US20050262862A1 - Hvac desiccant wheel system and method - Google Patents
Hvac desiccant wheel system and method Download PDFInfo
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- US20050262862A1 US20050262862A1 US10/855,912 US85591204A US2005262862A1 US 20050262862 A1 US20050262862 A1 US 20050262862A1 US 85591204 A US85591204 A US 85591204A US 2005262862 A1 US2005262862 A1 US 2005262862A1
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- air
- desiccant wheel
- passageway
- air passageway
- refrigerant system
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Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F24—HEATING; RANGES; VENTILATING
- F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
- F24F3/00—Air-conditioning systems in which conditioned primary air is supplied from one or more central stations to distributing units in the rooms or spaces where it may receive secondary treatment; Apparatus specially designed for such systems
- F24F3/12—Air-conditioning systems in which conditioned primary air is supplied from one or more central stations to distributing units in the rooms or spaces where it may receive secondary treatment; Apparatus specially designed for such systems characterised by the treatment of the air otherwise than by heating and cooling
- F24F3/14—Air-conditioning systems in which conditioned primary air is supplied from one or more central stations to distributing units in the rooms or spaces where it may receive secondary treatment; Apparatus specially designed for such systems characterised by the treatment of the air otherwise than by heating and cooling by humidification; by dehumidification
- F24F3/1411—Air-conditioning systems in which conditioned primary air is supplied from one or more central stations to distributing units in the rooms or spaces where it may receive secondary treatment; Apparatus specially designed for such systems characterised by the treatment of the air otherwise than by heating and cooling by humidification; by dehumidification by absorbing or adsorbing water, e.g. using an hygroscopic desiccant
- F24F3/1423—Air-conditioning systems in which conditioned primary air is supplied from one or more central stations to distributing units in the rooms or spaces where it may receive secondary treatment; Apparatus specially designed for such systems characterised by the treatment of the air otherwise than by heating and cooling by humidification; by dehumidification by absorbing or adsorbing water, e.g. using an hygroscopic desiccant with a moving bed of solid desiccants, e.g. a rotary wheel supporting solid desiccants
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F24—HEATING; RANGES; VENTILATING
- F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
- F24F2110/00—Control inputs relating to air properties
- F24F2110/30—Velocity
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F24—HEATING; RANGES; VENTILATING
- F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
- F24F2203/00—Devices or apparatus used for air treatment
- F24F2203/10—Rotary wheel
- F24F2203/1004—Bearings or driving means
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F24—HEATING; RANGES; VENTILATING
- F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
- F24F2203/00—Devices or apparatus used for air treatment
- F24F2203/10—Rotary wheel
- F24F2203/1016—Rotary wheel combined with another type of cooling principle, e.g. compression cycle
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F24—HEATING; RANGES; VENTILATING
- F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
- F24F2203/00—Devices or apparatus used for air treatment
- F24F2203/10—Rotary wheel
- F24F2203/1032—Desiccant wheel
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F24—HEATING; RANGES; VENTILATING
- F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
- F24F2203/00—Devices or apparatus used for air treatment
- F24F2203/10—Rotary wheel
- F24F2203/1056—Rotary wheel comprising a reheater
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F24—HEATING; RANGES; VENTILATING
- F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
- F24F2203/00—Devices or apparatus used for air treatment
- F24F2203/10—Rotary wheel
- F24F2203/1068—Rotary wheel comprising one rotor
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F24—HEATING; RANGES; VENTILATING
- F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
- F24F2203/00—Devices or apparatus used for air treatment
- F24F2203/10—Rotary wheel
- F24F2203/1084—Rotary wheel comprising two flow rotor segments
Definitions
- the subject invention generally pertains to HVAC systems and more specifically to an air conditioning system that includes a dehumidifying desiccant wheel.
- Energy wheels and desiccant wheels are two distinct types of wheels used in the HVAC industry.
- An energy wheel is a rotating, porous mass that functions as heat exchanger by transferring sensible heat from one air stream to another. With an energy wheel, half the wheel absorbs heat while the other half releases it. Examples of energy wheels are disclosed in U.S. Pat. Nos. 6,141,979 and 4,825,936.
- Desiccant wheels transfer moisture from one air stream to another, usually for the purpose of reducing humidity of a comfort zone.
- Examples of systems with desiccant wheels are disclosed in U.S. Pat. Nos. 6,311,511; 6,237,354; 5,887,784; 5,816,065; 5,732,562; 5,579,647; 5,551,245; 5,517,828 and 4,719,761.
- Another object of some embodiments is to start a refrigerant compressor and the rotation of a desiccant wheel regardless of the surrounding humidity, and then discontinue the wheel's rotation after a predetermined period, whereby the wheel, during the predetermined period, can reabsorb moisture that may have vaporized off an evaporator at startup.
- Another object of some embodiments is to discontinue the rotation of a desiccant wheel in response to a humidistat indicating that the humidity is below a certain level.
