WO2007146050A2 - Système et procédé de chauffage et de refroidissement à énergie thermique bio-renouvelable - Google Patents

Système et procédé de chauffage et de refroidissement à énergie thermique bio-renouvelable Download PDF

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Publication number
WO2007146050A2
WO2007146050A2 PCT/US2007/013397 US2007013397W WO2007146050A2 WO 2007146050 A2 WO2007146050 A2 WO 2007146050A2 US 2007013397 W US2007013397 W US 2007013397W WO 2007146050 A2 WO2007146050 A2 WO 2007146050A2
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WIPO (PCT)
Prior art keywords
heat
thermal energy
heating
water
source
Prior art date
Application number
PCT/US2007/013397
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English (en)
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WO2007146050A3 (fr
Inventor
Kevin E. Flammang
Karl J. Seggerman
Gene Veltkamp
Original Assignee
Waters Hot, Inc.
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Waters Hot, Inc. filed Critical Waters Hot, Inc.
Priority to MX2008015586A priority Critical patent/MX2008015586A/es
Priority to BRPI0712184-9A priority patent/BRPI0712184A2/pt
Priority to CA002659584A priority patent/CA2659584A1/fr
Priority to AU2007258621A priority patent/AU2007258621A1/en
Priority to EP07809376A priority patent/EP2024693A2/fr
Priority to JP2009514371A priority patent/JP2009540258A/ja
Publication of WO2007146050A2 publication Critical patent/WO2007146050A2/fr
Publication of WO2007146050A3 publication Critical patent/WO2007146050A3/fr
Priority to IL195705A priority patent/IL195705A0/en

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B29/00—Combined heating and refrigeration systems, e.g. operating alternately or simultaneously
    • F25B29/003—Combined heating and refrigeration systems, e.g. operating alternately or simultaneously of the compression type system
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B27/00—Machines, plants or systems, using particular sources of energy
    • F25B27/02—Machines, plants or systems, using particular sources of energy using waste heat, e.g. from internal-combustion engines
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B29/00—Combined heating and refrigeration systems, e.g. operating alternately or simultaneously
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2339/00—Details of evaporators; Details of condensers
    • F25B2339/04—Details of condensers
    • F25B2339/047—Water-cooled condensers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2400/00—General features or devices for refrigeration machines, plants or systems, combined heating and refrigeration systems or heat-pump systems, i.e. not limited to a particular subgroup of F25B
    • F25B2400/24—Storage receiver heat
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2600/00—Control issues
    • F25B2600/02—Compressor control
    • F25B2600/027—Compressor control by controlling pressure
    • F25B2600/0271—Compressor control by controlling pressure the discharge pressure
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B40/00—Subcoolers, desuperheaters or superheaters
    • F25B40/02—Subcoolers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B5/00—Compression machines, plants or systems, with several evaporator circuits, e.g. for varying refrigerating capacity
    • F25B5/02—Compression machines, plants or systems, with several evaporator circuits, e.g. for varying refrigerating capacity arranged in parallel
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B6/00—Compression machines, plants or systems, with several condenser circuits
    • F25B6/02—Compression machines, plants or systems, with several condenser circuits arranged in parallel
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02A—TECHNOLOGIES FOR ADAPTATION TO CLIMATE CHANGE
    • Y02A30/00—Adapting or protecting infrastructure or their operation
    • Y02A30/27—Relating to heating, ventilation or air conditioning [HVAC] technologies
    • Y02A30/274—Relating to heating, ventilation or air conditioning [HVAC] technologies using waste energy, e.g. from internal combustion engine

