WO2017112875A1 - Systèmes, procédés et appareils pour mettre en œuvre un cycle fermé entrainé par chaleur de basse qualité pour produire une réfrigération et une puissance d'axe - Google Patents

Systèmes, procédés et appareils pour mettre en œuvre un cycle fermé entrainé par chaleur de basse qualité pour produire une réfrigération et une puissance d'axe Download PDF

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Publication number
WO2017112875A1
WO2017112875A1 PCT/US2016/068342 US2016068342W WO2017112875A1 WO 2017112875 A1 WO2017112875 A1 WO 2017112875A1 US 2016068342 W US2016068342 W US 2016068342W WO 2017112875 A1 WO2017112875 A1 WO 2017112875A1
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air
gas
cycle
refrigerant
heat
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PCT/US2016/068342
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English (en)
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Jonathan SHERBECK
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Arizona Technology Enterprises
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Publication of WO2017112875A1 publication Critical patent/WO2017112875A1/fr

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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F22—STEAM GENERATION
    • F22B—METHODS OF STEAM GENERATION; STEAM BOILERS
    • F22B3/00—Other methods of steam generation; Steam boilers not provided for in other groups of this subclass
    • F22B3/02—Other methods of steam generation; Steam boilers not provided for in other groups of this subclass involving the use of working media other than water

Definitions

  • Embodiments of the invention relate generally to the field of thermodynamics and energy conversion, and more particularly, to methods and systems for implementing a closed low grade heat driven Rankine cycle driving a reverse Brayton cycle using an ejector with a liquid desiccant loop to produce shaft power and refrigeration by adiabatic expansion and evaporation (the Sherbeck cycle).
  • Figure 1 depicts a system architecture in accordance with an embodiment of the invention
  • Figure 2 depicts the four sub-cycles of a Sherbeck cycle in accordance with an embodiment of the invention
  • Figure 3A depicts a waste heat driven steam Rankine cycle in accordance with an embodiment of the invention
  • Figure 3B depicts a desiccant solution cycle in accordance with an embodiment of the invention
  • Figure 3C depicts a reverse Brayton cycle in accordance with an embodiment of the invention
  • Figure 3D depicts an evaporative cooler process in accordance with an embodiment of the invention
  • Figure 4 depicts a Sherbeck cycle in accordance with an embodiment of the invention
  • Figure 5 is a flow diagram illustrating a method for implementing a closed low grade heat driven Rankine cycle driving a reverse Brayton cycle using an ejector with a liquid desiccant loop to produce shaft power and refrigeration by adiabatic expansion and evaporation in accordance with described embodiments;
  • Figure 6 depicts an ejector refrigeration cycle which is heat driven in accordance with an embodiment of the invention
  • Figure 7 depicts a Sherbeck cycle psychometric chart in accordance with described embodiments
  • Figure 8 depicts another Sherbeck cycle in accordance with described embodiments
  • Figure 9 depicts a T-s or temperature-entropy diagram of the reverse Brayton cycle within the Sherbeck cycle in accordance with described embodiments
  • Figure 10 depicts yet another Sherbeck cycle in accordance with described embodiments.
  • FIGS 11A and 11B depict a complete Sherbeck cycle system in accordance with one embodiment of the invention.
  • Described herein are systems and methods for implementing a closed low grade heat driven Rankine cycle driving a reverse Brayton cycle using an ejector with a liquid desiccant loop to produce shaft power and refrigeration by adiabatic expansion and evaporation.
  • Sherbeck cycle dehumidification for air conditioning
  • Such technology is composed of subsystems based on reverse Brayton cycles, steam Rankine cycles, evaporative cooling cycles and desiccant solution cycles. Such sub-cycles operate internally at atmospheric and sub-atmospheric pressures.
  • a Sherbeck cycle system therefore utilizes only air and water as working fluids, which are non-hazardous and environmentally friendly, a key feature that distinguishes a Sherbeck cycle system from other cooling and dehumidification systems available in the marketplace today.
  • Using a numerical model for such a Sherbeck cycle system it has been demonstrated that commercially acceptable performance for dehumidification in dry and moderately humid ambient conditions is attainable.
  • Sherbeck cycle may provide means for off- grid refrigeration and electric power to the developing world and to remote locations which require off-grid power and/or refrigeration.
  • the a Sherbeck cycle plant has the potential to be made at a modest cost and thus is feasible to deploy into a wide array of commercial, industrial, residential, medical, military, and various support solutions and power/refrigeration
  • the described system is a closed loop system, a wide variety of working fluids can be employed at the discretion and preference of the operator and/or manufacturer.
  • the system is capable of operating anywhere from sub- atmospheric, to very high atmospheric, using, for instance, super-critical carbon dioxide.
  • the system is capable to work with low grade heat to a high heat limited only by the materials available.
  • Figure 1 depicts a system architecture 100 in accordance with an embodiment of the invention.
  • alternator 101 by which to output conversion power, for instance, converting shaft power to electrical output power for storage or immediate use.
  • the depicted cycle utilizes a gas, a refrigerant, and a desiccant to produce shaft power, and refrigeration from low grade heat, including heat which may be waste heat from another process or solar heat.
  • the depicted system 100 depicts a power plant capable of addressing the operational problems that prior known "open cycle” plants are known to encounter in practice owing to the simple fact an open cycle permits fouling from dust in the air, minerals in the makeup water, and noise pollution from the inlet and exhaust being excessively noisy.
  • an open cycle permits fouling from dust in the air, minerals in the makeup water, and noise pollution from the inlet and exhaust being excessively noisy.
