[go: up one dir, main page]

WO1989004443A1 - Appareil de stockage et de transfert d'energie thermique - Google Patents

Appareil de stockage et de transfert d'energie thermique Download PDF

Info

Publication number
WO1989004443A1
WO1989004443A1 PCT/US1987/002891 US8702891W WO8904443A1 WO 1989004443 A1 WO1989004443 A1 WO 1989004443A1 US 8702891 W US8702891 W US 8702891W WO 8904443 A1 WO8904443 A1 WO 8904443A1
Authority
WO
WIPO (PCT)
Prior art keywords
heat transfer
liquid
storing
heat
water
Prior art date
Legal status (The legal status 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 status listed.)
Ceased
Application number
PCT/US1987/002891
Other languages
English (en)
Inventor
Edward W. Dittell
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Individual
Original Assignee
Individual
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 Individual filed Critical Individual
Priority to AU13999/88A priority Critical patent/AU1399988A/en
Priority to PCT/US1987/002891 priority patent/WO1989004443A1/fr
Publication of WO1989004443A1 publication Critical patent/WO1989004443A1/fr
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

Links

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
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F5/00—Air-conditioning systems or apparatus not covered by F24F1/00 or F24F3/00, e.g. using solar heat or combined with household units such as an oven or water heater
    • F24F5/0046—Air-conditioning systems or apparatus not covered by F24F1/00 or F24F3/00, e.g. using solar heat or combined with household units such as an oven or water heater using natural energy, e.g. solar energy, energy from the ground
    • 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

