CN111316050A

CN111316050A - Refrigeration device and method

Info

Publication number: CN111316050A
Application number: CN201880072393.3A
Authority: CN
Inventors: 保罗·奈泽
Original assignee: Bao LuoNaize
Current assignee: Bao LuoNaize
Priority date: 2017-11-10
Filing date: 2018-11-09
Publication date: 2020-06-19
Also published as: EP3707445A1; US20190186786A1; WO2019094737A9; EP3707445A4; WO2019094737A1

Abstract

A heat exchange system includes a first storage volume having a first point and a second point and a first thermal material contained in the first storage volume. The first thermal contact is thermally coupled to the second point. Applying a force to the first thermal material can result in a temperature difference between the first point and the second point.

Description

Refrigeration device and method

Priority requirement

The present patent applications are non-provisional applications and claim the benefit of priority from the above provisional application No. 62/584,125 (attorney docket No. 5161.001PRV) filed on

day

10, 11, 2017, U.S. provisional patent application No. 62/708,959 (attorney docket No. 5161.001PV2) filed on

day

2, 1, 2018, and U.S. provisional patent application No. 62/766,143 (attorney docket No. 5161.001PV3) filed on

day

3, 10, 2018, each of which is incorporated herein by reference in its entirety.

Background

When the hot and cold thermal stores are in thermal contact with each other, heat typically flows from the hot thermal store to the cold thermal store. The heat may be transferred, for example, via conduction.

Conventional heat pumps need to perform mechanical work in order to transfer heat from a cold reservoir to a hot reservoir. For example, conventional refrigerators consume electrical power to transfer heat from a cold interior and to transfer heat to a warm exterior, such as the room in which the refrigerator is located.

Conventional heat engines do mechanical work by absorbing heat from a hot storage body and transferring the heat to a cold storage body. For example, in a marine steam engine, the working material absorbs heat from a heat storage in a boiler and then performs mechanical work, for example, on the steam engine, whereupon the steam transfers the heat in a condenser to a cold storage, such as the ocean.

It is desirable to provide an improved thermodynamic system.

Drawings

In the drawings, which are not necessarily drawn to scale, like numerals may describe like parts in different views. Like numerals having different letter suffixes may represent different instances of similar components. The drawings illustrate generally, by way of example, but not by way of limitation, various embodiments discussed in the present document.

FIG. 1 is a cross-sectional view of an exemplary embodiment of a heat transfer device.

FIG. 2 is a graph of material properties of the exemplary embodiment of FIG. 1 in equilibrium.

Fig. 3 is a graph of material properties for another example of the embodiment of fig. 1 in equilibrium.

FIG. 4 is a cross-sectional view of another exemplary embodiment of a heat transfer device.

FIG. 5 depicts a plot of pressure versus specific volume indicating changes in a parameter at different locations and at different points in time during one example thermodynamic cycle during operation within the example embodiments shown in FIGS. 6A-6B.

Fig. 6A shows a graph of normalized material properties as a function of position along the length of the device at a particular point in time, and fig. 6B depicts a cross-sectional view of an exemplary device.

In fig. 7A-7H, cross-sectional views of the example apparatus of fig. 6A-6B are shown in different configurations according to different points in time during one example method of operation shown in fig. 5.

FIG. 8 is a graph of material properties of an example embodiment during an example method of operation including either of the embodiments of FIG. 8 or FIG. 11.

FIG. 9 is a graph of material properties of an example embodiment during an example method of operation including any of the embodiments of FIGS. 9 and 13.

FIG. 10 is a graph of material properties of an example embodiment during an example method of operation including any of the embodiments of FIGS. 10 and 12.

FIG. 11 is a schematic diagram of various embodiments of the present invention.

FIG. 12 is a schematic diagram of various embodiments of the present invention.

FIG. 13 is a schematic diagram of various embodiments of the present invention.

FIG. 14 is a cross-sectional view of an exemplary embodiment of a refrigeration device.

FIG. 15 is a cross-sectional view of various components of another exemplary embodiment of a refrigeration device.

FIG. 16 is a cross-sectional view of an exemplary embodiment of a heat transfer device.

FIG. 17 is a cross-sectional view of an exemplary embodiment of a heat transfer device.

FIG. 18 is a cross-sectional view of an exemplary embodiment of a heat transfer device.

FIG. 19 is a cross-sectional view of an exemplary embodiment of a heat transfer device.

FIG. 20 is a cross-sectional view of one exemplary embodiment of an artificial heat storage body or artificial heat reservoir comprising a heat transfer device.

Detailed Description

When the thermal storage body and the cold storage body are in thermal contact with each other, heat typically flows from the thermal storage body to the cold storage body. The heat may be transferred, for example, via conduction.

According to the literature, the sum of the entropies of thermodynamic systems interacting with each other in a thermodynamic process increases or remains constant.

In some cases, it is desirable to provide a thermodynamic system where heat flows from a cooler region to a hotter region or where heat flows faster than existing systems. It is desirable to provide an improved thermodynamic system. At least some of these challenges are addressed by the exemplary embodiments disclosed herein.

FIG. 1 is a cross-sectional view of an exemplary embodiment of a heat transfer device. Various heat flows are described, but this is not intended to be limiting. One skilled in the art will appreciate that embodiments may include heat flow between any two points, and may include heat flow between any other two points. In this particular description, the device is configured to exchange heat between two points in the storage volume or between the first storage volume 2 and the second storage volume 7. The first storage body 2 contains a material a1, and the second storage body 7 contains a material B8. Also shown is a third reservoir 18 containing material C16 and a fourth reservoir 19 containing material D17.

Fig. 1 shows a heat exchange device 3 configured to facilitate heat flow between a set of two points described below, or between any or all of the two points described below. The heat flow may be between the first reservoir 2 and the third reservoir 18, the heat exchange device 20 and the heat exchange device 6, the heat exchange device 20 being configured to establish thermal contact and facilitate the heat flow between the third reservoir 18 and the fourth reservoir 19, and the heat exchange device 6 being configured to establish thermal contact and facilitate the heat flow between the fourth reservoir 19 and the second reservoir 7.

The heat exchange means 3 comprise an element 13 in thermal contact with the material a1 in the first reservoir 2, and an element 4 in thermal contact with the material C16 in the third reservoir 18. The heat exchanging means 6 comprises an element 5 in thermal contact with the material D17 in the fourth reservoir 19 and an element 14 in thermal contact with the material B8 in the second reservoir 7. The heat exchange device 20 comprises an element 23 in thermal contact with the material C16 in the third reservoir 18, and an element 24 in thermal contact with the material D17 in the fourth reservoir 19. Each element represents a portion of the associated heat exchange device in direct thermal contact with the material in the associated reservoir. In fig. 1, the element can be considered to be the portion of the heat exchange device not surrounded by the thermal insulation 15.

The three

heat exchange devices

3, 6 and 20 are constructed substantially identically. In other embodiments, the three

heat exchange devices

3, 6 and 20 need not be constructed substantially identically. In the embodiment shown in fig. 1, the

heat exchange elements

4, 5, 13, 14, 23 and 24 are configured to exchange heat with the respective material via conduction and via electromagnetic waves. For example, the aforementioned heat exchange elements may be solid and may be made of a material such as copper. In other embodiments, other methods of establishing thermal contact between the heat exchange element and the respective material in the associated reservoir, such as between element 23 and material C16 in third reservoir 18, may be employed.

The thermal contact between the elements of a particular heat exchange device, such as element 23 and element 24 of heat exchange device 20, may be arranged in a variety of ways. In fig. 1, the heat flow between the relevant elements is achieved by heat conduction. In other words, heat absorbed by the elements 23 can flow to the elements 24 via physical contact between the elements. In FIG. 1, this physical contact is provided by a third element of the heat exchange device, wherein the third element extends through the thermal shield 15 and is surrounded by the thermal shield 15. In fig. 1, all three elements of the heat exchange device are made of the same material. In this case, the heat exchange device may be constructed from a single piece of material.

In other embodiments, thermal contact between elements of a particular heat exchange device may be facilitated via forced convection. For example, a heat exchange element such as element 23 may include a fluid configured to flow through a cavity within the heat exchange element. The heat exchange element may take a shape similar to that shown in figure 1, except that the element does not have a solid cross-section but a tubular cross-section surrounding the fluid. A separate pump may be provided to move fluid around a closed path such as the path formed by the elements of the heat exchange device shown in figure 1. The fluid may be employed to absorb heat as the fluid flows through a particular heat exchange element, such as element 23. The fluid may then or simultaneously be pumped to a second heat exchange element of the heat exchange device, such as element 24 of heat exchange device 20. As it flows over the second heat exchange element, the fluid may transfer heat to the second heat exchange element and subsequently to an adjacent material, such as material D17 in the fourth reservoir 19, via conduction. The aforementioned fluid may be water or a gas such as air or any other suitable fluid. One skilled in the art will be able to recognize suitable fluids for a given application, such as fluids having high thermal conductivity and low viscosity. Alternatively, the fluid within the heat exchange element and the cavity may also be configured to allow natural convection of the fluid through the cavity. For example, the absorption of heat may reduce the density of the fluid, which may result in natural convection of the fluid from one element, such as element 23, to another element, such as element 24, due to buoyancy effects.

In other embodiments, thermal contact between elements of a particular heat exchange device may be facilitated via electromagnetic waves. For example, a first heat exchange element, such as element 23, may be isolated from a second heat exchange element, such as element 24, by a vacuum. The interface between the vacuum and each heat exchange element may be configured in the following manner: a specific proportion of the photons emitted by the first heat exchange element are absorbed by the second heat exchange element and a specific proportion of the photons emitted by the second heat exchange element are absorbed by the first heat exchange element. For some embodiments, the gap between the first heat exchange element and the second heat exchange element may be made as small as practical considerations will allow. The interfacial area between the vacuum and each heat exchange element may be determined by the specific heat flux. The geometry of the interface may also be subject to considerations regarding reducing heat loss during heat flow between the first and second heat exchange elements. The optimal configuration of the heat exchange device depends on the application or intended use of the invention. In other embodiments, the gap between the first and second heat exchange elements need not form a vacuum, but may be occupied by a fluid, for example a gas such as air or a liquid such as oil. In this case, thermal contact may involve not only photons, but also conduction, and in some embodiments convection.

In some embodiments, there may be relative motion between the heat exchange elements of any one heat exchange device, such as between element 5 and element 14 of heat exchange device 6. This may be caused by a relative movement between the fourth reservoir 19 and the second reservoir 7. For example, the relative movement may be facilitated and controlled by an electric motor. The mechanical connection may be established by roller bearings or magnetic bearings. In this case, additional considerations affect the configuration and design of the heat exchange device. For example, an additional purpose may be to reduce friction losses associated with relative motion. In this respect, the aforementioned use of electromagnetic waves or fluid as a thermal medium between the heat exchange elements may be advantageous. It is noted that any means of mechanically or electromagnetically connecting a thermal storage body to another thermal storage body may be employed in order to facilitate thermal connection between the storage bodies. For example, the associated heat exchange elements may be in thermal contact by means of a solid material such as a metal present in a roller bearing.

Those skilled in the art will be able to find suitable types, configurations and suitable methods of operation for each heat exchange device for the purpose and limitations of the intended application.

Any of the heat exchange devices may also include means for adjusting or modifying the flow of heat flow through the heat exchange device. Such devices and methods are well known in the art. For example, the heat flow through the heat exchange device may be adjusted by modifying the overall thermal conductivity of the heat exchange device. This may be achieved by placing a material of selected thermal conductivity in the path of the heat flow between the two heat storage bodies. For example, two heat exchange elements of a heat exchange device, such as elements 23 and 24 of heat exchange device 20, may be in thermal contact with each other via a third element having a selected thermal conductivity. The thermal conductivity of the third element may be selected as follows: the overall thermal conductivity of the heat exchange device is modified in a desired manner. Alternatively or simultaneously, the physical contact area between two elements of the heat exchange device may be adjusted to control the heat flow. The heat flow rate may be varied by using the length of the heat insulating portion of the heat exchange device, i.e., the length of the portion connecting the first heat exchange element and the second heat exchange element surrounded by the heat insulating device 15.

Where the flow of heat through the heat exchange device involves forced convection of fluid within the heat exchange device, the heat flow may be controlled by adjusting the flow rate of the fluid, which may in turn be modified by controlling the operation of a pump responsible for circulating the fluid through the heat exchange device. In the case where the fluid involved in the heat transfer process is subject to natural convection, the flow rate can be varied by adjusting the cross-sectional area at appropriate points along the fluid path throughout the convection process.

In the case where there is an exchange of electromagnetic waves between a first surface area of a first heat exchange element and a second surface area of a second heat exchange element of a particular heat exchange device, there are a number of ways to control the heat flow. For example, the proportion of photons emitted by the first surface region and absorbed by the second surface region may be adjusted. This can be achieved in several ways. For example, a third material having a high reflectivity may be placed between the first surface region and the second surface region such that the third material reflects some or all of the photons emitted by the first surface region back toward the first surface region and some or all of the photons emitted by the second surface region back toward the second surface region. Other methods for regulating the heat flow of these and other types of heat exchange devices are well known in the art.

Fig. 1 shows a thermal insulation device 15. One of the criteria for selecting and constructing the thermal insulation 15 may be the following capabilities of the materials: reducing unintended heat flow from a particular storage volume contained within or surrounded by the thermal isolation device 15, such as heat flow from the third storage volume 18 to another enclosed storage volume, such as heat flow to a fourth storage volume or to an open storage volume such as an external environment; or such as the heat flow of another closed storage volume to the third storage volume 18, such as the heat flow of an open storage volume, such as the external environment, to the fourth storage volume. In the embodiment shown, the thermal insulation means 15 is a solid material with a low coefficient of thermal conductivity. In explaining the operation of the apparatus shown in fig. 1, the insulation apparatus will be considered to be a substantially fully insulated material. In practice, the thermal insulation means 15 may not be completely thermally insulated.

In some embodiments, the thermal insulation 15 may include an inner layer and an outer layer, wherein the outer layer is isolated from the inner layer by a vacuum. In other embodiments, the outer layer may be isolated from the inner layer by another suitable material, such as a fluid. The vacuum may enhance the ability of the thermal isolation device 15 to inhibit accidental heat flow. In embodiments involving relative movement between the outer and inner layers, a vacuum or other suitable material in the space between the outer and inner layers may also be used to reduce frictional losses. For example, the outer layer may interact with a reservoir, such as an external environment or a second reservoir 7. The inner layer may interact with a different reservoir, such as the fourth reservoir 19, which may be movable relative to the fixed reservoir. Those skilled in the art will be able to find suitable materials such as fluids with low thermal conductivity and low viscosity.

In the simplified example shown in fig. 1, material a1 in the first reservoir 2 and material B8 in the second reservoir 7 are gases. The material C16 in the third storage volume 18 and the material D17 in the fourth storage volume 19 are also gases, which are considered ideal gases for the sake of simplicity.

According to the present exemplary embodiment, materials a1, B8, C16, and D17 are configured as "thermal media". The term "thermal medium" as used herein refers to any physical medium that can facilitate energy transfer. Thus, the thermal medium is not limited to the aforementioned gaseous embodiments, but may comprise any of a number of different materials or take any of a number of forms. For example, the thermal medium may be a solid or a fluid. The thermal medium may be any type of solid, such as a crystal or glass, and any type of fluid, such as a liquid, gas, plasma, or ferrofluid. The thermal medium may also contain individual sub-molecular particles such as electrons or protons. In some embodiments, the thermal medium may also consist essentially of photons. In this case, the reservoir containing the thermal medium can be described as a vacuum. In other words, the thermal medium may also be modeled as an object capable of emitting or absorbing electromagnetic waves. Note that the thermal medium may be composed of a collection or mixture of different types of materials. For example, one type of material in a thermal medium may be a particular type of molecule in gaseous form, such as molecular nitrogen, while another type of material in the same thermal medium may be photons. Note that the thermal medium may also be comprised of a collection of different sets of specific types or forms of materials. For example, one part of the thermal medium may be a solid such as copper, while another part may be a liquid such as water, while a third part may also be steam, i.e. water in the gas phase. In the context of materials a1, B8, C16, and D17, and

heat exchange devices

3, 6, and 20, the terms "material" and "thermal medium" may be used interchangeably herein, as the associated material is configured as a thermal medium. Note that this also applies to the case where a particular thermal medium may not be often, commonly or conventionally referred to as a material. For example, photons are thermal media, but are not conventionally referred to as materials. Note that material D17 may be one type of material such as a solid, such as a metal, such as copper or aluminum, while material C16 may be another type, such as a gas, such as argon or air. Note that there may be constraints on some of the material properties of materials D17 and C16. These constraints depend on the intended use of the device as will be explained later.

The flow of heat within a particular reservoir, such as the third reservoir 18, may take several forms. For example, heat may be transferred within the reservoir by thermal conduction. This may apply, for example, to the case where material D17 consists of a solid such as copper. In the embodiment shown in fig. 1, heat may be transferred via natural convection as well as other mechanisms. In other embodiments, forced convection may be employed to facilitate heat flow within a particular heat storage volume. For example, a fan may be used to circulate the fluid within the reservoir. In yet another embodiment, photons may be used to transport thermal energy throughout the reservoir. In this case, the inner walls of the thermal insulation means 15 at the interface with a particular reservoir may be given a large reflection coefficient, or have similar properties that contribute to the reflection of photons, in order to reduce any accidental heat flow from the reservoir into the thermal insulation means 15.

In fig. 1, there are volume forces per unit mass acting on the material C16 in the third storage body 18 and the material D17 in the fourth storage body 19. In this simplified example, the volume force is constant over time, and constant in magnitude and direction throughout the volume of each of the reservoirs, and is equal for each of the reservoirs. The volumetric force is directed vertically downward, toward the bottom of the page. In the configuration shown, this direction is also parallel to the long axis of the cross-section of the third reservoir 18. In other embodiments, the volumetric force need not be evenly distributed in space or constant in time. The volume force acts on at least a subset of the particles within materials C16 and D17. In other words, a subset of the particles of material C16 and material D17 experience acceleration contributions. The term "acceleration contribution" is used to distinguish the contribution of the volumetric force per unit mass to the instantaneous net acceleration of particles within the thermal medium from the instantaneous net acceleration itself. There are a variety of methods that can produce such a volumetric force per unit mass.

One type of volumetric force per unit mass is the acceleration of gravity acting on the thermal medium.

The volumetric force may be caused by the presence of a potential field gradient. One example is the force caused by the gradient of the electrical potential. For example, elements of the thermal medium may be configured to be electrically charged. In the context of a thermal medium, for example, the term "element" refers to a component of the thermal medium, such as a sub-molecular particle, a different or specific set of molecules or molecules. In the case of a gas, for example, the molecules may be positively or negatively ionized. The thermal medium may also comprise a collection of mobile electrons. Note that the set may be contained in a solid, such as a conductor, or it may be described as a gas. By applying an electric field within the reservoir, a volumetric force per unit mass can be generated on the charged element of the thermal medium within the reservoir.

For other embodiments, it may not be possible or convenient to use, acquire, or create a thermal medium with a moving charge. In this case, the elements of the thermal medium may be polarized by applying an electric field, or the elements may already have an intrinsic polarization, as is the case in polarized molecules, such as dihydrogen monoxide. These polarized elements can experience volumetric forces when placed in an electric field gradient. Note that the magnitude of the force depends, among other parameters, on the orientation of the polarization axis relative to the electric field. Thus, the electric field may be configured to generate a volume force on the polar element in the thermal medium in the reservoir and to polarize the element in the thermal medium if necessary. The electric field may be applied in a variety of ways known in the art.

