Thermoelectric or thermo-mechanical converter

Abstract

The invention relates to a thermoelectric or thermomechanical transducer comprising at least two volumes (381-384, 386, 481-483) whose size can be changed and which are limited by volume limiting elements (201, 221-224, 321, 401, 414-416) that, for example, include openings (271-278) for the inflow and outflow of liquid quantities, which are interconnected in a gas-permeable manner, which contain a working medium that is at least partially gaseous, and which can each be changed in size by volume changing elements (235-238, 335, 435), wherein at least one of the volume changing elements (235-238, 335, 435) changes the size of at least one of the volumes (381-384, 386, 481-483) such that its size on average during the operating size of the device is less than the mean of its maximum size and its minimum size for more than half the time, for example, for more than 60% of the time.

Description

[0001] The invention relates to a thermoelectric or thermomechanical converter according to the preamble of the independent claim. State of the art

[0002] For the efficient conversion of mechanical / electrical energy into usable heat, heat pumps, which utilize thermodynamic cycles, are primarily used today, but other methods, such as adsorption or absorption processes, are also employed. Similarly, heat engines, which utilize thermodynamic cycles, are primarily used for the efficient conversion of heat into mechanical / electrical energy. Some thermodynamic cycles involve a phase transition of a working fluid, such as the Clausius-Rankine cycle. Processes without a phase transition include the Ericsson cycle and the Stirling cycle.

[0003] The efficiency of a thermodynamic cycle can be described as the product of the process efficiency and the theoretically maximum achievable Carnot efficiency. The Stirling and Vuilleumier cycles can theoretically achieve very high efficiencies, which are theoretically higher than those of other processes, especially at large temperature differences between the useful / drive heat and the corresponding heat / cold sink. This means that the efficiency of Stirling and Ericsson engines drops less sharply at higher temperature differences (compared to lower temperature differences) than is the case with other processes. Therefore, they are particularly suitable for high-temperature heat pumps or for heat engines that have heat sources with particularly high temperatures or particularly large temperature differences compared to the heat sinks.Furthermore, they are suitable for the use or generation of heat quantities in a wide range of absolute temperatures, as they do not depend on any phase transition temperature of a working medium.

[0004] However, gas cycles without phase transitions, such as Stirling engines, can have some disadvantages that can lead to a significantly lower actual efficiency than the Carnot efficiency, i.e., a quality factor significantly lower than 1. One of these disadvantages is the existence of dead volumes in such engines. For example, in a Stirling engine, the working gas may not be entirely within its designated expansion or compression volumes during expansion or compression, or the working gas may even be in the compression volume during expansion and in the expansion volume during compression. This can result in so-called "dead volume losses," sometimes also referred to as "waste volume losses."

[0005] Concepts for minimizing these dead space losses are already known. For example, dead space losses can be reduced by arranging the heat exchangers within the working chambers, thus avoiding additional volumes where a portion of the working fluid is constantly present, as is the case with heat exchangers located outside the working chambers, as disclosed in EP23209033.2. Furthermore, a non-sinusoidal, i.e., anharmonic or discontinuous, motion of a displacer piston, such as that used in Stirling engines of the beta or gamma type or Vuilleumier engines, ensures that the working fluid is almost completely displaced from the other working chamber not intended for compression or expansion during its compression or expansion in the compression or expansion chamber. This is described in WO2010 / 139443A1.However, dead spaces still remain, for example in Stirling engines of the beta or gamma type in the space whose volume is changed by the working piston: In a gamma Stirling engine, this volume is not assigned to either the compression or expansion chamber, while in a beta Stirling engine, this volume is assigned to one of these working chambers. Since the working fluid should be entirely in the compression chamber during the compression phase and in the expansion chamber during the expansion phase, the working fluid in the volume changed by the working piston is, at least temporarily, not entirely in the working chamber (compression chamber or expansion chamber) that would be correct to avoid dead space losses.

[0006] Stirling engines of the beta or gamma type are characterized by a displacer piston that moves the working fluid back and forth between the expansion and compression chambers without changing the total volume of the working fluid in the working and dead spaces. In the beta and gamma designs, the change in total volume is achieved by an additional working piston, which, as described above, always results in dead spaces. Other volume-changing elements, such as diaphragms, are also used instead of pistons. In Stirling engines of the alpha type, the compression chamber is bounded and its volume changed by one piston, and the expansion chamber by another piston (again, other volume-changing elements are used instead of pistons in the alpha design). Typically, the two pistons perform a sinusoidal or near-sinusoidal motion over time.A change in the total volume, and thus compression or expansion, is achieved because the movement of the pistons exhibits a certain phase shift. During compression or expansion, the working fluid is at least partially located in the other, unintended working space, which is why dead space losses also occur here. Task

[0007] The object of the invention is to provide a thermoelectric or thermomechanical converter in which a working medium undergoes a thermodynamic cycle (for example, according to the Stirling cycle), whereby dead space losses can be reduced and an increase in efficiency can be achieved. Solution

[0008] The problem is solved by the thermoelectric or thermomechanical converter according to the independent claim. Further embodiments are disclosed in the dependent claims.

[0009] This invention relates to a thermoelectric or thermomechanical converter in which a working medium, which may contain a gas, undergoes a thermodynamic cycle, being alternately compressed and expanded in so-called working chambers. For example, this cycle can be a Stirling cycle, in which, 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 and from liquid to gaseous can also occur. Compared to the prior art, the thermoelectric or thermomechanical converter can exhibit a higher efficiency because dead space losses can be avoided.

[0010] The working chambers (expansion and compression chambers) can contain all or part of a liquid that can act as a heat transfer medium in direct contact with the working medium in the compression or expansion chamber (analogous to patent application EP23209033.2). The thermoelectric or thermomechanical converter can therefore also be used as a heat engine operating with very small temperature differences, or as a highly efficient heat pump generating relatively small temperature differences. This is because, in such an embodiment, very good heat transfer occurs between the working medium and the liquid, allowing significant amounts of heat to be transferred even with very small temperature differences.

[0011] The thermoelectric or thermomechanical transducer comprises at least two volumes containing a working medium or each containing a partial volume filled with working medium, wherein, for example, the working medium comprises at least some gas. The partial volumes containing the working medium are referred to as working spaces because of the expansion or compression of the working medium that takes place within them. The volumes are delimited by volume limiting elements and may be connected to each other by a gas-permeable connection, which may be temporarily interrupted, for example, by a valve or a controllable or adjustable shut-off device. The volume limiting elements may, for example, include openings for the inflow and outflow of liquid quantities in order to transfer quantities of heat into or out of the volumes.The thermoelectric or thermomechanical transducer further comprises at least one volume-changing element configured to change the volume of one of the two working spaces. At least one of the volume-changing elements is configured to perform a movement such that the time intervals in which the volume it encloses is smaller than the average of the maximum and minimum volumes are longer (for example, at least 1.2 times longer) than the time intervals in which the volume it encloses is larger than the average of the maximum and minimum volumes.Accordingly, on average (for example, in a long-term average), for example over a period longer than two, three, four, or more periods, this volume is also smaller than the mean of the maximum volume and the minimum volume for a longer period, and larger than the mean of the maximum volume and the minimum volume for a shorter period (for example, the volume is smaller than the mean at least 60% of the time).

