WO2019094737A1 - Refrigeration apparatus and method - Google Patents

Refrigeration apparatus and method Download PDF

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Publication number
WO2019094737A1
WO2019094737A1 PCT/US2018/060057 US2018060057W WO2019094737A1 WO 2019094737 A1 WO2019094737 A1 WO 2019094737A1 US 2018060057 W US2018060057 W US 2018060057W WO 2019094737 A1 WO2019094737 A1 WO 2019094737A1
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WO
WIPO (PCT)
Prior art keywords
reservoir
heat
point
compressor
thermal
Prior art date
Application number
PCT/US2018/060057
Other languages
English (en)
French (fr)
Other versions
WO2019094737A9 (en
Inventor
Paul NEISER
Original Assignee
Neiser Paul
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Neiser Paul filed Critical Neiser Paul
Priority to EP18875536.7A priority Critical patent/EP3707445A4/de
Priority to CN201880072393.3A priority patent/CN111316050A/zh
Publication of WO2019094737A1 publication Critical patent/WO2019094737A1/en
Publication of WO2019094737A9 publication Critical patent/WO2019094737A9/en

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24H—FLUID HEATERS, e.g. WATER OR AIR HEATERS, HAVING HEAT-GENERATING MEANS, e.g. HEAT PUMPS, IN GENERAL
    • F24H7/00—Storage heaters, i.e. heaters in which the energy is stored as heat in masses for subsequent release
    • F24H7/02—Storage heaters, i.e. heaters in which the energy is stored as heat in masses for subsequent release the released heat being conveyed to a transfer fluid
    • F24H7/04—Storage heaters, i.e. heaters in which the energy is stored as heat in masses for subsequent release the released heat being conveyed to a transfer fluid with forced circulation of the transfer fluid
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24V—COLLECTION, PRODUCTION OR USE OF HEAT NOT OTHERWISE PROVIDED FOR
    • F24V50/00—Use of heat from natural sources, e.g. from the sea
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01K—STEAM ENGINE PLANTS; STEAM ACCUMULATORS; ENGINE PLANTS NOT OTHERWISE PROVIDED FOR; ENGINES USING SPECIAL WORKING FLUIDS OR CYCLES
    • F01K3/00—Plants characterised by the use of steam or heat accumulators, or intermediate steam heaters, therein
    • F01K3/12—Plants characterised by the use of steam or heat accumulators, or intermediate steam heaters, therein having two or more accumulators
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02C—GAS-TURBINE PLANTS; AIR INTAKES FOR JET-PROPULSION PLANTS; CONTROLLING FUEL SUPPLY IN AIR-BREATHING JET-PROPULSION PLANTS
    • F02C1/00—Gas-turbine plants characterised by the use of hot gases or unheated pressurised gases, as the working fluid
    • F02C1/04—Gas-turbine plants characterised by the use of hot gases or unheated pressurised gases, as the working fluid the working fluid being heated indirectly
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D25/00—Pumping installations or systems
    • F04D25/02—Units comprising pumps and their driving means
    • F04D25/04—Units comprising pumps and their driving means the pump being fluid-driven
    • F04D25/045—Units comprising pumps and their driving means the pump being fluid-driven the pump wheel carrying the fluid driving means, e.g. turbine blades
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/58—Cooling; Heating; Diminishing heat transfer
    • F04D29/582—Cooling; Heating; Diminishing heat transfer specially adapted for elastic fluid pumps
    • F04D29/5826—Cooling at least part of the working fluid in a heat exchanger
    • F04D29/5833—Cooling at least part of the working fluid in a heat exchanger flow schemes and regulation thereto
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B21/00—Machines, plants or systems, using electric or magnetic effects
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2321/00—Details of machines, plants or systems, using electric or magnetic effects
    • F25B2321/002—Details of machines, plants or systems, using electric or magnetic effects by using magneto-caloric effects
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B29/00—Combined heating and refrigeration systems, e.g. operating alternately or simultaneously
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D20/00—Heat storage plants or apparatus in general; Regenerative heat-exchange apparatus not covered by groups F28D17/00 or F28D19/00
    • F28D2020/0065—Details, e.g. particular heat storage tanks, auxiliary members within tanks
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02B—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO BUILDINGS, e.g. HOUSING, HOUSE APPLIANCES OR RELATED END-USER APPLICATIONS
    • Y02B30/00—Energy efficient heating, ventilation or air conditioning [HVAC]

Definitions

  • Heat typically flows from a hot thermal reservoir to a cold thermal reservoir when these two thermal reservoirs are in thermal contact with each other. This heat can be transferred via conduction, for instance.
  • a conventional heat pump requires mechanical work to be done in order to transfer heat from a cold reservoir to a hot reservoir.
  • a conventional refrigerator consumes electricity in order to remove heat from the cold interior and deliver heat to the warm exterior, such as the room in which the refrigerator is located.
  • a conventional heat engine performs mechanical work by absorbing heat from a hot reservoir and transferring heat to a cold reservoir.
  • the working material absorbs heat from a hot reservoir in the boiler, and subsequently performs mechanical work, e.g. on a steam turbine, whereupon the steam transfers heat to a cold reservoir, e.g. the ocean, in the condenser.
  • FIG. 1 is a cross-sectional view of one exemplary embodiment of a heat transfer apparatus.
  • FIG. 2 is a plot of material properties for the exemplary embodiment of FIG. 1 in equilibrium.
  • FIG. 3 is a plot 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 apparatus.
  • FIG. 5 depicts a plot of pressure versus specific volume, which indicates the variation of parameters at different locations within an exemplary embodiment shown in FIGS. 6A-6B and at different points in time during one example thermodynamic cycle during operation.
  • FIG. 6A shows a plot of normalized material properties as a function of position along a length of the apparatus at a particular instant in time and FIG. 6B portrays a cross-sectional view of one exemplary apparatus.
  • FIGS. 7A-7H a cross-sectional view of the example apparatus of FIGS. 6A-6B is shown in different configurations in accordance with different points in time during one example method of operation shown in FIG. 5.
  • FIG. 8 is a plot of material properties for one example embodiment during one example method of operation of any embodiment, including Figs. 8 or 11.
  • FIG. 9 is a plot of material properties for one example embodiment during one example method of operation of any embodiment, including Figs. 9 and 13.
  • FIG. 10 is a plot of material properties for one example embodiment during one example method of operation of any embodiment, including Figs. 10 and 12.
  • FIG. 11 is a schematic representation of several embodiments of the invention.
  • FIG. 12 is a schematic representation of several embodiments of the invention.
  • FIG. 13 is a schematic representation of several embodiments of the invention.
  • FIG. 14 is a cross-sectional view of one exemplary embodiment of the refrigeration apparatus.
  • FIG. 15 is a cross-sectional view of several components of another exemplary embodiment of the refrigeration apparatus.
  • FIG. 16 is a cross-sectional view of one exemplary embodiment of a heat transfer apparatus.
  • FIG. 17 is a cross-sectional view of one exemplary embodiment of a heat transfer apparatus.
  • FIG. 18 is a cross-sectional view of one exemplary embodiment of a heat transfer apparatus.
  • FIG. 19 is a cross-sectional view of one exemplary embodiment of a heat transfer apparatus.
  • FIG. 20 is a cross-sectional view of one exemplary embodiment of an artificial heat source or artificial heat sink comprising a heat transfer apparatus.
  • Heat typically flows from a hot thermal reservoir to a cold thermal reservoir when these two thermal reservoirs are in thermal contact with each other. This heat can be transferred via conduction, for instance.
  • a conventional heat pump requires mechanical work to be done in order to transfer heat from a cold reservoir to a hot reservoir.
  • a conventional refrigerator consumes electricity in order to remove heat from the cold interior and deliver heat to the warm exterior, such as the room in which the refrigerator is located.
  • a conventional heat engine performs mechanical work by absorbing heat from a hot reservoir and transferring heat to a cold reservoir.
  • the working material absorbs heat from a hot reservoir in the boiler, and subsequently performs mechanical work, e.g. on a steam turbine, whereupon the steam transfers heat to a cold reservoir, e.g. the ocean, in the condenser.
  • thermodynamic systems interacting with each other in a thermodynamic process increases or remains constant.
  • FIG. 1 is a cross-sectional view of one exemplary embodiment of a heat transfer apparatus.
  • Various heat flows are described but this is not intended to be limiting.
  • the embodiment may include heat flow between any two points and may include heat flow between any other two points.
  • the apparatus is configured to exchange heat between two points in a reservoir or between a first reservoir 2 and a second reservoir 7.
  • the first reservoir 2 contains material A 1
  • the second reservoir 7 contains material B 8.
  • Also shown is a third reservoir 18, containing material C 16, and a fourth reservoir 19, containing material D 17.
  • FIG. 1 shows a heat exchanging apparatus 3, which is configured to facilitate heat flow between one set of two points as described below, or between any or all of the two points described below.
  • Heat flow may be between the first reservoir 2 and the third reservoir 18, a heat exchanging apparatus 20, which is configured to establish a thermal contact and facilitate heat flow between the third reservoir 18 and the fourth reservoir 19, and a heat exchanging apparatus 6, which is configured to establish a thermal contact and facilitate heat flow between the fourth reservoir 19 and the second reservoir 7.
  • Heat exchanging apparatus 3 comprises an element 13 which is in thermal contact with material A 1 in the first reservoir 2, as well as an element 4 which is in thermal contact with material C 16 in the third reservoir 18.
  • Heat exchanging apparatus 6 comprises an element 5 which is in thermal contact with material D 17 in the fourth reservoir 19, as well as an element 14 which is in thermal contact with material B 8 in the second reservoir 7.
  • Heat exchanging apparatus 20 comprises an element 23 which is in thermal contact with material C 16 in the third reservoir 18, as well as an element 24 which is in thermal contact with material D 17 in the fourth reservoir 19.
  • Each element represents the portion of the associated heat exchanging apparatus which is in direct thermal contact with the material in the associated reservoir. In FIG. 1, one can consider an element to be the portion of a heat exchanging apparatus which is not enveloped by insulating apparatus 15.
  • the three heat exchanging apparatuses 3, 6, and 20 are configured substantially identically. In other embodiments, this need not be the case.
  • the heat exchanging elements 4, 5, 13, 14, 23, and 24 are configured to exchange heat with the respective materials via conduction and via electromagnetic waves.
  • the aforementioned heat exchanging elements may be solid, and may be made of a material such as copper.
  • other methods of establishing the thermal contact between the heat exchanging elements and the respective materials in the associated reservoirs, such as element 23 and material C 16 in the third reservoir 18, may be employed.
  • the thermal contact between the elements of a particular heat exchanging apparatus can be arranged in several ways.
  • heat flow between related elements is enabled by thermal conduction.
  • heat absorbed by element 23 is able to flow to element 24 via the physical contact between said elements.
  • this physical contact is provided by a third element of a heat exchanging apparatus, where the third element extends through, and is enveloped by, insulating apparatus 15.
  • all three elements of a heat exchanging apparatus are made of the same material.
  • a heat exchanging apparatus may be constructed of a single piece of material.
  • a heat exchanging element such as element 23 may comprise a fluid which can be configured to flow through a cavity within the heat exchanging element.
  • the heat exchanging element may take the shape similar to the shapes shown in FIG. 1, with the exception that the elements do not have a solid cross-section but rather a tubular cross-section enclosing the
  • a separate pump can be configured to move the fluid around a closed path, such as the path formed by the elements of a heat exchanging apparatuses shown in FIG. 1.
  • Said fluid can be employed to absorb heat as it travels through a particular heat exchanging element such as element 23.
  • the fluid can be subsequently or simultaneously pumped to the second heat exchanging element of the heat exchanging apparatus, such as element 24 of heat exchanging apparatus 20. While traveling through the second heat exchanging element the fluid can transfer heat via conduction to the second heat exchanging element and subsequently to the adjacent material, such as material D 17 in the fourth reservoir 19.
  • the aforementioned fluid can be water or a gas such as air, or any other suitable fluid.
  • a suitable fluid for a given application such as a fluid with a high coefficient of thermal conductivity and a low viscosity.
  • the fluid and cavity within a heat exchanging element can also be configured to allow for natural convection of the fluid through the cavity.
  • the absorption of heat may reduce the density of the fluid, which may lead to the natural convection of the fluid from one element, such as element 23, to another element, such as element 24, due to buoyancy effects.
  • the thermal contact between the elements of a particular heat exchanging apparatus can be facilitated via electromagnetic waves.
  • a first heat exchanging element such as element 23, may be separated from a second heat exchanging element, such as element 24, by a vacuum.
  • the interface between the vacuum and each heat exchanging element may be configured in such a way, that a specified fraction of photons emitted by the first heat exchanging element are absorbed by the second heat exchanging element, and vice versa.
  • the gap between the first and second heat exchanging elements could be made as small as practical considerations will allow.
  • the interface area between the vacuum and each heat exchanging element could be determined by a specified heat flow rate.
  • the geometry of said interface can also be can be subject to considerations regarding the reduction of heat losses during heat flow between the first and second heat exchanging elements.
  • the optimal configuration of the heat exchanging apparatus depends on the application or intended use of the invention.
  • the gap between a first and second heat exchanging elements need not form a vacuum, but could be occupied by a fluid, such as a gas like air, or a liquid like oil.
  • the thermal contact may not only involve photons, but also conduction, and, in some embodiments, convection.
  • This relative motion can be facilitated and controlled by an electric motor, for example.
  • the mechanical connection can be established by roller bearings, or magnetic levitation bearings. In this case, additional considerations affect the
  • an additional objective may be the reduction of frictional losses associated with the relative motion.
  • the aforementioned use of electromagnetic waves or a fluid as a thermal medium between the heat exchanging elements may be favorable in that regard.
  • any apparatus which mechanically or electromagnetically connects a thermal reservoir with another thermal reservoir may also be employed to facilitate a thermal connection between the reservoirs.
  • the related heat exchanging elements may be placed in thermal contact by means of solid materials, such as metals found in roller bearings.
  • Any one heat exchanging apparatus may also comprise an apparatus for regulating or modifying the rate of heat flow through the heat exchanging apparatus.
  • Such apparatuses and methods are well known in the art.
  • the heat flow rate through a heat exchanging apparatus can be regulated by modifying the overall coefficient of thermal conductivity of the heat exchanging apparatus. This can be accomplished by placing a material of selected thermal conductivity in the path of the heat flow between the two thermal reservoirs.
  • two heat exchanging elements of a heat exchanging apparatus such as elements 23 and 24 of heat exchanging apparatus 20, may be placed in thermal contact with each other via a third element with a selected thermal conductivity.
  • the thermal conductivity of the third element can be selected in a way in which the overall thermal conductivity of the heat exchanging apparatus is modified in the desired manner.
  • the area of physical contact between two elements of a heat exchanging apparatus can be adjusted to control the heat flow rate.
  • the length of the insulated portion of the heat exchanging apparatus i.e. the portion connecting the first and second heat exchanging elements that is enveloped by insulating apparatus 15, can also be used to modify the heat flow rate.
  • the heat flow rate can be controlled by regulating the flow rate of the fluid, which in turn can be modified by controlling the operation of the pump responsible for circulating the fluid through the heat exchanging apparatus.
  • the flow rate can be modified by regulating the cross- sectional area at a suitable point along the path of the fluid throughout the convection process.
  • FIG. 1 shows an insulating apparatus 15.