Magnetic properties can also be used to generate the volume force. The thermal medium may include diamagnetic, paramagnetic or ferromagnetic elements. When magnetized, the individual elements in the thermal medium may form magnetic dipoles, or the elements may already have intrinsic magnetic dipoles, such as electrons. When these magnetic dipoles are placed in a magnetic field with a non-zero curl or gradient, the magnetic dipoles can experience a volumetric force. Note that the magnitude of the volumetric force is a function of, among other parameters, the orientation of the magnetic dipole with respect to the local magnetic field. Thus, the external magnetic field may be configured to generate a volume force per unit mass on the magnetized element in the thermal medium in the reservoir, and to magnetize the element in the thermal medium if necessary. The magnetic field may be generated by other at least momentarily magnetized elements, or by a current flowing through an electromagnet, among other methods known in the art.

The volumetric force per unit mass may also be caused by inertial effects. For example, the storage body may be subjected to acceleration in an inertial system. This results in an acceleration of the thermal medium relative to the storage body. When the storage volume is accelerated in the inertial system with a constant acceleration in a vertically upward direction towards the top of the page in fig. 1, the thermal medium inside the storage volume will experience an acceleration relative to the storage volume, wherein the acceleration is directed vertically downward towards the bottom of the page. The inertial force may be generated by linear acceleration, i.e. the movement of the storage body in a straight line in an inertial system. Inertial forces can also be generated by angular acceleration, i.e. the movement of the storage body along a curved path. In general, inertial forces may result from any acceleration motion in the inertial frame. Consider the foregoing situation in which the device described therein undergoes circular motion in an inertial system, with the radius and angular velocity remaining constant. In the embodiment shown in fig. 1, for example, the rotation axis may be parallel and coincident with a horizontal line passing through the centroids of the descriptive portions of the cross sections of the first and

second reservoirs

2, 7. Note that in this embodiment, the centripetal acceleration varies linearly with the radius. If it is desired that the volumetric force per unit mass of the thermal medium is substantially uniform, the described device may be at a larger radius, wherein the radial dimension of the device is only a fraction of said radius. For example, the radius may be increased by placing the horizontal axis of rotation further up towards the top of the page in FIG. 1. In some embodiments, the direction vector of the axis of rotation may be anywhere in a plane perpendicular to and horizontally intersecting the plane of the page. Other embodiments may have different positions and orientations of the axis of rotation as well as different rotational speeds. These parameters may also vary over time. Embodiments employing other types of forces or combinations thereof are within the scope of the invention.

The potential may be defined as the integral of the value of the volumetric force per unit mass over the displacement relative to a particular reference point. Note that in this context, potentials are mathematical constructs and need not have a physical manifestation. The location within any thermal storage body that is subjected to a volumetric force per unit mass may be defined in terms of the value of the potential at that location. For a given potential, there is a set of possible points within the reservoir at which the value of the potential is the value of the given potential. Typically, the set describes a three-dimensional equipotential surface. For example, consider a simplified case in which the thermal medium inside the thermal storage body is subjected to a volumetric force per unit mass, wherein the volumetric force is uniform in magnitude and direction throughout the storage body and constant in time. The thermal storage body is an insulation system, i.e. closed and completely insulated, and for example has a cylindrical shape with a length L and a radius R. A cartesian reference coordinate system may be defined, having a z-axis parallel to the length L of the cylinder, and oriented parallel to and in opposite directions of the volumetric force per unit mass. The origin of the reference frame is the center of the circular region at the top of the cylinder, where "top" is defined relative to the z-axis. In this case, the equipotential surfaces are planes perpendicular to the z-axis. The reference point may be defined as the origin of the reference frame. Thus, the value of the potential at the top of the cylinder is zero, while the value of the potential at the bottom of the cylinder is equal to the negative of the product of the volumetric force per unit mass and the length L of the cylinder. Equipotential surfaces of other embodiments can be found using similar principles.

Apparatus and methods for facilitating heat flow are provided. The device comprises a first thermal storage volume and a second thermal storage volume, wherein each storage volume contains a first thermal medium and a second thermal medium, respectively, and wherein the first storage volume is at least partially thermally insulated from the second storage volume and any other storage volume, such as an external environment, and vice versa. The thermal medium in each reservoir is subjected to a volumetric force per unit mass that typically does not have a uniform magnitude or direction for different points in space and may not be constant over time.

For purposes of illustration, the specific mode of operation of such a device will be considered. In this mode of operation, the volumetric force distribution per unit mass is assumed to be constant over time, and each reservoir is assumed to be in thermal equilibrium with its surroundings. The purpose during this mode of operation is to establish a temperature difference between point a in the first thermal storage volume and point D in the second thermal storage volume, where point a and point D are on the same equipotential surface defined by the first potential level.

According to the invention, at least one heat exchange device is configured to place a point B in the first thermal medium in thermal contact with a point C in the second thermal medium. Conventionally, points B and C are on the same potential plane defined by the second potential level. The second potential level may be greater than or less than but not equal to the first potential level. Since this mode of operation assumes thermal equilibrium, the temperatures at points B and C are equal. Note that the presence of the heat exchange means is a matter of definition. The definition of first thermal medium or second thermal medium may be extended to include heat exchange means. The method may be advantageous in embodiments where different heat exchange devices are not readily identifiable. In the example, the thermal medium and the storage volume may be defined in such a manner that the B point and the C point coincide.

According to the invention, the defining material properties of the first thermal medium in the first reservoir are configured relative to the defining material properties of the second thermal medium in the second reservoir in such a way that the changes in temperature or some other specific property of interest are not the same between the points a and B in the first reservoir and between the points D and C in the second reservoir. A "defined material property" is defined as a property of the thermal medium that determines the change in the material property of interest for a given change in potential of a given thermal medium. The foregoing object is satisfied due to equal temperatures at points B and C and the difference in temperature change between points a and B and the temperature change between points D and C.

Note that the definition of the extent of the thermal storage volume or the boundary between the first thermal medium and the second thermal medium is a matter of definition and is not limited to the geometry or configuration of a particular device, or discontinuity in the type of material that spatially occupies a given area. As previously mentioned, the thermal medium may comprise many different types of materials, where the materials may be present as a mixture, or as a collection of different materials or different phases of the same material. Along varying potential levels, a particular thermal medium may be composed of different types of materials. For example, the thermal medium may be a solid such as copper for a range of potential levels, and a gas such as air along a different range of potential levels within the associated reservoir.

The foregoing operational principles will now be described in the context of the simplified example embodiment shown in fig. 1. The first thermal medium is the material C16 in the third bank 18, and the second thermal medium is the material D17 in the fourth bank 19. The materials C16 and D17 are ideal gases to be insulated by the insulation 15. For simplicity, it is assumed that these reservoirs are completely insulated along the length of the reservoir. Recall that there is a volumetric force per unit mass acting on material C16 in the third reservoir 18 and material D17 in the fourth reservoir 19, wherein for simplicity the volumetric force per unit mass of the two reservoirs is equal, constant in time and constant in direction and magnitude throughout each reservoir, and oriented vertically downwards. A height z can be defined which decreases linearly towards the bottom of the page along the direction vector of the volume force per unit mass, i.e. in a vertically downward direction. Since the volumetric force per unit mass is constant, all points within the thermal medium at the same height z within the reservoir are on the same equipotential surface.

In the aforementioned mode of operation, it is assumed that all four storage banks shown in fig. 1 are in thermal equilibrium, i.e. the heat flow between any two storage banks is zero. In such a mode of operation, the purpose of the device described is to establish a temperature difference between the station 10, i.e. point a, in the third store 18 and the station 11, i.e. point D, in the fourth store 19. Note that points a and D are on the same equipotential surface defined by the first potential level. This is evident from the fact that the height z of the station 10 is equal to the height z of the station 11.

In the aforesaid equilibrium configuration, the heat exchange device 20 ensures that the temperature at station 21, point B, is equal to the temperature at station 22, point C. As previously mentioned, the positions of the

stations

21 and 22 along the height z are equal and the points B and C are on the same equipotential surface defined by the second potential level. In this case, the second potential level is lower than the first potential level.

The properties of the ideal gas within the third 18 and fourth 19 reservoirs vary adiabatically along the vertical length of the reservoirs due to thermal insulation and volumetric force per unit mass. Therefore, as the height z of the element of the material in the reservoir, such as the material C16 in the third reservoir 18, decreases, the temperature of the element increases. In this simplified model, the temperature increases linearly as the height z decreases within the reservoir. In this case, the material property of interest is temperature, while the defining material property of an ideal gas is the specific heat capacity at constant pressure. For other embodiments, such as the case where the material in the reservoir, such as material D17 in fourth reservoir 19, is not an ideal gas but a solid, other material properties may affect the change in temperature of the material along the height z of the associated reservoir. In the apparatus of FIG. 1, the configuration defining the material properties includes selecting as material C16 a material having a specific heat capacity and a constant pressure different from the specific heat capacity and the constant pressure of the selected material D17. The sign and magnitude of the difference between material C17 and material D17 defining the material property is determined by the expected sign and magnitude of the difference in the material property of interest, i.e., the change in temperature. In FIG. 1, the change in the material property of interest is measured between

stations

10 and 21 for material C17 and between

stations

11 and 22 for material D17.

The temperature change between station 10 and station 21 is not equal to the temperature change between station 11 and station 22 due to the difference in material properties defined between material D17 and material C16. Thus, the temperature at station 10 is not equal to the temperature at station 11. The object is thus met. Note that heat exchange device 3 ensures that the temperature at station 10 is equal to the temperature at station 9 in thermal equilibrium, and heat exchange device 6 ensures that the temperature of the heat at station 11 is equal to the temperature at station 12 in equilibrium. Thus, in thermal equilibrium, the temperature at station 9 is also not equal to the temperature at station 12. When there is a slight offset from the equilibrium configuration, the device shown in FIG. 1 will have a tendency to revert to the equilibrium configuration.

Consider a configuration in which the temperature at station 9 is lower than the temperature at station 12 when all four of the described storage volumes are in thermal equilibrium. In this case, the temperature at station 10 is equal to the temperature at station 9, and the temperature at station 11 is equal to the temperature at station 12. The specific heat capacity of material C16 at constant pressure was lower than that of material D17. For example, material C16 may be argon and material D17 may be air. Assuming that material C16 and material D17 are in thermal equilibrium at

stations

21 and 22, the temperature at station 10 must be lower than the temperature at station 11.

This situation is shown in fig. 2. The y-axis of the graph in fig. 2 is the height z. Note that, in this case, the unit of the height z is arbitrary. Line 25 indicates the change in the volumetric force per unit mass along the height z, where the volumetric force per unit mass has been normalized by its value at the point where the height z is zero. Similarly, line 26 describes the variation of the normalized temperature of material D17 in fourth reservoir 19 along height z, wherein the temperature has been normalized by its value at station 11. Line 27 illustrates the variation of the temperature of the material C16 in the third reservoir 18 along the height z, wherein the temperature has also been normalized by the value of the temperature of the material D17 at the station 11. As shown in fig. 1 and 2, station 11 depicts the state of material D17 at a point where height z is zero, while station 22 specifies the state at the minimum height z. Station 10 and station 21 mark the respective states of material C16.

In this configuration, the device shown in fig. 1 can be used as an artificial heat reservoir for the first storage volume 2. Consider the following: the first storage volume 2 is the interior of the refrigeration unit, and the material a1 includes air contained in the interior of the refrigeration unit as well as other materials, such as items to be refrigerated. The second storage volume 7 may be a room in which the refrigeration unit is located, and the material B8 may be air contained in the room. Consider an initial configuration in which all four banks are in thermal equilibrium, similar to the situation shown in fig. 2. Now consider the instantaneous increase in temperature in the first storage volume 2, which may be caused by the articles to be cooled being placed in the refrigeration compartment. The deviation from the initial equilibrium condition results in a momentarily larger temperature at station 9 than at station 10. Thus, the heat flows through the heat exchange device 3, which in turn increases the temperature at the station 10. Similarly, the temperature increase at station 10 propagates to station 12 via thermal medium C16, heat exchange device 20, thermal medium D17, and heat exchange device 6. This flow of heat from the first storage volume 2 to the second storage volume 7 via the third storage volume 18 and the fourth storage volume 19 will continue until thermal equilibrium is reached again.

In another embodiment, the device shown in fig. 1 can be used as an artificial heat storage for the first storage volume 2. Consider a configuration in which the temperature at station 9 is higher than the temperature at station 12 when all four of the described storage volumes are in thermal equilibrium. As previously described, the temperature at station 10 is equal to the temperature at station 9, and the temperature at station 11 is equal to the temperature at station 12. In this embodiment, the specific heat capacity of material C16 at constant pressure is greater than the specific heat capacity of material D17 at constant pressure. For example, material C16 may be helium and material D17 may be air. Assuming material C16 and material D17 are in thermal equilibrium at

stations

21 and 22, the temperature at station 10 must be greater than the temperature at station 11. This scenario is shown in fig. 3. Line 28 shows the variation of the temperature of material C16 in the third reservoir 18 along the height z, wherein the temperature has also been normalized by the temperature value of material D17 at station 11. The operation of the device shown in fig. 1 as an artificial heat storage body is in principle similar to the operation of the device as an artificial heat storage body described previously.

Note that for some embodiments, the temperature variation between station 21 and station 10 is negligible. This may be the case: for some gases with very large specific heat capacity at constant pressure, or for some liquids and some solids. For example, element 23 of heat exchange device 20 may be rigidly connected to element 4 of heat exchange device 3 by solid material C16, wherein the solid material may be the same as the material of heat exchange element 23 and heat exchange element 4.

Fig. 4 shows another exemplary embodiment. In this case, the volumetric force per unit mass is generated by centripetal acceleration of the material C34 inside the third reservoir 33, which is confined by the internal thermal insulation means 56. The material D36 inside the fourth storage volume 35, which is also confined by the internal insulation 56, experiences the same volumetric force distribution per unit mass as the material C34. Note that the magnitude and direction of the volumetric force per unit mass is not constant throughout the

reservoirs

33 and 35, but is determined by storing local values of centripetal and coriolis accelerations, among other possible accelerations. As in fig. 1, there are a first bank 29 including a material a30 and a second bank 31 including a material B32. The heat exchanger 37 is configured to exchange heat between the first storage body 29 and the third storage body 33. In order to transfer heat from the elements of one heat exchanger in the first reservoir to the elements of the other heat exchanger in the third reservoir, electromagnetic waves are exchanged between the outer plate 40 and the inner plate 41. The plates may be made of a solid material specifically selected and configured for a given desired heat flux. The material may be a metal such as copper. Although the heat exchanger 42 is similarly configured and performs a similar function for the fourth reservoir 35 and the second reservoir 31.

Stations

9, 10, 21, 22, 11 and 12 in fig. 1 correspond to

stations

50, 52, 53, 55, 54 and 51 in fig. 4, respectively. Similar to the heat exchange device 20 in fig. 1, the heat exchange device 47 is configured to promote heat flow between the third storage body 33 and the fourth storage body 35. The device shown in FIG. 4 is cylindrically symmetric about the axis of rotation 64 of the inner insulation 56. The inner insulation 56 is isolated from the outer insulation 57 by a gap 65, in this embodiment the gap 65 may be described as a vacuum. In other embodiments, the gap may comprise a different material, such as a fluid. The inner heat insulation device 56 accommodates the third storage body 35 and the fourth storage body 35, and is configured to rotate about a shaft 64 within the outer heat insulation device 57. In this particular embodiment, the mechanical support of the internal insulation 56 is provided by magnetic levitation means. In other embodiments, conventional mechanical bearings, such as roller bearings or fluid bearings, may be used. The magnetic levitation means comprise an axially inner magnet 61 and an axially outer magnet, as well as a radially inner magnet 63 and a radially outer magnet 62 for stability. The motor with stator 59 and rotor 58 provides angular acceleration and deceleration as well as the torque required to overcome any sources of friction. In order to transmit the angular acceleration to the material contained in the

storage bodies

35 and 33, there may be baffles radially arranged within these storage bodies. In other words, there may be a plurality of circumferentially arranged chambers. In this case, each chamber itself may be considered a reservoir. Alternatively, the angular acceleration may also be transmitted using viscous friction between the walls of the reservoir and the material within the reservoir. The operation of the device shown in fig. 4 follows the same principles and concepts set forth in the context of fig. 1.

Fig. 6A-6B are cross-sectional views of one example apparatus shown with a graph of normalized material properties as a function of position along the length of the apparatus at a particular point in time.

An example device includes a completely enclosed chamber 117, the chamber 117 containing a working material that may be a fluid or a solid, or a combination thereof. The working fluid may be a liquid such as water or a gas such as air. The working fluid may also be a mixture of steam and gas, such as a combination of water vapor and liquid water. The working fluid or solid may be any suitable material, where suitability is a function of material properties, as may be assessed by one skilled in the art. In the described example embodiment, the working fluid is an ideal gas. The chamber 117 forms a closed system around the working material. In other embodiments, the working material and the device employing it may form an open system.

The chamber 117 is insulated from the environment by the insulating material 110, which ideally prevents any accidental heat exchange between the working material in the chamber 117 and the external environment.

Elements of the external environment are able to perform work on the work material via work exchange device 107. For example, such elements may comprise a separate actuator, such as a motor. For simplicity, the actuator and its associated energy supply or storage volume are not shown. Such devices are well known in the art. In this particular embodiment, the work exchange device 107 is a piston having a head 109 and a circular shaft 108. In other embodiments, the work exchange device 107 may take other forms, such as an axial turbine or a nozzle. For example, these examples are particularly applicable where the working material and the device employing the working material form an open system. Furthermore, the work exchange device 107 is thermally insulated in order to prevent or minimize any accidental heat exchange between the working material in the chamber 117 and the external environment.

The piston head 109 features a surface that contacts the working material and an opposite surface that connects to the shaft 108. In the depicted embodiment, the opposite surface is in contact with the outer material 118. In other embodiments, for example, the opposing surface is isolated from the surrounding material 118 by an extension of the insulating material 110. Thus, the volume created by the opposing surfaces and the extension of the insulating material represents the "second chamber". The second chamber and outer material 118 will be part of the external environment as previously described. In some embodiments, the second chamber is evacuated. This may improve the effectiveness of the insulation and reduce the energy consumed by friction during movement of the piston. In other embodiments, the second chamber is pressurized, wherein the pressure is independent of the pressure of the surrounding material. The pressure of the second chamber may be modified in such a way that an improved efficiency of the actuator operating the power exchanging device 107 is obtained. For example, the pressure of the second chamber may be controlled in a manner in which the average force exerted by the actuator on the working material in the chamber 117 during one thermodynamic cycle is reduced or substantially zero. This may reduce the average power consumption of the actuator. Alternatively, this function may be performed by a separate device, such as an adjustable spring configured to exert a desired average force on the piston during one cycle.

There is a first internal heat exchange device 112 at location 119 in the chamber 117. Similarly, there is a second internal heat exchange device 115 at a location 120 in the chamber 117. There is also a first external heat exchange means 111 and a second external heat exchange means 114. In the described example, the heat exchange means are realized by a coil having a high thermal conductivity. An example material for the coil may be copper. In other embodiments, the heat exchange device may include a second working fluid specifically selected for heat exchange. The heat exchange device may also include a pump or other actuator for moving the second working fluid through the heat exchange device to facilitate a higher rate of heat transfer between the heat exchange device and the working or outer material 118. The second working fluid need not be contained by the heat exchange device in the closed system. For example, the outer material 118 may serve as a second working fluid that is allowed to enter and exit the heat exchange device in an open thermodynamic system. The second working fluid may pass through the heat exchange device via natural or forced convection. The heat exchange device may also be particularly suitable for radiant heat transfer to and from the exterior material 118, or to and from the working material. Numerous alternative types and configurations of heat exchange devices are known in the art. The first heat exchange means and the second heat exchange means need not be identical.

