JP2020106265A - Split dehumidification system with secondary evaporator coil and condenser coil - Google Patents

Abstract

To provide a dehumidification system.SOLUTION: A dehumidification system includes a compressor, a primary evaporator, a primary condenser, a secondary evaporator and a secondary condenser. The secondary evaporator receives an inlet airflow and outputs a first airflow to the primary evaporator. The primary evaporator receives the first airflow and outputs a second airflow to the secondary condenser. The secondary condenser receives the second airflow and outputs a third airflow to the primary condenser. The primary condenser receives the third airflow and outputs a dehumidified airflow. The compressor receives a flow of refrigerant from the primary evaporator and supplies the flow of refrigerant to the primary condenser.SELECTED DRAWING: Figure 3

Description

(Cross-reference of related applications)
This application is a continuation-in-part application claiming priority to US Nonprovisional Application No. 15/460,772 filed on March 16, 2017 by Dwaine Walter Tucker et al., entitled "DHUMIDIFIER WITH SECONDARY EVAPORATOR AND CONDENSER COILS". , Which is incorporated herein by reference in its entirety.

The present invention relates generally to dehumidification, and more particularly to dehumidifiers that include a secondary evaporator and condenser coil.

In some situations it is desirable to reduce the humidity of the air in the structure. For example, in fire and flood recovery applications, it may be desirable to quickly remove water from areas of damaged structure. To achieve this, one or more portable dehumidifiers may be installed in the structure to direct dry air to the damaged area of the water. However, current dehumidifiers have proven inefficient in many respects.

According to embodiments of the present disclosure, the drawbacks and problems associated with conventional systems may be reduced or eliminated.

In certain embodiments, the dehumidification system includes a compressor, a primary evaporator, a primary condenser, a secondary evaporator, and a secondary condenser. The secondary evaporator receives an inlet airflow and outputs a first airflow to the primary evaporator. The primary evaporator receives the first air stream and discharges the second air stream to the secondary condenser. The secondary condenser receives the second air stream and discharges the third air stream to the primary condenser. The primary condenser receives the third air stream and discharges the dehumidified air stream. The compressor receives a low-temperature, low-pressure refrigerant vapor flow from the primary evaporator and supplies a high-temperature, high-pressure refrigerant vapor flow to the primary condenser.

Certain embodiments of the present disclosure may provide one or more technical advantages. For example, certain embodiments include two evaporators, two condensers, and two metering devices that utilize a closed refrigeration loop. This configuration causes some of the refrigerant in the system to evaporate and condense twice in one cooling cycle, thereby increasing the compressor capacity for a typical system without adding additional power to the compressor. .. This improves the overall efficiency of the system by providing more dehumidification per kilowatt of power used. The low humidity exhaust airflow allows for increased drying capacity, which may be beneficial in certain applications, such as fire and flood remediation.

Particular embodiments of the present disclosure may include some, all, or none of the above advantages. One or more other technical advantages may be readily apparent to one skilled in the art from the figures, description, and claims included herein.

To provide a more complete understanding of the present invention and its features and advantages, reference is made to the following description in conjunction with the accompanying drawings.

6 illustrates an example of an exemplary split system for reducing the humidity of air in a structure, according to certain embodiments. 6 illustrates an exemplary portable system for reducing the humidity of air in a structure, according to certain embodiments. 3 illustrates an exemplary dehumidification system that can be used by the systems of FIGS. 1 and 2 to reduce the humidity of air in a structure, according to certain embodiments. 3 illustrates an exemplary dehumidification system that can be used by the systems of FIGS. 1 and 2 to reduce the humidity of air in a structure, according to certain embodiments. 3 illustrates an exemplary dehumidification method that can be used by the systems of FIGS. 1 and 2 to reduce the humidity of air in a structure, according to certain embodiments. 1 illustrates an exemplary dehumidification system, according to certain embodiments. 6 illustrates an exemplary capacitor system for use with the systems described herein, according to certain embodiments. 1 illustrates an exemplary dehumidification system, according to certain embodiments. 6 illustrates an example of a single coil pack for use with the systems described herein, according to certain embodiments. 6 illustrates an example of a single coil pack for use with the systems described herein, according to certain embodiments. 6 illustrates an example of a primary evaporator with three circuits for use in the systems described herein, according to certain embodiments. 6 illustrates an example of a primary evaporator with three circuits for use in the systems described herein, according to certain embodiments. 6 illustrates an example of a primary evaporator with three circuits for use in the systems described herein, according to certain embodiments. 6 illustrates an example of a primary evaporator with three circuits for use in the systems described herein, according to certain embodiments.

In some situations it is desirable to reduce the humidity of the air in the structure. For example, in fire and flood recovery applications, it is desirable to remove water from a damaged structure by placing one or more portable dehumidification units within the structure. As another example, in areas that experience high humidity levels of weather, or in buildings where low humidity levels are required (eg, libraries), it may be desirable to install a dehumidification unit within the central air conditioning system. Moreover, in some commercial applications it may be necessary to maintain the desired humidity level. However, current dehumidifiers have proven to be inadequate or inefficient in many respects.

To address the inefficiencies and other issues in current dehumidification systems, the disclosed embodiments provide a dehumidification system that includes a secondary evaporator and a secondary condenser, which provides a Part is evaporated and condensed twice in one cooling cycle. This increases compressor capacity for a typical system without adding additional power to the compressor. This improves the overall efficiency of the system by providing more dehumidification per kilowatt of power used.

FIG. 1 illustrates an exemplary dehumidification system 100 for supplying dehumidified air 106 to a structure 102, according to certain embodiments. Dehumidification system 100 includes an evaporator system 104 disposed within structure 102. Structure 102 may include all or part of a building or other suitable enclosed space, such as an apartment house, hotel, office space, commercial building, or private residence (eg, home). The evaporator system 104 receives inlet air 101 from within the structure 102, reduces moisture in the received intake air 101, and supplies dehumidified air 106 back to the structure 102. Evaporator system 104 may distribute dehumidified air 106 throughout structure 102 via an air duct, as shown.

Generally, the dehumidification system 100 is a separation system in which an evaporator system 104 is coupled to a remote condenser system 108 located outside the structure 102. The remote condenser system 108 may include a condenser unit 112 and a compressor unit 114 that facilitates the functioning of the evaporator system 104 by treating the flow of refrigerant as part of the refrigeration cycle. The refrigerant stream may include any suitable cooling material such as R410a refrigerant. In particular embodiments, compressor unit 114 may receive a flow of refrigerant vapor from evaporator system 104 via refrigerant line 116. The compressor unit 114 may pressurize the flow of refrigerant, thereby increasing the temperature of the refrigerant. The compressor speed may be adjusted to achieve the desired operating characteristics. The condenser unit 112 may receive a pressurized flow of refrigerant vapor from the compressor unit 114 and cool the pressurized refrigerant by promoting heat transfer from the refrigerant flow to the outside air outside the structure 102. In particular embodiments, remote condenser system 108 may utilize a heat exchanger, such as a microchannel heat exchanger, to remove heat from the refrigerant stream. The remote condenser system 108 may include a fan that draws ambient air from the outer structure 102 for use in cooling the flow of refrigerant. In certain embodiments, the speed of this fan is adjusted to achieve the desired operating characteristics. An exemplary embodiment of an exemplary capacitor system is shown, for example, in FIG. 7 (discussed in more detail below).

After being cooled by the condenser unit 112 and condensed into a liquid, the flow of the refrigerant moves to the evaporator system 104 via the refrigerant line 118. In certain embodiments, the refrigerant flow may be received by an expansion device (described below) that reduces the pressure of the refrigerant stream, thereby reducing the temperature of the refrigerant stream. The evaporator unit of evaporator system 104 (discussed in more detail below) may receive a flow of refrigerant from the expander and use the flow of refrigerant to dehumidify and cool the incoming airflow. The refrigerant flow then returns to the remote condenser system 108 and the cycle may repeat.

In particular embodiments, evaporator system 104 may be installed in series with an air mover. The blower may include a fan that blows air from one location to another. The blower may facilitate distribution of outgoing air from the evaporator system 104 to various parts of the structure 102. The blower and evaporator system 104 can have a separate return port through which air is aspirated. In certain embodiments, the exhaust air from evaporator system 104 may be mixed with air produced by another component (eg, an air conditioner) and blown through an air duct by a blower. In other embodiments, the evaporator system 104 can both cool and dehumidify, and thus can be used without conventional air conditioners.

Although particular embodiments of dehumidification system 100 are shown and described primarily, the present disclosure contemplates any suitable implementation of dehumidification system 100 according to particular needs. Further, although the various components of dehumidification system 100 are illustrated as located in particular locations, the present disclosure contemplates that these components may be located in any suitable location according to particular needs. Is intended.

FIG. 2 illustrates an exemplary portable dehumidification system 200 for reducing the humidity of air within structure 102, according to certain embodiments of the present disclosure. The dehumidification system 200 can be located anywhere within the structure 102 to direct the dehumidified air 106 to areas that require dehumidification (eg, water loss areas). Generally, the dehumidification system 200 receives an intake air stream 101, removes water from the intake air stream 101, and emits dehumidified air 106 back to the structure 102. In particular embodiments, structure 102 includes spaces that have been damaged by water (eg, as a result of a flood or fire). To restore the water-damaged structure 102, one or more dehumidification systems 200 quickly reduce the humidity of the air within the structure 102 and dry portions of the water-damaged structure 102. Can be strategically placed within structure 102.

Although a particular implementation of the portable dehumidification system 200 is shown and described primarily, the present disclosure contemplates any suitable implementation of the portable dehumidification system 200 according to the particular needs. Further, while the various components of portable dehumidification system 200 are illustrated as being located in particular locations within structure 102, the present disclosure is in accordance with particular needs that these components be in any suitable location. Intended to be located.