Definitions

  • U.S. Patent 7,040,108 described a method of recovering thermal energy from various environments and utilizing it in a process or storing it for later use.
  • the basic configuration in the '108 patent utilized a single evaporator and water cooled condenser with a compressor, expansion device, receiver, circulating pump and hot storage tank.
  • This patent emphasized the heating capability of the refrigeration process and extended the use of refrigeration technology towards the maximum utilization of the refrigeration cycle for its heating affects within a given application.
  • the refrigeration cycle was defined as a process involving a compressor, heat exchanger (condenser), expansion device, and evaporator.
  • Thermal energy was to be collected in the evaporator from air or from liquids or slurries and was generally to be placed into a liquid stream or storage device where it could also be used to heat a space or process.
  • the '108 system operated in a single mode, that is, reclamation.
  • the present invention extends the teaching of U.S. Patent 7,040,108 to include a formula or methodology for application of the refrigeration process to further enhance or optimize the utilization and control of refrigeration for the transformation of thermal energy available in one environment/media to another environment/media.
  • This is not the simple transfer of thermal energy from location to location but the efficient transformation of thermal energy from one condition to one or more conditions desirable for a given application.
  • This is accomplished through the balancing of the environmental variables with the properties of the refrigerant and the capabilities of the compressor. For example, in a meat processing facility, chillers are used to maintain workplace temperatures that are suitable for safe processing of the meat and boilers are used to heat kill process water and wash water.
  • the system of the present invention will provide the chilling while also providing a fixed temperature of liquid refrigerant to the expansion device and generating heated water for the kill process and the wash down.
  • the fixed liquid refrigerant temperature helps to optimize the performance of the compressor where most chiller condensers are currently exposed to the variability of the ambient air temperature which will cause compressor performance to vary off of the optimal condition.
  • the combination of compressor configuration, refrigerant, condenser configuration, expansion device/configuration, and evaporator configuration are driven by the requirements of the application and the nature of the refrigerant selected.
  • One goal of the system configuration is to achieve the most desirable balance of refrigerant and lubricant . conditions at the compressor while optimally utilizing thermal energy sources and thermal energy sinks available in the application.
  • One aspect of the present invention is the utilization of multiple evaporators and multiple condensers tied to a single compressor so as to increase the utilization of waste heat.
  • refrigerant heat is split for multiple uses.
  • the heat can be used for generating water, liquid or steam that is hotter than the condensing temperature of the refrigerant.
  • Producing steam represents use of the hot path to produce a phase change on the environment side of the refrigeration process.
  • a circulating loop with a water tank, pump and a condenser/heat exchanger provides control to the head pressure, so as to provide control and storage of higher temperature fluid, and to control the s ⁇ bcooling temperature for the improvement of the evaporator heat collection capacity, and to uniquely improve compressor efficiency.
  • the present invention uses water or a process stream to do this subcooling, rather than the refrigerant. This improves performance by collecting additional useful heat in the process stream through the subcooling of the refrigerant, as well as boosting the heat collection efficiency of the evaporator.
  • a circulating loop provides the basis for control of subcooling conditions to maintain higher compressor efficiency.
  • Another aspect of the present invention relates to desuperheating, which is known in the prior art, but only for the purpose of extracting the heat available from the superheat in the high temperature refrigerant vapor to heat water, while the remainder of the heat is rejected.
  • the present invention utilizes the full heat path towards heating a liquid prior to allowing rejection or switching to a heating application from a secondary priority, which is unique, and specifically not in conjunction with a circulating and storage loop used for process control.
  • This invention utilizes the full heat path as a priority and utilizes the desuperheating segment to produce and/or store water or fluid at temperatures above the condensing temperature of the refrigerant before allowing rejection or lower priority use.
  • Splitting the refrigerant hot side for various uses or controls significantly advances energy utilization beyond the prior art, which focused on rejection of the refrigeration heat.
  • a further aspect of the present invention is the splitting of the cold side of the refrigeration process, in conjunction with splitting of the hot side.
  • Evaporators in series or in parallel provide certain challenges, such as control of pressure in the suction line when two parallel evaporators operate at different temperatures and pressures.
  • Evaporators in series are a challenge to supply cooling at temperatures that are suitable for both environments, since the outlet temperature drives the control of the temperature of the refrigerant in all evaporators.
  • the system has the ability to heat potable water, cool interior space areas, use the hot water for heating interior space areas, recycle thermal energy by cooling one area while heating a second area, and save significant amounts of energy while completing these tasks.
  • a three-way reclaim valve is used to switch between the water-cooled condenser and the external condenser. This valve along with a check valve draws the refrigerant out of the external condenser and back into the system and keep the refrigerant from pooling in the external condenser. This allowed the system to provide heating, cooling and water heating.
  • the ability to control the condensing temperature at the temperature of the water tank via the circulation system is a unique characteristic.
  • the use of water for control, while also using the heat for useful heating, is unique.
  • the temperature of the water in the tank sets the head pressure of the compressor (i.e. corresponding to the condensing temperature of the refrigerant).
  • the limitation of the single condenser is overcome with a system that used two condensers in series each with its own tank and circulating system. This allows the first condenser to absorb all of the energy it could before the second heat exchanger begins to absorb energy. As the first heat exchanger system reaches the maximum condensing temperature, the majority of the heat is being captured by the second heat exchanger. As the system continues to operate, the water in the first circulation loop becomes hotter than the condensing temperature and the refrigerant entering the second heat exchanger is now accepting some superheated vapor refrigerant. The temperature of the first loop is above the condensing temperature of the refrigerant. This allows the system to heat water to over 200F in a batch mode operation.
  • cold water is introduced at the inlet of the circulating pump of the second circulating loop to allow the system to operate at a condensing temperature attributable to the mixture temperature of the hot water in the tank and the cold water entering the system.
  • This allows the system, to operate at lower head pressures while generating higher temperatures.
  • a reciprocating compressor operating on R22 can operate in continuous flow mode at temperatures as high as 130F without exceeding acceptable head pressures. This would be the result whether the system had one or two condensers. Applicants call the phenomenon tempering.
  • the same flow strategy is also applied to the hot water entering the first circulating loop. If the hot water is introduced at the suction of the circulating pump, the first condenser sees a mixture temperature that is lower than the tank temperature. Thus the system can absorb more heat at a given condition in the first condenser due to the greater temperature differential.
  • the first circulating loop controls the head pressure of the compressor, thereby increasing compressor efficiency.
  • the system performs better when the first condenser circulating loop is at or below the maximum condensing temperature of the refrigerant in the system — which for the given system was around 125F ⁇ and the second circulating loop is still relatively cool.
  • the second loop is removing additional heat and sub-cooling the liquid refrigerant.
  • the second circulating loop controls refrigerant subcooling, which also improves efficiency of the compressor. Subcooling provides two benefits:
  • the system gains the heat of subcooling for useful heating of the water. 2.
  • the refrigerant is expanded in the TX valve there are fewer flash gas losses (i.e. there is more liquid refrigerant to boil in the mixture inside of the evaporator and the heat transfer into the evaporator can be increased).
  • a third circulating loop may be provided for controlling desuperheating.
  • a second use for the dual condenser mode operation is to provide subcooling to increase the capacity of the system. It then follows that a third condenser can be used to provide both the ability to heat liquid to higher temperatures and subcool the refrigerant for the same system, yielding improved system performance.
  • thermodynamic formula inputs bio energy in the form of ambient air and recycled energy balanced on the capacity of the refrigerant and the compressor by first applying the energy into the application and rejecting the remaining energy in order to balance on the capacity of the refrigerant and compressor to all new levels.
  • thermal energy is defined as thermal energy that is available and exists naturally or has been released to an environment by an exothermic process.
  • Figure l is a schematic drawing of a basic prior art heating, cooling and hot water configuration according to the '108 patent.
  • Figure 2 is a schematic drawing of another embodiment of a prior art basic heating, cooling and hot water configuration according to the '108 patent.
  • Figure 3 is a schematic drawing of an embodiment of a basic heating, cooling and hot water configuration according to the present invention.
  • Figure 4 is a schematic view of an embodiment of the present invention showing heating, cooling and hot water utilizing multiple heat sinks.
  • FIGS. 5 A and 5B are schematic drawings showing alternative embodiments of a heating, cooling and hot water system having a warm water heat sink according to the present invention.
  • Figure 6 is a schematic drawing of another embodiment of a heating, cooling and hot water system having thermal loops and thermal storage according to the present invention.
  • Figure 7 is a schematic drawing of yet another embodiment of a heating, cooling and hot water system with mixed superheat cogeneration and rejection according to the present invention.
  • Figure 8 is a schematic drawing of still another embodiment of a heating, cooling and hot water system utilizing superheated liquid according to the present invention.
  • Figures 9 and 10 are schematic drawings of further embodiments of a heating, cooling and hot water system with subcooled liquid according to the present invention.
  • Figure 11 is a schematic drawing of another embodiment of a heating, cooling and hot water system with superheated heated liquid and supercooling according to the present invention.
  • Applicants have developed a universal formula necessary for balancing the co- generation of heat and cold within the refrigeration cycle with the constraints of two (or more) environments to be affected or controlled by the refrigeration process.
  • the variables must be balanced relative to the requirements of a given application of the system.
  • the first consideration is the choice of a refrigerant that has physical properties that will allow evaporation and condensation at temperatures that meet the demands of the application within the compression ratio and operating temperature limitations of available compressors and compressor oils.
  • refrigerant characteristics There are many materials and mixtures of materials having refrigerant characteristics.
  • new refrigerants will be selected or created to harness the efficiencies of the refrigeration cycle. Once a suitable refrigerant is selected, the formula can be applied along with the appropriate engineering principles to select or design the refrigeration system components that will properly balance the refrigeration cycle and withstand the rigors of the application.
  • equation 1 can be written as follows: (2) Evaporator energy collected — Evaporator side piping losses and heat gain +
  • Compressor work Condenser energy rejected — Condenser side piping and heat losses.
  • Compressor work Electricity consumed — Compressor and motor losses.
  • the formulae provides the basis for designing the system to match the environmental requirements with the refrigeration system requirements and optimize operating efficiency for simultaneously utilizing both the heating and cooling sides of the refrigeration cycle.
  • the goal of prior art systems was generally to maximize performance while satisfying either the heating or the cooling side.
  • Rejection systems have their place since they provide value to a process that pays for itself through product protection or production.
  • rejection systems such as chillers and freezers exist along side of boilers or furnaces which provide space and process heating based on combustion. These applications are candidates for conversion to reclamation or cogeneration refrigeration.
  • the refrigeration system In reclamation, the refrigeration system is often designed or optimized for utilization of one side of the refrigeration cycle while the other side is utilized as much as possible, but not necessarily all of the time or to the fullest extent possible.
  • the time dependent nature of many processes and the change of seasons is accommodated by the present invention wherein the refrigeration process is designed with additional flexibility to allow it to be utilized more efficiently and to a greater extent within a given application, including the need for multiple evaporators and multiple condensers to meet the priorities and time dependent requirements of the application.
  • a reclamation application may include periods of operation where priorities require rejection and may at times operate in cogeneration mode (discussed below). For example, Applicants' system installed in a home will operate in cogeneration mode when heating potable water while providing comfort cooling.
  • cogeneration When both the cooling and the heating side of the refrigeration cycle are fully utilized within a process, the application is called cogeneration.
  • an example of cogeneration is when a refrigeration system is used to provide comfort cooling while heating potable water. This effective utilization of the resource can be extended in a housing or hotel application if the same system can be used to heat a swimming pool and/or hot tub.
  • housing applications are rarely pure cogeneration applications. Pure cogeneration applications will mostly be found in agricultural, commercial and industrial applications where both cooling and heating are used to produce a product.
  • heat rejected from the cooked mash on its way to fermentation or from the fermentation process itself may be collected and used to heat the cook water or to heat the condensate returns for the boiler, hi the future, advances in refrigerants and refrigeration equipment may allow refrigeration systems to operate at temperatures that will allow refrigeration systems to displace the boiler.