Definitions

  • the present invention relates to a system for transferring heat derived from a liquid source, and for storage of liquid involved in the heat transfer process in at least three energy storage tanks maintained at respective different temperature operating ranges.
  • U.S. Patent 4,382,368 discloses a geothermal hot water system including a hot water tank and a warm water tank which are heated independently of each other by a closed-loop Freon system.
  • the system includes a main condenser which heats water for the warm water tank and a desuperheating condenser which heats water for the hot water tank, and where the Freon passes through a water evaporator which is typically heated by well water, or energy recovered from cooling type processes.
  • the Freon system is a closed-loop system, which passes the well water through the water evaporator but does not otherwise utilize the well water in the heating system.
  • the warm water tank and the hot water tank are independently supplied through a potable water system, such as a city water supply system.
  • the present invention represents an improvement over the foregoing patents by providing a liquid storage tank, referred to herein as a cool buffer, coupled to the liquid delivery system and the closed-loop heat exchanger, in order that cooled liquid may be stored for subsequent delivery to an energy transfer medium, referred to herein as an energy handler, for cooling purposes.
  • a liquid storage tank referred to herein as a cool buffer
  • the cool buffer is particularly useful under conditions of limited direct use of ground water. For example, in areas where the ground water is too warm for direct use in cooling, where large numbers of energy handlers would present control problems without a cool buffer, or where limited quantities of ground water are available.
  • the cool buffer would also allow the use of the system with city water where, as in prior art systems, the use of city or treated water would not be economical.
  • the energy handler may be a single device usable for both heating and cooling, coupled through suitable valving to a warm liquid storage tank, referred to herein as a warm buffer, for heating purposes and to the cool buffer for cooling purposes.
  • the power for driving the entire system is derived from one or more closed-loop refrigeration sections, referred to herein as power packs, scaled to provide sufficient power to drive the system according to the average energy demand needs of the individual energy handlers, rather than according to the peak energy demand needs of the system as is common with the prior art systems.
  • the invention will be described in the context of well water and city water sources.
  • the invention finds particular utility in building layouts having more than four different heating and cooling zones, wherein an energy handler may be placed within each heating/cooling zone, and all energy handlers are coupled to a central power pack/buffer equipment room.
  • multiple power packs may be staged to deliver incremental levels of energy for heating and cooling, to thereby tailor the energy delivered to average system demand rather than to peak system demand.
  • the power packs cycle on demand from the various buffers, typically at the rate of 2-4 times per day, rather than present art systems which typically cycle at peak demand at the rate of 4-6 times per hour.
  • FIG. 1 is a schematic diagram of the apparatus of the present invention
  • FIG. 2 is a schematic diagram of a heating/cooling section
  • FIG. 3 is a schematic diagram of a modular form of the apparatus of the present invention.
  • FIG. 4 shows a perspective view of a construction which advantageously utilizes the invention
  • FIG. 5 shows a floor plan of the construction of FIG. 4
  • FIG. 6 shows a further floor plan of a further portion of the construction of FIG. 4.
  • FIG. 7 shows a floor plan of a typical room of the construction of FIG. 4.
  • the energy transfer system of the present invention is schematically illustrated in FIG. 1.
  • the invention includes a source water section 20, a cool energy storage section 21, a refrigeration section 22, a warm energy storage section 24, and a heating/cooling section 26. It is to be appreciated that the present invention may be constructed in modular form, generally according to the layout of FIG. 1. One or more of each of the sections 21, 22, 24 and 26 are combinable to fulfill the heating and/or cooling requirements of a facility or building.
  • the source water section 20 supplies water from a well or other water source through conduit 28 for heat transfer therefrom by refrigeration section 22.
  • the source water may be potable or may be contaminated, the quality not being of any particular importance with respect to the invention, since the source water is never mixed with any of the other water or liquids used in connection with the invention.
  • the source water may be any industrial liquid from which heat can be extracted, or may be shallow well water containing pollutants. An expensive well providing clean, deep well water obtained from an aquifer is not needed, although it is preferable that the temperature of the source water is in the range of 40° F.- 90° F.
  • the well water is conveyed to a cool energy storage section 21 through conduit 30.
  • the water may be diverted, if the cool buffer is already cooled sufficiently, through conduit 32 to a drain or other disposal site.
  • the flow of well water to the cool energy storage section 21 is regulated by a solenoid valve 34, or other control valve, located in conduit 32.
  • the cool energy storage section 21 includes a cool buffer 42, into which the well water flows through conduit 30 as indicated by the arrow 44.
  • a pump 46 recirculates warmer water from the top of buffer 42 back into the well water conduit 28 for recirculation into the refrigeration section 22.
  • An optional check valve 40 in conduit 28 limits the direction of well water flow, as shown by the arrow 48.
  • the refrigeration section 22 preferably includes at least an evaporator 58, an accumulator 60, a compressor 62, a desuperheating condenser 64, a main condenser 66, a receiver 68, a filter dryer 70 and a thermal expansion valve 72, collectively referred to herein as a power pack 22.
  • the power pack 22 is described in my U.S. Patent No. 4,382,368, which is incorporated by reference herein.
  • the evaporator 58 is preferably a coaxial double tube heat exchanger wherein the well water flows through an outer conduit and the refrigerant (Freon) flows through an inner conduit, evaporating and extracting heat from the well water.
  • the desuperheating condenser 64 and the main condenser 66 are preferably also coaxial double tube heat exchangers with the refrigerant flowing through the outer conduit, and water flowing through the inner conduit, with heat being transferred from the refrigerant to the water in the inner conduit.
  • the desuperheating condenser 64 and the main condenser 66 are connected in series, with the superheat being extracted from the refrigerant in the desuperheating condenser 64 and the remaining heat being extracted from the refrigerant by the phase change in the main condenser 66.
  • a thermal expansion valve 72 is positioned upstream of the evaporator 58, and is operated through a temperature sensor 74 and a pressure sensor 75 positioned downstream of the evaporator 58, so that the evaporator 58 is operated at maximum efficiency.
  • the warm energy storage section 24 preferably includes a hot water tank 76, referred to herein as hot buffer 76, and a warm water tank 78, referred to herein as warm buffer 78.
  • Aquastats 80 and 82 are provided for buffer 76
  • aquastats 84 and 86 are provided for buffer 78.
  • Aquastats 80, 82, 84 and 86 upon sensing water temperature below predetermined individually selected temperatures, activate compressor 62. Water from the hot buffer 76 is conveyed through conduit 87 through the inner conduit of the desuperheating condenser 64, and back through a return conduit 88 which returns the water back to the top of buffer 76.
  • a pump 90 provides the motive force to pump the water from the bottom of buffer 76 to the desuperheating condenser 64 and back to the top of buffer 76.
  • a modulating valve 92 controls the flow of water through the desuperheating condenser 64 by way of a temperature sensor 94, preferably positioned upstream of the desuperheating condenser 64.
  • the warm buffer 78 is connected by conduit 96 to the inner conduit of the main condenser 66 for extracting heat from the refrigerant, and the heated liquid is transported back to the top of buffer 78 through conduit 98.
  • a pump 100 provides the motive force for pumping the liquid from the bottom of buffer 78 through the main condenser 66 and back to the top of buffer 78.
  • a modulating valve 102 controls the flow through the main condenser 66 by sensing head pressure of the compressor 62 proximate point 104, upstream of the desuperheating condenser 64. The modulating valve 102 provides protection to the compressor 62, in that as the pressure gets greater, the valve 102 permits more water to flow through the main condenser 66.
  • Modulating valve 101 is connected to the downstream side of main condenser 66, and has an outlet 103 which may be connected to a drain. Modulating valve 101 is also connected to sense the head pressure of the compressor 62 proximate point 104, so that when the head pressure proximate point 104 raises to or above a predetermined value modulating valve 101 opens outlet 103 to drain.
  • Modulating valve 101 only operates after modulating valve 102 has fully opened and is unable to fully reduce head pressure of compressor 62 to an efficient operating pressure.
  • a further protection for compressor 62 is provided by modulating valve 38, which senses the suction pressure of compressor 62 proximate point 105, permitting more flow of water through the evaporator 58 if the suction pressure of compressor 62 falls below a predetermined and preselected value.