The connection between the external heat exchange means and the corresponding internal heat exchange means may be modified so that the heat flow between the two means may be controlled. In the described embodiments, each external heat exchange device may be disconnected or insulated from the corresponding internal heat exchange device. As shown, 116 may form an insulating gap between the second external heat exchange device 114 and the second internal heat exchange device 115. Similarly, as shown in fig. 7B, an insulating gap 113 may also be formed between the first external heat exchange device 111 and the first internal heat exchange device 112. In this embodiment, therefore, heat cannot flow between the external heat exchange means and the corresponding internal heat exchange means when they are disconnected. In other embodiments, the amount of heat flow between the external heat exchange device and the corresponding internal heat exchange device is modified without the necessity of achieving a complete disconnection or insulation between the two heat exchange devices. The heat flow can be modified in a number of ways. For example, the surface area of the external heat exchange device may be reduced in order to reduce the rate of heat transfer between the working material within the inner chamber 117 and the external material 118. Where the heat exchange device employs a second working fluid, the flow rate of the second working fluid through the heat exchange device may be modified so as to control the rate of heat transfer between the chamber 117 and the outer material 118. Alternatively, the second material having a different thermal conductivity may be inserted into or removed from the thermal loop connecting the outer and respective inner heat exchange devices. For example, when the thermal conductivity of the second material is lower than that of the material used in the heat exchange device, the heat transfer rate between the chamber 117 and the exterior material 118 is reduced when the second material is inserted. For a given temperature difference between the two heat storage volumes, i.e., the working material and the external material 118, there are many other configurations and methods that can be used to vary and control the heat flow of the heat exchanger.

The outer material 118 may also be any type of material, such as a gas, a liquid, or a solid. For example, the external material may be the contents of a thermal storage body to be cooled, for example, by the inner chamber of a refrigerator. When the described device is operated as an artificial heat storage body, the outer material 118 is the heat storage body to be heated. The outer material 118 may also be modeled as an object capable of emitting or absorbing electromagnetic waves.

According to an exemplary embodiment, a force per unit mass acts on the working material in chamber 117, and the force may be a volumetric or mechanical force. In fig. 6A to 6B, the force is a volume force per unit mass. In a simplified example, the volumetric force per unit mass is constant in location and time throughout the chamber 117. This configuration is shown in fig. 6A-6B, where the volumetric force per unit mass is directed vertically downward toward the bottom of the page. Note that this description of direction is relative to the page only, and is independent of the orientation of the device relative to a system of inertia, such as that on the earth's surface. The graphs on the left of fig. 6A-6B illustrate the resultant change in the thermodynamic properties of the working material along the length "z" of the chamber 117, where the length is measured parallel to and indicated by the y-axis of the graphs. In this graph, line 104 indicates the change in volumetric force per unit mass along the length z, where the volumetric force per unit mass has been normalized by its value at the point where the length z equals zero. Similarly, line 103 depicts the normalized specific volume change along length z, while line 105 shows the normalized temperature change along length z, and line 106 shows the normalized pressure change along length z. In this example, the first external heat exchange device 111 is connected to the first internal heat exchange device 112. Thus, the temperature of the working material inside the chamber 117 at the location 119 is substantially equal to the temperature of the outer material 118 at that location. In the depicted example, the temperature of the outer material 118 is uniform in space and time for simplicity. As the volumetric force acting on the working material is directed toward the bottom of the page in fig. 6A-6B, the working material is compressed as the length z decreases. Therefore, the pressure rises and the specific volume decreases. In this case, the insulating material 110 around the chamber 117 ensures a substantially adiabatic compression, resulting in an increase in temperature at location 120 as compared to location 119, as indicated by line 105.

In other embodiments, the walls may not be completely insulated, resulting in a distribution of thermodynamic properties between the insulated box and the isothermal box. In other embodiments, the force need not be constant in space or time in chamber 117.

In other embodiments, the force generation device comprises a work exchange device. In other words, the force generation device or mechanism may be configured relative to the chamber 117 in such a way that the force may vary over time, such that work may be performed on or by the working material. For example, during a portion of the time that the purpose of the work exchange device is to compress the working material, the force inside the chamber 117 may increase. In the whole compression process, the volume force driving mechanism applies work to the working material. An extension procedure involving a work exchange device would follow a similar principle of operation.

As previously mentioned, the volumetric force may be generated in a variety of ways. One type of volumetric force is the force of gravity acting on the working material.

Another type of volumetric force is an inertial force, which can be generated by accelerating the described device comprising the chamber 117 and the insulating material 110 in an inertial frame of reference. When accelerating the device in a vertically upward direction toward the top of the page with a constant acceleration in the inertial system, the working material inside the chamber 117 will experience an apparent acceleration relative to the chamber 117 and the insulation material 110, wherein the apparent acceleration is oriented vertically downward toward the bottom of the page. Inertial forces may be generated by linear acceleration, i.e., linear motion of the device along a line in the inertial frame. Inertial forces may also be generated by angular acceleration, i.e., movement of the device along a curved path. In general, inertial forces may be generated by any acceleration motion in an inertial frame. Consider the foregoing embodiment in which the described device undergoes circular motion in the inertial system, in which the radius and angular velocity remain constant. In the embodiment shown in fig. 6A-6B, the axis of rotation may be, for example, parallel to and coincident with the centerline of the circular piston shaft 108. Note that in this embodiment, the centripetal acceleration varies linearly with the radius. If it is desired that the volumetric force per unit mass of the working material be substantially uniform, the described device may be at a larger radius where the radial dimension of the device is only a fraction of the radius. For example, in fig. 6A-6B, the radius may be increased by placing the axis of rotation further up toward the top of the page. In other embodiments, the directional vector of the axis of rotation may have a component parallel to the plane described by the vector that is directed perpendicularly out of the page containing fig. 6A-6B, and the vector is parallel to the centerline of the piston shaft 108. Other embodiments may have different positions and orientations of the axis of rotation, as well as different rotational speeds. These parameters may also vary over time.

Another type of volumetric force is an electromagnetic force. For example, the elements of the working material in the chamber 117 may be configured to be electrically charged. In the context of a material, for example, the term "element" refers to a constituent part of a material, such as a different or specific set of sub-atomic particles, atoms, molecules, or molecules. In the case of a gas, for example, atoms or molecules may be positively or negatively ionized. The working material may also comprise a collection of mobile electrons. Note that the collection may be contained in a solid such as a conductor, or the collection may be described as a gas. By applying an electric field within the chamber 117, a volumetric force may be generated on the charged element of the working material. When at least a subset of these elements are movable, in the sense that the elements can move relative to each other and be compressed, a pressure and temperature gradient can be generated within the chamber 117 according to the principles described previously.

Embodiments employing other types of forces or combinations thereof are within the scope of the invention. In one embodiment of the invention, a method for exchanging heat between two storage bodies is provided, wherein the range of the relative average temperature of the storage bodies for which heat can flow in a specific direction is increased compared to heat exchangers of the prior art. In the following method, the first reservoir is denoted "working material" and the second reservoir is denoted "external reservoir". The method comprises the following steps: subjecting the material defined as the working material in at least one of the two reservoirs to a volumetric force per unit mass such that a temperature difference can be generated between at least two different points in the working material, wherein the two points can be different in space or time; surrounding at least a portion of the working material by means of an insulating material, wherein the enclosing and insulating material is configured to inhibit or reduce heat flow in an undesired direction between the working material and the external reservoir, and to promote heat transfer in a desired direction between the external reservoir and the working material, wherein promoting may comprise thermally connecting a point in the working material and a point in the external reservoir such that a temperature difference between the two points enables heat to flow in the desired direction between the two reservoirs, wherein thermally connecting may comprise placing the two reservoirs in physical contact at the two points, wherein physical contact means that electromagnetic radiation emitted by one reservoir is to be absorbed by the other reservoir, wherein the two points may or may not be substantially coincident, or the physical contact may mean that the respective material elements are in direct contact so as to allow heat conduction to occur, wherein the two points are substantially coincident, or the physical contact may refer to exchanging material between the storage bodies during convection, or placing at least one heat exchange device between the two points, wherein the heat exchange device is configured to enable heat transfer between the external storage body and the working material in a desired direction, wherein the two points may or may not be substantially coincident. Note that the aforementioned external reservoir may also be subjected to forces in a similar manner to the working material. This may further increase the range of relative average temperatures between the reservoirs for which heat may flow in a particular direction between the reservoirs. In some embodiments, the difference between the average temperature of the thermal storage body and the average temperature of the thermal reservoir may be less than or equal to zero. For example, an artificial heat reservoir or an artificial heat storage body can be operated using the method. As shown in the figures and as described in the following paragraphs, the method may also be applied to the operation of a heat pump such as a refrigerator or a heat engine.

Note that in the case where the external storage body is in physical contact with the working material, the material properties of the external storage body and the working material may need to be specifically configured. For example, when placed in direct contact, if a stable equilibrium configuration is desired, the pressure of the outer reservoir at the contact location should match the pressure of the working material. Measures can be taken if diffusion of the two reservoirs is to be avoided or reduced. For example, the material of one reservoir may be in a different phase than the material of the other reservoir. For example, one reservoir may contain solid material, while the other reservoir may contain gaseous material.

FIG. 5 is a graph of pressure versus specific volume indicating changes in the parameter at different locations within an example apparatus and at different points in time during an example method of operation.

In fig. 7A-7H, cross-sectional views of the example apparatus of fig. 6A-6B are shown in different configurations according to different points in time during the example method of operation shown in fig. 5.

In fig. 7A, the example apparatus of fig. 6A-6B is shown in a configuration that may be described as follows. The first external heat exchange device 111 and the first internal heat exchange device 112 form a closed thermal circuit, allowing heat exchange between the external material 118 and the working material in the chamber 117. The thermodynamic properties of the working material are constant in time in the configuration shown in fig. 7A, and the outer material and the working material are in thermal equilibrium. Therefore, the temperature of the working material at the position 119 in fig. 6A to 6B is equal to the temperature of the exterior material 118. The thermodynamic state 81 of the working material at position 119 in fig. 6A-6B is indicated in fig. 7A and shown in fig. 5. In this configuration, there is an insulating gap 116 between the second external heat exchange device 114 and the second internal heat exchange device 115. A uniform volumetric force per unit mass acts on the working material in chamber 117, wherein the volumetric force is directed vertically downward toward the bottom of the page. In this simplified example, the insulating material 110 prevents any heat exchange between the working material and the exterior material 118. The insulating material 110 also spatially confines the working material, i.e., it exerts pressure on the working material. In other embodiments, the working material may be constrained by the action of volumetric forces or interactions with other elements of the working material. As a result, the working material is compressed along the negative length z of the chamber 117, as indicated in the graph on the left side of fig. 6A-6B. Since there is no heat exchange with the environment, the compression can be modeled as adiabatic compression, resulting in a temperature increase along the negative length z, as shown in 6A to 6B. This adiabatic compression is also illustrated by the thin dashed line 96 in fig. 5. The thermodynamic state 85 of the working material at location 120 in fig. 6A-6B is shown in fig. 7A and in fig. 5. The average thermodynamic state 89 of the entire working material enclosed in the chamber 117 in the configuration shown in fig. 7A is also shown in fig. 5. As shown, the piston of the work exchange device 107 is in a retracted position.

In fig. 7B, the equilibrium configuration shown in fig. 7A has been disturbed by the closed insulation gap 116, such that the second external heat exchange arrangement 114 and the second internal heat exchange arrangement 115 can form a closed thermal loop. The first external heat exchange device 111 has also been disconnected from the first internal heat exchange device 112 by means of the insulating gap 113. In the configuration shown in fig. 7A, thermodynamic state 85 is characterized as having a higher temperature than thermodynamic state 81, thermodynamic state 81 is characterized as having the same temperature as exterior material 118. Thus, after the insulating gap 116 is eliminated, there is a transient temperature difference between the working material and the outer material 118 at state 85 at location 120. As indicated by "QOUT," heat will flow from the working material to the outer material 118 until a new equilibrium configuration is reached.

Fig. 7C shows the new balancing configuration. In this particular example, it is assumed for simplicity that the temperature change of the outer material 118 is negligible throughout the process. This is a valid assumption when the ratio of the mass of the outer material 118 to the mass of the working material is large, or when there is an external energy storage volume or bank that regulates the internal energy of the outer material 118. In other embodiments, there may be a non-negligible change in temperature of the outer material 118 during a complete cycle. This is desirable when the device is to operate as an artificial thermal storage body or reservoir. Similar to the configuration in fig. 7A, the temperature of the thermodynamic state 86 is now equal to the temperature of the outer material 118. In fig. 5, this is illustrated by the fact that state 86 and state 81 are on an isotherm 94. Due to the effect of the volumetric force and the temperature boundary conditions provided by the thermodynamic state 86, the temperature at the thermodynamic state 82 is lower than the temperature at the state 86. Adiabatic line 97 shows the change in thermodynamic properties between state 86 and state 82 along the length z of the device. Note that the position of the piston head 109 is unchanged in fig. 7A to 7C. Since the working material has lost thermal energy without a volume change, the average pressure and temperature of the working material in chamber 117 has been reduced while the average specific volume remains constant. Thus, the new average thermodynamic state 90 is connected by a vertical line to the previous average thermodynamic state 89 in fig. 5. In other embodiments, the lines need not be vertical, but may have any other orientation, such as a horizontal orientation.

In fig. 7D, work is performed on the work material using work exchange device 107, where work is indicated by "WIN". In this particular embodiment, the actuator employs a piston head 109 to compress the working material. Note that the configurations of the first heat exchanging arrangement and the second heat exchanging arrangement are not changed as compared with fig. 7B to 7C. Thus, any increase in the temperature of the working material due to work performed on the working material results in an increase in the heat flow from the working material through the second internal heat exchange device 115 and the second external heat exchange device 114 to the external material 118, as indicated by "QOUT". The rate of work input into the working material is controlled such that it is substantially equal to the heat flow from the working material to the outer material 118 at all times during compression. In this case, the compression is isothermal. In other embodiments, the compression need not be isothermal, as will be explained later.

Fig. 7E shows the new equilibrium position once the work exchange device 107 is no longer performing work on the work material. As in fig. 7C to 7D, the temperature at state 87 is equal to the temperature of the exterior material 118. In this embodiment, the temperature at state 83 is substantially equal to the temperature at state 82. An isotherm 95 connects state 82 and state 83. The new average thermodynamic state 91 is also shown in fig. 5. The adiabatic line 98 describes the change in thermodynamic properties between

states

83 and 87 along the length z of the device. Note that the temperature at state 83 is lower than the temperature at state 87, and therefore lower than the temperature of exterior material 118.

In fig. 7F, the balanced configuration shown in fig. 7E has been disturbed by the closed insulation gap 113, which enables the first external heat exchange device 111 and the second internal heat exchange device 112 to form a closed thermal loop. The second external heat exchange means 114 has also been disconnected from the second internal heat exchange means 115 by the insulating gap 116. Due to the instantaneous temperature difference between the working material and the outer material 118 at state 83 at location 119, heat will flow from the outer material 118 to the working material until a new equilibrium configuration is reached. The heat flow is indicated by "QIN".

Fig. 7G shows the new balancing configuration. The temperature at state 84 is now equal to the temperature of the outer material 118. Adiabatic line 99 shows the change in thermodynamic properties between

states

84 and 88 along the length z of the device. Note that the position of the piston head 109 is unchanged in fig. 7E to 7G. The new average thermodynamic property 92 is shown in fig. 5.

In fig. 7H, the working material does work on the work exchange device 107, where work is indicated by "WOUT". Note that the actuator of the operation power exchanging device 107 is configured to be able to perform work on the working material, and to be able to extract work from the working material. Thus, the actuator and its associated energy storage body are configured to extract or recover energy from the work performed by the working material on the work exchange device 107. Following a similar principle of operation described in the context of fig. 7D, the expansion process shown in fig. 7H and 5 is isothermal. Thus, any decrease in the temperature of the working material due to expansion of the working material results in an increase in the heat flux from the outer material 118 through the first outer heat exchange device 111 and the first inner heat exchange device 112 into the working material, as indicated by "QIN". The thermodynamic properties of the working material at location 120 throughout the isothermal expansion are depicted by isotherm 93 in fig. 5.

Once the piston head 109 has reached its original position, the movement of the piston may stop. The new balanced configuration will then be the same as the initial configuration shown in fig. 7A. Thus, a complete, repeatable thermodynamic cycle has been described. The foregoing process of forming the cycle may also be performed in the reverse order.

The thermodynamic properties of the working material at location 120 during the entire cycle are depicted by the thick dashed line 102 in fig. 5. The thermodynamic properties of the working material at location 119 are depicted by the thick dashed line 100 in fig. 5. The average thermodynamic properties of the working material in chamber 117 are depicted by thick line 101.

Note that the aforementioned isothermal compression or expansion need not be isothermal. For example, the aforementioned isothermal compression or expansion may be adiabatic. In the adiabatic case, the shape or configuration of the thermodynamic property shown in fig. 5 would have to be altered or adapted to the new shape. For example, the temperature of the corresponding state 81 at the new shape may be configured to be lower than the corresponding temperature of the exterior material, while the temperature of the corresponding state 84 at the new shape may be less than or equal to the temperature of the corresponding exterior material. This will ensure a closed line similar to line 100 in fig. 5. In the aforementioned adiabatic case, the other closed lines shown in fig. 5 can be adjusted accordingly.

In fig. 5, the values of pressure and specific volume shown on the shaft are arbitrary and are selected only to provide examples. The values of pressure and specific volume are not intended to limit the scope of the present invention to a particular type of fluid or to a particular range of specific volume pressures.

FIG. 8 is a graph of material properties of an example embodiment during an example method of operation. The horizontal x-axis 167 represents the specific volume of the working material in question, and the vertical y-axis 168 represents the pressure of the working material. Note that the illustrated elements are arbitrary and included for exemplary purposes only, and are not intended to limit the scope of the present invention to a particular method of operation or a particular type of working material.

Fig. 8 shows a first cycle and a second cycle. The first cycle includes: adiabatic compression 151 between the first station 150 and the second station 155, isobaric expansion 152 with heat addition between the second station 155 and the third station 156, adiabatic expansion 153 between the third station 156 and the fourth station 157, and isobaric compression 154 with heat removal between the fourth station 157 and the fifth station, as with the first station 150. In some embodiments, the first station 150 describes the properties of the working material in a free stream (i.e., at ambient pressure and specific volume), and the fourth station 157 generally describes the properties of the working material at the thermodynamic device outlet or exhaust. Thus, isobaric compression 154 may occur in the wake, i.e., downstream, of embodiments of the present invention. In other embodiments, the first cycle may be a closed cycle. Note that the first cycle is similar to a conventional brayton cycle. In other embodiments, the first cycle may be similar to the otto cycle. In other embodiments, the first cycle may be similar to a diesel cycle. Many different shapes or forms of the first cycle are easily conceivable. For example, the compression between

stations

150 and 155 may be isothermal rather than adiabatic.

The second cycle includes: adiabatic expansion 159 between first station 150 and second station 163, isobaric compression 160 between second station 163 and third station 164 involving heat removal, adiabatic compression 161 between third station 164 and fourth station 165, and isobaric expansion 162 between fourth station 165 and fifth station, which are identical to first station 150. In some embodiments, the first station 150 describes the properties of the working material in a free stream (i.e., at ambient pressure and specific volume), and the fourth station 165 generally describes the properties of the working material at the outlet or exhaust pipe of a thermodynamic device such as a turboshaft engine. Thus, isobaric expansion 162 may occur in the wake, i.e., downstream, of embodiments of the present invention. In other embodiments, the second cycle may be a closed cycle.