  • Power plants, bio-diesel plants, chemical and petroleum refineries, commercial laundry/dry cleaners and a host of other energy intensive process oriented industries provide opportunities for cogeneration with a refrigeration system.
  • the goal is to maximize utilization of a balanced refrigeration cycle in a configuration that will minimize energy consumption and maximize efficiency and value to the application.
  • the systems are able to utilize the optimal combination of rejection, reclamation, and cogeneration as driven by the requirements and limitations imposed by the application.
  • the systems are capable of utilizing all three classes of operation within the same installation.
  • the bio-renewable reverse thermal energy nature of the system Historically the refrigeration process has been thought of as a simple transferring of energy from one location to another at the expense of electricity to operate the compressor.
  • the present invention endeavors not to simply transfer thermal energy, but through controls and system design, to transform thermal energy relative to its most desirable condition in a specific application given the constraints and capabilities of the refrigerant, compressor oil and the equipment. This is evident for example in the ethanol process described previously as an example of cogeneration.
  • the fermentation process requires a fixed 95°F while the cooked mash is held at 180 0 F. Fermentation gives off heat as the bacteria metabolize sugar into alcohol.
  • the mash is maintained (excess heat is collected) by the system and transformed into 130 0 F to 180 0 F water depending on the design of the refrigeration process.
  • the invention is capable of transforming electricity from any source into thermal "bio-energy" through reuse of thermal energy that would historically have been wasted to the environment and through reduction of toxic emissions associated with conventional combustion based heating systems.
  • the cook water is heated using a natural gas, coal, or biomass fired boiler. The excess heat in the cooked mash must be removed before it can be prepared for the fermentation process.
  • the thermal energy reclaimed by the new, inventive system is bio-energy.
  • a bio-energy system also exists when the energy that is reclaimed is derived from living organisms (such as in animal confinements, alcohol producing bacteria or incubating eggs). The system will inherently displace carbon dioxide (CO 2 ), carbon monoxide (CO), and nitrogen oxide (NO x ) emissions from all carbon based combustion processes and it will displace sulfur dioxide, mercury and ash emissions from oil, coal, solid waste or biomass combustion.
  • the renewable nature of this bio-energy can be derived by comparing the efficiency of the system with the efficiency of thermal power plants that generate the electricity for the application site.
  • Thermal plants include fossil fuel fired plants, nuclear plants, biomass fired plants, solar thermal plants and geothermal plants. AU of these types of generation emit significant amounts of waste heat into the environment, and the combustion based systems produce large quantities of combustion products that contribute to air and water • pollution.
  • the efficiency of thermal generating plants is characterized by the heat rate which is defined as the Btu input of fuel (or thermal energy) per kWh of electricity output.
  • the system operation in reclamation or rejection mode can similarly be characterized as the Btu of heat output per kWh of electricity input (the reverse thermal characteristic). If the system performance (Btu output/kWh input) is greater than the average heat rate (Btu input/kWh output) of the thermal electrical generating system, then the ratio of the two represents the renewable contribution of the system operation.
  • Applicants' system in a reclamation or cogeneration scenario will typically operate in the range of 11260 Btu/kWh to 13650Btu/kWh, and new advances are expected to increase the upper limit. As the reverse heat rate increases, the overall bio-renewable impact of the system will increase proportionally.
  • Non-thermal renewable energy sources have little if any airborne or thermal emissions and include technologies like wind, wave, hydro and solar photo- voltaic power.
  • the impact of non-thermal renewable generation on the Applicants' system renewable contribution will be proportional to the fraction of the total mix of generation produced from non-thermal sources.
  • the contribution of the Applicants' reverse thermal process and system relative to a non-thermal electricity source is better described based on the coefficient of performance (COP) or Btu of heat output per Btu of electricity used by the Applicants 1 system.
  • the units operating in reclamation and cogeneration mode are generally capable of operating at a COP of 3.3 or greater.
  • This level of COP is also possible in rejection mode, however the temperature of the heat source such as outdoor air on a very cold winter day during the heating season when the system is running in rejection mode can degrade the COP to levels as low as 1.0.
  • the system is operating in reclamation mode at a COP between 3.3 and 4.0.
  • the unit in reclamation mode will be generating 4 Btu of thermal energy for a process for every 1 Btu of electricity consumed.
  • Applicants' system multiplies the thermal capacity of electricity generated from non- thermal sources by a ratio equivalent to the COP.
  • renewable energy contribution is derived according to the following formula:
  • RTHR the reverse thermal heat rate of the system, Btu heat output / kWh electricity input
  • THPHR the heat rate of thermal generating plants, Btu heat input / kWh electricity output
  • REFTH Fraction of generation mix provided by thermal plants
  • REFNTH Fraction of generation mix provided by non-thermal generation systems
  • CompEff conversion efficiency of the thermal energy system that the system competes with Btu heat output / Btu of fuel fired. (2) Thermal energy at efficiencies greater than 100% when the efficiencies of the system reclamation are considered in combination with the efficiency of thermal generating plants.
  • a two pipe heating and cooling system in a hotel, hospital, or other commercial facility can be retrofit to include water source heat pumps in each unit and Applicants' system that will operate between the boiler and the chiller to significantly reduce the rejection mode operation of the chiller and the combustion of the boiler.
  • the Applicants' system will use cogeneration to take excess heat in the loop and apply it to heating potable water or the swimming pool and hot tub. If the loop needs additional heat, the system will use reclamation to take waste heat from the continuous exhaust system, waste water or other heat sources in the facility to provide the needed heating.
  • the Applicants' system possesses a unique market potential in a broad range of applications, some of which are described in the following sections.
  • Applicants' system provides flexibility to utilize rejection, reclamation and cogeneration in an optimal manner to maximize energy savings and emissions reductions for a wide array of applications. Claims for specific applications are listed at the end of this patent description. Applicants' system can provide residual benefits such as reduction in humidity or reduction in water usage in some applications that can be as valuable as the energy savings and emissions reduction benefits.
  • the number and type of condensers is determined by the number and type of required heating and cooling demands of the application.
  • the number of evaporators and condensers associated with a given unit is also driven by the economics of the installation and the timing of the available heat sources and the timing of the heating and cooling demands.
  • heat resources and heating and cooling demand do not occur simultaneously, it often becomes necessary to consider thermal storage as a method of retaining heat or cool for later utilization. In some instances the cooling demand consistently exceeds the heating demand in which case storage capacity for heat can be reduced by utilizing a higher storage temperature.
  • Figures 1 and 2 demonstrate basic configurations of the "108 patent.
  • Figure 2 is similar to Figure 1, and adds the concept of using a heat exchanger and circulating pump to remove heat from the storage tank for a purpose such as heating a space or heating a second stream.
  • Figures 1 and 2 are practical configurations for applications where there is a need for heating based on heat collected from a single ambient source or stream. These configurations were however inadequate to provide year-round heating and cooling for a home, for example, since the heat source changes from inside of the home during the comfort cooling season to the outside for the heating season.
  • Figure 3 demonstrates the use of the three-way reclaim valve and the reclaim check valve to switch between the water cooled condenser and the air cooled condenser. Also illustrated is the addition of 2 two-way solenoid valves used to supply liquid refrigerant to two evaporators labeled "A-Coil Evaporator" and "Evaporator". Multiple two-way valves or three-way valves may be used interchangeably for switching between multiple condenser paths or switching between multiple evaporator paths as the application requires.
  • This configuration provides the basic components necessary to provide heating and comfort cooling to any facility (home, office, warehouse, factory, etc.) while also heating the potable water.
  • the ability to cogenerate by heating potable water while providing comfort cooling provides a significant advantage. If the outdoor evaporator can be located where it can use reclamation from heated streams leaving the facility, then the overall performance of the system can be further improved during the heating season, and while heating water when there is no cooling demand.
  • an application presents an opportunity to provide useful heating of multiple locations or processes such as the heating of a space and the heating of a large heat sink such as a swimming pool or a process stream.
  • U.S. Patent 7,040,108 disclosed the use of one loop for the heating of a space but did not disclose the multi-circuit possibility.
  • Figure 4 demonstrates the use of more than one heating circuit tied to the hot water tank to allow the system to provide heating to multiple demands at or below the controlled temperature of the hot water tank.
  • the desired temperature of the heat sink must be at or below the operating temperature of the Applicants' system while operating on a given refrigerant to allow heat transfer into the heat sink.
  • this configuration allows the system to reduce, if not eliminate, rejection mode operation and maximize cogeneration during comfort cooling operation or a continuous process cooling operation.
  • a second heating circuit is used instead of a second water cooled condenser when the heat demand is at a temperature significantly below the typical refrigerant condensing temperature (hot tank setpoint) of the system. This will allow the Applicants' system to control refrigeration system operation and in some instances avoid excessive frost formation on the evaporator(s) and suction piping.
  • Each heating loop will have a solenoid valve to control flow of water through the loop based on application demand and priority.
  • a flow control valve may also be placed in each loop to allow the heat transfer out of the tank to be limited to the heat entering the tank from the water cooled condenser.
  • Each loop may have its own circulating pump as shown in Figure 4 or a single pump may be used to supply circulation for all loops.
  • FIG 5 A slight variation of the multiple heat sink concept advanced in Figure 4 is demonstrated in Figure 5.
  • warm water is supplied to the cold supply of plumbing fixtures throughout a facility except possibly for water used for drinking, ice making and food preparation purposes.
  • the intent is to provide additional heating load during the cooling season to help avoid the need for rejection mode operation as with an air cooled condenser.
  • the system would not be used during the heating season unless it provides value to some process within an application.
  • the fact that the cold water supply is heated will reduce the demand on the hot water since the mixing at the point of use will be biased more towards the cold than usual to arrive at the same level of comfort for the user.
  • Cool water supply with mixing valve There are two configurations presented in Figure 5, cool water supply with mixing valve and cool water supply with independent tank. Both options reduce energy consumption by reducing the need for rejection mode operation during a cooling process and can be used in specific applications where warm water is desirable.
  • the Hot Control valve is opened and Cool Control valve is closed only when the hot water tank is satisfied and the system is calling for cooling. As soon as the hot tank calls for heating, the valves will return to their de-energized positions (the Hot Control valve will close and the Cool Control valve will open).
  • the mixing valve configuration allows warm water to be generated on demand helping to reduce concerns about bacterial growth in warm water storage tanks. This approach is best used when there is a continuous demand for cool water since there must be a demand for cold water to provide continued support of the comfort cooling demand.
  • the independent tank option allows a larger supply of heated water to be stored and available for use and it allows the comfort cooling to be extended for a longer period of time after water usage or during periods of time when there is no cold water demand.
  • An additional benefit of the tank relative to the mixing valve is that the water supply temperature to the user will not suddenly switch from cold to cool or from cool to cold when the hot and cool control valves actuate.
  • the system will either shut off the cooling process or switch to a heat rejection mode if it is available until water is used allowing the system to continue to generate hot or cool water. If a mixing valve were added to the tank configuration the tank could be heated to a higher temperature while controlling cool water temperature at the faucet.
  • the cold water bypass valves in the independent tank option are used to allow the cool water tank to be used to store hot water during the heating season.
  • Bypass valve 1 is closed and bypass valve 2 open when the system is calling for cooling.
  • Bypass valve 1 is open and bypass valve 2 is closed when the system is calling for heating.
  • These valves may be manually operated valves or automated to respond to the system thermostat.
  • the thermostat on the cool tank may be set to allow it to reach hot water temperatures.
  • the thermostat on the cool tank may be set to hold the temperature to the warmest acceptable temperature for cool water supply.
  • the Applicants' system with its flexible configuration provides a unique capability to support heating and cooling operations that involve thermal fluid loops and thermal energy storage.
  • the thermal loop or storage system may operate to provide either cooling or heating on demand.
  • Figure 6 depicts a basic thermal system with both fluid loop and thermal storage.
  • the fluid and storage media may be water, a mixture of glycol and water or one of any number of thermal fluids available on the market.
  • the storage system may also utilize phase change or phase change materials to boost the energy density on the storage device.
  • the Applicants' system refrigeration cycle configuration is the same as any of the multi-heat source / multi-heat sink configurations illustrated in Figures 4 and 5 except this configuration explicitly utilizes a chiller as one of its evaporators.
  • a chiller as one of its evaporators.