  • the closed cycle of the described Sherbeck system generates water from the absorbed conditioned space humidity whereas open cycle systems require a water supply to input moisture or water into such open systems. In such a way, the Sherbeck system's closed cycle provides both a more economical and a more environmentally friendly implementation.
  • the depicted plant is a closed system for which cooling is accomplished with dry heat exchange coils to the air and optionally supplemented by external misting of the coils when operating in hot weather and implementations having high temperature ambient conditions.
  • heat may be rejected to water.
  • the heat to drive the plant may be taken directly from a hot gas stream, or the plant may alternatively be configured to run off of hot liquid, or vapor.
  • ejector 105 having Q e refrigeration load Heat Exchanger (HTX) 110 leading to evaporator 1 15 which in turn is connected with low pressure air (LP AIR) 120 and then turbine or expander 125 which connects with aforementioned alternator 101.
  • Evaporator 115 additionally is connected through e- Thermal Expansion Valve (TXV) 195 with condenser/cooler 190.
  • TXV e- Thermal Expansion Valve
  • Condenser/cooler 190 is depicted as outputting HP (High Pressure) Air Saturated 136 to dryer 135 which dries the air and outputs dry 130 air output to the turbine or expander 125.
  • HP High Pressure Air Saturated 136
  • dryer 135 which dries the air and outputs dry 130 air output to the turbine or expander 125.
  • weak solution 141 is depicted via the low grade heat driver Rankine cycle driving a Brayton cycle with liquid desiccant loop for power generation and refrigeration as depicted at element 145 which is connected with QIN 150 and then to QOUT 155 and then to Liquid desiccant cooler 160 and then back through strong solution 140 to dryer 135.
  • Second output from QIN 150 is depicted as vapor 165 leading to condenser QOUT 170 and in turn Boiler Feed Water Pump (BFWP) 175 which then connects back to
  • Condenser/cooler 190 and ejector 105 through the condenser/cooler 190 to boiler QIN 151 connection shown.
  • Condenser/Cooler 190 is additionally connected with ejector 105 by way of
  • the input to the closed loop system is heat, including waste and low grade heat and the output, as depicted, is rotational, shaft power, or electrical power.
  • FIG. 2 depicts the four sub-cycles 201 of a Sherbeck cycle in accordance with an embodiment of the invention.
  • waste heat 227 is input into the system beginning the steam Rankine cycle 226 on the left of the diagram.
  • shaft work 228 is input into the reverse Brayton cycle 231 and latent heat 229 is input into the desiccant solution cycle 232.
  • Cold dry air 237 proceeds from the reverse Brayton cycle 231 to the evaporative cooler 234 and dehumidified room air 238 proceeds from the desiccant solution cycle 232.
  • warm humid air 233 is returned into the reverse Brayton cycle 231 and cold water less than 20° Celsius (element 239) is provided as a second input into the cooling coil
  • warm and humid air 244 is then returned to the desiccant solution cycle 232 and the process continues.
  • the Sherbeck cycle utilizes four sub-cycles including the steam Rankine cycle 226, a reverse Brayton cycle 231, an evaporative cooling cycle (e.g., via evaporative cooler 234) and a desiccant solution cycle 232.
  • Figure 2 depicts the various relationships between the 4 sub-cycles in terms of their respective inter-relationships, inputs, outputs, and how they are utilized together to achieve cooling and dehumidification.
  • the Sherbeck cycle utilizes exhaust heat or low/middle grade heat to achieve air conditioning as an input. Such heat sources are very often considered waste heat 227 and are commonly released into the environment rather than being utilized to produce commercially viable workloads, such as air conditioning and dehumidification.
  • the Sherbeck cycle decouples sensible cooling and latent cooling thus leaving the cooling coil responsible for only sensible cooling loads while the desiccant solution cycle 232 is utilized to remove humidity (e.g., latent load cooling) from the air conditioned space 246.
  • the cooling coil may operate at higher temperatures within the Sherbeck cycle system when compared with conventional air conditioner systems and yet attain the same comfort levels (e.g., as measured by temperature and relative humidity).
  • the Sherbeck system therefore requires a lesser temperature difference between outdoor air and coolant in the cooling coil, which thus allows the reverse Brayton cycle 231 which is utilized to create the cooling effect to reach much higher efficiencies when compared with conventional systems.
  • Figure 3A depicts a waste heat driven steam Rankine cycle 302 in accordance with an embodiment of the invention.
  • a T-s diagram depicting multiple state points R5 to R2 to R3 to R4 which correspond to the chart provided at the bottom of Figure 3A which depicts in greater detail for each of the various state points 361 , enthalpy 362, entropy 363, pressure 364, and temperature 366.
  • the heat source is coming from exhaust heat (e.g., waste heat).
  • Steam is assumed to be heated up to 200°C.
  • condensation temperature is assumed to be 100°C. Therefore, the temperatures of points R4 and point R5 are 100°C.
  • quality of point R4 and R5 are assumed to be 1 and 0. Water 349 at point R5 will be pumped to point R2 with 90% pump isentropic efficiency. Steam at point R3 will expand to point R4 with 85% turbine isentropic efficiency.
  • equation 2 defines the isentropic efficiency of the steam turbine, as follows:
  • h r 4a is the enthalpy of point R4a, which is the turbine outlet state achieved by an equivalent isentropic expansion.
  • a steam Rankine cycle is not efficient at converting low grade heat to work because it excessively condenses out latent heat to ambient.