Both the first cycle and the second cycle produce a positive mechanical work output.

In some embodiments described by fig. 8, the rate of heat removed from the working material in the second cycle during isobaric compression 160 is substantially equal to the rate of heat added to the working material in the first cycle during isobaric expansion 152. Note that the mass flow rate of the working material in the first cycle need not be equal to the mass flow rate of the working material in the second cycle. In some embodiments, the heat removed from the working material in the second cycle is the same as the heat added to the working material in the first cycle. Heat transfer from the cooler working material between station 163 and station 164 to the hotter working material between

stations

155 and 156 is facilitated by a heat transfer device.

The working material in the first cycle need not be of the same type as the working material in the second cycle. For example, the working material of the first cycle may be air, and the working material of the second cycle may be helium.

In other embodiments, the expansion 159 may alternatively be compression, and the compression 161 may alternatively be expansion, with the pressure at the equivalent second station 163 of the second cycle being lower than the pressure at the second station 155 of the first cycle. In an embodiment, the first cycle produces a net mechanical work output, while the second cycle consumes work. In other words, the working material does work on the environment in a first cycle, and the environment does work on the working material in that particular second cycle. The first and second cycles may be configured in a manner in which the combined power output of the first and second cycles is positive.

FIG. 9 is a graph of material properties of an example embodiment during an example method of operation. Some features of the cycle are shown in fig. 9, and some principles of operation of the associated thermodynamic device have similarities to features and principles of operation described by other figures, and therefore will not be described in detail again in the context of fig. 9, and vice versa.

The horizontal x-axis 193 represents the specific volume of the working material in question, and the vertical y-axis 194 represents the pressure of the working material.

The thermodynamic cycle described comprises: a first adiabatic expansion 187 between the first station 180 and the second station 181, a first isostatic compression 188 to the third station 182, a first adiabatic compression 189 to the fourth station 183, a first isostatic expansion 190 to the fifth station 184, a second adiabatic expansion 191 to the sixth station 185, and a second isostatic expansion 192 to a seventh station equal to the first station 180.

In some embodiments, the first station 180 describes the properties of the working material in a free stream, e.g., air at ambient pressure and ambient specific volume, and the sixth station 185 generally describes the properties of the working material at the outlet or exhaust of the thermodynamic device. Thus, isobaric expansion 192 may occur in the wake, i.e., downstream, of embodiments of the present invention. In other embodiments, the first cycle may be a closed cycle.

The thermodynamic cycle described produces a net positive mechanical work output, i.e., work is done by the working material on the environment.

In some embodiments described by fig. 9, the rate of heat removed from the working material during isobaric compression 188 is substantially equal to the rate of heat added to the working material in the first cycle during isobaric expansion 190. In some embodiments, the heat removed from the working material during isobaric compression is the same as the heat added to the working material during isobaric expansion 190. Heat transfer from the cooler working material between

stations

181 and 182 to the hotter working material between

stations

183 and 184 is facilitated by a heat transfer device.

The working material may be a compressible gas such as air or carbon dioxide. The thermodynamic device performing the compression or expansion process may be, for example, a compressor or a turbine of the axial or centrifugal type. These processes can also be carried out in the piston.

FIG. 10 is a graph of material properties of an example embodiment during an example method of operation. Some features of the cycle shown in fig. 10 and some principles of operation of the associated thermodynamic device have similarities to those described by other figures and will therefore not be described in detail in the context of fig. 10, and vice versa.

The horizontal x-axis 218 represents the specific volume of the working material in question, and the vertical y-axis 219 represents the pressure of the working material.

The thermodynamic cycle described comprises: a first adiabatic compression 212 between the first station 205 and the second station 206, a first equal-pressure expansion 213 to the third station 207, a first adiabatic expansion 214 to the fourth station 208, a first equal-pressure compression 215 to the fifth station 209, a second adiabatic compression 216 to the sixth station 210 and a second equal-pressure expansion 217 to the seventh station, which is equal to the first station 205.

In some embodiments, the first station 205 describes the properties of the working material in a free stream, e.g., air at ambient pressure and ambient specific volume, and the sixth station 210 generally describes the properties of the working material at the outlet or exhaust of the thermodynamic device. Thus, isobaric expansion 217 may occur in the wake, i.e., downstream, of embodiments of the present invention. In other embodiments, the first cycle may be a closed cycle.

The thermodynamic cycle described produces a net positive mechanical work output, i.e., work performed by the working material on the environment, i.e., the thermodynamic device with which the working material interacts.

In some embodiments described by fig. 9, the rate of heat removed from the working material during isobaric compression 215 is substantially equal to the rate of heat added to the working material during isobaric expansion 213. In some embodiments, the heat removed from the working material during isobaric compression 215 is the same heat added to the working material during isobaric expansion 213. Heat transfer from the cooler working material between station 208 and station 209 to the hotter working material between station 206 and station 207 is facilitated by heat transfer means.

Fig. 11 is a schematic diagram of a heat engine or heat pump. Some features of the cycle shown in fig. 11 and some principles of operation of the associated thermodynamic device have similarities to those described by other figures, such as fig. 10 or fig. 15 in particular, and will therefore not be described in detail in the context of fig. 11, and vice versa.

The first thermodynamic cycle comprises: the working material enters an inflow 230 of an expander 231, an output stream 232 of the expander 231 is cooled by a heat transfer device 236, an output stream 237 of the heat transfer device 236 flows to a compressor 238, the compressor 238 is powered by the expander 231 by work "WINTA" 234, and an output stream 239 of the compressor is released to the same storage that provides the inflow 230. For example, the reservoir may be the atmosphere. Thus, the remaining work 233 of the thermodynamic cycle is available as "WOUTA".

An expander such as expander 231 may be performed by any thermodynamic device that can reduce the pressure of the working material. For example, the expander may be a piston, an axial or centrifugal turbine, or a pipe or nozzle. Typically, the working material will do mechanical work on the expander. Typically, a portion of this mechanical work may be recovered in order to do useful work, for example, to power a generator or to generate thrust.

The second thermodynamic cycle comprises: an inflow 241 of working material into the compressor 242, the compressor 242 being powered by an expander 248 by work "WINTB" 244, and an output flow 243 of the compressor 242 being heated by the heat transfer device 236, an output flow 247 of the heat transfer device 236 flowing into the expander 248, an output flow 249 of the expander 248 being released to the same storage providing the inflow 241. For example, the reservoir may be air. The remaining work 250 of the thermodynamic cycle is available as "WOUTB".

Heat flow "QINT" flows through heat transfer device 236.

For some embodiments, the first thermodynamic cycle shown in fig. 8 corresponds to the second thermodynamic cycle shown in fig. 11. For some embodiments, the second thermodynamic cycle shown in fig. 8 corresponds to the first thermodynamic cycle shown in fig. 11.

Fig. 12 is a schematic diagram of a heat pump or heat engine. Some features of the cycle shown in fig. 12 and some principles of operation of the associated thermodynamic device have similarities to those described by other figures, such as fig. 14 or fig. 10 in particular, and therefore will not be described in detail again in the context of fig. 10, and vice versa.

The thermodynamic cycle described comprises: an inflow 260 of working material into a first compressor 261 powered by an expander 267 via a shaft 263 and an output stream 262 of the compressor heated by a heat transfer device 265, an output stream 266 of the heat transfer device flowing into the expander 267, an output stream 268 of the expander 267 cooled by a conventional heat exchanger 269, and an output stream 270 of the heat exchanger 269 flowing into a second compressor 271, the second compressor 271 powered by the expander 267 via the shaft 275, and an output stream 272 of the second compressor released into the same storage volume providing the inflow 260. The hot fluid within the conduit means 274 is circulated by the pump so as to enhance heat transfer from the heat exchanger 269 to the heat transfer means 265. Heat flow "QINT" flows through heat transfer device 265. The remaining work of the thermodynamic cycle is available as "WOUT" 273.

Fig. 13 is a schematic view of a heat pump or heat engine. Some features of the cycle shown in fig. 13 and some principles of operation of the associated thermodynamic device have similarities to those described by other figures, in particular such as fig. 9, and therefore will not be described in detail again in the context of fig. 13, and vice versa.

The thermodynamic cycle described comprises: the working material inflow 290 entering the first expander 291, the output stream 292 of the expander 291 is cooled by a conventional heat exchanger 295, the output stream 296 of the conventional heat exchanger 295 flows into a compressor 297, the compressor 297 is powered by the first expander 291 through a shaft 293 and/or by the second expander 301 through a shaft 305, and the output stream 298 of the compressor 297 is heated by a heat transfer device 299, the output stream 300 of the heat transfer device 299 flows into the second expander 301, and the output stream 302 of the second expander 301 is released into the same storage providing the inflow 290. The thermal fluid within the conduit arrangement 304 is circulated by a pump to enhance heat transfer from the heat exchanger 295 to the heat transfer device 299. The heat flow "QINT" flows through heat transfer device 299. The remaining work of the thermodynamic cycle is available as "WOUT" 303.

In other embodiments, the position of the exchanger may be reversed from the position of the heat transfer device. In other words, the heat exchanger may be downstream of the compressor 297 and upstream of the second expander 301, and the heat transfer device may be downstream of the first expander 291 and upstream of the compressor 297.

In general, heat may be transferred from the output stream 292 to the output stream 298 via any number of heat exchangers and any type of heat transfer mechanism, such as radiation, natural or forced convection or conduction, as long as at least one suitably configured heat transfer device, such as the heat transfer devices shown in fig. 1, 4, or 15, is between the output stream 292 and the output stream 298 along a thermal path. The same applies to fig. 11 and 12. In the example shown in fig. 13, for example, heat is transferred from the output stream 262 via forced convection of the hot fluid through the conduit arrangement 304 and then into the heat transfer device 299 via conduction, from which heat is transferred to the output stream 298 via conduction, radiation.

FIG. 14 is a cross-sectional view of one embodiment of the present invention. Some features of the cycle shown in fig. 14 and some principles of operation of the associated thermodynamic device have similarities to those described by other figures, such as fig. 12 and 10 in particular, and therefore will not be described in detail in the context of fig. 14, and vice versa.

The engine 320 shares features and principles of operation with a conventional turbojet or turboshaft engine. The engine 320 includes a duct arrangement 321 and an internal arrangement 322.

Several components of the engine 320 are substantially axially symmetric about an axis 369.

The bulk material 323 of the engine 320 may include a variety of different material types. For example, bulk material 323 may include a metal such as titanium or aluminum, a ceramic, or a composite such as a carbon fiber composite or a glass fiber.

Inner device 322 includes an optional annular passage 342 between annular inlet 341 and annular outlet 343, and between outer inner surface 349 and inner surface 350. The outer surface 348 of the pipe fitting 321 is indicated.

The working material flows through the channel 342 from the inlet 341 to the outlet 343. The working material may be a compressible fluid. For example, the fluid may be a gas such as air or carbon dioxide. Note that liquids such as water are also compressible.

After passing through the inlet 341, the working material flowing through the passage 342 then sequentially encounters the first compressor 324, the first heat exchanger 326, the turbine 332, the second heat exchanger 334, and the second compressor 340 before exiting through the outlet 343.

In this embodiment, the first compressor 324 and the second compressor 340 may be described as axial flow compressors. Other embodiments may include other types of compressors. For example, the compressor may be a centrifugal compressor.

In this embodiment, the turbine 332 is an axial turbine. Other embodiments may include other types of turbines. For example, the turbine may be a centrifugal turbine.

The compressor and turbine may include a plurality of rotor blades, such as rotor blade 346, and a number of stator blades, such as stator blade 347. The rotor blades of the rotor disk are arranged circumferentially about the axis of rotation, i.e. shaft 369. The stator vane regions are also circumferentially disposed. The rotor disk and the downstream stator disk form a stage. In the described embodiment, the turbine has four stages. In other embodiments, the compressor and turbine may have at least one stage. In other embodiments, the compressor and turbine may have at least one rotor disk, with each rotor disk having at least one rotor blade.

In the described embodiment, each compressor rotor blade and each turbine rotor blade of the first and second compressors are connected to the same shaft. Thus, the engine 320 may be described as a single shaft engine.

In other embodiments, the engine may be a multi-shaft engine. In other words, there may be more than one drive shaft driven by at least one turbine rotor disk. For example, consider the following embodiments. The first two turbine rotor disks, counted in the downstream direction, may be connected to a first drive shaft, which is connected to the second and third compressor rotor disks of the first compressor 324. The third turbine rotor disk may be coupled to a second drive shaft that is coupled to the first compressor rotor disk of the first compressor 324. The third turbine rotor disk may be connected to a third drive shaft, which may for example drive an electrical generator, a propeller device of a turboprop or a fan of a turbofan aircraft. The fourth turbine rotor disk may be connected to a fourth drive shaft, which is connected to all of the compressor rotor disks of the second compressor 340.

First heat exchanger 326 is configured to transfer heat from heat transfer device 351 to the working material in channel 342 during nominal operation. The location of the heat exchanger 326 within the passage 342, i.e., the portion of the passage 342 downstream of the first compressor 324 and upstream of the turbine 332, is shown as a heated chamber. In this particular embodiment, this is achieved by forcing a convection of hot fluid through the piping arrangement via a pump, such as pump 329. The hot fluid may be water, oil, molten salt, or a working material particularly suitable for transferring heat via forced convection from a radially outward portion of a first storage volume, such as heat transfer device 351, to a second storage volume, such as a heating chamber. In some embodiments, the thermal fluid may undergo a phase change throughout the piping arrangement. A conduit arrangement and pump 329 facilitates the transport of the hot fluid through the heat transfer device 351 and through the working material in the heating chamber. In this particular embodiment, the portion of the plumbing within the passage 342 may be described as a counter-flow heat exchanger. In other embodiments, for example, the heat exchanger may be a co-current heat exchanger or a cross-flow heat exchanger. The portion of the conduit arrangement in contact with the working material in the channel 342 comprises several smaller conduits such as conduit 327 in order to increase the contact area and increase the heat flow from the hot fluid to the working material. The portion of the tubing of first heat exchanger 326 surrounded by the toroidal cylindrical heat transfer device 351 indicates the location of heat transfer from the heat transfer device 351 to the hot fluid within the tubing of first heat exchanger 326. Once heat has been transferred from the heat transfer device 351 to the hot fluid inside the pipe arrangement, the pipe arrangement transports the hot fluid back to the heating chamber where it is transferred from the hot fluid to the working material.

Note that during nominal operation, the hot fluid heats the working material and transfers heat from the radially outward portion of the transfer device 351. The term "thermal" is used only to indicate the heat transported by the fluid and should not be interpreted to indicate the magnitude or direction of temperature change of any thermal storage body associated with or in thermal contact with the thermal fluid. The hot fluid may also be described as a cooling fluid or refrigerant. Because the passage 342 is annular, the heat exchanger 326 is axially symmetric about the axis 369.

The second heat exchanger 334 is configured in a similar manner as the first heat exchanger 326 and vice versa. The second heat exchanger 334 is configured to transfer heat from the working material in the channel 342 to a radially inward portion or bottom of the heat transfer device 351 during nominal operation. The location of the heat exchanger 334 within the passage 342, i.e., the portion of the passage 342 downstream of the turbine 332 and upstream of the second compressor 340, is represented as a cooling chamber. As previously described, this is achieved via forced convection of the hot fluid through the plumbing 336 by a pump, such as pump 337. Note that the thermal fluid in the second heat exchanger 334 need not be the same as the thermal fluid in the first heat exchanger 326. A piping arrangement 336 and pump 337 facilitate the transport of the hot fluid through the heat transfer device 351 and through the working material in the cooling chamber. In this particular embodiment, the portion of the conduit arrangement within the channel 342 may be described as a counter-flow heat exchanger. The portion of the conduit means in contact with the working material in the channel 342 comprises a plurality of smaller conduits such as conduit 335. The portion of conduit arrangement 336 surrounded by heat transfer arrangement 351 indicates the location where heat from the hot fluid within conduit arrangement 336 is transferred to heat transfer arrangement 351. Once heat has been transferred from the hot fluid to the heat transfer device 351, the piping arrangement 336 transfers the hot fluid back to the pump and cooling chamber, where heat is transferred from the working material to the hot fluid.

The heat transfer device 351 is configured to be able to transfer heat from a first thermal storage volume to a second thermal storage volume, wherein the temperature of the first thermal storage volume is lower than the temperature of the second thermal storage volume. During nominal operation, the temperature of the first thermal storage volume of the heat transfer device 351 is lower than the temperature of the second thermal storage volume. Thus, the first thermal reservoir may be denoted as a cold reservoir and the second thermal reservoir may be denoted as a hot reservoir. In the engine 320, the cold storage body includes a working material in the cooling chamber, and the hot storage body includes a working material in the heating chamber.

The temporal change in the thermodynamic properties of the working material flowing through the channel 342 is similar to the change described in fig. 10, and the thermodynamic system is also described by the schematic shown in fig. 12.

After compression, the working material is again heated, expanded, cooled, and compressed before passing through the outlet 342. Immediately after the engine 320, the working material that has passed through the channel 342 is heated by the surrounding working material and returns to substantially the original free-flow thermodynamic properties. The thermodynamic cycle may be described as an open cycle due to work, matter, and heat exchange with the environment, i.e., the region outside of the channel 342. Other embodiments may completely enclose the working material, resulting in a closed thermodynamic cycle. In addition to the channel section connecting the outlet 343 with the inlet 341, some embodiments may include a device similar to the engine 320, wherein the channel section includes a third heat exchanger configured to transfer heat from the environment outside the enclosed channel to the enclosed channel. Depending on the temperature of the external environment, the third heat exchanger may be configured to transfer heat from the external cold store to the hot store inside the enclosed channel, or from the external hot store to the cold store inside the enclosed channel, as long as heat is transferred from the external environment to the enclosed channel by the third heat exchanger.

Note that the foregoing embodiments are configured to convert thermal energy into mechanical work. In fig. 8-10, the amount of work is determined by the area enclosed by the closed curve, where the sign of the work done by the working material is positive for clockwise cycles and negative for counterclockwise cycles. The thermal energy is determined by the net heat energy absorbed from the external storage. This is the heat absorbed during isobaric expansion 192 in fig. 9 or isobaric expansion 217 in fig. 10 or the heat absorbed during isobaric expansion 162 from which the heat released during isobaric compression 154 is subtracted. When friction is ignored, for example, the net heat absorbed by the working material during one cycle, i.e., the heat absorbed during isobaric expansion 192, is equal to the net mechanical work performed by the working material. In this ideal case, from the perspective of the external storage (i.e., the storage that provides thermal energy during isobaric expansion 192), for example, thermal energy is converted to mechanical work. Note that the thermodynamic system need not be closed. In other words, mass may be exchanged with an external storage, as discussed in the context of fig. 11-15. For some embodiments, the working material is the same as and derived from the material found in the aforementioned external reservoir.

In other embodiments, the mechanical work may be converted to thermal energy. In such embodiments, the direction of heat flow between the working material and the heat exchanger may be reversed compared to the previous embodiments. The direction of the cycles shown in fig. 8-10 may be reversed, i.e., compression may be replaced by expansion, and vice versa, resulting in a change in the sign of the work performed by the working material and the thermal energy absorbed by the working material. In other words, work is now done on the working material and thermal energy is released by the working material to the external storage volume. The term "engine" as used herein refers to heat engines and heat pumps.

In the described embodiments, the rate of heat extracted from the working material in the cooling chamber is substantially equal to the rate of heat added to the working material in the heating chamber.