[0012] For example, the at least two working spaces filled with a working medium and connected to each other by gas are each bounded by volume limiting elements and a volume change element, both of which are designed to perform a movement such that the time periods in which the volume bounded by them is smaller than the mean of the maximum volume and the minimum volume are longer (for example, at least 1.2 times as long) than the time periods in which the volume bounded by them is larger than the mean of the maximum volume and the minimum volume.

[0013] The combined size of at least two volumes can, on average, be at least the mean of their maximum and minimum sizes more than half the time, for example, more than 60% of the time.

[0014] At least one or two volume change elements can change the size of at least two volumes such that their sizes are, on average, less than the mean of their maximum and minimum sizes for more than half the time, for example, for more than 60% of the time.

[0015] The at least one volume change element can separate areas that are not connected to each other in a gas-permeable manner. One of these areas can be one of the at least two volumes, and the other volume can be an area that does not form such a volume or does not contain a working space. Alternatively, both areas can be volumes that are also working spaces or contain working spaces.

[0016] Two of the volumes can form a completely gas-tight sealed volume. This means that a gas-tight sealed volume can exist except for gaps at the sealing elements. These gaps can have a height of less than 0.2 mm. These gaps can be considered the smallest gaps. Exactly two of the volumes can form a completely gas-tight sealed volume.

[0017] Both working chambers can thus form an Alpha-type Stirling engine, with one working chamber being the expansion chamber and the other the compression chamber. The volume-changing elements periodically alter the volumes of their respective working chambers, with the volume changes occurring with a phase shift relative to each other. The compression chamber and the expansion chamber are connected by a gas-permeable connection. This connection can contain a regenerator material through which the working medium flows periodically in one direction or the other, allowing the working medium to transfer heat to or absorb heat from the regenerator material. The non-sinusoidal, i.e., anharmonic, change in the working chamber volumes and the corresponding phase shift ensure that dead volume losses are minimized.The working fluid is located almost entirely within the compression space during compression and almost entirely within the expansion space during expansion. The corresponding progression of the movement or deformation of the volume-changing elements, and the resulting volume changes of the working spaces, can be plotted over time. Similarly, the total volume of both working spaces can be represented in a single diagram over time. During compression (areas where the total volume decreases, i.e., where the slope of the total volume over time is negative), the working fluid can be located almost entirely within one working space. Conversely, during expansion (areas where the total volume increases, i.e., where the slope of the total volume over time is positive), the working fluid can be located almost entirely within one working space.

[0018] The volume-changing elements can comprise (or be) reciprocating pistons movably mounted in a cylinder, or deformable elements such as diaphragms or hollow pistons with single, double, or multiple outer walls, which continuously but to varying depths immerse themselves in a quantity of liquid. The volume-changing elements can also be parts of rotary pistons or pistons that move relative to other volume-limiting elements and can additionally perform a rotational or rotary motion relative to the volume-limiting elements or relative to the environment.

[0019] The at least one volume-changing element can be mechanically coupled to a crankshaft by means of a connecting rod or an alternative coupling element. The crankshaft can perform a circular motion, a non-circular motion, a rotationally symmetric motion with 3-fold symmetry (or with characteristic number 3), or a rotationally symmetric motion with multiple symmetry relative to other volume-limiting elements. The speed of the crankshaft relative to the volume-limiting elements can be constant or change over time. For example, the at least one volume-changing element can be mechanically coupled to a crankshaft by means of a connecting rod, with the crankshaft located between the attachment point of the connecting rod to the volume-changing element and the boundary surface of the volume-changing element with the working chamber.From the perspective of the crankshaft, the connecting rod points away from the working space to be confined, not towards it. This means that the volume-changing element can be mechanically coupled to a driving element (e.g., a crankshaft) via a coupling element (e.g., a connecting rod), whereby the attachment point of the coupling element to the volume-changing element is further away from the boundary surface of the volume-changing element and the volume it confines than the attachment point of the coupling element to the driving element.

[0020] The length of the connecting rod, relative to the radius of the circular motion that the crankshaft performs relative to the working chambers, can be relatively short in order to cause a particularly anharmonic motion of the volume-changing element relative to the working chamber, or to cause a particularly anharmonic change in the working chamber volume. Alternatively, the at least one volume-changing element can be mechanically coupled to a driving element (e.g., a crankshaft) via a coupling element (e.g., a connecting rod), wherein the length of the coupling element (measured between its attachment points on the driving element and on the volume-changing element) is less than 200% (e.g., less than 100%, for example, less than 75%) of the maximum distance between two points that the center of gravity of the driving element can assume relative to the working chambers or volume-limiting elements over time.By "particularly anharmonic" we mean that it deviates particularly strongly from a sinusoidal motion over time and in particular leads to longer time intervals in which the working space volume is smaller than the mean of its maximum and its minimum in relation to the time intervals in which the working space volume is larger than the mean of its maximum and its minimum.

[0021] A circular or rotational motion can be the movement of a body's center of gravity around another point. This applies to the present description of the invention as well as to the detailed description of the figures.

[0022] The thermoelectric or thermomechanical transducer can be mounted or arranged in or on a mounting device. For example, the thermoelectric or thermomechanical transducer can be arranged in a housing. The housing can also include a rod or frame to which the thermoelectric or thermomechanical transducer can be mounted or arranged. Alternatively, the thermoelectric or thermomechanical transducer can be mounted or arranged on a rod or frame without an additional housing. The mounting device and the volume limiting elements can be rotatably mounted, allowing them to rotate or twist.In this case, a drive element, for example a crankshaft, can be rigidly and non-rotatably connected to a stationary frame, so that the drive element performs a rotary movement relative to the rotating working spaces.

[0023] The crankshaft, or another drive element mechanically coupled to the at least one volume-changing element, can be an assembly of several elements or one of the elements of the assembly, such as an axle. For example, in the drive element, a pivot axis can be rotatably mounted at the center of an element that is fixed relative to the mounting device and includes an internal gear, by means of a first ball bearing. This pivot axis can be driven, for example, by a motor. The pivot axis can be rigidly connected to a crank. A second ball bearing can be connected to the crank, via which an eccentric gear can be rotatably mounted in the crank. An axle can be rigidly connected to this eccentric gear, but eccentrically to the axis of rotation of the eccentric gear, so that this axle can perform a circular motion around the axis of rotation of the eccentric gear.The circular motion of the eccentric gear around the axis of rotation of the first ball bearing can be mechanically coupled to the circular motion of the axle around the axis of rotation of the second ball bearing via the internal gear of the element and the external gear of the eccentric gear in such a way that these circular motions can have a constant speed ratio. Consequently, the axle can perform a motion that can be composed of two superimposed circular motions around the central axes of the two ball bearings, each with different radii and speeds, but these speeds can be in a constant ratio to each other.