  • One of the criteria for selecting and configuring insulating apparatus 15 may be the ability of the material to reduce the unintended heat flow rate from a particular reservoir contained within or enclosed by the insulating apparatus 15, such as the third reservoir 18, to another enclosed reservoir, such as the fourth reservoir 19, or to an open reservoir, such as the outside environment, or vice versa.
  • insulating apparatus 15 is a solid material with a low coefficient of thermal conductivity. While explaining the operation of the apparatus shown in FIG. 1, insulating apparatus will be treated as a substantially perfectly insulating material. In reality, insulating apparatus 15 may not be perfectly insulating.
  • insulating apparatus 15 may comprise an inside layer and an outside layer, with the outside layer separated from the inside layer by a vacuum.
  • the outside layer may be separated from the inside layer by another suitable material, such as a fluid.
  • a vacuum may improve the ability of insulating apparatus 15 to suppress unintended heat flow.
  • a vacuum or other suitable material in the space between the outside layer and the inside layer may also be useful for reducing frictional losses in embodiments involving relative motion between the outside and inside layer.
  • the outside layer may interface with a reservoir, such as the outside environment or the second reservoir 7.
  • the inside layer may interface with a different reservoir, such as the fourth reservoir 19, which may move relative to the stationary reservoir.
  • a suitable material such as a fluid with a low thermal conductivity and a low viscosity.
  • material A 1 in the first reservoir 2 and material B 8 in the second reservoir 7 are gases.
  • Material C 16 in the third reservoir 18, and material D 17 in the fourth reservoir 19 are also gases, which, for simplicity, will be treated as ideal gases.
  • thermal medium refers to any physical medium which can facilitate the transport of energy. A thermal medium is therefore not limited to the
  • a thermal medium may be a solid or a fluid, for example.
  • a thermal medium may be any type of solid, such as a crystal or glass, as well as any type of fluid, such as a liquid, gas, plasma or ferrofluid.
  • a thermal medium may also comprise individual sub- molecular particles, such as electrons or protons.
  • a thermal medium may also consist substantially of photons.
  • the reservoir containing the thermal medium may be described as a vacuum.
  • a thermal medium may also be modeled as an object capable of emitting or absorbing electromagnetic waves. Note that a thermal medium may consist of a collection or mixture of different types of materials.
  • one type of material in a thermal medium may be a particular type of molecule in gaseous form, such as dinitrogen, while another type of material in the same thermal medium may be a photon.
  • a thermal medium may also consist of an assembly of distinct collections of a particular type or form of material.
  • a portion of a thermal medium may be a solid such as copper, while another portion may be a liquid such as water, while yet a third portion may be steam, i.e. water in a gaseous phase.
  • materials A 1, B 8, C 16, and D 17, as well as heat exchanging apparatuses 3, 6 and 20 the terms
  • material and “thermal medium” are used interchangeably in this paper, since the associated materials are configured to be thermal media. Note that this also applies to cases in which a particular thermal medium may not frequently, commonly, or conventionally be referred to as a material. For instance, a photon is a thermal medium, but may not conventionally be referred to as a material.
  • material D 17 may be one type of material, such as a solid such as a metal such as copper or aluminum, while material C 16 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 material D 17 and C 16. These constraints depend on the intended use of the apparatus, as will be explained later.
  • the heat flow within a particular reservoir can take several forms.
  • the heat can be transported within a reservoir by thermal conduction, for example. This may apply to a scenario where material D 17 consists of a solid such as copper, for instance.
  • heat can be transported via natural convection, as well as other mechanisms.
  • forced convection may be employed to facilitate heat flow within a particular thermal reservoir.
  • a fan may be used to circulate a fluid within a reservoir.
  • photons may be used to transport thermal energy throughout a reservoir.
  • the interior wall of insulating apparatus 15 at the interface to a particular reservoir may be endowed with a large coefficient of reflectivity, or with similar properties conducive to the reflection of photons, in order to reduce any unintended heat flow rate from the reservoir into insulating apparatus 15.
  • FIG. 1 there is a body force per unit mass acting on material C 16 in the third reservoir 18 and material D 17 in the fourth reservoir 19.
  • the body force is constant in time, as well as constant in magnitude and direction within the entire volume of, and equal for, each of said reservoirs.
  • the body force is directed vertically downwards, towards 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.
  • the body force need not be distributed uniformly in space, or be constant in time.
  • the body force acts on at least a subset of particles within material C 16 and D 17. In other words, a subset of particles of material C 16 and material D 17 are subject to an acceleration contribution.
  • acceleration contribution is used to distinguish the contribution of the body force per unit mass to the instantaneous net acceleration of a particle within a thermal medium from the instantaneous net acceleration per se. There are numerous ways in which such body forces per unit mass can be generated.
  • One type of such a body force per unit mass is the gravitational acceleration acting on a thermal medium.
  • a body force may arise from the existence of a potential field gradient.
  • a potential field gradient is the force which arises from the gradient of an electric potential.
  • the elements of a thermal medium can be configured to be electrically charged.
  • the term "elements" refers to the constituent parts of the thermal medium, such as sub-molecular particles, molecules, or a distinct or specified collection of molecules, for example.
  • the molecules could be positively or negatively ionized, for instance.
  • the thermal medium may also comprise a collection of mobile electrons. Note that this collection may be contained in a solid, such as a conductor, or it may be described as a gas.
  • elements of the thermal medium may be polarized by applying an electric field, or these elements may already have an intrinsic polarization, as in the case of polar molecules, such as dihydrogen monoxide.
  • these polarized elements When placed in an electric field gradient, these polarized elements can experience a body force.
  • the magnitude of said force depends on the orientation of the polarization axis relative to the electric field, amongst other parameters.
  • an electric field can be configured to generate body forces per unit mass on the polar elements in the thermal medium in a reservoir, as well as polarize elements in the thermal medium, if necessary.
  • the electric field can be applied in a myriad of ways known in the art.
  • the thermal medium may comprise diamagnetic, paramagnetic, or ferromagnetic elements.
  • the individual elements in the thermal medium may form magnetic dipoles, or these elements may already have an intrinsic magnetic dipole, such as an electron.
  • these magnetic dipoles are placed in a magnetic field with a non-zero curl or gradient, they can experience a body force.
  • the magnitude of the body force is a function of the orientation of the magnetic dipole relative to the local magnetic field, amongst other parameters.
  • an external magnetic field can be configured to generate body forces per unit mass on the magnetized elements in the thermal medium in a reservoir, as well as magnetize the elements in the thermal medium, if necessary.
  • the magnetic field can be generated by ferromagnets other at least
  • the body forces per unit mass may also arise from inertial effects.
  • a reservoir may be subject to an acceleration in an inertial frame. This results an acceleration of the thermal medium relative to the reservoir.
  • Inertial forces can be generated by linear acceleration, i.e. motion of the reservoir along a straight line in the inertial frame.
  • Inertial forces can also be generated by angular acceleration, i.e. motion of the reservoir along a curved path.
  • inertial forces can be generated by any accelerating motion in an inertial frame.
  • the depicted apparatus undergoes circular motion in an inertial frame, where the radius and angular velocity remain constant.
  • the axis of rotation could be parallel to and coincident with a horizontal line passing through the centroid of the depicted portion of the cross-section of the first reservoir 2 and the second reservoir 7, for example.
  • the centripetal acceleration varies linearly with radius in this embodiment. If a substantially uniform body force per unit mass of thermal medium is desired, the depicted apparatus can be located at a larger radius, where the radial dimension of the apparatus is only a fraction of said radius.
  • the radius can be increased by placing the horizontal axis of rotation further upwards towards the top of the page in FIG. 1.
  • the direction vector of the axis of rotation can lie anywhere in a plane perpendicular to the plane of the page and intersecting the plane of the page horizontally.
  • Other embodiments can have different locations and orientations of the axis of rotation, as well as different rotational velocities. These parameters may also vary in time. Embodiments employing other types of forces or combinations thereof are within the scope of the invention.
  • the potential in this context is a mathematical construct, and need not have a physical manifestation.
  • 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. In general, this set describes a three dimensional equipotential surface. For example, consider a simplified case in which a thermal medium inside a thermal reservoir is subject to a body force per unit mass, where the body force is uniform in magnitude and direction throughout the reservoir and constant in time.
  • the thermal reservoir is an isolated system, i.e. closed and perfectly insulated, and has the shape of a cylinder with length L and radius R, for instance.
  • the origin of the reference frame is the center of the circular area at the top of the cylinder, where the "top" is defined relative to the z-axis.
  • the equipotential surfaces are planes perpendicular to the z-axis.
  • a reference point may be defined to be the origin of the reference frame.
  • the value of the potential at the top of the cylinder is therefore zero, while the value of the potential at the bottom of the cylinder is equal to the negative value of the product of the body force per unit mass and the length L of the cylinder.
  • the equipotential surfaces for other embodiments can be found using similar principles.
  • the apparatus comprises a first and second thermal reservoir, where each reservoir contains a first and second thermal medium respectively, and where the first reservoir is at least partially insulated from the second reservoir as well as any other reservoir, such as the outside environment, and vice versa.
  • the thermal medium in each reservoir is subject to a body force per unit mass, which, in general, does not have a uniform magnitude or direction for different points in space and may not be constant in time.
  • At least one heat exchanging apparatus is configured to place a point B in the first thermal medium into thermal contact with a point C in the second thermal medium.
  • point B and point C are located on the same equipotential surface defined by a second potential level.
  • the second potential level may be larger or smaller than, but not equal to, the first potential level. Since this mode of operation assumes a thermal equilibrium, the temperatures at point B and point C are identical. Note that the existence of said heat exchanging apparatus is a matter of definition.
  • the definition of the first or second thermal media can be extended to encompass the heat exchanging apparatus. This approach may be favorable in embodiments in which a distinct heat exchanging apparatus is not readily identified. In these instances, the thermal media and reservoirs may be defined in a way in which a point B and a point C coincide.
  • the defining material properties of the first thermal medium within the first reservoir are configured relative to the defining material properties of the second thermal medium within the second reservoir in a way in which the change in temperature, or some other specified material property of interest, between points A and B in the first reservoir and between points D and C in the second reservoir is not equal.
  • the "defining material properties" are defined as the properties of a thermal medium which determine the change of the material properties of interest for a given change in potential for a given thermal medium.
  • a thermal medium may comprise many different types of materials, where the materials may exist as a mixture, or as an assembly of distinct materials or distinct phases of the same material.
  • a particular thermal medium may consist of different types of material.
  • a thermal medium may be a solid such as copper for a certain range of potential levels, and gas such as air along a different range of potential levels within the associated reservoir.
  • the first thermal medium is material C 16 in the third reservoir 18, and the second thermal medium is material D 17 in the fourth reservoir 19.
  • Materials C 16 and D 17 are ideal gases, insulated by insulating apparatus 15. For simplicity, these reservoirs are assumed to be perfectly insulated along the length of the reservoirs. Recall that there is a body force per unit mass acting on material C 16 in the third reservoir 18 and material D 17 in the fourth reservoir 19, where, for simplicity, the body force per unit mass is equal for both reservoirs, constant in time and constant in direction and magnitude throughout each reservoir, and directed vertically downwards.
  • heat exchanging apparatus 20 ensures that the temperature at station 21, i.e. point B, is equal to the temperature at station 22, i.e. point C.
  • the position of stations 21 and 22 along height z is identical, and points B and C are located on the same equipotential surface defined by a second potential level. In this case, the second potential level is lower than the first potential level.
  • the properties of the ideal gas inside the third reservoir 18 and the fourth reservoir 19 vary adiabatically along the vertical length of the reservoir.
  • the height z of an element of a material in such a reservoir such as material C 16 in the third reservoir 18, decreases temperature of the element increases.
  • the temperature increases linearly as height z decreases within the reservoir.
  • the material property of interest is the temperature
  • the defining material property for an ideal gas is the specific heat capacity at constant pressure.
  • other material properties may affect the change in temperature of the material along the height z of the associated reservoir.
  • the configuration of the defining material properties comprises selecting as material C 16 an ideal gas with a specific heat capacity a constant pressure which is different to that of a selected material D 17.
  • the sign and the magnitude of the difference in the defining material properties between materials C 17 and D 17 is determined by the desired sign and magnitude of the difference in the change in the material properties of interest, i.e. the temperature.
  • the change in the material properties of interest is measured between stations 10 and 21 for material C 17, and between stations 11 and 22 for material D 17.
  • FIG.2 This scenario is shown in FIG.2.
  • the y-axis of the plot in FIG.2 is the height z. Note that the units of height z are arbitrary in this case.
  • Line 25 indicates the variation of the body force per unit mass along height z, where the body force per unit mass has been normalized by its value at the point where the height z is zero.
  • line 26 portrays the variation of the normalized temperature of material D 17 in the fourth reservoir 19 along height z, where the temperature has been normalized by its value at station 11.
  • Line 27 illustrates the variation of the temperature of material C 16 in the third reservoir 18 along height z, where the temperature has also been normalized by the value of the temperature of material D 17 at station 11.
  • station 11 describes the state of material D 17 at the point where the height z is zero, while station 22 designates the state at the minimum height z.
  • Stations 10 and 21 label the corresponding states of material C 16.
  • the apparatus shown in FIG.1 can be used as an artificial heat sink for the first reservoir 2.
  • first reservoir 2 is the interior of a refrigeration unit
  • material A 1 comprises the air contained in the interior of the refrigeration unit, as well as other materials, such as the items to be refrigerated.
  • the second reservoir 7 may be the room in which the refrigeration unit is located, and material B 8 may be the air contained in that room.
  • first reservoir 2 is the interior of a refrigeration unit
  • material A 1 comprises the air contained in the interior of the refrigeration unit, as well as other materials, such as the items to be refrigerated.
  • the second reservoir 7 may be the room in which the refrigeration unit is located
  • material B 8 may be the air contained in that room.
  • this increase in temperature at station 10 propagates through the thermal medium C 16, heat exchanging apparatus 20, thermal medium D 17, and heat exchanging apparatus 6 to station 12.
  • This heat flow from the first reservoir 2 to the second reservoir 7 via the third reservoir 18 and the fourth reservoir 19 will continue until a thermal equilibrium is reached once more.
  • the apparatus shown in FIG. 1 may be used as an artificial heat source for the first reservoir 2.
  • the temperature at station 9 is higher than the temperature at station 12 when all four depicted reservoirs are in thermal equilibrium.
  • 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 at constant pressure of material C 16 is larger than the same of material D 17.
  • material C 16 may be helium, while material D 17 may be air.
  • the temperature at station 10 must be larger than the temperature at station 11. This scenario is shown in FIG. 3.
  • Line 28 illustrates the variation of the temperature of material C 16 in the third reservoir 18 along height z, where the temperature has also been normalized by the value of the temperature of material D 17 at station 11.
  • the operation of the apparatus shown in FIG 1 as an artificial heat source is similar in principle to the aforementioned operation of the apparatus as an artificial heat sink.
  • element 23 of heat exchanging apparatus 20 may be rigidly connected to element 4 of heat exchanging apparatus 3 by a solid material C 16, where the solid material may be identical to the material of heat exchanging elements 23 and 4.
  • FIG. 4 shows another exemplary embodiment.
  • the body force per unit mass is generated by means of centripetal acceleration of a material C 34 inside a third reservoir 33, which is confined by an inside insulation apparatus 56.
