WO2000071944A1 - A semi self sustaining thermo-volumetric motor - Google Patents

A semi self sustaining thermo-volumetric motor Download PDF

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Publication number
WO2000071944A1
WO2000071944A1 PCT/AU2000/000469 AU0000469W WO0071944A1 WO 2000071944 A1 WO2000071944 A1 WO 2000071944A1 AU 0000469 W AU0000469 W AU 0000469W WO 0071944 A1 WO0071944 A1 WO 0071944A1
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WO
WIPO (PCT)
Prior art keywords
turbines
motor
vapour
thermo
fluid
Prior art date
Application number
PCT/AU2000/000469
Other languages
French (fr)
Inventor
Danh Thanh Trinh
Terry Howard Solomon
Kester Howard Solomon
Original Assignee
Thermal Energy Accumulator Products Pty Ltd
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Filing date
Publication date
Application filed by Thermal Energy Accumulator Products Pty Ltd filed Critical Thermal Energy Accumulator Products Pty Ltd
Priority to AU45251/00A priority Critical patent/AU4525100A/en
Publication of WO2000071944A1 publication Critical patent/WO2000071944A1/en

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Classifications

    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25BREFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B27/00Machines, plants or systems, using particular sources of energy
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01KSTEAM ENGINE PLANTS; STEAM ACCUMULATORS; ENGINE PLANTS NOT OTHERWISE PROVIDED FOR; ENGINES USING SPECIAL WORKING FLUIDS OR CYCLES
    • F01K25/00Plants or engines characterised by use of special working fluids, not otherwise provided for; Plants operating in closed cycles and not otherwise provided for
    • F01K25/08Plants or engines characterised by use of special working fluids, not otherwise provided for; Plants operating in closed cycles and not otherwise provided for using special vapours
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02CGAS-TURBINE PLANTS; AIR INTAKES FOR JET-PROPULSION PLANTS; CONTROLLING FUEL SUPPLY IN AIR-BREATHING JET-PROPULSION PLANTS
    • F02C1/00Gas-turbine plants characterised by the use of hot gases or unheated pressurised gases, as the working fluid
    • F02C1/04Gas-turbine plants characterised by the use of hot gases or unheated pressurised gases, as the working fluid the working fluid being heated indirectly
    • F02C1/05Gas-turbine plants characterised by the use of hot gases or unheated pressurised gases, as the working fluid the working fluid being heated indirectly characterised by the type or source of heat, e.g. using nuclear or solar energy
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02CGAS-TURBINE PLANTS; AIR INTAKES FOR JET-PROPULSION PLANTS; CONTROLLING FUEL SUPPLY IN AIR-BREATHING JET-PROPULSION PLANTS
    • F02C1/00Gas-turbine plants characterised by the use of hot gases or unheated pressurised gases, as the working fluid
    • F02C1/04Gas-turbine plants characterised by the use of hot gases or unheated pressurised gases, as the working fluid the working fluid being heated indirectly
    • F02C1/10Closed cycles
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25BREFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B27/00Machines, plants or systems, using particular sources of energy
    • F25B27/02Machines, plants or systems, using particular sources of energy using waste heat, e.g. from internal-combustion engines
    • YGENERAL 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
    • Y02TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02ATECHNOLOGIES FOR ADAPTATION TO CLIMATE CHANGE
    • Y02A30/00Adapting or protecting infrastructure or their operation
    • Y02A30/27Relating to heating, ventilation or air conditioning [HVAC] technologies
    • Y02A30/274Relating to heating, ventilation or air conditioning [HVAC] technologies using waste energy, e.g. from internal combustion engine