[0024] The shape of the axis's motion can be determined by varying the speed ratios of the two circular motions via the radius ratio of the element's internal gear and the eccentric gear's external gear, as well as by varying the axis's eccentricity relative to the first ball bearing's axis of rotation compared to the second ball bearing's eccentricity relative to the first ball bearing's axis of rotation. The characteristic value of the axis's rotational symmetry can then be derived from the radius ratio of the element's internal gear and the eccentric gear's external gear. For example, this value could be two, three, or four.

[0025] If at least one of the volume-changing elements is designed, for example, as a rotary piston, it can perform a movement such that its center of gravity is movable around a point fixed relative to the center of gravity of other volume limiting elements or the fastening device, whereby the movement deviates from a circular motion.

[0026] At least one of the volume-changing elements can comprise a rotatable piston. The rotatable piston can be configured to perform the movement about a fixed point or about a point fixed relative to the mounting device or to working spaces or volume limiting elements, wherein the movement deviates from a circular motion.

[0027] The movement of the at least one volume-changing element, or of the part of the volume-changing element, or of the drive element mechanically coupled to the volume-changing element, or of the crankshaft mechanically coupled to it, relative to the other volume-limiting elements or the fastening device, can be a movement resulting from a superposition of at least two circular rotational movements about different centers of rotation. For example, this movement can also be superimposed by other movements.

[0028] The rotational speeds of the two rotational movements can be in a constant ratio to each other.

[0029] The volume-changing element, or part of the volume-changing element, or the drive element mechanically coupled to the volume-changing element, may be configured to perform an incomplete rotary movement relative to the working spaces.

[0030] A rotational movement can be a movement of a body around its own axis. This applies to the present description of the invention as well as to the detailed description of the figures.

[0031] An incomplete rotational movement can be a rotational movement in which a body does not rotate completely around its own axis, i.e., it rotates less than 360° around its own axis.

[0032] The volume change element can be configured to perform an incomplete rotational movement relative to the workspaces around its center of gravity or another point.

[0033] The at least one volume-changing element or part of the volume-changing element or the drive element mechanically coupled to the volume-changing element can be configured to change the size of at least two different volumes and, accordingly, the volume of at least two different working spaces by its movement.

[0034] A part of the surface of the volume change element that can be in direct contact with the working medium of one workspace, at least temporarily, cannot also be in direct contact with the working medium of another workspace, at least temporarily.

[0035] The work areas, in whole or in part, can be designed to be rotatably mounted, so that a rotary or rotational movement of the corresponding work areas can be carried out.

[0036] At least one rotatably mounted working chamber can contain a quantity of liquid that may be in direct contact with the working medium within that chamber. Additional heat exchanger elements can be connected to the volume changer element; these heat exchanger elements alternately immerse themselves in and emerge from the liquid as the volume changer element moves relative to the liquid.

[0037] The at least one volume-changing element can be a deformable sealing element, for example a deformable membrane, or comprise a deformable sealing element such as a deformable membrane. This membrane can be designed to delimit a working space containing a quantity of fluid that performs a rotational movement, the shape of the membrane at the time of the minimum working space volume largely corresponding to the shape of the surface of the rotating quantity of fluid or a portion thereof.

[0038] The thermoelectric or thermomechanical converter can contain multiple pairs of compression and expansion chambers, each compression chamber and expansion chamber forming an alpha-type Stirling engine. The volumes comprising expansion chambers can each contain a quantity of fluid and be rotatably mounted about an axis of rotation in one part of a housing or mounting device, thus performing a rotary motion. Similarly, the volumes comprising compression chambers can each contain a quantity of fluid and be rotatably mounted about an axis of rotation in another part of a housing or mounting device, thus performing a rotary motion. All or some of the volume-changing elements that modify the volumes of expansion chambers can be mechanically coupled to the same crankshaft or drive element.All or some of the volume-changing elements that alter the volumes of compression chambers may be mechanically coupled to the same crankshaft or drive element.

[0039] The thermoelectric or thermomechanical converter, as described above or below, can be configured as follows: to realize a Stirling or Vuilleumier process, a double Stirling process, or a multiple Stirling process, or any of these processes in which, in addition to compression and expansion of the working medium, condensation and evaporation of the working medium or a component thereof are also possible. The working medium can be, for example, a mixture of air and water vapor or a mixture of helium and water vapor.

[0040] The thermoelectric or thermomechanical converter can be designed as follows: For converting mechanical or electrical energy into heat and / or cold (this may include an application as a "heat pump"), or for transporting heat quantities from a heat source to a heat sink using mechanical or electrical energy, or for generating mechanical or electrical energy by utilizing heat source(s) and heat sink(s) with different temperatures (this may include an application as a "heat engine"), or for converting heat quantities at specific temperatures (e.g., waste heat, heat from solar thermal systems, heat of combustion) into heat quantities at other specific temperatures, whereby mechanical / electrical energy may also be generated or used for operation. This may include an application as a "thermally driven heat pump".

[0041] The thermoelectric or thermomechanical converter can also be designed for hybrid applications from the above-mentioned uses.

[0042] The heat / cold can be thermally coupled to this thermoelectric or thermomechanical transducer using liquids or gases (e.g., combustion gases) as heat transfer fluids, or it can be introduced directly into the device as electromechanical radiation (e.g., sunlight or concentrated sunlight) through a specially designed, transparent housing. Because the working medium is at least partially gaseous and because operation without a phase transition of the working medium is possible, the thermoelectric or thermomechanical transducer is suitable for applications in a very wide temperature range and for applications where very high temperature differences can be utilized or generated (i.e., where the temperature difference between the useful heat / cold and the heat / cold sink is particularly high), e.g., as a high-temperature heat pump.For example, the thermoelectric or thermomechanical converter is suitable for generating very high or very low temperatures for industrial applications (e.g. steam generation, air liquefaction, freeze-drying), as well as for use as a heat pump for heating, for example, old buildings with radiator heating systems, where higher temperatures are required than with more modern heating systems, such as underfloor heating.

[0043] Due to its high efficiency and good heat transfer between the liquid as heat transfer medium and the working fluid, the thermoelectric or thermomechanical converter is also suitable for converting electrical energy into heat, which is then stored in a heat storage device (e.g., latent heat storage or an insulated liquid tank). It is equally suitable for converting this stored heat back into electrical energy.

[0044] In addition to or instead of heat exchanger elements that are in direct contact with the working medium in the work spaces, heat exchanger elements can also be used that are flowed through by the working medium when it flows back and forth between two work spaces.

[0045] A liquid located in the working spaces can be a liquid whose boiling point is in the range of the partially prevailing temperatures and pressures, in order to utilize the enthalpy of the phase transition from solid to gaseous and vice versa in such a way as to increase the performance of the device.