- Another object of some embodiments is to discontinue the rotation of a desiccant wheel in response to a thermostat indicating that the air temperature is above a certain level.
- Another object of some embodiments is to vary the rotational speed of a desiccant wheel in proportion to the airflow volume through the wheel.
- Another object of some embodiments is to vary the rotational speed of a desiccant wheel in proportion to the airflow volume through the wheel, wherein the airflow volume is determined based on a controller's speed command signal to a variable speed blower.
- Another object of some embodiments is to vary the rotational speed of a desiccant wheel in proportion to the airflow volume through the wheel, wherein the airflow volume is determined based on an airflow sensor.
- Another object of some embodiments is to preheat the air entering a desiccant wheel in response to a humidistat, wherein the preheating assists the wheel in reducing the humidity in situations where the rotational speed of the wheel is reduced due to lower airflow rates.
- Another object of some embodiments is to heat the air entering one portion of a desiccant wheel and cooling the air entering another portion of the wheel, wherein the heating is in response to a humidistat, and the cooling is in response to a temperature sensor.
- Another object of some embodiments is to decrease the cooling rate of a desiccant wheel system to meet a reduced sensible cooling demand, while maintaining or just slightly decreasing a heating rate to meet a latent heating demand.
- Another object of some embodiments is to install a heat recovery system upstream of a desiccant wheel to meet both a latent and sensible cooling demand.
- An air-to-air heat exchanger and a condenser/evaporator refrigerant circuit are just two examples of such a heat recovery system.
- Another object of some embodiments is to meet a latent cooling demand without having to preheat the incoming air or otherwise increase the sensible cooling demand.
- Another object of some embodiments is to provide an HVAC enclosure that conveys more airflow in some sections than others to accommodate the influx of both outside air and return air.
- Another object of some embodiments is to install a pre-dehumidifying heat recovery system upstream of the desiccant wheel to meet both a latent and sensible cooling demand.
- an HVAC system that includes a desiccant wheel, wherein the configuration and/or control of the system is such that the system takes full advantage of the wheel's ability to cool and dehumidify the air of a comfort zone under various conditions.
- FIG. 1 is a schematic diagram of one embodiment of an HVAC system that includes a desiccant wheel.
- FIG. 2 is a schematic diagram of a second embodiment of an HVAC system that includes a desiccant wheel.
- FIG. 3 is a schematic diagram of a third embodiment of an HVAC system that includes a desiccant wheel.
- FIG. 4 is a schematic diagram of a fourth embodiment of an HVAC system that includes a desiccant wheel.
- a refrigerant system 10 shown in FIG. 1 , is cycled on and off to meet a latent and/or sensible cooling demand, wherein a desiccant wheel 12 of the system operates for at least a predetermined period at the beginning of each cycle.
- a cooling coil 14 such as an evaporator of a refrigerant circuit
- Moisture which may have condensed on the surface of coil 14 during an earlier operating cycle, may later evaporate back into the air upon starting a new cycle. So, operating wheel 12 for a predetermined period at startup can help absorb that moisture before it raises the humidity of a comfort zone 18 , such as a room or other area of a building 20 .
- system 10 comprises an enclosure 22 that contains cooling coil 14 , desiccant wheel 12 driven by a motor 24 , a blower 26 , and a controller 28 .
- Enclosure 22 is schematically illustrated to represent any structure or combination of structures that can define an upstream air passageway 30 , an intermediate air passageway 32 , and a downstream air passageway 34 .
- enclosure 22 comprises a cabinet 22 A and a roof curb 22 B, wherein roof curb 22 B attaches cabinet 22 A to a roof of building 20 .
- enclosure 22 is shown having its two components, cabinet 22 A and roof curb 22 B, adjacent to each other, other embodiments may have an enclosure whose components are separated or interconnected by ductwork.
- Cooling coil 14 is schematically illustrated to represent any structure that can cool a stream of air by means of a chilled fluid from a chilled fluid source 33 .
- a chilled fluid source 33 for coil 14 include, but are not limited to, a conventional evaporator of a conventional refrigerant circuit, and a heat exchanger that conveys chilled water.
- Blower 26 is schematically illustrated to represent any apparatus that can move air 16 through enclosure 22 .
- blower 26 include, but are not limited to, a centrifugal fan, an axial fan, etc. Although blower 26 is shown disposed within intermediate air passageway 32 , blower 26 could be installed anywhere as long as it can move air 16 in an appropriate flow path through enclosure 22 .
- Desiccant wheel 12 is schematically illustrated to represent any rotatable, air-permeable structure that can absorb and release moisture from a stream of air 16 .
- Wheel 12 may comprise a honeycomb structure or porous pad or cage that contains or is coated with a desiccant, such as silica gel, montmorillonite clay, zeolite, etc.