  • a second condenser may be used to reject heat to a cooling tower or air cooled condenser when a facility's heating demands are satisfied and there is still need for comfort cooling.
  • the Heating Heat Exchanger, associated piping and the Fluid Control valves may be omitted from the configuration.
  • the system is used only for heating, it will take the configuration of the system depicted in Figure 4, except that now the hot water tank might involve a phase change mechanism to increase the storage capacity of the system.
  • the circulation loop between the water cooled condenser and the hot water tank adds a heat exchanger in the loop rather than utilizing a separate circulating loop.
  • This offers the advantages of providing the highest temperature for the heat exchange with the thermal loop/storage system and it avoids the operation of an additional pump. It does imply however, that the circulating pump must be wired to operate whenever there is a call for heat from either the thermal system or the water storage tank. It also forces the configuration of the thermal system loop to have the Chiller Fluid Control and Heating Fluid Control valves to avoid heating the loop during cooling operations when the system is in operation.
  • the alternative would be to provide an independent heat circulating loop between the hot water tank and the thermal system loop as illustrated in Figure 4.
  • the thermal system loop may or may not include a thermal storage device (Heat/cool Fluid Tank) depending on the requirements of the application. This implies that in some instances the tank and one of the pumps in the thermal system will not exist.
  • Backup heating and cooling may come from any economically viable source tied into the thermal loop. In most thermal loop systems like this today, the backup heating and cooling would be provided by a boiler and chiller or cooling tower.
  • This Applicants' system configuration provides a unique opportunity to utilize reclamation and/or cogeneration to significantly improve the efficiency of existing thermal loop systems in many facilities and it offers opportunity for a number of new applications where thermal energy (heat or cool) can be efficiently stored for later use.
  • thermal energy heat or cool
  • the two pipe system is represented by the thermal loop system either with or without the tank.
  • the tank will often be used in this application since it provides a dampening affect to the loop to help reduce the variability in loop temperature.
  • the chiller is used in cogeneration mode operation to provide cooling to the thermal loop system while it heats the potable water for showers and laundry or it heats a swimming pool.
  • the Evaporator (one or more of them), operated in reclamation mode to provide heating to the thermal loop system, can be located in various exhaust streams such as the continuous makeup air system exhaust, restaurant kitchen exhaust, laundry drier exhaust, or the wastewater from the showers and laundry.
  • the Applicants' system is sized to match the typical base load heating and cooling for the facility within the constraints of the available heat sources and heat sinks.
  • the backup heating and cooling systems may then be sized to makeup the difference between extreme operating conditions and the typical operating conditions. Another sizing approach would be to size the system to satisfy the demands usually experienced during the spring and fall and size the boiler and chiller for the remainder of the winter and summer extremes.
  • the loop may be operated either in hot and cold mode to provide heating and cooling via a simple fan coil in each hotel room or the loop may be operated at a given temperature such as 55F to provide heating and cooling via water source heat pumps in each hotel room or temperature controlled space serviced by the loop. It would be possible to also provide backup heating and cooling from a ground connected heat pump system as opposed to a boiler and chiller if sufficient ground connection capacity can be economically obtained in an environmentally acceptable manner at the application site. With the Applicants' system, the scale of the ground connected system can be reduced to help hold down overall implementation cost.
  • a good example of a system where this configuration is used for heat storage is in a green house.
  • the greenhouse is subject to significant solar gain on clear days even when the outdoor temperatures are cold. This affords the opportunity to collect the excess heat during the day and utilize it to heat the space during the night.
  • a phase change material will be used in the storage tank to increase the energy density of the storage tank and the phase change material will be selected to allow storage at the normal condensing temperature (hot water tank set point) of the Applicants' system.
  • An advantage of removing the excess heat from the greenhouse (beyond the obvious benefits to the plants) is that the total amount of heat that might be collected will increase, since the cooler temperature in the facility will reduce losses to the outdoors and more solar energy will be captured in a cooled space than in a heated space.
  • more than one energy reclamation unit with its various components is required to satisfy the heating and/or cooling requirement.
  • the more easily controlled multi-unit configuration on the water circulation side is a parallel configuration so that each unit will experience the same operating conditions or water temperatures in the water cooled condenser.
  • Using a series configuration will cause downstream units to experience higher temperatures in the water cooled condenser and as a result higher compressor head pressure and refrigerant temperature. While this temperature differential could be used as a means of turning units on and off, it can be difficult to synchronize the controls with the hot tank thermostat.
  • Each unit will have its own heat sources and will be controlled independently relative to those sources. Care should be taken to try to group units with reasonably similar heat sources to allow the units to operate at relatively similar operating conditions on the refrigerant side. For example, one unit may be servicing a chilled water loop at 40 0 F while the other unit is reclaiming heat from a wastewater tank at 125°F.
  • the compression ratio of the two compressors could be significantly different relative to the condensing temperature which is controlled by the temperature of the hot water tank.
  • the unit operating on the colder environment may reach a compression ratio condition that exceeds the recommendation for the compressor before the hot water tank thermostat is satisfied, putting that unit in danger of failure or reduced operating life.
  • a disadvantage of using common circulating pumps and common tanks for a group of units operating in parallel is that all of the units will be out of operation if the pump, the tank or a common header experience a failure.
  • the redundancy of using a circulating pump for each unit or supplying a spare pump in parallel maybe required in some applications to minimize risk or costs associated with an outage.
  • the Applicants' system can utilize one or more evaporators or one or more condensers independently to optimize utilization of available heat sources and heat demands according to the timing of events within a given application process. This extends the use of one evaporator and one condenser as disclosed in U.S. Patent 7,040,108.
  • the Applicants' system can be used to provide heating, cooling, and heated water for any application.
  • the Applicants' system will utilize 1 or more 3 -way or 2 or more 2- way valves and controls to switch between evaporators and between condensers according to the priorities of the application that are defined in the control system.
  • the system can provide hydronic heat to one or more heat sinks via a hydronic heating loop.
  • the system can provide both chilled water and heated water for a hydronic heating and cooling system.
  • the system can provide tempered water in place of cold water as a way to avoid use of an air cooled condenser during comfort cooling season. This reduces energy consumption by avoiding fan operation, increases heat storage capacity, and reduces sweating from pipes and fixture.
  • Units can be installed in parallel to utilize common circulating pumps and storage tanks for increasing capacity while reducing installation cost.
  • the system can be used with phase change materials to efficiently store heat or cold for later use in a process or facility.
  • the Applicants' system can be used with solar thermal heat collection systems or greenhouses to maximize the thermal energy capture because the collector is continuously cooled which reduces losses to the surroundings and increases the amount of thermal energy that can be collected.
  • Multi-stage heat dissipation configurations
  • the condensing path or heat dissipation side of the refrigerant cycle can be split into useful subcomponents for the purpose of transforming environments or process streams from one state to a desired state. For example, it is possible to utilize one portion of the heat dissipation path of the refrigeration cycle to heat a process stream while another part of the dissipation path is producing steam.
  • the refrigerant passes through three physical phases (vapor, vapor/liquid mixture, and liquid) during heat dissipation.
  • the refrigeration processes associated with each phase are desuperheating (vapor), condensing (vapor/liquid mix) and subcooling (liquid).
  • Desuperheating and subcooling occur over a range of temperatures while condensing occurs at a single temperature or over a small range of temperatures if the refrigerant is a mixture of refrigerants.
  • Each process occurs at approximately the same pressure, except as affected by pressure losses in the piping and system components.
  • each segment of the heat dissipation path may be used to accomplish specific tasks and each segment may be further split to satisfy application requirements. Because the refrigerant is going through a phase change and experiencing significant variation in density, it will be desirable to select heat exchangers that best accommodate the specific phase of refrigerant being processed.
  • a heat exchanger and associated piping that handles superheated vapor will be sized and designed differently than a heat exchanger and piping that will process subcooled liquid and both of these may be different than a heat exchanger and piping that processes a vapor/liquid mixture.
  • the physical state of the application space or process streams may also pass through or be in various phases such as if water were heated to produce steam which will further impact equipment and process design.
  • the water cooled condenser or external condenser of the system was assumed to accept or reject all of the energy associated with desuperheating and condensing. With multiple water cooled condensers, two or more heated conditions can be controlled at a desired temperature. Little attention has been given in the prior art to the energy of subcooling, although subcooling is a critical factor in claims related to frost formation on evaporators and will be an important consideration for process efficiency for some refrigerants. When subcooling is applied, a second or third water cooled condenser (technically called a subcooler) will be required, as described in the following sections.
  • the multi-stage heating configuration may be designed for a continuous heating process, batch heating, or both, depending on the application requirements.
  • the configurations described below extend the multi-heat source / multi-heat sink approach disclosed above to include multiple heat exchangers in a given heat dissipation path and the ability to control operation to heat process liquids to higher temperatures.
  • Heating, cooling, and hot water with mixed superheat coseneration and rejection A special refrigeration configuration has been developed for applications where the cooling demand exceeds the heating demand but the application will benefit from stored thermal energy at a temperature higher than the normal condensing temperature (hot water tank set point temperature).
  • the configuration is illustrated in Figure 7.
  • the configuration on the refrigeration side is like other multi-heat source / multi-heat sink configurations except that there are two 3 -way valves on the condenser side of the compressor and those valves are configured and controlled in a special way.
  • the 3 -way valve C3V1 supplies compressed refrigerant to the water cooled condenser or to the external condenser.
  • Valve C3 Vl as shown, is not a 3-way reclaim valve however it can be, since check valve 1 is required.
  • Valve C3V1 allows the system to operate in normal water heating mode or heat rejection mode (if the second condenser is not used for some specific heating application).
  • the second 3-way valve C3V2 is positioned down stream of the water cooled condenser and discharges either to the receiver or to the external condenser.
  • Valve C3 V2 must be a 3-way reclaim valve since it will be used to draw refrigerant out of the external condenser when the water cooled condenser is being used to heat the hot water tank to temperatures below hot water tank set point (i.e.
  • the refrigerant will be condensing in the water cooled condenser).
  • both valves When both valves are energized the system will continue to heat the hot water tank above the normal hot water set point (normal refrigerant condensing temperature) when there is a call for additional cooling.
  • the water cooled condenser will operate in desuperheat mode (i.e. the refrigerant remains a vapor in the water cooled condenser and is passed to the external condenser to complete condensation).
  • desuperheat mode i.e. the refrigerant remains a vapor in the water cooled condenser and is passed to the external condenser to complete condensation.
  • the system provides a mixed cogeneration and rejection mode operation when used for comfort cooing and water heating.
  • the refrigerant leaving the water cooled condenser at temperatures above the condensing temperature is still a vapor and will then travel to the external condenser to be condensed.
  • the hot refrigerant lines between the water cooled condenser and the external condenser are insulated to help keep the refrigerant from condensing in the lines before it arrives at the condenser.
  • the external condenser is physically located below the water cooled condenser so that any refrigerant that condenses to a liquid prior to the external condenser will be carried by gravity to the external condenser.
  • the receiver should be positioned below all condensers to allow the refrigerant to flow by gravity from the condensers to the receiver.
  • the amount of energy captured in the water will decrease.
  • the amount of heat captured in the water will range from 10% to 20% of the amount that would be captured while operating the hot water tank at or below the refrigerant condensing temperature (i.e. 10% to 20% of normal cogeneration capacity and 80% to 90% rejection).
  • the amount of thermal energy stored in the hot water tank will be greater than it could have been if the system were simply switched to rejection mode when the hot water tank reached its normal set point or the maximum condensing temperature of the refrigerant. Because the tank temperature is higher than the condensing temperature of the refrigerant, the system cannot revert to simple water heating mode until the temperature in the tank is reduced to the condensing temperature of the refrigerant.
  • This configuration is ideal for any facility with a high cooling load that can use a limited amount of higher temperature water.
  • a carwash that is co-located with a restaurant.
  • the cooling demand in a restaurant (particularly from the kitchen) will coincide with meal times, while the heating demand for the car wash will coincide with the car wash cycle which will usually be greatest after work hours on weekdays and all day on weekends.