Definitions

  • the present invention relates generally to a thermo- volumetric motor and relates particularly, though not exclusively, to a thermo-volumetric motor utilising a vapour-compression refrigeration cycle or a vapour- absorption refrigeration cycle for improved heating/cooling and/or power production.
  • thermo-volumetric motor comprising a continuous fluid path adapted to carry a working fluid, said path including one or more turbines or a hydraulic motor at least one of which is operatively coupled to a compressor of a vapour-compression refrigeration system, the fluid path adapted to be in heat conductive communication with at least a condenser of the vapour-compression refrigeration system whereby in operation the working fluid recovers latent heat from the condenser to effect expansion of said fluid which drives said one or more turbines or the hydraulic motor which drives the compressor and thus the vapour-compression refrigeration system, said fluid thereafter condensing and recirculating to recover latent heat from the condenser.
  • the continuous fluid path is also adapted, between said turbines or the hydraulic motor and the condenser, to be in heat conductive communication with an evaporator of the vapour-compression refrigeration system whereby in use the latent heat of vaporisation of a refrigerant gas flowing through the evaporator effects cooling of the working fluid.
  • the fluid path is not in heat conductive communication with the condenser and the fluid path additionally comprises a working fluid condenser positioned downstream of said turbines or the hydraulic motor.
  • the fluid path may include a turbine compressor or a boundary layer pump coupled to and thus driven by the turbines or the hydraulic motor, the turbine compressor or the boundary layer pump located downstream of said turbines or the hydraulic motor.
  • the continuous fluid path further comprises a heat exchanger disposed between the condenser of the vapour-compression refrigeration system and said one or more turbines or the hydraulic motor, the heat exchanger adapted to be in heat conductive communication with an external heat source which thus transfers heat to the working fluid in the continuous fluid path via the heat exchanger.
  • the external heat source can be a combusted fossil or other fuel or waste heat from a combustion engine such as a diesel exhaust, a water radiator jacket, solar, geothermal , wood kiln or other sources of waste heat.
  • the fluid path does not include the heat exchanger and thus is not in heat communication with an external heat source but rather an electrical motor coupled to the compressor and said turbines or the hydraulic motor is driven by an external electrical power supply.
  • the continuous fluid path includes multiple turbines coupled to one another, one of said multiple turbines being operatively coupled via a mechanical drive such as a belt drive to the compressor or an electric motor connected to the compressor.
  • the continuous fluid path also includes one or more mixing chambers located upstream of the multiple turbines, said chambers each being designed to receive and mix a gas and a liquid component of the working fluid so as to produce a wet gaseous working fluid.
  • the multiple turbines are boundary- layer turbines which operate effectively with the wet gaseous working fluid.
  • said one or more turbines or the hydraulic motor are mechanically coupled to a power generator designed for electrical or motive power generation in static or mobile applications from small to large sizes such as that required in power houses, vehicles or boats.
  • the continuous fluid path further includes a pump being designed to recirculate the working fluid around said path.
  • an air conditioning system and a thermo- volumetric motor combination comprising: a continuous vapour-compression refrigeration cycle adapted to carry a refrigerant or working fluid, said cycle including at least a compressor located upstream of a condenser which is positioned upstream of an evaporator; and a continuous fluid path adapted to carry an other working fluid, said path including one or more turbines or a hydraulic motor being coupled to the compressor, the fluid path being in heat conductive communication with at least the condenser whereby in operation the other working fluid recovers latent heat from the condenser to effect - - - expansion of said fluid which drives said one or more turbines or the hydraulic motor which drives the compressor and thus the air conditioning system, said other working fluid thereafter condensing and recirculating to recover latent heat from the condenser.
  • thermo-volumetric motor including a continuous fluid path adapted to carry a working fluid, said path including one or more turbines or a hydraulic motor; coupling one of said turbines or the hydraulic motor to a compressor of a vapour-compression refrigeration system; and coupling the continuous fluid path to the vapour- compression refrigeration system wherein at least a condenser of the vapour-compression refrigeration system is in heat conductive communication with said path whereby in operation the working fluid recovers latent heat from the condenser to effect expansion of said fluid which drives said one or more turbines or the hydraulic motor which drives the compressor and thus the vapour- compression refrigeration system, said fluid thereafter condensing and recirculating to recover latent heat from the condenser.
  • thermo-volumetric motor comprising a continuous fluid path adapted to carry a working fluid, said path being formed of a single stream and dual streams, the single stream including one or more turbines or a hydraulic motor at least one of which is operatively coupled to a compressor of a vapour-compression refrigeration system or a boundary layer pump, and a vapour/liquid separator located downstream of said turbines or the hydraulic motor, the separator providing vapour and liquid to each of the respective dual streams, one of the dual streams including the compressor or the boundary layer pump which is designed to pressurise the vapour, the dual streams together being connected to and in heat conductive communication with a condenser such that the latent heat of the pressurised vapour is exchanged with the liquid in the other of the dual streams, said dual streams thereafter combining for mixing of the vapour and liquid which drives said one or more turbines or the hydraulic motor which thus drives the compressor or the boundary layer pump of the vapour- compression refrigeration system.
  • a vapour-absorption refrigeration system and a thermo-volumetric motor combination comprising a continuous vapour-absorption cycle being adapted to carry a refrigerant/working fluid and water mixture, said cycle including a condensor located upstream of a heat generator which is upstream of one or more turbines or a hydraulic motor operatively coupled to a generator whereby in operation the heat generator effects partial vaporisation of the refrigerant/working fluid and water mixture wherein a refrigerant gas fraction is expanded through said turbines or the hydraulic motor which drives the generator, and an unevaporated fraction of said mixture is diverted to the condensor and combined with the expanded refrigerant gas fraction in the condensor and thereafter recirculated to the heat generator.
  • a method of generating motive power comprising the steps of : providing a continuous vapour-absorption cycle being adapted to carry a refrigerant/working fluid and water mixture, said cycle including a condensor located upstream of a heat generator which is upstream of one or more turbines or a hydraulic motor operatively coupled to a generator; evaporating at least part of the refrigerant/working fluid mixture in the heat generator; expanding a refrigerant gas fraction of said mixture through the turbines or the hydraulic motor which thus drives the generator; and diverting an unevaporated fraction of said mixture from the heat generator to the condensor where it is combined with the expanded refrigerant gas fraction in the condensor and thereafter recirculated to the heat generator .
  • thermo-volumetric motor comprising : one or multiple power cycles each having a continuous stream being adapted to carry a compressible fluid and a common continuous stream being adapted to carry an incompressible fluid; a hydraulic cylinder dedicated to each of the power cycles wherein the compressible fluid and the incompressible fluid flows to opposite sides of the respective cylinder,- a hydraulic motor included m the common continuous stream, said motor being operatively coupled to a generator; and a heat exchanger dedicated to each of the continuous streams, said heat exchanger being operatively coupled to a waste heat source whereby m operation the compressible fluid is heated via the waste heat source m the heat exchanger and expanded through the respective hydraulic cylinder which recirculates the incompressible fluid through the common continuous stream and the hydraulic motor which thus drives the generator.
  • the multiple power cycles are m heat conductive communication with each other.
  • a method of generating motive power comprising the steps of: providing a thermo-volumetric motor including one or more power cycles each having a continuous stream being adapted to carry a compressible fluid and a common continuous stream being adapted to carry an incompressible fluid, a hydraulic cylinder dedicated to each of the power cycles and a hydraulic motor included m the common continuous stream; heating the compressible fluid m each of the continuous streams and expanding said fluid through the respective hydraulic cylinder; and recirculating the incompressible fluid through the common continuous stream via the hydraulic cylinders thereby driving the hydraulic motor and a generator to which it is operatively coupled.
  • the working fluid includes but is not limited to hydrochlorofluorocarbons (HCFCs) R123, R22, hydrofluorocarbons (HFCs) R134a, ammonia, hydrocarbons (HCs) n-butane, isobutane, isopentane or propane gas.
  • the working fluid includes but is not limited to steam for high temperature applications.
  • thermo- volumetric motor and method of generating motive power together with other aspects of the invention
  • FIG. 1 is a schematic of a thermo-volumetric motor together with a vapour-compression refrigeration system
  • Figure 2 is a schematic of another thermo-volumetric motor together with a vapour-compression refrigeration system
  • FIG. 3 is a schematic of a further thermo- volumetric motor in conjunction with a vapour-compression refrigeration system
  • FIG. 4 is a schematic of yet another thermo- volumetric motor in conjunction with a vapour-compression refrigeration system
  • FIG. 5 is a schematic of a thermo-volumetric motor together with a compressor of a vapour-compression refrigeration system
  • Figure 6 is a schematic of another thermo-volumetric motor together with a vapour-compression refrigeration system
  • FIG. 7 is a schematic of yet another thermo- volumetric motor in conjunction with a vapour-compression refrigeration system
  • Figure 8 is a schematic of a further thermo- volumetric motor in conjunction with a vapour-absorption refrigeration system
  • Figure 9 is a schematic of an apparatus for producing motive power utilising waste heat from in this example a diesel engine .
  • thermo-volumetric motor 10 together with a vapour- compression refrigeration system 12.
  • components and assemblies of Figures 2 to 4 which generally correspond to components and assemblies of Figure 1 have been designated with the Figure numeral prefixing like components and assemblies.
  • thermo-volumetric motor of Figures 2, 3, and 4 have been designated as 210, 310, and 410, respectively.
  • the embodiments of a thermo-volumetric motor shown in Figures 7 and 8 are in essence similar to that of Figures 2 and 4, respectively, except for the turbines having been replaced with a hydraulic motor.
  • thermo-volumetric motor 10 and vapour-compression refrigeration system 12 of Figure 1 include a continuous fluid path 14 and a continuous vapour-compression refrigeration cycle 16, respectively.
  • both the fluid path 14 and the vapour-compression refrigeration cycle 16 are adapted to carry a working fluid in the form of a refrigerant gas such as R123, " R22, R134a, ammonia, n-butane, isobutane, isopentane or propane gas .
  • the continuous fluid path or thermo-volumetric cycle 14 of this embodiment includes a pair of turbines 18 and 20 connected to one another via a common shaft .
  • the turbines 18 and 20 are of a boundary- layer drag type.
  • the thermo-volumetric cycle 14 also includes a mixing chamber 22 and a heat exchanger 24 located upstream of the turbines 18 and 20.
  • the mixing chamber 22 is important in mixing liquid and vapour fractions or components of the working fluid, in this example a refrigerant gas, so as to produce a wet gaseous working fluid which is required for effective operation of the turbines 18 and 20.
  • the heat exchanger 24 may be of a shell and tube construction preferably with the refrigerant gas flowing through the shell.
  • the heat exchanger 24 is in heat conductive communication with a heat source 26 which can be a combusted fossil or other fuel or waste heat from a combustion engine such as a diesel exhaust, a water radiator jacket, solar, geothermal , wood kiln, or other sources of waste heat .
  • the vapour-compression refrigeration cycle 16 of this example is a standard air conditioning refrigeration cycle.
  • the cycle 16 includes a condenser 28, a compressor
  • the condenser 28 is typically a plate exchanger whereas the evaporator 32 is generally a tube-in-tube exchanger.
  • the compressor 30 may be driven by an electrical motor 36.
  • thermo-volumetric cycle 14 of Figure 1 is in heat conductive communication with both the condenser 28 and the evaporator 32.
  • the turbine or expeller 20 is mechanically coupled to the electrical motor 36 via a belt drive 38 or other suitable couplings or connections.