  • a material D 36 inside a fourth reservoir 35, which also confined by inside insulation apparatus 56 is subject to the same body force per unit mass distribution as material C 34.
  • the magnitude and direction of the body force per unit mass is not constant throughout reservoirs 33 and 35, but is instead determined by the local value of the centripetal and Coriolis accelerations, amongst other possible sources of acceleration.
  • a heat exchanger 37 is configured to exchange heat between the first reservoir 29 and the third reservoir 33.
  • electromagnetic waves are exchanged between an outside plate 40 and an inside plate 41.
  • the plate may be made of a solid material specially selected and configured for a given desired heat flow rate.
  • the material could be a metal such as copper.
  • Heat exchanger 42 is configured similarly and performs a similar function, albeit 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.
  • Heat exchanging apparatus 47 is configured to facilitate heat flow between the third reservoir 33 and the fourth reservoir 35, similar to heat exchanging apparatus 20 in FIG.1.
  • the apparatus shown in FIG.4 is cylindrically symmetric about the axis of rotation 64 of the inside insulating apparatus 56.
  • Inside insulating apparatus 56 is separated from an outside insulating apparatus 57 by a gap 65 which can be described as a vacuum in this embodiment. In other embodiments, the gap may comprise a different material, such as a fluid.
  • the inside insulating apparatus 56 contains the third reservoir 35 and the fourth reservoir 35, and is configured to rotate about axis 64 within outside insulating apparatus 57.
  • the mechanical support of inside insulating apparatus 56 is provided by magnetic levitation apparatus in this particular embodiment.
  • the magnetic levitation apparatus comprises axial inside magnets 61 and axial outside magnets, as well as radial inside magnets 63 and radial outside magnets 62 for stability.
  • An electric motor with a stator 59 and a rotor 58 provides the torque required for angular acceleration and deceleration, as well as for overcoming any sources of friction.
  • baffles arranged radially within these reservoirs.
  • the angular acceleration can also be transferred using viscous friction between the walls of the reservoirs and the materials within the reservoirs.
  • FIGS. 6A-6B are a cross-sectional view of one example apparatus shown together with a plot of normalized material properties as a function of position along a length of the apparatus at a particular point in time.
  • the example apparatus comprises a fully enclosed chamber 117, which contains a working material, which can be a fluid or solid, or a combination thereof.
  • the working fluid can be a liquid, such as water, or a gas, such as air.
  • the working fluid can also be a mixture of vapor and gas, such as a combination steam and liquid water.
  • the working fluid or solid can be any suitable material, where suitability is a function of material properties, which can be evaluated by those skilled in the art. In the depicted example embodiment, the working fluid is an ideal gas.
  • Chamber 117 forms a closed system around the working material. In other embodiments the working material and the apparatus employing it can form an open system.
  • Chamber 117 is isolated from the environment by an insulating material 110, which prevents any unintended heat exchange between the working material in chamber 117 and the outside environment, in the ideal case.
  • Elements of the outside environment are able to do work on the working material via a work exchange apparatus 107.
  • Such elements could comprise separate actuators, such as an electric motor, for example.
  • the actuators, as well as their associated energy supply or reservoir, are not shown for simplicity.
  • Such apparatuses are well known in the art.
  • work exchange apparatus 107 is a piston, with head 109 and circular shaft 108.
  • work exchange apparatus 107 can take other forms, such as an axial turbine or nozzle. These examples are particularly suitable in the case where the working material and the apparatus employing it form an open system, for instance.
  • Work exchange apparatus 107 is furthermore insulated in order to prevent or minimize any unintended heat exchange between the working material in chamber 117 and the outside environment.
  • Piston head 109 features a surface in contact with the working material, as well as an opposing surface connected to shaft 108.
  • the opposing surface is in contact with the outside material 118.
  • the opposing surface is isolated from the surrounding material 118 by an extension of the insulating material 110, for example.
  • the volume thus created by the opposing surface and the extension of the insulating material is denoted the "second chamber".
  • the second chamber and outside material 118 would be part of the aforementioned outside environment.
  • the second chamber is evacuated. This could improve the effectiveness of the insulation and reduce the energy consumed by friction during the motion of the piston.
  • the second chamber is pressurized, where the pressure is independent of the pressure of the surrounding material.
  • the pressure of the second chamber could be modified in a way in which improvements in efficiency of the actuator operating the work exchange apparatus 107 are attained.
  • the pressure of the second chamber can be controlled in a way in which the average force being exerted by the actuator on the working material in chamber 117 during one thermodynamic cycle is reduced or substantially zero. This could reduce the average power consumption of the actuator.
  • this function could be performed by a separate apparatus, such as an adjustable spring which is configured to apply a desired average force on the piston over one cycle.
  • the heat exchanging apparatuses are embodied by a coil with a high thermal conductivity.
  • An example material for the coil could be copper.
  • the heat exchanging apparatus can comprise a second working fluid specially selected for heat exchange.
  • the heat exchanging apparatus could also comprise a pump or other actuator for moving the second working fluid through the heat exchanging apparatus in order to facilitate a higher rate of heat transfer between the heat exchanging apparatus and the working material or outside material 118.
  • the second working fluid need not be contained by the heat exchanging apparatuses in a closed system.
  • the outside material 118 can be employed as the second working fluid, which is allowed to enter and exit the heat exchanging apparatuses in an open
  • thermodynamic system The second working fluid can pass through the heat exchanging apparatuses via natural or forced convection.
  • the heat exchanging apparatuses can also be specially adapted for irradiative heat transfer to and from outside material 118, or to and from the working material.
  • a vast number of alternative types and configurations of such a heat exchanging apparatuses are known in the art.
  • the first and second heat exchanging apparatuses need not be identical.
  • each outside heat exchanging apparatus can be disconnected or insulated from the corresponding inside heat exchanging apparatus.
  • an insulating gap 116 can be formed between the second outside heat exchanging apparatus 114 and the second inside heat exchanging apparatus 115.
  • an insulating gap 113 can also be formed between the first outside heat exchanging apparatus 111 and the first inside heat exchanging apparatus 112. In this embodiment, therefore, no heat is able to flow between the outside and corresponding inside heat exchanging apparatus when these two heat exchanging apparatuses are disconnected.
  • the amount of heat flow between the outside and corresponding inside heat exchanging apparatuses is modified without necessarily achieving a complete disconnection or insulation between these two heat exchanging apparatuses.
  • the heat flow can be modified in numerous ways. For example, the surface area of an outside heat exchanging apparatus can be reduced in order to reduce the rate of heat transfer between the working material inside chamber 117 and the outside material 118. In the case in which a second working fluid is employed by a heat exchanging apparatus, the flow rate of the second working fluid through the heat exchanging apparatus can be modified in order to control the rate of heat transfer between chamber 117 and the outside material 118.
  • a second material with a different thermal conductivity can be inserted into, or removed from, the thermal circuit connecting the outside and corresponding inside heat exchanging apparatuses.
  • the rate of heat transfer between chamber 117 and outside material 118 is reduced when the second material is inserted.
  • Outside material 118 can also be any type of material, such as a gas, liquid, or solid.
  • the outside material can be the contents of a thermal reservoir which is to be cooled, as exemplified by the inner chamber of a refrigerator.
  • outside material 118 is the thermal reservoir which is to be heated.
  • Outside material 118 may also be modeled as an object capable of emitting or absorbing electromagnetic waves.
  • a force per unit mass is acting on the working material in chamber 117 and the force may be a body force or a mechanical force.
  • the force is a body force per unit mass.
  • the body force per unit mass is constant in position and time throughout chamber 117. This configuration is shown in FIGS. 6A-6B, where the body force per unit mass is directed vertically downwards towards the bottom of the page. Note that this description of the direction is relative to the page only, and is unrelated to the orientation of the apparatus relative to an inertial frame, such as an inertial frame located on the surface of the earth.
  • FIG. 6A-6B illustrates the resulting variation of thermodynamic properties of the working material along the length "z" of chamber 117, where the length is measured parallel to and indicated by the y-axis of said plot.
  • line 104 indicates the variation of the body force per unit mass along length z, where the body force per unit mass has been normalized by its value at the point where the length z is equal to zero.
  • line 103 portrays the variation of the normalized specific volume along length z
  • line 105 illustrates the variation of the normalized temperature
  • line 106 the variation of the normalized pressure along length z.
  • the first outside heat exchanging apparatus 111 is connected to the first inside heat exchanging apparatus 112. Therefore the temperature of the working material inside chamber 117 at location 119 is substantially equal to the temperature of the outside material 118 at this location.
  • the temperature of outside material 118 is uniform in space and time, for simplicity. Since the body forces acting on the working material are directed towards the bottom of the page in FIGS. 6A-6B, the working material is compressed as the length z is decreased. Thus the pressure rises and the specific volume decreases.
  • the insulating material 110 around chamber 117 ensures a substantially adiabatic compression in this case, resulting in an increased temperature at location 120 compared to location 119, as indicated by line 105.
  • the walls may not be perfectly insulating, resulting in a distribution of thermodynamic properties which lies in between the adiabatic case and the isothermal case.
  • the force need not be constant in space or time in chamber 117.
  • the force generation apparatus comprises the work exchange apparatus.
  • the force generation apparatus or mechanism can be configured relative to chamber 117 in a manner in which the force can be made to vary with time, such that work can be done on and by the working material. For example, during a portion of time during which the purpose of the work exchange apparatus is to compress the working material, the force inside chamber 117 can be increased. Throughout the compression process work will be done by the body force actuation mechanism on the working material. An expansion process involving the work exchange apparatus would follow similar principles of operation.
  • body forces can be generated by a variety of methods.
  • One type of body force is the gravitational force acting on the working material.
  • Another type of body force is an inertial force, which can be generated by accelerating the depicted apparatus, comprising chamber 117 and insulating material 110, in an inertial reference frame.
  • Inertial forces can be generated by linear acceleration, i.e. motion of the apparatus along a straight line in the inertial frame.
  • Inertial forces can also be generated by angular acceleration, i.e. motion of the apparatus along a curved path.
  • inertial forces can be generated by any accelerating motion in an inertial frame.
  • the axis of rotation could be parallel to and coincident with the centerline of a circular piston shaft 108, for example. Note that the centripetal acceleration varies linearly with radius in this embodiment.
  • the depicted apparatus can be located at a larger radius, where the radial dimension of the apparatus is only a fraction of said radius.
  • the radius can be increased by placing the axis of rotation further upwards towards the top of the page in FIGS. 6A-6B,.
  • the direction vector of the axis of rotation can have components parallel to the plane described by the vector pointing perpendicularly out of the page containing FIGS. 6A-6B, as well as the vector parallel to the centerline of piston shaft 108.
  • Other embodiments can have different locations and orientations of the axis of rotation, as well as different rotational velocities. These parameters may also vary in time.
  • a further type of body force is an electromagnetic force.
  • the elements of the working material in chamber 117 can be configured to be electrically charged.
  • the term "elements" refers to the constituent parts of the material, such as subatomic particles, atoms, molecules, or a distinct or specified collection of molecules, for example.
  • the atoms or molecules could be positively or negatively ionized, for instance.
  • the working material may also comprise a collection of mobile electrons. Note that this collection may be contained in a solid, such as a conductor, or it may be described as a gas.
  • Embodiments employing other types of forces or combinations thereof are within the scope of the invention.
  • a method for exchanging heat between two reservoirs where the range of relative average temperatures of the reservoirs for which heat can be made to flow in a specified direction is increased compared to heat exchangers in the prior art.
  • the first reservoir is denoted the "working material” while the second reservoir is denoted the "external reservoir”.
  • the method comprises: subjecting the material in at least one of the two reservoirs, defined as the working material, to a body force per unit mass, such that a difference in temperature can be generated between at least two different points in the working material, where the two points can are distinct in space or time; enclosing at least a portion of the working material with an insulating material, where the enclosure and the insulating material are configured to inhibit or reduce heat flow between the working material and the external reservoir in an unintended direction, as well as facilitate the heat transfer between the external reservoir and the working material in the intended direction, where the facilitation can comprise thermally connecting a point in the working material as well as a point in the external reservoir, such that the temperature difference between these two points allows heat to flow between the two reservoirs in the intended direction, where the thermal connection can comprise placing the two reservoirs in physical contact at these two points, where physical contact can refer to electromagnetic radiation emitted by one reservoir to be absorbed by the other, where the two points may or may not be substantially coincident, or it can refer to individual material elements coming into
  • the aforementioned external reservoir can also be subjected to forces in a similar fashion as the working material. This could further increase the range of relative average temperatures between the reservoirs for which heat can be made to flow between the reservoirs in a specified direction.
  • the difference in the average temperature of a heat source and the average temperature of a heat sink can be less than or equal to zero.
  • This method can be employed to operate an artificial heat sink or artificial heat source, for example. As shown in the drawings and as will be described in the following paragraphs, said method can also be applied to the operation of a heat pump, such as a refrigerator, or heat engine.
  • the material properties of the external reservoir and working material may need to be specially configured.
  • the pressure of the external reservoir at the location of contact should match the pressure of the working material, if a steady equilibrium configuration is desired. If diffusion of the two reservoirs is to be avoided or reduced, provisions can be made.
  • the material of one reservoir could be in a different phase than the material of the other.
  • One reservoir could contain solid material, while the other contains gaseous material, for instance.
  • FIG. 5 is a plot of pressure versus specific volume, which indicates the variation of said parameters at different locations within one example apparatus and at different points in time during one example method of operation.
  • FIGS. 7A-7H a cross-sectional view of the example apparatus of FIGS. 6A-6B, is shown in different configurations in accordance with different points in time during the example method of operation shown in FIG. 5.
  • FIG. 7 A the example apparatus of FIGS. 6A-6B, is shown in a configuration that can be described as follows.
  • the first outside heat exchanging apparatus 111 and the first inside heat exchanging apparatus 112 form a closed thermal circuit, allowing heat exchange between outside material 118 and working material in chamber 117.
  • the thermodynamic properties of the working material are constant in time in the configuration shown in FIG. 7A, and the outside material and working material are in thermal equilibrium. Thus, the temperature of the working material at location 119 in FIGS.
  • thermodynamic state 81 of the working material at location 119 in FIGS. 6A-6B, is indicated in FIG. 7A and shown in FIG. 5.
  • an insulating gap 116 is present between the second outside heat exchanging apparatus 114 and the second inside heat exchanging apparatus 115.
  • a uniform body force per unit mass is acting on the working material in chamber 117, where the body force is directed vertically downwards towards the bottom of the page.
  • insulating material 110 prevents any exchange of heat between the working material and outside material 118.
  • the insulating material 110 also spatially confines the working material, i.e. it is exerting a pressure on the working material.
  • the working material can be confined by action of body forces, or interaction with other elements of the working material.
  • the working material is compressed along the negative length z of chamber 117 as indicated in the plot on the left of FIGS. 6A-6B. Since no heat is exchanged with the environment, the compression can be modeled as an adiabatic compression, resulting in an increase in temperature along the negative length z, as shown in FIGS. 6A-6B,. This adiabatic compression is also illustrated by the light dashed line 96 in FIG. 5.
  • the thermodynamic state 85 of the working material at location 120 in FIGS. 6A-6B is shown in FIG. 7A and shown in FIG. 5.
  • the average thermodynamic state 89 of the entire working material enclosed in chamber 117 in the configuration shown in FIG. 7A is also shown in FIG. 5.