  • the heating/cooling section 26 may include a blower system 124 for heating or cooling the environment.
  • a thermostat 126 may be used with the blower system 124, and in combination with a warm water pump 122 and a cold water pump 128.
  • heating/cooling section 26 is placed in a room environment, and thermostat 126 regulates the temperature of the room environment. If the thermostat 126 calls for heat it activates warm water pump 122, which pumps warm water through warm conduit 116 and return conduit 120. If the room thermostat 126 calls for cooling, thermostat 126 activates cold water pump 128, which delivers cold water through cold conduit 117 and return cold conduit 119.
  • the cool water becomes warmed.
  • This warmed water is returned to cool buffer 42 via conduit 119, resulting in a stratified warming of the water in cool buffer 42.
  • the aquastat 41 associated with cool buffer 42 activates power pack 22, causing circulation of water from cool buffer 42 through evaporator 58.
  • This process again cools the water returned to cool buffer 42 via line 30, and effectively heats the refrigerant flowing through power pack 22.
  • the heated refrigerant passes this accumulated heat onto hot buffer 76 and warm buffer 78 through normal operation of power pack 22, to increase the heat content of these buffers.
  • Power pack 22 remains activated until the stratified cooled water returned to buffer 42 reaches the level of aquastat 43, which senses the cool temperature and generates a signal which may deactivate power pack 22. Therefore, in effect, the excess heat accumulated in cool buffer 42 is effectively transferred into warm and hot buffers 78 and 76 respectively.
  • Another way of looking at this overall process is that the cooling action in a room environment results in the heat from the room being transferred from the room to the cool buffer, and from there to the warm and hot buffers, i.e., unwanted room heat is converted into desired hot water and heat energy for other purposes.
  • FIG. 2 shows a further schematic of heating/cooling section 26, referred to herein as an energy handler, illustrating one form of interconnection for the respective components.
  • Thermostat 126 through the system's electrical circuits, generates actuation signals for activating either cold water pump 128 or warm water pump 122. In either event, signals for blower motor 127 are activated. Blow motor 127 forces air flow through radiator 129, for cold air delivery, and radiator 131, for warm air delivery. In either event, the blower air flows through the radiators and into the room environment as indicated by the arrows.
  • the embodiment of FIG. 2 illustrates a heating/cooling section wherein the respective water supplies are totally isolated from one another. Other forms of heating/cooling section 26 could be utilized in connection with this system. It is preferable to maintain isolation between the respective water supply sources.
  • the invention is illustrated in a preferred modular form in FIG. 3.
  • the modular form permits usage of remote site energy handler units operated independently of each other, or in unison.
  • a plurality of staged power packs extract heat from the cool buffer and/or source water for storage in the hot and warm buffers, and the cooled source water is stored in a cool buffer.
  • a first power pack system 130 is connected to hot and warm buffers 132 and 134 and to cool buffer 135, in a manner similar to that illustrated for a single power pack system in FIG. 1.
  • a second power pack 136 is also similarly connected, and a third power pack 138 is also similarly connected.
  • the power packs are shown connected to the same source of well water, although they may be supplied through different sources in an alternative embodiment.
  • the well water source conduit is shown in FIG. 3 as conduit 148, and the well water return conduit is conduit 133.
  • Each of the power packs 130, 136 and 138 are turned on and off through individual aquastats which are symbolically illustrated in FIG. 3.
  • the upper aquastats are set at selected temperatures at different heights in the buffer, and are used to turn on the respective power packs as necessary to transfer sufficient heat from the cool buffer and/or source water to the buffers 132 and 134 as needed.
  • the aquastats for the respective systems are found at respective different heights in the cool buffer, and are turned on as necessary to maintain sufficient cool water in the cool buffer 135.
  • the turn-on temperature of aquastat no. 1 will activate power pack no. 1 for heating and/or cooling
  • the selected temperature of aquastat no. 2 will activate power pack no.
  • the modular system illustrated in FIG. 3 may be connected in a number of different ways.
  • the turn-on temperature setting for the three aquastats in warm buffer 134 can be set to the same temperature, so that their relative positional level in the buffer determines which power pack becomes activated first. Since cooled water returned to the warm buffer 134 enters into the bottom of the warm buffer, the cool water temperature is more or less stratified, and when this stratified cooled water reaches the level of aquastat no. 1 it will activate power pack no. 1. Power pack no. 1 will remain activated until the stratified cool water level returns to approximately the bottom of warm buffer 134, wherein a lower aquastat may generate the turn-off signal.
  • a power pack may be turned on by an aquastat in either the cool buffer 135, warm buffer 134, or hot buffer 132; once the power pack is turned on it remains on until all of the turn-off aquastats 4 in the respective buffers sense a return of the stratified water temperature line at the appropriate turn-off water level. While a single power pack is activated it simultaneously heats warm buffer 134, hot buffer 132, and cools cool buffer 135, and the respective aquastats may be wired to cause the power pack to remain on for so long as any turn-off aquastat does not sense the appropriate water temperature at its stratified level.
  • This operating convention eliminates excess cycling of the power packs, for a power pack will remain on until all buffers have been returned to their respective satisfactory water temperature conditions.
  • Another operational scheme which might be utilized with the modular system of FIG. 3 is to connect the respective power packs to the respective buffers so that a particular power pack always turns on first in response to a particular buffer's water temperature needs.
  • power pack no. 1 could be connected to aquastat no. 1 in cool buffer 135;
  • power pack no. 2 could be connected to aquastat no. 1 in hot buffer 132;
  • power pack no. 3 could be connected to aquastat no. 1 in warm buffer 134.
  • power pack no. 1 would always be the first power pack activated in response to a need for further cooling of the water in cool buffer 135;
  • power pack no. 2 would be the first power pack activated in response to a need for further hot water in hot buffer 132;
  • power pack no. 3 would be the first power pack activated in response to a need for warm water in warm buffer 134. Once activated, any of these power packs would continue operating until the respective cool, hot and warm temperature needs were all met in all of the buffers.
  • FIG. 4 shows a form of construction which can advantageously utilize the invention, and for which the invention may provide a typical savings in annual heating and cooling costs in the range of 60-75 percent.
  • FIG. 4 represents a three-story structure, typically a motel or commercial office building construction, having 50,000 square feet or greater of usable floor space. It is presumed that the construction of FIG. 4 is made according to currently commercial standards, and, if utilized as a motel or hotel structure, has a lobby entrance 152 into a first floor 155, which also encloses a lobby and lounge area, an atrium area, a pool area, various mechanical and facilities rooms, laundry, and other rooms which are commonly found in motel structures.
  • a second floor 156 and a third floor 157 typically are constructed to provide a number of living units, either rooms or suites, which may be constructed around the periphery of the structure, facing inwardly toward a three-story atrium.
  • the atrium is crowned by a glass roof section 154, thereby providing exposure to the interior of the structure to sunlight.
  • FIG. 4 it is not unusual to provide 3,750,000 Btus per day of heat energy for the hot water requirements of the building. This heat energy is typically delivered in high concentrations during a two-hour period in the morning and during a two-hour period in the evening, when demand for hot water is the highest.
  • Such a demand cycle would require a water heating capacity of 1,000,000 Btus per hour with prior art technolog digest.
  • the normal building heat loss is approximately 550,000 Btus per hour (Btuh) during the coldest days, if the building is located in a cold climate, such as is found in the northern United States. Infiltration and make-up air generally requires about 300,000 Btuh in order to maintain building comfort and air circulation.
  • the individual rooms or suites in the building are typically heated and cooled with self-contained conditioning units in each room.
  • the room heating and cooling demands are a function of the climate, the room exposure, the number of people occupying the room, and the time of day. It is not unusual for each room to require approximately 5,000 Btuh of heat energy.
  • FIG. 5 shows a typical floor plan for the first floor 155 of the structure of FIG. 4.
  • the floor plan includes a center atrium area which extends throughout the three-story structure to the glass roof section 154.