  • rotation of the turbines 18 and 20 effects rotation of the motor 36 which drives the compressor 30.
  • a portion of the thermo-volumetric cycle defines a tube of the evaporator 32 and further downstream a flow passage of the plate-type condenser 28.
  • COP Heating or cooling load (W) / compressor power (W) .
  • the COP of the standard air conditioning refrigeration can be from three to five. That is, a COP of three means that the system efficiency is 300% whereby the system can produce a heating or cooling output three times that of the power input. This will hereinafter be generally referred to as the COP effect.
  • thermo-volumetric motor such as 10.
  • the COP effect is to return heat to the thermo-volumetric motor 10 which thereby at least reduces its need for external heat.
  • the thermo- volumetric motor 10 drives the compressor 30 providing air conditioning or heating with a reduced need for power. Therefore, the thermo-volumetric motor converts what would otherwise be waste heat from a refrigeration cycle into an air conditioning application which may require little additional electrical power consumption. Accordingly, the COP effect is used to enhance the thermo-volumetric motor to at least semi self-sustaining status. Other heat sources may be required as illustrated depending on the cooling and/or heating load requirements of the system.
  • thermo- volumetric motor 10 is critical insofar as it drives the air conditioning compressor such as 30.
  • the system would typically be of a split air conditioning system design being simple and compact and having minimal noise within a building.
  • the electrical motor 36 and compressor 30 are directly coupled to the expeller 20 with a direct mechanical power conversion between these devices with zero electrical power loss.
  • the electrical motor 36 can be used as startup, back-up or top-up as needed.
  • the belt drive 38 is generally designed as a reducer in order to optimise the performance or match the speed of the compressor 30.
  • thermo-volumetric cycle 14 includes a pump 40 designed to recirculate the refrigerant gas around the cycle 14.
  • Another pump 42 may be included between the waste heat source 26 and the heat exchanger 24 as a means of transferring heat. It should also be appreciated that an electronic control system will typically be incorporated to control the various components described.
  • thermo-volumetric motor 210 and vapour-compression refrigeration cycle 212 of Figure 2 is similar to that of Figure 1 except it relies upon ambient cooling rather than forced cooling via the evaporator 232.
  • the ambient cooling is effected using a turbine condenser 211 located downstream of the expeller 220. This is appropriate where a suitable ambient source is available and maximises the cooling load of the refrigeration cycle 212.
  • the system of Figure 2 also excludes the electric motor 36 but rather relies upon the heat source 226 in initiating or sustaining operation of the thermo-volumetric motor 214.
  • thermo-volumetric motor 310 and refrigeration cycle 312 of Figure 3 uses a turbine compressor 311 or a boundary layer pump for pumping the refrigerant gas.
  • the pressurised refrigerant gas does not exchange heat with the refrigerant cycle 312 via the evaporator 332.
  • Both the compressor 330 and the turbine compressor 311 or a boundary layer pump are directly coupled to the turbines 318 and 320. It is expected that electrical power will be required to start up the system or use as a top-up with no external heat input .
  • the system of Figure 4 is substantially identical to the thermo-volumetric motor and refrigeration cycle of Figure 1 with the inclusion of a generator designated as 411.
  • the generator 411 is directly coupled to a common shaft of the turbines 418 and 420 and can be used for electrical generation or motive power generation in static or mobile applications from small to large sizes such as that required in power houses, vehicles or boats.
  • FIG. 5 illustrates one form of another aspect of the invention.
  • a thermo- volumetric motor shown generally as 510 comprising a continuous fluid path formed of a single stream 511 and dual streams 513 and 515.
  • the single stream 511 of the thermo-volumetric motor 510 includes a pair of turbines 518 and 520 constructed and arranged in a similar manner to the preceding embodiments.
  • a mixing chamber 522 is located upstream of the turbines 518 and 520.
  • a vapour-liquid separator 517 is positioned downstream of the expeller 520 and is designed to provide liquid and vapour fractions for the respective dual streams 513 and 515.
  • the vapour fraction flows to a compressor 530 of a standard vapour-compression refrigeration system.
  • the pressurised vapour from the compressor 530 ' then exchanges its latent heat with the liquid fraction of the other stream via a condenser 519 through which both of the dual streams 513 and 515 pass.
  • the dual streams 513 and 515 then combine in a heat exchanger 521 located upstream of the mixing chamber 522.
  • the heat exchanger 521 is in heat conductive communication with an external heat source 526.
  • the compressor 530 is directly coupled to a common shaft of the turbines 518 and 520 for the production of power. It will be appreciated that this application can be used for electrical generation or motive power such as that required in vehicles or boats. In essence, the thermo-volumetric motor and vapour- compression refrigeration cycle of the preceding examples have been combined into a single cycle. This is made possible through incorporation of the separator 517.
  • FIG. 6 is a schematic of another thermo-volumetric motor 610 and vapour-compression refrigeration cycle 612 similar to that of Figure 1 except that the turbines 18 and 20 are to be replaced with a hydraulic motor 618 such as that disclosed in the applicants International patent application No. PCT/AU95/00655. Further, it relies upon ambient cooling rather than forced cooling via the evaporator 632. The ambient cooling is effected using a condenser 611 located downstream of the hydraulic motor 618. This is appropriate where a suitable ambient source is available and maximises the cooling load of the refrigeration cycle 612. The system of Figure 6 also excludes the electric motor 36 but rather relies upon the heat source 626 in initiating or sustaining operation of the thermo-volumetric motor 614.
  • FIG 7 is a schematic of yet another thermo-volumetric motor 710 in conjunction with a vapour-compression refrigeration cycle 712 which are substantially identical to the thermo-volumetric motor and refrigeration cycle of Figure 1 with the inclusion of a generator designated as 711.
  • the generator 711 is directly coupled to a common shaft of the hydraulic motor 718 and can be used for electrical generation or motive power such as that in vehicles or boats.
  • FIG 8 is a schematic of one embodiment of a further aspect of the invention relating to a vapour-absorption refrigeration system and a thermo-volumetric motor combination designated generally as 800.
  • the vapour- absorption refrigeration system/thermo-volumetric motor 800 comprises a continuous vapour-absorption cycle 801 being adapted to carry a refrigerant/working fluid, in this example ammonia, and water mixture.
  • the continuous vapour-absorption cycle 801 includes a condensor or absorber 803 located upstream of a heat generator 805.
  • the vapour-absorption cycle 801 of this particular example also includes a hydraulic motor positioned between the heat generator 805 and the absorber 803.
  • the hydraulic motor 807 includes one or more hydraulic cylinders such as 809 together with the hydraulic motor 813 which is operatively coupled to an electrical generator 815.
  • the ammonia and water mixture is expanded through one side of the hydraulic cylinder 809 whilst in this embodiment pressurised oil is driven through an opposite side of the hydraulic cylinder 809 so as to actuate the hydraulic motor 813.
  • the heat generator 805 is in heat conductive communication with a driving heat source 817 which in this example is hot water being recirculated at a temperature of between 85 to 90°C.
  • the condensor or absorber 803 is a closed vessel which is in heat conductive communication with an ambient heat sink which is in the form of cooling water at a temperature of between 20 to 25°C.
  • vapour-absorption refrigeration system/thermo-volumetric motor 800 of Figure 8 involves the following general steps:
  • the ammonia and water mixture is partially evaporated through the heat generator 805;
  • an ammonia gas fraction flows to and is expanded within the hydraulic cylinder 809 whereas an unevaporated fraction of the ammonia and water mixture is diverted to the condenser or absorber 803;
  • the expanded ammonia gas is absorbed together with the unevaporated fraction of the ammonia/water mixture in the absorber 803;
  • the vapour-absorption cycle using in this example ammonia gas has a COP effect similar to the vapour-compression cycle of the preceding embodiments.
  • the vapour- compression cycle uses a compressor which requires electric input to compress the vapour whereas the vapour- absorption cycle uses a solution to absorb the vapour which requires heat and not electrical input .
  • the ammonia and water solution has an affinity towards and thus absorbs the expanded ammonia gas entering the condensor 803.
  • the hot water from a diesel engine may serve as the driving heat source 817 to effect vaporisation of the working fluid such as the ammonia and water mixture.
  • the vapour-absorption cycle does not require a compressor, and accordingly represents a different cycle to implement than the vapour-compression cycle.
  • the vapour-absorption cycle using ammonia, utilises the fact that the temperature of the ammonia exiting the hydraulic motor 807, is generally lower than the ambient temperature of the surrounding atmosphere. As a consequence the ammonia will absorb heat energy from the surrounding atmosphere.
  • the consequence of this aspect of the vapour-absorption cycle is that the energy content of the ammonia is raised by absorption of free energy from the surrounding atmosphere and therefore requires less heat energy input before its return to the heat generator 805.
  • FIG. 9 is a schematic of a thermo-volumetric motor 900 of an embodiment according to yet another aspect of the invention.
  • This motor is similar in construction to the multiple turbine motor system of the applicants disclosed in Australian provisional patent application No. PQ4237. However, in this instance hydraulic cylinders are operatively coupled to a hydraulic motor and a corresponding generator.
  • the thermo-volumetric motor 900 of this embodiment comprises two power cycles designated generally as 901 and 903 each having a continuous respective stream 905 and 907 being adapted to carry a compressible fluid which in this example is a refrigerant gas.
  • the multiple power cycles 901 and 903 also include a common continuous stream 909 which is adapted to carry an incompressible fluid, such as pressurised oil.
  • Each of the power cycles such as 901 includes a hydraulic cylinder such as 913 being adapted to carry the compressible and the incompressible fluids on its respective opposite sides. Furthermore, each of the power cycles such as 901 includes a heat exchangers 915 operatively coupled to a waste heat source.
  • the waste heat source for one of the power cycles such as 901 is a hot exhaust waste 917 from a diesel engine whereas the water radiator waste 919 of the diesel engine serves as the waste heat source for the other power cycle 903.
  • the hot exhaust of this example is at a temperature of about 500°C and the water radiator at a temperature of around 90°C.
  • each of the continuous streams 905 and 907 of the respective power cycles includes a recirculatory pump such as 921 located downstream of a condensor 923.
  • the heat exchanger on the "hot exhaust" side of the motor 900 is of a fin and tube construction whereas the heat exchanger on the "water radiator” side is of a shell and tube construction.
  • the common continuous stream or common hydraulic oil train 909 provides a flow of oil to a hydraulic motor 923 which is operatively coupled to an electrical generator 925.
  • the waste heat source heats the refrigerant gas of the respective power cycle wherein the gas is expanded through one side of the respective hydraulic cylinder such as 913.
  • the expanded refrigerant gas is then condensed within the respective condensor such as 923 and recirculated to the heat exchanger such as 915 via the recirculatory pump 921.
  • Expansion of the refrigerant gas through the hydraulic cylinder drives the pressurised oil on the opposite side of the cylinder so as to effect a flow of the pressurised oil through the hydraulic motor 923.
  • the pressurised oil is then returned to the respective hydraulic cylinder 913 whilst the hydraulic motor 923 actuates the electrical generator 925.
  • the principal of operation of this thermo- volumetric motor is similar to that disclosed in the applicant's Australian provisional patent application No. PQ4237 the disclosure of which is included herein by way of reference.
  • thermo-volumetric motor and vapour-compression refrigeration cycle when combined have low operational costs compared to existing air conditioning systems;
  • thermo-volumetric motor and vapour-compression refrigeration cycle are environmentally friendly;
  • the apparatus and method maximise waste heat energy recovery in generating motive power; and (iv) the configuration of the apparatus including single or multiple power cycles adapted to recover waste heat enables significant waste heat recovery.
  • thermo-volumetric motor may be replaced with one or more hydraulic motors such as that disclosed in the applicants International patent application No. PCT/AU95/00655. Further, it is not essential that the air conditioning refrigeration cycle or system is a standard system although this is preferable.