- a desiccant such as silica gel, montmorillonite clay, zeolite, etc.
- the actual structure of various desiccant wheels are well know to those skilled in the art. Examples of desiccant wheels are disclosed in U.S. Pat. Nos.
- Controller 28 provides at least one output signal that cycles cooling coil 14 and blower 26 on and off to meet the cooling and/or dehumidification demand of comfort zone 18 .
- controller 28 provides an output signal 36 for selectively energizing or energizing the source 33 of chilled fluid and/or the cooling coil 14 (or its associated refrigerant compressor) and an output signal 38 for energizing blower 26 .
- Controller 28 also provides another output signal 40 for selectively energizing and de-energizing motor 24 of desiccant wheel 12 .
- Controller 28 is schematically illustrated to represent any device that can provide such output signals. Examples of controller 28 include, but are not limited to, an electromechanical relay circuit, thermostat, PLC (programmable logic controller), computer, microprocessor, analog/digital circuit, and various combinations thereof.
- blower 26 draws return air 16 A and/or outside air 16 B into intermediate air passageway 32 and across coil 14 , which provides latent and sensible cooling of the air.
- blower 26 forces the conditioned air from intermediate air passageway 32 through a portion of wheel 12 that absorbs moisture from supply air 16 C.
- Downstream air passageway 34 then conveys the relatively cool, dry supply 16 C to comfort zone 18 .
- Some of the air in zone 18 may escape building 20 through a vent 42 or other outlet, and the rest of the air becomes return air 16 A that blower 26 draws back into upstream air passageway 30 .
- wheel 12 rotates, wheel 12 carries the moisture it absorbed in downstream passageway 34 and releases the moisture to the return air 16 A passing through upstream air passageway 30 .
- controller 28 Upon initially activating the source 33 and/or cooling coil 14 and blower 26 at the beginning of each on-cycle, controller 28 actuates or rotates wheel 12 for a predetermined limited period, e.g., five or ten minutes, regardless of any current dehumidification need. During this period, wheel 12 can absorb moisture that the surface of coil 14 may have accumulated from a previous on-cycle and is currently evaporating from that surface. Such evaporation can be caused by air 16 passing across the surface of coil 14 before the coil is sufficiently cool to hold the moisture in a condensed state. With wheel 12 rotating at the beginning of every on-cycle, downstream air passageway 34 can immediately convey relatively dry supply air 16 C to comfort zone 18 .
- a predetermined limited period e.g., five or ten minutes
- signal 40 can de-activate wheel 12 , while cooling coil 14 and blower 26 continue operating to meet the sensible cooling demand of zone 18 . If, however, a humidistat 44 determines that a dehumidification demand exists after the predetermined period expires, signal 40 may command wheel 12 to continue operating.
- system 10 may have difficulty meeting the sensible cooling demand of zone 18 .
- Such an overload can be determined based on a thermostat 46 indicating that the zone temperature has risen to a certain level (e.g., two degrees above a target zone temperature) even though system 10 is still operating.
- signal 40 may de-activate wheel 12 until system 10 can satisfy the zone's sensible cooling demand.
- a refrigerant system 48 comprises desiccant wheel 12 , blower 26 , cooling coil 14 , an optional heater 50 , and an enclosure 52 .
- Enclosure 52 defines an upstream air passageway 54 , an intermediate air passageway 56 , and a downstream air passageway 58 .
- Blower 26 forces air sequentially through upstream passageway 54 , through heater 50 , through a first portion 12 A of wheel 12 that releases moisture to the air, into intermediate air passageway 56 , through blower 26 , through cooling coil 14 to provide latent and sensible cooling, through another portion 12 B of wheel 12 to absorb moisture from the air, into downstream passageway 58 , and onto a comfort zone.
- the air in downstream air passageway 58 is supply air, and the air in upstream air passageway 54 can be return air and/or outside air. In this case, wheel 12 transfers moisture from the supply air to the return air or outside air.
- System 48 is particularly suited for VAV systems where the cooling demand of a building is met by a system that delivers supply air at a variable air volume.
- a controller 60 similar to controller 28 , provides one or more output signals to system 48 .
- Output signal 62 controls the speed or airflow volume of blower 26
- an output signal 64 controls the rotational speed of wheel 12
- an output signal 66 controls cooling coil 14 (e.g., by selectively actuating its associated compressor)
- an output signal 68 controls the operation of heater 50 .
- controller 60 varies the air delivery of blower 26 by providing output signal 62 in response to an input signal 70 from a temperature sensor 72 .
- controller 60 provides output signal 64 such that the rotational speed of wheel 12 increases with the air volume.
- the wheel's speed is preferably adjusted to be proportional to the blower's speed or airflow volume.
- Controller 60 can determine the airflow volume by way of an input signal 74 from a conventional airflow sensor 76 . Alternatively, controller 60 can simply assume the airflow volume or blower speed agrees with output signal 62 , whereby flow sensor 76 can be omitted.
