Thermal Vibration System

Abstract

A method and system for regulating the vapor and liquid fractions of a cycle liquid-vapor fluid operating within its phase change envelope by creating forced oscillatory heat transfer between the liquid and vapor fractions of the cycle stream. A liquid stream segment is expansion cooled and brought into thermal communication with a vapor stream segment. Contact with the expansion cooled liquid allows intermolecular forces to drive condensation to release condensation heat at a condensation temperature higher than the temperature of the expansion cooled stream segment. The resulting temperature gradient allows the expansion cooled segment to capture condensation heat and vaporize isochorically into a vapor stream segment that is again forced to condense, maintained at constant volume, to form an oscillatory heat cycle within the cycle liquid-vapor fluid.

Description

[Technical field]

[0001] The present invention relates generally to the field of thermal oscillation systems, and in particular to thermal oscillations in cycle liquid-vapor streams. [Background technology]

[0002] Engineers and scientists have been aware for hundreds of years that the ambient thermal energy of a solar heated environment contains an inexhaustible supply of free thermal energy. Unfortunately, all previous commercial and practical attempts to harness this natural thermal energy and convert it into useful mechanical work at high power density through closed-cycle condensation heat engines that utilize the natural environment as their high temperature heat source have failed.

[0003] Closed-cycle, condensing heat engines operate above ambient temperature because there is no natural heat sink below ambient temperature to absorb the latent heat of vaporization and re-liquefy the vapor released from the work produced by the expansion machine. Thus, closed-cycle condensing heat engines must operate above ambient temperature, where high temperature heat is maintained through expensive and environmentally harmful fuel combustion. The need to use high temperature "high quality" heat and reject lower temperature "lower quality" heat reduces work extraction efficiency.

[0004] The toy "water drinking bird" U.S. Pat. No. 2,402,463 A, found in most general stores, is a closed-cycle condensing heat engine that uses the surrounding environment as its high-temperature heat source and creates a low-temperature heat sink by evaporating water.

[0005] In a technical report published by the Rand Corporation in August 1966, entitled "A Simple Heat Engine of Possible Utility in Primitive Environments", Rand Corporation Publication No. P-3367, Richard Murrow proposed building a larger version of this engine to pump water from the Nile River. A scaled-up model of the basic drinking bird engine was built 7 feet (2.13 meters) tall, capable of extracting a significant amount of natural heat energy from the surrounding environment and converting it directly into mechanical work. As discussed in "The Research Frontier-Where is Science Taking Us" by Richard Murrow, Saturday Review, Vol. 50, Jun. 3, 1967, pp. 51-55, the engine would be capable of extracting an inexhaustible supply of natural heat energy and converting it into an inexhaustible supply of mechanical work.

[0006] Clearly, such engines that convert the natural thermal energy of the environment into mechanical work at ambient temperature are not "perpetual motion machines" since they depend on a constant input of energy. These engines show that it is indeed possible to extract natural thermal energy from the environment at ambient temperature and convert some of it into mechanical work by creating an artificial low-temperature heat sink below ambient temperature.

[0007] The drawback of engines operating in these environments is that they have such low power density that they are not practical.

[0008] Therefore, there is a need for a system that can capture ambient heat efficiently to provide sufficient power density for work extraction. Summary of the Invention

[0009] In accordance with the teachings of the present invention, a method of thermal management within a cycle liquid-vapor stream is provided, the method including isobarically releasing heat of condensation from a vapor of the cycle liquid-vapor stream to produce a condensate at a first temperature and a first pressure, simultaneously cooling the condensate of the liquid-vapor stream to a condensate having a second temperature lower than the first temperature and a second pressure lower than the first pressure, the cooling being accomplished as adiabatic or isenthalpic cooling, and thermally isochorically vaporizing the condensate.

[0010] According to a further feature of the invention, the cooling is achieved as expansion cooling.

[0011] According to a further feature of the invention, the heat is heat of condensation.

[0012] According to a further feature of the invention, there is also provided driving an external heat engine with the heat of condensation and using the condensate as a heat sink for the external heat engine.

[0013] According to a further feature of the invention, it is also provided to heat the boiler of the distillation unit with heat of condensation and to isochorically heat the expansion cooled condensate with heat produced in the condensation to form the distillate.

[0014] According to a further feature of the invention, it is also provided to receive external heat from the cooling space or from the surrounding environment in the expanded cooled condensate, the external heat supplementing the evaporation of the expanded cooled condensate.

[0015] According to a further feature of the invention, there is also provided a method for discharging a portion of the heat of condensation to the heated space or to the surrounding environment.

[0016] In accordance with a further aspect of the present invention, there is also provided extracting work from a portion of the mixed vibration-work stream.

[0017] According to a further feature of the invention, cooling of the condensate is accomplished by flash expansion into a constant volume pump.

[0018] In accordance with a further feature of the present invention, isochoric vaporization is achieved in a constant volume pump.

[0019] According to a further feature of the invention, the heat is heat of condensation captured within one or more non-circulating stream segments of the cycle liquid-vapor stream.

[0020] According to a further feature of the invention, the heat includes heat captured from an external source.

[0021] In accordance with the teachings of the present invention, a thermal oscillator for managing heat capacity in a cycle liquid-vapor stream is also provided, the oscillator including a condenser having a plurality of isobaric heat conductive cooling channels operative to dump heat of condensation from a vapor component of the cycle liquid-vapor fluid stream to form a condensate at a first temperature and a first pressure, a condensate expansion device configured to adiabatically or isenthalpically cool the condensate to a second temperature lower than the first temperature and a second pressure lower than the first pressure, and an isochoric heater pump having a plurality of thermally heated constant volume heating chambers, which vaporize the condensate into a vapor during transport through the pump.

[0022] According to a further feature of the invention, the condensate expansion device is realized as an expansion valve.

[0023] According to a further feature of the invention, the isochoric heater pump includes a twin screw drive with counter-rotating interleaved screws.

[0024] According to a further feature of the invention, the condensate expansion device is realized as a constant volume heater pump.

[0025] In accordance with a further aspect of the present invention, there is also provided a work extraction device in thermal communication with the isochoric heater pump.

[0026] According to a further feature of the invention, the heater pump is realized as a constant volume pump in thermal communication with an external heat exchanger.

[0027] According to a further feature of the invention, it is also provided to heat the boiler of the distillation unit with heat of condensation and to isochorically heat the expansion cooled condensate with heat produced in the condensation to form the distillate.

[0028] According to a further feature of the invention, the heat is captured heat from an external source.

[0029] In accordance with a further feature of the invention, the heater pump heat receives heat of condensation from one or more non-circulating stream segments of the cycle liquid-vapor fluid stream.

[0030] In accordance with the teachings of the present invention, a method of thermal management within a cycle liquid-vapor stream is provided, the method including isobarically releasing heat of condensation from a vapor of the cycle liquid-vapor stream to produce a condensate at a first temperature and a first pressure, simultaneously expanding and cooling the condensate of the liquid-vapor stream to an expanded-cooled condensate having a second temperature lower than the first temperature and a second pressure lower than the first pressure, and isochorically vaporizing the expanded-cooled condensate with the heat of condensation.

[0031] In accordance with a further feature of the present invention, there is also provided work extraction during expansion cooling.

[0032] A further feature of the invention provides for isobaric heating of the expansion-cooled condensate with heat of condensation prior to isovolumic vaporization.

[0033] In accordance with a further feature of the present invention, there is also provided the application of compression work to the isochoric vaporized expanded cooled condensate upon completion of isochoric vaporization of the expanded cooled condensate.

[0034] A further feature of the invention provides for driving an external heat engine with the heat of condensation and for using the expanded and cooled condensate as a heat sink for the external heat engine.

[0035] According to a further feature of the invention, it is also provided to heat the boiler of the distillation unit with heat of condensation and to isochorically heat the expansion cooled condensate with heat produced in the condensation to form the distillate.

[0036] According to a further feature of the invention, it is also provided to receive external heat from the cooling space or from the surrounding environment in the expanded cooled condensate, the external heat supplementing the evaporation of the expanded cooled condensate.

[0037] According to a further feature of the invention, there is also provided a method for discharging a portion of the heat of condensation to the heated space or to the surrounding environment.

[0038] In accordance with a further feature of the invention, there is also provided isovolumically mixing the working liquid-vapor stream with the expansion cooled condensate to form a mixed vibration-work stream.

[0039] In accordance with a further aspect of the present invention, there is also provided extracting work from a portion of the mixed vibration-work stream.

[0040] In accordance with a further feature of the present invention, there is also provided receiving external heat from the surrounding environment in the expanded cooled condensate.

[0041] According to a further feature of the invention, it is also provided to receive external heat from the cooling space or waste heat exhaust in the expanded cooled condensate.

[0042] According to a further feature of the present invention, it is also provided that the heating space is heated by a portion of the heat of condensation.