Abstract

The present invention relates generally to a thermo-volumetric motor (10) together with a vapour compression refrigeration system (12) each including a respective continuous fluid path (14) and a continuous vapour-compression refrigeration cycle (16). The continuous fluid path or thermo-volumetric cycle (14) includes a pair of turbines (18) and (20) connected to one another via a common shaft. The thermo-volumetric cycle (14) also includes a mixing chamber (22) and a heat exchanger (24) located upstream of the turbines (18) and (20). The vapour-compression refrigeration cycle of this example is a standard air conditioning refrigeration cycle. The cycle (16) includes a condenser (28) a compressor (30) and evaporator (32) and an expansion valve (34) connected together in a conventional manner. The thermo-volumetric cycle (14) is in heat conductive communication with both the condenser (28) and the evaporator (32). The turbine or expeller (20) is mechanically coupled to an electrical motor (36) via a belt drive (38) wherein rotation of the turbines (18) and (20) effects rotation of the motor (30) which drives the compressor (30).

Description

A SEMI SELF SUSTAINING THERMO-VOLUMETRIC MOTOR
FIELD OF THE INVENTION
The present invention relates generally to a thermo- volumetric motor and relates particularly, though not exclusively, to a thermo-volumetric motor utilising a vapour-compression refrigeration cycle or a vapour- absorption refrigeration cycle for improved heating/cooling and/or power production.
SUMMARY OF THE INVENTION
According to one aspect of the present invention there is provided a thermo-volumetric motor comprising a continuous fluid path adapted to carry a working fluid, said path including one or more turbines or a hydraulic motor at least one of which is operatively coupled to a compressor of a vapour-compression refrigeration system, the fluid path adapted to be in heat conductive communication with at least a condenser of the vapour-compression refrigeration system whereby in operation the working fluid recovers latent heat from the condenser to effect expansion of said fluid which drives said one or more turbines or the hydraulic motor which drives the compressor and thus the vapour-compression refrigeration system, said fluid thereafter condensing and recirculating to recover latent heat from the condenser.
Preferably the continuous fluid path is also adapted, between said turbines or the hydraulic motor and the condenser, to be in heat conductive communication with an evaporator of the vapour-compression refrigeration system whereby in use the latent heat of vaporisation of a refrigerant gas flowing through the evaporator effects cooling of the working fluid. Alternatively the fluid path is not in heat conductive communication with the condenser and the fluid path additionally comprises a working fluid condenser positioned downstream of said turbines or the hydraulic motor. According to another variant the fluid path may include a turbine compressor or a boundary layer pump coupled to and thus driven by the turbines or the hydraulic motor, the turbine compressor or the boundary layer pump located downstream of said turbines or the hydraulic motor.
Typically the continuous fluid path further comprises a heat exchanger disposed between the condenser of the vapour-compression refrigeration system and said one or more turbines or the hydraulic motor, the heat exchanger adapted to be in heat conductive communication with an external heat source which thus transfers heat to the working fluid in the continuous fluid path via the heat exchanger. Generally the external heat source can be a combusted fossil or other fuel or waste heat from a combustion engine such as a diesel exhaust, a water radiator jacket, solar, geothermal , wood kiln or other sources of waste heat. Alternatively the fluid path does not include the heat exchanger and thus is not in heat communication with an external heat source but rather an electrical motor coupled to the compressor and said turbines or the hydraulic motor is driven by an external electrical power supply.
Typically the continuous fluid path includes multiple turbines coupled to one another, one of said multiple turbines being operatively coupled via a mechanical drive such as a belt drive to the compressor or an electric motor connected to the compressor. Generally the continuous fluid path also includes one or more mixing chambers located upstream of the multiple turbines, said chambers each being designed to receive and mix a gas and a liquid component of the working fluid so as to produce a wet gaseous working fluid. In this instance the multiple turbines are boundary- layer turbines which operate effectively with the wet gaseous working fluid.
Typically said one or more turbines or the hydraulic motor are mechanically coupled to a power generator designed for electrical or motive power generation in static or mobile applications from small to large sizes such as that required in power houses, vehicles or boats.
Generally the continuous fluid path further includes a pump being designed to recirculate the working fluid around said path.
According to another aspect of the present invention there is provided an air conditioning system and a thermo- volumetric motor combination comprising: a continuous vapour-compression refrigeration cycle adapted to carry a refrigerant or working fluid, said cycle including at least a compressor located upstream of a condenser which is positioned upstream of an evaporator; and a continuous fluid path adapted to carry an other working fluid, said path including one or more turbines or a hydraulic motor being coupled to the compressor, the fluid path being in heat conductive communication with at least the condenser whereby in operation the other working fluid recovers latent heat from the condenser to effect - - - expansion of said fluid which drives said one or more turbines or the hydraulic motor which drives the compressor and thus the air conditioning system, said other working fluid thereafter condensing and recirculating to recover latent heat from the condenser.
According to a further aspect of the present invention there is provided a method of generating motive power, said method comprising the steps of : providing a thermo-volumetric motor including a continuous fluid path adapted to carry a working fluid, said path including one or more turbines or a hydraulic motor; coupling one of said turbines or the hydraulic motor to a compressor of a vapour-compression refrigeration system; and coupling the continuous fluid path to the vapour- compression refrigeration system wherein at least a condenser of the vapour-compression refrigeration system is in heat conductive communication with said path whereby in operation the working fluid recovers latent heat from the condenser to effect expansion of said fluid which drives said one or more turbines or the hydraulic motor which drives the compressor and thus the vapour- compression refrigeration system, said fluid thereafter condensing and recirculating to recover latent heat from the condenser.
According to yet another aspect of the present invention there is provided a thermo-volumetric motor comprising a continuous fluid path adapted to carry a working fluid, said path being formed of a single stream and dual streams, the single stream including one or more turbines or a hydraulic motor at least one of which is operatively coupled to a compressor of a vapour-compression refrigeration system or a boundary layer pump, and a vapour/liquid separator located downstream of said turbines or the hydraulic motor, the separator providing vapour and liquid to each of the respective dual streams, one of the dual streams including the compressor or the boundary layer pump which is designed to pressurise the vapour, the dual streams together being connected to and in heat conductive communication with a condenser such that the latent heat of the pressurised vapour is exchanged with the liquid in the other of the dual streams, said dual streams thereafter combining for mixing of the vapour and liquid which drives said one or more turbines or the hydraulic motor which thus drives the compressor or the boundary layer pump of the vapour- compression refrigeration system.
According to yet a further aspect of the present invention there is provided a vapour-absorption refrigeration system and a thermo-volumetric motor combination comprising a continuous vapour-absorption cycle being adapted to carry a refrigerant/working fluid and water mixture, said cycle including a condensor located upstream of a heat generator which is upstream of one or more turbines or a hydraulic motor operatively coupled to a generator whereby in operation the heat generator effects partial vaporisation of the refrigerant/working fluid and water mixture wherein a refrigerant gas fraction is expanded through said turbines or the hydraulic motor which drives the generator, and an unevaporated fraction of said mixture is diverted to the condensor and combined with the expanded refrigerant gas fraction in the condensor and thereafter recirculated to the heat generator.
According to still another aspect of the present invention there is provided a method of generating motive power, said method comprising the steps of : providing a continuous vapour-absorption cycle being adapted to carry a refrigerant/working fluid and water mixture, said cycle including a condensor located upstream of a heat generator which is upstream of one or more turbines or a hydraulic motor operatively coupled to a generator; evaporating at least part of the refrigerant/working fluid mixture in the heat generator; expanding a refrigerant gas fraction of said mixture through the turbines or the hydraulic motor which thus drives the generator; and diverting an unevaporated fraction of said mixture from the heat generator to the condensor where it is combined with the expanded refrigerant gas fraction in the condensor and thereafter recirculated to the heat generator .
According to still a further aspect of the present invention there is provided a thermo-volumetric motor comprising : one or multiple power cycles each having a continuous stream being adapted to carry a compressible fluid and a common continuous stream being adapted to carry an incompressible fluid; a hydraulic cylinder dedicated to each of the power cycles wherein the compressible fluid and the incompressible fluid flows to opposite sides of the respective cylinder,- a hydraulic motor included m the common continuous stream, said motor being operatively coupled to a generator; and a heat exchanger dedicated to each of the continuous streams, said heat exchanger being operatively coupled to a waste heat source whereby m operation the compressible fluid is heated via the waste heat source m the heat exchanger and expanded through the respective hydraulic cylinder which recirculates the incompressible fluid through the common continuous stream and the hydraulic motor which thus drives the generator.