  • the first floor also includes a lobby and lounge area, a pool area, a number of stairwells 158, one or more equipment rooms 162, conference and meeting rooms, a number of living units 160, and various other facilities such as restrooms, utility rooms, laundry rooms, storage rooms, etc.
  • Each of the various different rooms and areas shown on FIG. 5 have different heating and cooling needs, and a well-designed heating and cooling system will properly accommodate these needs.
  • each of the living units 160 are typically designed for an average occupancy of three persons, and require heating and make-up air energy of 4,000-5,000 Btuh.
  • Each of the stairwells 158 will typically require about 5,000 Btuh of heating/cooling energy.
  • Service rooms such as entrance areas, restrooms, laundries, mechanical rooms, typically require about 4,000 Btuh.
  • the lounge and lobby area will have energy demands proportionate to their size and other factors, but several energy handlers, on the order of
  • a swimming pool area requires 75,000 Btuh, but since the air must be constantly " dehumidified, it is possible to constantly recover about 30,000 Btuh from the dehumidification process.
  • the atrium area may suffer a heat loss of about 250,000 Btuh, including the make-up air requirements.
  • Each conference room may require from
  • FIG. 6 shows a typical floor plan for a second floor 156 or a third floor 157 of the structure shown in
  • the upper floors of the structure will also have a center atrium opening, but will be typically designed for more or less exclusive living unit construction.
  • These floors will usually have hallways 164, and a plurality of living units 160 having access doors entering into the hallway.
  • the heating needs of this building are taken into consideration, it requires a maximum average design heating capacity of about 900,000
  • the heating and cooling needs for such a structure are typically met by domestic hot water heaters, a central heating plant and boiler system, a central cooling tower, and multiple heat pumps distributed throughout the various rooms and heating/cooling zones in the structure. It is common for such systems to run a water supply loop throughout the various building areas. wherein water is maintained in constant flow at temperatures ranging from 60°-90° F.
  • FIGS. 4-7 An embodiment of the invention will now be described, with reference to FIGS. 4-7, in order that the full features and advantage of the invention may be fully understood.
  • the buffers and power packs are placed in an equipment room 162, wherein three power packs A, B, C, are designated by reference numeral 170.
  • Each of the power packs A, B, C are driven by a 20 horsepower (hp) compressor unit, wherein the total energy capacity of all three power packs is approximately
  • a cool buffer 140 has a liquid storage capacity of 4,800 gallons, as does a warm buffer 142.
  • a hot buffer 144 has a liquid storage capacity of 1,600 gallons. If power pack A is designated as the primary energy provider, under typical annual average energy demands it will be required to operate approximately 85 percent of the time. If power pack B is designated as the secondary energy provider, under the same annual average energy demands it will be required to run about 50 percent of the time; if power pack C is designated as the tertiary energy provider, under the same annual average energy demands it will be required to run about 15 percent of the time.
  • Each living unit 160 has an energy handler 161.
  • Cool water lines 145 and 146 are connected throughout the structure, typically running above the ceiling down the various hallways 164.
  • warm water lines 149 and 150 are connected throughout the structure.
  • Energy handler 161 is coupled in parallel to the respective cool water lines 145 and 146, and warm water lines 149 and 150, and thermostatic-controlled valves permit water flow through energy handler 161 via the lines.
  • the thermostat controlling energy handler 161 is typically located in a central position within living unit 160.
  • a hot water line (not shown) is run throughout the structure for coupling into the various hot water delivery faucets required for common usage.
  • the cool water and warm water used to supply lines 145 and 146, and 149 and 150, are coupled to cool buffer 140 and warm buffer 142.respectively.
  • the hot water lines are coupled to hot buffer 144.
  • the cold, warm and hot buffers are respectively coupled to the power packs as has been previously described herein.
  • Other energy handlers are similarly connected to the various heating/cooling zones throughout the structure, including the lobbies, conference rooms, pool and pool area, spa, atrium, stairwells, utility rooms, etc.
  • the principles of connection and operation of each of these energy handlers is the same as for the energy handler 161 in a living unit 160, and each of the separate energy handlers may have its own thermostatic control.
  • Heating energy handlers can also deice driveways or walkways, reheat air cooled for dehumidification purposes, heat industrial chemicals,- and heat swimming pools and spas, etc.
  • Cooling energy handlers can also cool industrial chemicals, dehumidify air, etc.
  • the instantaneous energy demands of any room within the structure is met by the thermostat in that particular room generating an activation signal to its energy handler; the energy handler then couples itself into the cold/warm water line and, typically through a water/air heat exchanger, delivers heated/cooled air into the room. If the room is heated, heat is transferred from the warm water supply line 149 into the room environment, and the cooled water is directed to return line 150. If cooling is demanded, cool air is delivered into the room through a similar heat exchange process, and cool water supply line 145 provides the cool water and cool water return line 146 is incrementally warmed to the extent that the heat transfer process takes place. Since cool water return line 146 and warm water return line 150 pass throughout the entire structure, terminating in the respective warm/cool buffer, the temperature of the water in the buffers is incrementally affected by the process.
  • power pack A As the stratified temperature in a buffer departs from a predetermined point, it activates power pack A to restore the temperature to its set point position. Power pack A also, through its operation, tends to restore the temperatures of the other buffers to their set point position. If the heating/cooling demand causes a respective buffer to depart past a second predetermined set s , point, power pack B is activated to assist in the restoration of temperature in the affected buffer.
  • the respective temperatures for activating each of the power packs A, B, C may be sensed at different levels in the warm buffer tank, the power pack A temperature sensor being lowest, the power pack B temperature sensor being an intermediate point, and the power pack C temperature sensor being a higher point. Therefore, as the temperature of warm buffer drops, the stratified cooler water is first sensed by the power pack A temperature sensor, and if the temperature of the buffer continues to drop the stratified temperature is sensed by the power pack B sensor, and if the temperature continues to drop the stratified temperature is sensed by the sensor for power pack C, because as the overall temperature in the warm buffer drops the cooler water strata will be sensed at higher and higher levels within the tank.
  • the inverse process is used to activate power packs by sensors attached to the cool buffer.
  • the heating of the hot buffer is assisted by virtue of the fact that its input is connected to the warm buffer; therefore, the water temperature input into the hot buffer is already elevated, and the hot buffer need only to increase incrementally the temperature of its water.
  • water from the warm and hot buffers can be mixed through suitable valving, in order that an excess stored accumulation of hot water can be used to assist the warm water demand needs under certain conditions.
  • the warm water from the warm buffer can be mixed into the hot water to provide hot water delivery at the optimum delivery temperature.
  • the living units along the south side of the building may require cooling air, while the living units along the north side of the building may.require heating air.
  • the cool buffer may be simultaneously delivering cooling energy to the south side of the building and to the dehumidifier while the warm buffer is delivering heat energy to the north side of the building and the pool, etc.
  • the system is in effect merely passing the recovered heat from the cooling requirements of the building to the heating requirements of the building. The transformation of this heat energy takes place through the buffer system, but the process may take place without any short term demand on the power packs themselves.
  • the respective buffers provide instantaneous and short-term peak energy requirements to satisfy all the energy handlers' heating and cooling demands in their respective zones of the building at any instant in time; the power packs supply energy to meet the overall average energy consumption of the building.
  • the power packs may be sized merely for average consumption, and further may be staged so as to accommodate short-term perturbations to the average energy demands.
  • FIG. 3 may also incorporate the specific control functions which are described in my U.S.
  • Patent 4,633,676 which is incorporated by reference herein.
  • Other forms and alternatives of the present invention may be devised, in addition to the preferred embodiments described herein, without departing from the spirit and scope of the invention.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Life Sciences & Earth Sciences (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Sustainable Energy (AREA)
  • Sustainable Development (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Other Air-Conditioning Systems (AREA)