[0043] In accordance with the teachings of the present invention, a thermal oscillator for managing heat capacity in a cycle liquid-vapor stream is also provided, the oscillator including a condenser having a plurality of isobaric heat conductive cooling channels operative to release heat of condensation from a vapor component of the cycle liquid-vapor fluid stream to form a condensate at a first temperature and a first pressure, a condensate expansion device configured to expand and cool the condensate to an expanded-cooled condensate at a second temperature lower than the first temperature and a second pressure lower than the first pressure, and a constant volume, isochoric heater pump having a heating chamber heated by the heat of condensation from the condenser, the heater pump vaporizing the expanded-cooled condensate into a vapor during transport.

[0044] According to a further feature of the invention, the condensate expansion device is realized as an expansion valve.

[0045] According to a further feature of the invention, the isochoric heater pump includes a twin screw drive with counter-rotating interleaved screws.

[0046] In accordance with a further feature of the present invention, an isochoric heater pump includes a plurality of retractable vanes forming a heating chamber, the vanes being biased to conform to a surface geometry during vane rotation such that the heating chamber volume is defined by the degree of vane retraction following the surface geometry.

[0047] According to a further feature of the invention, the condensate expansion device is realized within the constant volume heater pump.

[0048] In accordance with a further feature of the present invention, the isochoric heater pump includes a heat exchanger.

[0049] In accordance with a further aspect of the present invention, there is also provided a work extraction device in thermal communication with the isochoric heater pump.

[0050] In accordance with a further feature of the invention, thermal communication is achieved through isochoric mixing of the expanded and cooled condensate with a working fluid of the work cycle within each of one or more of the constant volume chambers.

[0051] In accordance with the teachings of the present invention, a thermal oscillator for managing heat capacity in a cycle liquid-vapor stream is also provided, the oscillator including a condenser means for isobarically condensing a vapor component of the cycle liquid-vapor fluid stream to form a condensate at a first temperature and a first pressure, a condensate expansion device for expanding and cooling the condensate to an expanded cooled condensate at a second temperature lower than the first temperature and a second pressure lower than the first pressure, and an isochoric heater pump for vaporizing the expanded cooled condensate to a vapor during transport.

[0052] In accordance with a further feature of the present invention, there is also provided work extraction means for extracting work from the cycle liquid-vapor stream, the work extraction means being in thermal communication with the isochoric heater pump. Effect of the Invention

[0053] In accordance with the teachings of the present invention, there is also provided an isochoric heater / boiler pump including a heating shell having embedded heat exchange channels and a porous inner surface that promotes heat transfer while maintaining no contact between the fluid and a plurality of actuated constant volume heating chambers in thermal communication with the heat exchange channels for isochorically vaporizing the fluid disposed within the heating chambers by a heat source disposed within the heating channels during transport through the heating shell.

[0054] The subject matter which is regarded as the invention is particularly pointed out and distinctly claimed in the concluding portion of the specification. The invention is best understood in consideration of the accompanying drawings. [Brief description of the drawings]

[0055] [Figure 1] A simple Rankine cycle is shown on a pressure-enthalpy (PH) phase diagram for common refrigerants. [Diagram 2] 1 illustrates a constant volume evaporation cycle according to one embodiment. [Figure 3A] The Rankine cycle of FIG. 1 is shown superimposed on a constant volume cycle of FIG. 2 for comparison. [Figure 3B] Indicates an ineffective cycle. [Figure 3C] 1 illustrates an inefficient heat pump cycle. [Figure 3D] 1 illustrates an efficient heat pump work input correction of an inefficient heat pump cycle according to one embodiment. [Figure 4A] A forced thermal oscillation cycle is shown on a pH diagram according to one embodiment. [Figure 4B] 4B is a schematic diagram of a thermal oscillator with a cross-sectional side view of a screw-heater pump that realizes the thermal oscillation cycle of FIG. 4A according to one embodiment. [Figure 4C] FIG. 4C is a schematic cross-sectional end view of the screw-heater pump of FIG. 4B, according to one embodiment. [Figure 5A] 1 is a flow diagram illustrating the process steps and heat transfer stages in a forced thermal oscillation cycle according to one embodiment. [Figure 5B] A forced thermal oscillation cycle is shown on a ph diagram illustrating the heat transfer into and out of the oscillation cycle and the work output from an external heat engine thermally coupled to the oscillation cycle, according to one embodiment. [Figure 6A] The coupled thermal oscillation and work cycle is shown on a pH diagram according to one embodiment. [Figure 6B] A schematic diagram of a forced thermal oscillator-heat engine system is shown with a cross-sectional side view of a screw-heater pump implementing the coupled oscillation and work cycle of FIG. 6A according to one embodiment. [Figure 7] 4 is a flow diagram illustrating the exchange of coupled forced vibration cycles and work cycles in each of the processing steps according to one embodiment. [Figure 8] The driven oscillator is shown in FIG. 6A along with a cross-sectional side view of a vane-heater pump that realizes the coupled vibration and work cycle. [Figure 9A] 13 illustrates a combined vibration and work cycle according to an alternative embodiment. [Figure 9B] FIG. 13 is an exploded, partial perspective view of a disk-based oscillator work extraction system according to a third embodiment. [Figure 9C]FIG. 9B illustrates the stream flows between the main components of the disk-based oscillator work extraction system that realizes the integrally coupled vibration and work cycle of FIG. 9A. [Figure 9D] FIG. 9C is a schematic top view of a disk condenser of the disk-based oscillator work extraction system of FIG. 9B. [Figure 9E] FIG. 9C is a schematic perspective top view of a blade assembly of the disk-based oscillator work extraction system of FIG. 9B. [Figure 9F] 9F-9H show schematic cross-sectional side views of a constant volume vertical vane heater pump at a fluid exhaust stage and two intake stages, according to one embodiment. [Figure 10] 1 illustrates a combined vibration and work cycle in which isochoric heating is performed to a dryness fraction of less than 1.0, according to one embodiment. [Figure 11A] 13 illustrates a combined vibration and work cycle employing flash expansion according to an alternative embodiment. [Figure 11B] 11B-11D show schematic cross-sectional side views of a constant volume vane heater pump in a fluid exhaust stage and two intake stages according to a flush embodiment. [Figure 12A] FIG. 13 is a PH diagram of a combined thermal oscillator and work extractor employing isochoric flash and non-circulating isochoric heating, according to one embodiment. [Figure 12B] FIG. 12B is an enlarged view of a portion of the PH diagram of FIG. 12A. [Figure 13] FIG. 1 is a schematic diagram of a combined thermal oscillator and work extractor employing isochoric flash and non-circulating isochoric heating according to one embodiment. [Figure 14] FIG. 14 is a flow diagram of the process steps employed by the combined thermal oscillator and work extractor of FIG. DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS

[0056] It will be understood that, for clarity, elements shown in the figures may not be drawn to scale and reference numerals may be repeated in different figures to indicate corresponding or similar elements.

[0057] In the following detailed description, specific details are set forth in order to facilitate an understanding of the present invention, but it will be understood by those skilled in the art that the present invention may be practiced without these specific details.

[0058] Disclosed are methods and systems for thermal management in various energy systems, such as solid-vapor, solid-gas, solid-liquid, liquid-liquid, gas-gas, ionic, and cyclic vapor-liquid systems. Without limiting the scope, the present description focuses on cyclic liquid-vapor systems.

[0059] Specifically, thermal energy oscillates between different fluid states within the cycle liquid-vapor stream. A first stream segment is delivered at a high temperature relative to a second stream segment. Although the first stream segment is relatively hot, the temperature is still low enough for the vapor molecules to experience intermolecular forces that cause the vapor to condense and release the heat of condensation at the high temperature of the first stream segment at isobaric conditions. This high temperature heat can be used to drive isochoric evaporation of the second segment, which was previously expansion-cooled to a temperature lower than its high temperature. The second stream segment is brought through isochoric evaporation to essentially the first stream segment at the first temperature. At this point, the heat of condensation previously released from the vapor of the first stream segment has been captured through the evaporation of the second stream segment. This repeated process of heat release and capture between stream segments forms a forced thermal oscillation cycle in which the initial steady state between the liquid and vapor stream segments of the cycle liquid-vapor mixture is continually forced out of steady state by expansion cooling and subsequent vaporization. The expanded cooled liquid is in thermal communication with the vapor segment to isobarically condense the vapor, and the released heat of condensation causes isochoric evaporation of the expanded cooled liquid. It should be understood that heat losses require additional heat input from an external source to maintain the oscillatory cycle operation at its original high temperature and additional pumping work to achieve continuous isochoric processing. In an embodiment, the high temperature of the first stream segment is at the ambient temperature of the environment and the low temperature is below ambient, allowing spontaneous heat flow from the first stream segment to the second stream segment according to the second law of thermodynamics, as further described.

[0060] When coupled with a work extraction device, the second cycle is employed as a working cycle that is isochorically mixed with a cooled second stream segment and is isochorically heated as the mixed vibrating stream segment and working stream are further addressed.