  • the piston of work exchange apparatus 107 is in a retracted position, as shown.
  • FIG. 7B the equilibrium configuration shown in FIG. 7A has been disturbed by closing insulating gap 116, allowing the second outside heat exchanging apparatus 114 and the second inside heat exchanging apparatus 115 to form a closed thermal circuit.
  • the first outside heat exchanging apparatus 111 has also been disconnected from the first inside heat exchanging apparatus 112 with insulating gap 113.
  • the configuration shown in FIG. 7A the
  • thermodynamic state 85 featured a higher temperature than thermodynamic state 81, which featured the same temperature as outside material 118. Therefore, following the elimination of insulating gap 116, there is an instantaneous temperature difference between the working material at state 85 at location 120 and outside material 118. As indicated by "QOUT", heat will flow from the working material to outside material 118 until a new equilibrium configuration is reached.
  • FIG. 7C illustrates the new equilibrium configuration.
  • the temperature change of outside material 118 is negligible throughout this process. This would be a valid assumption when there is a large ratio of the mass of outside material 118 to the mass of the working material, or when there is an external energy source or sink regulating the internal energy of outside material 118. In other embodiments, there may be a non-negligible change in temperature of outside material 118 throughout one cycle. This would be desirable when the apparatus is operated as an artificial heat source or sink. Similar to the configuration in FIG. 7A, the temperature of thermodynamic state 86 is now equal to the temperature of outside material 118. In FIG.
  • thermodynamic state 86 and state 81 lie on isothermal line 94. Due to the action of the body forces, and the temperature boundary condition provided by thermodynamic state 86, the temperature at thermodynamic state 82 is lower compared to state 86.
  • Adiabatic line 97 illustrates the variation of the thermodynamic properties between state 86 and state 82 along length z of the apparatus. Note that the position of piston head 109 is unchanged in FIGS. 7A-C. Since the working material has lost thermal energy without a change in volume, the average pressure and temperature of the working material in chamber 117 have been reduced while the average specific volume has remained constant. The new average thermodynamic state 90 is therefore connected by a vertical line to the previous average thermodynamic state 89 in FIG. 5. In other embodiments, this line need not be vertical, but can have any other orientation, such as a horizontal orientation.
  • FIG. 7D work exchange apparatus 107 is employed to do work on the working material, where the work is indicated by "WIN”.
  • piston head 109 is employed by an actuator to compress the working material.
  • the configuration of the first and second heat exchanging apparatuses is unchanged compared to FIGS. 7B-7C. Therefore any increase in temperature of the working material as a result of work being done on it leads to an increase in the rate of heat flow from the working material through the second inside and outside heat exchanging apparatuses 115 and 114 to outside material 118, as indicated by "QOUT".
  • the rate of work input into the working material is controlled in such a manner, that it substantially equals the rate of heat flow from the working material to outside material 118 at all instants of time during the compression. In this case, the compression would be isothermal. In other embodiments, the compression need not be isothermal, as will be explained later.
  • FIG. 7E illustrates the new equilibrium position once work exchange apparatus 107 is no longer doing work on the working material.
  • the temperature at state 87 is equal to the temperature of outside material 118.
  • the temperature at state 83 is substantially equal to the temperature at state 82.
  • Isothermal line 95 connects state 82 and state 83.
  • the new average thermodynamic state 91 is also shown in FIG. 5.
  • Adiabatic line 98 describes the variation of the thermodynamic properties between state 83 and state 87 along length z of the apparatus. Note that the temperature at state 83 is lower than the temperature at state 87, and hence the temperature of outside material 118.
  • FIG. 7F the equilibrium configuration shown in FIG. 7E has been disturbed by closing insulating gap 113, which allows the first outside heat exchanging apparatus 111 and the second inside heat exchanging apparatus 112 to form a closed thermal circuit.
  • the second outside heat exchanging apparatus 114 has also been disconnected from the second inside heat exchanging apparatus 115 by insulating gap 116. Due to the instantaneous temperature difference between the working material at state 83 at location 119 and outside material 118, heat will flow from outside material 118 to the working material to until a new equilibrium configuration is reached. The heat flow is indicated by "QIN".
  • FIG. 7G illustrates the new equilibrium configuration.
  • the temperature at state 84 is now equal to the temperature of outside material 118.
  • Adiabatic line 99 illustrates the variation of the thermodynamic properties between state 84 and state 88 along length z of the apparatus. Note that the position of piston head 109 is unchanged in FIGS. 7E-7G.
  • the new average thermodynamic properties 92 are indicated in FIG. 5.
  • FIG. 7H the working material does work on work exchange apparatus 107, where the work is indicated by "WOUT".
  • the actuator operating the work exchange apparatus 107 is configured to be able to do work on the working material, as well as extract work from the working material.
  • the actuator and its associated energy reservoir is configured to extract or recover energy from the work done by the working material on work exchange apparatus 107.
  • the expansion process shown in FIG. 7H and FIG. 5 is isothermal.
  • any decrease in temperature of the working material as a result of its expansion results in an increase in the rate of heat flow from outside material 118 through the first outside and inside heat exchanging apparatuses 111 and 112 into the working material, as indicated by "QIN”.
  • the thermodynamic properties of the working material at location 120 throughout the isothermal expansion are described by isothermal line 93 in FIG. 5.
  • thermodynamic properties of the working material at location 120 are described by bold dashed line 102 in FIG. 5.
  • the thermodynamic properties of the working material at location 119 are described by bold dotted line 100 in FIG. 5.
  • the average thermodynamic properties of the working material in chamber 117 are described by bold line 101.
  • the aforementioned isothermal compressions or expansions need not be isothermal. They can be adiabatic, for example. In the adiabatic case, the shape or configuration of the thermodynamic properties shown in FIG. 5 will have to be changed or adapted to a new shape.
  • the temperature at the corresponding state 81 of the new shape may be configured to be lower than the corresponding temperature of the outside material, while temperature at the corresponding state 84 of the new shape can be less than or equal to the temperature of the corresponding outside material. This would ensure a closed line similar to line 100 in FIG. 5.
  • the other closed lines shown in FIG. 5 can be adapted accordingly in the aforementioned adiabatic case.
  • FIG. 8 is a plot of material properties for one example embodiment during one example method of operation.
  • the horizontal x-axis 167 denotes the specific volume of the working material in question, and the vertical y-axis 168 denotes the pressure of the working material. Note that the units shown are arbitrary and included only for the sake of example, and are not intended to limit the scope of the invention to a particular method of operation or type of working material.
  • FIG. 8 shows a first cycle and a second cycle.
  • the first cycle comprises an adiabatic compression 151 between a first station 150 and a second station 155, an isobaric expansion 152 with heat addition between second station 155 and third station 156, an adiabatic expansion 153 between third station 156 and fourth station 157, and an isobaric compression 154 with heat removal between fourth station 157 and a fifth station, which is identical to first station 150.
  • first station 150 describes the properties of a working material in the free stream, i.e. at ambient pressure and specific volume
  • fourth station 157 approximately describes the properties of a working material at the outlet or the exhaust of a thermodynamic apparatus.
  • the isobaric compression 154 can thus occur in the wake, i.e. downstream, of an embodiment of the invention.
  • the first cycle can be a closed cycle. Note that the first cycle is similar to a conventional Brayton cycle. In other embodiments, the first cycle can be similar to an Otto cycle. In other
  • the first cycle can be similar to a Diesel cycle.
  • a wide variety of different shapes or forms of the first cycle are readily conceivable.
  • the compression between station 150 and station 155 can be isothermal instead of adiabatic.
  • the second cycle comprises an adiabatic expansion 159 between a first station 150 and a second station 163, an isobaric compression 160 involving heat removal between second station 163 and third station 164, an adiabatic compression 161 between third station 164 and fourth station 165, and an isobaric expansion 162 between fourth station 165 and a fifth station, which is identical to first station 150.
  • first station 150 describes the properties of a working material in the free stream, i.e. at ambient pressure and specific volume
  • fourth station 165 approximately describes the properties of a working material at the outlet or the exhaust of a thermodynamic apparatus, such as a turboshaft engine.
  • the isobaric expansion 162 can thus occur in the wake, i.e. downstream, of an embodiment of the invention.
  • the second cycle can be a closed cycle.
  • Both the first cycle and the second cycle produce a positive mechanical work output.
  • 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.
  • the mass flow rate of working material in the first cycle need not be equal to the mass flow rate of working material in the second cycle.
  • the heat removed from the working material in the second cycle is the same heat which is added to the working material in the first cycle. The heat transfer from the colder working material between stations 163 and 164 to the hotter working material between stations 155 and 156 is facilitated by a heat transfer apparatus.
  • the working material in the first cycle need not be of the same type as the working material of the second cycle.
  • the working material of the first cycle can be air, while the working material of the second cycle can be helium, for example.
  • expansion 159 can be a compression instead, and compression 161 can be an expansion instead, where the pressure at the equivalent second station 163 of the second cycle is lower than the pressure at the second station 155 of the first cycle.
  • the first cycle produces a net mechanical work output, while the second cycle consumes work.
  • the working material does work on the environment in the first cycle, and the environment does work on the working material in this particular second cycle.
  • the first cycle and the second cycle can be configured in a manner in which the combined power output of the first and second cycles is positive.
  • FIG. 9 is a plot of material properties for one example embodiment during one example method of operation. Some features of the cycle shown in FIG. 9 as well as some of the principles of operation of the associated thermodynamic apparatuses share similarities with features and principles of operation described by the other figures, and will therefore not be described in the same detail in the context of FIG. 9, and vice versa.
  • the horizontal x-axis 193 denotes the specific volume of the working material in question, and the vertical y-axis 194 denotes the pressure of the working material.
  • the depicted thermodynamic cycle comprises a first adiabatic expansion 187 between first station 180 and second station 181, a first isobaric compression 188 to third station 182, a first adiabatic compression 189 to fourth station 183, a first isobaric expansion 190 to fifth station 184, a second adiabatic expansion 191 to sixth station 185, and a second isobaric expansion 192 to a seventh station, which is equal to first station 180.
  • first station 180 describes the properties of a working material in the free stream, e.g. air at ambient pressure and ambient specific volume
  • sixth station 185 approximately describes the properties of a working material at the outlet or the exhaust of a thermodynamic apparatus.
  • the isobaric expansion 192 can thus occur in the wake, i.e. downstream, of an embodiment of the invention.
  • the first cycle can be a closed cycle.
  • the depicted thermodynamic cycle produces a net positive mechanical work output, i.e. the working a material does work on the environment.
  • 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.
  • the heat removed from the working material during isobaric compression 188 is the same heat which is added to the working material during isobaric expansion 190. The heat transfer from the colder working material between stations 181 and 182 to the hotter working material between stations 183 and 184 is facilitated by a heat transfer apparatus.
  • the working material can be a compressible gas such as air or carbon dioxide.
  • the thermodynamic apparatus performing the compression or expansion processes can be a compressor or turbine of the axial flow type, or of the centrifugal type, for example. These processes can also be carried out in a piston.
  • FIG. 10 is a plot of material properties for one example embodiment during one example method of operation. Some features of the cycle shown in FIG. 10 as well as some of the principles of operation of the associated thermodynamic apparatuses share similarities with features and principles of operation described by the other figures, and will therefore not be described in the same detail in the context of FIG. 10, and vice versa.
  • the horizontal x-axis 218 denotes the specific volume of the working material in question, and the vertical y-axis 219 denotes the pressure of the working material.
  • the depicted thermodynamic cycle comprises a first adiabatic compression 212 between first station 205 and second station 206, a first isobaric expansion 213 to third station 207, a first adiabatic expansion 214 to fourth station 208, a first isobaric compression 215 to fifth station 209, a second adiabatic compression 216 to sixth station 210, and a second isobaric expansion 217 to a seventh station, which is equal to first station 205.
  • first station 205 describes the properties of a working material in the free stream, e.g. air at ambient pressure and ambient specific volume
  • sixth station 210 approximately describes the properties of a working material at the outlet or the exhaust of a thermodynamic apparatus.
  • the isobaric expansion 217 can thus occur in the wake, i.e. downstream, of an embodiment of the invention.
  • the first cycle can be a closed cycle.
  • thermodynamic cycle produces a net positive mechanical work output, i.e. the working a material does work on the environment, i.e. the thermodynamic apparatus it interacts with.
  • 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 which is added to the working material during isobaric expansion 213. The heat transfer from the colder working material between stations 208 and 209 to the hotter working material between stations 206 and 207 is facilitated by a heat transfer apparatus.
  • FIG. 11 is a schematic representation of a heat engine or heat pump. Some features of the cycles shown in FIG. 11 as well as some of the principles of operation of the associated thermodynamic apparatuses share similarities with features and principles of operation described by the other figures, such as FIG. 8 or FIG. 15 in particular, and will therefore not be described in the same detail in the context of FIG. 11, and vice versa.
  • a first thermodynamic cycle comprises an inflow 230 of a working material into a expander 231, the outflow 232 of which is cooled by heat transfer apparatus 236, the outflow 237 of which flows into a compressor 238 which is powered via work "WINTA" 234 by expander 231 , and the outflow 239 of which is released into the same reservoir which provides the inflow 230.
  • This reservoir can be the atmosphere, for example.
  • the surplus work 233 of the thermodynamic cycle is available as "WOUTA".
  • An expander such as expander 231
  • an expander can be a piston, an axial or centrifugal turbine, or a duct or nozzle.
  • the working material will do mechanical work on the expander.
  • a portion of this mechanical work can be recovered to do useful work, e.g. power an electric generator or produce thrust.
  • a second thermodynamic cycle comprises an inflow 241 of a working material into a compressor 242, which is powered via a work "WINTB" 244 by expander 248, and the outflow 243 of which is heated by heat transfer apparatus 236, the outflow 247 of which flows into a expander 248, the outflow 249 of which is released into the same reservoir which provides the inflow 241.
  • This reservoir can be the atmosphere, for example.
  • the surplus work 250 of the thermodynamic cycle is available as "WOUTB".
  • 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 for some embodiments.
  • FIG. 12 is a schematic representation of a heat pump or a heat engine. Some features of the cycle shown in FIG. 12 as well as some of the principles of operation of the associated thermodynamic apparatuses share similarities with features and principles of operation described by the other figures, such as FIG. 14 or FIG. 10 in particular, and will therefore not be described in the same detail in the context of FIG. 12, and vice versa.
  • the depicted thermodynamic cycle comprises an inflow 260 of working material into a first compressor 261, which is powered via a shaft 263 by expander 267, and the outflow 262 of which is heated by a heat transfer apparatus 265, the outflow 266 of which flows into a expander 267, the outflow
  • a thermal fluid within a pipe apparatus 274 is circulated by a pump in order to enhance the heat transfer from heat exchanger
  • FIG. 13 is a schematic representation of a heat pump or a heat engine. Some features of the cycle shown in FIG. 13 as well as some of the principles of operation of the associated thermodynamic apparatuses share similarities with features and principles of operation described by the other figures, such as FIG. 9 in particular, and will therefore not be described in the same detail in the context of FIG. 13, and vice versa.
  • the depicted thermodynamic cycle comprises an inflow 290 of working material into a first expander 291, the outflow 292 of which is cooled by a conventional heat exchanger 295, the outflow 296 of which flows into a compressor 297, which is powered via a shaft 293 by first expander 291 and/or via shaft 305 by second expander 301, and the outflow 298 of which is heated by a heat transfer apparatus 299, the outflow 300 of which flows into a second expander 301, the outflow 302 of which is released into the same reservoir which provides the inflow 290.