Abstract

Système destiné à utiliser de préférence de l'eau de puits comme milieu de source ou de puits d'énergie thermique, en combinaison avec un échangeur thermique (58) et un réservoir de stockage d'eau (42), dans lequel de la chaleur est extraite de l'eau de puits par l'échangeur thermique, et l'eau de puits refroidie est transférée jusqu'au réservoir de stockage (42) à des fins de refroidissement (26). L'échangeur thermique (58) est couplé à d'autres échangeurs thermiques (64, 66) respectivement couplés aux réservoirs (78, 76) de stockage d'eau tiède et chaude, en vue de transférer de la chaleur à partir du milieu de l'échangeur thermique jusque dans un réservoir de stockage tiède (78), et de transférer de la chaleur surchauffée à partir du milieu de l'échangeur thermique dans le réservoir de stockage d'eau chaude (76), respectivement utilisés pour le chauffage d'eau tiède (26) et pour l'alimentation d'eau chaude (114) en vue d'une utilisation directe. Le système de refroidissement d'eau de puits est en isolation liquide du milieu fluide de transfert thermique, et également en isolation liquide des systèmes respectifs de stockage et d'alimentation d'eau tiède et chaude.
PCT/US1987/002891 1987-11-03 1987-11-03 Appareil de stockage et de transfert d'energie thermique Ceased WO1989004443A1 (fr)

Priority Applications (2)

Application Number Priority Date Filing Date Title
AU13999/88A AU1399988A (en) 1987-11-03 1987-11-03 Heat energy storage and transfer apparatus
PCT/US1987/002891 WO1989004443A1 (fr) 1987-11-03 1987-11-03 Appareil de stockage et de transfert d'energie thermique

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
PCT/US1987/002891 WO1989004443A1 (fr) 1987-11-03 1987-11-03 Appareil de stockage et de transfert d'energie thermique

Publications (1)

Publication Number Publication Date
WO1989004443A1 true WO1989004443A1 (fr) 1989-05-18

Family

ID=22202649

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/US1987/002891 Ceased WO1989004443A1 (fr) 1987-11-03 1987-11-03 Appareil de stockage et de transfert d'energie thermique

Country Status (2)

Country Link
AU (1) AU1399988A (fr)
WO (1) WO1989004443A1 (fr)