Alternatively or additionally the multiple power cycles are m heat conductive communication with each other.
According to an additional aspect of the present invention there is provided a method of generating motive power, said method comprising the steps of: providing a thermo-volumetric motor including one or more power cycles each having a continuous stream being adapted to carry a compressible fluid and a common continuous stream being adapted to carry an incompressible fluid, a hydraulic cylinder dedicated to each of the power cycles and a hydraulic motor included m the common continuous stream; heating the compressible fluid m each of the continuous streams and expanding said fluid through the respective hydraulic cylinder; and recirculating the incompressible fluid through the common continuous stream via the hydraulic cylinders thereby driving the hydraulic motor and a generator to which it is operatively coupled.
Generally the working fluid includes but is not limited to hydrochlorofluorocarbons (HCFCs) R123, R22, hydrofluorocarbons (HFCs) R134a, ammonia, hydrocarbons (HCs) n-butane, isobutane, isopentane or propane gas. Alternatively, the working fluid includes but is not limited to steam for high temperature applications.
BRIEF DESCRIPTION OF THE DRAWINGS
In order to achieve a better understanding of the nature of the present invention several embodiments of a thermo- volumetric motor and method of generating motive power together with other aspects of the invention will now be described, by way of example only, with reference to the accompanying drawings in which:
Figure 1 is a schematic of a thermo-volumetric motor together with a vapour-compression refrigeration system; Figure 2 is a schematic of another thermo-volumetric motor together with a vapour-compression refrigeration system;
Figure 3 is a schematic of a further thermo- volumetric motor in conjunction with a vapour-compression refrigeration system;
Figure 4 is a schematic of yet another thermo- volumetric motor in conjunction with a vapour-compression refrigeration system;
Figure 5 is a schematic of a thermo-volumetric motor together with a compressor of a vapour-compression refrigeration system; Figure 6 is a schematic of another thermo-volumetric motor together with a vapour-compression refrigeration system;
Figure 7 is a schematic of yet another thermo- volumetric motor in conjunction with a vapour-compression refrigeration system;
Figure 8 is a schematic of a further thermo- volumetric motor in conjunction with a vapour-absorption refrigeration system; and Figure 9 is a schematic of an apparatus for producing motive power utilising waste heat from in this example a diesel engine .
DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS As shown in Figures 1 to 4 there are various embodiments of a thermo-volumetric motor 10 together with a vapour- compression refrigeration system 12. For ease of reference and to avoid repetition those components and assemblies of Figures 2 to 4 which generally correspond to components and assemblies of Figure 1 have been designated with the Figure numeral prefixing like components and assemblies. For example, the thermo-volumetric motor of Figures 2, 3, and 4 have been designated as 210, 310, and 410, respectively. Furthermore, the embodiments of a thermo-volumetric motor shown in Figures 7 and 8 are in essence similar to that of Figures 2 and 4, respectively, except for the turbines having been replaced with a hydraulic motor.
The thermo-volumetric motor 10 and vapour-compression refrigeration system 12 of Figure 1 include a continuous fluid path 14 and a continuous vapour-compression refrigeration cycle 16, respectively. In this example both the fluid path 14 and the vapour-compression refrigeration cycle 16 are adapted to carry a working fluid in the form of a refrigerant gas such as R123," R22, R134a, ammonia, n-butane, isobutane, isopentane or propane gas .
The continuous fluid path or thermo-volumetric cycle 14 of this embodiment includes a pair of turbines 18 and 20 connected to one another via a common shaft . The turbines 18 and 20 are of a boundary- layer drag type.
The thermo-volumetric cycle 14 also includes a mixing chamber 22 and a heat exchanger 24 located upstream of the turbines 18 and 20. The mixing chamber 22 is important in mixing liquid and vapour fractions or components of the working fluid, in this example a refrigerant gas, so as to produce a wet gaseous working fluid which is required for effective operation of the turbines 18 and 20. The heat exchanger 24 may be of a shell and tube construction preferably with the refrigerant gas flowing through the shell. The heat exchanger 24 is in heat conductive communication with a heat source 26 which can be a combusted fossil or other fuel or waste heat from a combustion engine such as a diesel exhaust, a water radiator jacket, solar, geothermal , wood kiln, or other sources of waste heat .
The vapour-compression refrigeration cycle 16 of this example is a standard air conditioning refrigeration cycle. The cycle 16 includes a condenser 28, a compressor
30, an evaporator 32, and an expansion valve 34 connected together in a conventional manner. The condenser 28 is typically a plate exchanger whereas the evaporator 32 is generally a tube-in-tube exchanger. The compressor 30 may be driven by an electrical motor 36.
The thermo-volumetric cycle 14 of Figure 1 is in heat conductive communication with both the condenser 28 and the evaporator 32. The turbine or expeller 20 is mechanically coupled to the electrical motor 36 via a belt drive 38 or other suitable couplings or connections. Thus, rotation of the turbines 18 and 20 effects rotation of the motor 36 which drives the compressor 30. In this example, a portion of the thermo-volumetric cycle defines a tube of the evaporator 32 and further downstream a flow passage of the plate-type condenser 28.
In a standard vapour-compression refrigeration cycle such as that described the coefficient of performance (COP) is defined as: COP = Heating or cooling load (W) / compressor power (W) .
Depending on operational parameters it is generally recognised that the COP of the standard air conditioning refrigeration can be from three to five. That is, a COP of three means that the system efficiency is 300% whereby the system can produce a heating or cooling output three times that of the power input. This will hereinafter be generally referred to as the COP effect.
A significant feature of the present invention relates to utilisation of the COP effect in the thermo-volumetric motor such as 10. It will be appreciated that by coupling the thermo-volumetric motor 10 to the standard vapour- compression refrigeration cycle 12 that the overall system performance is enhanced by maximising waste heat recovery from the refrigeration cycle 12 utilising the COP effect. In particular, the COP effect is to return heat to the thermo-volumetric motor 10 which thereby at least reduces its need for external heat. Accordingly the thermo- volumetric motor 10 drives the compressor 30 providing air conditioning or heating with a reduced need for power. Therefore, the thermo-volumetric motor converts what would otherwise be waste heat from a refrigeration cycle into an air conditioning application which may require little additional electrical power consumption. Accordingly, the COP effect is used to enhance the thermo-volumetric motor to at least semi self-sustaining status. Other heat sources may be required as illustrated depending on the cooling and/or heating load requirements of the system.
In all embodiments described and illustrated the thermo- volumetric motor 10 is critical insofar as it drives the air conditioning compressor such as 30. In an air conditioning application the system would typically be of a split air conditioning system design being simple and compact and having minimal noise within a building. The electrical motor 36 and compressor 30 are directly coupled to the expeller 20 with a direct mechanical power conversion between these devices with zero electrical power loss. The electrical motor 36 can be used as startup, back-up or top-up as needed. The belt drive 38 is generally designed as a reducer in order to optimise the performance or match the speed of the compressor 30.
The thermo-volumetric cycle 14 includes a pump 40 designed to recirculate the refrigerant gas around the cycle 14. Another pump 42 may be included between the waste heat source 26 and the heat exchanger 24 as a means of transferring heat. It should also be appreciated that an electronic control system will typically be incorporated to control the various components described.
The thermo-volumetric motor 210 and vapour-compression refrigeration cycle 212 of Figure 2 is similar to that of Figure 1 except it relies upon ambient cooling rather than forced cooling via the evaporator 232. The ambient cooling is effected using a turbine condenser 211 located downstream of the expeller 220. This is appropriate where a suitable ambient source is available and maximises the cooling load of the refrigeration cycle 212. The system of Figure 2 also excludes the electric motor 36 but rather relies upon the heat source 226 in initiating or sustaining operation of the thermo-volumetric motor 214.
The thermo-volumetric motor 310 and refrigeration cycle 312 of Figure 3 uses a turbine compressor 311 or a boundary layer pump for pumping the refrigerant gas. In this instance the pressurised refrigerant gas does not exchange heat with the refrigerant cycle 312 via the evaporator 332. Once again this maximises the cooling load of the standard air conditioning refrigeration cycle 312. Both the compressor 330 and the turbine compressor 311 or a boundary layer pump are directly coupled to the turbines 318 and 320. It is expected that electrical power will be required to start up the system or use as a top-up with no external heat input .
The system of Figure 4 is substantially identical to the thermo-volumetric motor and refrigeration cycle of Figure 1 with the inclusion of a generator designated as 411. The generator 411 is directly coupled to a common shaft of the turbines 418 and 420 and can be used for electrical generation or motive power generation in static or mobile applications from small to large sizes such as that required in power houses, vehicles or boats.
