 of the motor 107 is also indirectly coupled to the rotational movement of the rotors 108, 109 via the gears 200, 202 and the internal gears 201, 203.

A first liquid 115 can flow into or out of the interior of the housing 102 through a first inlet line 103 and a first outlet line 104. A second liquid 116 can flow into or out of the interior of the housing 102 through a second inlet line 105 and a second outlet line 106.

The housing 102 is divided inside into six chambers 120, 121, 122, 123, 124, 125, each of which is rotationally symmetrical. In one inner chamber 120, which is also referred to as the first main chamber 120, there is the first rotor 108, which is mounted eccentrically to the housing 102, and in the other inner chamber 121, which is also referred to as the second main chamber 121, it is located eccentrically to the housing 102 mounted second rotor 109. The rotors 108, 109 are not connected to the housing 102 and can rotate within the chambers 120, 121.

In the 7 Sections of gas-permeable connecting elements 157 can also be seen. The gas-permeable connecting elements 157 each connect a volume from the first main chamber 120 with a different volume from the second main chamber 121. Two volumes 131, 135 of the total of six volumes and two partial volumes 151, 155 of the first main chamber 120 and two volumes 161, 165 the second main chamber 121 are shown.

In this second embodiment, the first liquid 115 flows through the device through the inlet line 104 into the chamber 122 and from there via a first line 206 into a chamber 208 of the first main chamber 120. From there it passes through a gap with a certain flow resistance 212 into the volumes of the first main chamber 120 (see 8th ), where it is heated or cooled during operation. The first liquid 115 can leave the volumes of the first main chamber 120 again via a gap 214 and enters the chamber 210, then through an opening 216 into the chamber 123, in which it forms a liquid ring. From there it can leave the device again via the first drain line 104, the first drain line 104 with its length in the radial direction defining the height up to which the water ring forms in the chambers 123 and 210, to which the fill levels of the first Adjust liquid 115 in the volumes of the first main chamber 120.

In the same way, the second liquid 116 flows through the device via the second inlet line 105, the chamber 124, a second line 207, a chamber 209 of the second main chamber 121. From there, the second liquid 116 passes through a gap 213 with a certain flow resistance the volumes of the second main chamber 121. The second liquid 216 can leave the volumes of the second main chamber 121 again via a gap 215 and enters the chamber 211, then through openings 217 into the chamber 125 and leaves the device through the second drain line 106.

The 8th shows a first cross section (section AA) through the first main chamber 120. The volumes 131, 132, 133, 134, 135, 136, in which the partial volumes 151, 152, 153, 154, 155, 156 containing the working medium are located formed by the first rotor 108 and the outer limiting element 191 as volume limiting elements. The outer limiting element 191 is firmly connected to the housing 102 and is located together with the first rotor 108 in the first main chamber 120. The cross section of the first line 206 can be seen.

The outer limiting element 191 is shaped in such a way that the elements projecting outwards in a star shape from the first rotor 108 together with the limiting element 191 always only form a very fine gap 205, through which only very small amounts of the first liquid 115 can flow per unit of time and so during During operation only a very small amount of fluid exchange or pressure equalization can take place between adjacent volumes (e.g. 131 and 132).

The 9 shows a second cross section (section BB) through the first main chamber 120. It can be seen how the gear 200, which is firmly connected to the first rotor 108, and the internal gear 201, which is firmly connected to the housing 102, mesh with one another , whereby the first rotor 108 is mechanically coupled to the housing 102 such that the rotational speed of the first rotor 108 is in a fixed relationship to the rotational speed of the housing 102.

The 10 shows a three-dimensional view of the rotors 108, 109 together with the gas-permeable connecting elements 157, via which the working medium can flow from the partial volumes 151, 152, 153, 154, 155, 156 of the first rotor 108 into one of the partial volumes of the second rotor 109 and vice versa. The working medium can change its temperature via the wall of the connecting elements 157 or additionally via a regenerator located in the connecting element 157. Also shown are the gear 200, which is firmly connected to the first rotor 108, and the gear 202, which is firmly connected to the second rotor 109. The rotors 108, 109 each have circular volume limiting elements on both sides perpendicular to their axis of rotation, which prevent the working medium from escaping laterally.

A third embodiment of a device for compressing, expanding, changing volume and / or displacing a fluid containing a gas is in the 11 , 12 and 13 shown.

The 11 shows a longitudinal section through a third embodiment of a thermodynamic converter, which includes devices for compression, expansion, volume change and / or displacement of a fluid containing a gas.