  • the Sherbeck cycle system exploits both the shaft work and the latent heat rejected by the steam Rankine cycle.
  • the shaft work is utilized to drive a reverse Brayton cycle, which produces cold air for sensible cooling.
  • the latent heat then regenerates a desiccant solution which provides dehumidification.
  • the steam Rankine cycle as a work producing block is an environmentally friendly altemative to organic Rankine cycles for which fluid leakage is an environmental concern further because it poses less working hazard than a sorption system with pressurized ammonia.
  • FIG. 3A On the right side of Figure 3A there is depicted a process diagram of the steam Rankine cycle for which there are depicted the air 347, water vapor 348, water 349, and desiccant solution 352 phases.
  • an auxiliary turbine 356 At the top left there is provided an auxiliary turbine 356 which receives water vapor 348 from the heat source 354 and pushes the water vapor 348 and air 347 into the solution cycle 358 (Q-in). Water 349 is then output from the HTX #2 condenser (Q-Out) 357 and input into pump #2 at element 353 thus completing the cycle.
  • FIG. 3B depicts a desiccant solution cycle 303 in accordance with an embodiment of the invention.
  • FIG. 369 there is depicted an exemplary cycle for indoor swimming pool air 369 originating from the air conditioned space 381 in which the SPA1 (swimming pool air) 372 is input into dryer #2 373 which outputs dry air SPA2 at element 374 and also outputs reject heat 376.
  • the key at the lower left depicts the various phases elements present within the cycle including air 347, water vapor 348, water 349, the desiccant solution 352.
  • the reject heat 376 proceeds to be cooled by a cold storage water cooling coil at element 368 which is then released into the air conditioning space 381.
  • the output dry air SPA2 at element 374 outputs desiccant solution 352 which continues to heat exchanger HTX #2 at element 378 where it is then looped back as reject heat 384 and returned to dryer #1 at element 382. In the middle there is the circulating air 383 which removes condensed fresh water 377 which is output from the cycle.
  • the equations 386, 387, 388, and 389 depicted on the right define the various details of the process.
  • Figure 3C depicts a reverse Brayton cycle 304 in accordance with an embodiment of the invention.
  • a reverse Brayton cycle includes both heat and mass recuperation to push external heat transfer to the extreme temperature ends of the cycle.
  • Gate valve 355 connects outdoor air to help balance any pressure differences in the reverse Brayton cycle after shutting off the system.
  • the reverse Brayton cycle in Sherbeck cycle systems utilize moist air as the refrigerant.
  • the moisture content changes throughout the cycle.
  • the cold, low pressure air from the turbine outlet is passed through evaporative media to increase the cooling capacity. Excess moisture is then removed at the high pressure side to keep the turbine inlet dry.
  • the compressed air is cooled via recuperation with the low pressure side in HTX#1 as shown at element 320. As shown here, HTX# 1 (element 320) assists dryer 397 by condensing out some of the moisture.
  • dryer 397 dehumidifies the air stream to 3% relative humidity and heats the air stream to a temperature of 46°C at point B8 from which the air then rejects heat to environment as shown at element 396. Additionally depicted is element 399 showing the water at operations B 12 and B 13 going to the evaporative cooler as well as the air at operation B9 headed to the evaporative cooler.
  • Equation 17 provides the COP of the reverse Brayton cycle as follows:
  • Figure 3D depicts an evaporative cooler process 305 in accordance with an embodiment of the invention.
  • the evaporative cooling process 305 depicts how an evaporative cooler is modeled on the psychometric chart depicted at element 391. Depicted by the chart psychometric chart 391, point Bl lies outside the moist air states because it represents a concurrent flow of moist air and liquid water, which becomes fully evaporated by point B2.
  • the purpose of the evaporative cooler is to add cooling capacity since the air coming from reverse Brayton cycle is dry and can absorb water vapor. Water flowing in the direct evaporative cooler will be cooled by both sensible cooling (heat transfer) and latent cooling (mass transfer). In practice, during operation of such an evaporative cooler, sensible cooling and latent cooling will happen simultaneously. However, in order to simplify the model, the process is separated into several steps. For instance, after air at B10 is introduced into the evaporative cooler, sprayed water is cooled down by cold air and the air is humidified and cooled to point Bl l . Second, in order to make air become saturated at point B2, more water is injected after point Bl l .
  • condensation temperature As condensation temperature is lowered, more shaft work will be delivered to the cooling cycle, but less latent heat will be provided for desiccant solution regeneration. Although reduction of condensation temperature down as far as environment temperature is possible, doing so may not yield practical results as the heat is needed to regenerate desiccant solution well above ambient temperature. Consequently, optimal performance suggests that condensation temperature should be no lower than 80°C or the efficiency of the desiccant regeneration process will be much lower.
  • condensation temperature plays an important role in influencing the steam Rankine cycle efficiency, it would be reasonable to set the temperature to 80°C or higher according to certain embodiments.
  • a pressure of 70kPa would be the theoretical optimal set point for B9 to maximize COP.
  • the optimal low pressure level decreases. If environment temperature exceeds 42°C, the ideal expansion pressure will be 40kPa.
  • Exemplary optimal set points for a Sherbeck cycle system may therefore be 80°C condensation temperature and 18.5°C cold water temperature.
  • the low pressure level at B9 may be set depending on ambient temperature such that (a) when environmental temperatures are in the range of 24°C-33°C then the pressure is set to be 70kPa, (b) when environmental temperatures are in the range of 34°C-37°C then the pressure is set at 60kPa, (c) when environmental temperatures are in the range of 37°C-42°C then pressure is set to 50kPa, and finally (d) when environmental temperatures are above 42°C then pressure is set to 40kPa.