3 and 4 show an exemplary dehumidification system 300 that may be used by the dehumidification system 100 of FIGS. 1 and 2 and the portable dehumidification system 200 to reduce the humidity of the air within the structure 102. Dehumidification system 300 includes a primary evaporator 310, a primary condenser 330, a secondary evaporator 340, a secondary condenser 320, a compressor 360, a primary metering device 380, a secondary metering device 390, and a fan 370. In some embodiments, the dehumidification system 300 may additionally include a sub-cooling coil 350. In particular embodiments, subcooling coil 350 and primary capacitor 330 are combined into a single coil. The flow of refrigerant 305 is circulated through the dehumidification system 300 as shown. Generally, the dehumidification system 300 receives an intake air stream 101, removes water from the intake air stream 101, and discharges dehumidified air 106. Water is removed from the intake air 101 using a cooling cycle of the flow of refrigerant 305. However, by including the secondary evaporator 340 and the secondary condenser 320, the dehumidification system 300 causes at least a portion of the refrigerant 305 flow to evaporate and condense twice in a single cooling cycle. This increases the cooling capacity for a typical system without adding additional power to the compressor, thereby increasing the overall dehumidification efficiency of the system.

Generally, the dehumidification system 300 attempts to match the saturation temperature of the secondary evaporator 340 to the saturation temperature of the secondary capacitor 320. The saturation temperature of the secondary evaporator 340 and the secondary condenser 320 is generally controlled according to the formula (temperature of the intake air 101+temperature of the second air flow 315)/2. Evaporation occurs in the secondary evaporator 340 because the saturation temperature of the secondary evaporator 340 is lower than that of the intake air 101. The saturation temperature of the secondary condenser 320 is higher than that of the second air stream 315, so that condensation occurs in the secondary condenser 320. The amount of the refrigerant 305 evaporated in the secondary evaporator 340 is substantially equal to the amount condensed in the secondary condenser 320. Primary evaporator 310 receives the flow of refrigerant 305 from secondary metering device 390 and discharges the flow of refrigerant 305 to compressor 360. The primary evaporator 310 can be any type of coil (eg, fin tube, microchannel, etc.). Primary evaporator 310 receives first air stream 345 from secondary evaporator 340 and discharges second air stream 315 to secondary condenser 320. The second air stream 315 is generally at a lower temperature than the first air stream 345. To cool the incoming first air stream 345, the primary evaporator 310 transfers heat from the first air stream 345 to a stream of the refrigerant 305, thereby at least partially liquefying the stream of the refrigerant 305. To vaporize to gas. This transfer of heat from the first air stream 345 to the refrigerant 305 stream also removes water from the first air stream 345.

Secondary condenser 320 receives the flow of refrigerant 305 from secondary evaporator 340 and discharges the flow of refrigerant 305 to secondary metering device 390. Secondary capacitor 320 can be any type of coil (eg, fin tube, microchannel, etc.). The secondary condenser 320 receives the second air stream 315 from the primary evaporator 310 and discharges the third air stream 325. The third air stream 325 is generally warmer and drier (ie, has the same dew point but lower relative humidity) than the second air stream 315. The secondary condenser 320 produces a third air stream 325 by transferring heat from the stream of refrigerant 305 to a second air stream 315, thereby condensing the stream of refrigerant 305 at least partially from a gas to a liquid. Let

Primary condenser 330 receives the flow of refrigerant 305 from compressor 360 and discharges the flow of refrigerant 305 to either primary metering device 380 or subcooling coil 350. The primary capacitor 330 can be any type of coil (eg, fin tube, microchannel, etc.). Primary condenser 330 receives either third air flow 325 or fourth air flow 355 and discharges dehumidified air 106. Dehumidified air 106 is generally warmer and drier (ie, has a lower relative humidity) than third air flow 325 and fourth air flow 355. Primary condenser 330 produces dehumidified air 106 by transferring heat from the flow of refrigerant 305, thereby condensing the flow of refrigerant 305 at least partially from a gas to a liquid. In some embodiments, the primary condenser 330 fully condenses the flow of refrigerant 305 into a liquid (ie, 100% liquid). In other embodiments, the primary condenser 330 partially condenses the flow of refrigerant 305 into a liquid (ie, less than 100% liquid). In a particular embodiment, as shown in FIG. 4, a portion of the primary condenser 330 receives a separate airflow in addition to the airflow 101. For example, the rightmost end of the primary capacitor 330 of FIG. 4 extends or overhangs beyond the right end of the secondary evaporator 340, the primary evaporator 310, the secondary capacitor 320, and the subcooling coil 350. This overhanging portion of primary capacitor 330 may receive an additional, separate air stream.

Secondary evaporator 340 receives the flow of refrigerant 305 from primary metering device 380 and discharges the flow of refrigerant 305 to secondary condenser 320. The secondary evaporator 340 can be any type of coil (eg, fin tube, microchannel, etc.). Secondary evaporator 340 receives intake air 101 and discharges first air stream 345 to primary evaporator 310. The first air stream 345 is generally cooler than the intake air 101. To cool the incoming intake air 101, the secondary evaporator 340 transfers heat from the intake air 101 to the flow of refrigerant 305, thereby at least partially evaporating the flow of refrigerant 305 from liquid to gas.

An optional component of dehumidification system 300, sub-cooling coil 350, sub-cools liquid refrigerant 305 as it exits primary condenser 330. This in turn supplies the primary metering device 380 with a liquid refrigerant that is cooled to 30 degrees (or more) than before it entered the sub-cooling coil 350. For example, if the flow of refrigerant 305 entering subcooling coil 350 is 340 psig/105°F/60% vapor, the flow of refrigerant 305 will be 340 psig/80°F/0% as it exits subcooling coil 350. It can be steam. The sub-cooled refrigerant 305 has a higher thermal enthalpy coefficient as well as a higher density, resulting in a reduced cycle time and frequency of the vaporization cycle of the refrigerant 305 stream. This results in higher efficiency of dehumidification system 300 and less energy use. Embodiments of dehumidification system 300 may or may not include subcooling coil 350. For example, an embodiment of a dehumidification system 300 utilized within a portable dehumidification system 200 having a microchannel condenser 330 or 320 may include a sub-cooling coil 350, while a dehumidification system utilizing another type of condenser 330 or 320. The embodiment of 300 may not include the sub-cooling coil 350. As another example, dehumidification system 300 utilized within a separation system, such as dehumidification system 100, may not include subcooling coil 350.

Compressor 360 pressurizes the flow of refrigerant 305, thereby increasing the temperature of refrigerant 305. For example, if the refrigerant 305 flow entering the compressor 360 is 128 psig/52°F/100% steam, the refrigerant 305 flow may be 340 psig/150°F/100% steam on exiting the compressor 360. The compressor 360 receives the flow of the refrigerant 305 from the primary evaporator 310 and supplies the pressurized refrigerant 305 to the primary condenser 330.

Fan 370 is operable to draw intake air 101 into dehumidification system 300 and through secondary evaporator 340, primary evaporator 310, secondary condenser 320, subcooling coil 350, and primary condenser 330. It may include appropriate components. The fan 370 can be any type of blower (eg, axial fan, forward inclined impeller, backward inclined impeller, etc.). For example, the fan 370 can be a rear tilt impeller located adjacent to the primary condenser 330, as shown in FIG. Although fan 370 is shown in FIG. 3 as being located adjacent primary condenser 330, it is understood that fan 370 may be located anywhere along the air flow path of dehumidification system 300. Should be. For example, the fan 370 may be located in the air flow path of any one of the air streams 101, 345, 315, 325, 355, or 106. In addition, dehumidification system 300 may include one or more additional fans located within any one or more of these air flow paths. Primary metering device 380 and secondary metering device 390 are any suitable type of metering/inflating device. In some embodiments, the primary metering device 380 is a thermostatic expansion valve (TXV) and the secondary metering device 390 is a fixed orifice device (or vice versa). In certain embodiments, metering devices 380 and 390 remove pressure from the flow of refrigerant 305, allowing liquid-to-vapor expansion or change of state within evaporators 310 and 340. The high pressure liquid (or mostly liquid) refrigerant entering metering devices 380 and 390 is at a higher temperature than liquid refrigerant 305 exiting metering devices 380 and 390. For example, if the flow of refrigerant 305 entering primary metering device 380 is 340 psig/80°F/0% steam, the flow of refrigerant 305 will be 196 psig/68°F/5% steam upon exiting primary metering device 380. possible. As another example, if the refrigerant 305 flow entering the secondary metering device 390 is 196 psig/68°F/4% steam, the refrigerant 305 flow may be 128 psig/44°F upon exiting the secondary metering device 390. /14% steam.

Refrigerant 305 can be any suitable refrigerant such as R410a. In general, the dehumidification system 300 includes a compressor 360, a primary condenser 330, an (optional) subcooling coil 350, a primary metering device 380, a secondary evaporator 340, a secondary condenser 320, a secondary metering device 390, and a primary evaporator 310. A closed refrigeration loop of the passing refrigerant 305 is used. Compressor 360 pressurizes the flow of refrigerant 305, thereby increasing the temperature of refrigerant 305. A primary condenser 330 and a secondary condenser 320, which may include any suitable heat exchangers, flow from the refrigerant 305 through their respective air streams (ie, fourth air stream 355 and second air stream 315). Cools the pressurized stream of refrigerant 305 by promoting heat transfer to. The cooled refrigerant 305 flow exiting the primary and secondary condensers 330 and 320 is a respective expander (ie, primary metering device 380 and secondary metering device 390) operable to reduce the pressure of the refrigerant 305 stream. ), thereby reducing the temperature of the refrigerant 305 stream. Primary evaporator 310 and secondary evaporator 340, which may include any suitable heat exchangers, receive a flow of refrigerant 305 from secondary metering device 390 and primary metering device 380, respectively. Primary evaporator 310 and secondary evaporator 340 facilitate the transfer of heat from their respective airflows (ie, intake air 101 and first airflow 345) passing therethrough to the flow of refrigerant 305. The flow of refrigerant 305 exits the primary evaporator 310 and then returns to the compressor 360, where the cycle repeats.