- Heater 50 which is optional, can be used for preheating the return air in situations where the rest of system 48 is unable to effectively dehumidify the air without excessively cooling the supply air to a level where the comfort zone begins feeling unpleasantly cold.
- Heater 50 can be a primary or auxiliary condenser of the same refrigerant circuit that contains cooling coil 14 , or heater 50 can be a separate heater, such as an electric heater, hot water coil, radiator, etc.
- the heat transfer rate between heater 50 and the current of air passing therethrough can remain constant or be reduced by a first delta-heat transfer rate, and the heat transfer rate between cooling coil 14 and the current of air passing therethrough can be reduced by a second delta-heat transfer rate, wherein the second delta-heat transfer rate is greater than the first delta-heat transfer rate.
- Deactivating or increasing the surface temperature of cooling coil 14 can be the primary cause of the second delta-heat transfer rate, while a decrease in airflow volume can cause the first delta-heat transfer rate. If, however, the airflow volume is not reduced, then the first delta-heat transfer rate may be substantially zero (i.e., the heat transfer rate of heater 68 remains substantially constant).
- FIG. 3 shows a system 78 that is similar to system 48 of FIG. 2 ; however, system 78 has a second cooling coil 80 and a heat recovery system 82 . With the heat recovery system and second cooling coil, system 78 can provide greater dehumidification with little or no auxiliary heat, i.e., heater 50 may be optional.
- System 78 includes blower 26 that forces air 84 through an enclosure 86 that defines various air passageways.
- blower 26 forces air 84 sequentially through an outside air inlet 88 , a cooling section 82 A of heat recovery system 82 , an intermediate air chamber 90 , cooling coil 80 , a heating section 82 B of heat recovery system 82 , an outside air outlet 92 , an upstream air passageway 94 where return air 84 A from a comfort zone and outside air 84 B can mix, optional heater 50 , a moisture-releasing section 12 A of desiccant wheel 12 , an intermediate air passageway 94 that contains blower 26 and cooling coil 14 , a moisture-absorbing section 12 B of wheel 12 , and a downstream air passageway 96 that discharges supply air 85 C to a comfort zone.
- system 78 From upstream air passageway 94 to downstream air passageway 96 , the function of system 78 is very similar to that of system 48 . To enhance dehumidification, however, system 78 employs cooling coil 80 and heat recovery system 82 . Cooling coil 80 removes moisture from the air, while heat recovery system 82 transfer heat from the air passing from outside air inlet 88 to intermediate air chamber 90 to the air passing from intermediate air chamber 90 to outside air outlet 92 , whereby the air moving from outside air outlet 92 to upstream air passageway 94 is cooler and drier than the air entering system 48 of FIG. 2 .
- the air in passageway 94 is not only drier but is also cooler than the air in passageway 94 is an important advantage over conventional systems that preheat or warm the air to achieve dehumidification.
- reheating the air increases the sensible cooling load.
- dehumidification can be achieved without increasing the sensible cooling load, thus the current system is more efficient.
- Heat recovery system 82 is schematically illustrated to represent any apparatus for transferring heat from one airstream to another.
- Heat recovery system 82 can be a conventional air-to-air heat exchanger or it can be the condenser and evaporator of a conventional refrigerant circuit.
- System 98 includes a refrigerant circuit that comprises a refrigerant compressor 100 , a condenser 102 , an expansion device 104 (e.g., a flow restriction, capillary, orifice, expansion valve, etc.), and an evaporator 106 .
- the refrigerant circuit operates in a conventional manner in that compressor 100 discharges hot pressurized refrigerant gas into condenser 102 .
- the refrigerant within condenser 102 condenses as the refrigerant releases heat to the surrounding air (the air passing from an intermediate chamber 90 ′ to an outside air outlet 92 ′).
- the condensed refrigerant cools by expansion by passing through expansion device 104 .
- the refrigerant then enters evaporator 106 where the relatively cool refrigerant absorbs heat from the incoming outside air.
- the refrigerant returns to the inlet of compressor 100 to be compressed again.
- the refrigerant circuit transfers heat from the air passing through evaporator 106 to the air passing through condenser 102 .
- upstream air passageway 94 conveys a mixture of outside air 84 B and return air 84 A, in some embodiments there is no return air, only outside air. In such cases, the airflow volume through intermediate air chamber 90 or 90 ′ is substantially equal to that of intermediate air passageway 94 . If, however, enclosure 86 or 86 ′ receives both outside air and return air, then intermediate air passageway 94 conveys more air than does intermediate air chamber 90 or 90 ′. Any excess air can be released from the building through some sort of exhaust or other opening in the building.
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Abstract
Description
- 1. Field of the Invention
- The subject invention generally pertains to HVAC systems and more specifically to an air conditioning system that includes a dehumidifying desiccant wheel.