  • the heat rejected from the kitchen will be stored in the hot tank at the highest temperature permissible for the installed equipment and the water going to the car wash from the hot tank will be tempered down to acceptable conditions for use in the carwash by use of a mixing valve.
  • the system will revert to normal water heating mode to eliminate the rejection mode operation of the external condenser and maximize heat capture into the water.
  • the external condenser operates to reject heat. It is not necessary that this condenser be used solely for rejection.
  • a combination dry cleaner / laundry with a small laundry load could use this configuration to provide comfort cooling for the dry cleaning process while generating water at 80 0 F, 125 0 F, and . 180 0 F.
  • the 125°F water would be generated using only the water cooled condenser while the 80 0 F and 180 0 F water would be generated using both the water cooled condenser and the external condenser, which in this case would be another water cooled condenser.
  • the external condenser would be used to heat incoming cold water to 80 0 F, which is a luxury that adds value to the laundry process but is usually not affordable when heating water with a fuel.
  • the heat rejection goes to a useful heating process that is optional.
  • Heating, coolins. and hot water with superheated liquid Li some applications it is of value to incorporate two or more water or liquid cooled condensers in series to achieve one or more objectives as was identified in the dry cleaner/laundry example described in the previous section. These condensers may provide desuperheating, condensing or subcooling to the refrigerant while heating the liquid to desired conditions or providing stable, efficient refrigeration system operation.
  • a two water cooled condenser configuration shown in Figure 8 is similar to Figure
  • the first water cooled condenser WCCl is used for generating water or liquid at temperatures greater than the normal condensing temperature of the refrigerant. It will operate in condensing mode until the temperature of the water in its circulating loop exceeds the condensing temperature of the refrigerant.
  • WCCl will handle superheated refrigerant vapor and is capable of heating the water in its circulating loop and storage tank to a temperature that approaches the temperature of the superheated vapor entering WCCl .
  • Tanks, pumps, valves, piping, insulation, etc. associated with this loop must all be selected to withstand the temperatures that are desired or possible with superheat operation.
  • Testing with R22 in a 5-ton reciprocating compressor has yielded water temperatures in the neighborhood of 200° F in batch mode operation.
  • the refrigerant vapor entering WCCl can be in the range of 22O 0 F to 260 0 F. This implies that it would be possible to generate steam at atmospheric and low pressure conditions using R22. This was verified in testing, as a few times the system vapor-locked due to steam formation in WCCl .
  • a different heat exchanger and piping arrangement would have been needed to separate the steam and water for a steam production process.
  • WCC2 is used to heat water or liquid in its circulation loop up to the maximum condensing temperature of the refrigerant as controlled by the thermostat in WCC2's hot water tank. This water can be supplied either to WCCl 's circulation loop or to a hot water supply system for the application. When using a system like this it is good to have a use for a hot liquid at the condensing temperature provided by WCC2 and at a higher temperature provided by WCCl . When WCCl is in desuperheating mode on an R22 system, 80% to 90% of the available heat will come out through WCC2 while 10% to 20% will come out through WCCl. These percentages will vary with the refrigerant used in the system.
  • Cold water is introduced into the WCC2 loop on the suction side of the circulating pump to take advantage of tempering. If the system is controlled to produce a continuous flow at a specific temperature, the cold water will mix with the heated water entering
  • WCC2 This can allow the tank in the WCC2 loop to operate at 5°F to 8°F higher than the normally acceptable condensing temperature of the refrigerant, since the compressor will see a head pressure corresponding with the mixed water temperature rather than the temperature of the water in the tank.
  • the flow in WCC2's circulating loop is controlled using the Hot Circ Flow Control valve and the tempering water flow rate can be controlled by the Tempering Flow Control valve. These flow rates can be adjusted to obtain the desired level of temperature control. This tempering affect is of course only available if there is a continuous flow of water through the system.
  • hot water leaving the WCC2 tank is routed to the suction side of WCCl 's circulating pump. This allows the desuperheating process to see a lower temperature at the water side inlet to WCCl, which increases the amount of heat transfer that can be obtained for a given temperature in
  • the HT Supply Flow Control valve is used to control the flow of water to allow the system to maintain a set point temperature leaving the tank. If there was no Hot Supply line (i.e. the system heats water on a once through basis) then the HT Supply Flow Control valve could also provide the same affect as the Tempering Flow Control valve for WCC2's circulation loop.
  • the number, style and location of flow control valves will vary with the requirements or opportunities of an application. For example, if the Hot Supply and HT Supply are exposed to atmospheric pressure, then the flow control valves will be best located in the Hot Supply and HT Supply lines. Another example is where a 3-way proportional control valve can be located in the circulation line between the tank and the tempering supply.
  • the 3-way valve would discharge water at a rate sufficient to allow the temperature in the tank to be held relatively constant.
  • the priority in any combination of flow control valves will be to ensure that the compressor head pressure is controlled to within acceptable limits while meeting the temperature requirements of the application. There is no need to limit the circulation flow rate in WCCl 's circulation loop although it could help to impose a temperature differential across the water side of WCCl to promote better heat transfer.
  • the refrigerant condensing temperature can be maintained as high as 150 0 F.
  • the greatest limitation on the use of this configuration is the temperature of the superheated refrigerant vapor, or more importantly, the temperature of the oil in the superheated vapor entering WCCl. This temperature must remain below the point where the oil begins to break down and lose its lubricating capability. The choice of refrigerant and the efficiency of the compressor can have a significant impact on this temperature. With proper equipment selection the configuration can be used to produce saturated steam at low pressures. An additional heat exchanger of appropriate design would be needed to generate superheated steam.
  • Hydronic heating loops can be applied to either tank.
  • the return from a hydronic loop originating in the WCCl tank may return either to the same tank or to the WCC2 tank.
  • the primary factor in determining which tank it will return to is the temperature of the return relative to the temperature of the tanks. If the return is hotter than the temperature in the WCC2 tank it must be returned to the WCCl tank, the return from a hydronic heating loop originating from the WCC2 loop must return to the WCC2 tank.
  • This configuration to produce a liquid or vapor at a temperature higher than the nominal refrigerant condensing temperature, will be useful in any application where there is a need for cleaning or sterilization of clothing, and equipment such as in laundry, agricultural, food processing, and medical sectors.
  • a hatchery has a significant cooling load to keep the eggs from over heating.
  • the hatchery also needs to sterilize the equipment used to hold the eggs and the chicks several times a week.
  • This configuration can be used to generate and store high temperature water for use in the wash while maintaining the cooling for the eggs.
  • Figure 9 is the same as Figure 8 except it utilizes the configuration very differently.
  • the objective of this utilization is to provide heated liquid at the condensing temperature in WCCl and warmed water from subcooling in WCC2.
  • the circulating loop for WCC2 is used to maintain an average temperature in the tank for subcooling. This is useful if the water usage through the system is intermittent or the temperature of water returned from hydronic heating loops is variable.
  • the tank helps to keep the refrigeration system operation more stable. If the conditions of the cool liquid entering WCC2 will be consistent such as might be the case with a once through heating system, the circulating loop and tank may not be necessary as depicted in Figure 10. In this case, the warmed water is introduced directly into the suction side of the WCCl circulating loop pump. There may be applications where warmed water or liquid can be useful.
  • This configuration will be important for use of refrigerants such as R410A and R422B.
  • the added subcooling is important for obtaining the maximum efficiency out of the refrigeration cycle.
  • a certain fraction of the refrigerant is converted to a vapor and the rest remains a liquid.
  • the expansion process is considered to be isenthalpic or it occurs at a constant enthalpy.
  • Enthalpy is the measure of the energy content of the refrigerant in Btu/lb.
  • the enthalpy of the liquid refrigerant leaving condenser WCC2 will be greater than the enthalpy of the liquid leaving WCC2, since some energy will have been imparted to the water or liquid.
  • This subcooling will allow the fraction of vapor in the mixture to be lower and the fraction of liquid in the mix to be higher after the TX valve. Since the refrigeration effect is produced by the boiling of the remaining liquid fraction of the liquid/vapor mixture in the evaporator, the mixture generated from the subcooled refrigerant will be able to capture more heat in the evaporator. When the evaporator captures more heat, the refrigeration effect is increased and the COP of the system is enhanced. The maximum refrigeration effect occurs when the liquid refrigerant is subcooled to the temperature which corresponds to saturated liquid at the suction pressure or pressure at the inlet of the evaporator.
  • the system can lose in the neighborhood of 40% to 50% of the refrigeration effect during expansion in the TX valve.
  • subcooling the refrigeration effect and system efficiency will be significantly increased.
  • This utilization of this configuration can be applied anywhere that the system can be used with consideration of the issues related to using once through subcooling as in Figure 10 or using a tank and circulating loop as depicted in Figure 9.
  • the system is best applied in situations where there will be a consistent flow of water or liquid to be heated or in the case of a hydronic heating system to be reheated.
  • Figure 11 illustrates a system configured to provide subcooling via WCC3, condensing via WCC2 and superheating via WCCl .
  • the configuration basically combines the concepts of the previous 2 sections to arrive at a way of generating higher liquid temperatures while maintaining higher efficiency through use of s ⁇ bcooling.
  • the same concepts of superheat and subcooling apply except they are combined into the same system.
  • a fourth heat exchanger would be needed prior to WCCl in the refrigeration path if the system were to be used to generate superheated steam.
  • WCCl desuperheats the refrigerant
  • WCC2 condenses the refrigerant
  • WCC3 subcools the refrigerant.
  • Flow controls may include but will not be limited to manually operated valves or any of a variety of automated valves operated to vary the flow so as to maintain the desired temperature of a given circulating loop and storage system.
  • Operating modes include use of two different evaporators to collect heat to heat either the hot tank (WCC2) or the high temperature tank (WCCl). Also included is a mode for mixed cogeneration k to the high temperature tank and rejection via the external condenser EC and a mode for pure heat rejection operation using the external condenser EC.
  • the Applicants' system may utilize any evaporator or evaporator configuration that satisfies the requirements of the refrigeration cycle while serving the demands of the application.
  • This patent previously described the use of more than one evaporator circuit to allow thermal energy to be collected from different locations where only one evaporator circuit was used at a time.
  • the evaporator circuit may be split into more than one evaporator when the application provides multiple heat sources that are smaller than the nominal capacity of the Applicants' system selected to satisfy the thermal energy demands of the application.
  • the basic parallel configuration includes the use of an expansion configuration at each evaporator.
  • the high pressure liquid refrigerant leaving the receiver may pass through a set of valves (2-way or 3-way) to select the desired evaporator circuit based on environmental variables.
  • the refrigerant is split through use of tees or a distribution device to supply each parallel evaporator path in the circuit. It is important that the splitting process be designed so as to avoid expansion of the refrigerant until it reaches the expansion configuration. After the split the liquid refrigerant will pass through the expansion configuration (TX valve, orifice, distributor, etc.) on its way to the evaporators.
  • the superheated refrigerant will be recombined into the suction line feeding the compressor using tees or other means to collect multiple refrigerant streams into one.
  • tees or other means to collect multiple refrigerant streams into one.
  • parallel evaporators it may be necessary to utilize a pressure control device between the evaporators and the compressor to ensure that the pressure leaving the evaporators is the same.
  • An example where parallel evaporators can be used is in a hog barn. Two or more evaporators may be placed in front of separate exhaust fans to allow thermal energy capture sufficient to allow the unit to operate at nominal capacity.
  • the basic series configuration uses only one expansion configuration but splits the evaporator into two or more parts to provide the cooling effect to two or more environments while satisfying the superheating requirements of the refrigeration cycle.
  • the multiple evaporators will usually be reasonably close to each other and the pipe connecting the evaporators will usually be well insulated to avoid losing the refrigeration effect between the evaporators.
  • the refrigerant may pass between the evaporators through a single pipe or it may pass through multiple pipes or a multi-port mixing device.
  • An example where a series configuration is useful is where an environment may require a small or controlled amount of cooling relative to the total cooling capacity.
  • the evaporators will be sized to support the controlled cooling activity and may be made from any material as dictated by the environment served by the evaporator.
  • the temperature of the refrigerant during evaporation (a liquid/vapor mixture) will be constant or for a refrigerant mixture, will vary by a small amount while the refrigerant is boiling within the evaporator (i.e. just like water boils at 212°F at standard atmospheric pressure). After all of the refrigerant is boiled, its temperature will begin to rise as more thermal energy is applied to the evaporator (this is called superheat). The temperature rise (degrees of superheat) is limited to only the amount necessary to avoid introducing liquid refrigerant into the compressor. It is also beneficial to limit the amount of superheat because the capacity of the compressor decreases as the amount of superheat increases due to the reduction in density of the superheated vapor as its temperature increases.