  • Other pressures and temperature ranges may be utilized according to specific design considerations.
  • the temperature of superheated steam at R3 is assumed as 200°C, however, depending on the heat source, this could be different. If superheated steam temperature increases, the COP of Sherbeck cycle system will increase as well.
  • the Sherbeck cycle system decouples the sensible cooling and latent cooling, it can operate at various ratios of latent load fraction. Also because the desiccant cooling circuit bypasses most of the losses generated in the system (by the power and cooling cycles), the system may operate more efficiently for dehumidifi cation than for cooling. However, COP will increase with increasing latent cooling load percentage and vice versa, where COP is defined to treat both latent and sensible cooling as equally important.
  • Sherbeck cycle systems are especially useful where air dehumidification is much more important than air cooling.
  • Sherbeck cycle systems utilize air and water as working fluids, the system is extremely environmentally friendly when compared to known conventional systems.
  • Figure 4 depicts a Sherbeck cycle 400 in accordance with an embodiment of the invention.
  • the depicted Sherbeck cycle 400 produces refrigeration and produces shaft power via turbine 498 and alternator 499 as outputs.
  • the depicted Sherbeck cycle 400 additionally reduces noise pollution while utilizing a closed loop methodology.
  • waste heat from industrial processes are utilized as the heat input 401 into the depicted Sherbeck cycle 400 to produce refrigeration and shaft power.
  • the depicted Sherbeck cycle 400 utilizes a turbocharger having a completely self contained bearing system capable of operating above the first critical, the second critical, and optionally the third critical.
  • liquid desiccant of the air is located immediately preceding the turbine 498 entrance by which the air is cooled permitting greater quantities of refrigerant or water to be condensed and collected as a liquid rather than having to go through the desiccant loop.
  • coefficient of performance is proportional to the quantity of heat input 401 provided into the system. Therefore, in accordance with a particular embodiment, heat required to regenerate the desiccant is taken from the condensers 425. In such a way, heat energy is utilized at least twice, for instance, once from the heat input 401 and again as waste heat energy from the condensers 425, thus making the system operate with greater conversion efficiency.
  • Other heat re-generation sources internal to the system during operation may likewise be utilized but it is observed that a greatest quantity of such heat energy, other than the heat input 401, is provided from the condensing cooling action.
  • Turboexpanders for both cooling and energy recovery may likewise be utilized in conjunction with the described system.
  • the depicted Sherbeck cycle 400 negates the need to exhaust such waste heat or exhaust the working fluid while improving conversion efficiency.
  • the waste heat from power generation is used to drive a gas cycle turboexpansion refrigerator while allowing waste heat to be rejected to the atmosphere in an air to air heat exchanger.
  • the working fluid of the gas cycle e.g., moist air 420
  • the desiccant air dryer 450 thus producing dry air 455 for the turbine 498 with the water being extracted out by the dryer, after being separated to separating tank 415 from the desiccant solution.
  • waste process heat is utilized to generate a cold source without requiring the traditional infrastructure of compression refrigeration; further still, there is no loss of working fluids, still further, durability and steady state operation suitable for a central plant cooling are provided, and the system may be adapted to reject heat directly to the atmosphere rather than having to cycle through a source of fresh treated water.
  • the liquid desiccant air dryer is placed immediately before the entrance of the turbine which provides the advantage of condensing greater quantities of water out of the flow before entering the dryer.
  • a second temperature jog is added to the high pressure line at the bottom to show a temperature rise and pressure loss of the liquid desiccant dryer before the turbine entry.
  • a small temperature drop corresponding to the water injection after the evaporative cooler is also present and heat transfer from the high pressure air stream extends to the coldest part of the low pressure air stream after the water injection.
  • the liquid desiccant loop is used to increase efficiency still further by adding a second semipermeable membrane air dryer downstream of the turbine air dryer in the conditioned space which produces temperatures which are in a comfortable range and which may be maintained without the need for the cooling loop to reach the dew point to extract out the latent cooling load.
  • Raising the cooling loop temperature will increase the COP (coefficient of performance) still further. Additionally, temperatures in a comfortable range may also be maintained with a chilled water supply as high as about 70-F. Having the condensate from the high pressure air flow condensation in the cooler/dryer/condenser/liquid desiccant regenerator, and air-to-air heat exchanger drain into a fill-to-spill tank further allows the moisture taken from the conditioned space to be collected as a liquid which is advantageous as the liquid water collected will be directly potable so long as corrosion within the cycle is eliminated.
  • the collected water may be utilized to assist the cold sink by evaporative cooling.
  • a float valve to control water flow from the fill-to-spill tank to the evaporative cooler, allows a constant mass of water within the cycle regardless of the latent load.
  • the conditioned space air dryer is an array of vertical plates on a wall.
  • a delta T e.g. a temperature differential
  • the air temperature in the room and the liquid desiccant solution therefore drives an air flow over the dryer by buoyancy.
  • such a float valve may be integrated into an air handler.
  • passive cooling is achieved by use of a chilled ceiling, chilled beams, or valences without concern of condensation occurring. If the inside liquid desiccant dryer included heat transfer fluid passages, they will yield heat and humidity which is beneficial during the cold season. By providing year round comfort control the return on investment is improved thus shortening the payback period and in turn driving marketability.
  • the moisture content of air flow exiting the evaporative cooler is permitted.
  • evaporative coolers and cooling towers are designed to minimize excess water in the exiting air flow as this water is wasteful, and can be damaging.