- 2. Description of Related Art
- Energy wheels and desiccant wheels are two distinct types of wheels used in the HVAC industry. An energy wheel is a rotating, porous mass that functions as heat exchanger by transferring sensible heat from one air stream to another. With an energy wheel, half the wheel absorbs heat while the other half releases it. Examples of energy wheels are disclosed in U.S. Pat. Nos. 6,141,979 and 4,825,936.
- Desiccant wheels, on the other hand, transfer moisture from one air stream to another, usually for the purpose of reducing humidity of a comfort zone. Examples of systems with desiccant wheels are disclosed in U.S. Pat. Nos. 6,311,511; 6,237,354; 5,887,784; 5,816,065; 5,732,562; 5,579,647; 5,551,245; 5,517,828 and 4,719,761.
- Although many air conditioning systems that are enhanced with desiccant wheels have been developed, such systems often implement the use of desiccant wheels whenever there is a dehumidification load. However many air conditioning systems may be most efficient if the desiccant wheel is only utilized at part load conditions or when the load on the system shifts from a sensible cooling load to more of a latent cooling or dehumidification load. Current systems often fail to address these efficiency concerns. Moreover, current systems with desiccant wheels often disregard a critical period when the refrigerant system is first activated. At startup, it takes a moment for the refrigerant system's evaporator to become sufficiently cold to remove moisture from the air. So, when the refrigerant system is first energized and before the evaporator becomes cold, condensed water on the surface of the evaporator may actually evaporate into the air, which can increase the humidity of the comfort zone.
- Consequently, a need exists for air conditioning systems that are enhanced with desiccant wheels that address efficiency concerns at part load operation for variable air volume systems.
- It is a primary object of the invention to improve an HVAC system's overall effectiveness by configuring the system with a desiccant wheel in a manner that takes full advantage of the wheel's ability to reduce humidity over a variety of operating conditions.
- Another object of some embodiments is to start a refrigerant compressor and the rotation of a desiccant wheel regardless of the surrounding humidity, and then discontinue the wheel's rotation after a predetermined period, whereby the wheel, during the predetermined period, can reabsorb moisture that may have vaporized off an evaporator at startup.
- Another object of some embodiments is to discontinue the rotation of a desiccant wheel in response to a humidistat indicating that the humidity is below a certain level.
- Another object of some embodiments is to discontinue the rotation of a desiccant wheel in response to a thermostat indicating that the air temperature is above a certain level.
- Another object of some embodiments is to vary the rotational speed of a desiccant wheel in proportion to the airflow volume through the wheel.
- Another object of some embodiments is to vary the rotational speed of a desiccant wheel in proportion to the airflow volume through the wheel, wherein the airflow volume is determined based on a controller's speed command signal to a variable speed blower.
- Another object of some embodiments is to vary the rotational speed of a desiccant wheel in proportion to the airflow volume through the wheel, wherein the airflow volume is determined based on an airflow sensor.
- Another object of some embodiments is to preheat the air entering a desiccant wheel in response to a humidistat, wherein the preheating assists the wheel in reducing the humidity in situations where the rotational speed of the wheel is reduced due to lower airflow rates.
- Another object of some embodiments is to heat the air entering one portion of a desiccant wheel and cooling the air entering another portion of the wheel, wherein the heating is in response to a humidistat, and the cooling is in response to a temperature sensor.
- Another object of some embodiments is to decrease the cooling rate of a desiccant wheel system to meet a reduced sensible cooling demand, while maintaining or just slightly decreasing a heating rate to meet a latent heating demand.
- Another object of some embodiments is to install a heat recovery system upstream of a desiccant wheel to meet both a latent and sensible cooling demand. An air-to-air heat exchanger and a condenser/evaporator refrigerant circuit are just two examples of such a heat recovery system.
- Another object of some embodiments is to meet a latent cooling demand without having to preheat the incoming air or otherwise increase the sensible cooling demand.
- Another object of some embodiments is to provide an HVAC enclosure that conveys more airflow in some sections than others to accommodate the influx of both outside air and return air.
- Another object of some embodiments is to install a pre-dehumidifying heat recovery system upstream of the desiccant wheel to meet both a latent and sensible cooling demand.
- One or more of these and/or other objects of the invention are provided by an HVAC system that includes a desiccant wheel, wherein the configuration and/or control of the system is such that the system takes full advantage of the wheel's ability to cool and dehumidify the air of a comfort zone under various conditions.