[0061] The thermal oscillation stream advantageously increases the efficiency of work extraction when combined or mixed with the work cycle. The increased efficiency is a result of the negation of waste heat from the oscillation cycle, and correspondingly, retains the amount of energy within the cycle fluid. Furthermore, the oscillation cycle operates at a temperature that utilizes intermolecular forces to achieve condensation, thereby eliminating the need for significant external compression work. The significant reduction in heat input and the negation of significant externally supplied compression work reduces operating costs.

[0062] Moreover, the combined vibration and work cycle allows for work extraction at ambient temperatures, thereby further saving fuel costs and reducing pollution. It should be understood that "high" and "low" refer to the relative operating parameters of the system, with condensation occurring at the upper limit and isochoric evaporation occurring at the lower limit, as previously discussed.

[0063] In another embodiment, thermal oscillations are achieved using an ambient environment where condensation heat is rejected into the environment and heat is captured from the environment to drive isochoric mixing. The amount of condensation heat rejected, and similarly the amount of environmental heat input, are separately configurable according to the operating conditions.

[0064] FIG. 1 shows a simple Rankine cycle on a pressure-enthalpy (PH) phase diagram, along with isentropic, isothermal, and isosteric lines for common refrigerants, as is known in the art.

[0065] As shown, heating the working fluid from state 1 increases enthalpy at constant pressure until complete vaporization at state 2. The resulting working fluid expands in a turbine or other work extraction means from a high temperature, high pressure fluid at state 2 to state 3. Heat is rejected into a heat sink, such as the ambient environment, until complete condensation at state 4, and then pumped back to state 1 with substantially constant enthalpy and entropy. Because pumping is generally applied to the fluid as a highly incompressible liquid, the amount of work associated with pumping is negligible, thereby reducing the efficiency η1 to the useful work W out , state point 1 to 2 / (Q inl+Q in2 ) to the heat energy given up to; η1=W out / (Q inl +Q in2 )(Formula 1)

[0066] Figure 2 shows a constant volume evaporation cycle in which a constant volume of fluid is heated from point 3' to point 2 and work is extracted from 2 to 3 through expansion in a turbine or other work extraction means. The expanded working fluid is condensed from point 3 to 3' through contact with a cryostat and returned to point 3'. Accordingly, the efficiency of this cycle is such that the same amount of work W can be done with less heat input. out This is larger than the regular Rankine cycle shown in Figure 1.

[0067] FIG. 3A shows the Rankine cycle of FIG. 1 superimposed on the constant volume cycle of FIG. 2 for comparison. The shaded area of ​​the Rankine cycle represents the heat input Q inl is the amount of work generated, W out The emphasis is on "wasted effort," in the sense that it will have no effect.

[0068] Figure 3B shows a completely inefficient cycle in which heat is added at a high temperature and rejected at a low temperature, as realized in the standard Rankine cycle of Figure 1. As shown, pressure reduction and cooling occurs along the constant volume line 3'~2, and therefore produces no work, since work is the integral of RdV.

[0069] FIG. 3C shows a case in which a fluid is depressurized from 1 to 4 at constant enthalpy, then heated from 4 to 3′ at a low temperature, and then further heated by external heat Q in2 At this point, heat is released from 3' to 2 along the line of constant volume. out1is rejected at a higher temperature from 2 to 1, completing the cycle. Essentially, heat is absorbed at a lower temperature and rejected at a higher temperature, as in heat pumps such as refrigerators and air conditioners. However, to complete the cycle at the hottest temperature at point 2, heat must be supplied to isochorically evaporate a liquid at a higher temperature than the temperature of the heat rejected in isobaric condensation to ensure heat transfer, thereby making the cycle ineffective.

[0070] FIG. 3D shows a heat pump that is effective in contrast to that shown in FIG. 3C. The cycles of FIG. 3C and FIG. 3D are substantially similar. However, instead of the additional heat employed in the cycle of FIG. 3C, the cycle of FIG. 3D employs additional work W between points 2 and 2′ to close the cycle. in This represents a significant leap in efficiency since the cycle is completed by inputting external heat Q in is taken from the cooling space, waste heat exhaust, and the environment, and the vibration heat Q discharged during condensation osc and heats the condensate that is expanded and cooled between 3' and 2. External heat Q inIt should be understood that in applications where the heat input is hotter, it can contribute to isochoric evaporation. Furthermore, in some embodiments, the vibration thermal management system outputs a portion of the condensation heat as heat output to the heated space. It should be understood that the vibration thermal management system can be advantageously configured to function as a heat pump to provide either cooling, heating, or both cooling and heating. An example of a cooled space is a space from which heat is extracted for refrigeration, refrigeration, or air conditioning. An example of a heated space is a steam boiler. In implementation, any of the three described embodiments of the isochoric heater pump can be employed. In some embodiments, the vibration thermal management system is realized as multiple serially coupled units, thereby increasing the temperature gradient between the input heat and the output heat. In such a serial arrangement, the condensation heat rejected in the upstream unit is used to isochoric evaporation of the expanded cooled condensate of the downstream unit. In some other embodiments, the system is further coupled to a work cycle with a work extraction device as described.

[0071] Heat transfer in an oscillating cycle allows pressure and temperature to be increased without significant work provision for compression. It is only necessary to provide pumping work and is therefore significantly more efficient than that of a heat pump operating in the same temperature range.

[0072] FIG. 4A shows a forced thermal oscillation cycle in which heat is rejected at high temperature and absorbed at low temperature to drive low temperature heating and vaporization according to the second law of thermodynamics. Heat release is achieved through high temperature condensation and simultaneous expansion cooling of the condensate, where latent heat energy is released in the resulting vapor. Vaporization causes a temperature drop in the remaining condensate. The heat of condensation is released to the maximum temperature of the cycle, T high As heat is rejected at 1000 rpm, a temperature gradient is created between the stream segments, thereby allowing high temperature condensation heat to drive low temperature processing, as previously described.

[0073] Specifically, heat oscillates between two stream segments I and II of the cycle fluid stream as shown in the thermal oscillation cycle on the PH diagram of Figure 4A. Stream segment I, in one embodiment, begins at high temperature and pressure close to ambient temperature at state 6. Ambient temperatures range, for example, between 15 degrees Celsius and 25 degrees Celsius. Stream segment I undergoes constant temperature and pressure condensation and some additional cooling from state 6 to state 8.

[0074] During condensation of the first stream segment I, stream segment IIA expands from a cooled liquid at state 8 to a liquid-vapor mixture at state 5. The expansion, as previously described, causes a temperature drop in stream segment IIA, thereby creating a temperature gradient that induces heat transfer between the condensing stream segment I and stream segments IIB and IIC. The heat of condensation and cooling Q osc is isobarically captured by stream segment IIB from state 5 to 5′, heated, and then isochorically vaporized from 5′, approaching the original temperature and pressure of segment I at state 6. The proximity of stream segment I to the starting state at state 6 is a function of system losses, as is known in the art. The thermal oscillation cycle advantageously conserves heat in the cycle 6-8-5-5′, thereby reducing the heat input required to extract work when coupled to a work extraction device, or the work input when thermally coupled to a heat pump, desalination or distillation system, or other thermal device, as will be explained later. The expansion of stream segment IIA is achieved isenthalpic in some embodiments, and in other embodiments the expansion is achieved isentropically or adiabatically. The oscillator advantageously allows for adjustment of the vapor and liquid fractions, so that a temperature gradient can be stably established in the coupled system by changing the mass flow rate and the degree of expansion.

[0075] Figure 4B shows an embodiment of a thermal oscillator 9 that realizes the cycle of Figure 4A. As shown, the thermal oscillator 9 includes a twin screw 13, a starter motor 15 for driving the screw 13, a vapor reservoir 17 in fluid communication with the fluid output of the twin screw 13 to maintain a constant pressure during condensation and cooling, a liquid reservoir 17A in fluid communication with the condensate output from the heat exchange channels 12 embedded in the exchanger shell 11, and an isochoric heat exchanger pump 10 with an expansion valve 14 for either isenthalpic or isentropic expansion of the stream segment IIA.

[0076] FIG. 4C shows a cross-sectional end view of the dual screw drive 13 of the isovolumetric heat exchanger pump 10 according to one embodiment. As shown, the twin screw drive 13 is a set of counter-rotating interleaved screws, one of left-handed helicity and the other of right-handed helicity, adapted to push fluid along the screw length. The fluid is pushed between a constant volume chamber 16 formed within the screw 13, which also provides a high degree of thermal contact between stream IIC and the exchanger housing 11. As shown, the exchanger housing 11 has embedded channels 12 and a porous inner surface 19 to maximize heat exchange between the segment stream I condensing / evaporating and cooling while being pumped through the channels 12, and the expanded cooled stream segment IIC driven through the heat exchanger 11 by the twin screws 13 in the constant volume chamber 16.