  • some moisture exhaust may be desirable in certain use cases. Configurations may produce air at about 95% of saturation.
  • an alcohol/water mix is sprayed directly into the centrifugal compressor inlet of a turboprop engine to provide a power boost in hot weather.
  • Such a practice may be suitable for short durations depending on the turboprop design and configuration utilized.
  • cooling power of the air-to- air heat exchanger is improved and by lowering the compressor inlet temperature, efficiency is improved also. Because the evaporative cooler is a counter flow arrangement, water exits at a colder temperature than the air which will therefore extend the low temperature loop on the T-s diagram depicted at Figure 9.
  • Figure 5 is a flow diagram illustrating a method 500 for implementing a closed low grade heat driven Rankine cycle driving a reverse Brayton cycle using an ejector with a liquid desiccant loop to produce shaft power and refrigeration by adiabatic expansion and evaporation in accordance with described embodiments.
  • Some of the blocks and/or operations listed below are optional in accordance with certain embodiments. The numbering of the blocks presented is for the sake of clarity and is not intended to prescribe an order of operations in which the various blocks must occur. Additionally, operations from flow 500 may be utilized in a variety of combinations.
  • Method 500 converts input heat energy into output rotational shaft power as depicted at block 505.
  • operation receives the input heat energy at a vapor generator having the first fluid therein.
  • operation vaporizes the first fluid at the vapor generator to create high pressure vapor.
  • operation ejects the high pressure vapor through an ej ector to create a low pressure by drawing the first gas through a turbine.
  • At block 530 operation drives an alternator through Adiabatic expansion of the first gas in the turbine to output the rotational shaft power from the alternator.
  • operation condenses the first gas via condenser, wherein the first gas flows through a separator before cycling back into the turbine and further wherein the refrigerant flows returns to the boiler feedwater pump drawn by the low pressure through an expansion component and into an evaporator.
  • operation cycles the first gas which is saturated with the refrigerant from the condenser through a dryer via a sorbent loop to dry the first gas.
  • input heat energy is converted into output rotational shaft power, by way of a method or other means which include at least means for evaporating a refrigerant in a first gas; means for receiving the input heat energy at a vapor generator having the first fluid therein; means for vaporizing the first fluid at the vapor generator to create high pressure vapor; means for ejecting the high pressure vapor through an ejector to create a low pressure by drawing the first gas through a turbine; means for driving an alternator through Adiabatic expansion of the first gas in the turbine to output the rotational shaft power from the alternator; means for condensing the first gas via condenser, wherein the first gas flows through a separator before cycling back into the turbine and further wherein the refrigerant flows returns to the boiler feedwater pump drawn by the low pressure through an expansion component and into an evaporator; and means for cycling the first gas which is saturated with the refrigerant from the condenser through a dryer via
  • the first gas is air.
  • the refrigerant is water.
  • the refrigerant is a refrigerant mixture.
  • the refrigerant is an immiscible fluid.
  • the refrigerant is not water and produces sub-OC temperatures in an evaporator through one of water/ethanol or water/acetone refrigerant mixtures.
  • evaporating a refrigerant in a first gas includes using the gas to drive a turbine in a reverse Brayton cycle to evaporate the refrigerant in the first gas.
  • the vapor generator is a boiler.
  • the high pressure exists between a boiler feedwater pump and the ejector nozzle where the fluid is vaporized in the boiler.
  • the adiabatic expansion in the turbine cools the first gas.
  • further cooling of the first gas is attained by re-evaporating the refrigerant in the gas which is the drawn by the ejector through a load heat exchanger.
  • the expansion component comprises float valve.
  • the expansion component comprises thermostatic expansion valve to hold a fixed superheat at the load heat exchanger exit.
  • the expansion component comprises a thermoacoustic or a Hilsch tube expansion device to permit heat to be rejected from the cycle.
  • cycling the first gas through a dryer via a sorbent loop comprises spraying a weak solution of sorbent to dry the first gas and remove the refrigerant from the first gas.
  • a strong solution is produced from spraying the weak solution of sorbent to dry the first gas and remove the refrigerant from the first gas.
  • the method further includes pumping the strong solution into a generator where refrigerant vapor is released from the sorbent by heating.
  • the sorbent is a salt solution.
  • the sorbent is one of LiBr or calcium chloride.
  • the sorbent is an ionic fluid.
  • the method further includes cycling the strong solution through a second condenser the strong solution is liquefied and returned to the separator.
  • the method further includes cooling the weak solution and pumping the weak solution back to the dryer.
  • Figure 6 depicts an ejector refrigeration cycle which is heat driven in accordance with an embodiment of the invention.
  • the Sherbeck cycle air loop involves three pressures. First, Atmospheric (high) pressure where steam from the Rankine loop, mixed with saturated air from the cooling loop in the ejector are condensed and cooled. The heat is delivered to the liquid desiccant regenerator, rejected to the cold sink, and a heat exchange with air returning from the evaporative cooler takes place. Much of the remaining water in the air is removed by the desiccant loop before entry into the turbine. Second, a medium pressure at the compressor discharge/ejector inlet. Third, a low pressure between the turbine exit, and compressor inlet, where water in the cooling loop is evaporated, and heat is exchanged with air going to the liquid desiccant dryer.