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FIG. 1 is a schematic diagram of one embodiment of an HVAC system that includes a desiccant wheel. -
FIG. 2 is a schematic diagram of a second embodiment of an HVAC system that includes a desiccant wheel. -
FIG. 3 is a schematic diagram of a third embodiment of an HVAC system that includes a desiccant wheel. -
FIG. 4 is a schematic diagram of a fourth embodiment of an HVAC system that includes a desiccant wheel. - A
refrigerant system 10, shown inFIG. 1 , is cycled on and off to meet a latent and/or sensible cooling demand, wherein adesiccant wheel 12 of the system operates for at least a predetermined period at the beginning of each cycle. At the start of each cycle, it can take a moment for acooling coil 14, such as an evaporator of a refrigerant circuit, to become sufficiently cool to condense moisture from theair 16. Moisture, which may have condensed on the surface ofcoil 14 during an earlier operating cycle, may later evaporate back into the air upon starting a new cycle. So, operatingwheel 12 for a predetermined period at startup can help absorb that moisture before it raises the humidity of acomfort zone 18, such as a room or other area of abuilding 20. - For the illustrated embodiment,
system 10 comprises anenclosure 22 that containscooling coil 14,desiccant wheel 12 driven by amotor 24, ablower 26, and a controller 28. -
Enclosure 22 is schematically illustrated to represent any structure or combination of structures that can define anupstream air passageway 30, anintermediate air passageway 32, and adownstream air passageway 34. In this example,enclosure 22 comprises acabinet 22A and aroof curb 22B, whereinroof curb 22B attachescabinet 22A to a roof ofbuilding 20. Althoughenclosure 22 is shown having its two components,cabinet 22A androof curb 22B, adjacent to each other, other embodiments may have an enclosure whose components are separated or interconnected by ductwork. -
Cooling coil 14 is schematically illustrated to represent any structure that can cool a stream of air by means of a chilled fluid from a chilledfluid source 33. Examples of a chilledfluid source 33 forcoil 14 include, but are not limited to, a conventional evaporator of a conventional refrigerant circuit, and a heat exchanger that conveys chilled water. - Blower 26 is schematically illustrated to represent any apparatus that can move
air 16 throughenclosure 22. Examples ofblower 26 include, but are not limited to, a centrifugal fan, an axial fan, etc. Althoughblower 26 is shown disposed withinintermediate air passageway 32,blower 26 could be installed anywhere as long as it can moveair 16 in an appropriate flow path throughenclosure 22. -
Desiccant wheel 12 is schematically illustrated to represent any rotatable, air-permeable structure that can absorb and release moisture from a stream ofair 16.Wheel 12, for example, may comprise a honeycomb structure or porous pad or cage that contains or is coated with a desiccant, such as silica gel, montmorillonite clay, zeolite, etc. The actual structure of various desiccant wheels are well know to those skilled in the art. Examples of desiccant wheels are disclosed in U.S. Pat. Nos. 6,311,511; 6,237,354; 5,887,784; 5,816,065; 5,732,562; 5,579,647; 5,551,245; 5,517,828 and 4,719,761, all of which are specifically incorporated by reference herein. - Controller 28 provides at least one output signal that
cycles cooling coil 14 andblower 26 on and off to meet the cooling and/or dehumidification demand ofcomfort zone 18. In this example, controller 28 provides anoutput signal 36 for selectively energizing or energizing thesource 33 of chilled fluid and/or the cooling coil 14 (or its associated refrigerant compressor) and anoutput signal 38 for energizingblower 26. Controller 28 also provides anotheroutput signal 40 for selectively energizing and de-energizingmotor 24 ofdesiccant wheel 12. Controller 28 is schematically illustrated to represent any device that can provide such output signals. Examples of controller 28 include, but are not limited to, an electromechanical relay circuit, thermostat, PLC (programmable logic controller), computer, microprocessor, analog/digital circuit, and various combinations thereof. - Under normal operation,
blower 26 draws returnair 16A and/oroutside air 16B intointermediate air passageway 32 and acrosscoil 14, which provides latent and sensible cooling of the air. Next,blower 26 forces the conditioned air fromintermediate air passageway 32 through a portion ofwheel 12 that absorbs moisture fromsupply air 16C.Downstream air passageway 34 then conveys the relatively cool,dry supply 16C tocomfort zone 18. Some of the air inzone 18 may escape building 20 through avent 42 or other outlet, and the rest of the air becomesreturn air 16A thatblower 26 draws back intoupstream air passageway 30. Aswheel 12 rotates,wheel 12 carries the moisture it absorbed indownstream passageway 34 and releases the moisture to thereturn air 16A passing throughupstream air passageway 30. - Upon initially activating the