The eight volumes filled with working medium and the first liquid 315 (two of which, namely 331a, 331e, can be seen in the illustration) are located here in the first main chamber 320a and the second main chamber 320b of the housing 302. The one with working medium and the second Eight volumes filled with liquid 316 (two of which, namely 371a, 371e, can be seen in the illustration) are located here in the third main chamber 321a and the fourth main chamber 321b of the housing 302.

The eccentrics 393, 394 are firmly connected to the fixed axis 310, which is firmly connected to the frame 301.

The ball bearing 397 is attached to the eccentric 393, which limits the position of eight pistons (two of which, namely 308a, 308e, can be seen in the illustration) in the first main chamber 320a by preventing them from moving further inwards through contact To move inside the device. The ball bearing 398 is attached to the eccentric 394, which limits the position of six pistons (two of which, namely 309a, 309e, can be seen in the illustration) in the third main chamber 321a by preventing them from moving further inwards by contact To move inside the device.

Since all of the sixteen pistons (308a, 308e, 309a, 309e) have a lower density than the first or second liquid 315, 316, they “float” on the corresponding liquid 315, 316, so that they generally always have the same density touch the corresponding ball bearings 397, 398. The axis of rotation 318 of the motor 307 is firmly connected to the rotatably mounted housing 302 and can set it in rotation or brake it.

The first main chamber 320a also includes eight cylinders (two of which, namely 391a, 391e, can be seen in the illustration). The third main chamber 321a also includes eight cylinders (two of which, namely 392a, 392e, can be seen in the illustration).

The first liquid 315 can be discharged into the first and second main chambers 320a, 320b through a first feed line 303 and out of it through a first drain line 304.

The second liquid 316 can be discharged into the third and fourth main chambers 321a, 321b through a second feed line 305 and out of it through a second drain line 306.

The eight volumes 331a, 331e of the second main chamber 320b can each be connected to the six volumes 371a, 371e of the fourth main chamber 321b by means of gas-permeable connecting elements 357.

The 12 shows a cross section (section AA) through the first main chamber 320a, which includes the volumes 331a, 331b, 331c, 331d, 331e, 331f, 331g, 331h with working medium and first liquid 315.

The first eccentric 393, on which the ball bearing 397 is attached, is firmly connected to the axis 310. The ball bearing 397 limits the position of the pistons 308a, 308b, 308c, 308d, 308e, 308f, 308g, 308h by preventing them from moving further into the interior of the machine through contact.

If the housing 302 rotates, then the cylinders 391a, 391b, 391c, 391d, 391e, 391f, 391g, 391h also rotate because they are firmly connected to the housing 302. In the cylinders 391a-391h, the pistons 308a-308h can move freely in the radial direction and their position is defined by the ball bearing 397 attached to the eccentric 393. During a complete rotation of the housing 302 through 360°, the pistons 308a-308h therefore, in addition to their rotational movement about the rotation axis 310 of the housing 302, also each carry out a period of oscillating movement in the radial direction. Together with the housing 302 and the cylinders 391a-391h, the pistons 308a-308h form the volume limiting elements of the volumes 331a-331h, which contain the working medium and the first liquid 315, respectively.

If the piston (eg 308a) in a volume (eg 331a) is pushed radially outwards by the rotation of the housing 302, it displaces the liquid (eg 315) in the volume (eg 331a) in the direction of the main chamber located further inside (eg 320b), so that it displaces the working medium adjacent to it from the volume (eg 331a) into the volume (eg 371a) connected to it via the connecting element 357 and/or compresses the working medium. The connecting element 357 may contain a regenerator material. If the two eccentrics 393, 394, due to their position, cause a suitable phase shift between the two pistons (eg 308a and 309a), which limit the two volumes, which are each connected to one another via a connecting element 357, an alpha can be achieved again with this embodiment -Stirling District Pro process when used as a heat pump or as a heat engine.

The first liquid 315 passes through the machine through the first inlet line 303, through the chamber 322, through the openings 380, through the volumes 331a-331h, driven by the excess pressure in the volumes 331a-331h through the gaps between the pistons 308a-308h and the cylinders 391a-391h, through the interior 399 of the main chamber 320a, through the openings 381, through the chamber 323 and through the first drain line 304. The second liquid 316 flows analogously through the device.

The 13 shows a cross section (section BB) through the second main chamber 320b, which includes the volumes 331a-331h with working medium and first liquid 315. In addition, parts of the housing 302 are shown, in which the volumes 331a-331h are arranged.