Figure 5 illustrates one form of another aspect of the invention. In this embodiment there is a thermo- volumetric motor shown generally as 510 comprising a continuous fluid path formed of a single stream 511 and dual streams 513 and 515. The single stream 511 of the thermo-volumetric motor 510 includes a pair of turbines 518 and 520 constructed and arranged in a similar manner to the preceding embodiments. A mixing chamber 522 is located upstream of the turbines 518 and 520.
A vapour-liquid separator 517 is positioned downstream of the expeller 520 and is designed to provide liquid and vapour fractions for the respective dual streams 513 and 515. The vapour fraction flows to a compressor 530 of a standard vapour-compression refrigeration system. The pressurised vapour from the compressor 530 ' then exchanges its latent heat with the liquid fraction of the other stream via a condenser 519 through which both of the dual streams 513 and 515 pass. The dual streams 513 and 515 then combine in a heat exchanger 521 located upstream of the mixing chamber 522. As with the preceding examples the heat exchanger 521 is in heat conductive communication with an external heat source 526.
Importantly the compressor 530 is directly coupled to a common shaft of the turbines 518 and 520 for the production of power. It will be appreciated that this application can be used for electrical generation or motive power such as that required in vehicles or boats. In essence, the thermo-volumetric motor and vapour- compression refrigeration cycle of the preceding examples have been combined into a single cycle. This is made possible through incorporation of the separator 517.
Figure 6 is a schematic of another thermo-volumetric motor 610 and vapour-compression refrigeration cycle 612 similar to that of Figure 1 except that the turbines 18 and 20 are to be replaced with a hydraulic motor 618 such as that disclosed in the applicants International patent application No. PCT/AU95/00655. Further, it relies upon ambient cooling rather than forced cooling via the evaporator 632. The ambient cooling is effected using a condenser 611 located downstream of the hydraulic motor 618. This is appropriate where a suitable ambient source is available and maximises the cooling load of the refrigeration cycle 612. The system of Figure 6 also excludes the electric motor 36 but rather relies upon the heat source 626 in initiating or sustaining operation of the thermo-volumetric motor 614.
Figure 7 is a schematic of yet another thermo-volumetric motor 710 in conjunction with a vapour-compression refrigeration cycle 712 which are substantially identical to the thermo-volumetric motor and refrigeration cycle of Figure 1 with the inclusion of a generator designated as 711. The generator 711 is directly coupled to a common shaft of the hydraulic motor 718 and can be used for electrical generation or motive power such as that in vehicles or boats.
Figure 8 is a schematic of one embodiment of a further aspect of the invention relating to a vapour-absorption refrigeration system and a thermo-volumetric motor combination designated generally as 800. The vapour- absorption refrigeration system/thermo-volumetric motor 800 comprises a continuous vapour-absorption cycle 801 being adapted to carry a refrigerant/working fluid, in this example ammonia, and water mixture. The continuous vapour-absorption cycle 801 includes a condensor or absorber 803 located upstream of a heat generator 805. The vapour-absorption cycle 801 of this particular example also includes a hydraulic motor positioned between the heat generator 805 and the absorber 803. The hydraulic motor 807 includes one or more hydraulic cylinders such as 809 together with the hydraulic motor 813 which is operatively coupled to an electrical generator 815. The ammonia and water mixture is expanded through one side of the hydraulic cylinder 809 whilst in this embodiment pressurised oil is driven through an opposite side of the hydraulic cylinder 809 so as to actuate the hydraulic motor 813. The heat generator 805 is in heat conductive communication with a driving heat source 817 which in this example is hot water being recirculated at a temperature of between 85 to 90°C. The condensor or absorber 803 is a closed vessel which is in heat conductive communication with an ambient heat sink which is in the form of cooling water at a temperature of between 20 to 25°C.
In operation, the vapour-absorption refrigeration system/thermo-volumetric motor 800 of Figure 8 involves the following general steps:
(i) the ammonia and water mixture is partially evaporated through the heat generator 805; (ii) an ammonia gas fraction flows to and is expanded within the hydraulic cylinder 809 whereas an unevaporated fraction of the ammonia and water mixture is diverted to the condenser or absorber 803; (iii) the expanded ammonia gas is absorbed together with the unevaporated fraction of the ammonia/water mixture in the absorber 803; and
(iv) the ammonia and water solution is recirculated to the heat generator 805 via a recirculatory pump 819.
The vapour-absorption cycle using in this example ammonia gas has a COP effect similar to the vapour-compression cycle of the preceding embodiments. The vapour- compression cycle uses a compressor which requires electric input to compress the vapour whereas the vapour- absorption cycle uses a solution to absorb the vapour which requires heat and not electrical input . The ammonia and water solution has an affinity towards and thus absorbs the expanded ammonia gas entering the condensor 803. Furthermore, in this example the hot water from a diesel engine may serve as the driving heat source 817 to effect vaporisation of the working fluid such as the ammonia and water mixture. The vapour-absorption cycle does not require a compressor, and accordingly represents a different cycle to implement than the vapour-compression cycle. In its implementation, the vapour-absorption cycle, using ammonia, utilises the fact that the temperature of the ammonia exiting the hydraulic motor 807, is generally lower than the ambient temperature of the surrounding atmosphere. As a consequence the ammonia will absorb heat energy from the surrounding atmosphere. The consequence of this aspect of the vapour-absorption cycle is that the energy content of the ammonia is raised by absorption of free energy from the surrounding atmosphere and therefore requires less heat energy input before its return to the heat generator 805.
Figure 9 is a schematic of a thermo-volumetric motor 900 of an embodiment according to yet another aspect of the invention. This motor is similar in construction to the multiple turbine motor system of the applicants disclosed in Australian provisional patent application No. PQ4237. However, in this instance hydraulic cylinders are operatively coupled to a hydraulic motor and a corresponding generator. The thermo-volumetric motor 900 of this embodiment comprises two power cycles designated generally as 901 and 903 each having a continuous respective stream 905 and 907 being adapted to carry a compressible fluid which in this example is a refrigerant gas. The multiple power cycles 901 and 903 also include a common continuous stream 909 which is adapted to carry an incompressible fluid, such as pressurised oil. Each of the power cycles such as 901 includes a hydraulic cylinder such as 913 being adapted to carry the compressible and the incompressible fluids on its respective opposite sides. Furthermore, each of the power cycles such as 901 includes a heat exchangers 915 operatively coupled to a waste heat source. In this particular construction of the thermo-volumetric motor 900 the waste heat source for one of the power cycles such as 901 is a hot exhaust waste 917 from a diesel engine whereas the water radiator waste 919 of the diesel engine serves as the waste heat source for the other power cycle 903. The hot exhaust of this example is at a temperature of about 500°C and the water radiator at a temperature of around 90°C. Otherwise, each of the continuous streams 905 and 907 of the respective power cycles includes a recirculatory pump such as 921 located downstream of a condensor 923. The heat exchanger on the "hot exhaust" side of the motor 900 is of a fin and tube construction whereas the heat exchanger on the "water radiator" side is of a shell and tube construction. The common continuous stream or common hydraulic oil train 909 provides a flow of oil to a hydraulic motor 923 which is operatively coupled to an electrical generator 925.
In operation, the waste heat source heats the refrigerant gas of the respective power cycle wherein the gas is expanded through one side of the respective hydraulic cylinder such as 913. The expanded refrigerant gas is then condensed within the respective condensor such as 923 and recirculated to the heat exchanger such as 915 via the recirculatory pump 921. Expansion of the refrigerant gas through the hydraulic cylinder drives the pressurised oil on the opposite side of the cylinder so as to effect a flow of the pressurised oil through the hydraulic motor 923. The pressurised oil is then returned to the respective hydraulic cylinder 913 whilst the hydraulic motor 923 actuates the electrical generator 925. Otherwise, the principal of operation of this thermo- volumetric motor is similar to that disclosed in the applicant's Australian provisional patent application No. PQ4237 the disclosure of which is included herein by way of reference.
Now that several embodiments of the various aspects of the invention have been described in some detail it will be apparent to those skilled in the art that these embodiments of the invention have at least the following advantages : (i) the thermo-volumetric motor and vapour-compression refrigeration cycle when combined have low operational costs compared to existing air conditioning systems; (ii) the thermo-volumetric motor and vapour-compression refrigeration cycle are environmentally friendly;
(iii) the apparatus and method maximise waste heat energy recovery in generating motive power; and (iv) the configuration of the apparatus including single or multiple power cycles adapted to recover waste heat enables significant waste heat recovery.
Those skilled in the art will appreciate that the invention described herein is susceptible to variations and modifications other than those specifically described. For example, the turbines of the thermo-volumetric motor may be replaced with one or more hydraulic motors such as that disclosed in the applicants International patent application No. PCT/AU95/00655. Further, it is not essential that the air conditioning refrigeration cycle or system is a standard system although this is preferable.
All such variations and modifications are to be considered within the scope of the present invention the nature of which is to be determined from the foregoing description.