In certain embodiments, the cooling loop described above may be configured such that evaporators 310 and 340 operate in a flooded state. In other words, the refrigerant 305 stream may enter the evaporators 310 and 340 in the liquid state, and a portion of the refrigerant 305 stream may still be in the liquid state as it exits the evaporators 310 and 340. Thus, a phase change in the flow of refrigerant 305 (from liquid to vapor as heat is transferred to the flow of refrigerant 305) occurs across evaporators 310 and 340, resulting in near pressure and temperature across evaporators 310 and 340. It becomes constant (and as a result the cooling capacity increases). In operation of the exemplary embodiment of dehumidification system 300, intake air 101 is drawn into dehumidification system 300 by fan 370. The intake air 101 passes through the secondary evaporator 340 where heat is transferred from the intake air 101 to the cold flow of the refrigerant 305 passing through the secondary evaporator 340. As a result, the intake air 101 can be cooled. As an example, if the intake air 101 is at 80°F/60% humidity, the secondary evaporator 340 may discharge the first air stream 345 at 70°F/84% humidity. As a result, the flow of the refrigerant 305 may be partially evaporated in the secondary evaporator 340. For example, if the refrigerant 305 flow entering the secondary evaporator 340 is 196 psig/68°F/5% steam, then the refrigerant 305 flow is 196 psig/68°F/38% steam upon exiting the secondary evaporator 340. possible.

The cooled intake air 101 leaves the secondary evaporator 340 as a first air flow 345 and enters the primary evaporator 310. Similar to the secondary evaporator 340, the primary evaporator 310 transfers heat from the first air stream 345 to the cold stream of refrigerant 305 passing through the primary evaporator 310. As a result, the first air stream 345 is cooled to or below its dew point temperature, condensing moisture in the first air stream 345 (thereby increasing the absolute humidity of the first air stream 345). Decrease). As an example, if the first air stream 345 is at 70°F/84% humidity, the primary evaporator 310 may discharge the second air stream 315 at 54°F/98% humidity. This may cause the flow of refrigerant 305 to partially or completely evaporate within the primary evaporator 310. For example, if the refrigerant 305 flow entering the primary evaporator 310 is 128 psig/44°F/14% steam, the refrigerant 305 flow may be 128 psig/52°F/100% steam upon exiting the primary evaporator 310. .. In certain embodiments, liquid condensate from the first air stream 345 may be collected in a drain pan connected to a condensate reservoir, as shown in FIG. In addition, the condensate reservoir includes a condensate pump that moves the collected condensate from the dehumidification system 300 (eg, via a drain hose) to a suitable drain or storage location, either continuously or at periodic intervals. obtain.

The cooled first air stream 345 leaves the primary evaporator 310 as a second air stream 315 and enters the secondary condenser 320. Secondary condenser 320 facilitates heat transfer from the flow of hot refrigerant 305 through secondary condenser 320 to second air stream 315. This reheats the second air stream 315, thereby reducing the relative humidity of the second air stream 315. As an example, if the second air stream 315 is at 54°F/98% humidity, the secondary condenser 320 may discharge the third air stream 325 at 65°F/68% humidity. This may cause the flow of refrigerant 305 to partially or completely condense within the secondary condenser 320. For example, if the refrigerant 305 flow entering the secondary condenser 320 is 196 psig/68°F/38% steam, then the refrigerant 305 flow is 196 psig/68°F/4% steam as it exits the secondary condenser 320. possible.

In some embodiments, dehumidified second air stream 315 exits secondary condenser 320 as third air stream 325 and enters primary condenser 330. The primary condenser 330 facilitates heat transfer from the flow of hot refrigerant 305 through the primary condenser 330 to the third air stream 325. This further heats the third air stream 325, thereby further reducing the relative humidity of the third air stream 325. As an example, if the third air stream 325 is at 65°F/68% humidity, the secondary condenser 320 may discharge the dehumidified air 106 at 102°F/19% humidity. This may cause the flow of refrigerant 305 to partially or completely condense within the primary condenser 330. For example, if the refrigerant 305 flow entering the primary condenser 330 is 340 psig/150°F/100% steam, then the refrigerant 305 flow may be 340 psig/105°F/60% steam upon exiting the primary condenser 330. ..

As mentioned above, some embodiments of the dehumidification system 300 may include a sub-cooling coil 350 in the airflow between the secondary condenser 320 and the primary condenser 330. The sub-cooling coil 350 facilitates heat transfer from the flow of hot refrigerant 305 passing through the sub-cooling coil 350 to the third air stream 325. This further heats the third air stream 325, which further reduces the relative humidity of the third air stream 325. As an example, if the third air stream 325 is at 65°F/68% humidity, the sub-cooling coil 350 may discharge the fourth air stream 355 at 81°F/37% humidity. This may cause the flow of refrigerant 305 to partially or completely condense within the cooling subcoil 350. For example, if the flow of refrigerant 305 entering subcooling coil 350 is 340 psig/150°F/60% vapor, the flow of refrigerant 305 will be 340 psig/80°F/0% as it exits subcooling coil 350. It can be steam.

Some embodiments of dehumidification system 300 may include a controller that may include one or more computer systems at one or more locations. Each computer system may receive, process, store, or store any suitable input device (such as a keypad, touch screen, mouse, or other device capable of accepting information), output device, mass storage medium, or data. And other suitable components for communicating. Both input and output devices may include fixed or removable storage media, such as magnetic computer disks, CD-ROMs, or other suitable media for receiving input from and providing output to a user. Each computer system may be a personal computer, workstation, network computer, kiosk, wireless data port, personal data assistant (PDA), one or more processors in these or other devices, or any other suitable processing unit. Can be included. In short, the controller may include any suitable combination of software, firmware, and hardware. The controller may additionally include one or more processing modules. Each processing module may include one or more microprocessors, controllers, or any other suitable computing device or resource, functioning alone or with other components of dehumidification system 300. It may provide some or all of the functions described in the document. The controller may additionally include computer memory (or may be communicatively coupled to computer memory via wireless or wired communication). The memory may include any memory or database module, and may include magnetic media, optical media, random access memory (RAM), read only memory (ROM), removable media, or any other suitable local or remote memory component. It may take the form of volatile or non-volatile memory, including but not limited to.

Although a particular implementation of the dehumidification system 300 is shown and described primarily, the present disclosure contemplates any suitable implementation of the dehumidification system 300 depending on the particular needs. Further, although the various components of dehumidification system 300 have been shown to be located in particular locations and relative to each other, the present disclosure contemplates that these components may be of any suitable configuration, depending on the particular needs. It is intended to be placed in various positions.

FIG. 5 illustrates an exemplary dehumidification method 500 that may be used by the dehumidification system 100 of FIGS. 1 and 2 and the portable dehumidification system 200 to reduce the humidity of the air within the structure 102. The method 500 may begin at step 510 with a secondary evaporator receiving an inlet airflow and ejecting a first airflow. In some embodiments, the secondary evaporator is secondary evaporator 340. In some embodiments, the intake airflow is intake air 101 and the first airflow is first airflow 345. In some embodiments, the secondary evaporator of step 510 receives the flow of refrigerant from a primary metering device, such as primary metering device 380, and changes the refrigerant flow to a secondary condenser, such as secondary condenser 320. Supply). In some embodiments, the refrigerant stream of method 500 is the refrigerant 305 stream described above.

In step 520, the primary evaporator receives the first air stream of step 510 and discharges the second air stream. In some embodiments, the primary evaporator is primary evaporator 310 and the second air stream is second air stream 315. In some embodiments, the primary evaporator of step 520 receives refrigerant flow from a secondary metering device, such as secondary metering device 390, and directs the refrigerant flow (altered) to a compressor, such as compressor 360. Supply.

In step 530, the secondary condenser receives the second air stream of step 520 and discharges the third air stream. In some embodiments, the secondary condenser is the secondary condenser 320 and the third air stream is the third air stream 325. In some embodiments, the secondary condenser of step 530 receives the refrigerant flow from the secondary evaporator of step 510 and directs the refrigerant flow to a secondary metering device, such as secondary metering device 390 (in a modified state). ) Supply. In step 540, the primary condenser receives the third air stream of step 530 and discharges the dehumidified air stream. In some embodiments, the primary condenser is primary condenser 330 and the dehumidified air stream is dehumidified air 106. In some embodiments, the primary condenser of step 540 receives the refrigerant flow from the compressor of step 520 and provides the primary metering device of step 510 with the refrigerant flow (altered). In an alternative embodiment, the primary condenser of step 540 directs the flow of refrigerant (altered) to a sub-cooling coil, such as sub-cooling coil 350, which supplies the primary metering device of step 510 (altered). Supply).

In step 550, the compressor receives the flow of refrigerant from the primary evaporator of step 520 and provides (in a modified state) the flow of refrigerant to the primary condenser of step 540. After step 550, method 500 may end.

Certain embodiments may repeat one or more steps of method 500 of FIG. 5, if applicable. Although this disclosure describes and describes particular steps of the method of FIG. 5 that occur in a particular order, this disclosure contemplates any suitable step of the method of FIG. 5 that occurs in any suitable order. doing. Further, although the present disclosure describes and describes an exemplary dehumidification method for reducing the humidity of air in a structure that includes certain steps of the method of FIG. 5, the present disclosure, where applicable, Any for reducing the humidity of the air in the structure, including any suitable step that may include all steps, some steps, or none of the steps of the method of Appropriate methods are contemplated. Further, although the present disclosure describes and describes particular components, devices or systems that perform the particular steps of the method of FIG. 5, the present disclosure describes any suitable step of the method of FIG. Any suitable combination of any suitable components, devices, or systems for carrying out.

Although the exemplary method of FIG. 5 has been described above with respect to dehumidification system 300 of FIG. 3, the same or similar method includes dehumidification systems 600 and 800 of FIG. 6 (described below). It should be appreciated that it can be performed with any of the dehumidification systems described herein. Further, with respect to the exemplary method of FIG. 5, reference to an evaporator or capacitor refers to a single coil operable to perform the functions of these components, eg, as described above with respect to the examples of FIGS. 9 and 10. It should be understood that it can refer to the evaporator portion or the condenser portion of the pack.