Cited By (39)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2750480A1 (fr) * 1996-07-01 1998-01-02 Paquot Michel Systeme de chauffage et refroidissement d'un local et de production d'eau chaude sanitaire et d'eau brute
US6834714B2 (en) * 2002-11-22 2004-12-28 Paul J. Walsh Variable constant volume cooling/heating unit
US6976524B2 (en) 2003-10-27 2005-12-20 Walsh Paul J Apparatus for maximum work
WO2006100709A1 (fr) * 2005-03-24 2006-09-28 Lambda S.P.A. Systeme integre de production de chaud et de froid pour leur utilisation simultanee par des dispositifs de refroidissement et de chauffage
US7356997B2 (en) 2002-05-29 2008-04-15 Gruber Duane A Chilled water storage for milk cooling process
EP1746370A3 (fr) * 2005-07-18 2008-07-30 Blue Box Group S.r.l. Unité de chauffage et/ou de refroidissement
WO2010061205A1 (fr) * 2008-11-03 2010-06-03 Laing O'rourke Plc Commande du climat ambiant pour bâtiments commerciaux
US20110041536A1 (en) * 2009-08-18 2011-02-24 TRIEA Systems, LLC Heat exchange system
US20110154838A1 (en) * 2009-08-18 2011-06-30 TRIEA Systems, LLC Heat exchange system
CN102788448A (zh) * 2012-06-29 2012-11-21 苟仲武 建筑物中节能减排能量综合利用系统
CN109737619A (zh) * 2019-01-09 2019-05-10 青岛海尔空调器有限总公司 一种能源系统的控制方法、装置、计算机设备及存储介质
CN109764716A (zh) * 2019-01-09 2019-05-17 青岛海尔空调器有限总公司 能量存储站及用于能量存储站的控制方法
CN109764722A (zh) * 2019-01-09 2019-05-17 青岛海尔空调器有限总公司 能量存储站及用于能量存储站的控制方法
CN109764719A (zh) * 2019-01-09 2019-05-17 青岛海尔空调器有限总公司 能量存储站及用于能量存储站的控制方法
CN109764727A (zh) * 2019-01-09 2019-05-17 青岛海尔空调器有限总公司 能量存储站及用于能量存储站的控制方法
CN109764718A (zh) * 2019-01-09 2019-05-17 青岛海尔空调器有限总公司 能量存储站及用于能量存储站的控制方法
CN109764733A (zh) * 2019-01-09 2019-05-17 青岛海尔空调器有限总公司 能量存储站及用于能量存储站的控制方法
CN109764713A (zh) * 2019-01-09 2019-05-17 青岛海尔空调器有限总公司 能量存储站及用于能量存储站的控制方法
CN109764711A (zh) * 2019-01-09 2019-05-17 青岛海尔空调器有限总公司 能量存储站及用于能量存储站的控制方法
CN109764724A (zh) * 2019-01-09 2019-05-17 青岛海尔空调器有限总公司 能量存储站及用于能量存储站的控制方法
CN109764731A (zh) * 2019-01-09 2019-05-17 青岛海尔空调器有限总公司 能量存储站及用于能量存储站的控制方法
CN109764717A (zh) * 2019-01-09 2019-05-17 青岛海尔空调器有限总公司 能量存储站及用于能量存储站的控制方法
CN109764712A (zh) * 2019-01-09 2019-05-17 青岛海尔空调器有限总公司 能量存储站及用于能量存储站的控制方法
CN109764725A (zh) * 2019-01-09 2019-05-17 青岛海尔空调器有限总公司 能量存储站及用于能量存储站的控制方法
CN109764714A (zh) * 2019-01-09 2019-05-17 青岛海尔空调器有限总公司 能量存储站及用于能量存储站的控制方法
CN109764728A (zh) * 2019-01-09 2019-05-17 青岛海尔空调器有限总公司 能量存储站及用于能量存储站的控制方法
CN109764726A (zh) * 2019-01-09 2019-05-17 青岛海尔空调器有限总公司 能量存储站及用于能量存储站的控制方法
CN109764720A (zh) * 2019-01-09 2019-05-17 青岛海尔空调器有限总公司 能量存储站及用于能量存储站的控制方法
CN109764715A (zh) * 2019-01-09 2019-05-17 青岛海尔空调器有限总公司 能量存储站及用于能量存储站的控制方法
CN109764732A (zh) * 2019-01-09 2019-05-17 青岛海尔空调器有限总公司 能量存储站及用于能量存储站的控制方法
CN109764710A (zh) * 2019-01-09 2019-05-17 青岛海尔空调器有限总公司 能量存储站及用于能量存储站的控制方法
CN109764730A (zh) * 2019-01-09 2019-05-17 青岛海尔空调器有限总公司 能量存储站及用于能量存储站的控制方法
CN109764723A (zh) * 2019-01-09 2019-05-17 青岛海尔空调器有限总公司 能量存储站及用于能量存储站的控制方法
CN109764729A (zh) * 2019-01-09 2019-05-17 青岛海尔空调器有限总公司 能量存储站及用于能量存储站的控制方法
CN109764721A (zh) * 2019-01-09 2019-05-17 青岛海尔空调器有限总公司 能量存储站及用于能量存储站的控制方法
CN109764505A (zh) * 2019-01-09 2019-05-17 青岛海尔空调器有限总公司 能源系统、能源系统的控制方法及装置、存储介质
CN109780912A (zh) * 2019-01-09 2019-05-21 青岛海尔空调器有限总公司 一种能源站及其控制方法和存储介质
CN109855227A (zh) * 2019-01-09 2019-06-07 青岛海尔空调器有限总公司 能源系统、能源系统的控制方法及装置、存储介质
CN109855459A (zh) * 2019-01-09 2019-06-07 青岛海尔空调器有限总公司 一种能源系统的控制方法