In other embodiments, there may be alternative or additional thermal storage or reservoirs that may assist in transferring heat to the working material in the heating chamber or in removing heat from the working material in the cooling chamber. For example, when an engine similar to engine 320 is employed to power an aircraft or ship, a portion of the submerged area of the fuselage or hull may be configured to extract heat from the surrounding fluid. Thus, a portion of the external environment or a portion of the fluid that does not flow through the channels 342 can be cooled and used as a thermal store for the working material in the heating chamber in a manner similar to the way the working material in the cooling chamber is used as a thermal store for the working material in the heating chamber. Alternatively or simultaneously, a portion of the fluid in contact with the fuselage or hull may be configured to transfer heat to the surrounding fluid. Thus, a portion of the external environment or a portion of the fluid that does not flow through the channels 342 can be heated and used as a thermal reservoir for the working material in the cooling chamber in a manner similar to the working material in the heating chamber being used as a thermal reservoir for the working material in the cooling chamber.

The principles of the present invention may also be applied to other types of thermodynamic devices such as, for example, turboshaft engines, turboprop engines, turbofan engines, piston engines, refrigerators, or air conditioning systems.

In another embodiment, the first and second compressors of the engine 320 are replaced with first and second turbines, the working material is expanded via the first and second turbines, and the turbine of the engine 320 is replaced with a compressor. The temporal changes in thermodynamic properties of the working material flowing through such an embodiment are similar to those described in fig. 9, and the thermodynamic system is also described by the schematic shown in fig. 13.

In the engine 320, the compressor and turbine adiabatically change the properties of the working material. In other embodiments, there may be heat exchange with the environment during compression or expansion of the working material. In some embodiments, the first compression, second compression, or expansion may be isothermal. The heat transferred from the working material during isothermal compression or to the working material during isothermal expansion may be arranged in a similar manner as previously described with heat transferred from a cooling chamber to a heating chamber in the engine 320 or from the external environment.

In other embodiments, the first engine 390 may be replaced by a conventional heat exchanger configured to extract heat from a working material, such as a fluid surrounding a hull or skin of an aircraft, such as the skin of a wing, fuselage or empennage, and transfer the heat to a heat transfer device 472, which heat transfer device 472 in turn is configured to transfer the heat to at least one engine, such as the engine 431.

Figure 15 is a cross-sectional view of three components of another embodiment of a heating or cooling system. Some features of the apparatus shown in fig. 15 and some principles of operation of the apparatus have similarities to the apparatus shown in other figures, such as in particular fig. 8 and 11, and will therefore not be described in detail again in the context of fig. 15, and vice versa.

The first component is a first engine 390, the second component is a heat transfer device 472, and the third component is a second engine 431.

First engine 390 includes a conduit means 391 and an inner means 392. The various components of the engine 390 are substantially axially symmetric about the shaft 422.

The inner device 392 includes an annular passage 395, optionally between the annular inlet 394 and the annular outlet 403, and between the outer inner surface and the inner surface.

Working material flows through passageway 395 from inlet 394 to outlet 403. The working material may be a compressible fluid. As previously mentioned, the fluid may be a gas such as air, for example.

After passing through inlet 394, the working material flowing through passage 395 encounters, in sequence, turbine 396, heat exchanger 398, and compressor 402 before exiting through outlet 403.

In this embodiment, the turbine 396 and compressor 402 may be described as axial flow turbines and compressors. Other embodiments may include other types of turbomachinery devices, such as, for example, centrifugal compressors or turbines. The principles of the present invention may also be applied to embodiments that include pistons, such as those found in piston engines or pumps.

The heat exchanger 398 is configured to transfer heat from the working material in the channel 395 to the heat transfer device 472 during nominal operation. The location of the heat exchanger 398 within the passage 395, i.e., the portion of the passage 395 upstream of the compressor 402 and downstream of the turbine 396, is illustrated as a cooling chamber. In this particular embodiment, this is accomplished via forced convection of the hot fluid through a pump, such as pump 487, of the conduit device 486. The hot fluid may be water or oil, or a fluid particularly suited to said forced convection. A conduit arrangement and pump 487 facilitates the transfer of the hot fluid through heat transfer device 398. In this particular embodiment, the portion of the duct means 486 within the passage 395 may be described as a counter flow heat exchanger. The portion of the conduit means in contact with the working material in the channel 395 comprises a plurality of smaller conduits, such as conduit 399, in order to increase the contact area and increase the heat flow from the working material to the hot fluid.

In other embodiments, the hot fluid may transfer heat through the heat exchanger 398 via natural convection. In other embodiments, the heat exchanger 398 may transfer heat from the cooling chamber to the heat transfer device 472 via thermal conduction. For example, the conduit means 486 may be composed of a solid material such as copper or silver, or the conduit means may comprise a different suitable material, such as a material having a high thermal conductivity. Various other heat exchange methods are available.

The second motor 431 includes a conduit means 432 and an inner means 433. Several components of the motor 431 are substantially axially symmetric about the axis 463.

The inner device 433 includes an annular channel 436 between the annular inlet 435 and the annular outlet 444 and between the outer inner surface and the inner surface.

The working material flows through the channel 436 from the inlet 435 to the outlet 444. The working material may be a compressible fluid. As previously mentioned, the fluid may be, for example, a gas such as air.

After passing through the inlet 435, the working material flowing through the channels 436 sequentially encounters the compressor 437, the heat exchanger 439, and the turbine 443 before exiting through the outlet 444.

In this embodiment, the turbine 443 and the compressor 437 can be described as axial flow turbines and compressors.

The heat exchanger 439 is configured to transfer heat from the heat transfer device 472 to the working material in the channel 436 during nominal operation. The location of the heat exchanger 439 within the passages 436, i.e., the portion of the passages 436 downstream of the compressor 437 and upstream of the turbine 443, is depicted as a heated chamber. In this particular embodiment, this is achieved via forced convection of the hot fluid through a pump, such as pump 490, of the channel arrangement 489. The hot fluid may be water or oil, or a fluid particularly suited to said forced convection. The piping arrangement and pump 490 facilitates the transport of the thermal fluid through the heat transfer device 439. In this particular embodiment, the portion of the conduit device 489 within the channel 436 may be described as a counter-flow heat exchanger. The portion of the conduit arrangement that contacts the working material in the channel 436 includes a plurality of smaller conduits, such as conduit 440, to increase the contact area and increase the heat flow from the hot fluid to the working material.

In the depicted embodiment, the working material flowing through channel 436 during nominal operation is the same as the working material flowing through channel 395. For example, the working material for first engine 390 and second engine 431 may be air. In other embodiments, the working material flowing through the first engine 390 and the second engine 431 need not be the same. Other embodiments may include at least one engine, such as engine 390 or engine 431. Embodiments that include a single engine may include a conventional heat exchanger. For example, the first engine 390 may be replaced by a conventional heat exchanger configured to exchange heat between the heat transfer device 472 and a heat storage volume. For example, the medium in the heat storage volume may be air surrounding an aircraft or water surrounding a ship. In some such embodiments, the heat transfer device 472 may be configured to transfer heat from the heat storage body to a heating chamber of the engine 431. In some such embodiments, the working material flowing through the engine 431 may be a gas, such as air, and the working material flowing through or interacting with a conventional heat exchanger or exchanging heat with a conventional heat exchanger may be a gas, a liquid, or any other heat storage. In other embodiments, the second motor 431 may be replaced by a conventional heat exchanger, and the heat transfer device 472 may be configured to transfer heat from a cooling chamber of the motor 390 into a thermal storage in thermal contact with the heat exchanger.

In other embodiments, heat may also be transferred to the working material within the heating chamber of the engine 431 via an external heat or substance source, such as heat provided by a chemical reaction (such as a chemical reaction between a fuel and a portion of the working material).

The heat transfer device 472 is configured to transfer heat from a first thermal storage volume to a second thermal storage volume, wherein the temperature of the first thermal storage volume is lower than the temperature of the second thermal storage volume. During nominal operation, the temperature of the first thermal storage volume of heat transfer device 472 is lower than the temperature of the second thermal storage volume. Thus, the first thermal reservoir may be denoted as a cold reservoir and the second thermal reservoir may be denoted as a hot reservoir. For the embodiment depicted in fig. 15, the cold storage volume comprises working material in a cooling chamber in engine 390 and the hot storage volume comprises working material in a heating chamber in engine 431.

Heat transfer device 472 includes a sleeve device 473 and an annular rotation device 475 configured to rotate relative to sleeve device 473 about axis 495 during nominal operation. The sleeve device 473 is cylindrical with a central axis of symmetry coinciding with the axis 495 in this embodiment. In other words, the cross-section of the sleeve device 473 is circular when viewed along the axis 495. The cannula device 473 also includes a hollow central shaft 484. The rotary device 475 is also axially symmetric about the axis 495. The rotation device 475 encloses a central volume 496, as shown, the central volume 496 being annular about the axis 495 and rectangular in cross-section when viewed along an axis perpendicular to the axis 495.

The central volume 496 comprises a material that can experience an increase in temperature when adiabatically compressed. In the depicted embodiment, the central volume 496 includes a compressible gas such as helium, hydrogen, or air. It may be advantageous to select a core material having a large thermal conductivity. This can increase the heat flow from the cooling chamber to the heating chamber for a given plant operating condition, and thus increase the net power output, for the most part. For some embodiments, a small specific heat capacity at constant pressure may help reduce the mass of heat transfer device 472. For example, a smaller specific heat capacity may result in a smaller rotational angular velocity of the rotary device 475, reducing the size of the carrier member. In some embodiments, the central volume 496 may include a solid such as a metal or a liquid such as water. Note that the material represented as the center material in center volume 496 may be of the same type as the working material flowing through channel 436 or channel 395.

In the described embodiment, in order to minimize viscous friction due to relative movement of the sleeve device and the rotation device 475, the isolation volume 497 between the rotation device 475 and the sleeve device 473 is evacuated. In other embodiments, the isolated volume 497 may comprise a fluid. For example, the fluid may be helium or lubricating oil. Such fluid may increase the pressure within the isolation volume 497 and reduce the mass of the sleeve device 473 without the necessity of substantially increasing the energy losses associated with the relative movement of the sleeve device 473 and the rotating device 475.

The geometry of the rotating device 475 may also accommodate large centripetal loads within the walls of the rotating device 475 in a manner that reduces the mass of the rotating device 475 for a given heat flux or radius. For example, the cross-section of the annular rotary device 475 may be, or share similarities with, a teardrop shape when viewed along an axis perpendicular to the axis of rotation 497, wherein the long axis of the teardrop is perpendicular to the axis of rotation 497, and wherein the nominally rounded, blunt end of the teardrop is in a radially outward direction as compared to the nominally more pointed end. In such embodiments, the sleeve device may have a spherical shape. In other such embodiments, the sleeve device may have a cylindrical shape, wherein the central portion of the outer surface is parallel to axis 495 and the ends are convex, i.e., outwardly rounded, or concave, i.e., inwardly rounded. A variety of other geometries of cannula devices and rotating devices are available.

The preferred path of heat flow from the plumbing 494 to the plumbing 489 is from the interior inner surface 477 to the interior outer surface 476 via the adjoining portion of the isolated volume, through the interior wall of the rotating device 475 parallel to the axis 495, through the central volume 496, through the exterior wall of the rotating device 475 parallel to the axis 495, from the exterior inner surface 480 to the exterior outer surface 479 via the adjoining portion of the isolated volume, as indicated by the arrow perpendicular to the axis 495.

The hot fluid is conveyed through the conduit arrangement 486 to the interior surface 477 via a plurality of smaller conduits such as conduit 494. Heat may be transferred from the conduit arrangement to the interior surface 477 via thermal conduction. The interior surface 477 is configured to transfer heat to the interior exterior surface 476 via thermal radiation through the evacuated insulation volume 497. In other embodiments, at least a portion of the heat transfer may include conduction through a material, such as a gas or liquid, contained within the isolated volume 497. In some embodiments, at least a portion of the heat transfer may include thermal conduction through a component of the roller bearing between the inner surface and the opposite outer surface.

The inner surface 477 is cylindrical and surrounds a portion of the central axis 484. The inner outer surface 476 is also cylindrical and is connected to the cylindrical inner surface of the rotating device 475. The isolation distance between the interior inner face 477 and the interior outer face 476 is as small as possible in order to maximize the heat flow between the faces. This also applies to the separation distance between the outer inner surface 480 and the outer surface 479. The aforementioned inner or outer surface may comprise a metal such as copper or aluminum.

In some embodiments, the inner surface and the outer surface comprise radial protrusions, wherein, typically, the protrusions of the inner surface are between two protrusions of the outer surface. In this way, the surface area of the interface between the inner and outer surfaces can be artificially increased. For a given average circumferential footprint of the inner and outer surfaces, a larger interface area may increase the rate of heat transfer between the inner and outer surfaces. For example, the protrusion may be an annular, flat metal disc, wherein the plane of the disc is perpendicular to the axis 495. The metal disc may be rigidly connected to an associated surface, such as an inner or outer surface. The protrusions of the inner surface may be between two protrusions of the outer surface such that the protrusions of the inner surface and the protrusions of the outer surface are staggered without contact. To maximize the interface area between the inner and outer surfaces, the protrusions or the disks or fins may be constructed to be thin and the gaps between the protrusions may be minimized. The protrusions may be electrostatically charged such that the protrusions of the inner surface electrostatically repel the protrusions of the outer surface. In this way, the thin and flexible protrusions of the inner surface may be placed in close proximity to the thin and flexible protrusions of the outer surface without the protrusions touching or touching. Due to the relative movement of the rotation means 475 and the sleeve means 473, the contact will result in a friction loss. In other embodiments, the repulsive force between adjacent protrusions may be provided by a magnetic field. For example, repelling permanent magnets may be embedded in the protrusions. Alternatively, the electrical conductors may be embedded within the protrusions such that current flows in adjacent conductors of adjacent protrusions in opposite circumferential directions, resulting in repulsive magnetic forces. Various other methods are available to ensure separation between adjacent protrusions.

The bearing assembly prevents the rotation device 475 from contacting the sleeve device 473. The bearing assembly is not shown in fig. 15. For example, the bearing assembly may be on the outer inner surface and the outer surface. Alternatively, the bearing assembly may be on the inner surface and the inner outer surface.

The heat transferred to the inner outer surface 476 is conducted through the inner wall of the rotating device 475 and into the central material in the central volume 496. The material of the inner wall may comprise a material having a high thermal conductivity, such as copper or silver. In other embodiments, heat may be transferred through the inner wall by forced convection through a separate conduit arrangement by a pump so that heat may be transferred from the inner outer surface 476 to the core material. In other embodiments, the inner wall of the central volume 496, i.e., the wall closest to the axis 495, may also include protrusions, pins, fins, or plates to increase the surface area of the inner wall. For simplicity, this may increase the heat flow from the inner wall into the center material as compared to the two-dimensional cylindrical inner wall surface of the center volume 496 shown in fig. 15. The outer wall of the central volume 496, i.e., the wall facing in the radially inward direction, may also impart a protrusion to increase surface area.

Baffles within the central volume 496 ensure that fluid within the central volume 496 rotates with the walls of the rotating device 475. This is particularly significant during acceleration or deceleration of the rotational speed of the wall of the rotating device 475. In this embodiment, each baffle is planar, with each plane being parallel to axis 495 and to a vector perpendicular to axis 495. Other embodiments do not include the described baffles. For example, the material within the central volume 496 may be a solid, or viscous friction between the fluid and the walls of the central volume 496 may be used to accelerate or decelerate the rotational velocity of the fluid within the central volume 496 such that, in a steady state, the rotational angular velocity of the fluid matches the rotational angular velocity of the solid walls of the rotational device 475. In other embodiments, the center material may be constrained by an electrostatic or magnetic field, as opposed to the solid wall depicted in fig. 15.

Due to the rotation of the central material, a pressure gradient exists within the central material, wherein the pressure increases in a radially outward direction, as discussed in the context of fig. 4 and 1. In the depicted embodiment, the walls of the rotating device 475 are insulated. For simplicity, the wall may be considered an ideal insulator. In the simplified model, compression of the center material in a radially outward direction relative to axis 495 may be considered adiabatic. As a result, the temperature of the central material rises in a radially outward direction, resulting in a temperature at the outer wall of the central volume 496 that is greater than the temperature at the inner wall of the central volume. The temperature difference at the outer and inner walls of the central volume 496 is represented as an internal temperature difference. The magnitude of the internal temperature difference is a function of the material properties of the center material, such as the specific heat capacity at constant pressure, and the rotational angular velocity of the rotary device 475, as well as the geometry of the rotary device 475, particularly the radius of the inner wall and the radius of the outer wall, among other parameters. When the internal temperature difference is sufficiently large, heat can flow from the cooling chamber of the engine 390 to the heating chamber of the engine 431. For example, when assuming that thermal conductivity between the inner wall of the central volume 496 and the cooling chamber of the engine 390, and between the outer wall of the central volume 496 and the heating chamber of the engine 431 is ideal, and that transient heat transfer between the ducting arrangement and the working material is ideal, the internal temperature differential should be greater than the temperature differential of the working material entering the heating chamber and the working material entering the cooling chamber. In that case, heat may flow through the central volume 496 in a radially outward direction via heat conduction from the cold reservoir to the heat reservoir.

Note that in some embodiments, heat may be lost by conduction, convection, or radiation through the isolated volume 497. For example, these heat losses can be mitigated by including an insulation volume 497 of a material having a low thermal conductivity, by minimizing the size of the insulation volume 497, or by placing an insulating material around the optimal path of heat flow from the plumbing 494 to the plumbing 489.

Similar to the heat transfer from inner surface 477 to the inner wall of central volume 496, heat may be transferred from outer inner surface 480 to outer surface 479. At the outer exterior surface 479, heat is transferred to the hot fluid within the conduit device 489 via heat conduction. The hot fluid in the tubing set 489 is pumped by pump 490 to heat exchanger 439 in the heating chamber of the engine 431 where the heat is transferred to the working material in the channel 436.

In some embodiments, heat transfer device 472 may be within an engine, such as engine 431. For example, axis 495 may coincide with axis 463, and heat transfer device 472 may be within the volume enclosed by channel 436. In other embodiments, the engine may be within heat transfer device 472. For example, where the shaft 422 is coincident with the shaft 495, a portion of the motor 390 may be within a hollow central shaft 484.

The temporal variation of the thermodynamic properties of the working material flowing through channel 395 is similar to that described in the second cycle in figure 8. The temporal variation of the thermodynamic properties of the working material flowing through the channel 436 is similar to the variation described in the first cycle in fig. 8. The thermodynamic system in fig. 15 is also depicted by the schematic diagram shown in fig. 11.

In this embodiment, both the first engine 390 and the second engine 431 produce a positive mechanical work output.

In some embodiments, axis 463, axis 495, and axis 422 are substantially coincident. For example, a portion of the motor 390 may be within the hollow central axis 484 and the heat transfer device 472 may be surrounded by the channel 436 of the motor 431. In other embodiments, the order may be reversed. The heat transfer device 472 may surround the motor 431, both surrounded by the passage 395 of the motor 390.

In other embodiments, the engine 390 may be configured in a similar manner as the engine 431. In other words, after passing through inlet 394, the working material flowing through passage 395 sequentially encounters the compressor, the cooling chamber housing heat exchanger 398, and the turbine before exiting through outlet 403. In this case, the temperature of the working material exiting the compressor is lower than the temperature of the working material exiting the compressor 437 in the engine 431. As previously described, heat transfer device 472 is configured to transfer heat from working material in a cooling chamber of engine 390 to working material in a heating chamber of engine 431. Note that engine 390 performs work on the working material, which performs work on engine 431. The combined engine 390 and engine 431 may be configured to produce a net positive mechanical work output.