FIG. 6 illustrates an exemplary dehumidification system 600 that may be used in accordance with the dehumidification system 100 of FIG. 1 to reduce the humidity of the air within the structure 102. Dehumidification system 600 includes a dehumidification unit 602, which is generally indoors, and a condenser system 604 (eg, condenser system 108 of FIG. 1). The dehumidification unit 602 includes a primary evaporator 610, a secondary evaporator 640, a secondary condenser 620, a primary metering device 680, a secondary metering device 690, and a first fan 670, while the condenser system 604 includes , Primary condenser 630, compressor 660, optional sub-cooling coil 650, and second fan 695.

The flow of refrigerant 605 is circulated through the dehumidification system 600 as shown. Generally, the dehumidification unit 602 receives an intake air stream 601, removes water from the intake air stream 601, and discharges dehumidified air 625 to a conditioned space. Water is removed from the incoming air 601 using a cooling cycle of the flow of refrigerant 605. The flow of refrigerant 605 through system 600 of FIG. 6 proceeds in a similar manner as the flow of refrigerant 305 through dehumidification system 300 of FIG. However, the path of airflow through system 600 is different than that through system 300, as described herein. However, by including the secondary evaporator 640 and the secondary condenser 620, the dehumidification system 600 causes at least a portion of the flow of refrigerant 605 to evaporate and condense twice in one cooling cycle. This increases the cooling capacity over a typical system without requiring additional power to the compressor, thereby increasing the overall efficiency of the system.

The separate configuration of system 600, including dehumidification unit 602 and condenser system 604, dissipates heat from the cooling and dehumidification process outdoors or in an unconditioned space (eg, outside the dehumidified space). Enable that. This allows the dehumidification system 600 to have a footprint similar to that of a typical central air conditioning system or heat pump. In general, the temperature of the third air stream 625 discharged from the system 600 into the conditioned space is significantly reduced compared to the temperature of the air stream 106 discharged from the system 300 of FIG. Thus, the configuration of system 600 allows dehumidified air to be delivered to the conditioned space at a reduced temperature. Thus, system 600 may perform the functions of both a dehumidifier (dehumidifying air) and a central air conditioner (cooling air).

In general, dehumidification system 600 attempts to match the saturation temperature of secondary evaporator 640 with the saturation temperature of capacitor 620. The saturation temperature of the secondary evaporator 640 and the secondary condenser 620 is generally controlled according to the formula of (temperature of intake air 601 + temperature of second air flow 615)/2. Since the saturation temperature of the secondary evaporator 640 is lower than that of the intake air 601, evaporation occurs in the secondary evaporator 640. The saturation temperature of the secondary condenser 620 is higher than that of the second air stream 615, so that condensation occurs in the secondary condenser 620. The amount of the refrigerant 605 that evaporates in the secondary evaporator 640 is substantially equal to the amount that condenses in the secondary condenser 620. Primary evaporator 610 receives the flow of refrigerant 605 from secondary metering device 690 and discharges the flow of refrigerant 605 to compressor 660. The primary evaporator 610 can be any type of coil (eg, fin tube, microchannel, etc.). Primary evaporator 610 receives first air stream 645 from secondary evaporator 640 and discharges second air stream 615 to secondary condenser 620. The second air stream 615 is generally at a lower temperature than the first air stream 645. To cool the incoming first air stream 645, the primary evaporator 610 transfers heat from the first air stream 645 to the stream of the refrigerant 605, thereby at least partially liquidating the stream of the refrigerant 605. To vaporize to gas. This transfer of heat from the first air stream 645 to the refrigerant 605 stream also removes water from the first air stream 645.

Secondary condenser 620 receives the flow of refrigerant 605 from secondary evaporator 640 and discharges the flow of refrigerant 605 to secondary metering device 690. Secondary capacitor 620 can be any type of coil (eg, fin tube, microchannel, etc.). The secondary condenser 620 receives the second air flow 615 from the primary evaporator 610 and discharges the third air flow 625. The third air stream 625 is generally warmer and drier (ie, has the same dew point but lower relative humidity) than the second air stream 615. The secondary condenser 620 produces a third air flow 625 by transferring heat from the flow of the refrigerant 605 to the second air flow 615, thereby condensing the flow of the refrigerant 605 at least partially from a gas to a liquid. Let As mentioned above, the third air stream 625 is discharged into the conditioned space. In other embodiments (eg, as shown in FIG. 8), the third air stream 625 first passes through the sub-cooling coil 650 before being exhausted to the conditioned space with further reduced relative humidity. And/or pass through a sub-cooling coil 650.

Refrigerant 605 flows to the compressor 660 of the condenser system 604 outdoors or in an unconditioned space. Compressor 660 pressurizes the flow of refrigerant 605, thereby increasing the temperature of refrigerant 605. For example, if the flow of refrigerant 605 entering compressor 660 is 128 psig/52°F/100% steam, the flow of refrigerant 605 may be 340 psig/150°F/100% steam as it exits compressor 660. The compressor 660 receives the flow of the refrigerant 605 from the primary evaporator 610 and supplies the pressurized flow of the refrigerant 605 to the primary condenser 630.

Primary condenser 630 receives the flow of refrigerant 605 from compressor 660 and discharges the flow of refrigerant 605 to sub-cooling coil 650. The primary capacitor 630 can be any type of coil (eg, fin tube, microchannel, etc.). Primary condenser 630 and sub-cooling coil 650 receive first outdoor air stream 606 and discharge second outdoor air stream 608. The second outdoor airflow 608 is generally warmer (ie, has a lower relative humidity) than the first outdoor airflow 606. Primary condenser 630 transfers heat from the flow of refrigerant 605, thereby condensing the flow of refrigerant 605 at least partially from a gas to a liquid. In some embodiments, the primary condenser 630 fully condenses the flow of refrigerant 605 into a liquid (ie, 100% liquid). In other embodiments, primary condenser 630 partially condenses the flow of refrigerant 605 into a liquid (ie less than 100% liquid).

A sub-cooling coil 650, which is an optional component of dehumidification system 600, sub-cools liquid refrigerant 605 as it exits primary condenser 630. This, in turn, supplies the primary metering device 680 with a liquid refrigerant that is 30 degrees (or more) colder than before it entered the subcooling coil 650. For example, if the flow of refrigerant 605 entering subcooling coil 650 is 340 psig/105°F/60% vapor, the flow of refrigerant 605 will be 340 psig/80°F/0% as it exits subcooling coil 650. It can be steam. The subcooled refrigerant 605 has a higher thermal enthalpy coefficient as well as a higher density, which improves the energy transfer between the air flow and the evaporator and removes additional latent heat from the refrigerant 605. This further results in higher efficiency of dehumidification system 600 and less energy consumption. Embodiments of dehumidification system 600 may or may not include subcooling coil 650.

In particular embodiments, sub-cooling coil 650 and primary capacitor 630 are integrated into a single coil. Such a single coil includes suitable circuits for air flows 606 and 608 and a flow of refrigerant 605. An illustrative example of a capacitor system 604 having a single coil capacitor and subcooling coil is shown in FIG. The single unit coil has an inner tube 710 corresponding to the condenser and an outer tube 705 corresponding to the subcooling coil. Refrigerant may be directed through inner tube 710 before flowing through outer tube 705. In the example shown in FIG. 7, the airflow is drawn through the single unit coil by fan 695 and discharged upward. However, it should be appreciated that other embodiments of the condenser system may include condensers, compressors, optional sub-cooling coils, and other configurations of fans known in the art.

Secondary evaporator 640 receives the flow of refrigerant 605 from primary metering device 680 and discharges the flow of refrigerant 605 to secondary condenser 620. The secondary evaporator 640 can be any type of coil (eg, fin tube, microchannel, etc.). Secondary evaporator 640 receives intake air 601 and discharges first air stream 645 to primary evaporator 610. The first air stream 645 is generally cooler than the intake air 601. To cool the incoming intake air 601, the secondary evaporator 640 transfers heat from the intake air 601 to the flow of refrigerant 605, thereby at least partially evaporating the flow of refrigerant 605 from liquid to gas.

Fan 670 may include any suitable component operable to draw intake air 601 into dehumidification unit 602 and through secondary evaporator 640, primary evaporator 610, and secondary condenser 620. Fan 670 can be any type of blower (eg, axial fan, forward impeller, rear impeller, etc.). For example, the fan 670 can be a rear tilt impeller located adjacent to the secondary condenser 620.

Although fan 670 is shown in FIG. 6 as being located adjacent condenser 620, it is understood that fan 670 may be located anywhere along the air flow path of dehumidifying unit 602. Should be. For example, fan 670 may be located in the airflow path of any one of airflow 601, 645, 615, or 625. Further, dehumidification unit 602 may include one or more additional fans located within any one or more of these airflow paths. Similarly, although the fan 695 of the condenser system 604 is shown in FIG. 6 as being located above the primary condenser 630, the fan 695 includes an air flow 606 that the fan 695 directs to the primary condenser 630 and the subcooling coil 650. Can be located anywhere (eg, above, below, laterally) with respect to capacitor 630 and subcooling coil 650, as long as they are properly arranged and configured to facilitate the flow of

The rate of airflow produced by fan 670 may be different than that produced by fan 695. For example, the flow rate of air flow 606 produced by fan 695 may be higher than the flow rate of air flow 601 produced by fan 670. This difference in flow rates may provide several benefits to the dehumidification system described herein. For example, the high airflow produced by fan 695 may provide improved heat transfer in subcooling coil 650 and primary condenser 630 of condenser system 604. Generally, the velocity of the air flow produced by the second fan 695 is between about 2 and 5 times the velocity of the air flow produced by the first fan 670. For example, the velocity of the airflow generated by the first fan 670 can be about 200-400 cubic feet per minute (cfm). For example, the velocity of the airflow produced by the second fan 695 can be about 900-1200 cubic feet per minute (cfm).