[0046] In addition to its use as a Stirling or Vuilleumier engine, the invention is also applicable to the realization of other thermodynamic cycles by using the working spaces, whose volume is changed by volume-changing elements, as compression or expansion spaces for these cycles, whereby additional inlet and outlet openings can be provided in the working spaces, which are temporarily opened or closed. Brief character description

[0047] The accompanying figures illustrate aspects and / or embodiments of the invention for better understanding and demonstration purposes. They show: Figure 1 a longitudinal section of a Stirling engine in gamma design according to the state of the art, Figure 2 a movement of the pistons of a Stirling engine in gamma or beta configuration over time and the change in the total volume over time according to the state of the art, Figure 3a longitudinal section of a Stirling engine in Alpha design according to the state of the art, Figure 4 a movement of the pistons of a Stirling engine in Alpha design over time and the change in the total volume over time according to the state of the art, Figure 5 a movement of the volume-changing elements of a Stirling engine according to the invention in alpha construction over time and the change of the total volume over time according to the embodiment from Fig. 6b , Figure 6a a longitudinal section of a piston of a Stirling engine, which performs a harmonic (sinusoidal) or nearly harmonic motion according to the state of the art, Figure 6b a longitudinal section of an embodiment of a reciprocating piston of a Stirling engine that performs an anharmonic motion, Figure 6c a longitudinal section of another embodiment of a reciprocating piston of a Stirling engine, which performs an anharmonic motion, Figure 7a movement of the volume-changing elements of a Stirling engine according to the invention in alpha construction over time and the change of the total volume over time according to the embodiment from Fig. 6c , Figure 8 an embodiment of a drive element as a 3D view, Figure 9a a longitudinal section of the drive element, Figure 9b a corresponding cross-section along axis AA, Figure 9c a corresponding cross-section along axis BB, Figure 10 a rotationally symmetrical motion pattern with characteristic number three, Figure 11 a longitudinal section of a double Stirling engine of the Alpha design, Figure 12 a corresponding sectional view along axis AA Figure 13 a corresponding sectional view along axis BB, Figure 14 a 3D view of the Stirling engine from Fig. 11 with the case cut in half and some elements not shown for the sake of clarity, Figure 15a 3D view of a piston of this Stirling engine, Figure 16 an alternative embodiment of a volume change element with a membrane, Figure 17 a cross-section of an alternative embodiment with rotary pistons, Figure 18 a 3D view of a rotary piston of the embodiment made of Figure 16 . Detailed character description

[0048] In the section drawings shown, only the elements (with hatching) that lie in the section plane are depicted, with the exception of a few elements that are shown with dashed lines or without hatching.

[0049] The following section describes the function of a Stirling engine in gamma configuration. Fig. 1Figure 1 schematically shows a Stirling engine of the gamma type known from the prior art. The volume-changing element 61, here a displacer piston in the form of a reciprocating piston, is movably mounted in the cylinder 63 and, by its oscillating motion in the cylinder 63, alternately moves the working medium from the compression chamber 65 to the expansion chamber 66 and vice versa. The working medium flows through the openings 72, the heat exchanger 70, the regenerator 78, the heat exchanger 79, and the openings 71 (or vice versa). The working medium releases heat to the heat exchanger 70, or, in the reverse direction, absorbs heat from the heat exchanger 79. The heat exchangers 70 and 79 are each thermally coupled to external heat sources or sinks. The outer casing 73 prevents the working medium from leaving the system and prevents pressure equalization with the volume outside the device.The working piston 62, which performs an oscillating motion in the cylinder 64 that is phase-shifted relative to the movement of the displacer piston 61, changes the pressure inside the device, including in the compression chamber 65 and the expansion chamber 66. For this purpose, the volume 74 is connected to the compression chamber 65 and the expansion chamber 66 via the connecting element 67, allowing gas to pass through. During compression, the working medium in the compression chamber 65 is heated and can then partially transfer this heat to the heat exchanger 70 as it flows through it. During expansion, the working medium is cooled in the expansion chamber 66 and can then partially absorb heat from the heat exchanger 79 as it flows through it.In addition to the volumes in the connecting element 67, in the heat exchangers 70, 79 and in the regenerator 78, the volume 74 represents a dead space which reduces the efficiency, since the working medium contained therein is not located in the compression chamber 65 or the expansion chamber 66 provided for this purpose during compression or expansion.

[0050] Fig. 2 The curve x1 represents the sinusoidal motion of the displacer piston 61 and the working piston 62 (curve x2) over time t. Curve V shows the distribution of the total volume within the device. 100% here represents the maximum displacement of the displacer piston or the working piston, respectively, and the maximum of the working volume confined by each of them (for curves x1 and x2), or the maximum of the total volume (for curve V). The pressure in the system can also be derived from this curve. Fig. 2It is evident that the working medium is mostly located in compression chamber 65 during compression, but that a certain proportion of the working medium is also located in expansion chamber 66 and in chamber 74. This means a reduction in the efficiency of the Stirling engine.

[0051] The following section describes the principle of a Stirling engine in Alpha configuration according to the state of the art, using an example from the Fig. 3The schematic embodiment shown is explained below. A first volume-changing element 1 (here, for example, a piston) is movably mounted in a first cylinder 3 and defines a first working chamber 5. Likewise, the second volume-changing element 2 (here, for example, a piston), mounted in the second cylinder 4, defines a second working chamber 6. The two working chambers 5, 6 are connected to each other via a gas-permeable connecting pipe 7, in which a regenerator 8 is located.Working chambers 5, 6 and connecting pipe 7 contain a working medium, which can be, for example, a gaseous medium or at least partially composed of a gas. This working medium is thermally coupled to a first heat exchanger element 9 and a second heat exchanger element 10, with heat transfer occurring from a quantity of liquid in the first heat exchanger element 9 via a first partition 15 to the working medium in the first working chamber 5 (or vice versa). Similarly, heat transfer occurs from a quantity of liquid in the second heat exchanger element 10 via a second partition 16 to the working medium in the second working chamber 6. The liquid flows into the first heat exchanger element 9 via a first inlet line 11 and can flow out again via a first outlet line 12, thus achieving heat transport by the liquid as the heat carrier to / from the first heat exchanger element 9.The liquid flows into the second heat exchanger element 10 via a second inlet line 13, and the liquid can flow out again via a second outlet line 14, thereby realizing heat transport by the liquid as heat carrier to / from the second heat exchanger element 10.

[0052] In conventional Stirling engines, the volume-changing elements 1, 2 can typically be mechanically coupled to crankshafts via connecting rods or mechanically coupled to other gears, so that they perform a largely harmonic (i.e., sinusoidal) motion, which exhibits a phase shift between the two volume-changing elements 1, 2. This phase shift is typically between 90° and 180°.