[0077] In operation, oscillator 9 starts with stream segment I and stream segment IIB of one fluid stream in two different thermodynamic states. Segment stream I starts with high temperature, high pressure steam as shown in state 6, and segment stream IIA starts with high temperature, high pressure condensate as shown in state 8.

[0078] As segment I cools in the exchanger channel 12, segment IIA expands rapidly through expansion valve 14. The expansion transforms segment IIA into a cooled two-phase segment IIB. The resulting temperature difference between cycle fluid stream segment I and segments IIB and IIC causes the heat of condensation released during the cooling of segment I to be captured by the thermally connected stream segments IIB and IIC as both streams pass through isochoric heat exchanger 10. Specifically, segment I cools while being pumped through channel 12, while segment IIC captures the heat of condensation while being transported in constant volume chamber 16 of driven screw drive 13. As segment IIC progresses, it captures additional heat and vaporizes, and under the effect of additional heat capture in constant volume chamber 16, the temperature and pressure continue to rise. When the temperature and pressure reach starting point 6, segment IIC becomes segment I and is either cooled in channel 12 or stored in reservoir 17 for future cooling. The condensate is either expanded and cooled through expansion valve 14 or stored in condensate reservoir 17A for future expansion.

[0079] The repeated heat transfer between two different stream segments of the cycle fluid stream creates thermal oscillations within the entire cycle fluid stream. The resulting storage of thermal energy within the cycle fluid stream advantageously reduces the heat input required to extract work from the fluid stream, as will be explained later.

[0080] FIG. 5A shows a flow diagram of the interaction of the two segments I and II of the cycle fluid stream in each of the processing steps of the thermal oscillator 9, considering the cycle of the PH diagram of FIG. 4A, according to one embodiment.

[0081] As shown, the cycle fluid streams are treated as two synchronized cycle stream segments, segment I and segment II. As previously mentioned, each stream segment begins at a different thermodynamic state and is synchronized to ensure that high temperature heat released as heat of condensation by one stream segment is captured by the other segment and vice versa. Each repeated heat transfer between stream segments requires that the segment receiving heat is at a lower temperature than the temperature of the stream from which heat is being released, as is well known in the art. Specifically, high temperature and pressure stream segment I is isobarically condensed from state 6 to 8 in step A (followed by cooling in some configurations). In parallel, stream segment II is rapidly expanded from state 8 to 5 in step E, with associated cooling allowing heat transfer from segment I to isobarically heat segment II from state 5 to 5′ in step F, which then isovolumetrically vaporizes segment II in step G. Continuing with segment I, it is cooled from state 8 to 5 through expansion in step B, which also causes the temperature drop necessary to accept heat from the isobaric condensation of segment II in step H. After isobaric heating of segment I in step C and then isovolumetric vaporization of segment II in step D, the cycle proceeds to step A with isobaric condensation and simultaneous expansion in step E for segment II. It should be understood that the isobaric heating of segment I in step C and similar isobaric heating of segment II in step F are optional, and in some embodiments, in the absence of isobaric heating, isovolumetric heating is employed in steps D and G.

[0082] FIG. 5B shows a forced thermal oscillation cycle thermally coupled to an external heat engine Gn, such as an organic Rankine cycle engine, a steam engine, a Stirling engine, or other type of heat engine. For example, the oscillation cycle, realized by the system of FIG. 4B, acts as both a heat source and a heat sink for the engine Gn. As shown, the high-temperature condensation heat Q1 released during isobaric condensation in states 6-68 is oscis trapped in the isovolumetric segment 5′-5″ of the thermal oscillation cycle and released during isobaric condensation in state 68-8, Q2 osc is the work output W engine The heat source that drives the engine Gn for the purpose of engine According to the second law of thermodynamics, the condensate that has been expanded and cooled to state 5-5′ in the oscillation cycle is isobarically heated. The rejected low-temperature engine heat Q engine The capture and utilization of rejected low-temperature engine heat, Q, represents a major advance in heat engine efficiency, where low-temperature heat is typically considered waste heat and does not contribute to the engine work function during its next cycle. As shown in the figure, the rejected low-temperature engine heat, Q, engine The capture of advantageously determines the proper functioning of the vibration cycle and the resulting work output W engine This reduces the amount of external heat that needs to be supplied in the next cycle to maintain . An alternative embodiment applies compression work as shown in Figures 3D and 9A to increase the temperature gradient and promote the transfer of condensation heat for isochoric heating.

[0083] FIG. 6A illustrates a combined oscillation and work cycle on a PH diagram according to one embodiment. As shown, the oscillation cycle of fluid stream segments I, II, and V cycles through points 6-8-5-5′-5″-6, while the work fluid stream cycles through state points 5′-5″-6-7-5′. After expansion cooling at state point 5, stream segment II isovolumetrically mixes with work stream IV after work extraction at point 7 into a single stream V of average enthalpy of 5′ due to isovolumetric heating at state 5′-5″-6. The isovolumetric heating from 5′ to 5″ emphasizes the heating from the captured condensation heat released from the condensation of segment I, while the heating from 5″ to 6 emphasizes the heating from the heat Q supplied from an external heat source. in Emphasis on heating from. Work extraction W out is the externally supplied heat Q to complete the isochoric heating of the mixed oscillating-work stream V to achieve the starting thermodynamic state of stream segment I of oscillating stream segment 6 inAfter isochoric heating, stream segment V is split according to configuration options into stream segment I for condensation in an oscillation cycle and stream VI for work extraction in a work cycle.

[0084] FIGURE 6B shows an embodiment of a thermal vibration work extractor formed from an integrally coupled thermal oscillator and turbine or other work extraction device 20 that generally implements the cycle of FIGURE 6A. In addition to the system shown in FIGURE 4B, a vibration work extractor 9A extracts work W by expanding a fraction of the high energy stream V. out and a heat exchanger 18 that operates to supply external heat during isochoric heating as shown in cycle 5″-6 of FIG. 6A.

[0085] During operation, stream segment I condenses during transport through channel 12 of isochoric heater pump 10. At the same time, the condensate of oscillating stream segment II expands almost instantaneously through expansion valve 14 to a temperature significantly lower than the temperature of stream I that is condensing to drive heat flow, as previously described. Stream segment II isochorically mixes with working stream IV at state 5′ to form mixed stream V having a weighted average enthalpy of the combined masses of stream II at point 5 and IV at point 7. Mixed stream V at point 5′ has a temperature 25-30° C. lower than condensate stream I in channel 12, in some embodiments. As previously described, the forced temperature gradient advantageously enables thermal oscillations between different segments of the fluid cycle. In some other embodiments, the temperature gradient ranges between 20-25° C. or 30-35° C., and in yet other embodiments, the temperature gradient ranges between 15-20° C. In embodiments employing serially coupled heater pumps, the temperature gradient increases proportionally with the number of each additional heater pump. The mixed vibration-work stream V is driven through the constant volume heater pump 10 in the constant volume chamber 16 of the screw 13 and is vaporized by the heat of condensation upon contact with the extended contact surface of the porous inner surface 19. It should be understood that the surface porosity does not traverse the exchanger wall and there is no intermixing of the condensed and vaporized streams. The external heat exchanger 18 supplies the external heat Q in is fed through exchanger channel 12 to the mixed stream V to raise the temperature and pressure of oscillator stream segment I, which is now primarily or entirely vapor, to the starting temperature and pressure at state 6. in Heat may be provided through any of a variety of sources, such as environmental heat, combustion heat, electric heat, solar heat, or other heat supply technologies.

[0086] After completion of isochoric heating, the stream is split into two fractions through a control valve (not shown) according to configuration parameters, one fraction becomes the oscillatory cycle stream segment I while the second fraction becomes the work cycle stream IV which expands from state 6 to 7 for work extraction. Both the oscillatory stream segment II and the work stream IV are recombined into the isochoric cycle V to repeat the isochoric heating as described.

[0087] The coupling of a thermal oscillator to a heat engine system reduces the process efficiency W / Q in This provides a significant improvement in the thermal efficiency and thereby reduces the external heat input required to extract useful work.

[0088] The following is a set of equal ratio mass flows of expander flow m1 and oscillator flow m2, each of 1.0 kg / cycle, and a combined pump volume flow rate of 360 m 3 6B is a simulation result for the integrally coupled cycle of FIG. 6A, with the time given per second. [Table 1] JPEG2024541335000003.jpg85159

[0089] FIG. 7 shows a flow diagram illustrating the interaction between the oscillator and the work stream during each of the processing steps of thermal vibration work extractor 9A of FIG. 6B, according to one embodiment.