In the 13 Sections of gas-permeable connecting elements 357 can also be seen, each of which connects a volume 331a-331h from the first and second main chambers 320a, 320b with a volume from the third and fourth main chambers 321a, 321b. For example, the volumes 331a and 371a may be connected by a connecting element 357.

Like in the 14 shown, in an alternative embodiment those in the 11 Elements provided in the first main chamber 320a and the third main chamber 321a, which have the function of periodically displacing the first and second liquids 315, 316 in and out towards the second main chamber 320b and the fourth main chamber 321b, are replaced by a rotary piston 408. The rotary piston 408 rotates about an axis of rotation that passes through the center of the ball bearing 497, via which it is rotatably mounted. The axis of rotation of the rotary piston 408 is eccentric to the axis of rotation of the housing 402, which corresponds to the position of the fixed axis 410. The position of the two axes of rotation relative to one another is defined by the eccentric 493, on which the rotary piston 408 is rotatably mounted via the ball bearing 497. The gear 700 integrated into the rotary piston 408 and the internal gear 701, which is firmly connected to the housing 402, are analogous to the second embodiment from the 7 ensures that the rotation speeds of these two rotations of the housing 402 and the rotary piston 408 have a constant ratio to one another. In this way, it can be ensured that the rotary piston 408 causes the periodic displacement of the first liquid 415 described above, with the gaps between the sealing elements 402a, which are firmly connected to the housing 402, and the rotary piston 408 always remaining very small. Using additional sealing strips that are movably attached to the tips of the sealing elements 402a and are pressed against the rotary piston 408 by means of springs or similar force-causing elements, the gap width between the sealing elements 402a and the rotary piston 408 can be further reduced and the sealing effect improved accordingly.

The 15 shows the rotary piston 408 with the internal gear 700 in a three-dimensional view.

The 16 and 17 show a further embodiment of a thermodynamic converter that includes devices for compression, expansion, volume change and / or displacement of a fluid containing a gas. In contrast to those in the 1 until 15 In the embodiments shown, this further embodiment realizes a Stirling process in the variant as a beta Stirling process.

Those in the cross section of the 16 Embodiment shown contains an axle 510 which is firmly connected to an external, fixed frame and is not rotatable. An eccentric 593 is firmly connected to the axis 510, so that it is also stationary. A ball bearing 597 sits on the eccentric 593 and limits the movement of hollow pistons 508a, 508b, 509a, 509b and compressor pistons 510a, 510b radially inwards. The hollow pistons 508a, 508b, 509a, 509b have the function of a “displacer piston” and the compressor pistons 510a, 510b have the function of a “working piston”, which are the terms commonly used in Beta Stirling engines.

In this further embodiment, the axis of rotation of a motor is firmly connected to the rotatably mounted housing 502 and can accelerate or decelerate its rotational movement. The axis of rotation of the housing 502 corresponds to the position of the fixed axis 510. The compressor pistons 510a, 510b have a lower density than the liquids 515a, 515b, 516a, 516b contained in the housing 502, which are pressed radially outwards by the centrifugal force when the housing 502 rotates become. Therefore, the compressor pistons 510a, 510b “float” on the liquid 515a, 515b and are displaced radially inwards by it until this movement is limited by the ball bearing 597 mounted on the eccentric 593. The radially opposite hollow pistons 508a, 508b, 509a, 509b are connected via gas-permeable connecting elements (see 17 ) connected to each other, so that each hollow piston, which is pressed radially outwards by the ball bearing 597, pulls the hollow piston opposite it inwards.

The volumes 531, 532, 561, 562 are limited by the following volume limiting elements: the housing 502, which forms six cylinders in the radial inward direction, and the hollow pistons 508a, 508b, 509a, 509b and displacer pistons 510a, 510b movably arranged in the cylinders . Within this Volumina 531, 532, 561, 562 there are also the partial volumes 551, 571 filled with the working medium, which are from the liquids 515a, 515b, 516a, 516b, the hollow pistons 508a, 509a, 509b, the compressor piston 510a, 510b and the connecting elements.