[0053] A corresponding piston movement of a Stirling engine of the Alpha type, known from the prior art, is described in Fig. 4 depicted. Fig. 4Figure 1 shows the movement of the volume-changing elements (e.g., pistons) over time t, where x1 represents the movement of one volume-changing element in the direction of the cylinder axis and x2 represents the movement of the other volume-changing element in the direction of the cylinder axis. 100% again represents the maximum displacement at which the volume of the respective working chamber adjacent to the volume-changing element is at its maximum. Due to the phase shift of the movement of the two volume-changing elements relative to each other, the total volume of the two working chambers and the connecting pipe 7 changes, with the gas volume in Fig. 4 This is represented by the curve labeled V. 100% here represents the maximum total volume. Consequently, the pressure within the total volume also changes; that is, the working medium is alternately compressed and expanded. Compression occurs while the majority of the working medium is located in the single working chamber 5 (in Fig. 4This is x1). The expansion takes place while the majority of the working medium is located in the other workspace 6 (in Fig. 4(This is x2). During compression, the working fluid heats up and transfers heat to the fluid in the first heat exchanger element 9. During expansion, the working fluid cools down and absorbs heat from the fluid in the second heat exchanger element 10. The working fluid flows alternately back and forth through the connecting pipe 7 between the two working chambers 5 and 6. When flowing in one direction, it transfers heat to the regenerator 8 and is cooled to approximately the temperature of the working chamber into which it flows. When flowing in the other direction, it absorbs heat from the heat stored in the regenerator 8 and is heated to approximately the temperature of the working chamber into which it flows. If the two volume change elements 1 and 2 are driven by an external drive (e.g., an electric motor), this Stirling gas cycle can be used to generate useful heat or cooling.In this case, the energy required for the compression of the working medium, transferred from one of the volume-changing elements to the working medium, can outweigh the energy transferred to the other volume-changing element during the expansion of the working medium. Alternatively, the heat exchanger elements 9 and 10 can also be brought to different temperatures using liquids of different temperatures. In this case, the two volume-changing elements, provided they are mechanically coupled with a corresponding phase shift, are moved by the alternating expansion and compression, thereby driving, for example, a generator that can be mechanically coupled to the two volume-changing elements, perhaps by means of a crank mechanism.

[0054] Based on Fig. 4It is evident that during compression (i.e., during the phase of decreasing total volume V), the working medium is largely contained within one of the two working spaces, specifically the one whose individual volume is represented by curve x1. Curve x1 represents both the displacement of the volume change element bounding this working space and the volume of the working space itself, as both quantities are proportional to each other. However, it is also evident that a significant portion of the working medium is located in the other working space during compression, the volume of which is represented by curve x2. During compression, the working medium heats up, and ideally, this heating should occur exclusively in one of the two working spaces, while the expansion of the working medium should take place exclusively in the other.Since this is not the case with the harmonic (sinusoidal) piston motion shown here, the efficiency of the Stirling engine is reduced accordingly. This results in so-called "dead space losses".

[0055] The previously described dead volume losses of an Alpha-type Stirling engine and their effects can be significantly reduced by moving the volume change elements over time t, as described in Fig. 5 This is represented by curves x1 and x2. Due to the phase shift in the movement of the two volume change elements relative to each other, the total volume of the two working chambers and the connecting pipe changes, with the total volume in Fig. 5This is also represented by the curve labeled V. During compression of the working medium, the working medium is located almost exclusively in one of the two working chambers, the volume of which is represented here by curve x1. During expansion of the working medium, the working medium is located almost exclusively in the other working chamber, the volume of which is represented here by curve x2. 100% represents the maximum total volume. The two volume-changing elements move in such a way that they each remain in a position representing less than 50% of their maximum displacement for a longer period. Accordingly, the working chamber volume they define is also less than half the maximum volume during longer time intervals compared to the time intervals in which it exceeds half the maximum volume. The present invention enables a corresponding movement of the volume-changing elements.Consequently, the volume of the workspace is, on average, less than the mean of its maximum and minimum sizes more than half the time.

[0056] Fig. 6a This represents a method known from the prior art of moving a reciprocating piston 21 by means of a piston drive in conventional Stirling engines. The reciprocating piston 21, which is mounted in the cylinder 23 and defines the working chamber 25, is connected to a connecting rod 27 via a ball bearing 28 and a first connecting rod axis 35. A circular movement of a second connecting rod axis 32 along the dashed line 31, e.g., caused by a mechanical coupling of the second connecting rod axis 32 to a crankshaft drive, causes the reciprocating piston 21 to perform an approximately harmonic (sinusoidal) movement, as described in Fig. 2 or in Fig. 4The shorter the connecting rod is chosen relative to the radius of rotation of the crankshaft, the more the movement of the piston 21 deviates from a harmonic motion; however, in this embodiment, the time intervals during which the piston 21 is in a position with more than 50% of its maximum displacement or in which the volume of the working chamber 25 is more than half the average of its maximum and its minimum become longer (compared to the time intervals during which the piston 21 is in a position with less than 50% of its displacement or in which the volume of the working chamber 25 is less than half the average of its maximum and its minimum).

[0057] One of the Fig. 5 The corresponding piston movement, however, can be achieved with the in Fig. 6bof the manner shown, to move a reciprocating piston 22 which is mounted in a cylinder 24 and defines a working chamber 26. The reciprocating piston 22 is connected to a connecting rod 29 via a ball bearing 30 and a first connecting rod axis 36. In contrast to Fig. 6a Here, a second connecting rod axis 34 executes a movement along the dashed line 33, which deviates from a circular motion. In the illustration, the movement follows a triangular shape with rounded corners. This movement causes a movement of the piston 22, which is in Fig. 5 The depicted anharmonic motion pattern corresponds to the present invention. The invention can enable such a motion by, for example, replacing conventional crank mechanisms or other drives with a drive element that allows for such a motion.

[0058] Alternatively, one of the Fig. 5A largely corresponding piston movement can be achieved with the in Fig. 6c The device is designed to move a reciprocating piston 41, which is mounted in a cylinder 42 and defines a working chamber 43. The reciprocating piston 41 is rigidly connected to the actuating element 46 via guide axes 44, 45, which may be mounted in a linear bearing. The actuating element 46 is arranged in the opposite direction to the reciprocating piston 41 from the perspective of the axis of rotation of the crankshaft 52. The actuating element 46 is connected to a connecting rod 50 via a ball bearing 47 and a first connecting rod axis 48. As shown in Fig. 6aA second connecting rod axis 49, which can be a crankshaft, performs a circular motion along the dashed line 51 around the axis 52. Since the connecting rod 50 is relatively short compared to the radius of motion of the connecting rod axis 49 around the axis 52, the motion of the piston 41 deviates significantly from a harmonic motion. By arranging the attachment point of the connecting rod 50 with the actuating element 46 over the connecting rod axis 48 on the side opposite the piston 41 relative to the axis 52, the motion of the piston 41 is such that the working volume 43 is less than half its mean value of its maximum and minimum values ​​during longer time intervals, compared to time intervals in which the working volume 43 is more than half its mean value of its maximum and minimum values. The resulting motion of such a piston over time is...The change in a corresponding workspace volume over time is in . Fig. 7 represented by curves x1 and x2. The resulting total volume over time is in Fig. 7 represented by curve V.