[0090] As shown, in the thermal oscillation cycle, the condensate is expanded and cooled in step I, as previously described. At the same time, in the work extraction cycle, work is extracted from a fraction of the mixed oscillation-work stream IV in step K. In step J, the expanded cooled condensate of the oscillation cycle and the expanded working fluid of the work cycle are isochorically mixed in step J and then isochorically heated in step L as mixed stream V. Isochoric mixing and isochoric vaporization prevent intensive mechanical work on the fluid streams and conserve all heat capacity in the cycle fluids, advantageously excluding any process-associated heat losses and explicitly rejecting heat. Isochoric mixing occurs in state 5′ to form mixed stream V, which has the average state of 5 and 7 at a lower temperature than the temperature at which the heat of condensation was released, thereby allowing the capture of the heat of condensation, as previously described. Upon mixing, the oscillation and work cycles overlap as shown in FIG. 6A. The mixed stream V is isochorically vaporized and further heated with the released heat of condensation and external heat from states 5′-5″ to 6, as previously described.

[0091] FIG. 8 shows a second embodiment of a vibratory work extractor 9A employing a vane-based isochoric heater 10B to achieve the cycle of FIG. 6A.

[0092] As shown, system 9B is similar to the system shown in FIG. 6B and includes an isochoric heater pump 10B, a vapor reservoir 17, a liquid reservoir 17A, and an expansion valve 14, and a heater 18. However, vane-based isochoric heater pump 10B is realized as a modified vane pump having an eccentric rotor 22 mounted within a housing 21. A plurality of telescopic vanes 23 are mounted on the rotor 22A and are biased to maintain contact with the inner wall of the housing wall 21. During rotation, the vanes 23 expand and contract according to the inner wall surface geometry. As the vanes 23 expand, the chamber volume between the vanes 23 increases, and conversely, as the vanes 23 contract, the chamber volume decreases. As shown, the isochoric housing wall 21 includes a highly porous surface 19 to increase the surface area for heat transfer and turbulence from boiling and two-phase isochoric heating. The vane heater 10B also includes embedded channels 12 for the transport of stream segment I during condensation and cooling, as previously described.

[0093] Operation is generally realized in the context of a screw-driven embodiment, as previously described. The mixed vibration-work stream V is fed into the vane heater 10B as a multi-feed according to increasing chamber size during rotor rotation. During rotor rotation, the mixed stream V is fed with the heat of condensation released by stream segment I during transport through channel 12 and any additional external heat Q provided by heater 18. in 10B, where it is vaporized and heated while in contact with the porous surface 19. As the rotor rotation continues, the vanes 23 begin to contract, reducing the volume of the chamber 16a and eliminating the vaporized stream segment V, prior to mechanical compression to ensure the required isochoric heating. In response, the vaporized stream exits the vane heater 10B through multiple outlets according to the chamber size to ensure isochoric heating. After heating, the high temperature and pressure stream is pumped to the turbine 20 or the work W outto state 7, and then recombined at equal volume with the valve-expanded stream segment II to repeat the cycle, as described above. In an alternative embodiment, the heater pump outlet port is adjusted with an outlet valve to allow mechanical compression on the fluid to complete the oscillatory cycle.

[0094] In an alternative embodiment, the expansion of the condensate is accomplished through a turbine or similar work extraction device to advantageously extract additional work from the oscillator-engine system 10B.

[0095] Alternative embodiments employ various types of isochoric heater constant volume pumps, such as, for example, progressive cavity pumps, piston pumps, lobe pumps, and / or gear pumps. It should be appreciated that in some embodiments, isochoric vaporization is achieved through other means, such as a valved heating chamber that operates to release vapor in response to a threshold pressure in the absence of pumping during vaporization, to minimize compression work on the vapor against the valve during vaporization.

[0096] FIG. 9A shows an alternative embodiment of a coupled vibration and work extraction cycle. As shown, a mixed stream of m1 and m2 is heated by an external Q in In addition, Q osc1 and Q osc2 As shown, at point 6, the mixed stream of m1 and m2 is split into three stream fractions, one stream fraction is condensed to state 8, and the second stream fraction is condensed to state 6′ using externally applied work W inThe third stream fraction is expanded to state 7 for work extraction. The stream fraction compressed to state 6' is condensed to state 8' at a higher temperature than the condensation from state 6 to 8, thus providing a larger temperature gradient for isochoric heating of the mixed stream of m1 and m2. The expanded work stream with mass m1 is isochorically mixed with the expansion-cooled oscillating segment of mass m2 from 8 and 8' to state 5. Isochoric mixing in state 5' converts the mixed stream into H mix The average enthalpy of

[0097] FIG. 9B is an exploded, partial perspective view of the major components of a disk-based oscillator work extraction unit in their housing according to a third embodiment. The unit includes a condenser 30 and a vertical vane-heater pump 25, which are stacked vertically when deployed all coupled to the work extraction device 20. The condenser 30 includes one or more sets of narrowing circumferential channels that provide additional surface area to facilitate heat transfer as the hot working fluid cools during passage through the cooling channels. The vertical vane heater 25 includes a heat transfer disk 25C in thermal communication with the condenser 30 in deployment. The heater plate 25C is constructed from a highly thermally conductive material such as copper, aluminum nitride, and other materials that provide such functionality, and has a porous surface to increase surface area and resulting heat transfer and evaporation. The disk 25C is also fitted with a wedge configured to open and close the vanes during rotation according to a wedge surface geometry, as will be further described. The vertical vane heater 25 also includes a plurality of radial vanes slidably mounted within vane plate 25A driven by shaft 25B. During shaft rotation, the vanes follow the surface of disk 25C and rise and fall following the contours of the disk wedges. The rise and fall of the vanes during rotation provides a valve function to allow for the injection and removal of fluids into and out of the vane heater during operation. Synchronization with the fluid flow is described further.

[0098] FIG. 9C illustrates the stream flows between the main components of the disk-based thermal vibration work extraction system of FIG. 9B that implements the thermal vibration and work extraction cycle of FIG. 9A.

[0099] As shown, this embodiment includes two condensing disks 30i and 30ii, two vertical vane heat exchanger pumps 25i and 25ii, an expander 20, expansion valves 14i and 14ii, and a heat exchanger connected to an external heat source 18. Only the vane assembly is shown, and the heater plate 25C shown in FIG. 9B, along with the liquid and vapor reservoirs, are all omitted for clarity. It should be understood that the heat released in the two condensers 30i and 30ii is conducted through each heat exchanger disk 25C mounted on its respective condenser. It should be further understood that in some embodiments, the vanes 25ii are realized in more than two sets, and in other variant embodiments, multiple regulated vane heater pumps are also employed.

[0100] During operation, full hot and high pressure fluid is fed (at state 6') to the first inlet 31A of the condensers 30i and 30ii, where the fluid travels through a first set of gradually narrowing condenser channels as shown in FIG. 9D. After condensation, the condensate from each condenser is expanded through each respective expansion valve 14i from state 8' to state 5. Concurrently, hot and high pressure fluid is fed (at state 6) to the second condenser inlet 31A2, where the fluid is expanded through the expansion valve 14ii from state 8 to state 5. Supplementary heat is also provided from an external heat exchanger, where the auxiliary heat stream cools and is cooled within each of the condensers 30i and 30ii, where the heat is transferred to the heating plate 25C. The condensation heat transferred through the heating plate 25C is captured by the second stream segment of the oscillating stream within each of the two vertical vane heaters 25i and 25ii, as will be further explained. Concurrently, work is extracted within the expander 20 from state 7 to state 6. The stream is then split into two streams and each of the expanded streams is isochorically mixed with each of the expansion cooled, oscillating stream segments in each of the vertical vane heaters 25i and 25ii. As shown in Figure 9A, the isochoric heating of the mixed oscillating and work streams is also heated from the condensation heat released from each of the two condensers 30i and 30ii and from auxiliary heat provided by a heat exchanger 18 in thermal communication with an external heat source realized as a heat transfer material such as a hot gas or liquid, or directly with a heat source such as ambient air, a solar heater, or a combustion chamber.

[0101] It should be appreciated that the exterior surfaces of condensers 30i and 30ii are insulated, except for the surfaces in thermal contact with heater plate 25C, to minimize heat loss and maximize heat transfer.

[0102] 9D is a schematic top view of disk condenser 30, according to one embodiment. As shown, condenser 30 includes multiple cooling channel sets 31 and 32 and adiabatic segment 34. As shown, cooling channel set 31 includes hot inlets 31A, 31A2 and channel 31B in communication with a narrowing channel branch to maximize heat transfer area for condensation and cooling of the vapor-liquid cycle fluid as it is conveyed through channel 31B and exits as condensate through outlet 31C. Condenser 30 also includes a dedicated set of channels 32 for condensing or cooling an externally heated stream, for example, for incorporating externally generated heat into the working fluid to complete the cycle of FIG. 9A from point 5″ to 6. Again, a high temperature heated stream is injected through inlet 32A and conveyed through channel 32B to outlet 32C, thereby allowing heat transfer to the walls of channel 32B and, when assembled, heat exchange plate 25C of FIG. 9B. All channel walls are constructed from a highly thermally conductive material such as copper, aluminum, aluminum nitride, or other material that provides such high thermal conductivity. In contrast, section 34 is a non-conductive section, which in one embodiment includes two sections, 33 and 33A, each of different heights. Condenser segment 34 is considered to be aligned with non-thermally conductive heating wedge 25D, seen most clearly in FIGS. 9F-9H.