  • a thermal fluid within a pipe apparatus 304 is circulated by a pump in order to enhance the heat transfer from heat exchanger 295 to heat transfer apparatus 299. Heat flow "QINT" flows through heat transfer apparatus 299.
  • the surplus work of the thermodynamic cycle is available "WOUT" 303.
  • the location of the exchanger can be reversed with the location of the heat transfer apparatus.
  • the heat exchanger can be located downstream of compressor 297 and upstream of second expander 301, and the heat transfer apparatus can be located downstream of first expander 291 and upstream of compressor 297.
  • the heat can be transported from outflow 292 to outflow 298 via any number of heat exchangers and any type of heat transport mechanism, such as radiation, natural or forced convection, or conduction, as long as at least one suitably configured heat transfer apparatus, such as the heat transfer apparatuses shown in FIG. 1, FIG. 4, or FIG. 15, is located along the thermal path between outflow 292 and outflow 298.
  • the heat transfer apparatus such as the heat transfer apparatuses shown in FIG. 1, FIG. 4, or FIG.
  • FIG. 11 and FIG. 12 the heat is transferred from outflow 262 via forced convection of a thermal fluid through a pipe apparatus 304, and subsequently via conduction into the heat transfer apparatus 299, from which the heat is delivered to outflow 298 via conduction, radiation.
  • FIG. 14 is a cross-sectional view of one embodiment of the invention. Some features of the cycle shown in FIG. 14 as well as some of the principles of operation of the associated thermodynamic apparatuses share similarities with features and principles of operation described by the other figures, such as FIG. 12 and FIG. 10 in particular, and will therefore not be described in the same detail in the context of FIG. 14, and vice versa.
  • Engine 320 shares features and principles of operation with a conventional turbojet or turboshaft engines.
  • Engine 320 comprises a duct apparatus 321 and an inside apparatus 322.
  • Bulk material 323 of engine 320 can comprise several different material types.
  • bulk material 323 can comprise metals such as titanium or aluminum, ceramics, or composites, such as carbon fiber composites or fiberglass.
  • Inside apparatus 322 comprises an optionally annular shaped channel 342 between annular inlet 341 and annular outlet 343, and between outer inside surface 349 and interior inside surface 350.
  • the outside surface 348 of duct apparatus 321 is indicated.
  • a working material flows through channel 342 from inlet 341 to outlet 343.
  • the working material can be a compressible fluid.
  • the fluid can be a gas such as air or carbon dioxide for example. Note that liquids such as water are also compressible.
  • the working material flowing through channel 342 sequentially encounters a first compressor 324, a first heat exchanger 326, a turbine 332, a second heat exchanger 334, and a second compressor 340 before exiting through the outlet 343.
  • the first compressor 324 and the second compressor 340 can be described as axial flow compressors. Other embodiments can comprise other types of compressors.
  • the compressors can be centrifugal compressors, for example.
  • the turbine 332 is an axial flow turbine. Other embodiments can comprise other types of turbines.
  • the turbines can be centrifugal turbines, for example.
  • the compressors and turbine may comprise several rotor blades, such as rotor blade 346, and several stator blades, such as stator blade 347.
  • the rotor blades of a rotor disc are arranged circumferentially about the axis rotation, i.e. axis 369.
  • the stator blades area also arranged circumferentially.
  • a rotor disc and the downstream stator disc form a stage.
  • the turbine has 4 stages.
  • the compressors and the turbine can have at least one stage.
  • the compressors and the turbine can have at least one rotor disc, where each rotor disc has at least one rotor blade.
  • Engine 320 can therefore be described as a single spool engine.
  • the engine can be a multi-spool engine.
  • the first two turbine rotor discs counted in a downstream direction can be connected to a first drive shaft which is connected to the second and third compressor rotor discs of the first compressor 324.
  • the third turbine rotor disc can be connected to a second drive shaft which is connected to the first compressor rotor disc of the first compressor 324.
  • the third turbine rotor disc can be connected to a third drive shaft, which can power an electric generator, the propeller apparatus of a turboprop aircraft, or the fan of a turbofan aircraft, for instance.
  • the fourth turbine rotor disc can be connected to a fourth drive shaft, which is connected to all of the compressor rotor discs of the second compressor 340.
  • First heat exchanger 326 is configured to transfer heat from a heat transfer apparatus 351 to the working material in channel 342 during nominal operations.
  • the location of heat exchanger 326 inside channel 342, i.e. the portion of channel 342 located downstream of first compressor 324 and upstream of turbine 332 is denoted the heating chamber.
  • this is accomplished via forced convection of a thermal fluid by a pump, such as pump 329, through a pipe apparatus.
  • the thermal fluid can be water, oil, molten salt, or a fluid specially adapted for the application of transferring heat from a first reservoir, such as the radially outward portion of the heat transfer apparatus 351, to a second reservoir, such as the working material in the heating chamber, via forced convection.
  • the thermal fluid can undergo a phase change throughout the pipe apparatus.
  • the pipe apparatus and pump 329 facilitate the transport of said thermal fluid through the heat transfer apparatus 351 and through the working material in the heating chamber.
  • the portion of the pipe apparatus within channel 342 can be described as a counter-current heat exchanger.
  • the heat exchanger can be a co-current heat exchanger, or a cross-flow heat exchanger, for example.
  • the portion of the pipe apparatus which is in contact with the working material in channel 342 comprises several smaller pipes, such as pipe 327, in order to increase the contact area and enhance the heat flow rate from the thermal fluid to the working material.
  • the portion of the pipe apparatus of first heat exchanger 326 which is enclosed by the annular, cylindrical heat transfer apparatus 351 indicates the location where heat is transferred from the heat transfer apparatus 351 to the thermal fluid inside the pipe apparatus of first heat exchanger 326. Once the heat has been transferred from the heat transfer apparatus 351 to the thermal fluid inside the pipe apparatus, the pipe apparatus transports the thermal fluid back to the heating chamber, where heat is transferred from the thermal fluid to the working material.
  • thermal fluid heats the working material and transfers heat from the radially outward portion of the heat transfer apparatus 351 during nominal operations.
  • the term "thermal" is used only to indicate the transport of heat by the fluid, and should not be interpreted to indicate the magnitude or direction of the change of temperature of any thermal reservoirs associated with, or in thermal contact with, the thermal fluid.
  • the thermal fluid can also be described as a cooling fluid, or a refrigerant. Since the channel 342 is annular, the heat exchanger 326 is axially symmetric about axis 369.
  • Second heat exchanger 334 is configured in a similar manner as first heat exchanger 326, and vice versa. Second heat exchanger 334 is configured to transfer heat from the working material in channel 342 to the radially inward portion, or the base, of heat transfer apparatus 351 during nominal operations.
  • the location of heat exchanger 334 inside channel 342, i.e. the portion of channel 342 located downstream of turbine 332 and upstream of second compressor 340 is denoted the cooling chamber. As before, this is accomplished via forced convection of a thermal fluid by a pump, such as pump 337, through a pipe apparatus 336. Note that the thermal fluid in the second heat exchanger 334 need not be identical to the thermal fluid in the first heat exchanger 326.
  • the pipe apparatus 336 and pump 337 facilitate the transport of said thermal fluid through the heat transfer apparatus 351 and through the working material in the cooling chamber.
  • the portion of the pipe apparatus within channel 342 can be described as a counter-current heat exchanger.
  • the portion of the pipe apparatus which is in contact with the working material in channel 342 comprises several smaller pipes, such as pipe 335.
  • the portion of the pipe apparatus 336 which is enclosed by heat transfer apparatus 351 indicates the location where heat from the thermal fluid inside pipe apparatus 336 is transferred to the heat transfer apparatus 351. Once the heat has been transferred from the thermal fluid to the heat transfer apparatus 351, the pipe apparatus 336 transports the thermal fluid back to the pump and the cooling chamber, where heat is transferred from the working material to the thermal fluid.
  • Heat transfer apparatus 351 is configured to be able to transfer heat from a first thermal reservoir to a second thermal reservoir, where the temperature of the first thermal reservoir is lower than the temperature of the second thermal reservoir. During nominal operations, the temperature of the first thermal reservoir of heat transfer apparatus 351 is lower than the temperature of the second thermal reservoir.
  • the first thermal reservoir can be denoted the cold reservoir
  • the second thermal reservoir can be denoted the hot reservoir.
  • the cold reservoir comprises the working material in the cooling chamber
  • the hot reservoir comprises the working material in the heating chamber.
  • thermodynamic properties of the working material flowing through channel 342 is similar to the variation depicted in FIG. 10, and the thermodynamic system is also described by the schematic diagram shown in FIG. 12.
  • thermodynamic cycle can be described as an open cycle, since work, matter and heat are exchanged with the environment, i.e. the region outside of channel 342.
  • Other embodiments can fully enclose a working material, resulting in a closed thermodynamic cycle.
  • Some such embodiments can comprise an apparatus similar to engine 320, in addition to a channel section which connects outlet 343 with inlet 341, where said channel section comprises a third heat exchanger which is configured to transfer heat from the environment outside of the closed channel into the closed channel.
  • the third heat exchanger can be configured to transfer heat from a cold reservoir outside to a hot reservoir inside the closed channel, or from a hot reservoir outside to a cold reservoir inside the closed channel, as long as heat is transferred from the outside environment into the closed channel by the third heat exchanger.
  • the aforementioned embodiments are configured to convert thermal energy into mechanical work.
  • the amount of work is determined by the areas enclosed by the closed curves, where the sign of the work done by the working material is positive for a clockwise cycle and negative for an anti-clockwise cycle.
  • the thermal energy is determined by the net thermal energy absorbed from the external reservoir. This is the heat absorbed during the isobaric expansion 192 in FIG. 9, or the isobaric expansion 217 in FIG. 10, or the heat absorbed during the isobaric expansion 162 from which the heat released during the isobaric compression 154 is subtracted. When neglecting friction, 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 done by the working material.
  • the thermal energy is converted into mechanical work.
  • the thermodynamic system need not be closed.
  • the mass can be exchanged with an external reservoir, as discussed in the context of FIGS. 11-15.
  • the working material is identical to and sourced from the material found in the aforementioned external reservoir.
  • mechanical work can be converted into thermal energy.
  • the heat flow direction between the working material and the heat exchangers can be reversed compared to the
  • FIGS. 8-10 The direction of the cycles shown in FIGS. 8-10 can be reversed, i.e. a compression can be replaced by an expansion, and vice versa, resulting in a sign change of the work done 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 into an external reservoir.
  • engine used herein refers to both a heat engine and a heat pump.
  • 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 the depicted embodiment.
  • a portion of the wetted surface area of the fuselage or the hull of the ship can be configured to extract heat from the surrounding fluid.
  • a portion of the outside environment or a portion of the fluid not flowing through channel 342 can be cooled, and act as a heat source to the working material in the heating chamber in a similar manner in which the working material in the cooling chamber acts as a heat source to the working material in the heating chamber.
  • a portion of the fluid in contact with the fuselage or hull of the ship can be configured to transfer heat into the surrounding fluid.
  • a portion of the outside environment or a portion of the fluid not flowing through channel 342 can be heated, and act as a heat sink to the working material in the cooling chamber in a similar manner in which the working material in the heating chamber acts as a heat sink to the working material in the cooling chamber.
  • thermodynamic apparatuses such as turboshaft engines, turboprop engines, turbofan engines, piston engines, refrigerators, or air-conditioning systems, for example.
  • first and second compressors of engine 320 are replaced by a first and second turbine through which the working material is expanded, and the turbine of engine 320 is replaced by a compressor.
  • the temporal variation of the thermodynamic properties of the working material flowing through such an embodiment is similar to the variation depicted in FIG. 9, and the thermodynamic system is also described by the schematic diagram shown in FIG. 13.
  • the compressors and the turbine change the properties of the working material adiabatically.
  • the first compression, second compression, or expansion can be isothermal.
  • the heat transfer from the working material during an isothermal compression or to the working material during an isothermal expansion can be arranged in a similar manner as the heat transfer from the cooling chamber to the heating chamber in engine 320, or from the outside environment, as mentioned.
  • the first engine 390 can be replaced by a conventional heat exchanger which is configured to extract heat from a working material, such as the fluid surrounding the hull of a ship or the skin of an aircraft, such as the skin of the wing, fuselage or empennage, and transfer it to the heat transfer apparatus 472, which in turn is configured to transfer the heat to at least one engine, such as engine 431.
  • a working material such as the fluid surrounding the hull of a ship or the skin of an aircraft, such as the skin of the wing, fuselage or empennage
  • the heat transfer apparatus 472 which in turn is configured to transfer the heat to at least one engine, such as engine 431.
  • FIG. 15 is a cross-sectional view of three components of another embodiment of a heating or refrigeration system. Some features of the apparatus shown in FIG. 15, as well as some of the principles of operation of the apparatus share similarities with the apparatus shown in the other figures, such as FIG. 8 and FIG. 11 in particular, and will therefore not be described in the same detail in the context of FIG. 15, and vice versa.
  • the first component is a first engine 390
  • the second component is a heat transfer apparatus 472
  • the third component is a second engine 431.
  • First engine 390 comprises a duct apparatus 391 and an inside apparatus 392. Several components of engine 390 are substantially axially symmetric about axis 422.
  • Inside apparatus 392 comprises an optionally annular shaped channel 395 between annular inlet 394 and annular outlet 403, and between the outer inside surface and the interior inside surface.
  • a working material flows through channel 395 from inlet 394 to outlet 403.
  • the working material can be a compressible fluid.
  • the fluid can be a gas such as air, for example.
  • the turbine 396 and the compressor 402 can be described as an axial flow turbine and compressor.
  • Other embodiments can comprise other types of turbomachinery, such as centrifugal compressors or turbines, for example.
  • the principles of the invention can also be applied to embodiments comprising pistons, such as those found in a reciprocating engine or pump.
  • Heat exchanger 398 is configured to transfer heat from the working material in channel 395 to heat transfer apparatus 472 during nominal operations.
  • the location of heat exchanger 398 inside channel 395, i.e. the portion of channel 395 located upstream of compressor 402 and downstream of turbine 396 is denoted the cooling chamber.
  • this is accomplished via forced convection of a thermal fluid by a pump, such as pump 487, through pipe apparatus 486.
  • the thermal fluid can be water, or oil, or a fluid specially adapted for said forced convection.
  • the pipe apparatus and pump 487 facilitate the transport of said thermal fluid through the heat transfer apparatus 398.
  • the portion of the pipe apparatus 486 within channel 395 can be described as a counter-current heat exchanger.
  • the portion of the pipe apparatus which is in contact with the working material in channel 395 comprises several smaller pipes, such as pipe 399, in order to increase the contact area and enhance the heat flow rate from the working material to the thermal fluid.
  • the thermal fluid can transport heat through the heat exchanger 398 via natural convection.
  • the heat exchanger 398 can transport heat from the cooling chamber to the heat transfer apparatus 472 via thermal conduction.
  • the piping apparatus 486 can consist of a solid material such as copper or silver, or the piping apparatus can comprise a different suitable material, such as a material with a high coefficient of thermal conductivity. A wide variety of other methods for exchanging heat are available.
  • Second engine 431 comprises a duct apparatus 432 and an inside apparatus 433. Several components of engine 431 are substantially axially symmetric about axis 463.