  • the thermal expansion (TX) valve usually provides a means to adjust the degrees of superheat.
  • the expansion and evaporator configuration must be selected to provide the best possible system capacity while satisfying the cooling demands of the environments served.
  • the evaporators must be selected to account for differences in the environmental conditions. For example if two evaporators operating in series experience different environmental temperatures then the evaporators may or may not be the same size depending on how much of the evaporation process each evaporator is intended to handle. In contrast two evaporators operating in parallel will likely be sized differently if they are exposed to different temperature environments to help match the temperature and pressure of the refrigerant leaving each evaporator. Parallel and series evaporator configurations are most easily applied to multiple similar environments. Series evaporator configurations can be more easily applied to multiple environments with different operating conditions or multiple environments with similar operating conditions. Summary of Multi-Stage Heat Collection Claims
  • evaporators manufactured from any material (copper, stainless steel, aluminum, etc.) as dictated by the environment served by the evaporator to protect the evaporator from failure due to corrosion, erosion, thermal fatigue, or other phenomenon.
  • Laundromat In a laundromat, the system heats fresh water for a wash cycle while providing comfort cooling for the workers/customers, by collecting waste heat from the drier exhaust vents, or collecting waste heat from the waste water.
  • Dry cleaner/Laundromat combination The system heats fresh water or tempered water from dry cleaner cooling system while providing comfort cooling for workers/customers, collecting waste heat from the drier exhausts, or collecting waste heat from the waste water.
  • the system utilizes the excess thermal energy from a laundromat, dry cleaner, or other energy intensive business located in a commercial or residential area to heat water that can be piped and metered to neighboring businesses or residents for direct use as heated water and for use in space or process-heating.
  • Meat Processing (kill and products)
  • the meat processing process generally requires a significant amount of heated water for washing and sterilization.
  • the system has the ability to heat water from several sources: waste heat from the singe process, excess ambient heat from the sterilization or cooking processes (comfort cooling), waste heat from the carcass wash and facility cleanup wastewater, and heat expelled from the refrigeration processes required to chill the carcass prior to cutting or after processing.
  • Waste heat from the singe process excess ambient heat from the sterilization or cooking processes (comfort cooling), waste heat from the carcass wash and facility cleanup wastewater, and heat expelled from the refrigeration processes required to chill the carcass prior to cutting or after processing.
  • the ability to provide comfort cooling through use of a forced draft air handler with a-coil provided the environment does not present a high fouling potential.
  • Finless evaporators may be used to recover waste heat from singe and waste water to minimize fouling and allow ease of cleanup.
  • Car Wash The system heats wash water for a car wash and in floor heated water loops used for office heating and eliminates ice formation at the approaches to the wash bays.
  • the heat derives from several heat sources: wastewater, excess heat in the office or mechanical room, excess heat from an adjoining convenience store or restaurant, warm humid air exhausted from the wash bays or the outdoor ambient air.
  • a restaurant benefits from both heating and cooling affects of the system.
  • the kitchen is cooled year-round while water is heated for dish washing and for use in heating the restaurant.
  • the restaurant can be cooled during high occupancy and during the cooling season while heating water for dish washing. Since the cooling load usually exceeds the water heating demand an air cooled condenser, warm water supply, or district water heating system will be needed during the summer.
  • the system can heat swimming pool water using heat from the ambient air or from excess heat in the offices, shower house or mechanical room (comfort cooling).
  • Campground shower house shower house water can be heated with the system using heat from the ambient air or from excess heat and humidity in the shower house or mechanical room (comfort cooling).
  • Comfort cooling in the shower house may help to extend the life of equipment and parts that are subject to the high humidity usually found within the shower house.
  • Animal Confinement (Animals and foul including but not limited to: hogs, dairy cattle, beef cattle, chickens, turkeys, etc.)
  • the system has the ability to heat the living space using the waste heat that is exhausted via the ventilation system or from comfort cooling in critical areas such as the breeding room or boar stud area.
  • Heating may be in the form of heating the air in the room or localized heating as for baby pigs in a farrowing crate or small animals for the first few days or weeks after they are weaned or hatched. Some animals may also benefit from the ability to heat drinking water using waste heat from an exhaust or heat captured from comfort cooling processes. Some stages of animal husbandry will benefit extensively (weight gain, survival, conception rates, reduced stress/susceptibility to disease%) by providing comfort cooling during hot humid summer days. Excess heat from comfort cooling is generally used for heating wash water or drinking water or is expelled in an air cooled condenser. If animal confinements can be properly co-located, the system has the ability to use excess heat generated by larger animals to heat spaces for smaller animals.
  • Heating spaces using Applicant's hydronic heating system has the ability to reduce humidity and toxic gas loadings in the space when compared against direct fired propane or gas heaters.
  • the system has the ability to use excess heat from animal confinements (heat and humidity generated by the animals) to heat anaerobic digesters year-round.
  • the system can also provide the ability to transform the waste thermal energy to heat the residence, shop/office or to provide some heat input for low temperature grain drying either in the bin or in a drying process via an appropriate district heating system.
  • the system has the ability to heat water for the sterilization processes using waste heat from ventilation exhaust, waste heat in the wastewater, and excess heat in the rooms where the sterilization equipment resides (comfort cooling for the workers).
  • Dairy The dairy farm provides a unique opportunity.
  • the system provides cooling for the milk and can be used to cool the offices, and milking parlor.
  • a cooled parlor may contribute to comfort for the cows and increase milk volume.
  • the captured heat can be used to heat Clean In Place (CIP) water and the drinking water. Warm drinking water may also help increase the amount of water the cows drink which can contribute to increased milk production. Since dairy manure is well suited for digesters, the excess heat from the various value added cooling activities can also be used to support an onsite digester.
  • CIP Clean In Place
  • In-Line Processes The in-line process involves the integration of the system into a process to utilize the simultaneous cooling and heating affects. Most in-line processes will use cogeneration on a continuous basis when the process is operating. The introduction of the system will displace a portion if not the entire use of separate heat sources and cooling sources. Any manufacturing process that needs both heating and cooling presents an opportunity to apply the system.
  • Hatchery The system also has the ability to collect heat from cooling water used to cool the incubators and from ventilation exhaust.
  • the reclaimed heat can be used for space heating and to heat wash water and humidification spray water.
  • the ability to recycle the cooling water will provide significant savings in water and wastewater disposal costs.
  • the ability to integrate the system into the incubators will provide both heating and cooling inside the box through finned hydronic systems.
  • Anaerobic Digesters - Anaerobic digesters require close monitoring of temperature to ensure bacterial activity. The manure must be heated as it enters the digester and the temperature must be maintained throughout the anaerobic conversion process. Our system provides the ability to collect heat from the manure leaving the digester and use it to preheat the manure entering the digester.
  • Bio-diesel Production requires that the raw oil be heated and that the various process streams be heated and cooled at various points along the way. Most processes use a boiler to heat the oil and a cooling tower to help cool the process stream. Many processes also use a chiller at some point in the process. The chiller can be replaced with Applicants' stem to provide both chilling and process heating. In addition, the heat remaining in the bio-diesel after conversion may be extracted for process use.
  • Heat in the cooling water going to the cooling tower can also be used to heat makeup or condensate water for the boiler or for heating a process stream.
  • Excess heat in the boiler/mechanical room includes waste heat generated by compressors
  • waste heat from the boiler exhaust can also be captured and introduced into the process.
  • the oil is usually generated in an extrusion process. Extrusion generates a good deal of heat which might also be captured and reintroduced into the process at an appropriate location.
  • Ethanol Production Ethanol production has some similarities to bio-diesel processing. The process involves a boiler and a cooling tower and may involve a chiller. The process streams are heated and cooled for the various stages of the process.
  • Some ethanol processes utilize a great deal of fresh water to wet and cook the mash and makeup water for boiler. All of this water must be heated.
  • the present invention can heat the water used for the cook process and preheat the condensate and makeup water for the boiler. Heat may be collected from the cooling water lines either before or after the cooling processes. In a retrofit application, the system can help to compensate for an undersized cooling tower. Excess heat from the boiler/mechanical room and boiler exhaust are also available for heating. It may also be possible to design a condensing system to cool the exhaust from the distiller's grain driers. In addition to recycling the heat, the condensed water can also be treated and reused in the process.
  • Seasonal applications such as space heating or comfort cooling may also be incorporated into the plant however the payback on a season application is longer than the payback from supporting the process.
  • Canned or frozen vegetable or prepared food processing The canned food process usually requires cooking and elevated temperatures to vacuum seal containers. The excess and waste heat from the process can be recycled into heated process and wash water using the system.
  • the frozen food process usually requires chilling and may involve cooking or blanching. The excess or waste heat from these processes can be used to heat process or wash water. With our system the chilling process can perform both chilling and water heating. Excess heat can also be used to heat other parts of the facility or for a district heating system.
  • Powder coat and baked paint processes utilize ovens to cure the paint and produce a great deal of excess and waste heat.
  • the system can utilize this excess thermal energy to heat wash water, heat other parts of the manufacturing facility or heat water for a district heating system.
  • Extrusion and molding processes Extrusion processes generate a great deal of excess heat which can be utilized to heat other parts of the facility or to heat process and wash water.
  • Some molding processes such as foam pallet forming utilize a great deal of heated water/steam and generate a large sensible and latent heat load in the facility. This system can cool the facility and the cooling water while generating preheated water going into the boiler.
  • Boiler and mechanical rooms provide opportunity to collect excess or waste heat and heat water.
  • Air and refrigeration compressors generate appreciable amounts of heat arid boilers have ambient radiation and convection losses as well as exhaust. Other types of equipment also generate heat.
  • Our system will benefit compressors by cooling the air and the environment around the compressor. Cooler air will increase the density of the air and improve the capacity of the compressor and cooler operating conditions will reduce wear on the equipment and lubricating oils resulting from excessive heat.
  • the excess or waste heat can be reclaimed by the system to preheat makeup or condensate return water or to preheat combustion air.
  • the scale of such systems can range from a few thousand Btu/hr to large utility scale power plants. Extracting heat from a boiler exhaust will require special evaporator configurations and use of materials such as stainless steel that will be suitable for the potentially corrosive boiler exhaust.
  • Greenhouse A greenhouse provides a significant source of heat during the day. Even on sunny cold winter days the temperature in the greenhouse can climb and produce warmer temperatures than desired. During summer months the temperatures in a greenhouse become oppressive. This heat source can be utilized in a number of settings. In an actual functional greenhouse the excess heat generated during the day can be captured by the system and stored in heated water and then distributed into the facility at night. During the summer when excess heat prohibits plant culture the excess heat might be used to heat water for nearby processes.
  • the greenhouse can also be used in commercial office buildings, apartments, hotels, concrete plants, hospitals or any building requiring heat that doesn't have a waste heat source. The greenhouse can be used to collect ventilation exhaust and solar heat gain (not necessarily used for growing plants).
  • the heat captured from the greenhouse by the system can be used to heat water for showers, laundry, swimming pools, concrete mix on cold days, etc. By cooling the space the amount of thermal energy that can be captured will increase.
  • the moisture in a building exhaust that is captured in the greenhouse can be collected and reused for non-potable uses or treated for potable use.
  • the system can tie into large heating cooling and water heating systems for large high rise buildings. Using a hydronic loop and localized water heat pump/fan units heating and cooling can be accomplished in different parts of the building simultaneously by collecting excess solar gain from the sunny side of the building and transferring it to the shaded side of the building.
  • Our system is used to chill the loop during the summer and the excess heat is used to heat potable water for showers/baths, laundry, swimming pools, etc., and can also be used to recoup heat from continuous ventilation exhaust and wastewater to makeup heat into the hydronic heating loop and to heat other spaces such as the parking garage, makeup air, etc. during the heating season.
  • Hydrocarbon to oil systems Recently a number of systems are being developed for converting wet hydrocarbon materials to crude oil through a process involving high pressure and temperature (hydrothermal depolymerization).
  • the system can be integrated into the process to preheat the hydrocarbon-water slurry based on heat collected from the discharged oil and heat losses from the process.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Heat-Pump Type And Storage Water Heaters (AREA)
  • Sorption Type Refrigeration Machines (AREA)