[0103] It should be understood that in some embodiments, the cooling channels are implemented without branches, and the channels become narrower and narrower. Moreover, in some embodiments, additional cooling sets are employed, all according to the cooling requirements.

[0104] FIG. 9E is a partial perspective view of the vane assembly 25A of the vertical vane heater pump 25 without its cylindrical vane housing, according to one embodiment. As shown, the vane assembly 25A includes a plurality of radial vanes 27 that define a constant volume chamber for isochoric mixing and heating of the expanded cooled oscillating fluid together with the expanded working fluid after work extraction. As shown, in one embodiment, the expanded cooled oscillating fluid 5 is fed to the heater through the inlet 29, and the expanded working fluid 7 enters through the inlet 30 as the vane blades 27 rotate in a clockwise direction. After heating, the fluid is pushed through the outlet 28 as either the maximum hot fluid 6′ or the hot fluid 6, depending on the external work input added to the condensation heat driving the isochoric vaporization during the vane rotation. According to one embodiment, work is generated by overcoming the valve resistance of the valve 26, as shown in FIG. 9C. It should be understood that in other embodiments, the work is input using a compressor.

[0105] 9F-9H are schematic cross-sectional side views of a vertical vane heater pump 25 showing vane assembly 25A in thermal communication with heater plate 25C at various stages of rotation.

[0106] Specifically, during rotation, the vanes 27 follow the surface geometry of the heated plate 25C and plate wedge 25D. The volume between the vanes 27 defines a constant volume in which the mixed stream of oscillating and working fluids is isovolumically vaporized from the heat of condensation conducted through the heated plate 25C. The oscillating and working fluids are isovolumically mixed by pumping the oscillating and working fluids separately into a volume-variable chamber defined by the vertically slidable vanes 27 that follow the contours of the top surfaces of the heated plate 25C and heated wedge 25D. The hot mixed fluid is forced out of the outlet port 28 as the chamber volume gradually decreases to zero volume as the vanes 27 are forced into their slots 27A by the wedge ramps 25E during plate rotation as shown in FIG. 9G.

[0107] As shown in FIG. 9G, the chamber separation is maintained by a wedge adjacent to the vane 25A. The vane 27 further proceeds to the first suction port 29 and ensures isochoric suction of the expansion-cooled oscillating fluid 5, in which the expansion-cooled oscillating fluid is neither compressed nor expanded, according to the recess 25E that allows the suction of the expansion-cooled oscillating fluid 5 into a reduced volume corresponding to the volume of the expansion-cooled condensate.

[0108] In FIG. 9H, as the vane 27 further extends following the downward slope 25F of the wedge 25D so that the expansion-cooled oscillating stream 5 fed through the inlet 29 and the post-expansion work stream 7 fed through the inlet 30 are isochorically mixed, the vane 27 further proceeds to the larger suction port 30.

[0109] FIG. 10 shows a different form of the combined thermo-oscillation and work extraction cycle of FIG. 9A. As shown in the figure, the oscillation and work cycles are similar to those of FIG. 9A, except that the mixed oscillation-work stream of m1 and m2 is isochorically heated to a dryness much lower than 1.0 to ensure that the oscillation cycle remains within the phase transition envelope, where m2 is the mass flow of the oscillation cycle, m1 is the work cycle, and the fraction (a) defines the specific enthalpy ratio of the post-expansion streams 7-5' and the expansion-cooled oscillating stream segment m2 of 5-5'. For example, m2 = (a)m1 and the mixed stream has a mass of m2 + m1 or (a + l)m1. The dryness (q) at point 8 is 0, the q at point 6 is 1.0, and at point 5″, q a is in the range of 0.05 < q a ≦1.0. The fraction (b) dryness at point 6″ defines the fraction of the total mass in the range of 0.00 < b ≦ 0.5. In each flow stream, the mass is, for example, as follows: · 5″-6″-8': 0.Zm2 = b(m2 + m1) = b((a + l)m1 (kg) · 5″-6: q(l - b)(m2 + m1) = q a (l - b)(a + l)m1 (kg) · 5″-8: 0.Xm2 = (l - q a )(1 - b)(m2 + m1) = (1 - qa )(lb)(a+l)m1(kg) 7-5′:m1(kg) 6-8″:0.Ym2=(lq a )(lb)(m2+m1)-m1=0.Ym2(lq a )(lb)(a+l)m1-m1(kg) where "X", "Y", and "Z" are the fractions of m2 in each respective designated stream.

[0110] In an embodiment, the stream is split into two parts at point 5" in the transition envelope. A portion of the liquid and vapor are separated from each other using a separator. The separated vapor is conveyed to point 6 where it is split again before expansion. The work portion is expanded and the unexpanded portion is condensed to point 8". The remaining unseparated stream at split point 5" is compressed from externally supplied work to state 6" and condensed to state 8'. The heat of condensation released from each of the two condensations is used to isochorically heat the mixture from 5' to 5'" and from 5'" to 5"", providing external heat Q in is supplied to complete the isochoric heating to point 5". Work W in is provided to further compress a fraction of the mixed stream to point 6'. Isochoric vaporization to a dryness below a value of 1.0 advantageously prevents accidental isochoric superheating. Superheating requires the rejection of heat because the high kinetic energy of the superheated vapor molecules prevents the intermolecular bonding that causes condensation. This intermolecular bonding in the condensate advantageously allows for the storage of thermal energy that is later released in the expansion cooling to a subambient heat sink.

[0111] Simulation results Next, 360m 3 11 is a simulation result showing the work output level as a function of mass flow rate for the fully coupled cycle of FIG. 10 employing working fluid R717, given a combined pump volumetric flow rate per hour. high and P high refers to the hottest condensation segment 6″~8′, T mid and Pmid refers to the cold condensing segment and 6 to 8". "H" refers to the enthalpy and specified state. [Table 2] [Table 3]

[0112] FIG. 11A shows a variation of the coupled thermal oscillation and work cycle of FIG. 9A in which the condensate is expansion cooled using flash expansion instead of an expansion valve.

[0113] As shown, the condensate at points 8 and 8' is flash cooled to state 5 and simultaneously mixed with the expanded working fluid at 5'. The superheating of the working fluid to point 7' and subsequent mixing at point 5' are depicted to illustrate the thermodynamic conditions involved, although in fact they are conditions that are achieved simultaneously in the system shown in FIG. 9C, except for expansion valves 14i and 14ii, as previously discussed.

[0114] 11B-11D are schematic cross-sectional side views of a modified embodiment of the vertical vane heater pump 25 of FIG. 9F-9H at various stages of rotation to achieve isochoric mixing through flash evaporation shown in FIG. 11A. This modified embodiment uses a heater plate wedge 45 with an upward and downward inclination as well as an apex completely adjacent to the vane plate 25A. The expanded working fluid after work extraction is pumped through the inlet 40, and while the vane advances, liquid condensate is pumped through the port inlet 41 into the low pressure heater environment, thereby causing flash evaporation and mixing with the expanded working fluid. Isochoric heating is achieved as the vane rotates around the heater plate 25C, and the high temperature and high pressure mixed fluid is forced out of the outlet port 28 as the chamber volume decreases as the vane 27 follows the upward inclination of the plate wedge 45.

[0115] 12A-12B show an alternative embodiment of a forced thermal oscillation cycle integrally coupled to a work extraction cycle. As described in other embodiments, heat is rejected at high temperature and absorbed at low temperature to drive low temperature heating and vaporization. Heat release is achieved through high temperature condensation in a first stream segment and simultaneously through flash cooling of the condensate in a second stream segment where latent heat energy is released into the resulting vapor. The description of the process steps is presented in the context of the flow diagram shown in FIG. 14. It should be understood that there are numerous process steps that occur almost instantaneously when the streams meet or split. Such streams are presented as either dashed or dotted lines. Furthermore, it should be understood that certain lines are shown in positions shifted from their actual positions in the PH diagram characterizing those parameters for clarity only. For example, dashed lines 54-56 and 54-55 have been shifted downwards and are in fact the I extending from 51-56. a Similarly, the I c has been shifted upwards, and in fact, I b Furthermore, the compression lines 56-57 have been shifted to the right and should in fact follow the constant entropy line.

[0116] FIG. 12B is an enlarged view of a portion of the PH diagram shown in FIG. 12A. The closer enlargement shows the compression between 56 and 57 achieved through the work of the pump against the outlet valve 69C of the pump, as will be further explained in the context of FIG. 14. Also more clearly visible is the I b After merging with Stream I b Stream segment I branching off from c The circulation is carried by a very low pressure pump (VLP) 76 between 51′-51″-57″-57 via an external evaporator 67.