The partial volumes 551, 571 filled with the working medium are connected to one another with two gas-permeable connecting elements, wherein the connecting elements can contain a regenerator material. Due to the movement of the hollow pistons 508a, 509a caused by the rotation of the housing, the partial volumes 551, 571 are alternately reduced and enlarged, with a partial volume (e.g. 551) being particularly small if the partial volume radially opposite it (e.g. 571) is particularly large and vice versa. Depending on the direction of rotation of the housing 502, the partial volume 551 forms the expansion space of a beta Stirling process and the partial volume 571 forms the compression space (or vice versa). The working medium is alternately moved back and forth between the two partial volumes 551, 571, flowing through the connecting elements. Within the partial volumes 551, 571, the working medium is thermally coupled to one of the liquids 515a, 516b and can absorb quantities of heat from them or release them to them. While flowing through the connecting elements, it can be heated or cooled in such a way that when it enters the partial volumes 551, 571 it has already largely assumed their temperature.

The displacer piston 510a also carries out a periodic movement in the radial direction. In doing so, it displaces the liquid 515a in such a way that the partial volume 551 is reduced or increased. This changes the pressure in the partial volumes 551, 571, causing the compression and expansion of the working gas and consequently its temperature change. However, this temperature change only occurs to a small extent, since the partial volumes 551, 571 are thermally coupled to the liquids 515a and 516a and can give off amounts of heat to them or can absorb them from them and thus continuously adapt their temperature to that of the liquids 515a and 516a . By positioning the displacer piston 510a, the phase shift of its radial, sinusoidal movement can be defined in comparison to the radial, sinusoidal movement of the reciprocating pistons 508a and 508b. In the case shown, the phase shift between the displacer piston 510a and the hollow piston 509a is 60°. In a further preferred embodiment, this phase shift is 90°, whereby the displacer pistons 510a, 510b do not have to lie in the same plane perpendicular to the axis (510) as the reciprocating pistons 508a, 508b, 509a, 509b. The partial volumes 552, 572 form a beta Stirling process in an analogous manner, the pressure change in this case being caused by the radial movement of the displacer piston 510b.

The 17 shows a three-dimensional view of the reciprocating pistons 508a, 508b, 509a, 509b, the displacer pistons 510a, 510b, the connecting elements 557a, 557b, the eccentric 593 and the ball bearing 597.

This arrangement allows in the 16 For example, the radially opposite hollow pistons 508a, 509a can be connected to one another via the gas-permeable connecting element 557b and the radially opposite hollow pistons 508b, 509b can be connected to one another via the gas-permeable connecting element 557a. Thus, for example, the partial volumes 551, 571 filled with the working medium are connected to one another by the gas-permeable connecting element 557b.

Further embodiments are possible, in which the expansion and compression of a working medium are caused by a rotating quantity of liquid set into oscillation by inertial forces. For example, a quantity of liquid can be caused to oscillate by varying centrifugal forces through a periodically fluctuating rotational speed. It is also possible to superimpose a further periodic movement on the rotation speed, e.g. a rotation about another axis, whereby a rotating amount of liquid is set into an oscillatory movement.

A further embodiment is given in that in the 7 until 10 In the embodiments shown, the fixed axis (eg 110) is replaced by an axis rotating at a certain speed. In this way it can be achieved that the rotation of the housing (eg 102) is higher compared to the frequency of the realized Stirling process than in the 7 until 10 illustrated embodiments. In this way, the centrifugal force that presses the quantities of liquid from the inside against the outer wall of the housing (eg 102) can be further increased without simultaneously increasing the frequency of the Stirling process. This is analogous to the embodiment from the 11 until 13 , from the embodiment from the 14 and 15 or at the Embodiment from the 16 and 17 possible.

In addition to the preferred embodiments of a Stirling process mentioned here, which can be operated in the function of a heat pump or heat engine, a preferred embodiment also consists of mechanically coupling one of these embodiments, which works as a heat engine, with another embodiment, which acts as a Heat pump is working. This means that useful heat and/or cold can be generated by using a temperature difference between two different heat reservoirs (e.g. ambient heat or waste heat from an industrial process and a suitable heat sink). This is desirable with the present invention, since it also allows the use of small temperature differences in such an application through the effective coupling of the working medium to the liquid as a heat transfer medium and thus also makes use of waste heat or ambient heat that has only small temperature differences to an existing heat sink .

QUOTES INCLUDED IN THE DESCRIPTION

This list of documents listed by the applicant was generated automatically and is included solely for the better information of the reader. The list is not part of the German patent or utility model application. The DPMA assumes no liability for any errors or omissions.