Primary metering device 680 and secondary metering device 690 are any suitable type of metering/inflating device. In some embodiments, the primary metering device 680 is a thermostatic expansion valve and the secondary metering device 690 is a fixed orifice device (or vice versa). In certain embodiments, metering devices 680 and 690 remove pressure from the flow of refrigerant 605, allowing liquid-to-vapor expansion or change of state within evaporators 610 and 640. The high pressure liquid (or almost liquid) refrigerant entering the metering devices 680 and 690 is at a higher temperature than the liquid refrigerant 605 exiting the metering devices 680 and 690. For example, if the flow of refrigerant 605 entering primary metering device 680 is 340 psig/80°F/0% steam, the flow of refrigerant 605 will exit primary metering device 680 at 196 psig/68°F/5% steam. possible. As another example, if the flow of refrigerant 605 entering the secondary metering device 690 is 196 psig/68°F/4% steam, the flow of refrigerant 605 may leave the secondary metering device 690 at 128 psig/44°F. /14% steam.

In certain embodiments, the secondary metering device 690 is substantially open so that the pressure of the refrigerant 605 entering the metering device 690 is substantially the same as the pressure of the refrigerant 605 exiting the metering device 690. state) (referred to herein as the "fully open" state). For example, the pressure of the refrigerant 605 can be up to 80%, 90%, 95%, 99%, or 100% of the pressure of the refrigerant 605 entering the metering device 690. With the secondary metering device 690 operating in the “fully open” state, the primary metering device 680 is the primary source of pressure drop in the dehumidification system 600. In this configuration, the air flow 615 is not substantially heated as it passes through the secondary condenser 620, and the secondary evaporator 640, the primary evaporator 610, and the secondary condenser 620 are effective as a single evaporator. Act on. When the secondary metering device 690 operates in the "full open" condition, less water may be removed from the air flow 601 but at a lower temperature than when the secondary metering device 690 is not in the "full open" condition. Are discharged into the air-conditioned space. This configuration accommodates a relatively high sensible heat ratio (SHR) mode of operation in which the dehumidification system 600 is capable of producing a cold air flow 625 with characteristics similar to those of the air flow produced by a central air conditioner. To do. If the speed of airflow 601 is increased to a threshold (eg, by increasing the speed of fan 670 or one or more other fans of dehumidification system 600), dehumidification system 600 removes water from airflow 601. Sensible cooling can be done without removal.

Refrigerant 605 can be any suitable refrigerant such as R410a. Generally, dehumidification system 600 passes from compressor 660 through primary condenser 630, (optionally) subcooling coil 650, primary metering device 680, secondary evaporator 640, secondary condenser 620, secondary metering device 690, and primary evaporator 610. A closed cooling loop of the cooling medium 605 is used. Compressor 660 pressurizes the flow of refrigerant 605, thereby increasing the temperature of refrigerant 605. A primary condenser 630 and a secondary condenser 620, which may include any suitable heat exchangers, are provided for the respective airflows (ie, the first outdoor airflow 606 and the second airflow 615) passing therethrough from the flow of refrigerant 605. Cooling the pressurized stream of refrigerant 605 by promoting heat transfer to The flow of cooled refrigerant 605 exiting the primary and secondary condensers 630 and 620 is a respective expander (ie, primary metering device 680 and secondary metering device 690) operable to reduce the pressure of the refrigerant 605 stream. ), thereby reducing the temperature of the flow of refrigerant 605. Primary evaporator 610 and secondary evaporator 640, which may include any suitable heat exchangers, receive a flow of refrigerant 605 from secondary metering device 690 and primary metering device 680, respectively. Primary and secondary evaporators 610 and 640 facilitate the transfer of heat from their respective airflows (ie, intake air 601 and first airflow 645) passing therethrough to the flow of refrigerant 605. The flow of refrigerant 605 exits primary evaporator 610 and then returns to compressor 660 to repeat the cycle.

In certain embodiments, the cooling loop described above may be configured such that evaporators 610 and 640 operate in a laid down condition. In other words, the flow of refrigerant 605 may enter the evaporators 610 and 640 in the liquid state, and a portion of the flow of refrigerant 605 may still be in the liquid state as it exits the evaporators 610 and 640. Thus, a phase change in the flow of refrigerant 605 (from liquid to vapor as heat is transferred to the flow of refrigerant 605) occurs across evaporators 610 and 640, resulting in near pressure and temperature across evaporators 610 and 640. It remains constant (and thus increases the cooling capacity). In operation of the exemplary embodiment of dehumidification system 600, intake air 601 may be drawn into dehumidification system 600 by fan 670. The intake air 601 passes through the secondary evaporator 640 where heat is transferred from the intake air 601 to the cold flow of the refrigerant 605 passing through the secondary evaporator 640. As a result, the intake air 601 can be cooled. As an example, if the intake air 601 is at 80°F/60% humidity, the secondary evaporator 640 may discharge the first air stream 645 at 70°F/84% humidity. This may cause the flow of refrigerant 605 to partially evaporate within the secondary evaporator 640. For example, if the refrigerant 605 flow entering the secondary evaporator 640 is 196 psig/68°F/5% steam, the refrigerant 605 flow will exit the secondary evaporator 640 at 196 psig/68°F/38% steam. Can be

The cooled intake air 601 leaves the secondary evaporator 640 as a first air stream 645 and enters the primary evaporator 610. Similar to the secondary evaporator 640, the primary evaporator 610 transfers heat from the first air stream 645 to the cold stream of refrigerant 605 passing through the primary evaporator 610. As a result, the first air stream 645 is cooled to or below its dew point temperature, condensing moisture in the first air stream 645 (thereby increasing the absolute humidity of the first air stream 645). Decrease). As an example, if the first air stream 645 is at 70°F/84% humidity, the primary evaporator 610 may discharge the second air stream 615 at 54°F/98% humidity. This may cause the flow of refrigerant 605 to partially or completely evaporate within the primary evaporator 610. For example, if the flow of refrigerant 605 entering primary evaporator 610 is 128 psig/44°F/14% steam, then the flow of refrigerant 605 may be 128 psig/52°F/100% steam as it exits primary evaporator 610. .. In a particular embodiment, as shown in FIG. 4, the liquid condensate from the first air stream 645 may be collected in a drain pan connected to a condensate reservoir. In addition, the condensate reservoir may include a condensate pump that moves the collected condensate from the dehumidification system 600 (eg, via a drain hose) to a suitable drainage or storage location at continuous or periodic intervals. ..

Cooled first air stream 645 leaves primary evaporator 610 as second air stream 615 and enters secondary condenser 620. Secondary condenser 620 facilitates heat transfer from the flow of hot refrigerant 605 through secondary condenser 620 to second air stream 615. This reheats the second air stream 615, thereby reducing the relative humidity of the second air stream 615. As an example, if the second air stream 615 is 54°F/98% humidity, the secondary condenser 620 may discharge the dehumidified air stream 625 at 65°F/68% humidity. This may cause the flow of refrigerant 605 to partially or completely condense within the secondary condenser 620. For example, if the refrigerant 605 flow entering the secondary condenser 620 is 196 psig/68°F/38% steam, then the refrigerant 605 flow is 196 psig/68°F/4% steam upon exiting the secondary condenser 620. possible. In some embodiments, the second air stream 615 exits the secondary condenser 620 as a dehumidified air stream 625 and exits into the conditioned space.

Primary condenser 630 facilitates heat transfer from the flow of hot refrigerant 605 through primary condenser 630 to first outdoor airflow 606. This heats the outdoor airflow 606, which is discharged as a second outdoor airflow 608 into the non-air conditioned space (eg, outdoors). As an example, if the first outdoor airflow 606 is at 65°F/68% humidity, then the primary condenser 630 may discharge the second outdoor airflow 608 at 102°F/19% humidity. This may cause the flow of refrigerant 605 to partially or completely condense within the primary condenser 630. For example, if the flow of refrigerant 605 entering primary condenser 630 is 340 psig/150°F/100% steam, then the flow of refrigerant 605 is 340 psig/105°F/60% steam as it exits primary condenser 630. obtain. As mentioned above, some embodiments of dehumidification system 600 may include a subcooling coil 650 in the airflow between the inlet of condenser system 604 and primary condenser 630. The sub-cooling coil 650 facilitates heat transfer from the flow of hot refrigerant 605 passing through the sub-cooling coil 650 to the first outdoor airflow 606. This heats the first outdoor air stream 606, thereby raising the temperature of the first outdoor air stream 606. As an example, if the first outdoor airflow 606 is at 65°F/68% humidity, the sub-cooling coil 650 may discharge the airflow at 81°F/37% humidity. This may cause the flow of refrigerant 605 to partially or completely condense within the subcooling coil 650. For example, if the flow of refrigerant 605 entering subcooling coil 650 is 340 psig/150°F/60% vapor, the flow of refrigerant 605 will be 340 psig/80°F/0% as it exits subcooling coil 650. It can be steam.

In the embodiment shown in FIG. 6, the subcooling coil 650 is in the condenser system 604. This configuration minimizes the temperature of the third air stream 625 exhausted to the conditioned space. An alternative embodiment is shown as dehumidification system 800 in FIG. 8 where dehumidification unit 802 includes subcooling coil 650. In this embodiment, the airflow 625 first passes through the sub-cooling coil 650 before being discharged as an airflow 855 via the fan 670 into the conditioned space. As described herein, the fan 670 may alternatively be located anywhere within the dehumidification unit 802 along the path of the airflow, with one or more additional fans. , Dehumidification unit 802.

Without wishing to be bound by any particular theory, the dehumidification system 800 configuration is believed to be more energy efficient than the dehumidification system 600 configuration of FIG. 6 under common operating conditions. For example, when the temperature of the third air flow 625 is lower than the outside air temperature (that is, the temperature of the air flow 606), the refrigerant 605 is cooled more effectively by the sub-cooling coil 650 arranged in the dehumidifying unit 802. Or be subcooled. Such operating conditions can be prevalent, for example, in warm climate locations and/or during the summer. In certain embodiments, the indoor unit 802 also includes a compressor 660 (configuration not shown) that may be located near the secondary evaporator 640, the primary evaporator 610, and/or the secondary condenser 620, for example.