[0117] FIG. 13 is a schematic diagram of an alternative embodiment of a thermal vibration work extractor 60 formed from an alternative embodiment of a constant volume pump 61 integrally coupled to a work extraction device 63, which generally realizes the cycle shown in FIG. 12A. The constant volume pump 61 includes a motor-driven rotor 62 having retractable vanes 64 that operate to follow the contours of the inner housing surface geometry during rotation. The vane spacing defines input and output volumes such that during fluid transport through the pump, the fluid is uncompressed prior to outlet 65A. The pump housing 66 has inlet ports 69 and 69a, one for supplying the mixed thermal vibration stream I. a +I b for the input of I, and the second for the mixed stream I comb Work Stream I to Form w The housing 61a also includes two outlet ports 69B and 69C, one unvalved and the other valved. The two ports provide for the two outlet streams, I a +I w and l b Stream I is effectively split into equal volumes of mixed and heated fluids entering Stream I. a +I w is freely discharged through the non-valved port 69B, while I b is compressed as it is discharged through valved port 69C. Additionally, in one embodiment, constant volume pump 61 includes a heating chamber 66" embedded within pump wall 61a according to one embodiment. Heating chamber 66" has a chamber inlet port 65a in communication with pump cavity 78 and a chamber outlet port 65b in communication with heated pump cavity 79. Additionally, pump wall 61a includes embedded pump heat exchangers 66 and 66' in thermal communication with heating chamber 66" according to one embodiment. Pump heat exchanger 66 exchanges thermal vibration stream I with heat exchanger 66'. a The exchanger 66′ receives heat from the hotter thermal vibration stream I b +I c Both heat exchangers 66 and 66′ are transferred to a non-circulating static stream I of mass m3 permanently located in a heating chamber 66″. s Therefore, I sFor example, when vane 64 rotates counterclockwise, it contacts through heater inlet port 65A and generates mixed stream I comb The pump heat exchanger 66' includes insulation elements 77 and is connected to the heat transfer stream I. b It blocks the heat received from the colder vibration stream I a 6, thereby maximizing heat transfer for heating chamber 66''.

[0118] Non-circulating volume I s The use of as a heat transfer agent advantageously prevents the cycle stream from overheating, thereby ensuring that the intermolecular forces of the liquid-vapor mixture within the PH envelope are available to drive condensation. Additionally, expansion achieved through flash expansion within the pump's constant volume chamber prior to heating advantageously eliminates the need for pre-expansion cooling through an expansion valve. The reduction in expansion advantageously preserves additional expansion capacity for work extraction.

[0119] In another embodiment, both heating chambers 66″ and heat exchangers 66 and 66′ are connected to a mixed stream I disposed in isovolumetric and isobaric pump chambers 78 and 79, respectively. comb It should be understood that the heat exchanger 61a is implemented as an external heat exchanger outside of the pump wall 61a while maintaining thermal communication with Stream I. a +I w The system 60 is configured to supply stream I a +I w The work stream I w and thermal vibration stream I a The system 60 includes a splitter 71 operable to split the working stream I for work extraction. w The system 60 includes a thermal vibration stream I and another work extraction device operative to expand the thermal vibration stream I. a to a heat exchanger 66 where the heat is transferred to a heating chamber 66″ and circulated to a stream combiner 68 where it is combined with the thermal vibration stream Ib Mix with.

[0120] As explained, Stream I b The refrigerant exits pump 61 through valved outlet port 69C where it is compressed. b to a heat exchanger 66′ where heat is also transferred to a heating chamber 66″, and then to stream I b to the stream combiner 68, where it is circulated to the thermal vibration stream I b and flows into the constant volume pump cavity 78 at port 69 and again into the I w As shown in the figure, before the heat transfer in the heat exchanger 66′, I b Cycle I c Stream I c receives heat from an external heat source at heater 67, and then b +I c Stream I then discharges its collective heat load in 66′. c Stream I b and recirculates when driven by a very low pressure pump (VLP) 67. In this manner, external heat is conveniently supplied to the system 60 according to operational needs. It should be understood that all embodiments have the option of adding heat from an external heat source according to operational needs.

[0121] In some circumstances, I b has a heat capacity that is not transferred to the system operation, and the system 60 is b Stream I can be configured to be directed into a bypass loop where it is cooled by a cooler 74 by rejecting heat to the cooler surroundings, as will be further described. b It is then directed through valves 72 and 75 to heater 66'.

[0122] Liquid reservoir 70 and vapor reservoirs 70A and 70B are employed to facilitate start-up or overcome other operational complications by providing the necessary liquid and vapor pressures, as is known in the art.

[0123] In yet another embodiment, the oscillating heat stream I freely exiting the first constant volume pump is a +I w But Stream I b together with the second pump, where the stream is mixed with the non-circulating stream I s Two or more constant volume pumps are coupled in series so that the heat stream I is isochorically mixed and heated through contact with the b is compressed through a valved pump outlet and directed to a pump heat exchanger disposed within the second pump, where it is converted into non-circulating stream I s2 Stream I is heated in the second pump. a +I w A second pump in the series splits the working stream, which is then free to exit and expanded through an expander or other work extraction device to produce stream I. b The first pump is directed to the second pump for isovolumic mixing with the split off of the first stream. In the first pump, the two streams are directed to another non-circulating stream segment I s1 When it comes into contact with the non-circulating stream segment I, it is mixed and heated isovolumically. s1 As it exits the second pump, it is heated by a stream split off from the working stream. The continuous constant volume pumping approach and the associated dual isochoric heating approach advantageously result in higher efficiency due to the larger mixing, heating, and compression capacity.

[0124] FIG. 14 is a flow diagram illustrating process steps taking into account the PH diagrams of FIGS. 12A and 12B and the system of FIG. 13, according to one embodiment.

[0125] For purposes of this description, the process is described in a continuous mode, with two thermal oscillation stream segments I at thermodynamic states 56 and 57 exiting pump outlet 69B and valved port 69C in step I. a and I b Starting from the pump power of , there are two thermal oscillation stream segments I with collective mass m2 and their respective molecular masses a and I b I b For (0.x)m2, I a For (1.0-0.x)m2. Work Extraction Segment I w is the vibration stream segment I a and through splitter 71 as shown at point 56 on the PH diagram.

[0126] In step J, work extraction segment I w Following work extraction, in step K, work is extracted from stream segment I w A constant volume of is directed through port 69A to constant volume pump 61. At the same time, thermal oscillation stream segment I a and I b The processing proceeds as follows:

[0127] In step L, stream segment I a is isobarically condensed to state 51 through pump heat exchanger 66, which produces condensation heat Q which is used to heat the working fluid disposed in pump heating chamber 66″. OSC-A is released.

[0128] At step M, thermal oscillation stream segment I b is adiabatically compressed to state 57 by vanes 64 to drive the working fluid through valve 69C, thereby raising the stream temperature to facilitate the transfer of condensation heat when discharged in heat exchanger 66′. bIn situations where the heat contained in the pump 61 contains excess heat or needs to be rejected for proper system function, the outlet valve 69C allows the heat from the pump 61 to flow through the segment I b is further compressed to raise the stream temperature above ambient temperature. Then, segment I b The heat Q is transferred to the cooler 74. out is released to the cooler surroundings, thereby b The flow direction is achieved through the valve configuration of valves 72 and 75 as shown. After rejection of excess heat, stream segment I b In step O, the thermal vibration segment I b +I c is isobarically condensed or condensed in heat exchanger 66' to cool to state 51'. c The released condensation heat Q OSC-B is used to isochorically heat the mixed stream segment, as will be explained later.

[0129] In step N, the self-contained cycle stream is converted to external heat Q in evaporator 67. in isobarically evaporated from state 51' to state 57'' using c For clarity purposes only, b 5, but in reality it should be understood that states 57′ and 57″ are identical. c is the stream segment I b and is isobarically condensed and cooled to state 51' in heat exchanger 66' in step O. After condensation, I c is recycled to the evaporator 67 through the low pressure pump 76, while stream segment I b is the previously isobarically condensed stream I a Mix with.

[0130] At step P, the expanded work stream I is wPreviously split work stream I from w As explained above, both thermal vibration streams I a +I b Mixed with Mixed Stream I comb It should be understood that the processes shown in dotted or dashed lines in the PH diagrams of Figures 12A and 12B represent near instantaneous processes that occur when the streams meet or split. The mixed thermal vibration stream of mass m2 and the work stream volume of mass m1 mix isochorically and / or isenthalpically upon entering the constant volume pump cavity 78 at point 52 in the PH diagram. At step Q, a static stream of mass m3 previously split off from the mixed stream in step T and permanently placed in the heating chamber 66" mixes with the static stream of mass m2. s is the thermal vibration heat Q OSC-A and Q OSC-B + Input heat Q in Receive.