[0059] Out of Fig. 5 and Fig. 7It is evident that, with a corresponding movement of the volume-changing elements over time, or with a corresponding change in the working chamber volumes over time according to curves x1 and x2, dead spaces in an Alpha-type Stirling engine can be reduced to a minimum. The resulting total volume, encompassing both working chambers, is represented by curve V. During compression, when this total volume decreases, the working fluid is located almost exclusively in the compression chamber, whose volume over time is represented by curve x1. Conversely, during expansion, when the total volume increases, the working fluid is located almost exclusively in the expansion chamber, whose volume over time is represented by curve x2.During the phases in which the working medium is located to a greater extent in both the compression space and the expansion space, the total volume remains largely constant.

[0060] Fig. 8 , Fig. 9a, Fig. 9b and Fig. 9c shows a possible embodiment of a drive element with which a Fig. 6b depicted non-circular motion of a connecting rod axis and a corresponding anharmonic motion of a volume change element, as in Fig. 5 and Fig. 6b can be represented and realized.

[0061] Fig. 8 This possible embodiment is shown as a 3D view, Fig. 9a shows a longitudinal section and Fig. 9b and Fig. 9cFigures 1 and 2 show cross-sections along axes AA and BB, respectively. At the center of a stationary element 101, which includes an internal gear, a pivot axis 103 is rotatably mounted by means of a ball bearing 102. This pivot axis 103 can be driven, for example, by a motor. The pivot axis 103 is rigidly connected to the crank 104. A ball bearing 105 is connected to the crank 104, and the eccentric gear 106 is rotatably mounted in the crank 104 via this bearing. The axis 107 is rigidly connected to this eccentric gear 106, but eccentrically to the axis of rotation of the eccentric gear 106, so that this axis 107 can perform a circular motion around the axis of rotation of the eccentric gear 106.The circular motion of the eccentric gear 106 about the axis of rotation of the ball bearing 102 is mechanically coupled to the circular motion of the axis 107 about the axis of rotation of the ball bearing 105 via the internal gear of element 101 and the external gear of the eccentric gear 106 in such a way that these circular motions have a constant speed ratio. The axis 107 therefore performs a motion that consists of two superimposed circular motions about the central axes of the ball bearings 102 and 105, each with different radii and speeds, but these speeds are in a constant ratio to each other.

[0062] The shape of the motion of the axis 107 can be determined by varying the speed ratios of the two circular motions via the radius ratio of the inner gear of element 101 and the outer gear of the eccentric gear 106, as well as by varying the eccentricity of the axis of rotation of the ball bearing 105 compared to the eccentricity of the axis of rotation of the ball bearing 105 with respect to the axis of rotation of the ball bearing 102. The characteristic value of the rotational symmetry of the motion of the axis 107 results from the radius ratio of the inner gear of element 101 and the outer gear of the eccentric gear 106. Fig. 10This shows a rotationally symmetric motion pattern realized with the parameter 3. It is possible to realize a rotationally symmetric motion with multiple symmetries; for example, the parameter can be 2 or 4. By varying the ratio of the two eccentricities, i.e., the radii of the two superimposed circular motions of axis 107, it is possible to determine whether the motion pattern is more "bulging" as in Fig. 10 is similar to a triangular shape with rounded corners, or rather "pointed" to a triangular shape with concave, inwardly curved side lines and without rounded corners.

[0063] Fig. 11 shows a longitudinal section of an embodiment of the present invention with volume change elements according to the embodiment shown Fig. 6cThe housing 201 is rotatably mounted in the frame 204 via ball bearings 202 and 203. The motor / generator 205, which is rigidly connected to the frame 204 (connection not shown here), can drive the rotational movement of the housing 201 or be driven by the rotating housing. For this purpose, the shaft 206 of the motor / generator 205 is rigidly connected to the housing 201 by means of the shaft mount 207. Inside the housing 201 are the crankshafts 208 and 209, which, together with the cranks 210 and 211 and the connecting element 212, form a stationary unit, as they are rigidly connected to the frame 204 by means of the shaft 213 and the shaft mount 214. The crank 211 is fixed in its position by being mounted in the rotating housing 201 via the shaft 215 and the ball bearing 216.

[0064] The cylinders 221, 222, 223, 224 are rigidly connected to the housing 201 and, as volume limiting elements, form volumes 381, 382, ​​383, 384, which partially contain liquid quantities 225, 226, 227, 228 and partially contain working medium in the working chambers 231, 232, 233, 234. The working chambers 231, 232, 233, 234 form partial volumes of the volumes 381, 382, ​​383, 384. The liquid quantities 225, 226, 227, 228 are held in their shape and position by their rotation together with the housing 201 and the cylinders 221, 222, 223, 224, due to centrifugal forces acting upon them. Cylinders 221, 222, 223, 224 each contain pistons 235, 236, 237, 238, which are rigidly connected to actuating elements 245, 246, 247, 248 by means of guide shafts 241a / b, 242a / b, 243a / b, 244a / b. The guide shafts 241a / b, 242a / b, 243a / b, 244a / b are linearly movable relative to the housing 201 in linear bearings 251a / b, 252a / b, 253a / b, 254a / b (see [reference]). Fig. 12 and Fig. 13), to enable linear movement of the pistons 235, 236, 237, 238 without causing lateral forces of the pistons 235, 236, 237, 238 on the cylinders 221, 222, 223, 224. The pistons 235, 236, 237, 238 include piston rings 255, 256, 257, 258, which provide a gas-tight seal for the working chambers 231, 232, 233, 234. The pistons 235, 236, 237, 238 also include heat exchanger elements 261a-j, 262a-j, 263a-j, 264a-j, which are each rigidly connected to them. These heat exchanger elements 261a-j, 262a-j, 263a-j, 264a-j immerse themselves to different depths in the liquid quantities 225, 226, 227, 228 depending on the position of the pistons 235, 236, 237, 238 and can thus absorb heat quantities from them or transfer them to them.Since these heat exchanger elements 261a-j, 262a-j, 263a-j, 264a-j are also always partially located in the working spaces 231, 232, 233, 234 and are thus thermally coupled to the working medium contained therein, they can also transfer heat quantities to or absorb them from the working medium relatively quickly. Via these heat exchanger elements 261a-j, 262a-j, 263a-j, 264a-j, the working fluid in the working chambers 231, 232, 233, 234 is therefore indirectly thermally coupled to the liquid quantities 225, 226, 227, 228 and can thus transfer heat to or absorb it from the liquid elements 225, 226, 227, 228 more quickly than would be the case without the heat exchanger elements 261a-j, 262a-j, 263a-j, 264a-j. This also ensures that compression or expansion of the working fluid in the working chambers 231, 232, 233, 234 is largely isothermal.