Abstract

La présente invention concerne un système de chauffage et de refroidissement à énergie thermique bio-renouvelable, capable de fonctionner en évacuation, en récupération et en cogénération. Le système de réfrigération de la présente invention utilise un ou plusieurs évaporateurs et un ou plusieurs condenseurs pour transformer de l'énergie thermique sous forme de chaleur perdue dans un environnement en vue de son utilisation dans un autre environnement. Les sources chaude et froide du processus de réfrigération peuvent être séparées pour de multiples applications en vue d'une exploitation accrue de l'énergie du système. Les variables d'environnement sont équilibrées de façon à optimiser les propriétés de l'agent frigorigène et les capacités du compresseur du système.
PCT/US2007/013397 2006-06-07 2007-06-07 Système et procédé de chauffage et de refroidissement à énergie thermique bio-renouvelable WO2007146050A2 (fr)

Priority Applications (7)

Application Number Priority Date Filing Date Title
MX2008015586A MX2008015586A (es) 2006-06-07 2007-06-07 Sistema y metodo de calentamiento y enfriamiento de energia termica bio-renovable.
BRPI0712184-9A BRPI0712184A2 (pt) 2006-06-07 2007-06-07 sistema e método de aquecimento e resfriamento de energia térmica renovável
CA002659584A CA2659584A1 (fr) 2006-06-07 2007-06-07 Systeme et procede de chauffage et de refroidissement a energie thermique bio-renouvelable
AU2007258621A AU2007258621A1 (en) 2006-06-07 2007-06-07 Bio-renewable thermal energy heating and cooling system and method
EP07809376A EP2024693A2 (fr) 2006-06-07 2007-06-07 Système et procédé de chauffage et de refroidissement à énergie thermique bio-renouvelable
JP2009514371A JP2009540258A (ja) 2006-06-07 2007-06-07 バイオ再生可能熱エネルギー加熱冷却システム及び方法
IL195705A IL195705A0 (en) 2006-06-07 2008-12-04 Bio-renewable thermal energy heating and cooling system and method

Applications Claiming Priority (2)

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US80414806P 2006-06-07 2006-06-07
US60/804,148 2006-06-07

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WO2007146050A3 WO2007146050A3 (fr) 2008-05-15

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US (1) US20100018228A1 (fr)
EP (1) EP2024693A2 (fr)
JP (1) JP2009540258A (fr)
KR (1) KR20090021213A (fr)
AU (1) AU2007258621A1 (fr)
BR (1) BRPI0712184A2 (fr)
CA (1) CA2659584A1 (fr)
IL (1) IL195705A0 (fr)
MX (1) MX2008015586A (fr)
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Cited By (14)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2010065922A (ja) * 2008-09-10 2010-03-25 Fujitsu Ltd 吸着式冷凍機及びその制御方法
FR2937410A1 (fr) * 2008-10-17 2010-04-23 Orhan Togrul Pompe a chaleur
ITMI20090331A1 (it) * 2009-03-06 2010-09-07 Ecold S N C Di Colferai Roberta & C Impianto termico particolarmente per punti vendita di prodotti alimentari come supermercati e simili.
ITTV20090044A1 (it) * 2009-03-17 2010-09-18 Clivet S P A Apparato di termoregolazione per sistemi di climatizzazione ambientale
EP2287547A1 (fr) * 2009-08-19 2011-02-23 Steffen Karow Pompe à chaleur et procédé de réglage de la température d'entrée de sources sur une pompe à chaleur
LU92502B1 (fr) * 2014-07-22 2016-01-25 Regandsy & Hates Sarl Installation de production de froid comprenant desmoyens de condensation à la fois par air et par e au, ainsi que son procédé de mise en oeuvre
WO2016036688A1 (fr) * 2014-09-02 2016-03-10 Rheem Manufacturing Company Appareil et procédé pour le chauffage d'eau et le refroidissement d'air hybrides et leur commande
US9879881B2 (en) 2013-03-13 2018-01-30 Rheem Manufacturing Company Apparatus and methods for heating water with refrigerant from air conditioning system
WO2018145884A1 (fr) * 2017-02-13 2018-08-16 Siemens Aktiengesellschaft Procédé permettant de faire fonctionner une installation de pompes à chaleur, installation de pompes à chaleur et centrale électrique comprenant une installation de pompes à chaleur
EP3470748A1 (fr) * 2017-05-12 2019-04-17 Artik-A Climatiseur d'air
WO2019197975A1 (fr) 2018-04-09 2019-10-17 Kiss Zoltan J Chauffage solaire à l'air avec co2 intégré à partir d'un système d'absorption d'air
US10458678B2 (en) 2016-07-06 2019-10-29 Rheem Manufacturing Company Apparatus and methods for heating water with refrigerant and phase change material
EP3764026A1 (fr) * 2019-07-10 2021-01-13 DNM Refrigeration Limited Système de chauffage et de refroidissement
EP3961127A1 (fr) * 2020-08-31 2022-03-02 Mitsubishi Electric R&D Centre Europe B.V. Système de climatisation et son procédé de commande