Note that while the heat flow out of the cooling chamber is substantially equal to the heat flow into the heating chamber, the mass flow of working material through the motor 390 need not be equal to the mass flow through the motor 431. Therefore, the amount of heat per unit mass removed from the working material in the engine 390 need not be equal to the amount of heat per unit mass added to the working material in the engine 431. This allows for more flexibility in optimizing the design of the engine 431 and engine 390 for a particular application. For example, the mass flow rate of the working material through the engine 390 may be greater than the mass flow rate of the working material through the engine 431. By increasing the mass flow rate through the engine 390, the minimum temperature of the working material in the cooling chamber may be increased. This may increase the temperature at the inner wall of the central volume 496, which may increase the average thermal conductivity of the central material, which may increase the heat flow from the cooling chamber to the heating chamber, which may increase the net positive power output of the combined device.

In some embodiments, a majority of the working material exiting the engine 431 through the outlet 444 also enters the engine 390 through the inlet 394. In some such embodiments, the working material that has flowed through the engine 431 may be a fraction of the total flow of working material into the engine 390. In other words, ambient working material, such as ambient air, is drawn into the engine 390 along with working material from the exhaust of the engine 431. As previously described, this may increase the average temperature of the working material entering the engine 390, which may increase the temperature of the working material at the cooling chamber, which may increase the net power output of the combined device.

In other embodiments, heat transfer device 472 may be configured differently. In fig. 15, the inertial load on the center material can be thought of as the volumetric force per unit mass acting on the elements of the center material in a radially outward direction. The inertial load is caused by the circular motion of the molecules of the central material rotating with the rotating device 475. This inertial load is also referred to as centrifugal force, which is the apparent force. As previously mentioned, a variety of other methods and devices for generating a volumetric force per unit mass within the core material are available.

FIG. 16 is a cross-sectional view of an exemplary embodiment 520 of a heat transfer device. Some features of the embodiment shown in fig. 16 and some principles of operation of the embodiment have similarities with features and principles of operation described by other figures, and therefore will not be described in detail again in the context of fig. 16, and vice versa.

Fig. 16 shows a reservoir 521 comprising a thermal material 522. In this particular example, the thermal material 522 is a gas in which individual molecules or atoms may be electrically polarized by an applied electric field. For example, the gas may be air, nitrogen, helium, or argon. In other embodiments, the thermal material 522 may be a liquid or a solid. As in the case of water, the thermal material may also comprise permanently polarized molecules.

An electrically insulating and heat insulating material 523 surrounds the storage body 521. In the embodiment, the storage body 521 has a cylindrical shape. In other embodiments, for example, the storage 521 may be rectangular or circular. The storage body 521 may generally take any shape.

The first heat exchanger 526 is located near a first point 524 in the reservoir 521. In this particular embodiment, the first heat exchanger 526 includes a plurality of fins, such as fin 530, which may be described as a planar metal plate. A conduit 527 comprising a thermal fluid is rigidly attached to the fin, allowing heat to be conducted from the thermal material 522 to the fin and from the fin into the thermal fluid within the conduit 527, and vice versa. The hot fluid is pumped through the tubing by a pump, not shown. Thus, the tubes may transfer heat to heat exchanger 526, or from heat exchanger 526. In other embodiments, the heat exchanger 526 may be configured differently. For example, the heat exchanger 526 may employ conduction, radiation or natural convection, as opposed to the aforementioned forced convection of the hot fluid through the conduit 527, in order to exchange heat between the first point 524 in the storage volume 521 and another storage volume, not shown.

The second heat exchanger 531 is located near the second point 525 in the reservoir 521. The second heat exchanger 531 is configured in a similar manner as the first heat exchanger 526. In other embodiments, the second heat exchanger 531 may be configured differently than the first heat exchanger 526. The second heat exchanger 531 includes plates or fins such as fins 535 and tubes 532.

The heat transfer device 520 comprises a volumetric force generating device configured to generate a volumetric force per unit mass having a substantial component in a vertically downward direction towards the bottom of the page, wherein the volumetric force per unit mass acts on the thermal material 522 within the reservoir 521.

The volumetric force generating device includes a number of sets of charges, such as a first set of positive charges 539, a second set of positive charges 540, a third set of positive charges 541, and a set of negative charges 542. The charge collection may be contained within an electrical conductor, such as a metal such as copper. A voltage difference applied between conductors, such as between conductor 541 and conductor 542, will result in the accumulation of charge within both conductors. In the described embodiments, the net charge contained within the volumetric force generating device is zero. The

electrical conductors

541, 540 and 539 are annular and surround a cylindrical reservoir 521. The electrical conductor 542 is cylindrical. The amount of charge contained within each set of charges may be adjusted relative to the other sets of charges by adjusting the voltage associated with the set of charges relative to the other sets of charges. Various other configurations of charge sets may achieve the same effect as the described configuration. For example, the collection of charges may be within the storage 521.

The thermal material 522 is electrically polarized due to the electric field within the reservoir 521. The component of the electric field along the longitudinal axis of the page increases in the direction towards the bottom of the page due to the charge collection. Thus, individual molecules of the thermal material 522 experience a volumetric force per unit mass toward the bottom of the page. In equilibrium, the pressure, density, and temperature of the thermal material 522 increase toward the bottom of the page. Thus, the temperature at the second point 525 is greater than the temperature at the first point 524. In this particular embodiment, the insulating material accommodates the pressure and electric field applied to the thermal material 522.

Depending on the external temperature applied at the first heat exchanger 526 and the second heat exchanger 531, heat may flow through the thermal material 522 from the first heat exchanger 526 to the second heat exchanger 531, or vice versa. For example, if the external temperatures of the first heat exchanger 526 and the second heat exchanger 531 are the same, heat will flow from a first external reservoir thermally connected to the first heat exchanger 526, through the first heat exchanger 526 to the first point 524 and through the thermal material 522 to the second point 525, and through the second heat exchanger 531 to a second external reservoir thermally connected to the second heat exchanger 531. This is due to the artificially created temperature difference between the first point 524 and the second point 525 by the volumetric force generating means, wherein the temperature difference is maintained by the thermally insulating material 523. The higher temperature at the second point 525 makes the first external reservoir appear hotter than the second external reservoir. Thus, as long as the temperature difference between the first external storage and the second external storage is smaller in magnitude for a given operating condition than the temperature difference between the first point 524 and the second point 525, the heat transfer device 520 may be employed to transfer heat from the first external storage to the hotter second external storage.

When the temperature of the first external storage volume is greater than the temperature of the second external storage volume, the amount of heat transferred through a heat transfer device configured according to the present invention may be greater than equivalent heat exchangers of the prior art. The equivalent heat exchanger of the prior art may be an infinitely thin interface between the first reservoir and the second reservoir. The amount of heat transferred through the heat transfer device is a function of the thermal conductivity and the temperature gradient. The limited length of the heat transfer device will reduce the temperature gradient by increasing the length at which the temperature difference is measured, compared to a theoretically equivalent heat exchanger and associated thermal boundary layer. For some embodiments and some configurations, the built-in temperature difference of the heat transfer device, i.e., the temperature difference between the first point and the second point in equilibrium at zero heat flow, may offset this increase in length, however, resulting in a larger temperature gradient and a larger amount of heat transfer from the hot storage body to the cold storage body.

FIG. 17 is a cross-sectional view of an exemplary embodiment 570 of a heat transfer device. Some features of the embodiment shown in fig. 17 and some principles of operation of the embodiment have similarities with features and principles of operation described by other figures, and therefore will not be described in detail again in the context of fig. 17, and vice versa.

Fig. 17 shows a reservoir 571 comprising a thermal material 572. In this particular example, the thermal material 572 is a gas in which individual molecules or atoms are positively or negatively charged. In other embodiments, the thermal material 572 can be a liquid or a solid. In other embodiments, the thermal material 572 may include other types of mobile charges, such as freely moving electrons.

An electrically insulating insulation 573 surrounds the reservoir 571. In this embodiment, the storage body 571 is cylindrical. In other embodiments, the shape of the storage body 571 may be rectangular or circular, for example. The reservoir 571 may generally take any shape.

The first heat exchanger 576 is located near a first point 574 in the reservoir 571 and comprises a plurality of fins and tubes 577. Second heat exchanger 581 is located near a second point 575 in reservoir 571 and includes a plurality of fins and tubes 582. These heat exchangers are configured in a similar manner to the heat exchanger shown in fig. 16.

The heat transfer device 570 comprises a volumetric force generating device configured to generate a volumetric force per unit mass having a substantial component along the long axis of the page, wherein the volumetric force per unit mass acts on the thermal material 572 within the reservoir 571.

The volumetric force generating device includes a plurality of charge sets, such as a positive first charge set 589, a negative second charge set 590. Various other configurations of devices that generate a volumetric force per unit mass can be designed and used to generate a potential energy difference of the elements of the thermal material 572 between the first point 574 and the second point 575.

The potential energy difference results in a temperature difference between the first point 574 and the second point 575 during thermal equilibrium, i.e., zero heat flow between the first point 574 and the second point 575. For example, when the thermal material comprises positively charged ions, the ions will experience a volumetric force per unit mass toward the bottom of the page within reservoir 571. As described in the context of fig. 16, this results in a higher temperature at the second point 575 than at the first point 574. Thus, embodiment 570 may operate as a heat transfer device in the same manner as embodiment 520 and other heat transfer devices mentioned herein.

By reversing the polarity of the charges contained within the charge collection, the direction of the bulk force within the thermal material 572 may be reversed. This can be used to control the heat flow through the heat transfer device. This may be used, for example, to change the mode of operation of the heat transfer device 570 from a mode corresponding to an artificial heat storage to a mode corresponding to an artificial heat reservoir.

By adjusting the magnitude of the potential difference applied to the first set of charges 589 relative to the second set of charges 590, the magnitude of the volumetric force per unit mass within the reservoir 571 can be controlled. In this manner, the magnitude of the temperature difference between the first point 574 and the second point 575 can be controlled. This enables the heat flow through the thermal material 571 and through the heat transfer device 570 to be controlled. Other methods of controlling the heat flow through the heat transfer device 570 are also available. For example, the mass flow of the thermal fluid through the conduit 582 may be varied.

FIG. 18 is a cross-sectional view of an exemplary embodiment 610 of a heat transfer device. Some features of the embodiment shown in fig. 18 and some principles of operation of the embodiment have similarities with features and principles of operation described by other figures, and therefore will not be described in detail again in the context of fig. 18, and vice versa.

Fig. 18 shows a reservoir 611 comprising a thermal material 612. In this particular example, the thermal material 612 is a gas in which individual molecules or atoms may be magnetically polarized. In other embodiments, the thermal material 612 may be a liquid or a solid. In other embodiments, the thermal material 612 may include other types of magnetic dipoles, such as free-moving electrons. In other embodiments, the magnetic dipole may be permanent as opposed to being induced by an externally applied magnetic field.

An electrically insulating and heat insulating material 613 surrounds the reservoir 611. In the embodiment, storage body 611 is cylindrical. In other embodiments, for example, reservoir 611 may be rectangular or annular in shape. Reservoir 611 may generally take any shape.

First heat exchanger 616 is located near first point 614 in reservoir 611 and includes a plurality of fins and tubes 617. A second heat exchanger 621 is located near the second point 615 in the reservoir 611 and includes a plurality of fins and tubes 622. These heat exchangers are configured in a similar manner to the heat exchanger shown in fig. 16.

The heat transfer device 610 includes a volumetric force generating device configured to generate a volumetric force per unit mass having a substantial component along a long axis of the page, wherein the volumetric force per unit mass acts on the thermal material 612 within the reservoir 611.

The volume force generating device includes a number of current coils, such as coil 629 looping conductor 630, coil 631 looping conductor 632, coil 633 looping conductor 634, coil 635 looping conductor 636, or coil 637 looping conductor 638. As indicated, each coil carries a current that is directed out of the page on the left side of the page and into the page on the right side of the page. Each coil is made of an electrical conductor such as copper. In some embodiments, the coil comprises a superconducting material.

Various other configurations of volumetric force generating devices per unit mass may be designed and employed to generate a potential energy difference of an element of the thermal material 612 between the first point 614 and the second point 615.

The potential energy difference results in a temperature difference between the first point 614 and the second point 615 during thermal equilibrium. Due to the increase in the magnetic field strength component towards the bottom of the page in a direction parallel to the long axis of the page, the magnetic dipoles induced within the thermal material 612 will experience a volumetric force per unit mass with a non-zero component towards the bottom of the page within reservoir 611. As described in the context of fig. 16, this results in a higher temperature at the second point 615 as compared to the first point 614. Thus, embodiment 610 may operate as a heat transfer device in the same manner as embodiment 520 and other heat transfer devices mentioned herein.

FIG. 19 is a cross-sectional view of an exemplary embodiment 650 of a heat transfer device. Some of the features of the embodiment shown in fig. 19 and some of the operating principles of the embodiment have similarities with the features and operating principles described by the other figures, and therefore will not be described in detail again in the context of fig. 19, and vice versa.

Fig. 19 shows a reservoir 651 comprising a thermal material 652. In the particular example, the thermal material 652 is a gas such as air, helium, or argon. In other embodiments, the thermal material 652 may be a liquid.

The insulating material 653 surrounds the storage body 651. In this embodiment, the storage body 651 is cylindrical. In other embodiments, for example, the storage body 651 may be rectangular or annular. The reservoir 651 may generally take any shape, so long as the volumetric force generating device is configured to enable the heat transfer device to operate as intended.

The first heat exchanger 656 is located near a first point 654 in the storage body 651 and includes a plurality of fins and tubes 657. The second heat exchanger 661 is located near a second point 655 in the storage body 651 and includes a plurality of fins and tubes 662. Fins of the heat exchanger, such as fins 660 or fins 665, are cylindrically disposed about axis 675 so as to provide little resistance to the swirling of the thermal material 652 within the reservoir 651 during nominal operation.

The heat transfer device 650 comprises a force generating device configured to generate a force having a substantial component oriented along the long axis of the page towards the bottom of the page, wherein the force acts on the thermal material 652 within the reservoir 651.

The force generating means comprise an axial compressor configured in a similar manner to that of a conventional turbojet engine. Note that during nominal operation of the depicted embodiment, there is no net flow of thermal material 652 in a direction parallel to axis 675. In other embodiments, there may be a bulk flow of thermal material 652 along axis 675 that is still capable of transferring a sufficient amount of heat between first point 654 and second point 655 during nominal operation. For example, when heat is transferred against the direction of the general flow of the thermal material 652, the amount of heat transferred is reduced compared to an average stationary thermal material 652. This is because convection of the thermal material partially offsets conduction of heat through the thermal material in the opposite direction. In embodiments where the thermal material is experiencing bulk flow, the force generation means may also include expansion or contraction of the cross-sectional area of the channel through which the thermal material flows. In examples involving subsonic bulk flow, this may generate a force on the thermal material in the upstream or downstream direction, respectively, of the bulk flow of the thermal material. In other embodiments, therefore, the force generation means may comprise a contracting or expanding conduit. In still other embodiments, the force generation device may comprise a centrifugal compressor. In other embodiments, the force generation device may comprise a coaxial, counter-rotating axial flow compressor.

The axial compressor shown in fig. 19 includes a drive shaft 670 connected to a plurality of rotor disks, each of which includes a plurality of rotor blades, such as rotor blade 672 or rotor blade 671. To balance the swirl of the thermal material 652, a plurality of stator discs comprising a plurality of blades such as stator blades 674 or stator blades 673 are connected to a sleeve arrangement comprising an insulating material 653. In the depicted embodiment, the rotor blades and stator blades are rigidly attached to the shaft 670 or sleeve device. In other embodiments, at least a portion of the blade is rotatably connected to the drive shaft 670 or sleeve arrangement, wherein the axis of rotation of the rotatable connection is substantially perpendicular to the axis 675. The rotatable connection is configured such that the angle of attack of the stator and/or rotor blades can be controlled such that the amount of force exerted by the force generating device on the thermal material 652 can be adjusted.

The axial compressor shown in fig. 19 is driven by a motor 669. Motor 669 in fig. 19 is an electric machine. In other embodiments, motor 669 may be a piston engine or a turboshaft engine, for example. In general, any type of power source and any type of shaft work generating device may be employed to drive the axial flow compressor shown in FIG. 19. Note that the described embodiments consume power during nominal operation due to frictional losses of the axial compressor relative to the movement of the thermal material 652. Frictional losses increase the temperature of the thermal material 652, which may be desirable for certain applications, such as applications where the heat transfer device is used as an artificial heat storage body. Due to these frictional losses of the axial compressor, the thermal material 652 will swirl, i.e. experience a general rotational flow about the shaft 675 within the storage body 651. During stable nominal operation, the rotational speed of the thermal material 652 is the speed at which the torque exerted by the rotating parts of the axial compressor balances the torque exerted on the thermal material 652 by the stators, walls and other wet surfaces of the reservoir 651.

During nominal operation, the axial compressor increases the temperature at the second point 655 compared to the first point 654. Thus, embodiment 610 may operate as a heat transfer device in the same manner as embodiment 520 and other heat transfer devices mentioned herein.

In the ideal case where the insulating material 653 is completely insulating, the compression of the thermal material at the second point 655 compared to the first point 654 can be modeled as an adiabatic compression. In other embodiments, the compression is not adiabatic.

Fig. 20 is a cross-sectional view of one exemplary embodiment 690 of an artificial thermal storage body or artificial thermal reservoir employing a heat transfer device. Some features of the embodiment shown in fig. 20 and some principles of operation of the embodiment have similarities with features and principles of operation described by other figures, and therefore will not be described in detail again in the context of fig. 20, and vice versa.

Fig. 20 shows a heat transfer device comprising a storage body 691, which storage body 691 in turn comprises a thermal material 692. In this particular example, the thermal material 692 is a gas. In other embodiments, the thermal material 692 may be a liquid or a solid.

The thermal insulation material 693 surrounds the storage body 691. In this embodiment, the storage body 691 is cylindrical. In other embodiments, storage 691 may be rectangular or circular, for example. Storage 691 can generally take any shape.

The first heat exchanger 698 is near a first point 695 in the storage volume 691 and includes a plurality of fins, such as fins 702 and tubes 699. The second heat exchanger 703 is proximate a second point 696 in the storage volume 691 and includes a plurality of fins such as fins 707 and tubes 704. These heat exchangers are configured in a similar manner to the heat exchanger shown in fig. 16. For simplicity, pumps for pumping hot fluid through the conduit 699 and the conduit 704 are not shown.

The heat transfer device may have any suitable configuration, such as the configuration shown in fig. 16, 17, 18, or 19, or any other configuration discussed herein or within the scope of the present invention. For simplicity and general purposes, detailed features of the heat transfer device, such as features related to the force generation device, are not shown.

In fig. 20, a first external storage volume is shown on a portion of first heat exchanger 698 external to storage volume 691. For example, the first external storage volume may be the earth's atmosphere. The atmospheric temperature at point 694 and the temperature at point 697 and the equilibrium temperature difference between the first and

second points

695, 696 of the heat transfer device determine the amount of heat transfer and the direction of heat transfer through the heat transfer device, as discussed in the context of fig. 16.

A second external storage volume 710 comprising thermal material 711 is shown on a portion of the second heat exchanger 703 that is external to the storage volume 691. For example, the second external storage body may be an interior of a building, a vehicle, or a refrigerator. Depending on the material properties of the thermal material 692, the direction of the force exerted on the thermal material 692 and the temperature of the larger external reservoir, i.e. in this case at the point 694 in the first external reservoir, heat may flow from the first external reservoir to the second external reservoir and vice versa. From the perspective of the second external storage volume, the heat transfer device may thus be configured as an artificial heat storage volume or an artificial heat reservoir.