[0065] The liquids 225, 226, 227, 228 serve as heat transfer fluids, enabling the transport of heat into and out of the working chambers 231, 232, 233, 234. For this purpose, openings 271, 272, 273, 274 allow liquid to flow into the interior of the cylinders 221, 222, 223, 224. This liquid originates from the annular inlet chambers 279, 280, in which a liquid ring can form. New liquid can flow into the inlet chambers 279, 280 from the outside via the inlet pipes 281, 282. Through the openings 275, 276, 277, 278, liquid can flow from the interior of the cylinders 221, 222, 223, 224 into the annular drain chambers 283, 284, in which a liquid ring can form.Liquid can flow out of the drain chambers 283, 284 via the drain pipes 285, 286, the immersion depth of the drain pipes 285, 286 into the drain chambers 283, 284 regulating the fill level of the liquid ring in the drain chambers 283, 284, and correspondingly also the fill level of the liquid quantities within the cylinders 221, 222, 223, 234.

[0066] Figure 12 shows a sectional view of this embodiment along the section axis AA. Figure 13Figure 1 shows a sectional view of this embodiment along the section axis BB. In these sectional views, the mechanical coupling of the rotating pistons 235, 236, 237, 238 with the stationary crankshafts 208, 209 is evident, causing the anharmonic movement of the pistons 235, 236, 237, 238 relative to the cylinders 221, 222, 223, 224. The actuating elements 245, 246, 247, 248 are mechanically connected to the connecting rods 291, 292, 293, 294 via the connecting rod axes 295, 296, 297, 298 which are fixedly connected to them. The connecting rods 291, 292, 293, 294 include ball bearings and are movably connected to the connecting rod axes 295, 296, 297, 298. Likewise, the connecting rods 291, 292, 293, 294 are rotatably mechanically coupled to the crankshafts 208, 209. The actuating elements 245, 246, 247, 248 are rigidly connected to the guide axes 241a / b, 242a / b, 243a / b, 244a / b, and these in turn are rigidly connected to the pistons 235, 236, 237, 238.The guide axes 241a / b, 242a / b, 243a / b, 244a / b are linearly displaceable in linear bearings 251a / b, 252a / b, 253 / a / b, 254a / b, which are rigidly connected to the linear bearing holders 301, 302, 303, 304. When the housing 201 rotates, together with the linear bearing holders 301, 302, 303, 304, which are fixedly connected to the housing 201, the actuating elements 245, 246, 247, 248 consequently rotate about the crankshafts 208, 209, which are fixed eccentrically to the axis of rotation of the housing. This causes their linear oscillating motion relative to the cylinders 221, 222, 223, 224 via the mechanical coupling through the connecting rods 291, 292, 293, 294. Since the connecting rods 291, 292, 293, 294 are relatively short, i.e., their lengths correspond approximately to the diameter of the rotation of the crankshafts 208, 209 relative to the housing, this linear oscillating motion is not harmonic / sinusoidal, but anharmonic.

[0067] Working chambers 231 and 234 are interconnected via the pipes 305, 308 and the regenerator housing 309, the regenerator housing 309 containing a gas-permeable regenerator material 311 (e.g., stainless steel wool). They thus form a first Stirling engine of the Alpha type. Working chambers 232 and 233 are interconnected via the pipes 306, 307 and the regenerator housing 310, the regenerator housing 310 containing a gas-permeable regenerator material 312. They thus form a second Stirling engine of the Alpha type.

[0068] Fig. 14 shows a 3D view of the embodiment Fig. 11 , Fig. 12 and Fig. 13 , whereby only the lower half of the housing 201 is shown. Likewise, the upward-projecting pistons 236, 237 with their actuating elements 246, 247 and their guide axes 242a / b, 243a / b and their connecting rods 292, 293 and cylinders 222, 223 are missing.

[0069] Fig. 15Figure 1 shows a 3D view of a reciprocating piston 235 of this embodiment with its piston ring 255, the guide axes 241a, 241b, the actuating element 245 and the heat exchanger elements 261a-j. The reciprocating piston 235 includes a flow channel 325 through which partial quantities of the working medium can flow from one space between two of the heat exchanger elements 261a-j to another space between two of the heat exchanger elements 261a-j, which is why the heat exchanger elements 261a-j also include openings in the area of ​​the flow channel 325.

[0070] Fig. 16 shows an alternative embodiment of a volume change element 335 and a volume limiting element 321, which replaces the one described in Fig. 11 , Fig. 12 , Fig. 13 . Fig. 14 and Fig. 15The volume-changing elements and volume-limiting elements shown can be used. The volume-changing element 335 is a piston which is connected to the cylindrical volume-limiting element 321 by means of a flexible and stretchable diaphragm 355 such that the volume 386 according to the invention, which contains the partial volume 331 containing a working medium, is completely gas-tight except for a gas-permeable connection to another volume (this connection is in Fig. 16(not shown). Heat exchanger elements 361a-g are rigidly connected to the piston 335. As the piston 335 moves relative to the volume limiting element 321, these elements periodically move into and out of the liquid 325. The liquid 325, along with the volume limiting elements 321, is held in its position and shape by centrifugal forces around an axis of rotation, thus preventing the heat exchanger elements 361a-g from entraining large quantities of liquid when emerging from the liquid 325. The guide axes 341a, 341b, mounted in linear bearings (not shown), ensure that the piston 335 moves linearly relative to the volume limiting element 321. The piston 335 is mechanically connected to the crankshaft 399 via the actuating element 345 and the connecting rod 391, which is rotatably connected to the actuating element 345 via the connecting rod axis 395.The crankshaft is fixedly connected to a frame located outside the housing and does not move, thus performing a circular motion relative to the rotating volume limiting elements 321.

[0071] Fig. 17 and Fig. 18 reveal a further embodiment. In Fig. 17 and Fig. 18Each of two volume-changing elements 435 is shown, each of which defines three volumes 481, 482, 483 with their three working spaces 431, 432, 433 and can change them by moving around the rotational axis of the housing 401. This is a triple Stirling engine of the Alpha type, the construction of which is similar to a Vuilleumier engine disclosed in EP23209033.2. In contrast to the Vuilleumier machine from EP23209033.2, here the three volumes 481, 482, 483, bounded by a volume-changing element 435, with their subvolumes 431, 432, 433, are not interconnected by gases. Instead, each subvolume 431, 432, 433 bounded by the volume-changing element 435 is connected by gases to another volume bounded by the second volume-changing element. Each of these gas-permeable connections contains a regenerator material (the gas-permeable connections and regenerator material are described in [reference missing]). Fig. 17 and Fig. 18 (not shown). Thus, they each form a Stirling engine of the Alpha type. In contrast to the Vuilleumier engine from EP23209033.2, the volume-changing elements 435 therefore each separate at least two volumes 481, 482, 483, which are connected to each other in a gas-impermeable manner.