  • Atmospheric (high) pressure where steam from the Rankine loop, mixed with saturated air from the cooling loop in the ejector are condensed and cooled. The heat is delivered to the liquid desiccant regenerator, rejected to the cold sink, and a heat exchange with air returning from the evaporative cooler takes place
  • FIG. 6 Specifically depicted at Figure 6 is state-space representation of ejector cycle with water as both motive fluid and refrigerant. Also indicated with dashed lines are the external flows, re-scaled to match on horizontal axis, thus showing the pinch points for heat transfer.
  • the generator transferring heat from HTF, 22- 23- 24- 25, to motive stream, 1 ->2- 3 - 4) has a pinch point where 24 heats point 2.
  • the diffuser efficiency is also a so-called isentropic efficiency, where 7' is an artificial state that would result from isentropic expansion from state 6, where: r/diffuser
  • Figure 7 depicts a Sherbeck cycle psychometric chart 700 in accordance with described embodiments. In particular, there are depicted points 1-4 at high pressure, point 8 at medium pressure, and points 5-7 at low pressure. Point 1 represented by element 710 is off the scale of the chart as depicted.
  • FIG. 8 depicts another Sherbeck cycle 800 in accordance with described embodiments.
  • the cooling load temperature can be raised while maintaining comfort conditions.
  • Using a fill to spill tank to feed the evaporative cooler 804 allows the collected condensed moisture from the air conditioned space to spill out of the cycle as depicted at element 828.
  • condensate 806 captured from the re-gen 802 phase through the air to air HTX 803 exits the cycle as a liquid at atmospheric pressure. Raising cooling loop temperatures further increases the coefficient of performance (COP).
  • COP coefficient of performance
  • Figure 9 depicts a T-s or temperature-entropy diagram of the reverse Brayton cycle within the Sherbeck cycle in accordance with described embodiments.
  • the liquid desiccant regenerator 920 at point 1 heading to cooler 921 at point 2 and the liquid desiccant dryer 938 at point 3 which via QA to A HTX proceeds to point 5 and on to evaporative cooler 904 at point 5.
  • Water injection 905 at point 6A results in 3 ⁇ super saturated 911 air at point 6B.
  • the compressor 919 taking point 7 at 21.5 KPA to the ej ector 922 of point 8 at 101 KPA.
  • a gas used to drive a turbine 125 in the reverse Brayton portion which may be air, or any other gas in which the refrigerant will evaporate
  • a refrigerant which may be water or may include refrigerant mixtures, and/or immiscible fluids
  • a desiccant which may be as simple as a salt solution such as LiBr, calcium chloride, or an ionic fluid.
  • the high pressure exists between the Boiler Feed Water Pump (BFWP) 175, and the ejector nozzle where that fluid is vaporized in the boiler.
  • BFWP Boiler Feed Water Pump
  • the high pressure vapor is used in the ejector 105 to create the system low pressure (LP AIR 120) by drawing the gas through the turbine 125.
  • LP AIR 120 system low pressure
  • Adiabatic expansion in the turbine 125 extracts work from the gas to drive an alternator 101 or other device with the resulting shaft power, and results in cooling of the gas.
  • Further cooling is produced by evaporating the refrigerant in the gas which is the drawn by the ejector 105 through the refrigeration load Heat Exchanger (HTX) 110.
  • HTX Heat Exchanger
  • Choice of a refrigerant other than water may produce temperatures in the evaporator below freezing.
  • water/ethanol, or water/acetone mixtures may be utilized to permit sub-OC temperatures in the evaporator 115, and add temperature glide to the condenser/cooler 190 to improve operational conditions.
  • the medium pressure is set by the condensing/gas cooling temperature. From the condenser/cooler 190, the flow enters a separator (dryer 135) from which the gas heads back to the turbine 125, and the refrigerant returns to the Boiler Feed Water Pump (BFWP) 175, and is drawn by the low pressure through an expansion device into the evaporator.
  • the expansion device may be a float valve, a thermostatic expansion valve, which holds a fixed superheat at the load heat exchanger exit, a thermoacoustic, or Hilsch tube expansion device which permits another location for heat to be rejected from the cycle, etc.
  • the cold refrigerant flow exiting the load Heat Exchanger (HTX) 110 could be used to pre-chill the liquid refrigerant before it enters the evaporator, or the dry air before it enters the turbine 125 to improve the cycles' efficiency.
  • HTX load Heat Exchanger
  • the cycle uses a gas, a refrigerant, and a desiccant to produce the shaft power as well as refrigeration from low grade heat that might be waste heat, or solar heat or other available sources.
  • FIG. 10 depicts yet another Sherbeck cycle 1000 in accordance with described embodiments.
  • the air conditioned space 1055 shown on the lower left is where a second dryer 1050 is added to the desiccant loop to take the latent load from the air conditioned space and in particular, condensed moisture from the air conditioned space' spills out of the cycle as depicted at H2O spill element 1035.
  • the mass of water in the cycle is held constant despite the humidity being removed from the space by adding a fill to spill 1034 provision to the air/water separator at the lower right side.
  • Air to air H2O HTX 1005 and solution to solution heat exchangers are introduced in this variant to create additional temperature differences from the left side of the diagram where refrigeration is produced, and the right side where the heat source 1010 is used to power the cycle.
  • a steam turbine 1094 is further depicted in this embodiment at the top right. Where the product of the steam turbine and the compressor efficiencies exceed those of the ejector, it may be preferential and economical to implement such a steam turbine.
  • the pressure ratio of the steam loop in the initially targeted is high enough that a multi-stage turbine may be desirable.
  • Use of an impulse turbine permits such a pressure ratio to be accomplished in a single rotor by having the flow reverse and go through the turbine blades two or more iterations in opposing directions. Such an approach additionally negates rotor thrust issues.