Claims

THE CLAIMS DEFINING THE INVENTION ARE AS FOLLOWS :
1. A thermo-volumetric motor comprising a continuous fluid path adapted to carry a working fluid, said path including one or more turbines or a hydraulic motor at least one of which is operatively coupled to a compressor of a vapour-compression refrigeration system, the fluid path adapted to be in heat conductive communication with at least a condenser of the vapour-compression refrigeration system whereby in operation the working fluid recovers latent heat from the condenser to effect expansion of said fluid which drives said one or more turbines or the hydraulic motor which drives the compressor and thus the vapour-compression refrigeration system, said fluid thereafter condensing and recirculating to recover latent heat from the condenser.
2. A thermo-volumetric motor as defined in claim 1 wherein the continuous fluid path is also adapted, between said turbines or the hydraulic motor and the condenser, to be in heat conductive communication with an evaporator of the vapour-compression refrigeration system whereby in use the latent heat of vaporisation of a refrigerant gas flowing through the evaporator effects cooling of the working fluid.
3. A thermo-volumetric motor as defined in claim 1 wherein the fluid path is not in heat conductive communication with the condenser and the fluid path additionally comprises a working fluid condenser positioned downstream of said turbines or the hydraulic motor .
4. A thermo-volumetric motor as defined in claim 1 wherein the fluid path includes a turbine compressor or a boundary layer pump coupled to and thus driven by the turbines or the hydraulic motor, the turbine compressor or the boundary layer pump located downstream of said turbines or the hydraulic motor.
5. A thermo-volumetric motor as defined in any one of the preceding claims wherein the continuous fluid path further comprises a heat exchanger disposed between the condenser of the vapour-compression refrigeration system and said one or more turbines or the hydraulic motor, the heat exchanger adapted to be in heat conductive communication with an external heat source which thus transfers heat to the working fluid in the continuous fluid path via the heat exchanger.
6. A thermo-volumetric motor as defined in any one of claims 1 to 4 wherein an electrical motor is coupled to the compressor and said turbines or the hydraulic motor is thus driven by an external electrical power supply.
7. A thermo-volumetric motor as defined in any one of the preceding claims wherein the continuous fluid path includes multiple turbines coupled to one another, one of said multiple turbines being operatively coupled via a mechanical drive such as a belt drive to the compressor or an electric motor connected to the compressor.
8. A thermo-volumetric motor as defined in any one of the preceding claims wherein the continuous fluid path also includes one or more mixing chambers located upstream of the multiple turbines, said chambers each being designed to receive and mix a gas and a liquid component of the working fluid so as to produce a wet gaseous working fluid.
9. A thermo-volumetric motor as defined m claim 8 wherein the multiple turbines are boundary- layer turbines which operate effectively with the wet gaseous working fluid.
10. A thermo-volumetric motor as defined m any one of the preceding claims wherein said one or more turbines or the hydraulic motor are mechanically coupled to a power generator designed for electrical or motive power generation m static or mobile applications.
11. A thermo-volumetric motor as defined m any one of the preceding claims wherein the continuous fluid path further includes a pump being designed to recirculate the working fluid around said path.
12. An air conditioning system and a thermo-volumetric motor combination comprising: a continuous vapour-compression refrigeration cycle adapted to carry a refrigerant or working fluid, said cycle including at least a compressor located upstream of a condenser which is positioned upstream of an evaporator; and a continuous fluid path adapted to carry an other working fluid, said path including one or more turbines or a hydraulic motor being coupled to the compressor, the fluid path being m heat conductive communication with at least the condenser whereby m operation the other working fluid recovers latent heat from the condenser to effect expansion of said fluid which drives said one or more turbines or the hydraulic motor which drives the compressor and thus the air conditioning system, said other working fluid thereafter condensing and recirculating to recover latent heat from the condenser.
13. A method of generating motive power, said method comprising the steps of: providing a thermo-volumetric motor including a continuous fluid path adapted to carry a working fluid, said path including one or more turbines or a hydraulic motor; coupling one of said turbines or the hydraulic motor to a compressor of a vapour-compression refrigeration system; and coupling the continuous fluid path to the vapour- compression refrigeration system wherein at least a condenser of the vapour-compression refrigeration system is in heat conductive communication with said path whereby in operation the working fluid recovers latent heat from the condenser to effect expansion of said fluid which drives said one or more turbines or the hydraulic motor which drives the compressor and thus the vapour- compression refrigeration system, said fluid thereafter condensing and recirculating to recover latent heat from the condenser.
14. A thermo-volumetric motor comprising a continuous fluid path adapted to carry a working fluid, said path being formed of a single stream and dual streams, the single stream including one or more turbines or a hydraulic motor at least one of which is operatively coupled to a compressor of a vapour-compression refrigeration system or a boundary layer pump, and a vapour/liquid separator located downstream of said turbines or the hydraulic motor, the separator providing vapour and liquid to each of the respective dual streams, one of the dual streams including the compressor or the boundary layer pump which is designed to pressurise the vapour, the dual streams together being connected to and in heat conductive communication with a condenser such that the latent heat of the pressurised vapour is exchanged with the liquid in the other of the dual streams, said dual streams thereafter combining for mixing of the vapour and liquid which drives said one or more turbines or the hydraulic motor which thus drives the compressor or the boundary layer pump of the vapour- compression refrigeration system.
15. A vapour-absorption refrigeration system and a thermo-volumetric motor combination comprising a continuous vapour-absorption cycle being adapted to carry a refrigerant/working fluid and water mixture, said cycle including a condensor located upstream of a heat generator which is upstream of one or more turbines or a hydraulic motor operatively coupled to a generator whereby in operation the heat generator effects partial vaporisation of the refrigerant/working fluid and water mixture wherein a refrigerant gas fraction is expanded through said turbines or the hydraulic motor which drives the generator, and an unevaporated fraction of said mixture is diverted to the condensor and combined with the expanded refrigerant gas fraction in the condensor and thereafter recirculated to the heat generator.
16. A method of generating motive power, said method comprising the steps of: providing a continuous vapour-absorption cycle being adapted to carry a refrigerant/working fluid and water mixture, said cycle including a condensor located upstream of a heat generator which is upstream of one or more turbines or a hydraulic motor operatively coupled to a generator; evaporating at least part of the refrigerant/working fluid mixture in the heat generator; expanding a refrigerant gas fraction of said mixture through the turbines or the hydraulic motor which thus drives the generator; and diverting an unevaporated fraction of said mixture from the heat generator to the condensor where it is combined with the expanded refrigerant gas fraction in the condensor and thereafter recirculated to the heat generator .
17. A thermo-volumetric motor comprising: one or multiple power cycles each having a continuous stream being adapted to carry a compressible fluid and a common continuous stream being adapted to carry an incompressible fluid; a hydraulic cylinder dedicated to each of the power cycles wherein the compressible fluid and the incompressible fluid flows to opposite sides of the respective cylinder; a hydraulic motor included in the common continuous stream, said motor being operatively coupled to a generator; and a heat exchanger dedicated to each of the continuous streams, said heat exchanger being operatively coupled to a waste heat source whereby in operation the compressible fluid is heated via the waste heat source in the heat exchanger and expanded through the respective hydraulic cylinder which recirculates the incompressible fluid through the common continuous stream and the hydraulic motor which thus drives the generator.
18. A thermo-volumetric motor as defined in claim 17 wherein the multiple power cycles are in heat conductive communication with each other.
19. A method of generating motive power, said method comprising the steps of : providing a thermo-volumetric motor including one or more power cycles each having a continuous stream being adapted to carry a compressible fluid and a common continuous stream being adapted to carry an incompressible fluid, a hydraulic cylinder dedicated to each of the power cycles and a hydraulic motor included in the common continuous stream; heating the compressible fluid in each of the continuous streams and expanding said fluid through the respective hydraulic cylinder; recirculating the incompressible fluid through the common continuous stream via the hydraulic cylinders thereby driving the hydraulic motor and a generator to which it is operatively coupled.
PCT/AU2000/000469 1999-05-20 2000-05-18 A semi self sustaining thermo-volumetric motor WO2000071944A1 (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
AU45251/00A AU4525100A (en) 1999-05-20 2000-05-18 A semi self sustaining thermo-volumetric motor