In operation of the exemplary embodiment of dehumidification system 800, intake air 601 may be drawn into dehumidification system 800 by fan 670. The intake air 601 passes through the secondary evaporator 640 where heat is transferred from the intake air 601 to the flow of the cold refrigerant 605 passing through the secondary evaporator 640. As a result, the intake air 601 can be cooled. For example, if the intake air 601 is at 80°F/60% humidity, the secondary evaporator 640 may discharge the first air stream 645 at 70°F/84% humidity. This may cause the flow of refrigerant 605 to partially evaporate within the secondary evaporator 640. For example, if the refrigerant 605 flow entering the secondary evaporator 640 is 196 psig/68°F/5% steam, the refrigerant 605 flow will exit the secondary evaporator 640 at 196 psig/68°F/38% steam. Can be

The cooled intake air 601 exits the secondary evaporator 640 as a first air flow 645 and enters the primary evaporator 610. Similar to the secondary evaporator 640, the primary evaporator 610 transfers heat from the first air stream 645 to the flow of cold refrigerant 605 passing through the primary evaporator 610. As a result, the first air stream 645 can be cooled to or below its dew point temperature, condensing moisture within the first air stream 645 (thereby increasing the absolute humidity of the first air stream 645). Decrease). As an example, if the first air stream 645 is at 70°F/84% humidity, the primary evaporator 610 may discharge the second air stream 615 at 54°F/98% humidity. This causes the flow of refrigerant 605 to partially or completely evaporate within the primary evaporator 610. For example, if the flow of refrigerant 605 entering primary evaporator 610 is 128 psig/44°F/14% steam, then the flow of refrigerant 605 may be 128 psig/52°F/100% steam as it exits primary evaporator 610. .. In a particular embodiment, as shown in FIG. 4, liquid condensate from the first air stream 645 may be collected in a drain pan connected to a condensate reservoir. In addition, the condensate reservoir may include a condensate pump that moves the collected condensate from the dehumidification system 800 (eg, via a drain hose) to a suitable drain or storage location at continuous or periodic intervals.

The cooled first air stream 645 exits the primary evaporator 610 as a second air stream 615 and enters the secondary condenser 620. Secondary condenser 620 facilitates heat transfer from the flow of hot refrigerant 605 through secondary condenser 620 to second air stream 615. This reheats the second air stream 615, thereby reducing the relative humidity of the second air stream 615. As an example, if the second air stream 615 is 54°F/98% humidity, the secondary condenser 620 may discharge the dehumidified air stream 625 at 65°F/68% humidity. This causes the flow of refrigerant 605 to partially or completely condense within the secondary condenser 620. For example, if the flow of refrigerant 605 entering secondary condenser 620 is 196 psig/68°F/38% vapor, the flow of refrigerant 605 will be 196 psig/68°F/4% as it exits secondary condenser 620. It can be steam. In some embodiments, the second air stream 615 exits the secondary condenser 620 as a dehumidified air stream 625 and exits into the conditioned space.

Dehumidified air stream 625 enters subcooling coil 650, which facilitates heat transfer from the flow of hot refrigerant 605 through subcooling coil 650 to dehumidified air stream 625. This heats the dehumidified air stream 625, which further reduces the humidity of the dehumidified air stream 625. As an example, if the dehumidified air stream 625 is at 65°F/68% humidity, the sub-cooling coil 650 may discharge the air stream 855 at 81°F/37% humidity. This causes the flow of refrigerant 605 to partially or completely condense within the subcooling coil 650. For example, if the flow of refrigerant 605 entering subcooling coil 650 is 340 psig/150°F/60% vapor, the flow of refrigerant 605 will be 340 psig/80°F/0% as it exits subcooling coil 650. It can be steam.

Primary condenser 630 facilitates heat transfer from the flow of hot refrigerant 605 through primary condenser 630 to first outdoor airflow 606. This heats the outdoor airflow 606 which is discharged to the non-air conditioned space as the second outdoor airflow 608. As an example, if the first outdoor airflow 606 is at 65°F/68% humidity, then the primary condenser 630 may discharge the second outdoor airflow 608 at 102°F/19% humidity. This may partially or completely condense the flow of refrigerant 605 within the primary condenser 630. For example, if the flow of refrigerant 605 entering primary condenser 630 is 340 psig/150°F/100% steam, the flow of refrigerant 605 may be 340 psig/105°F/60% steam as it exits primary condenser 630. ..

Some embodiments of dehumidification systems 600 and 800 of FIGS. 6 and 8 may include a controller that may include one or more computer systems at one or more locations. Each computer system receives, processes, stores, receives any suitable input device (such as a keypad, touch screen, mouse, or other device capable of accepting information), output device, mass storage medium, or data. It may include other suitable components for communicating. Both input and output devices may include fixed or removable storage media, such as magnetic computer disks, CD-ROMs, or other suitable media for receiving input from and providing output to a user. .. Each computer system may be a personal computer, workstation, network computer, kiosk, wireless data port, personal data assistant (PDA), one or more processors in these or other devices, or any other suitable processing device. Can be included. In short, the controller may include any suitable combination of software, firmware and hardware.

The controller may additionally include one or more processing modules. Each processing module may include one or more microprocessors, controllers, or any other suitable computing device or resource, each functioning alone or with other components of dehumidification systems 600 and 800, It may provide some or all of the functionality described herein. The controller may additionally include computer memory (or may be communicatively coupled to computer memory via wireless or wired communication). The memory may include any memory or database module, including magnetic media, optical media, random access memory (RAM), read only memory (ROM), removable media, or any other suitable local or remote memory component. It may take the form of volatile or non-volatile memory, including but not limited to.

Although particular implementations of dehumidification systems 600 and 800 are shown and described primarily, the present disclosure contemplates any suitable implementation of dehumidification systems 600 and 800 depending on the particular needs. Further, although the various components of dehumidification systems 600 and 800 have been shown to be in specific locations and relative to each other, the present disclosure is not limited to these components in accordance with particular needs. Intended to be placed in a suitable position.

In a particular embodiment, the secondary evaporator (340, 640), primary evaporator (310, 610) and secondary capacitor (320, 620) of FIG. 3, 6 or 8 are combined into one coil pack. A single coil pack may include portions (e.g., separate refrigerant circuits) corresponding to the functions of the secondary evaporator, primary evaporator, and secondary condenser, respectively, described above. An illustrative example of such a single coil pack is shown in FIG. FIG. 9 shows a single coil pack 900 containing multiple coils (represented by circles in FIG. 9). Coil pack 900 includes a secondary evaporator portion 940, a primary evaporator portion 910, and a secondary capacitor portion 920. The coil pack may include and/or be fluidly connectable to metering devices 980 and 990, as shown in the exemplary case of FIG. In particular embodiments, metering devices 980 and 990 correspond to primary metering device 380 and secondary metering device 390 of FIG.

In general, metering devices 980 and 990 can be any suitable type of metering/inflating device. In some embodiments, metering device 980 is a thermostatic expansion valve (TXV) and secondary metering device 990 is a fixed orifice device (or vice versa). In general, metering devices 980 and 990 remove pressure from the flow of refrigerant 905, allowing liquid to vapor expansion or change of state within evaporator portions 910 and 940. The high pressure liquid (or predominantly liquid) refrigerant 905 entering the metering devices 980 and 990 is at a higher temperature than the liquid refrigerant 905 exiting the metering devices 980 and 990. For example, if the flow of refrigerant 905 entering metering device 980 is 340 psig/80°F/0% steam, the flow of refrigerant 905 will be 196 psig/68°F/5% steam as it exits primary metering device 980. Can be As another example, if the flow of refrigerant 905 entering secondary metering device 990 is 196 psig/68°F/4% steam, the flow of refrigerant 905 may be 128 psig/44°F as it exits secondary metering device 990. /14% steam. Refrigerant 905 may be any suitable refrigerant, as described above for refrigerant 305 in FIG.

In operation of the exemplary embodiment of the single coil pack 900, the intake airflow 901 causes the secondary evaporator portion 940 to transfer heat from the intake air 901 to the flow of cold refrigerant 905 through the secondary evaporator portion 940. pass. As a result, the intake air 901 can be cooled. As an example, if the intake air 901 is at 80°F/60% humidity, the secondary evaporator portion 940 may discharge the first air stream at 70°F/84% humidity. This may cause the flow of refrigerant 905 to partially evaporate within the secondary evaporator portion 940. For example, if the flow of refrigerant 905 entering the secondary evaporator portion 940 is 196 psig/68°F/5% vapor, the flow of refrigerant 905 will exit the secondary evaporator portion 940 at 196 psig/68°F/38. It can be% steam.

The cooled intake air 901 travels through the coil pack 900 and reaches the primary evaporator portion 910. Similar to the secondary evaporator portion 940, the primary evaporator portion 910 transfers heat from the air stream 901 to the cold refrigerant 905 flow passing through the primary evaporator portion 910. As a result, the air stream 901 is cooled to or below its dew point temperature, condensing moisture in the air stream 901 (and thereby reducing the absolute humidity of the air stream 901). As an example, if airflow 901 is 70°F/84% humidity, primary evaporator portion 910 may cool airflow 901 to 54°F/98% humidity. This may cause the flow of refrigerant 905 to partially or fully evaporate within the primary evaporator portion 910. For example, if the flow of refrigerant 905 entering the primary evaporator portion 910 is 128 psig/44°F/14% steam, the flow of refrigerant 905 will be 128 psig/52°F/100% steam upon exiting the primary evaporator portion 910. possible. In certain embodiments, liquid condensate from the airflow through the primary evaporator portion 910 is collected in a drain pan connected to a condensate reservoir (eg, as shown in FIG. 4 and described herein). Can be done. In addition, the condensate reservoir includes a condensate pump that moves the collected condensate from the coil pack 900 (eg, via a drain hose) to a suitable drain or storage location, either continuously or at periodic intervals. obtain.