source 33 and/or coolingcoil 14 andblower 26 at the beginning of each on-cycle, controller 28 actuates or rotateswheel 12 for a predetermined limited period, e.g., five or ten minutes, regardless of any current dehumidification need. During this period,wheel 12 can absorb moisture that the surface ofcoil 14 may have accumulated from a previous on-cycle and is currently evaporating from that surface. Such evaporation can be caused byair 16 passing across the surface ofcoil 14 before the coil is sufficiently cool to hold the moisture in a condensed state. Withwheel 12 rotating at the beginning of every on-cycle,downstream air passageway 34 can immediately convey relativelydry supply air 16C tocomfort zone 18. - Once the predetermined period expires, signal 40 can de-activate
wheel 12, while coolingcoil 14 andblower 26 continue operating to meet the sensible cooling demand ofzone 18. If, however, ahumidistat 44 determines that a dehumidification demand exists after the predetermined period expires, signal 40 may commandwheel 12 to continue operating. - In some
cases system 10 may have difficulty meeting the sensible cooling demand ofzone 18. Such an overload can be determined based on athermostat 46 indicating that the zone temperature has risen to a certain level (e.g., two degrees above a target zone temperature) even thoughsystem 10 is still operating. In such situations, signal 40 may de-activatewheel 12 untilsystem 10 can satisfy the zone's sensible cooling demand. - In another embodiment, shown in
FIG. 2 , arefrigerant system 48 comprisesdesiccant wheel 12,blower 26, coolingcoil 14, anoptional heater 50, and anenclosure 52.Enclosure 52 defines anupstream air passageway 54, anintermediate air passageway 56, and adownstream air passageway 58.Blower 26 forces air sequentially throughupstream passageway 54, throughheater 50, through afirst portion 12A ofwheel 12 that releases moisture to the air, intointermediate air passageway 56, throughblower 26, through coolingcoil 14 to provide latent and sensible cooling, through another portion 12B ofwheel 12 to absorb moisture from the air, intodownstream passageway 58, and onto a comfort zone. The air indownstream air passageway 58 is supply air, and the air inupstream air passageway 54 can be return air and/or outside air. In this case,wheel 12 transfers moisture from the supply air to the return air or outside air. -
System 48 is particularly suited for VAV systems where the cooling demand of a building is met by a system that delivers supply air at a variable air volume. Acontroller 60, similar to controller 28, provides one or more output signals tosystem 48.Output signal 62, for example, controls the speed or airflow volume ofblower 26, anoutput signal 64 controls the rotational speed ofwheel 12, anoutput signal 66 controls cooling coil 14 (e.g., by selectively actuating its associated compressor), and anoutput signal 68 controls the operation ofheater 50. To meet the building's cooling needs,controller 60 varies the air delivery ofblower 26 by providingoutput signal 62 in response to aninput signal 70 from atemperature sensor 72. - To help maintain the wheel's efficiency over a range of airflow volumes,
controller 60 providesoutput signal 64 such that the rotational speed ofwheel 12 increases with the air volume. The wheel's speed is preferably adjusted to be proportional to the blower's speed or airflow volume.Controller 60 can determine the airflow volume by way of aninput signal 74 from aconventional airflow sensor 76. Alternatively,controller 60 can simply assume the airflow volume or blower speed agrees withoutput signal 62, wherebyflow sensor 76 can be omitted. -
Heater 50, which is optional, can be used for preheating the return air in situations where the rest ofsystem 48 is unable to effectively dehumidify the air without excessively cooling the supply air to a level where the comfort zone begins feeling unpleasantly cold.Heater 50 can be a primary or auxiliary condenser of the same refrigerant circuit that contains coolingcoil 14, orheater 50 can be a separate heater, such as an electric heater, hot water coil, radiator, etc. - In some cases where the sensible cooling demand drops significantly while the latent cooling demand remains high, the heat transfer rate between
heater 50 and the current of air passing therethrough can remain constant or be reduced by a first delta-heat transfer rate, and the heat transfer rate between coolingcoil 14 and the current of air passing therethrough can be reduced by a second delta-heat transfer rate, wherein the second delta-heat transfer rate is greater than the first delta-heat transfer rate. Deactivating or increasing the surface temperature of coolingcoil 14 can be the primary cause of the second delta-heat transfer rate, while a decrease in airflow volume can cause the first delta-heat transfer rate. If, however, the airflow volume is not reduced, then the first delta-heat transfer rate may be substantially zero (i.e., the heat transfer rate ofheater 68 remains substantially constant). -
FIG. 3 shows asystem 78 that is similar tosystem 48 ofFIG. 2 ; however,system 78 has asecond cooling coil 80 and aheat recovery system 82. With the heat recovery system and second cooling coil,system 78 can provide greater dehumidification with little or no auxiliary heat, i.e.,heater 50 may be optional. -