  • Inside apparatus 433 comprises an annular channel 436 between annular inlet 435 and annular outlet 444, and between the outer inside surface and the interior inside surface.
  • a working material flows through channel 436 from inlet 435 to outlet 444.
  • the working material can be a compressible fluid.
  • the fluid can be a gas such as air, for example.
  • the turbine 443 and the compressor 437 can be described as an axial flow turbine and compressor.
  • Heat exchanger 439 is configured to transfer heat from heat transfer apparatus 472 to the working material in channel 436 during nominal operations.
  • the location of heat exchanger 439 inside channel 436, i.e. the portion of channel 436 located downstream of compressor 437 and upstream of turbine 443 is denoted the heating chamber. In this particular embodiment, this is
  • the thermal fluid can be water, or oil, or a fluid specially adapted for said forced convection.
  • the pipe apparatus and pump 490 facilitate the transport of said thermal fluid through the heat transfer apparatus 439.
  • the portion of the pipe apparatus 489 within channel 436 can be described as a counter-current heat exchanger.
  • the portion of the pipe apparatus which is in contact with the working material in channel 436 comprises several smaller pipes, such as pipe 440, in order to increase the contact area and enhance the heat flow rate from the thermal fluid to the working material.
  • the working material flowing through channel 436 during nominal operations is the same working material flowing through channel 395 in the depicted embodiment.
  • the working material can be air for both first engine 390 and second engine 431.
  • the working material flowing through first engine 390 and second engine 431 need not be identical.
  • Other embodiments can comprise at least one engine, such as engine 390 or engine 431.
  • Embodiments comprising a single engine can comprise a
  • the first engine 390 can be replaced by a conventional heat exchanger which is configured to exchange heat between the heat transfer apparatus 472 and a thermal reservoir.
  • the medium within the thermal reservoir can be air surrounding an aircraft or the water surrounding a ship, for example.
  • the heat transfer apparatus 472 can be configured to transfer heat from said thermal reservoir into the heating chamber of engine 431.
  • the working material flowing through engine 431 can be a gas such as air, and the working material flowing through, or interacting with, or exchanging heat with, the conventional heat exchanger can be a gas, a liquid, or any other thermal reservoir.
  • the second engine 431 can be replaced by a conventional heat exchanger, and the heat transfer apparatus 472 can be configured to transfer heat from the cooling chamber of engine 390 into a thermal reservoir in thermal contact with said heat exchanger.
  • heat transfer apparatus 472 is configured to be able to transfer heat from a first thermal reservoir to a second thermal reservoir, where the temperature of the first thermal reservoir is lower than the temperature of the second thermal reservoir. During nominal operations, the temperature of the first thermal reservoir of heat transfer apparatus 472 is lower than the temperature of the second thermal reservoir.
  • the first thermal reservoir can be denoted the cold reservoir
  • the second thermal reservoir can be denoted the hot reservoir.
  • the cold reservoir comprises the working material in the cooling chamber in engine 390
  • the hot reservoir comprises the working material in the heating chamber in engine 431.
  • Heat transfer apparatus 472 comprises a casing apparatus 473 and an annular rotating apparatus 475, which is configured to rotate relative to casing apparatus 473 during nominal operations about axis 495.
  • Casing apparatus 473 is cylindrical in shape, with the central axis of symmetry being coincident with axis 495 in this embodiment. In other words, the cross-section of casing apparatus 473 is circular when viewed along axis 495.
  • Casing apparatus 473 also comprises a hollow central shaft 484.
  • Rotating apparatus 475 is also axially symmetric about axis 495.
  • Rotating apparatus 475 encloses a central volume 496, which is annular about axis 495 and rectangular in cross-section when viewed along an axis perpendicular to axis 495, as shown.
  • Central volume 496 comprises a material which, when compressed adiabatically, can experience an increase in temperature.
  • central volume 496 comprises a compressible gas such as helium, hydrogen, or air. It can be advantageous to select a central material with a large coefficient of thermal conductivity. This can increase the rate of heat flow from the cooling chamber to the heating chamber for a given apparatus operating condition, and thus increase the net power output, ceteris paribus.
  • a small specific heat capacity at constant pressure can help reduce the mass of the heat transfer apparatus 472 for some embodiments. For instance, a smaller specific heat capacity can lead to a smaller angular rate of rotation of rotating apparatus 475, reducing the size of load carrying members.
  • central volume 496 can comprise a solid such as a metal or a liquid such as water. Note that the material in central volume 496, denoted the central material, can be of the same type as the working material flowing through channel 436 or channel 395.
  • the separation volume 497 between the rotating apparatus 475 and the casing apparatus 473 is evacuated in the depicted embodiment.
  • the separation volume 497 can comprise a fluid.
  • the fluid can be helium or lubricating oil.
  • Such a fluid can increase the pressure within separation volume 497 and reduce the mass of casing apparatus 473, without increasing the energy losses associated with the relative motion of casing apparatus 473 and rotating apparatus 475 by an unnecessarily large amount.
  • the geometry of rotating apparatus 475 can also be adapted to the large centripetal loads within the walls of rotating apparatus 475 in a manner which reduces the mass of the rotating apparatus 475 for a given heat flow rate or radius.
  • the cross-section of annular rotating apparatus 475 can be a teardrop shape, or share similarities to a teardrop shape, when viewed along an axis perpendicular to rotation axis 497, where the long axis of the teardrop is perpendicular to the rotation axis 497, and where the nominally rounded, blunt end of the teardrop is located in a radially outward direction compared to the nominally sharper end.
  • the casing apparatus can have a spherical shape.
  • the casing apparatus can have a cylindrical shape, where the central portion of the outside surface is parallel to axis 495, and the end portions are convex, i.e. rounded outwards, or concave, i.e. rounded inwards.
  • the casing apparatuses and of the rotating apparatuses are available.
  • the preferred path of the heat flow from pipe apparatus 494 to pipe apparatus 489 is from to interior inside surface 477 to interior outside surface 476 via the adjoining portion of the separation volume, through the interior wall of rotating apparatus 475 which is parallel to axis 495, through central volume 496, through the exterior wall of rotating apparatus 475 which is parallel to axis 495, from exterior inside surface 480 to exterior outside surface 479 via the adjoining portion of the separation volume, as indicated by the arrows perpendicular to axis 495.
  • the thermal fluid is transported through pipe apparatus 486 to an interior inside surface 477 via several smaller pipes, such as pipe 494. Heat can be delivered from a pipe apparatus to the interior inside surface 477 via thermal conduction.
  • Interior inside surface 477 is configured to transfer heat to the interior outside surface 476 via thermal radiation through the evacuated separation volume 497.
  • at least a portion of said heat transfer can comprise conduction through a material, such as a gas or a liquid, contained within separation volume 497.
  • at least a portion of said heat transfer can comprise thermal conduction through the components of a roller bearing between and inside surface and an opposing outside surface.
  • Interior inside surface 477 is cylindrical in shape, and encloses a portion of central shaft 484.
  • Interior outside surface 476 is also cylindrical in shape and connected to the cylindrical interior surface of rotating apparatus 475.
  • the distance of separation between interior inside surface 477 and interior outside surface 476 is as small as possible in order to maximize the rate of heat flow between said surfaces. This also applies to the distance of separation between exterior inside surface 480 and exterior outside surface 479.
  • the aforementioned inside or outside surfaces can comprise metal, such as copper or aluminium.
  • the inside surfaces and the outside surfaces comprise radial protrusions, where, in general, a protrusion of the inside surface is located between two protrusions of the outside surface.
  • a protrusion of the inside surface is located between two protrusions of the outside surface.
  • a larger interface area can increase the rate of heat transfer between the inside surface and the outside surface for a given average circumferential footprint of the inside and outside surfaces.
  • a protrusion can be an annular, flat, metal disc, where the plane of the disc is perpendicular to axis 495.
  • the metal disc can be rigidly connected to the associated surface, such as an inside surface or an outside surface.
  • a protrusion of an inside surface can be located between two protrusions of an outside surface, such that the protrusions of the inside surface and the outside surface interleave without touching.
  • the protrusions, or discs, or fins can be configured to be thin, and the gap between protrusions can be minimized.
  • the protrusions can be electrostatically charged such that the protrusions of an inside surface and the protrusions of an outside surface electrostatically repel. In this manner, thin and flexible protrusions of an inside surface can be placed in close proximity to the thin and flexible protrusions of an outside surface without the protrusions coming into contact, or touching.
  • the repulsive forces between adjacent protrusions can be provided by magnetic fields.
  • Repelling permanent magnets can be embedded in the protrusions, for example.
  • electric conductors can be embedded within the protrusions, such that electric current can be made to flow in the opposite circumferential direction in adjacent conductors of adjacent protrusions, resulting in a repulsive magnetic force.
  • a wide variety of other methods are available to ensure separation between adjacent protrusions.
  • a bearing assembly prevents the rotating apparatus 475 from contacting the casing apparatus 473.
  • the bearing assembly is not shown in FIG. 15.
  • the bearing assembly can be located on exterior inside and outside surfaces, for example. Alternatively the bearing assembly can be located on the interior inside and outside surfaces.
  • the heat transferred to the interior outside surface 476 is conducted through the interior wall of the rotating apparatus 475 and into the central material in central volume 496.
  • the material of the inside wall can comprise material with a high coefficient of thermal conductivity, such as copper or silver.
  • the heat can be transferred through the interior wall by forced convection through a separate pipe apparatus by a pump, such that heat can be transferred from interior outside surface 476 to the central material.
  • the interior wall of central volume 496 i.e. the wall closest to axis 495, can also comprise protrusions, pins, fins, or plates in order to increase the surface area of the interior wall.
  • the outside wall of central volume 496 i.e. the wall facing in a radially inward direction, can also be endowed with protrusions in order to increase the surface area.
  • baffles within central volume 496 ensure the fluid within central volume 496 rotates together with the walls of rotating apparatus 475. This is particularly relevant during acceleration or deceleration of the rate of rotation of the walls of rotating apparatus 475.
  • Each baffle is planar in this embodiment, where each plane is parallel to axis 495 and parallel to a vector perpendicular to axis 495. Other embodiments do not comprise baffles as described.
  • the material within central volume 496 can be a solid, or the viscous friction between the fluid and the walls of central volume 496 can be used to accelerate or decelerate the rate of rotation of the fluid within central volume 496 such that, in the steady state, the angular rate of rotation of the fluid matches the angular rate of rotation of the solid walls of the rotating apparatus 475.
  • the central material can be confined by electrostatic or magnetic fields as opposed to the solid walls depicted in FIG. 15.
  • the temperature of the central material increases in a radially outward direction, resulting in a larger temperature at the outside wall of central volume 496 than at the inside wall of the same.
  • the difference of the temperature at the outside wall and the inside wall of central volume 496 is denoted the internal temperature difference.
  • the magnitude of the internal temperature difference is a function of the material properties of the central material, such as the specific heat capacity at constant pressure, as well as the angular rate of rotation of the rotating apparatus 475, as well as the geometry of the rotating apparatus 475, in particular the radius of the inside wall and the radius of the outside wall, amongst other parameters.
  • the internal temperature difference should be larger than the temperature difference of the working material entering the heating chamber and the working material entering the cooling chamber.
  • heat can be made to flow through the central volume 496 in the radially outward direction via thermal conduction from a cold reservoir to a hot reservoir.
  • separation volume 497 comprising a material with a low thermal conductivity, by minimizing the size of separation volume 497, or by placing insulating material around the preferred path of the heat flow from pipe apparatus 494 to pipe apparatus 489, for example.
  • heat can be transferred from the exterior inside surface 480 to the exterior outside surface 479.
  • the heat is transferred to a thermal fluid inside pipe apparatus 489 via thermal conduction.
  • the thermal fluid inside pipe apparatus 489 is pumped by pump 490 to heat exchanger 439 in the heating chamber of engine 431, where the heat is transferred to the working material inside channel 436.
  • the heat transfer apparatus 472 can be located within an engine, such as engine 431.
  • axis 495 can be coincident with axis 463, and heat transfer apparatus 472 can be located within the volume enclosed by channel 436.
  • an engine can be located within heat transfer apparatus 472.
  • a portion of engine 390 can be located within hollow central shaft 484, with axis 422 being coincident with axis 495.
  • thermodynamic properties of the working material flowing through channel 395 is similar to the variation depicted in the second cycle in FIG. 8.
  • the temporal variation of the thermodynamic properties of the working material flowing through channel 436 is similar to the variation depicted in the first cycle in FIG. 8.
  • thermodynamic system in FIG. 15 is also described by the schematic diagram shown in FIG. 11.
  • Both the first engine 390 and the second engine 431 produce a positive mechanical work output in this embodiment.
  • axis 463, axis 495, and axis 422 are substantially coincident.
  • a portion of engine 390 can be located within hollow central shaft 484, and heat transfer apparatus 472 can be enclosed by channel 436 of engine 431. In other embodiments the order can be reversed.
  • Heat transfer apparatus 472 can enclose engine 431, both of which are enclosed by channel 395 of engine 390.
  • engine 390 can be configured in a similar manner as engine 431.
  • the working material flowing through channel 395 sequentially encounters a compressor, a cooling chamber containing heat exchanger 398, and a turbine before exiting through outlet 403.
  • the temperature of the working material exiting the compressor is lower than the temperature of the working material exiting compressor 437 in engine 431.
  • heat transfer apparatus 472 is configured to transfer heat from the working material in the cooling chamber of engine 390 to the working material in the heating chamber of engine 431. Note that engine 390 does work on the working material, while the working material does work on engine 431. Combined, engine 390 and engine 431 can be configured to produce a net positive mechanical work output.
  • the mass flow rate of working material through engine 390 need not be equal to the mass flow rate through engine 431. Therefore the amount of heat per unit mass removed from the working material in engine 390 need not be equal to the amount of heat per unit mass added to the working material in engine 431.
  • the mass flow rate of working material through engine 390 can be larger than the mass flow rate of working material through engine 431.
  • the minimum temperature of the working material in the cooling chamber can be increased. This can increase the temperature at the inside wall of central volume 496, which can increase the average coefficient of thermal conductivity of the central material, which can increase the heat flow rate from the cooling chamber to the heating chamber, which can increase the net positive power output of the combined apparatus.
  • a substantial portion of the working material exiting engine 431 through outlet 444 also enters engine 390 through inlet 394.
  • the working material having flown through engine 431 can be a small fraction of the total flow rate of working material entering engine 390.
  • ambient working material such as ambient air
  • This can increase the average temperature of the working material entering engine 390, which can increase the temperature of the working material at the cooling chamber, which can increase the net power output of the combined apparatus, as mentioned.
  • heat transfer apparatus 472 can be configured in a different manner.
  • the inertial loads on the central material can be considered to be a body force per unit mass which acts on elements of the central material in a radially outwards direction.
  • the inertial loads arise from the circular motion of the molecules of the central material rotating with rotating apparatus 475.
  • This inertial load is also referred to as a centrifugal force, which is an apparent force.
  • a wide variety of other methods and apparatuses are available for generating a body force per unit mass within a central material.
  • FIG. 16 is a cross-sectional view of one exemplary embodiment 520 of a heat transfer apparatus. Some features of the embodiment shown in FIG. 16 as well as some of the principles of operation of the embodiment share similarities with features and principles of operation described by the other figures, and will therefore not be described in the same detail in the context of FIG. 16, and vice versa.