Citations (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2935857A (en) * 1957-02-19 1960-05-10 Alden I Mcfarlan Air conditioning
US3069867A (en) * 1961-05-29 1962-12-25 Trane Co Summer-winter air conditioning system
US3996759A (en) * 1975-11-03 1976-12-14 Milton Meckler Environment assisted hydronic heat pump system
US4134273A (en) * 1977-04-22 1979-01-16 Brautigam Robert F Home heating and cooling system
US4165036A (en) * 1977-08-29 1979-08-21 Milton Meckler Multi source heat pump air conditioning system
GB2016668A (en) * 1978-03-16 1979-09-26 Carrier Drysys Ltd Energy recovery system
JPS5585840A (en) * 1978-12-20 1980-06-28 Hitachi Ltd Controlling method of capacity of chilling unit
US4382368A (en) * 1981-03-20 1983-05-10 Dittell Edward W Geothermal hot water system
JPS60233443A (ja) * 1984-05-07 1985-11-20 Matsushita Electric Ind Co Ltd ヒ−トポンプ温水装置
US4559788A (en) * 1981-09-14 1985-12-24 Mcfarlan Alden I Air conditioning system and method
US4633676A (en) * 1984-11-19 1987-01-06 Dittell Edward W Cooling and heating apparatus

Patent Citations (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2935857A (en) * 1957-02-19 1960-05-10 Alden I Mcfarlan Air conditioning
US3069867A (en) * 1961-05-29 1962-12-25 Trane Co Summer-winter air conditioning system
US3996759A (en) * 1975-11-03 1976-12-14 Milton Meckler Environment assisted hydronic heat pump system
US4134273A (en) * 1977-04-22 1979-01-16 Brautigam Robert F Home heating and cooling system
US4165036A (en) * 1977-08-29 1979-08-21 Milton Meckler Multi source heat pump air conditioning system
GB2016668A (en) * 1978-03-16 1979-09-26 Carrier Drysys Ltd Energy recovery system
JPS5585840A (en) * 1978-12-20 1980-06-28 Hitachi Ltd Controlling method of capacity of chilling unit
US4382368A (en) * 1981-03-20 1983-05-10 Dittell Edward W Geothermal hot water system
US4559788A (en) * 1981-09-14 1985-12-24 Mcfarlan Alden I Air conditioning system and method
JPS60233443A (ja) * 1984-05-07 1985-11-20 Matsushita Electric Ind Co Ltd ヒ−トポンプ温水装置
US4633676A (en) * 1984-11-19 1987-01-06 Dittell Edward W Cooling and heating apparatus