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WO2004022920A1 (en) * 2002-09-06 2004-03-18 Drysdale Kenneth William Patte Apparatus, method and software for use with an air conditioning cycle
FR2853016A1 (en) * 2003-03-25 2004-10-01 Denso Corp LOST HEAT USE SYSTEM
EP1574698A1 (en) * 2004-02-27 2005-09-14 Kabushiki Kaisha Toyota Jidoshokki Vehicle exhaust heat recovery system
WO2007042215A1 (en) 2005-10-07 2007-04-19 Alf Gundermann Method and device for generating mechanical or electrical energy from heat
EP1803593A1 (en) * 2005-12-28 2007-07-04 Sanden Corporation Air conditioning systems for vehicles
EP1895139A1 (en) * 2006-08-22 2008-03-05 Werner Schmidt Energy supply system
CN100408940C (en) * 2002-02-25 2008-08-06 奥特菲特能源公司 Waste heat solar energy system
GB2449130A (en) * 2007-05-09 2008-11-12 Joseph Francis Brown Jr Steam cycle condenser cooled by refrigeration cycle
WO2010117299A1 (en) * 2009-04-10 2010-10-14 Katchanov Sergey Aleksandrovitch Method and device for converting the inherent energy of the environment
US7845171B2 (en) 2006-06-23 2010-12-07 Man Nutzfahrzeuge Ag Supercharged internal combustion engine with an expander unit in a heat recovery circuit
WO2014031526A1 (en) * 2012-08-20 2014-02-27 Echogen Power Systems, L.L.C. Supercritical working fluid circuit with a turbo pump and a start pump in series configuration
WO2014059231A1 (en) * 2012-10-12 2014-04-17 Echogen Power Systems, L.L.C. Supercritical carbon dioxide power cycle for waste heat recovery
US8857186B2 (en) 2010-11-29 2014-10-14 Echogen Power Systems, L.L.C. Heat engine cycles for high ambient conditions
US8869531B2 (en) 2009-09-17 2014-10-28 Echogen Power Systems, Llc Heat engines with cascade cycles
US8966901B2 (en) 2009-09-17 2015-03-03 Dresser-Rand Company Heat engine and heat to electricity systems and methods for working fluid fill system
FR3010739A1 (en) * 2013-09-19 2015-03-20 Renault Sa COOLING AN ELECTRIC MACHINE OF A MOTOR VEHICLE
US9014791B2 (en) 2009-04-17 2015-04-21 Echogen Power Systems, Llc System and method for managing thermal issues in gas turbine engines
US9062898B2 (en) 2011-10-03 2015-06-23 Echogen Power Systems, Llc Carbon dioxide refrigeration cycle
WO2015117621A1 (en) * 2014-02-06 2015-08-13 Talbot New Energy Ag Low-pressure power generation system
US9118226B2 (en) 2012-10-12 2015-08-25 Echogen Power Systems, Llc Heat engine system with a supercritical working fluid and processes thereof
US9284855B2 (en) 2010-11-29 2016-03-15 Echogen Power Systems, Llc Parallel cycle heat engines
US9316404B2 (en) 2009-08-04 2016-04-19 Echogen Power Systems, Llc Heat pump with integral solar collector
US9441504B2 (en) 2009-06-22 2016-09-13 Echogen Power Systems, Llc System and method for managing thermal issues in one or more industrial processes
US9458738B2 (en) 2009-09-17 2016-10-04 Echogen Power Systems, Llc Heat engine and heat to electricity systems and methods with working fluid mass management control
US9638065B2 (en) 2013-01-28 2017-05-02 Echogen Power Systems, Llc Methods for reducing wear on components of a heat engine system at startup
US9752460B2 (en) 2013-01-28 2017-09-05 Echogen Power Systems, Llc Process for controlling a power turbine throttle valve during a supercritical carbon dioxide rankine cycle
US9863282B2 (en) 2009-09-17 2018-01-09 Echogen Power System, LLC Automated mass management control
CN108662809A (en) * 2017-03-30 2018-10-16 李华玉 Double-work medium combined cycle compression heat pump
US10934895B2 (en) 2013-03-04 2021-03-02 Echogen Power Systems, Llc Heat engine systems with high net power supercritical carbon dioxide circuits
US11187112B2 (en) 2018-06-27 2021-11-30 Echogen Power Systems Llc Systems and methods for generating electricity via a pumped thermal energy storage system
US11293309B2 (en) 2014-11-03 2022-04-05 Echogen Power Systems, Llc Active thrust management of a turbopump within a supercritical working fluid circuit in a heat engine system
US11435120B2 (en) 2020-05-05 2022-09-06 Echogen Power Systems (Delaware), Inc. Split expansion heat pump cycle
US11629638B2 (en) 2020-12-09 2023-04-18 Supercritical Storage Company, Inc. Three reservoir electric thermal energy storage system

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Cited By (40)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN100408940C (en) * 2002-02-25 2008-08-06 奥特菲特能源公司 Waste heat solar energy system
WO2004022920A1 (en) * 2002-09-06 2004-03-18 Drysdale Kenneth William Patte Apparatus, method and software for use with an air conditioning cycle
FR2853016A1 (en) * 2003-03-25 2004-10-01 Denso Corp LOST HEAT USE SYSTEM
US7748226B2 (en) 2003-03-25 2010-07-06 Denso Corporation Waste heat utilizing system
EP1574698A1 (en) * 2004-02-27 2005-09-14 Kabushiki Kaisha Toyota Jidoshokki Vehicle exhaust heat recovery system
US7353661B2 (en) 2004-02-27 2008-04-08 Kabushiki Kaisha Toyota Jidoshokki Vehicle exhaust heat recovery system
WO2007042215A1 (en) 2005-10-07 2007-04-19 Alf Gundermann Method and device for generating mechanical or electrical energy from heat
EP1803593A1 (en) * 2005-12-28 2007-07-04 Sanden Corporation Air conditioning systems for vehicles
US7845171B2 (en) 2006-06-23 2010-12-07 Man Nutzfahrzeuge Ag Supercharged internal combustion engine with an expander unit in a heat recovery circuit
EP1895139A1 (en) * 2006-08-22 2008-03-05 Werner Schmidt Energy supply system
GB2449130A (en) * 2007-05-09 2008-11-12 Joseph Francis Brown Jr Steam cycle condenser cooled by refrigeration cycle
GB2449130B (en) * 2007-05-09 2011-11-30 Joseph Francis Brown Jr Refrigerant cooled main steam condenser binary cycle
WO2010117299A1 (en) * 2009-04-10 2010-10-14 Katchanov Sergey Aleksandrovitch Method and device for converting the inherent energy of the environment
US9014791B2 (en) 2009-04-17 2015-04-21 Echogen Power Systems, Llc System and method for managing thermal issues in gas turbine engines
US9441504B2 (en) 2009-06-22 2016-09-13 Echogen Power Systems, Llc System and method for managing thermal issues in one or more industrial processes
US9316404B2 (en) 2009-08-04 2016-04-19 Echogen Power Systems, Llc Heat pump with integral solar collector
US9458738B2 (en) 2009-09-17 2016-10-04 Echogen Power Systems, Llc Heat engine and heat to electricity systems and methods with working fluid mass management control
US9115605B2 (en) 2009-09-17 2015-08-25 Echogen Power Systems, Llc Thermal energy conversion device
US9863282B2 (en) 2009-09-17 2018-01-09 Echogen Power System, LLC Automated mass management control
US8869531B2 (en) 2009-09-17 2014-10-28 Echogen Power Systems, Llc Heat engines with cascade cycles
US8966901B2 (en) 2009-09-17 2015-03-03 Dresser-Rand Company Heat engine and heat to electricity systems and methods for working fluid fill system
US9410449B2 (en) 2010-11-29 2016-08-09 Echogen Power Systems, Llc Driven starter pump and start sequence
US8857186B2 (en) 2010-11-29 2014-10-14 Echogen Power Systems, L.L.C. Heat engine cycles for high ambient conditions
US9284855B2 (en) 2010-11-29 2016-03-15 Echogen Power Systems, Llc Parallel cycle heat engines
US9062898B2 (en) 2011-10-03 2015-06-23 Echogen Power Systems, Llc Carbon dioxide refrigeration cycle
US9091278B2 (en) 2012-08-20 2015-07-28 Echogen Power Systems, Llc Supercritical working fluid circuit with a turbo pump and a start pump in series configuration
WO2014031526A1 (en) * 2012-08-20 2014-02-27 Echogen Power Systems, L.L.C. Supercritical working fluid circuit with a turbo pump and a start pump in series configuration
US9118226B2 (en) 2012-10-12 2015-08-25 Echogen Power Systems, Llc Heat engine system with a supercritical working fluid and processes thereof
US9341084B2 (en) 2012-10-12 2016-05-17 Echogen Power Systems, Llc Supercritical carbon dioxide power cycle for waste heat recovery
WO2014059231A1 (en) * 2012-10-12 2014-04-17 Echogen Power Systems, L.L.C. Supercritical carbon dioxide power cycle for waste heat recovery
US9752460B2 (en) 2013-01-28 2017-09-05 Echogen Power Systems, Llc Process for controlling a power turbine throttle valve during a supercritical carbon dioxide rankine cycle
US9638065B2 (en) 2013-01-28 2017-05-02 Echogen Power Systems, Llc Methods for reducing wear on components of a heat engine system at startup
US10934895B2 (en) 2013-03-04 2021-03-02 Echogen Power Systems, Llc Heat engine systems with high net power supercritical carbon dioxide circuits
FR3010739A1 (en) * 2013-09-19 2015-03-20 Renault Sa COOLING AN ELECTRIC MACHINE OF A MOTOR VEHICLE
WO2015117621A1 (en) * 2014-02-06 2015-08-13 Talbot New Energy Ag Low-pressure power generation system
US11293309B2 (en) 2014-11-03 2022-04-05 Echogen Power Systems, Llc Active thrust management of a turbopump within a supercritical working fluid circuit in a heat engine system
CN108662809A (en) * 2017-03-30 2018-10-16 李华玉 Double-work medium combined cycle compression heat pump
US11187112B2 (en) 2018-06-27 2021-11-30 Echogen Power Systems Llc Systems and methods for generating electricity via a pumped thermal energy storage system
US11435120B2 (en) 2020-05-05 2022-09-06 Echogen Power Systems (Delaware), Inc. Split expansion heat pump cycle
US11629638B2 (en) 2020-12-09 2023-04-18 Supercritical Storage Company, Inc. Three reservoir electric thermal energy storage system

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