[0131] In step R, the pump impeller 64 rotates to pump the mixed stream I comb is a non-circulating, static volume I with mass m3 located in the pump heating chamber 66″. s and through port 65A to allow isochoric mixing to state 53. In step S, stream I s The condensation heat Q previously released from OSC-A and Q OSC-B Stream I b +I c Input heat Q from in Mixed Stream I comb and static volume I s isochorically heated and / or evaporated to a first temperature and pressure. All condensation heat and input heat is transferred to a static volume I disposed within the heating chamber 66″. s Mixing with the mixed stream I comb is transmitted to.

[0132] At step T, a non-circulating static stream I of mass m s As previously described and shown at point 54 on the PH diagram, the mixed stream I combThe impeller 64 conveys the stream into the heating chamber volume 66''.

[0133] Alternative embodiments and applications

[0134] The described embodiments of the vibration thermal management system and thermal vibration work extractor can be configured to operate according to alternative embodiments and applications.

[0135] In one variation of the thermal vibration work extractor, additional heat or work is input to complete the isochoric heating back to the high temperature and pressure.

[0136] One alternative embodiment of the thermal vibration work extractor employs a working fluid mixed with an inert gas. After condensation of the non-inert fraction of the mixture in an isochoric heater pump, the inert gas from the condensate passes through a separator and is used to drive an expander. The condensate is expanded cooled to a liquid vapor mixture and isochorically heated as previously described.

[0137] An alternative embodiment of the thermal vibration work extractor employs an expansion to expand cooling condensate instead of an expansion valve to advantageously extract work from the vibration cycle with the expanded inert gas in addition to the combined work cycle as described above.

[0138] In one variant of the thermal vibration work extractor, the mixed stream is split into a work cycle superheated from condensed vapor from the vibration cycle and heat recovered through a recuperator from an external heat source and a heat rejection source having a higher temperature than the temperature of the mixed stream at its hottest temperature.

[0139] One embodiment of the oscillator-engine system is realized as a series arrangement of isochoric heater pumps operating to isochorically vaporize the mixed vibration-work stream using heat of condensation released from a series of condensations in progressive stages.

[0140] Specifically, the mixed oscillating-work stream with a first dryness is isochorically heated with heat released from a first condensation, then isobarically cooled to a second dryness higher than the first dryness, and isochorically reheated with condensation heat released in another condensation. The isobaric cooling to a higher dryness and subsequent isochoric heating are repeated according to the number of heater pumps in the series arrangement. External heat is added to complete the isochoric heating to the desired temperature and pressure. The mixed oscillating-work stream is then split into a work fraction for work extraction and a fraction for condensation within the oscillating cycle. It should be understood that any of the three isochoric heater pumps mentioned above can be employed in the series arrangement.

[0141] Another variation of the continuous heater pump arrangement employs multiple mixing stages of the expanded cooled condensate and the post-work-expanded working fluid to form multiple mixed oscillating-work streams, each of which is isochorically vaporized from the heat released in a single condensation.

[0142] Specifically, after the first mixing, the resulting first oscillating-work stream having a first dryness is isochorically vaporized from a portion of the condensation heat released in the single condensation. The first oscillating-work stream is isobarically cooled and mixed with the expansion-cooled condensate to form a second oscillating-work stream. The resulting second oscillating-work stream is also isochorically vaporized from a portion of the condensation heat released in the single condensation. External heat is added to complete the isochoric heating to the desired temperature and pressure. The mixed oscillating-work stream is then split into a work fraction for work extraction and a fraction for condensation within the oscillating cycle. It should be understood that any of the three aforementioned isochoric heater pumps can be employed in a series arrangement, as described above.

[0143] In some cooling applications, the vibratory thermal management system provides air conditioning, refrigeration, or refrigeration to a cooling space from which heat is transferred and used to supplement condensation heat in isobaric and / or isochoric heating in isobaric heat exchangers and / or isochoric heater pumps of the condensate expanded and cooled in the vibratory cycle.

[0144] In one heating application, the oscillating thermal management system is thermally coupled to the boiler of a desalination or distillation unit. The condensation heat released during the oscillating cycle drives the desalination or distillation, and the condensation heat released in the production of distillate is redirected to an isochoric heater pump for isochoric heating within the oscillating cycle.

[0145] In heat transfer applications, the vibrating thermal management system operates to provide both the heating and cooling functions discussed above through coupling to chillers and boilers as described.

[0146] In another application, the vibrating thermal management system is coupled to an external heat engine or integrally coupled with a work extraction device as described above to provide work in addition to cooling and / or heating.

[0147] It should be understood that all described embodiments suffer from heat losses. These heat losses are not shown for clarity. Similarly, provisions for elimination of excess heat are included in all embodiments. Some embodiments do not show these provisions, also for clarity. Additionally, while controls used in start-up and troubleshooting procedures are included in all embodiments, in some embodiments they are not shown, also for clarity.

[0148] While certain features of the invention have been illustrated and described herein, modifications, substitutions, changes, and equivalents, as known to those skilled in the art, are within the scope of the invention, and it is therefore to be understood that the appended claims are intended to cover all such modifications and changes as fall within the true spirit of the invention.

Claims

1. 1. A method of heat management in a cycle liquid-vapor stream, the method comprising: isobarically rejecting heat of condensation from a vapor of a portion of said cycle liquid-vapor stream to produce a condensate at a first temperature and a first pressure; simultaneously cooling a condensate of the cycle liquid-vapor stream to a condensate to form a cooled condensate having a second temperature lower than the first temperature and a second pressure lower than the first pressure, wherein the cooling is performed as an adiabatic or isenthalpic cooling; isochorically evaporating the cooled condensate with the heat of condensation and / or external heat; A method comprising:

2. The method of claim 1 , wherein the cooling is performed as expansion cooling.

3. The method according to claim 1 or 2, wherein the heat is the heat of condensation.

4. The method of any one of claims 1 to 3, further comprising driving an external heat engine with the heat of condensation and using the condensate as a heat sink for the external heat engine.

5. 4. The method of claim 1, further comprising heating a boiler of a distillation unit with the heat of condensation and isochorically heating the expansion-cooled condensate with heat produced in the condensation to form the distillate.

6. The method of claim 3, further comprising receiving external heat from a cooling space or the surrounding environment in the expanded and cooled condensate, the external heat supplementing the evaporation of the expanded and cooled condensate.

7. The method of claim 3 , further comprising rejecting a portion of the heat of condensation to the heated space or to the surrounding environment.

8. The method of claim 3, further comprising extracting work from a portion of the mixed vibration-work stream.

9. The method of claim 1, wherein the cooling is performed as a flash expansion into a constant volume pump.

10. The method of claim 9 , wherein the isochoric vaporization is performed in the constant volume pump.

11. 11. The method of claim 9 or 10, wherein the heat is heat of condensation captured in one or more non-circulating stream segments of the cycle liquid-vapor stream.

12. The method of claim 9 or 10, wherein the heat comprises heat captured from an external source.

13. 1. A thermal oscillator for managing heat capacity in a cycle liquid-vapor stream, said thermal oscillator comprising: a condenser having a plurality of isobaric heat conductive cooling channels operative to reject a heat of condensation from a vapor component of said cycle liquid-vapor fluid stream to form a condensate at a first temperature and a first pressure; a condensate expansion device configured to adiabatically or isenthalpicy cool the condensate to a second temperature that is lower than the first temperature and a second pressure that is lower than the first pressure to form a cooled condensate; and 1. An isochoric heater pump comprising: A plurality of constant volume heating chambers heated by the condensation heat and / or external heat; at least one inlet forming at least one mixed stream from a vibrating stream comprising the cooled condensate and at least one expanded input stream; at least one outlet configured to split the mixed stream into a first vibrated stream segment and at least one second vibrated stream segment; an isochoric heater pump including: Including, The isochoric heater pump vaporizes the cooled condensate into a vapor during transport within the isochoric heater pump, and a split first oscillating stream undergoes condensation.

14. The thermal oscillator of claim 13 , wherein the condensate expansion device is implemented as an expansion valve.

15. 15. The thermal oscillator of claim 13 or 14, wherein the isochoric heater pump comprises a twin screw drive with counter-rotating interleaved screws.

16. The thermal oscillator of claim 13 , wherein the condensate expansion device is implemented as the isochoric heater pump.

17. The thermal oscillator of claim 13 further comprising a work extraction device in thermal communication with the isochoric heater pump.

18. A thermal oscillator as described in claim 13, wherein the multiple constant volume heating chambers are heated by external heat and the constant volume heater pump is implemented as a constant volume pump in thermal communication with an external heat exchanger configured to provide the external heat.

19. A thermal oscillator described in any one of claims 13 to 16, wherein the thermal oscillator is thermally coupled to a boiler of a distillation unit and isovolumically heats the condensate heated and expanded and cooled by the condensation heat with heat released in the production of distillate.

20. The thermal oscillator of any one of claims 13 to 16, wherein the isochoric heater pump receives heat of condensation from one or more non-circulating stream segments of the cycle liquid-vapor fluid stream.

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