Notes and examples

The following non-limiting examples detail certain aspects of the present subject matter in order to address the challenges and provide the benefits discussed herein, among others.

In one aspect, a heat exchange system includes: a first storage volume having a first point and a second point; a first thermal material contained in the first storage body; a first thermal contact thermally coupled to the first point; and a second thermal contact thermally coupled to the second point, and wherein applying a force to the first thermal material may result in a temperature difference between the first point and the second point.

The system may further include: a second storage volume having a first point and a second point; and a second thermal material contained in the second reservoir, wherein at least some thermodynamic properties of the second material are different from those of the first material.

A distance between the first point and the second point of the first bank or the second bank may be less than 100 km.

The first thermal material may comprise a gas, a liquid or a solid material.

The force may comprise a volumetric force or a mechanical force.

The method for facilitating heat flow may include: employing a first reservoir having a first point and a second point; using a first thermal material contained in a first reservoir; wherein the first thermal material is subjected to a force, thereby forming a temperature difference between the first point and the second point; allowing heat flow via the first thermal material between the first thermal contact adjacent the first point and the second thermal contact adjacent the second point.

The method may further comprise: employing a second storage volume having a first point and a second point; employing a second thermal material contained in a second reservoir, wherein at least some thermodynamic properties of the second material are different from the first material; and wherein the second thermal material is subjected to a force, thereby forming a temperature difference between the first point and the second point in the second reservoir.

Applying the force may include applying a volumetric or mechanical force to the first material.

The first material may comprise a gas, liquid or solid material.

The method for facilitating heat flow may include: employing a first reservoir containing a first thermal material, the first thermal material having a first point and a second point; employing a second reservoir containing a second thermal material, the second reservoir having a first point and a second point, wherein at least some thermodynamic properties of the second material are different from those of the first material; wherein the first thermal material in the first reservoir is subjected to a force and wherein the second thermal material in the second reservoir is subjected to a force, thereby creating a temperature difference between the first point and the second point in the first reservoir and a temperature difference between the first point and the second point in the second reservoir; allowing heat to flow between a first point and a second point in the first reservoir and between a first point and a second point in the second reservoir; and allowing heat to flow between a second point in the first reservoir and a second point in the second reservoir.

The method may further include flowing heat between a third reservoir containing a third thermal material and a first point in the first thermal material in the first reservoir.

The third material may be different from the first material.

The method may further include flowing heat between a first point in the second reservoir and a fourth reservoir containing a fourth thermal material.

The fourth thermal material may be the same as or different from the second thermal material.

The method may further comprise at least partially insulating the first storage volume or the second storage volume from each other.

Flowing heat between a second point in the first reservoir and a second point in the second reservoir or between a first point and a second point in the first reservoir or in the second reservoir may include conduction, radiation, natural convection, or forced convection.

Flowing heat between a second point in the first reservoir and a second point in the second reservoir or between a first point and a second point in the first reservoir or in the second reservoir may include pumping a fluid through a heat exchanger or creating a vacuum therein.

Flowing heat between a second point in the first reservoir and a second point in the second reservoir or between a first point and a second point in the first reservoir or in the second reservoir may include transmitting electromagnetic waves.

The method may further include accelerating the first storage volume or the second storage volume.

The method may further comprise regulating the heat flow through the first storage volume or the second storage volume.

Providing the force may include applying a volumetric force within the first reservoir and the second reservoir that is constant in magnitude and direction over time during nominal operation.

The first thermal material or the second thermal material may comprise a charged element, and wherein providing the force comprises generating a potential difference between a first point and a second point in any of the first reservoir and the second reservoir.

The first material or the second material may include an electric dipole, and wherein providing the force may include generating an electric field gradient between the first point or the second point in any one of the first reservoir and the second reservoir.

Providing the force may include subjecting a first point and a second point in any one of the first storage body and the second storage body to a gravitational potential difference or accelerating the first storage body or the second storage body in an inertial space.

The first thermal material or the second thermal material may comprise a magnetic dipole, and wherein providing the force may comprise subjecting the first material or the second material to a magnetic field.

The application of force may include a thermodynamic compressor or expander.

The thermodynamic compressor or expander may comprise an axial compressor or turbine, a centrifugal compressor or turbine, or a converging or diverging tube.

The heat exchange system may include: a first storage volume having a first point and a second point; a first thermal material contained in the first storage body; a second storage volume having a first point and a second point; a second thermal material contained in a second reservoir, wherein at least some thermodynamic properties of the second material are different from those of the first material; and a thermal contact between the second point of the first reservoir and the second point of the second reservoir, such that heat can be transferred from the second point in the first reservoir to the second point in the second reservoir via the thermal contact, at which thermal contact the first reservoir is subjected to a force, which force acts to generate a temperature difference between the first point and the second point of the first reservoir, and wherein the second reservoir can be subjected to a force, which force acts to generate a temperature difference between the first point and the second point of the second reservoir.

The system may also include a third storage volume containing a third thermal material and a second heat exchanger operatively coupled to the first storage volume and the third storage volume such that heat may be exchanged from the third storage volume to the first point of the first storage volume.

The third thermal material may be the same as or different from the first thermal material.

The system may also include a fourth reservoir containing a fourth thermal material, and a thermal contact operatively coupled to the second reservoir and the fourth reservoir to enable heat to be exchanged from the first point of the second reservoir to the fourth reservoir.

The system may further include insulation along a path of heat flow between a first point and a corresponding second point in the first thermal material or the second thermal material.

The thermal contact may be achieved via conduction, radiation, natural convection or forced convection.

The first material or the second material may be configured to facilitate heat transfer between a first point and a second point in the first reservoir or the second reservoir, and wherein the heat transfer is by means of conduction, radiation, natural convection or forced convection.

The system may further include a motor to accelerate the first storage volume or the second storage volume.

The system may further include a heat flow regulator configured to regulate a flow of heat through the first storage volume, the second storage volume, or the heat exchanger.

The system may further include a force applying device configured to apply a force to the first storage body and the second storage body.

The force applying means may comprise a turbomachinery device or a volumetric force generating device.

The method for facilitating heat flow may include: employing a first reservoir containing a first thermal material, the first reservoir having a first point and a second point; using a second storage volume to transfer heat from the first storage volume to the second storage volume when the second storage volume is at a lower temperature relative to the first storage volume, or to transfer heat from the second storage volume to the first storage volume when the second storage volume is at a higher temperature relative to the first storage volume; applying a force to the first thermal material, thereby creating a temperature difference between a first point and a second point in the first reservoir; operatively coupling or operatively decoupling the second heat exchanging means disposed in the first storage body with the first heat exchanging means disposed in the second storage body, thereby allowing or preventing heat from flowing between the second heat exchanging means in the first storage body and the first heat exchanging means disposed in the second storage body; operatively coupling or operatively decoupling the third heat exchanging means disposed in the first storage body with the fourth heat exchanging means disposed in the second storage body, thereby allowing or preventing heat from flowing between the third heat exchanging means disposed in the first storage body and the fourth heat exchanging means disposed in the second storage body; driving a work exchange device to perform work on a first material; and driving the work exchange device to allow the first material to work the work exchange device.

The second reservoir may have a first point and a second point, and wherein the second reservoir contains a second thermal material having at least some different thermodynamic properties than the first thermodynamic material.

The second heat exchange means may be arranged adjacent to a first point of the first storage volume, and wherein the third heat exchange means is arranged adjacent to a second point of the first storage volume.

The first storage volume may be a closed storage volume or an open storage volume.

The method may further include disposing an insulation material between the first storage body and the second storage body.

The drive work exchange means may comprise a drive piston, a turbine or a nozzle.

The method may further comprise varying the pressure in the second reservoir.

The method may further comprise controlling the flow of heat between the second or third heat exchange means and the respective first or fourth heat exchange means.

Providing the force may include driving a work exchange device.

Employing the force may include providing an inertial force, a gravitational force, or an electromagnetic force.

The heat exchange system may include: a first reservoir containing a first thermal material having a first point and a second point; a second storage volume, wherein heat is transferred from the first storage volume to the second storage volume when the second storage volume is at a lower temperature relative to the first storage volume, or wherein heat is transferred from the second storage volume to the first storage volume when the second storage volume is at a higher temperature relative to the first storage volume; the second heat exchange means in the first storage volume may be operatively coupled and decoupled with the first heat exchange means in the second storage volume to allow or prevent heat flow between the second heat exchange means and the first heat exchange means; the third heat exchange means in the first storage volume can be operatively coupled and decoupled with the fourth heat exchange means in the second storage volume to allow or prevent heat flow between the third and fourth heat exchange means, wherein the force applied to the first thermal material creates a temperature difference between the first and second points in the first storage volume; and a drivable work exchange device, wherein driving of the work exchange device applies work to the first material, and wherein driving the work exchange device allows the first material to apply work to the work exchange device.

The second reservoir may contain a second thermal material having a first point and a second point, and wherein at least some thermodynamic properties of the second material are different from those of the first material.

The system may further include an insulation material between the first storage body and the external storage body.

The system may also include a force generation device configured to provide a force to the first material.

The force generating means may comprise an inertial force mechanism or an electromagnetic force mechanism.

The work exchange device may comprise a piston, a turbine or a nozzle.

The system may also include a thermal flow controller operatively coupled to the first or third heat exchange device and the respective first or fourth heat exchange device, the thermal flow controller configured to control a flow of heat between the first or third heat exchange device and the respective first or fourth heat exchange device.

The energy conversion system may include: a first reservoir containing a first material; a first expander having an inflow end and an outflow end, wherein the first material is input into the inflow end and output from the outflow end; a heat transfer device having a first point thermally coupled to the output stream of the first material from the first expander and configured to extract heat from or transfer heat to the first material in the output of the first expander; and a compressor configured to receive an output flow of the first working material from the heat transfer device, wherein the output flow from the compressor is released into the first storage volume.

Heat may be transferred between the first storage volume and the first material output from the first expander.

The first expander may comprise a piston, a centrifugal or axial turbine, a pipe or a nozzle.

The compressor may comprise a piston, a centrifugal or axial compressor, a pipe or a nozzle.

The heat extracted from the first material output from the outflow end of the expander may be transferred to or extracted from the first storage volume and exchanges heat with the first material output from the outflow end of the expander.

The system may further include: a second compressor having an inflow end and an outflow end, wherein a second material is input into the second compressor inflow end and output from the outflow end; the heat transfer device may have a second point thermally coupled to and configured to transfer heat to or extract heat from the material in the output flow of the second compressor, wherein the output flow of the second material from the heat transfer device is input into the input of the second expander and the output flow from the second expander is released into the first storage volume.

Heat may be transferred between the first storage volume and an output stream of the first material from the first compressor.

The second material may be the same or different from the first material.

The energy conversion system may include: a first material contained in the first storage body; a first compressor having an inflow end and an outflow end, wherein a first material is input into the first compressor inflow end and output from the outflow end; a heat transfer device having a first point thermally coupled to an output flow of the first material from the first compressor and configured to transfer heat to or extract heat from the first material in the output of the first compressor; and a first expander, wherein the output stream of the first material of the heat transfer device is input into the input of the first expander and the output stream of the first expander is released into the first storage volume.

The heat extracted from the first material output from the outflow end of the compressor can be exchanged with the first storage volume, or heat is extracted from the first storage volume and exchanged with the first material output from the outflow end of the first compressor.

The method of converting energy may include: providing a first material contained in a first reservoir; inputting a first material into an inflow end of a first expander and outputting the first material from an outflow end of the first expander; transferring heat between the first material output by the first expander and the heat transfer device; inputting the first material output from the heat transfer device into a first compressor; and releasing the output flow from the first compressor into the first storage volume.

The method may further comprise: providing a second material contained in the first reservoir; inputting a second working material into an inflow end of a second compressor; transferring heat between the heat transfer device and a second working material output by an output stream of a second compressor; and inputting the output flow from the heat transfer device into the second expander, and outputting the output flow from the output of the second expander into the first storage body.

The second material may be the same or different from the first material.

The energy conversion system may include: a first reservoir containing a first material; a first compressor having an inflow end and an outflow end, wherein a first material is input to the inflow end; an expander; a heat transfer device, wherein the output stream of the first compressor can exchange heat with a first point of the heat transfer device, and wherein the output stream from the expander can exchange heat with a second point of the heat transfer device, wherein the output stream from the first compressor is input into the expander after exchanging heat with the heat transfer device; and a second compressor, wherein the output flow from the expander flows into the second compressor after exchanging heat with the heat exchanger, and wherein the output flow from the second compressor is released into the first storage volume.

The system may also include a heat exchanger thermally coupled to the heat transfer device and configured to exchange heat with the heat transfer device.

The method of converting energy may include: providing a first material disposed in a first reservoir, inputting the first material into a first compressor; outputting the first material from the first compressor and exchanging heat with a first point in the heat transfer device; inputting the first material into an expander after exchanging heat with the heat transfer device; outputting the first material from the expander and exchanging heat with a second point in the heat transfer device; inputting the first material into a second compressor after exchanging heat with the heat transfer device; supplying power to the second compressor; and releasing the output flow from the second compressor.

The method may further include exchanging heat between the heat transfer device and a heat exchanger.

The energy conversion system may include: a first reservoir containing a first working material; a first expander having an inflow end and an outflow end, wherein a first working material is input to the inflow end; a first point of a heat transfer device configured to exchange heat with an output stream of a first working material from an outflow end of a first expander; a compressor, wherein an output stream of the first material from the first expander is input into the compressor after exchanging heat with the heat transfer device; and a second point of the heat transfer device for exchanging heat with the first working material output from the compressor, wherein, after exchanging heat with the heat transfer device, an output flow of the first working material of the compressor is input into the second expander, and wherein the output flow of the second expander is released into the first storage volume.

The method of converting energy may include: providing a first working material in a first reservoir; inputting a first working material into a first expander; exchanging heat between a first point of the heat transfer device and an output of the first expander; after exchanging heat with the heat exchanger, feeding the first working material to a compressor; supplying power to the compressor; transferring heat between a second point of the heat transfer device and an output flow of the compressor; inputting the first working material into a second expander after exchanging heat with the heat transfer device; and releasing the output flow from the second expander into the first storage volume.

The engine may include: a conduit means having an inlet and an outlet, the conduit means having a passage extending through the conduit means; a first working material disposed in the channel; a first compressor, wherein the first working material passes through the first compressor; a first heat exchanger, wherein the first working material passes through the first heat exchanger and exchanges heat between the first working material and the first heat exchanger; a first expander, wherein the first working material passes through the first expander after exiting the first compressor; a first chamber arranged within or downstream of the first compressor or within or upstream of the first expander, wherein the first heat exchanger is disposed in the first chamber; a second heat exchanger, wherein the first working material passes through the second heat exchanger and exchanges heat between the first working material and the second heat exchanger; a second compressor, wherein the first working material passes through the second compressor, and wherein the first working material exits the second compressor and exits the outlet of the conduit arrangement; a second chamber disposed within or downstream of the first expander or within or upstream of the second compressor, wherein the second heat exchanger is disposed in the second chamber; and a heat transfer device configured to transfer heat between the first heat exchanger and the second heat exchanger, wherein the heat transfer may be from the second chamber to the first chamber when net work is done by the first working material, or wherein the rate of heat transfer may be from the first chamber to the second chamber when net work is done on the working material.

The method of converting energy may include: a channel provided in the pipe arrangement; inputting a first material into the channel and into a first compressor and compressing the first material; passing the first material in or after the first compressor through a first heat exchanger; passing the first material output from the first compressor after being heated through a first expander while being heated and expanding the first working material; cooling the first working material with the second heat exchanger after or while the first working material is expanded in the first expander; and compressing the first working material after or while cooling the first working material in the second heat exchanger.

The engine may include: a first engine comprising a conduit arrangement having a passage arranged through the conduit arrangement; a first working material disposed in the channel; a first expander, wherein the first working material enters the first expander; a first heat exchanger configured to exchange heat with a first material; a first compressor, wherein the first heat exchanger is disposed within or downstream of the first expander or within or upstream of the first compressor, and wherein the first material enters the first compressor after exiting the first expander, and wherein the first material exits the first compressor.

The engine may further include: a second engine comprising a conduit arrangement having a passage disposed therein; a second working material disposed in the channel; a second compressor, wherein the second working material is input into the second compressor; a second heat exchanger configured to transfer heat with a second working material; and a second expander, wherein the second heat exchanger is arranged within or downstream of the second compressor or upstream of or within the second expander, and wherein the second working material is input into the second expander after leaving the second compressor.

The first material may be the same or different from the second material.

The method of converting energy may include: providing a first engine comprising a conduit arrangement having a passage arranged through the conduit arrangement; passing a first working material along a channel; inputting a first working material into a first expander; passing the first working material through a first heat exchanger and exchanging heat between the first working material and the first heat exchanger; the first working material is compressed in a first compressor, wherein a first heat exchanger is arranged in a first chamber arranged within or downstream of the first expander or within or upstream of the first compressor.

The method may further comprise: providing a second engine comprising an internal device disposed in a conduit device having a passage disposed therebetween; disposing a second working material in the channel; inputting a second working material into a second compressor; passing the second working material through a second heat exchanger and exchanging heat between the second working material and the second heat exchanger; the second working material is input into a second expander, and wherein the second heat exchanger is arranged in a second chamber arranged within or downstream of the second compressor or within or upstream of the second expander.

The second working material may be the same or different from the first working material.

The foregoing detailed description includes references to the accompanying drawings, which form a part of the detailed description. The drawings show, by way of illustration, specific embodiments in which the invention may be practiced. The embodiments are also referred to herein as "examples". The examples may include elements in addition to those shown or described. However, the inventors also contemplate examples providing only those elements shown or described. Moreover, the inventors contemplate examples using any combination or permutation of those elements shown or described (or one or more aspects thereof), with respect to a particular example (or one or more aspects thereof), or with respect to other examples (or one or more aspects thereof) shown or described herein.

In the event of usage inconsistencies between this document and any document incorporated by reference, the usage in this document controls.

In this document, the terms "a" or "an" are used, as is common in patent documents, to include one or more than one, independent of any other examples or usages of "at least one" or "one or more than one". In this document, unless otherwise indicated, the term "or" is used to indicate a non-exclusive or such that "a or B" includes "a but not B", "B but not a", and "a and B". In this document, the terms "including" and "wherein" are used as shorthand, English equivalents of the respective terms "comprising" and "wherein". Thus, in the following claims, the terms "comprises" and "comprising" are open-ended, i.e., a system, apparatus, article, composition, system description, or process that comprises an element other than those listed after the term in a claim is still considered to be within the scope of that claim. Furthermore, in the following claims, the terms "first," "second," and "third," etc. are used merely as labels, and are not intended to impose numerical requirements on their objects.

The above description is intended to be illustrative, and not restrictive. For example, the above-described examples (or one or more aspects thereof) may be used in combination with each other. Other embodiments may be used, such as by one of ordinary skill in the art, upon reviewing the above description. The abstract is provided to enable the reader to quickly ascertain the nature of the technical disclosure. At the time of filing, it should not be used to interpret or limit the scope or meaning of the claims. Thus, in the foregoing detailed description, various features may be grouped together to simplify the disclosure. This should not be interpreted as intending that an unclaimed disclosed feature is essential to any claim. Rather, inventive subject matter may lie in less than all features of a particular disclosed embodiment. Thus, where each claim independently exists as a separate embodiment, the following claims are hereby incorporated into the detailed description as examples or embodiments, and it is contemplated that the embodiments may be combined with each other in various combinations or permutations. The scope of the invention should be determined with reference to the appended claims, along with the full scope of equivalents to which such claims are entitled.