System 78 includesblower 26 that forcesair 84 through anenclosure 86 that defines various air passageways. In some embodiments,blower 26forces air 84 sequentially through anoutside air inlet 88, acooling section 82A ofheat recovery system 82, anintermediate air chamber 90, coolingcoil 80, aheating section 82B ofheat recovery system 82, anoutside air outlet 92, anupstream air passageway 94 wherereturn air 84A from a comfort zone and outsideair 84B can mix,optional heater 50, a moisture-releasingsection 12A ofdesiccant wheel 12, anintermediate air passageway 94 that containsblower 26 and coolingcoil 14, a moisture-absorbing section 12B ofwheel 12, and adownstream air passageway 96 that discharges supply air 85C to a comfort zone. - From
upstream air passageway 94 todownstream air passageway 96, the function ofsystem 78 is very similar to that ofsystem 48. To enhance dehumidification, however,system 78 employs coolingcoil 80 andheat recovery system 82. Coolingcoil 80 removes moisture from the air, whileheat recovery system 82 transfer heat from the air passing fromoutside air inlet 88 tointermediate air chamber 90 to the air passing fromintermediate air chamber 90 tooutside air outlet 92, whereby the air moving fromoutside air outlet 92 toupstream air passageway 94 is cooler and drier than theair entering system 48 ofFIG. 2 . - The fact that the air in
passageway 94 is not only drier but is also cooler than the air inpassageway 94 is an important advantage over conventional systems that preheat or warm the air to achieve dehumidification. With conventional systems, reheating the air increases the sensible cooling load. With the current system, however, dehumidification can be achieved without increasing the sensible cooling load, thus the current system is more efficient. -
Heat recovery system 82 is schematically illustrated to represent any apparatus for transferring heat from one airstream to another.Heat recovery system 82, for example, can be a conventional air-to-air heat exchanger or it can be the condenser and evaporator of a conventional refrigerant circuit. - Such a refrigerant circuit is incorporated into a
system 98 that is illustrated inFIG. 4 .System 98 includes a refrigerant circuit that comprises arefrigerant compressor 100, acondenser 102, an expansion device 104 (e.g., a flow restriction, capillary, orifice, expansion valve, etc.), and anevaporator 106. The refrigerant circuit operates in a conventional manner in thatcompressor 100 discharges hot pressurized refrigerant gas intocondenser 102. The refrigerant withincondenser 102 condenses as the refrigerant releases heat to the surrounding air (the air passing from anintermediate chamber 90′ to anoutside air outlet 92′). Fromcondenser 102, the condensed refrigerant cools by expansion by passing throughexpansion device 104. The refrigerant then entersevaporator 106 where the relatively cool refrigerant absorbs heat from the incoming outside air. Fromevaporator 106, the refrigerant returns to the inlet ofcompressor 100 to be compressed again. As a result, the refrigerant circuit transfers heat from the air passing throughevaporator 106 to the air passing throughcondenser 102. - It should be noted, that although
upstream air passageway 94 conveys a mixture ofoutside air 84B and returnair 84A, in some embodiments there is no return air, only outside air. In such cases, the airflow volume throughintermediate air chamber intermediate air passageway 94. If, however,enclosure intermediate air passageway 94 conveys more air than doesintermediate air chamber - Although the invention is described with reference to a preferred embodiment, it should be appreciated by those skilled in the art that various modifications are well within the scope of the invention. Therefore, the scope of the invention is to be determined by reference to the following claims:
Claims (33)
Priority Applications (5)
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US10/855,912 US6973795B1 (en) | 2004-05-27 | 2004-05-27 | HVAC desiccant wheel system and method |
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US11/332,652 US7178355B2 (en) | 2004-05-27 | 2006-01-17 | HVAC desiccant wheel system and method |
US11/639,573 US7389646B2 (en) | 2004-05-27 | 2006-12-18 | HVAC desiccant wheel system and method |
US11/645,164 US7340906B2 (en) | 2004-05-27 | 2006-12-26 | HVAC desiccant wheel system and method |
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US10/855,912 US6973795B1 (en) | 2004-05-27 | 2004-05-27 | HVAC desiccant wheel system and method |
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US11/332,652 Expired - Lifetime US7178355B2 (en) | 2004-05-27 | 2006-01-17 | HVAC desiccant wheel system and method |
US11/639,573 Expired - Lifetime US7389646B2 (en) | 2004-05-27 | 2006-12-18 | HVAC desiccant wheel system and method |
US11/645,164 Expired - Lifetime US7340906B2 (en) | 2004-05-27 | 2006-12-26 | HVAC desiccant wheel system and method |
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US11/639,573 Expired - Lifetime US7389646B2 (en) | 2004-05-27 | 2006-12-18 | HVAC desiccant wheel system and method |
US11/645,164 Expired - Lifetime US7340906B2 (en) | 2004-05-27 | 2006-12-26 | HVAC desiccant wheel system and method |
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Also Published As
Publication number | Publication date |
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US7340906B2 (en) | 2008-03-11 |
US20060117781A1 (en) | 2006-06-08 |
US7389646B2 (en) | 2008-06-24 |
US6973795B1 (en) | 2005-12-13 |
US20070113573A1 (en) | 2007-05-24 |
US20070101743A1 (en) | 2007-05-10 |
US20050268635A1 (en) | 2005-12-08 |
US7178355B2 (en) | 2007-02-20 |
US7017356B2 (en) | 2006-03-28 |
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