[0072] Fig. 17Figure 435 shows the cross-section through one of the two volume-changing elements 435. Both volume-changing elements 435 are located in adjacent sections of the housing 401. The housing 401 is rotatably mounted to the frame 404 and can be driven in its rotational movement by a motor / generator or drive the motor / generator. The volume-changing elements 435 are mechanically coupled to the housing 401 and the frame 404 via a gear 410 such that they each perform a rotational movement at the same rotational speed as the housing 401, superimposed by an additional translational movement of the volume-changing elements 435 relative to the housing 401, which has the shape of... Fig. 10 This results in the volume change elements 435 periodically increasing and decreasing the three volumes 481, 482, 483, and the three further volumes not shown here, over a period of time, as shown by curve x1. Fig. 5The heat exchanger elements 461a-I, 432a-I, 463a-I are immersed in and out of the liquid volumes 425, 426, 427, respectively, so that they can transfer heat to or absorb heat from them. Sealing elements 411, 412, 413, mounted radially inwardly in shafts 414, 415, 416, create a gas-tight seal between the volumes 431, 432, 433. These sealing elements are continuously pressed against the volume change element 435 by springs, buoyancy forces in a surrounding liquid, magnetic forces, or other forces.Alternatively, the sealing elements 411, 412, 413 can also be mounted in the volume change element 435 so as to be displaceable radially outwards and accelerated outwards by centrifugal forces, where they seal the volumes 431, 432, 433 against each other by contact with a part of the housing which is higher than the liquid quantities 425, 426, 427 in the radially inwards direction and is therefore not covered by liquid.

[0073] The second volume change element, not shown here, limits in the same way as the one in Fig. 17 and Fig. 18The volume-changing element 435 depicted here changes three other volumes and periodically alters their size in an analogous manner, with each of the volumes 481, 482, 483 of the first volume-changing element being permeably connected to one of the three other volumes of the second volume-changing element. The movement of the two volume-changing elements is phase-shifted such that the volume changes of any two gas-permeably connected volumes are also phase-shifted such that their total volume changes over time as described in Fig. 5 is represented by curve V, where the time course of the size of the two volumes is also shown by curves x1 and x2. Fig. 5 corresponds.

[0074] The gearbox 410 can have the structure shown in Fig. 12a and Fig. 12b from EP 23209033.2.

[0075] Fig. 18shows a 3D view of one of the two volume change elements 435 with its heat exchanger elements 461a-I, 462a-I, 463a-I and part of the gearbox 410.

Claims

1. Thermoelectric or thermomechanical transducer comprising at least two volumes (381, 382, ​​383, 384, 386, 481, 482, 483) whose size can be changed, - which are limited by volume limiting elements (201, 221, 222, 223, 224, 321, 401, 414, 415, 416) which include, for example, openings (271, 272, 273, 274, 275, 276, 277, 278) for the inflow and outflow of liquid quantities - and which are interconnected in a gas-permeable manner - and which contain a working medium that is at least partially gaseous - and which are each limited by volume changing elements (235, 236, 237, 238, 335, 435) can be changed in size, wherein at least one of the volume-changing elements (235, 236, 237, 238, 335, 435) changes the size of at least one of the volumes (381, 382, ​​383, 384, 386, 481, 482, 483) such that its size changes on average during the operation of the device for more than half the time, for example, for more than 60% of the time,less than the average of its maximum size and its minimum size.

2. The thermoelectric or thermomechanical converter according to claim 1, wherein the total size of the at least two volumes is, on average, at least the mean of their maximum size and their minimum size for more than half the time, for example, for more than 60% of the time.

3. The thermoelectric or thermomechanical converter according to claim 1 or 2, wherein at least one or two volume-changing elements change the size of at least two volumes such that their sizes are, on average, less than the mean of their maximum size and their minimum size for more than half the time, for example, for more than 60% of the time.

4. The thermoelectric or thermomechanical transducer according to any one of claims 1 to 3, wherein the at least one volume change element separates at least two volumes according to claim 1 or other volumes from each other which are not connected to each other in a gas-permeable manner.

5. The thermoelectric or thermomechanical transducer according to any one of claims 1 to 4, wherein two of these volumes together form a total volume that is sealed gas-tight to the outside, for example, the gas-tight total volume can consist of gaps at sealing elements, for example, the gaps have a height in a range of less than 0.2 mm, for example, exactly two of the volumes form a total volume that is completely sealed gas-tight to the outside.

6. The thermoelectric or thermomechanical converter according to any one of claims 1 to 5, wherein the gas-permeable connection of the at least two volumes comprises a heat exchanger element or a regenerator, for example steel wool.

7. The thermoelectric or thermomechanical converter according to any one of claims 1 to 6, wherein the two volumes form part of an alpha-type Stirling engine.

8. The thermoelectric or thermomechanical transducer according to any one of claims 1 to 7, wherein at least part of the volume limiting elements are capable of performing a rotational movement.

9. The thermoelectric or thermomechanical converter according to any one of claims 1 to 8, wherein at least one of the volumes contains a quantity of liquid (225, 226, 227, 228, 325, 425, 426, 427).

10. The thermoelectric or thermomechanical converter according to any one of claims 1 to 9, wherein the at least one volume change element is mechanically coupled to a drive element, for example a gearbox or a crankshaft (52, 208, 209, 399).

11. The thermoelectric or thermomechanical transducer according to claim 10, wherein the drive element performs a movement about an axis or point relative to volume limiting elements that deviates from a circular motion.

12. The thermoelectric or thermomechanical converter according to any one of claims 1 to 11, wherein the at least one volume-changing element is mechanically coupled to a drive element via a coupling element, wherein the length of the coupling element, for example measured between its attachment points on the drive element and on the volume-changing element, is less than 200%, for example less than 100%, for example less than 75% of the maximum distance between two points that the center of gravity of the drive element can assume over time relative to the volume-limiting elements, wherein, for example, the coupling element comprises a connecting rod (48, 49, 50, 291, 292, 293, 294, 391), and wherein, for example, the drive element comprises a crankshaft (52, 208, 209, 399).

13. The thermoelectric or thermomechanical converter according to any one of claims 1 to 11, wherein the at least one volume change element is mechanically coupled to a drive element via a coupling element, wherein the attachment point of the coupling element to the volume change element is further away from the boundary surface of the volume change element with the volume bounded by it than the attachment point of the coupling element to the drive element, wherein, for example, the coupling element comprises a connecting rod (48, 49, 50, 291, 292, 293, 294, 391), wherein, for example, the drive element comprises a crankshaft (52, 208, 209, 399).

14. The thermoelectric or thermomechanical transducer according to any one of claims 1 to 13, wherein the at least one volume change element comprises a reciprocating piston and / or a deformable sealing element such as a diaphragm (355).

15. The thermoelectric or thermomechanical transducer according to any one of claims 1 to 14, wherein the at least one volume change element is a rotary piston which performs a rotating movement of its center of gravity and / or a rotary movement relative to volume limiting elements.

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