  • the cooler/condenser 1040 is depicted which is utilized to heat the desiccant loop (re)generator, where moisture 1025 is driven from the weak solution to create the strong solution 1030. This is possible because the solution regenerates at temperatures as low as 60C, while at ambient pressure, the steam in the boiler ejector 1045 discharge will condense at l OOC. The boiler ejector 1045 discharge may enter the
  • cooler/condenser/liquid desiccant regenerator at a higher temperature which may lead to crystallization in the regenerator, but which is addressed via a shut down delay to the solution pump such that any crystallization is dissolved after every operation.
  • cooler/condenser to drive the regenerator eliminates a separate use of the heat from the heat source and improves the cycle coefficient of performance (COP).
  • the rejection of heat to ambient in and/or between the two dryers (1050 and 1065) in the desiccant loop may be preferred depending on the particular implementation and use case.
  • FIGS 11A and 11B depict a complete Sherbeck cycle system 1100 in accordance with one embodiment of the invention.
  • an evaporative cooler is depicted at the upper left having a cooling load 1 150 in which incoming air at point B10 1 125 is introduced into the evaporative cooler 1 101 , sprayed water is cooled down by cold air and air is humidified and cooled to point Bi l l 130.
  • Point Bl 1 105 lies outside the moist air states because it represents a concurrent flow of moist air and liquid water, which becomes fully evaporated by point B2 1 180 via HTX # 1 at element 11 10.
  • the low pressure level at point B9 1 175 is set depending on ambient temperature for the system 1100. Higher cold water temperature in the evaporative cooler 1101 at point Elr 1135 results in a higher temperature at point B2 1 180 and less temperature difference between point B2 1180 and point B88 1196.
  • hb3 is the real enthalpy of state point B3 1195 and hb2 is the enthalpy of state point B2 1180, representing the compressor inlet 1190.
  • gate valve 1114 permitting outdoor air 1116 into the system 1100 to balance any pressure differences in the reverse Brayton cycle after shut off the system 1100.
  • point S9 1117 where water from the room and dryer #1 passes through water separator #1 1113 to point A2 1123 where pump #2 1118 (e.g., such as a circulating fan) pushes outdoor air at point AO 1119 through an extra air to air indirect evaporative cooling phase at point A3 1127 and releasing the air at point A4 1121 into the environment 1170.
  • Pump #2 1118 e.g., such as a circulating fan
  • Water from room and dryer #1 at element 1117 is additionally passed through point Al 1122 back to the evaporative cooler 1101 through point B12 1160 where the water is cooled before entering or returning to the evaporative cooler 1101 as depicted by element 1155.
  • Circle connectors (a) and (b) and (d) and (e) on the right side of Figure 11A connect with the corresponding circle connectors (a) and (b) and (d) and (e) on the left side of Figure 11B to form one continuous system 1100 which is split over the two images for the sake of clarity.
  • circle connector (a) leads to the auxiliary turbine 1172 where water vapor originating from heat source 1151 is pulled through point R3 1164 through the auxiliary turbine 1172 and pushed through point R4 1171 to heat exchanger HTX #2 1156 on the condenser side condensing the water vapor to water and pushing the water through point R5 1154 through pump #3 1153 and looped back into the heat source 1151 through point R2 1152.
  • the heat source 1151 is waste heat, low grade heat, or exhaust heat. Steam is assumed to be heated up to 200°C.
  • condensation temperature at HTX #2 1156 is assumed to be 100°C and temperatures of water vapor at point R4 1171 and therefore the water condensed at point R5 1154 is likewise assumed to be 100°C according to the depicted embodiment.
  • return air SPA 1 e.g., swimming pool air
  • air conditioning space 1191 is returned to dryer #2 11169 which receives desiccant solution S I 1163 from dryer #1 1167 returning dehumidified air from dryer #2 1169 as SPA2 1173 through heat exchanger HTX #3 1174 through the water cooling coil 1178 which cools the dehumidified air SPA2 by cold storage water in the water cooling coil 1178 before the air is then returned into the air conditioning space at element 1191.
  • desiccant solution S I 1163 from dryer #1 1167 returning dehumidified air from dryer #2 1169 as SPA2 1173 through heat exchanger HTX #3 1174 through the water cooling coil 1178 which cools the dehumidified air SPA2 by cold storage water in the water cooling coil 1178 before the air is then returned into the air conditioning space at element 1191.
  • a system to dehumidify air and cool air using an input heat source includes at least: an auxiliary turbine to receive input steam from a heat source, in which the input steam is to expand within the auxiliary turbine to output shaft power and release low pressure air cooled to a first temperature from an outlet of the auxiliary turbine; a heat exchanger to pass the low pressure air from the outlet of the auxiliary turbine through an evaporative media with moist air in an air to air indirect evaporative cooling process to further cool the low pressure air to a second temperature; a dryer to dehumidify the low pressure air via a desiccant solution in the dryer; an evaporative cooler to further cool the low pressure air to a third temperature via absorption of water vapor within the evaporative cooler, in which the cool low pressure air is to be sprayed with water within the evaporative cooler to humidify the low pressure air and to cool the low pressure air to the third temperature; and a cool
  • the auxiliary turbine to receive the steam input from the heat source is to implement a steam Rankine cycle for the system.
  • the heat exchanger to pass the low pressure air from the outlet of the auxiliary turbine through the evaporative media is to implement a reverse Brayton cycle for the system.