The cooled airflow 901 exiting the primary evaporator section 910 enters the secondary condenser section 920. Secondary condenser portion 920 facilitates heat transfer from the flow of hot refrigerant 905 through secondary condenser portion 920 to air stream 901. This reheats the air stream 901, resulting in a decrease in relative humidity. As an example, if the airflow 901 is 54°F/98% humidity, the secondary condenser portion 920 may discharge the outlet airflow 925 at 65°F/68% humidity. This may cause the flow of refrigerant 905 to partially or completely condense within the secondary condenser portion 920. For example, if the flow of refrigerant 905 entering secondary condenser portion 920 is 196 psig/68°F/38% vapor, the flow of refrigerant 905 will exit secondary condenser portion 920 at 196 psig/68°F/4%. It can be steam. The outlet airflow 925 can enter, for example, the primary condenser portion 330 or the subcooling coil 350 of FIG.

Although a particular implementation of the coil pack 900 is shown and described primarily, the present disclosure contemplates any suitable implementation of the coil pack 900 depending on the particular needs. Further, while the various components of coil pack 900 are shown as being in particular locations, the present disclosure contemplates that these components be placed in any suitable location depending on the particular needs. It is intended.

In certain embodiments, the secondary evaporator (340, 640) and secondary capacitor (320, 620) of FIG. 3, FIG. 6, or FIG. Are combined in a single coil pack to include portions (eg, separate refrigerant circuits) corresponding to the functions of. Capacitor An illustrative example of such an embodiment is shown in FIG. FIG. 10 shows a single coil pack 1000 that includes a secondary evaporator portion 1040 and a secondary capacitor portion 1020. As shown in the illustrative example of FIG. 10, the primary evaporator 1010 is located between the secondary evaporator portion 1040 and the secondary capacitor portion 1020 of a single coil pack 1000. In this exemplary embodiment, the single coil pack 1000 is shown as a "U" shaped coil. However, alternative embodiments may be used as long as the flowing air stream 1001 passes sequentially through the secondary evaporator portion 1040, the primary evaporator 1010, and the secondary condenser portion 1020. In general, a single coil pack 1000 can include the same or different coil types as compared to that of the primary evaporator 1010. For example, the single coil pack 1000 may include a microchannel coil type and the primary evaporator 1010 may include a fin tube coil type. This may provide additional flexibility to optimize the dehumidification system in which a single coil pack 1000 and primary evaporator 1010 is used.

In operation of the exemplary embodiment of the single coil pack 1000, the intake air 1001 passes through the secondary evaporator portion 1040 where heat is transferred from the intake air 1001 to the cold refrigerant stream passing through the secondary evaporator portion 1040. .. As a result, the intake air 1001 can be cooled. As an example, if the intake air 1001 is at 80°F/60% humidity, the secondary evaporator portion 1040 may discharge the airflow at 70°F/84% humidity. This may partially vaporize the flow of refrigerant within the secondary evaporator portion 1040. For example, if the refrigerant flow entering the secondary evaporator 1040 is 196 psig/68°F/5% vapor, the refrigerant 1005 flow will be 196 psig/68°F/38 as it exits the secondary evaporator portion 1040. It can be% steam.

The cooled intake air 1001 exits the secondary evaporator portion 1040 and enters the primary evaporator 1010. Similar to the secondary evaporator portion 1040, the primary evaporator portion 1010 transfers heat from the air stream 1001 to the cold refrigerant stream passing through the primary evaporator 1010. As a result, the air stream 1001 is cooled to or below its dew point temperature, condensing moisture in the air stream 1001 (and thereby reducing the absolute humidity of the air stream 1001). As an example, if the airflow 1001 entering the primary evaporator 1010 is at 70°F/84% humidity, the primary evaporator 1010 may discharge the airflow at 54°F/98% humidity. This causes the flow of refrigerant to partially or completely evaporate within the primary evaporator 1010. For example, if the refrigerant flow entering the primary evaporator 1010 is 128 psig/44°F/14% steam, then the refrigerant flow may be 128 psig/52°F/100% steam as it exits the primary evaporator 1010. In certain embodiments, liquid condensate from air stream 1010 may be collected in a drain pan connected to a condensate reservoir, as shown in FIG. In addition, the condensate reservoir moves the collected condensate from the primary evaporator 1010 and associated dehumidification system to a suitable drain or storage location (eg, via a drain hose) at continuous or periodic intervals. A condensate pump may be included.

Cooled air stream 1001 exits primary evaporator 1010 and enters secondary condenser portion 1020. Secondary condenser portion 1020 facilitates heat transfer from the flow of hot refrigerant through secondary condenser 1020 to air stream 1001. This reheats the air stream 1001, thereby reducing its relative humidity. As an example, if the airflow 1001 entering the secondary condenser portion 1020 is 54°F/98% humidity, the secondary condenser 1020 may discharge the airflow 1025 at 65°F/68% humidity. This may cause the refrigerant stream to partially or completely condense within the secondary condenser 1020. For example, if the refrigerant flow entering the secondary condenser portion 1020 is 196 psig/68°F/38% vapor, then the refrigerant flow is 196 psig/68°F/4% vapor as it exits the secondary condenser 1020. obtain. The outlet airflow 1025 may enter, for example, the primary condenser 330 or subcooling coil 350 of FIG.

Although a particular implementation of the coil pack 1000 is shown and described primarily, the present disclosure contemplates any suitable implementation of the coil pack 1000 depending on the particular needs. Further, while the various components of coil pack 1000 are shown to be located in particular locations, the present disclosure contemplates that these components may be located in any suitable location depending on the particular needs. I am planning to do so.

In certain embodiments, one or both of the secondary evaporator (340, 640) and the primary evaporator (310, 610) of FIG. 3, 6, or 8 is subdivided into two or more circuits. .. In such an embodiment, each circuit of the subdivided evaporator(s) is supplied with refrigerant by a corresponding metering device. The metering device may include a passive metering device, an active metering device, or a combination thereof. For example, metering device 380 (or 690) may be an active thermostatic expansion valve (TXV) and secondary metering device 390 (or 690) may be a passive fixed orifice device (or vice versa). The metering device can be configured to supply the refrigerant to each circuit in the evaporator at a desired mass flow rate. The metering device that supplies refrigerant to each circuit of the subdivided evaporator(s) may be used in combination with metering devices 380 and 390, or may replace one or both of metering devices 380 and 390.

11, 12, 13, and 14 show an exemplary example of a portion 1100 of a dehumidification system in which a primary evaporator 1110 has three circuits for refrigerant flow, according to certain embodiments. Portion 1100 includes primary metering device 1180, secondary metering devices 1190a-c, secondary evaporator 1140, primary evaporator 1110, and secondary capacitor 1120. Primary evaporator 1110 includes three circuits for receiving the flow of refrigerant from secondary metering devices 1190a-c. In the examples of FIGS. 11, 12, 13, and 14, each of the secondary metering devices 1190a-c is a passive metering device (ie, having a fixed inner diameter and length orifice). However, it should be understood that one or more (up to all) of the secondary metering devices 1190a-c may be active metering devices (eg, thermostatic expansion valves).

In operation of the exemplary embodiment of the dehumidification system portion 1100, a flow of cooled (or subcooled) refrigerant is received at the inlet 1102 from, for example, the subcool coil 350 or the primary condenser 330 of the dehumidification system 300 of FIG. .. Primary metering device 1180 determines the flow rate of the refrigerant to secondary evaporator 1140. 11, 12, 13, and 14 are shown as having a single primary metering device 1180, other embodiments may include multiple primary metering devices in parallel (eg, two. If the next evaporator 1140 has more than one circuit for the flow of refrigerant).

When the cooled refrigerant passes through the secondary evaporator 1140, heat is exchanged between the refrigerant and the air flow passing through the secondary evaporator 1140 to cool the intake air. As an example, if the intake air is 80°F/60% humidity, the secondary evaporator 1140 may discharge the airflow at 70°F/84% humidity. This causes the flow of refrigerant to partially evaporate within the secondary evaporator 1140. For example, if the refrigerant flow entering the secondary evaporator 1140 is 196 psig/68°F/5% steam, the refrigerant flow may be 196 psig/68°F/38% steam upon exiting the secondary evaporator 1140. ..

Secondary condenser 1120 receives the warmed refrigerant from secondary evaporator 1140 via tube 1106. Secondary condenser 1120 facilitates heat transfer from the flow of hot refrigerant through secondary condenser 1120 to the air stream. This reheats the air stream, thereby reducing the relative humidity. As an example, if the airflow rate is 54°F/98% humidity, the secondary capacitor 1120 may discharge the airflow rate at 65°F/68% humidity. This may cause the flow of refrigerant to partially or completely condense within the secondary condenser 1120. For example, if the refrigerant flow entering secondary condenser 1120 is 196 psig/68°F/38% steam, then the refrigerant flow may be 196 psig/68°F/4% steam as it exits secondary condenser 1120. .. The cooled refrigerant exits the secondary condenser at 1108 and is received by metering devices 1190a-c that distribute the refrigerant flow into the three circuits of the primary evaporator 1110. FIG. 14 shows a diagram including the circuitry of the primary evaporator 1110. The air stream passing through the primary evaporator 1110 may be cooled below its dew point temperature, condensing moisture in the air stream (thus reducing the absolute humidity of the air). As an example, if the air flow rate is 70°F/84% humidity, the primary evaporator 1110 may eject the airflow at 54°F/98% humidity. This may cause the flow of refrigerant to partially or completely evaporate within the primary evaporator 1110.