  • FIG. 16 shows a reservoir 521 comprising a thermal material 522.
  • the thermal material 522 is a gas, where the individual molecules or atoms can be electrically polarized by an applied electric field.
  • the gas can be air, nitrogen, helium, or argon, for example.
  • thermal material 522 can be a liquid, or a solid.
  • the thermal material can also comprise permanently polarized molecules, as is the case for water.
  • An electrically and thermally insulating material 523 encompasses reservoir 521.
  • Reservoir 521 is cylindrical in shape in this embodiment. In other embodiments, reservoir 521 can be rectangular or annular in shape, for example. Reservoir 521 can take any shape in general.
  • a first heat exchanger 526 is located in the proximity of a first point 524 in reservoir 521.
  • first heat exchanger 526 comprises several fins, such as fin 530, which can be described as a planar metal plate.
  • a pipe 527 comprising a thermal fluid is rigidly attached to the fins, allowing heat to be conducted from the thermal material 522 to the fins, and from the fins into the thermal fluid within pipe 527, and vice versa.
  • the thermal fluid is pumped through the pipe by a pump, which is not shown.
  • the pipe can thus transfer heat to heat exchanger 526, or deliver heat from heat exchanger 526.
  • heat exchanger 526 can be configured differently.
  • heat exchanger 526 can employ conduction, radiation, or natural convection, as opposed to the aforementioned forced convection of the thermal fluid through pipe 527, to exchange heat between first point 524 in reservoir 521 with another reservoir, which is also not shown.
  • a second heat exchanger 531 is located in the proximity of a second point 525 in reservoir 521.
  • the second heat exchanger 531 is configured in a similar manner as first heat exchanger 526. In other embodiments, the second heat exchanger 531 can be configured in a different manner compared to first heat exchanger 526.
  • the second heat exchanger 531 comprises plates or fins, such as fin 535, and pipe 532.
  • Heat transfer apparatus 520 comprises a body force generating apparatus configured to generate a body force per unit mass with a substantial component in the vertically downwards direction, towards the bottom of the page, where the body force per unit mass is acting on the thermal material 522 within reservoir 521.
  • the body force generating apparatus comprises several collections of charge, such as a first positive collection of charge 539, a second positive collection of charge 540, a third positive collection of charge 541, and a negative collection of charge 542. These collections of charge can be contained within electrical conductors, such as a metal such as copper. A voltage difference applied between conductors, such as conductor 541 and conductor 542 will result in an accumulation of charge within both conductors. In the depicted embodiment, the net charge contained within the body force generating apparatus is zero. Electrical conductors 541, 540, and 539 are annular in shape and encompass the cylindrical reservoir 521. Electrical conductor 542 is cylindrical in shape.
  • the amount of charge contained within each collection of charge relative to other collections of charge can be regulated by regulating the voltage associated with said collection of charge relative to other collections of charge.
  • a wide variety of other configurations of collections of charge can achieve the same effect as the depicted configuration.
  • collections of charge can be located within reservoir 521.
  • the thermal material 522 is electrically polarized.
  • the component of the electrical field along the longitudinal axis of the page increases in the direction towards the bottom of the page.
  • the individual molecules of thermal material 522 experience a body force per unit mass towards the bottom of the page.
  • the temperature at second point 525 is therefore larger than the temperature at first point 524.
  • the pressure and the electric field applied to the thermal material 522 are contained by the insulating material 523 in this particular embodiment.
  • heat can be made to flow through the thermal material 522 from first heat exchanger 526 to second heat exchanger 531, or vice versa.
  • first heat exchanger 526 and second heat exchanger 531 are identical, heat will flow from the first exterior reservoir thermally connected to the first heat exchanger 526 through the first heat exchanger 526 to first point 524 and through the thermal material 522 to second point 525 and through second heat exchanger 531 to the second external reservoir thermally connected to the second heat exchanger 531.
  • the heat transfer apparatus 520 can be employed to transfer heat from a first exterior reservoir to a hotter second exterior reservoir, provided the temperature difference between the first and second exterior reservoirs is smaller in magnitude than the temperature difference between the first point 524 and the second point 525 for the given operating condition.
  • the rate of heat transfer through the heat transfer apparatus configured in accordance with the invention can be greater than an equivalent heat exchanger of the prior art.
  • An equivalent heat exchanger of the prior art can be an infinitely thin contact surface between the first reservoir and the second reservoir.
  • the rate of heat transfer through the heat transfer apparatus is a function of the thermal conductivity, as well as the temperature gradient.
  • the finite length of the heat transfer apparatus will reduce the temperature gradient by increasing the length over which the difference in temperature is measured compared to the theoretical equivalent heat exchanger and associated thermal boundary layer.
  • the built-in temperature difference of the heat transfer apparatus i.e.
  • the temperature difference between a first point and a second point in equilibrium at zero heat flow can offset this increase in length for some embodiments and some configurations, however, resulting in a larger temperature gradient and a larger rate of heat transfer from a hot reservoir to a cold reservoir.
  • FIG. 17 is a cross-sectional view of one exemplary embodiment 570 of a heat transfer apparatus.
  • FIG. 17 shows a reservoir 571 comprising a thermal material 572.
  • the thermal material 572 is a gas, where the individual molecules or atoms are positively or negatively charged.
  • thermal material 572 can be a liquid, or a solid.
  • thermal material 572 can comprise other types of mobile charges, such as free moving electrons.
  • An electrically and thermally insulating material 573 encompasses reservoir 571.
  • Reservoir 571 is cylindrical in shape in this embodiment. In other embodiments, reservoir 571 can be rectangular or annular in shape, for example. Reservoir 571 can take any shape in general.
  • a first heat exchanger 576 is located in the proximity of a first point 574 in reservoir 571 and comprises several fins and pipe 577.
  • a second heat exchanger 581 is located in the proximity of a second point 575 in reservoir 571 and comprises several fins and pipe 582. These heat exchangers are configured in a similar manner as the heat exchangers shown in FIG. 16.
  • Heat transfer apparatus 570 comprises a body force generating apparatus configured to generate a body force per unit mass with a substantial component along the long axis of the page, where the body force per unit mass is acting on the thermal material 572 within reservoir 571.
  • the body force generating apparatus comprises several collections of charge, such as a positive first collection of charge 589, a negative second collection of charge 590.
  • a wide variety of other configurations of a body force per unit mass generating apparatuses can be devised and employed to produce an electrical potential energy difference for elements of the thermal material 572 between the first point 574 and the second point 575.
  • the electrical 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.
  • the thermal material comprises positively charged ions
  • the ions will experience a body force per unit mass directed towards the bottom of the page within reservoir 571. As described in the context of FIG. 16, this results in a larger temperature at second point 575 compared to the first point 574.
  • embodiment 570 can be operated as a heat transfer apparatus in the same manner as embodiment 520 and other heat transfer apparatuses mentioned herein.
  • the direction of the body force within thermal material 572 can be reversed. This can be used to control the direction of heat flow through the heat transfer apparatus. For example, this can be used to change the mode of operation of the heat transfer apparatus 570 from the mode corresponding to an artificial heat source to the mode corresponding to an artificial heat sink.
  • the magnitude of the body force per unit mass within the reservoir 571 can be controlled.
  • the magnitude of the temperature difference between the first point 574 and the second point 575 can be controlled.
  • Other methods for controlling the heat flow through heat transfer apparatus 570 are also available.
  • the mass flow rate of the thermal fluid through pipe 582 can be modified.
  • FIG. 18 is a cross-sectional view of one exemplary embodiment 610 of a heat transfer apparatus.
  • FIG. 18 shows a reservoir 611 comprising a thermal material 612.
  • the thermal material 612 is a gas, where the individual molecules or atoms can be magnetically polarized.
  • thermal material 612 can be a liquid, or a solid.
  • thermal material 612 can comprise other types of magnetic dipoles, such as free moving electrons.
  • the magnetic dipoles can be permanent as opposed to induced by an externally applied magnetic field.
  • An electrically and thermally insulating material 613 encompasses reservoir 611.
  • Reservoir 611 is cylindrical in shape in this embodiment. In other embodiments, reservoir 611 can be rectangular or annular in shape, for example. Reservoir 611 can take any shape in general.
  • a first heat exchanger 616 is located in the proximity of a first point 614 in reservoir 611 and comprises several fins and pipe 617.
  • a second heat exchanger 621 is located in the proximity of a second point 615 in reservoir 611 and comprises several fins and pipe 622. These heat exchangers are configured in a similar manner as the heat exchangers shown in FIG. 16.
  • Heat transfer apparatus 610 comprises a body force generating apparatus configured to generate a body force per unit mass with a substantial component along the long axis of the page, where the body force per unit mass is acting on the thermal material 612 within reservoir 611.
  • the body force generating apparatus comprises several current coils, such as coil 629 forming a loop with conductor 630, coil 631 forming a loop with conductor 632, coil 633 forming a loop with conductor 634, coil 635 forming a loop with conductor 636, or coil 637 forming a loop with conductor 638.
  • Each coil carries a current which is directed out of the page on the left side of the page and into the page on the right side of the page, as indicated.
  • Each coil is made of an electrical conductor, such as copper.
  • a coil comprises superconducting material.
  • a wide variety of other configurations of a body force per unit mass generating apparatuses can be devised and employed to produce an potential energy difference for elements of the thermal material 612 between the first point 614 and the second point 615.
  • FIG. 19 is a cross-sectional view of one exemplary embodiment 650 of a heat transfer apparatus.
  • FIG. 19 shows a reservoir 651 comprising a thermal material 652.
  • the thermal material 652 is a gas, such as air, helium, or argon.
  • thermal material 652 can be a liquid.
  • a thermally insulating material 653 encompasses reservoir 651.
  • Reservoir 651 is cylindrical in shape in this embodiment. In other embodiments, reservoir 651 can be rectangular or annular in shape, for example. Reservoir 651 can take any shape in general, provided the force generating apparatus is configured to allow the heat transfer apparatus to be operated as intended.
  • a first heat exchanger 656 is located in the proximity of a first point 654 in reservoir 651 and comprises several fins and pipe 657.
  • a second heat exchanger 661 is located in the proximity of a second point 655 in reservoir 651 and comprises several fins and pipe 662.
  • the fins of the heat exchangers, such as fin 660 or fin 665 are arranged cylindrically around axis 675 in order to provide little resistance to the swirling of the thermal material 652 within reservoir 651 during nominal operations.
  • Heat transfer apparatus 650 comprises a force generating apparatus configured to generate a force with a substantial component along the long axis of the page, directed towards the bottom of the page, where the force is acting on the thermal material 652 within reservoir 651.
  • the force generating apparatus comprises an axial compressor, which is configured in a similar manner as an axial compressor of a conventional turbojet engine. Note that during nominal operations of the depicted
  • the rate of heat transfer is diminished compared to a thermal material 652 which is stationary on average. This is due to the advection of the thermal material partially cancelling the conduction of heat through the thermal material in the opposite direction.
  • the force generating apparatus can also comprise an expanding or contracting cross- sectional area of the channel through which the thermal material is flowing. This can produce a force on the thermal material in a direction upstream or downstream of the bulk flow of the thermal material respectively in an example involving subsonic bulk flow.
  • the force generating apparatus can comprise a contracting or expanding duct.
  • the force generating apparatus can comprise a centrifugal compressor.
  • the force generating apparatus can comprise coaxial, counter-rotating axial compressors.
  • the axial compressor shown in FIG. 19 comprises a drive shaft 670 connected to several rotor discs, each comprising several rotor blades, such as rotor blade 672 or rotor blade 671.
  • several stator discs comprising several blades, such as stator blade 674 or stator blade 673, are connected to the casing apparatus comprising insulating material 653.
  • the rotor and stator blades are rigidly attached to the shaft 670 or the casing apparatus in the depicted embodiment.
  • At least a portion of the blades is ratably connected to the drive shaft 670 or the casing apparatus, where the axis of rotation of said rotable connection is substantially perpendicular to axis 675.
  • This rotable connection is configured to allow the angle of attack of the stator and/or rotor blades to be controlled such that the magnitude of the force applied by the force generating apparatus on the thermal material 652 can be regulated.
  • the axial compressor shown in FIG. 19 is driven by a motor 669.
  • the motor 669 in FIG. 19 is an electric motor.
  • the motor 669 can be a piston engine, or a turboshaft engine, for example.
  • any type of power supply and any type of shaft work generating apparatus can be employed to drive the axial compressor shown in FIG. 19.
  • the depicted embodiment consumes power during nominal operations due to frictional losses of the axial compressor moving relative to the thermal material 652. These frictional losses increase the temperature of the thermal material 652, which can be desirable for some applications, such as applications in which the heat transfer apparatus is employed as an artificial heat source. Due to these frictional losses of the axial compressor, the thermal material 652 will swirl, i.e.
  • the rate of rotation of the thermal material 652 is the rate for which the torque applied by the rotating portion of the axial compressor is balanced by the torque applied by the stator, the walls, and other wetter surfaces of the reservoir 651 on the thermal material 652.
  • embodiment 610 can be operated as a heat transfer apparatus in the same manner as embodiment 520 and other heat transfer apparatuses mentioned herein.
  • the compression of the thermal material at second point 655 compared to first point 654 can be modelled 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 heat source or artificial heat sink employing a heat transfer apparatus.
  • FIG. 20 shows a heat transfer apparatus comprising a reservoir 691 which in turn comprises a thermal material 692.
  • the thermal material 692 is a gas, In other embodiments, thermal material 692 can be a liquid, or a solid
  • a thermally insulating material 693 encompasses reservoir 691.
  • Reservoir 691 is cylindrical in shape in this embodiment. In other embodiments, reservoir 691 can be rectangular or annular in shape, for example. Reservoir 691 can take any shape in general.
  • a first heat exchanger 698 is located in the proximity of a first point 695 in reservoir 691 and comprises several fins, such as fin 702, and pipe 699.
  • a second heat exchanger 703 is located in the proximity of a second point 696 in reservoir 691 and comprises several fins, such as fin 707, and pipe 704. These heat exchangers are configured in a similar manner as the heat exchangers shown in FIG. 16. The pumps which pump the thermal fluid through pipe 699 and pipe 704 are not shown for simplicity.
  • the heat transfer apparatus can be of any suitable configuration, such as a configuration shown in FIG. 16, FIG. 17, FIG. 18, or FIG. 19, or any other configuration discussed herein or within the scope of the invention.
  • Detailed features of the heat transfer apparatus such as features pertaining to the force generating apparatus, are not shown for simplicity and generality.
  • first exterior reservoir located on the portion of first heat exchanger 698 which is located outside of reservoir 691.
  • first exterior reservoir can be the earth's atmosphere.
  • a second exterior reservoir 710 comprising thermal material 711, located on the portion of second heat exchanger 703 which is located outside of reservoir 691, is shown.
  • the second exterior reservoir can be the interior of a building, a vehicle, or a refrigerator, for example.
  • the direction of the force applied to the thermal material 692, as well as the temperature of the larger exterior reservoir, i.e. the temperature at point 694 in the first exterior reservoir in this case heat can be made to flow from the first exterior reservoir to the second exterior reservoir, or vice versa.
  • the heat transfer apparatus can thus be configured to be an artificial heat source or an artificial heat sink.
  • a heat exchange system comprises a first reservoir having a first point and a second point; a first thermal material contained in the first reservoir; a first thermal contact thermally coupled with the first point; and a second thermal contact thermally coupled with the second point, and wherein application of a force to the first thermal material can result in a temperature difference between the first and second points.