Cited By (43)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2750480A1 (fr) * 1996-07-01 1998-01-02 Paquot Michel Systeme de chauffage et refroidissement d'un local et de production d'eau chaude sanitaire et d'eau brute
US7356997B2 (en) 2002-05-29 2008-04-15 Gruber Duane A Chilled water storage for milk cooling process
US6834714B2 (en) * 2002-11-22 2004-12-28 Paul J. Walsh Variable constant volume cooling/heating unit
US6976524B2 (en) 2003-10-27 2005-12-20 Walsh Paul J Apparatus for maximum work
WO2006100709A1 (fr) * 2005-03-24 2006-09-28 Lambda S.P.A. Systeme integre de production de chaud et de froid pour leur utilisation simultanee par des dispositifs de refroidissement et de chauffage
EP1746370A3 (fr) * 2005-07-18 2008-07-30 Blue Box Group S.r.l. Unité de chauffage et/ou de refroidissement
WO2010061205A1 (fr) * 2008-11-03 2010-06-03 Laing O'rourke Plc Commande du climat ambiant pour bâtiments commerciaux
US20110041536A1 (en) * 2009-08-18 2011-02-24 TRIEA Systems, LLC Heat exchange system
US20110154838A1 (en) * 2009-08-18 2011-06-30 TRIEA Systems, LLC Heat exchange system
US9027359B2 (en) * 2009-08-18 2015-05-12 Triea Technologies, LLC Heat exchange system
CN102788448A (zh) * 2012-06-29 2012-11-21 苟仲武 建筑物中节能减排能量综合利用系统
CN109764724A (zh) * 2019-01-09 2019-05-17 青岛海尔空调器有限总公司 能量存储站及用于能量存储站的控制方法
CN109764728A (zh) * 2019-01-09 2019-05-17 青岛海尔空调器有限总公司 能量存储站及用于能量存储站的控制方法
CN109764722A (zh) * 2019-01-09 2019-05-17 青岛海尔空调器有限总公司 能量存储站及用于能量存储站的控制方法
CN109764719A (zh) * 2019-01-09 2019-05-17 青岛海尔空调器有限总公司 能量存储站及用于能量存储站的控制方法
CN109764727A (zh) * 2019-01-09 2019-05-17 青岛海尔空调器有限总公司 能量存储站及用于能量存储站的控制方法
CN109764718A (zh) * 2019-01-09 2019-05-17 青岛海尔空调器有限总公司 能量存储站及用于能量存储站的控制方法
CN109764733A (zh) * 2019-01-09 2019-05-17 青岛海尔空调器有限总公司 能量存储站及用于能量存储站的控制方法
CN109764713A (zh) * 2019-01-09 2019-05-17 青岛海尔空调器有限总公司 能量存储站及用于能量存储站的控制方法
CN109764711A (zh) * 2019-01-09 2019-05-17 青岛海尔空调器有限总公司 能量存储站及用于能量存储站的控制方法
CN109737619A (zh) * 2019-01-09 2019-05-10 青岛海尔空调器有限总公司 一种能源系统的控制方法、装置、计算机设备及存储介质
CN109764731A (zh) * 2019-01-09 2019-05-17 青岛海尔空调器有限总公司 能量存储站及用于能量存储站的控制方法
CN109764717A (zh) * 2019-01-09 2019-05-17 青岛海尔空调器有限总公司 能量存储站及用于能量存储站的控制方法
CN109764712A (zh) * 2019-01-09 2019-05-17 青岛海尔空调器有限总公司 能量存储站及用于能量存储站的控制方法
CN109764725A (zh) * 2019-01-09 2019-05-17 青岛海尔空调器有限总公司 能量存储站及用于能量存储站的控制方法
CN109764714A (zh) * 2019-01-09 2019-05-17 青岛海尔空调器有限总公司 能量存储站及用于能量存储站的控制方法
CN109764716A (zh) * 2019-01-09 2019-05-17 青岛海尔空调器有限总公司 能量存储站及用于能量存储站的控制方法
CN109764726A (zh) * 2019-01-09 2019-05-17 青岛海尔空调器有限总公司 能量存储站及用于能量存储站的控制方法
CN109764720A (zh) * 2019-01-09 2019-05-17 青岛海尔空调器有限总公司 能量存储站及用于能量存储站的控制方法
CN109764715A (zh) * 2019-01-09 2019-05-17 青岛海尔空调器有限总公司 能量存储站及用于能量存储站的控制方法
CN109764732A (zh) * 2019-01-09 2019-05-17 青岛海尔空调器有限总公司 能量存储站及用于能量存储站的控制方法
CN109764710A (zh) * 2019-01-09 2019-05-17 青岛海尔空调器有限总公司 能量存储站及用于能量存储站的控制方法
CN109764730A (zh) * 2019-01-09 2019-05-17 青岛海尔空调器有限总公司 能量存储站及用于能量存储站的控制方法
CN109764723A (zh) * 2019-01-09 2019-05-17 青岛海尔空调器有限总公司 能量存储站及用于能量存储站的控制方法
CN109764729A (zh) * 2019-01-09 2019-05-17 青岛海尔空调器有限总公司 能量存储站及用于能量存储站的控制方法
CN109764721A (zh) * 2019-01-09 2019-05-17 青岛海尔空调器有限总公司 能量存储站及用于能量存储站的控制方法
CN109764505A (zh) * 2019-01-09 2019-05-17 青岛海尔空调器有限总公司 能源系统、能源系统的控制方法及装置、存储介质
CN109780912A (zh) * 2019-01-09 2019-05-21 青岛海尔空调器有限总公司 一种能源站及其控制方法和存储介质
CN109855227A (zh) * 2019-01-09 2019-06-07 青岛海尔空调器有限总公司 能源系统、能源系统的控制方法及装置、存储介质
CN109855459A (zh) * 2019-01-09 2019-06-07 青岛海尔空调器有限总公司 一种能源系统的控制方法
CN109855459B (zh) * 2019-01-09 2021-01-29 青岛海尔空调器有限总公司 一种能源系统的控制方法
CN109764720B (zh) * 2019-01-09 2021-11-23 青岛海尔空调器有限总公司 能量存储站及用于能量存储站的控制方法
CN109764713B (zh) * 2019-01-09 2021-11-23 青岛海尔空调器有限总公司 能量存储站及用于能量存储站的控制方法

Also Published As

Publication number Publication date
AU1399988A (en) 1989-06-01

Similar Documents

Publication Publication Date Title
WO1989004443A1 (fr) Appareil de stockage et de transfert d'energie thermique
US6347527B1 (en) Integrated system for heating, cooling and heat recovery ventilation
US4111259A (en) Energy conservation system
US9915450B2 (en) Multi-split heat pump for heating, cooling, and water heating
US5320166A (en) Heat pump system with refrigerant isolation and heat storage
US5183102A (en) Heating and cooling system
US9310087B2 (en) System and method for maintaining air temperature within a building HVAC system
US6976524B2 (en) Apparatus for maximum work
US6041613A (en) Energy conserving heat pump system
US6082125A (en) Heat pump energy management system
US8327655B2 (en) Heating and air-conditioning installation with a heat pump, the installation including at least one heat transfer fluid distributor unit with coupling to a plurality of heat collection and delivery circuits
CA2044448A1 (fr) Systeme integre de chauffage, refroidissement et ventilation
JPH03129215A (ja) 閉鎖空間加熱装置および空間加熱方法
US9212835B1 (en) Heating and cooling system utilizing a water source heat pump and a swimming pool
US20050183773A1 (en) Multi-story water distribution system
US5054542A (en) Heat transfer system
EP2450641B1 (fr) Installation pour la récupération de chaleur de l'air d'évacuation utilisant une pompe à chaleur, et bâtiment comportant cette installation
EP0882202B1 (fr) Systeme de gestion d'energie a pompe a chaleur
US20240167701A1 (en) Modular hvac-shw system and a method of integrating thereof
Cox Heating, ventilating and air conditioning systems
CN213514240U (zh) 一种高温高湿环境空调系统
AU720230B2 (en) Heat pump energy management system
US20170362843A1 (en) Available and Heated Air from Warm Spaces and/or Exhaust of Air Conditioners from Residences or Buildings for Use with Heating Water of Nearby Swimming Pool
JPH0454867B2 (fr)
Bean et al. Vertically integrated systems in stand-alone multistory buildings

Legal Events

Date Code Title Description
AK Designated states

Kind code of ref document: A1

Designated state(s): AU JP US

AL Designated countries for regional patents

Kind code of ref document: A1

Designated state(s): AT BE CH DE FR GB IT LU NL SE