Claims

1. A heat exchange system, the system comprising:

a first storage volume having a first point and a second point;

a first thermal material contained in the first storage body;

a first thermal contact thermally coupled to the first point; and

a second thermal contact thermally coupled to the second point, and

wherein applying a force to the first thermal material can result in a temperature difference between the first point and the second point.

2. The system of claim 1, further comprising:

a second storage volume having a first point and a second point; and

a second thermal material contained in the second reservoir, wherein at least some thermodynamic properties of the second material are different from the first material.

3. The system of claim 2, wherein a distance between the first point and the second point is less than 100 kilometers.

4. The system of claim 1, wherein a distance between the first point and the second point is less than 100 kilometers.

5. The system of claim 1, wherein the first thermal material comprises a gas, a liquid, or a solid material.

6. The system of claim 1, wherein the force comprises a volumetric force or a mechanical force.

7. A method for promoting heat flow, the method comprising:

employing a first reservoir having a first point and a second point;

with the first thermal material contained in the first reservoir,

wherein the first thermal material is subjected to a force, thereby creating a temperature difference between the first point and the second point;

allowing heat flow via the first thermal material between a first thermal contact adjacent the first point and a second thermal contact adjacent the second point.

8. The method of claim 7, further comprising:

employing a second storage volume having a first point and a second point;

employing a second thermal material contained in the second reservoir, wherein at least some thermodynamic properties of the second material are different from the first material; and

wherein the second thermal material is subjected to a force, thereby forming a temperature difference between the first point and the second point in the second reservoir.

9. The method of claim 7, wherein applying the force comprises applying a volumetric or mechanical force to the first material.

10. The method of claim 7, wherein the first material comprises a gas, a liquid, or a solid material.

11. A method for promoting heat flow, the method comprising:

employing a first reservoir containing a first thermal material, the first thermal material having a first point and a second point;

using a second reservoir containing a second thermal material, the second reservoir having a first point and a second point,

wherein at least some thermodynamic properties of the second material are different from the first material;

wherein the first thermal material in the first reservoir is subjected to a force and wherein the second thermal material in the second reservoir is subjected to a force, thereby creating a temperature difference between a first point and a second point in the first reservoir and a temperature difference between a first point and a second point in the second reservoir;

allowing heat to flow between a first point and a second point in the first reservoir and between a first point and a second point in the second reservoir; and

allowing heat to flow between a second point in the first reservoir and a second point in the second reservoir.

12. The method of claim 11, further comprising flowing heat between a third reservoir containing a third thermal material and a first point in the first thermal material in the first reservoir.

13. The method of claim 12, wherein the third material is different from the first material.

14. The method of claim 11, further comprising flowing heat between a first point in the second reservoir and a fourth reservoir containing a fourth thermal material.

15. The method of claim 14, wherein the fourth thermal material is different from the second thermal material.

16. The method of claim 11, further comprising at least partially insulating the first storage volume or the second storage volume from each other.

17. The method of claim 11, wherein flowing heat between a second point in the first storage volume and a second point in the second storage volume or between a first point and a second point in the first storage volume or the second storage volume comprises conduction, radiation, natural convection, or forced convection.

18. The method of claim 11, wherein flowing heat between a second point in the first storage volume and a second point in the second storage volume or between a first point and a second point in the first storage volume or the second storage volume comprises pumping a fluid through a heat exchanger or creating a vacuum therein.

19. The method of claim 11, wherein flowing heat between a second point in the first reservoir and a second point in the second reservoir or between a first point and a second point in the first reservoir or the second reservoir comprises transmitting electromagnetic waves.

20. The method of claim 11, further comprising accelerating the first storage volume or the second storage volume.

21. The method of claim 11, further comprising regulating heat flow through the first storage volume or the second storage volume.

22. The method of claim 11, wherein providing the force comprises applying a volumetric force within the first and second reservoirs that is constant in magnitude and direction over time during nominal operation.

23. The method of claim 11, wherein the first thermal material or the second thermal material comprises a charged element, and wherein providing the force comprises generating a potential difference between a first point and a second point in any of the first reservoir and the second reservoir.

24. The method of claim 11, wherein the first material or the second material comprises an electric dipole, and wherein providing the force comprises creating an electric field gradient between a first point or a second point in any of the first reservoir and the second reservoir.

25. The method of claim 11, wherein providing the volumetric force comprises subjecting a first point and a second point in any of the first reservoir and the second reservoir to a gravitational potential difference or accelerating the first reservoir or the second reservoir in inertial space.

26. The method of claim 11, wherein the first or second thermal material comprises a magnetic dipole, and wherein providing the force comprises subjecting the first or second material to a magnetic field.

27. The method of claim 11, wherein applying the force comprises a thermodynamic compressor or expander.

28. The method of claim 14, wherein the thermodynamic compressor or expander comprises an axial compressor or turbine, a centrifugal compressor or turbine, or a converging or diverging tube.

29. A heat exchange system, the system comprising:

a first storage volume having a first point and a second point;

a first thermal material contained in the first storage body;

a second storage volume having a first point and a second point;

a second thermal material contained in the second reservoir, wherein at least some thermodynamic properties of the second material are different from the first material; and

thermal contact between a second point of the first reservoir and a second point of the second reservoir, such that heat can be transferred from the second point in the first reservoir to the second point in the second reservoir via the thermal contact, at which thermal contact the first reservoir is subjected to a force, which acts to create a temperature difference between the first point and the second point of the first reservoir, and wherein the second reservoir can be subjected to a force, which acts to create a temperature difference between the first point and the second point of the second reservoir.

30. The system of claim 29, further comprising: a third reservoir containing a third thermal material, and a second heat exchanger operatively coupled to the first reservoir and the third reservoir such that heat can be exchanged from the third reservoir to a first point of the first reservoir.

31. The system of claim 30, wherein the third thermal material is different from the first thermal material.

32. The system of claim 30, further comprising: a fourth reservoir containing a fourth thermal material, and a thermal contact operatively coupled to the second reservoir and the fourth reservoir such that heat can be exchanged from a first point of the second reservoir to the fourth reservoir.

33. The system of claim 32, wherein the fourth thermal material is different from the second thermal material.

34. The system of claim 29, further comprising insulation along a path of heat flow between a first point and a corresponding second point in the first or second thermal material.

35. The system of claim 29, wherein the thermal contact is achieved via conduction, radiation, natural convection, or forced convection.

36. The system of claim 29, wherein the first or second material is configured to facilitate heat transfer between a first point and a second point in the first or second storage volume, and wherein the heat transfer is by conduction, radiation, natural convection, or forced convection.

37. The system of claim 29, further comprising a motor to accelerate the first storage volume or the second storage volume.

38. The system of claim 29, further comprising a heat flow regulator configured to regulate heat flow through the first storage volume, the second storage volume, or the heat exchanger.

39. The system of claim 29, further comprising a force application mechanism configured to apply a force to the first reservoir and the second reservoir.

40. The system of claim 39, wherein the force application mechanism comprises a turbo-mechanical device.

41. The system of claim 39, wherein the force application mechanism comprises a volumetric force generating device.

42. A method of promoting heat flow, the method comprising:

employing a first reservoir containing a first thermal material, the first reservoir having a first point and a second point;

adopting a second storage body;

employing a force applied to the first thermal material, thereby creating a temperature difference between a first point and a second point in the first reservoir;

coupling or decoupling operatively the second heat exchange means disposed in the first storage volume with the first heat exchange means disposed in the second storage volume, thereby allowing or preventing heat flow between the second heat exchange means in the first storage volume and the first heat exchange means disposed in the second storage volume;

operatively coupling or operatively decoupling a third heat exchange means disposed in the first storage volume with a fourth heat exchange means disposed in the second storage volume, thereby allowing or preventing heat flow between operation of the third heat exchange means disposed in the first storage volume and the fourth heat exchange means disposed in the second storage volume or the fourth heat exchange means disposed in the second storage volume;

driving a work exchange device to perform work on the first material; and

driving the work exchange device to allow the first material to perform work on the work exchange device.

43. The method of claim 42, wherein the second reservoir has a first point and a second point, and wherein the second reservoir contains a second thermal material having at least some different thermodynamic properties than the first thermodynamic material.

44. The method of claim 42, wherein the second heat exchange device is disposed adjacent a first point of the first storage volume, and wherein the third heat exchange device is disposed adjacent a second point of the first storage volume.

45. The method of claim 42, wherein the first reservoir is a closed reservoir or an open reservoir.

46. The method of claim 42, further comprising disposing an insulating material between the first storage volume and the second storage volume.

47. A method according to claim 42, wherein driving the work exchange device comprises driving a piston, compressor, turbine or nozzle.

48. The method of claim 42, further comprising controlling the flow of heat between the second or third heat exchange device and the respective first or fourth heat exchange device.

49. A method according to claim 42, wherein providing the force comprises actuating the work exchange device in addition to actuating the work exchange device.

50. The method of claim 42, wherein employing the force comprises providing an inertial force, a gravitational force, or an electromagnetic force.

51. A heat exchange system, the system comprising:

a first reservoir containing a first thermal material having a first point and a second point;

a second storage body;

a second heat exchange means in the first storage volume, the second heat exchange means being capable of being operatively coupled and decoupled with the first heat exchange means in the second storage volume to allow or prevent heat flow between the second heat exchange means and the first heat exchange means;

the third heat exchange means in the first storage volume being capable of operatively coupling and decoupling with the fourth heat exchange means in the second storage volume to allow or prevent heat flow between the third and fourth heat exchange means,

wherein applying a force to the first thermal material creates a temperature difference between a first point and a second point in the first reservoir; and

a drivable work exchange device, wherein driving of the work exchange device applies work to the first material, an

Wherein actuation of the work exchange device allows the first material to perform work on the work exchange device.

52. The system of claim 51, wherein the first and second heat exchange devices are adjacent a first point in the first storage volume, and wherein the third and fourth heat exchange devices are adjacent a second point in the first storage volume.

53. The system of claim 51, wherein the second reservoir contains a second thermal material having a first point and a second point, and wherein at least some thermodynamic properties of the second material are different than the first material, and wherein the first heat exchanger is adjacent to the first point in the second reservoir, and wherein the fourth heat exchanger is adjacent to the second point in the second reservoir.

54. The system of claim 51, wherein the first reservoir is a closed reservoir or an open reservoir.

55. The system of claim 51, further comprising an insulating material between the first storage volume and an external storage volume.

56. The system of claim 51, further comprising a force generation device configured to provide the force to the first material.

57. The system of claim 56, wherein the force generating device comprises an inertial force mechanism or an electromagnetic force mechanism.

58. A system according to claim 51, wherein the work exchange device comprises a piston, compressor, turbine or nozzle.

59. The system of claim 51, further comprising a thermal flow controller operatively coupled to the first or third heat exchange device and the respective first or fourth heat exchange device, the thermal flow controller configured to control a flow of heat between the first or third heat exchange device and the respective first or fourth heat exchange device.

60. An energy conversion system, the system comprising:

a first reservoir containing a first material;

a first expander having an inflow end and an outflow end, wherein the first material is input into the inflow end and output from the outflow end;

a heat transfer device having a first point thermally coupled to an output stream of the first material from the first expander and configured to extract heat from or transfer heat to the first material in the output of the first expander; and

a compressor configured to receive an output flow of the first working material from the heat transfer device, wherein the output flow of the compressor is released into the first storage volume.

61. The system of claim 60, wherein heat is transferred between the first storage volume and the first material output from the first expander.

62. The system of claim 60, wherein the first expander comprises a piston, a centrifugal or axial turbine, a pipe, a volumetric force generating device, or a nozzle.

63. The system of claim 60, wherein the compressor comprises a piston, a centrifugal or axial compressor, a pipe, a volumetric force generating device, or a nozzle.

64. The system of claim 60, further comprising:

a second compressor having an inflow end and an outflow end, wherein a second material is input into the second compressor inflow end and output from the outflow end;

the heat transfer device having a second point thermally coupled to the output flow of the material from the second compressor and configured to transfer heat to or extract heat from the material in the output flow of the second compressor,

wherein the output flow of the second material from the transfer device is input into the input of the second expander and the output flow from the second expander is released into the first storage volume.

65. The system of claim 64, wherein heat is transferred between the first storage volume and an output stream of the first material from the first compressor.

66. The system of claim 64, wherein the second material is the same as the first material.

67. An energy conversion system, the system comprising:

a first material contained in the first storage body;

a first compressor having an inflow end and an outflow end, wherein the first material is input into the first compressor inflow end and output from the outflow end;

a heat transfer device having a first point thermally coupled to an output flow of the first material from the first compressor and configured to transfer heat to or extract heat from the first material in the output of the first compressor; and

a first expander, wherein an output stream of the first material from the heat transfer device is input into an input of the first expander and an output stream from the first expander is released into a first storage volume.

68. The system of claim 67, wherein heat extracted from the first material output from the outflow end of the compressor is exchanged with the first storage volume, or heat is extracted from the first storage volume and exchanged with the first material output from the outflow end of the first compressor.

69. A method of converting energy, the method comprising:

providing a first material contained in a first reservoir;

inputting the first material into an inflow end of a first expander and outputting the first material from an outflow end of the first expander;

transferring heat between the first material output from the first expander and a heat transfer device;

inputting the first material output from the heat transfer device into a first compressor; and

releasing an output flow from the first compressor into the first storage volume.

70. The method of claim 69, further comprising:

providing a second material contained in the first reservoir;

inputting the second working material into an inflow end of a second compressor;

transferring heat between the heat transfer device and the second working material output from the output flow of the second compressor; and

inputting an output stream from the heat transfer device into a second expander, and outputting an output stream from an output of the second expander into the first storage volume.

71. The method of claim 70, wherein the second material is the same as the first material.

72. An energy conversion system, the system comprising:

a first reservoir containing a first material;

a first compressor having an inflow end and an outflow end, wherein the first material is input into the inflow end;

an expander;

a heat transfer device, wherein the output flow from the first compressor is capable of exchanging heat with a first point of the heat transfer device, and wherein the output flow from the expander is capable of exchanging heat with a second point of the heat transfer device,

wherein an output stream from the first compressor is input into the expander after exchanging heat with the heat transfer device; and

a second compressor, wherein an output stream from the expander flows into the second compressor after exchanging heat with the heat exchanger, an

Wherein an output flow from the second compressor is released into the first storage volume.

73. The system of claim 72, further comprising a heat exchanger thermally coupled with the heat transfer device and configured to exchange heat with the heat transfer device.

74. A method of converting energy, the method comprising:

providing a first material arranged in a first reservoir;

inputting a first material into a first compressor;

outputting a first material from the first compressor and exchanging heat with a first point in the heat transfer device;

inputting the first material into an expander after exchanging heat with the heat transfer device;

outputting the first material from the expander and exchanging heat with a second point in the heat transfer device;

inputting the first material into a second compressor after exchanging heat with the heat transfer device;

powering the second compressor; and

releasing an output flow from the second compressor.

75. The method of claim 74, further comprising exchanging heat between the heat transfer device and a heat exchanger.

76. An energy conversion system, the system comprising:

a first reservoir containing a first working material;

a first expander having an inflow end and an outflow end, wherein the first working material is input into the inflow end;

a first point of a heat transfer device configured to exchange heat with an output stream of the first working material from the outflow end of the first expander;

a compressor, wherein an output stream of the first material from the first expander is input into the compressor after exchanging heat with the heat transfer device; and

a second point of a heat transfer device for exchanging heat with the first working material output from the compressor,

wherein the output flow of the first working material of the compressor is input into the second expander after exchanging heat with the heat transfer device, and

wherein an output flow from the second expander is released into the first storage volume.

77. The system of claim 76, further comprising a heat exchanger thermally coupled to the heat transfer device and configured to exchange heat with the heat transfer device.

78. A method of converting energy, the method comprising:

a first working material provided in a first reservoir;

inputting the first working material into a first expander;

exchanging heat between a first point of a heat transfer device and an output of the first expander;

inputting the first working material into a compressor after exchanging heat with the heat exchanger;

supplying power to the compressor;

exchanging heat between a second point of the heat transfer device and an output flow from the compressor;

inputting the first working material into the second expander after exchanging heat with the heat transfer device; and

releasing an output stream from the second expander into the first storage volume.

79. The method of claim 78, further comprising exchanging heat between the heat transfer device and a heat exchanger.

80. An engine, comprising:

a conduit means having an inlet and an outlet, the conduit means having a passage extending therethrough;

a first working material disposed in the channel;

a first compressor, wherein the first working material passes through the first compressor;

a first heat exchanger, wherein the first working material passes through the first heat exchanger and exchanges heat between the first working material and the first heat exchanger;

a first expander, wherein the first working material passes through the first expander after exiting the first compressor;

a first chamber arranged within or downstream of the first compressor or within or upstream of the first expander, wherein the first heat exchanger is arranged in the first chamber;

a second heat exchanger, wherein the first working material passes through the second heat exchanger and exchanges heat between the first working material and the second heat exchanger;

a second compressor, wherein the first working material passes through the second compressor, and wherein the first working material exits the second compressor and exits an outlet of the piping arrangement;

a second chamber disposed within or downstream of the first expander or within or upstream of the second compressor, wherein the second heat exchanger is disposed in the second chamber; and

a heat transfer device configured to transfer heat between the first heat exchanger and the second heat exchanger, wherein heat transfer is enabled from the second chamber to the first chamber when net work is done by the first working material, or wherein a heat transfer rate may be from first chamber into second chamber when net work is done on the working material.

81. A method of converting energy, the method comprising:

a channel provided in the pipe arrangement;

inputting a first material into the channel and into a first compressor and compressing the first material;

passing the first material within or after the first compressor through a first heat exchanger;

passing the first material output from the first compressor through a first expander and expanding the first working material after or while being heated;

cooling the first working material with a second heat exchanger after or while the first working material is expanded in the first expander; and

compressing the first working material after or while cooling the first working material in the second heat exchanger.

82. An engine, comprising:

a first engine comprising a conduit arrangement having a passage arranged therethrough;

a first working material disposed in the channel;

a first expander, wherein the first working material enters the first expander;

a first heat exchanger configured to exchange heat with the first material,

a first compressor, wherein the first heat exchanger is disposed within or downstream of the first expander or within or upstream of the first compressor, and wherein the first material enters the first compressor after exiting the first expander, and wherein the first material exits the first compressor.

83. The engine according to claim 82, further comprising:

a second engine comprising a conduit arrangement having a passage disposed therein;

a second working material disposed in the channel;

a second compressor, wherein the second working material is input into the second compressor;

a second heat exchanger configured to exchange heat with the second working material; and

a second expander, wherein the second heat exchanger is arranged within or downstream of the second compressor or upstream of or within the second expander, and

wherein the second working material is input into the second expander after exiting the second compressor.

84. The engine of claim 83, wherein the first material is the same material as the second material.

85. A method of converting energy, the method comprising:

providing a first engine comprising a conduit arrangement having a passage arranged therethrough;

passing a first working material along the channel;

inputting the first working material into a first expander;

passing the first working material through a first heat exchanger and exchanging heat between the first working material and the first heat exchanger;

compressing the first working material in a first compressor, wherein the first heat exchanger is arranged in a first chamber arranged within or downstream of the first expander and within or upstream of the first compressor.

86. The method of claim 85, further comprising:

providing a second engine comprising an internal device disposed in a conduit device having a passage disposed therebetween;

disposing a second working material in the channel;

inputting the second working material into a second compressor;

passing the second working material through a second heat exchanger and exchanging heat between the second working material and the second heat exchanger;

inputting the second work into a second expander, and wherein the second heat exchanger is arranged in a second chamber arranged within or downstream of the second compressor or within or upstream of the second expander.

87. The method of claim 86, wherein the second working material is the same as the first working material.