Cited patent literature

• EP 2657497 B1 [0005, 0030]
• DE 102018212088 B3 [0006, 0023]

Claims (15)

Device for compression, expansion, volume change, displacement of a fluid working medium which consists at least partially of gas, the device comprising: - at least one volume that includes a liquid quantity of a liquid (15, 16, 115, 116, 315, 316, 415, 515a, 515b, 516a, 516b, 615, 616a, 616b) and a partial volume with a working medium, - Volume limiting elements (2, 8, 9, 41, 42, 43, 44, 45, 46, 50, 60, 70, 102, 108, 109, 191, 192, 302, 391a-391e, 392a-392e, 308a-308e , 309a-309e, 402, 408, 502, 508a, 508b, 509a, 509b, 510a, 510b), which limit the volume and which are designed such that one or more passages allow flow out during a compression, expansion or displacement period of a maximum of a predetermined subset of the amount of liquid, the amount of liquid rotating about a rotation axis (10, 110, 310, 410, 510) during the compression, expansion or displacement period, wherein the volume limiting elements are also designed to prevent an annular flow of the amount of liquid around the axis of rotation (10, 110, 310, 410, 510), wherein during the compression, expansion or displacement period the volume can be changed in its overall size by displacing at least one of the volume limiting elements. Device according to Claim 1 , wherein the device comprises at least two of the volumes, each of which comprises at least a partial volume of the working medium and quantities of liquid, wherein the at least two volumes are each limited by the volume limiting elements, so that the liquid quantities of different volumes do not mix up to a maximum of the predetermined partial quantity. Device according to Claim 1 or 2 , where the specified subset is 5% or 10% or 15%. Device according to one of the Claims 1 until 3 , wherein at least a first volume limiting element of the volume limiting elements: - carries out a rotational movement in a housing (2, 102, 302, 402, 502, 602) which comprises the at least one volume, wherein an axis of rotation of the first volume limiting element is different from a central axis of the housing and/or - carries out a first rotational movement and at least one second volume limiting element carries out a second rotational movement, wherein a first axis of rotation of the first rotational movement and a second axis of rotation of the second rotational movement are different from one another. Device according to one of the Claims 1 until 4 , wherein a first volume limiting element of the volume limiting elements, which carries out a rotational movement, comprises movable limiting elements which periodically change their position relative to the first volume limiting element during the rotation of the first volume limiting element. Device according to one of the Claims 1 until 5 , wherein a first volume limiting element of the volume limiting elements performs a movement that includes a rotational movement about a first axis and a rotational movement about a second axis. Device according to one of the Claims 1 until 6 , wherein a first volume limiting element of the volume limiting elements executes a rotational movement, the rotational speed of which is in a constant relationship to the rotational movement of a housing. Device according to one of the Claims 1 until 3 , wherein at least a first volume limiting element of the volume limiting elements comprises a piston or hollow piston (508a, 508b, 509a, 509b) which carries out a rotational movement which is superimposed by a periodic translational movement. Device according to one of the Claims 1 until 3 , wherein at least one of the quantities of liquid moves caused by inertial forces or by movement of at least one of the volume limiting elements in the volume relative to other of the volume limiting elements and thereby changes a size of at least one of the partial volumes. Device according to one of the Claims 1 until 9 , further comprising heat transfer elements which periodically dip into and out of the liquid quantity in the volume, the heat transfer elements comprising, for example, plates, grids and/or rods. Thermoelectric converter for converting quantities of heat into mechanical or electrical energy or for converting mechanical or electrical energy into heat/cold or for converting quantities of heat at first temperatures into quantities of heat at second temperatures temperatures, the at least one device according to one of the Claims 1 until 10 includes. Thermoelectric converter according to Claim 11 , thereby realizing a thermodynamic cycle, for example a Stirling process, an Ericsson process, a Clausius-Rankine process or a Stirling process, in which, in addition to the compression and expansion or displacement of the working gas, a condensation and / or evaporation of a Part of the working medium or liquid takes place. Thermoelectric converter according to Claim 11 or 12 , which has at least one device according to one of the Claims 4 until 10 includes, wherein the housing is freely rotatable about the central axis of the housing. Computer-controlled or electronically controlled method for operating a thermoelectric converter according to one of Claims 11 until 13 . The computer-controlled or electronically controlled process Claim 14 , where the volume change elements (2, 8, 9, 40, 41, 42, 43, 44, 45, 46, 50, 60, 70, 102, 108, 109, 191, 192,, 302, 391a-391e, 392a- 392e, 308a-308e, 309a-309e, 402, 408, 502, 508a, 508b, 509a, 509b, 510a, 510b) is controlled in such a way that during compression of the working medium it at least partially condenses and evaporates during a subsequent expansion.

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