  • the system may further comprise a second reservoir 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 than the first material.
  • a distance between the first point and the second point of the first reservoir or the second reservoir may be less than 100 kilometers.
  • the first thermal material may comprise a gas, a liquid, or a solid material.
  • the force may comprise a body force or a mechanical force.
  • a method for facilitating heat flow may comprise employing a first reservoir having a first point and a second point; employing a first thermal material contained in the first reservoir; where the first thermal material is subjected to a force thereby forming a temperature difference between the first and second points; allowing heat flow through the first thermal material between a first thermal contact adjacent the first point and a second thermal contact adjacent the second point.
  • the method may further comprise employing a second reservoir 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 than the first material; and wherein the second thermal material is subjected to a force thereby forming a temperature difference between the first and second points in the second reservoir.
  • Applying the force may comprise applying a body force or a mechanical force to the first material.
  • the first material may comprise a gas, a liquid, or a solid material.
  • a method for facilitating heat flow may comprise 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 than 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 creating a temperature difference between the first point and the second point in the second reservoir; allowing heat to flow between the first and second points in the first reservoir and between the first and second points in the second reservoir; and allowing heat to flow between the second point in the first reservoir and the second point in the second reservoir.
  • the method may further comprise flowing heat between a third reservoir containing a third thermal material and the first point in the first thermal material in the first reservoir.
  • the third material may be different than the first material.
  • the method may further comprise flowing heat between the first point in the second reservoir and a fourth reservoir containing a fourth thermal material.
  • the fourth thermal material may be the same or different than the second thermal material.
  • the method may further comprise at least partially thermally insulating the first reservoir or the second reservoir from each other.
  • Flowing heat between the second points in the first and second reservoirs or between the first and second points in either the first reservoir or second reservoir may comprise conduction, radiation, natural convection, or forced convection.
  • Flowing heat between the second points in the first and second reservoirs or between the first and second points in either the first reservoir or second reservoir may comprise pumping a fluid through a heat exchanger or creating a vacuum therein.
  • Flowing heat between the second points in the first and second reservoirs or between the first and second points in either the first reservoir or second reservoir may comprise transmitting electromagnetic waves.
  • the method may further comprise accelerating the first reservoir or the second reservoir.
  • the method may further comprise regulating a rate of heat flow through the first reservoir or the second reservoir.
  • Providing the force may comprise applying a constant body force in magnitude and direction over time within the first and the second reservoirs during nominal operation.
  • the first or the second thermal material may comprise electrical charged elements and wherein providing the force comprises producing an electrical potential difference between the first and second points in either of the first and second reservoirs.
  • the first or the second material may comprise electric dipoles, and wherein providing the force may comprise producing an electrical field gradient between the first or second points in either of the first and second reservoirs.
  • Providing the force may comprise subjecting the first and second points in either of the first and second reservoirs to a gravitational potential difference or accelerating the first or second reservoirs in inertial space.
  • the first or the second thermal material may comprise magnetic dipoles and wherein providing the force may comprise subjecting the first or the second materials to a magnetic field.
  • Applying the force may comprise a thermodynamic compressor or expander.
  • thermodynamic compressor or expander may comprise an axial compressor or turbine, a centrifugal compressor or turbine, or a converging or diverging duct.
  • a heat exchange system may comprise a first reservoir having a first point and a second point; a first thermal material contained in the first reservoir; a second reservoir 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 than the first material; and a thermal contact between the second point of the first reservoir and the second point of the second reservoir so that heat can transfer from the second point in the first reservoir to the second point in the second reservoir via the thermal contact where the first reservoir is subject to a force acting to produce a temperature difference between the first point and the second point of the first reservoir, and wherein the second reservoir can be subject to a force acting to produce a temperature difference between the first point and the second point of the second reservoir
  • the system may further comprise a third reservoir containing a third thermal material and a second heat exchanger operably coupled to the first and third reservoirs such that heat can be exchanged from the third reservoir to the first point of the first reservoir.
  • the third thermal material may be the same or different than the first thermal material.
  • the system may further comprise a fourth reservoir containing a fourth thermal material and a thermal contract operably coupled to the second and fourth reservoirs such that heat can be exchanged from the first point of the second reservoir to the fourth reservoir.
  • the fourth thermal material may be the same or different than the second thermal material.
  • the system may further comprise thermal insulation along the path of the heat flow between the first point and the corresponding second point in either the first or 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 the transfer of heat between the first and second points in either the first reservoir or second reservoir, and wherein the transfer of heat is by conduction, radiation, natural convection, or forced convection.
  • the system may further comprise a motor for accelerating the first reservoir or the second reservoir.
  • the system may further comprise a heat flow regulator configured to regulate heat flow through the first reservoir, the second reservoir, or the heat exchanger.
  • the system may further comprise a force applying mechanism configured to apply the force to the first and second reservoirs.
  • the force applying mechanism may comprise turbomachinery or a body force generating apparatus.
  • a method for facilitating heat flow may comprise employing a first reservoir containing a first thermal material, the first reservoir having a first point and a second point; employing a second reservoir, transferring heat from the first reservoir to the second reservoir when the second reservoir is at a lower temperature relative to the first reservoir, or transferring heat from the second reservoir to the first reservoir when the second reservoir is at a higher temperature relative to the first reservoir; employing a force to the first thermal material thereby creating a temperature difference between the first point and the second point in the first reservoir; operably coupling or operably decoupling a second heat exchange apparatus disposed in the first reservoir with a first heat exchange apparatus disposed in the second reservoir thereby allowing heat to flow therebetween or preventing heat to flow therebetween; operably coupling or operably decoupling a third heat exchange apparatus disposed in the first reservoir with a fourth heat exchange apparatus disposed in the second reservoir thereby allowing heat to flow therebetween or preventing heat to flow
  • the second reservoir may have a first point and a second point and wherein the second reservoir contains a second thermal material, the second thermal material having at least some thermodynamic properties different than the first thermodynamic material.
  • the second heat exchange apparatus may be disposed adjacent the first point of the first reservoir, and wherein the third heat exchange apparatus is disposed adjacent the second point of the first reservoir.
  • the first reservoir may be a closed reservoir or an open reservoir.
  • the method may further comprise providing an insulating material between the first and second reservoirs.
  • Actuating the work exchange apparatus may comprise actuating a piston, a turbine, or a nozzle.
  • the method may further comprise changing a pressure in the second reservoir.
  • the method may further comprise controlling heat flow between the second or third heat exchange apparatus with the respective first or fourth heat exchange apparatus.
  • Providing the force may comprise actuating the work exchange apparatus.
  • Employing the force may comprise providing an inertial force, a gravitational force, or an electromagnetic force.
  • a heat exchange system may comprise a first reservoir containing a first thermal material having a first point and a second point; a second reservoir wherein heat is transferred from the first reservoir to the second reservoir when the second reservoir is at a lower temperature relative to the first reservoir, or wherein heat is transferred from the second reservoir to the first reservoir when the second reservoir is at a higher temperature relative to the first reservoir; a second heat exchange apparatus in the first reservoir operably couplable and decouplable with a first heat exchange apparatus in the second reservoir to allow heat to flow therebetween or to prevent heat flow therebetween; a third heat exchange apparatus in the first reservoir operably couplable and decouplable with a fourth heat exchange apparatus in the second reservoir to allow heat to flow therebetween or to prevent heat flow therebetween, wherein application of a force to the first thermal material forms a temperature difference between the first point and the second point in the first reservoir; and an actuatable work exchange apparatus, wherein actuation of the work exchange apparatus performs work on the first material, and wherein actuation of the work
  • the second reservoir may contain a second thermal material having a first point and a second point, and wherein the at least some thermodynamic properties of the second material are different than the first material.
  • the first reservoir may be a closed reservoir or an open reservoir.
  • the system may further comprise an insulating material between the first and outside reservoirs.
  • the system may further comprise a force generating apparatus configured to provide the force to the first material.
  • the force generating apparatus may comprise an inertial force mechanism or an electromagnetic force mechanism.
  • the work exchange apparatus may comprise a piston, a turbine, or a nozzle.
  • the system may further comprise a heat flow control operably coupled to the first or the third heat exchange apparatus and a respective first or fourth heat exchange apparatus, the heat flow control configured to control heat flow therebetween.
  • An energy conversion system may comprise 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 apparatus having a first point thermally coupled to the outflow of the first material from the first expander and configured to extract heat from or deliver heat to the first material in the output of the first expander; and a compressor configured to receive outflow of the first working material from the heat transfer apparatus, wherein the outflow from the compressor is released into the first reservoir.
  • the heat may be transferred between the first reservoir and the first material output from the first expander.
  • the first expander may comprise a piston, a centrifugal or axial turbine, a duct, or a nozzle.
  • the compressor may comprise a piston, a centrifugal or axial compressor, a duct or a nozzle.
  • Heat extracted from the first material output from the outflow end of the expander may be delivered to the first reservoir or heat is extracted from the first reservoir and exchanged with the first material output from the outflow end of the expander.
  • the system may further comprise 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 apparatus may have a second point thermally coupled with the outflow of the material from the second compressor and configured to deliver heat to or extract heat from the material in the outflow of the second compressor, wherein the outflow of the second material from the heat transfer apparatus is input into an input of the second expander and an outflow from the second expander is released into the first reservoir.
  • Heat may be transferred between the first reservoir and outflow of the first material from the first compressor.
  • the second material may be the same as or different than the first material.
  • An energy conversion system may comprise a first material contained in a first reservoir; 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 apparatus having a first point thermally coupled with the outflow of the first material from the first compressor and configured to deliver heat to or extract heat from the first material in the output of the first compressor; and a first expander, wherein outflow of the first material from the heat transfer apparatus is input into an input of the first expander and an outflow from the first expander is released into the first reservoir.
  • the heat extracted from the first material output from the outflow end of the compressor may be exchanged with the first reservoir or heat is extracted from the first reservoir and exchanged with the first material output from the outflow end of the first compressor.
  • a method of converting energy may comprise 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 apparatus; inputting the first material output from the heat transfer apparatus into a first compressor; and releasing an outflow from the first compressor into the first reservoir.
  • the method may further comprise 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 apparatus and the second working material output from an outflow of the second compressor; and inputting outflow from the heat transfer apparatus into a second expander and outputting outflow from an output of the second expander into the first reservoir.
  • the second material maybe the same as or different than the first material.
  • An energy conversion system may comprise 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 apparatus, wherein outflow from the first compressor can exchange heat with a first point of a heat transfer apparatus, and wherein outflow from the expander can exchange heat with a second point of the heat transfer apparatus, wherein the outflow from the first compressor after exchanging heat with the heat transfer apparatus is input into the expander; and a second compressor, wherein outflow from the expander flows into the second compressor after exchanging heat with the heat exchanger, and wherein outflow from the second compressor is released into the first reservoir.
  • the system may further comprise a heat exchanger thermally coupled with the heat transfer apparatus and configured to exchange heat therewith.
  • a method of converting energy may comprise 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 a heat transfer apparatus; inputting the first material into an expander after exchanging heat with the heat transfer apparatus; outputting the first material from the expander and exchanging heat with a second point in the heat transfer apparatus; inputting the first material into a second compressor after exchanging heat with the heat transfer apparatus;
  • the method may further comprise exchanging heat between the heat transfer apparatus and a heat exchanger.
  • An energy conversion system may comprise 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 apparatus configured to exchange heat with outflow of the first working material from the outflow end of the first expander; a compressor, wherein the outflow of the first material from the first expander is input into the compressor after exchanging heat with the heat transfer apparatus; and a second point of a heat transfer apparatus for exchanging heat with the first working material output from the compressor, wherein outflow of the first working material from the compressor is input into the second expander after exchanging heat with the heat transfer apparatus, and wherein outflow from the second expander is released into the first reservoir.
  • the system may further comprise a heat exchanger thermally coupled with the heat transfer apparatus and configured to exchange heat therewith.
  • a method of converting energy may comprise providing a first working material in a first reservoir; inputting the first working material into a first expander; exchanging heat between a first point of a heat transfer apparatus and output from the first expander; inputting the first working material into a compressor after exchanging heat with the heat exchanger; powering the compressor; exchanging heat between a second point of the heat transfer apparatus and outflow from the compressor; inputting the first working material into the second expander after exchanging heat with the heat transfer apparatus; and releasing outflow from the second expander into the first reservoir.
  • the method may further comprise exchanging heat between the heat transfer apparatus and a heat exchanger.
  • An engine may comprise a duct apparatus having an inlet and an outlet with a channel extending therethrough; a first working material disposed in the channel; a first compressor, wherein the first working material passes therethrough; a first heat exchanger, wherein the first working material passes therethrough and heat is exchanged between the first working material and the first heat exchanger; a first expander, wherein the first working material passes therethrough after exiting the first compressor; a first chamber disposed 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 therethrough and heat is exchanged between the first working material and the second heat exchanger; a second compressor, wherein the first working material passes therethrough, and wherein the first working material exits the second compressor and exits the outlet of the duct apparatus; a second chamber disposed within or downstream of the first expander or within or upstream of the second
  • the second heat exchanger is disposed in the second chamber; and a heat transfer apparatus configured to transfer heat between the first heat exchanger and the second heat exchanger, wherein the heat transfer can be from the second chamber to the first chamber when net work is done by the first working material, or where a rate of the heat transfer can be from the first chamber into the second chamber when net work is done on the working material.
  • a method of converting energy may comprise providing a channel in a duct apparatus; 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 after or while being heated and expanding the first working material; cooling the first working material after or while expanding it in the first expander with a second heat exchanger; and compressing the first working material after or while cooling the first working material in the second heat exchanger.
  • An engine may comprise a first engine comprising a duct apparatus with a channel disposed 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.
  • the engine may further comprise a second engine comprising a duct apparatus with a channel 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 the second working material; and a second expander, wherein the second heat exchanger is disposed within the second compressor or downstream of the second compressor or upstream of the second expander or within the second expander, and wherein the second working material is input into the second expander after exiting the second compressor.
  • the first material may be the same as or different than the second material.
  • a method of converting energy may comprise providing a first engine comprising a duct apparatus with a channel disposed 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 therebetween; compressing the first working material in a first compressor wherein the first heat exchanger is disposed in a first chamber disposed within or downstream of the first expander and within or upstream of the first compressor.
  • the method may further comprise providing a second engine comprising an inside apparatus disposed in a duct apparatus with a channel 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 therebetween; inputting the second working into a second expander, and wherein the second heat exchanger is disposed in a second chamber disposed within or downstream of the second compressor or within or upstream of the second expander.
  • the second working material may be the same as or different than the first working material.

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  • Thermal Sciences (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physical Or Chemical Processes And Apparatus (AREA)
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PCT/US2018/060057 2017-11-10 2018-11-09 Refrigeration apparatus and method WO2019094737A1 (en)

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EP18875536.7A EP3707445A4 (de) 2017-11-10 2018-11-09 Kühlvorrichtung und -verfahren
CN201880072393.3A CN111316050A (zh) 2017-11-10 2018-11-09 制冷装置和方法

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WO2019094737A9 (en) 2019-07-04
EP3707445A1 (de) 2020-09-16
EP3707445A4 (de) 2021-08-11
US20190186786A1 (en) 2019-06-20
CN111316050A (zh) 2020-06-19

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