  • the system further includes: a gate valve to connect outdoor air with the auxiliary turbine to balance pressure differences between the reverse Brayton cycle implemented by the auxiliary turbine and the outdoor air after shutting off the system.
  • the auxiliary turbine is to further output shaft power; in which the shaft power is an input to the reverse Brayton cycle for the system; and in which the shaft power is to drive the low pressure air from through the evaporative media of the heat exchanger to produce the cool air as an output from the system.
  • the dryer to dehumidify the low pressure air via a desiccant solution is to implement desiccant solution cycle for the system.
  • the auxiliary turbine is to further reject latent heat; and in which the rejected latent heat from the auxiliary turbine is used to recharge the desiccant solution.
  • the evaporative cooler is to implement an evaporative cooling cycle for the system.
  • the system further includes: a cooling coil, in which the cool air released from the system via the cool air output passes through the cooling coil prior to system egress; and in which the cooling coil operates at a temperature above dew point.
  • the cooling coil reduces a temperature of the cool air to produce the cool air from the system and further in which the desiccant solution is to dehumidify the air; and in which the dehumidified and cooled air is released into an air conditioned space via the cool air output of the system.
  • a Sherbeck cycle system which utilizes ocean water as a heat sink to extract heat from the system or into which heat may be rejected by the Sherbeck cycle system.
  • river or lake water or another body of water may be utilized.
  • MW multi-megawatt
  • a highest surface temperature for such ocean water may be 83 °F and even cooler several meters deeper.
  • the Sherbeck cycle system may be utilized to produce both desalinized water and refrigeration from low grade or waste heat.
  • such a variation of the Sherbeck cycle system utilizes a Rankine cycle to drive the reverse-Brayton cycle, while eliminating the desiccant loop and evaporative cooling components.
  • the condenser heat rejection would instead heat sea water under a vacuum to produce desalinized water as an output from the Sherbeck cycle system.
  • desalinization of ocean water occurs in an elevated position such that a column of brine returning to the ocean (as a bi-product of the desalinization process) produces the necessary vacuum and thus reduces the requisite work by the pump needed to bring the source sea water to a desalinization chamber.
  • water may be vaporized in the vacuum and condense on a plate cooled by sea water to produce the desalinized fresh water.
  • the brine then flows through a counter-flow heat exchanger to preheat the source sea water.
  • Such a configuration makes both the reverse-Brayton cycle and the Rankine cycle closed such that the working fluid choices may be selected from among a very wide array of choices. For instance, super-critical carbon dioxide or helium may be utilized in the reverse Brayton cycle.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Drying Of Gases (AREA)

Abstract

Selon des modes de réalisation, l'invention concerne des procédés et des systèmes pour mettre en œuvre un cycle de Rankine fermé entraîné par chaleur de basse qualité entraînant un cycle de Brayton inverse à l'aide d'un éjecteur avec une boucle de déshydratant liquide pour produire une réfrigération et une puissance d'axe par évaporation et dilatation adiabatique (le cycle de Sherbeck). Par exemple, dans un mode de réalisation, un tel système comprend des moyens pour convertir l'énergie thermique d'entrée en puissance d'axe de rotation de sortie, lesdits moyens comprenant au moins des moyens pour évaporer un réfrigérant en un premier gaz; des moyens pour recevoir l'énergie thermique d'entrée au niveau d'un générateur de vapeur ayant le premier fluide à l'intérieur de ce dernier; des moyens pour vaporiser le premier fluide au niveau du générateur de vapeur pour créer une vapeur à haute pression; des moyens pour éjecter la vapeur à haute pression à travers un éjecteur pour créer une basse pression en aspirant le premier gaz à travers une turbine; des moyens pour entraîner un alternateur par dilatation adiabatique du premier gaz dans la turbine pour délivrer en sortie la puissance d'axe de rotation depuis l'alternateur; des moyens pour condenser le premier gaz par l'intermédiaire d'un condenseur, le premier gaz circulant à travers un séparateur avant cyclage en retour dans la turbine et, en outre, les flux de réfrigérant revenant vers la pompe d'eau d'alimentation de chaudière aspirés par la basse pression à travers un élément de dilatation et dans un évaporateur; et des moyens pour faire cycler le premier gaz qui est saturé avec le réfrigérant provenant du condenseur à travers un sécheur par l'intermédiaire d'une boucle de sorbant pour sécher le premier gaz. La présente invention concerne d'autres modes de réalisation associés.
PCT/US2016/068342 2015-12-22 2016-12-22 Systèmes, procédés et appareils pour mettre en œuvre un cycle fermé entrainé par chaleur de basse qualité pour produire une réfrigération et une puissance d'axe WO2017112875A1 (fr)

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CN109296511A (zh) * 2018-11-09 2019-02-01 中国科学技术大学 一种超临界二氧化碳布雷顿循环塔式太阳能热发电系统
CN112523826A (zh) * 2020-11-25 2021-03-19 江苏科技大学 多模式船舶主机余热利用系统及运行方法
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US11029064B2 (en) 2018-04-09 2021-06-08 Arizona Board Of Regents On Behalf Of Arizona State University Solar adsorption heat pump and evacuated tube adsorption heat pump and desalination system
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CN107830657A (zh) * 2017-09-14 2018-03-23 中国科学院理化技术研究所 变温冷却吸收器以及吸收式循环系统
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CN112523826A (zh) * 2020-11-25 2021-03-19 江苏科技大学 多模式船舶主机余热利用系统及运行方法
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CN113339082A (zh) * 2021-06-30 2021-09-03 上海康恒环境股份有限公司 一种低温冷能回收发电系统

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