Families Citing this family (44)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US8463441B2 (en) 2002-12-09 2013-06-11 Hudson Technologies, Inc. Method and apparatus for optimizing refrigeration systems
US8413669B2 (en) 2006-11-23 2013-04-09 Suncor Energy Inc. Heating system for outdoor conveyors in a carwash
DE602007007287D1 (de) * 2007-02-23 2010-08-05 Electrolux Home Prod Corp Wäschetrockner für den Haushalt
US7748137B2 (en) * 2007-07-15 2010-07-06 Yin Wang Wood-drying solar greenhouse
US8553416B1 (en) * 2007-12-21 2013-10-08 Exaflop Llc Electronic device cooling system with storage
EP2103879B1 (fr) * 2008-03-20 2015-07-29 Daikin Industries, Ltd. Dispositif de chauffage
WO2011041408A2 (fr) 2009-09-29 2011-04-07 Carrier Corporation Système et procédé pour maintenir une température de l'air à l'intérieur d'un système hvac (chauffage, ventilation et conditionnement d'air) de bâtiment
FI124016B (fi) * 2009-10-26 2014-01-31 Vapo Oy Menetelmä biomassakuivattimessa käytetyn kuivatusilman lämmittämiseksi välipiirinesteen avulla sekä vesi-glykoliseoksen tai sitä vastaavan jäätymättömän välipiirinesteen käyttö biomassakuivattimessa käytetyn kuivatusilman lämmittämiseksi
US20110239666A1 (en) * 2010-03-12 2011-10-06 Allen Jack W Heat transfer processes and equipment for industrial applications
US8820080B2 (en) * 2010-06-28 2014-09-02 Marvin Duane Julian Nonfractionalized biomass-fueled refrigerant-based cogeneration
US8528227B2 (en) 2010-07-26 2013-09-10 General Electric Company Apparatus and method for refrigerant cycle capacity acceleration
US8601717B2 (en) * 2010-07-26 2013-12-10 General Electric Company Apparatus and method for refrigeration cycle capacity enhancement
US8353114B2 (en) 2010-07-26 2013-01-15 General Electric Company Apparatus and method for refrigeration cycle with auxiliary heating
TW201209555A (en) * 2010-08-26 2012-03-01 Hon Hai Prec Ind Co Ltd Container data center and cooling cycle system thereof
KR101009599B1 (ko) * 2010-10-25 2011-01-20 박영 지열원 히트펌프
US20120109704A1 (en) * 2010-10-27 2012-05-03 Ratnesh Kumar Sharma Managing utilization of biogas in an infrastructure
US8720109B2 (en) 2011-01-25 2014-05-13 Technologies Holdings Corp. Portable heating system for pest control
EP2489775A1 (fr) * 2011-02-18 2012-08-22 Electrolux Home Products Corporation N.V. Sèche-linge à pompe à chaleur et procédé de fonctionnement d'un sèche-linge à pompe à chaleur
US8768528B2 (en) * 2011-05-16 2014-07-01 Vcharge, Inc. Electrical thermal storage with edge-of-network tailored energy delivery systems and methods
US20130047616A1 (en) * 2011-08-23 2013-02-28 GM Global Technology Operations LLC Electrical power cogeneration system
US9435551B2 (en) * 2011-09-15 2016-09-06 Khanh Dinh Dehumidifier dryer using ambient heat enhancement
WO2013138695A1 (fr) * 2012-03-15 2013-09-19 Pas, Inc. Pompe à chaleur à multiples fentes pour le chauffage, le refroidissement et le chauffage de l'eau
US9719062B1 (en) * 2012-07-05 2017-08-01 Nutech Ventures Gas generation
CN102797661B (zh) * 2012-08-03 2015-06-03 齐齐哈尔轨道交通装备有限责任公司 空压机余热利用系统及空压机余热利用方法
DE102012024577A1 (de) * 2012-12-17 2014-06-18 Robert Bosch Gmbh Wärmepumpenanordnung und Verfahren zum Betrieb einer Wärmepumpenanordnung
CN103900251B (zh) * 2012-12-25 2016-03-30 福州斯狄渢电热水器有限公司 即热式热水器
WO2014145685A1 (fr) 2013-03-15 2014-09-18 Crowder College Système géothermique solaire à deux champs
US9016074B2 (en) * 2013-03-15 2015-04-28 Energy Recovery Systems Inc. Energy exchange system and method
US10260775B2 (en) * 2013-03-15 2019-04-16 Green Matters Technologies Inc. Retrofit hot water system and method
GB201313742D0 (en) * 2013-07-31 2013-09-11 Sasie Ltd Energy system
FR3009202B1 (fr) * 2013-07-31 2017-01-27 Ifp Energies Now Procede de captation d'un metal lourd contenu dans un gaz humide integrant une pompe a chaleur pour refroidir le gaz avant elimination de l'eau
WO2016033633A1 (fr) * 2014-09-01 2016-03-10 Smac Technologies Pty Ltd Système de climatisation à détente directe
KR101569677B1 (ko) 2015-02-04 2015-11-17 한국기계연구원 고희박연소를 이용한 트라이젠 시스템 및 그 제어방법
CN104697238B (zh) * 2015-02-12 2017-01-11 清华大学 适于主动配电网的蓄能型热电冷联供装置及其运行方法
US9808327B1 (en) * 2016-07-22 2017-11-07 ProSomnus Sleep Technologies, Inc. Automated method of manufacturing oral appliances
US10648713B2 (en) 2017-02-08 2020-05-12 Titan, Llc Industrial heat transfer unit
CN107702249A (zh) * 2017-09-25 2018-02-16 山西三水能源股份有限公司 智能控制冷热联产系统
CN108645247A (zh) * 2018-07-03 2018-10-12 中海油能源发展股份有限公司珠海冷能利用分公司 一种综合利用液化天然气冷能的换冷系统及方法
KR20210076677A (ko) * 2019-12-16 2021-06-24 엘지전자 주식회사 가스 히트펌프 시스템 및 그 제어방법
WO2022087491A1 (fr) * 2020-10-23 2022-04-28 Illuminated Extractors, Ltd. Système de chauffage et de réfrigération
TWI786509B (zh) * 2021-01-07 2022-12-11 國立虎尾科技大學 農舍沼氣再利用溫控循環系統
CN113409164B (zh) * 2021-08-19 2022-01-25 中冶节能环保有限责任公司 一种开路循环水系统的水质预警处理方法及装置
CN114777350A (zh) * 2022-05-19 2022-07-22 华北电力大学 一种光伏热-地源热耦合的双蒸发器混合供热供冷系统
CN116839244B (zh) * 2023-09-01 2023-12-19 国网江苏省电力有限公司南京供电分公司 多热源热泵相变蓄能型冷热联供系统控制方法与装置

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE2161495A1 (de) * 1971-12-10 1973-06-20 Rhein Westfael Elect Werk Ag Waermerueckgewinnungsanlage
DE20102546U1 (de) * 1999-09-08 2001-04-19 Gautsch Hermann Kühlanlage
DE202004008964U1 (de) * 2004-06-05 2004-09-09 Dietz, Erwin Niedrigenergie-Haus

Family Cites Families (19)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
AU509901B2 (en) * 1976-04-29 1980-05-29 University Of Melbourne, The Solar heat-pump
US4314456A (en) * 1980-05-05 1982-02-09 Borg-Warner Corporation Refrigerant condensing system
JPS5899665A (ja) * 1981-12-09 1983-06-14 株式会社システム・ホ−ムズ ヒ−トポンプ式給湯装置
US4540874A (en) * 1984-01-13 1985-09-10 Borg-Warner Corporation Control system for electric water heater with heat pump external heat source
KR900000809B1 (ko) * 1984-02-09 1990-02-17 미쓰비시전기 주식회사 냉난방 · 급탕용(給湯用) 히트펌프장치
US5056588A (en) * 1990-12-28 1991-10-15 Instatherm Company Evaporative cooling enhanced cold storage system
US5255338A (en) * 1991-07-12 1993-10-19 Electric Power Research Institute, Inc. Heat pump water heater control circuit
US5277038A (en) * 1992-08-28 1994-01-11 Instatherm Company Thermal storage system for a vehicle
US5367602A (en) * 1993-10-21 1994-11-22 Lennox Industries Inc. Control apparatus and method for electric heater with external heat source
US5471851A (en) * 1994-03-15 1995-12-05 Zakryk; John M. Self-regulating swimming pool heater unit
AU719740B2 (en) * 1996-03-29 2000-05-18 Waterfurnace International, Inc. Microprocessor control for a heat pump water heater
US5941091A (en) * 1998-01-14 1999-08-24 Broadbent; John A. Low cost ice making evaporator
US6138744A (en) * 1999-06-07 2000-10-31 Coffee; Derek A. Closed loop geothermal heat exchanger
US6408633B1 (en) * 2000-08-08 2002-06-25 Instatherm Company Interfacing of thermal storage systems with air conditioning units
JP2003023887A (ja) * 2001-07-19 2003-01-28 Kubota Corp 循環型施設栽培方法
JP2003299397A (ja) * 2002-03-29 2003-10-17 Ntt Power & Building Facilities Inc コージェネレーション型ゴミ処理システム
JP2004271080A (ja) * 2003-03-10 2004-09-30 Tokyo Electric Power Co Inc:The 冷熱機器と温熱機器の統合機器
US7040108B1 (en) * 2003-12-16 2006-05-09 Flammang Kevin E Ambient thermal energy recovery system
KR100802571B1 (ko) * 2004-12-13 2008-02-13 엘지전자 주식회사 연료전지의 폐열을 이용한 냉난방 장치

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE2161495A1 (de) * 1971-12-10 1973-06-20 Rhein Westfael Elect Werk Ag Waermerueckgewinnungsanlage
DE20102546U1 (de) * 1999-09-08 2001-04-19 Gautsch Hermann Kühlanlage
DE202004008964U1 (de) * 2004-06-05 2004-09-09 Dietz, Erwin Niedrigenergie-Haus

Cited By (22)

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ITMI20090331A1 (it) * 2009-03-06 2010-09-07 Ecold S N C Di Colferai Roberta & C Impianto termico particolarmente per punti vendita di prodotti alimentari come supermercati e simili.
ITTV20090044A1 (it) * 2009-03-17 2010-09-18 Clivet S P A Apparato di termoregolazione per sistemi di climatizzazione ambientale
EP2287547A1 (fr) * 2009-08-19 2011-02-23 Steffen Karow Pompe à chaleur et procédé de réglage de la température d'entrée de sources sur une pompe à chaleur
US9879881B2 (en) 2013-03-13 2018-01-30 Rheem Manufacturing Company Apparatus and methods for heating water with refrigerant from air conditioning system
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US10281178B2 (en) 2014-07-22 2019-05-07 Syrah S.A. Cold production apparatus, including means for condensation by air and water simultaneously, and the method for implementing said facility
US20170198950A1 (en) * 2014-07-22 2017-07-13 Regandsy & Hates Sàrl Cold Production Apparatus, Including Means for Condensation by Air and Water Simultaneously, and the Method for Implementing Said Facility
LU92502B1 (fr) * 2014-07-22 2016-01-25 Regandsy & Hates Sarl Installation de production de froid comprenant desmoyens de condensation à la fois par air et par e au, ainsi que son procédé de mise en oeuvre
WO2016012501A1 (fr) * 2014-07-22 2016-01-28 Regandsy & Hates Sàrl Installation de production de froid comprenant des moyens de condensation a la fois par air et par eau, ainsi que son procede de mise en œuvre
US10041702B2 (en) 2014-09-02 2018-08-07 Rheem Manufacturing Company Apparatus and method for hybrid water heating and air cooling and control thereof
WO2016036688A1 (fr) * 2014-09-02 2016-03-10 Rheem Manufacturing Company Appareil et procédé pour le chauffage d'eau et le refroidissement d'air hybrides et leur commande
US9945587B2 (en) 2014-09-02 2018-04-17 Rheem Manufacturing Company Apparatus and method for hybrid water heating and air cooling and control thereof
US10458678B2 (en) 2016-07-06 2019-10-29 Rheem Manufacturing Company Apparatus and methods for heating water with refrigerant and phase change material
WO2018145884A1 (fr) * 2017-02-13 2018-08-16 Siemens Aktiengesellschaft Procédé permettant de faire fonctionner une installation de pompes à chaleur, installation de pompes à chaleur et centrale électrique comprenant une installation de pompes à chaleur
EP3470748A1 (fr) * 2017-05-12 2019-04-17 Artik-A Climatiseur d'air
WO2019197975A1 (fr) 2018-04-09 2019-10-17 Kiss Zoltan J Chauffage solaire à l'air avec co2 intégré à partir d'un système d'absorption d'air
US10617998B2 (en) 2018-04-09 2020-04-14 Zoltan J. Kiss Methods to extract carbon dioxide from the atmosphere using a solar PV module as part of a combined cycle energy converter
EP3764026A1 (fr) * 2019-07-10 2021-01-13 DNM Refrigeration Limited Système de chauffage et de refroidissement
EP3961127A1 (fr) * 2020-08-31 2022-03-02 Mitsubishi Electric R&D Centre Europe B.V. Système de climatisation et son procédé de commande

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JP2009540258A (ja) 2009-11-19
WO2007146050A3 (fr) 2008-05-15
IL195705A0 (en) 2009-09-01
KR20090021213A (ko) 2009-02-27
US20100018228A1 (en) 2010-01-28
CA2659584A1 (fr) 2007-12-21

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