Each of secondary metering devices 1190a, 1190b, and 1190c is configured to supply a desired flow rate of refrigerant to each circuit of primary evaporator 1110. For example, the flow rate delivered to each circuit can be optimized to improve the performance of the primary evaporator 1110. For example, under certain operating conditions it may be beneficial to prevent the entire flow of refrigerant from passing through the entire evaporator, as occurs with traditional evaporator coils. Refrigerant flowing through such an evaporator changes from a liquid phase to a vapor phase before exiting the coil, resulting in poor performance in the portion of the evaporator that contacts only the gaseous refrigerant. To significantly reduce or eliminate this problem, the present disclosure provides a desired flow rate of refrigerant flow through each circuit. The desired flow rate can be predetermined (eg, based on known design criteria and/or operating conditions) and/or variable (eg, manually and/or automatically adjustable in real time) during operation. .. The flow rates can be configured so that the flow of refrigerant exits each circuit immediately after transition to gas. For example, the airflow rate near the evaporator edge may be less than near the evaporator center. Therefore, a lower refrigerant flow rate may be provided by the secondary metering devices 1190a-c to the circuit corresponding to the edge of the primary evaporator 1110.

The examples of FIGS. 11, 12, 13, and 14 include a primary evaporator subdivided into two or more circuits. In other embodiments, the secondary evaporator 1110 may also, or alternatively, the secondary evaporator 1110, be subdivided into two or more circuits. Also, it should be understood that the circuits illustrated by FIGS. 11, 12, 13, and 14 can also be accomplished with a single coil pack as shown in FIGS. 9 and 10.

Although a particular implementation of the dehumidification system portion 1100 is shown and described primarily, the present disclosure contemplates any suitable implementation of the dehumidification system portion 1100 according to particular needs. Further, while the various components of the dehumidification system portion 1100 are illustrated as being located in particular locations, the present disclosure contemplates that these components be located in any suitable location according to particular needs. It is intended.

As used herein, a computer-readable non-transitory storage medium may optionally include one or more semiconductor-based or other integrated circuits (ICs) (eg, field programmable gate arrays (FPGAs) or application-specific integrated circuits ( ASIC), hard disk drive (HDD), hybrid hard drive (HHD), optical disk, optical disk drive (ODD), magneto-optical disk, magneto-optical drive, floppy disk, floppy disk drive (FDD), magnetic tape, solid state drive ( SSD), RAM drive, secure digital card or drive, any other suitable computer readable non-transitory storage medium, or any suitable combination of two or more thereof. The computer-readable non-transitory storage medium may be volatile, non-volatile, or a combination of volatile and non-volatile, where appropriate.

As used herein, “or” is inclusive and not exclusive unless explicitly indicated otherwise or the context does not. Thus, as used herein, "A or B" means "A, B, or both," unless expressly stated otherwise or otherwise indicated by context. Furthermore, "and" are both solid and individual unless explicitly stated otherwise or indicated otherwise by context. Thus, herein, "A and B" means "A and B, either contiguously or individually," unless expressly indicated otherwise or indicated otherwise by context. .. The scope of the present disclosure includes all changes, substitutions, variations, alterations, and modifications to the exemplary embodiments described or illustrated herein as would be understood by a person skilled in the art. The scope of the present disclosure is not limited to the exemplary embodiments described or illustrated herein. Furthermore, although this disclosure describes and describes each embodiment herein as including a particular component, element, feature, function, operation, or step, any of these embodiments , And may include any combination or substitution of any of the components, elements, features, functions, acts, or steps described or illustrated anywhere in this specification, as would be understood by one of ordinary skill in the art. Ah Further, a device or system, or a configuration of a device or system, adapted, arranged, capable, configured, enabled, operable, or operative to perform a particular function. Reference in the appended claims to an element, whether or not possible, is that apparatus, system, or component so adapted, arranged, capable, configured, capable As long as it is enabled, operable, or operational, that device, system, or component is covered, whether or not that particular function is activated, turned on, or unlocked. Additionally, although this disclosure describes or illustrates certain embodiments as providing certain advantages, certain embodiments provide none, some, or all of these advantages. Can be provided.

Claims (15)

The dehumidification unit:
Primary weighing device;
Secondary weighing device;
A secondary evaporator:
Operable to receive a flow of refrigerant from the primary metering device; and operable to receive an intake air flow and discharge a first air flow, the first air flow being the intake air flow Containing cooler air, the first air stream being generated by transferring heat from the intake air stream to the refrigerant stream as the intake air stream passes through the secondary evaporator;
With a secondary evaporator:
The primary evaporator:
Operable to receive a flow of the refrigerant from the secondary metering device; and operable to receive the first air flow and discharge a second air flow, the second air flow Includes air that is cooler than the first air stream and the second air stream transfers heat from the first air stream to the refrigerant stream as the first air stream passes through the primary evaporator. Generated by transmitting;
A primary evaporator;
The secondary capacitor:
Is operable to receive a flow of the refrigerant from the secondary evaporator; and is operable to receive the second air flow and discharge a dehumidified air flow, the dehumidified air flow being the second Of air that is warmer and less humid than the air stream of, and the dehumidified air stream transfers heat from the refrigerant stream to the dehumidified air stream when the second air stream passes through the secondary condenser. Generated by;
With a secondary capacitor:
A first fan operable to produce the intake air stream, the first air stream, the second air stream, and the dehumidified air stream;
A dehumidifying unit; and a condenser unit comprising:
A second fan operable to generate a third air flow;
The sub-cooling coil:
Receiving the flow of the refrigerant from the primary condenser;
Discharging the flow of the refrigerant to the primary metering device;
Transferring heat from the refrigerant stream to the third air stream when the third air stream contacts the sub-cooling coil;
With a sub-cooling coil, which is operable as;
The primary capacitor is:
Receiving a flow of said refrigerant from a compressor;
Transferring heat from the refrigerant stream to the third air stream when the third air stream contacts the primary condenser;
And a primary capacitor operable to:
The compressor is operable to receive a flow of the refrigerant from the primary evaporator and supply the flow of the refrigerant to the primary condenser, the flow of the refrigerant supplied to the primary condenser is the compressor. A compressor having a higher pressure than the flow of the refrigerant received at;
Having a capacitor unit;
Dehumidification system. The sub-cooling coil and the primary capacitor are combined into a single coil unit,
The dehumidification system according to claim 1. Two or more members selected from the group consisting of the secondary evaporator, the primary evaporator, and the secondary capacitor are combined into a single coil pack,
The dehumidification system according to claim 1. The primary evaporator and/or the secondary evaporator has two or more circuits for the flow of the refrigerant,
The dehumidification system according to claim 1 or 3. A passive metering device and/or an active metering device operable to provide a subdivided flow of the refrigerant to the primary evaporator and/or the secondary evaporator,
The dehumidification system according to claim 4. The primary metering device and the secondary metering device are operable to provide a subdivided flow of the refrigerant to the primary evaporator and/or the secondary evaporator.
The dehumidification system according to claim 4. The second fan is configured to generate the third air flow at an air flow rate between about 2 and about 5 times the air flow rate of the first air flow generated by the first fan. Is operational,
The dehumidification system according to claim 1. The secondary metering device operates in a substantially open state,
The dehumidification system according to claim 1. The dehumidification unit:
Primary weighing device;
Secondary weighing device;
A secondary evaporator:
Operable to receive a flow of refrigerant from the primary metering device; and operable to receive an intake air flow and discharge a first air flow, the first air flow being the intake air flow Containing cooler air, the first air stream being generated by transferring heat from the intake air stream to the refrigerant stream as the intake air stream passes through the secondary evaporator;
With a secondary evaporator:
The primary evaporator:
Operable to receive a flow of the refrigerant from the secondary metering device; and operable to receive the first air flow and discharge a second air flow, the second air flow Includes air that is cooler than the first air stream and the second air stream transfers heat from the first air stream to the refrigerant stream as the first air stream passes through the primary evaporator. Generated by transmitting;
A primary evaporator;
The secondary capacitor:
Operable to receive a flow of the refrigerant from the secondary evaporator; and operable to receive the second air flow and discharge a third air flow, the third air flow being , Warmer and less humid than the second air stream, wherein the third air stream is drawn from the refrigerant stream to the third air stream when the second air stream passes through the secondary condenser. Produced by transferring heat to an air stream;
With a secondary capacitor:
The sub-cooling coil:
Operable to receive the flow of the refrigerant from a primary condenser;
Operable to discharge the flow of refrigerant to the primary metering device;
Operable to receive the third air stream and to discharge a dehumidified air stream, the dehumidified air stream comprising warmer and less humid air than the third air stream, the dehumidified air stream comprising: Is produced by transferring heat from the refrigerant stream to the dehumidified air stream as the third air stream passes through the sub-cooling coil;
With sub-cooling coil;
A first fan operable to produce the intake air stream, the first air stream, the second air stream, the third air stream, and the dehumidified air stream;
A dehumidifying unit; and a condenser unit comprising:
A second fan operable to generate a fourth air flow;
The sub-cooling coil:
Receiving the flow of the refrigerant from the primary condenser;
Discharging the flow of the refrigerant to the primary metering device;
Transferring heat from the refrigerant stream to the fourth air stream when the fourth air stream contacts the sub-cooling coil;
With a sub-cooling coil, which is operable as;
The primary capacitor is:
Receiving a flow of said refrigerant from a compressor;
Transferring heat from the refrigerant stream to the fourth air stream when the fourth air stream contacts the primary condenser;
And a primary capacitor operable to:
The compressor is operable to receive a flow of the refrigerant from the primary evaporator and supply the flow of the refrigerant to the primary condenser, the flow of the refrigerant supplied to the primary condenser is the compressor. A compressor having a higher pressure than the flow of the refrigerant received at;
Having a capacitor unit;
Dehumidification system. Two or more members selected from the group consisting of the secondary evaporator, the primary evaporator, the secondary capacitor, and the sub-cooling coil are combined into a single coil pack.
The dehumidification system according to claim 9. The primary evaporator and/or the secondary evaporator has two or more circuits for the flow of the refrigerant,
The dehumidification system according to claim 9 or 10. A passive metering device and/or an active metering device operable to provide a subdivided flow of the refrigerant to the primary evaporator and/or the secondary evaporator,
The dehumidification system according to claim 11. The primary metering device and the secondary metering device are operable to provide a subdivided flow of the refrigerant to the primary evaporator and/or the secondary evaporator.
The dehumidification system according to claim 11. The second fan is configured to generate the fourth air flow at an air flow rate between about 2 and about 5 times greater than the air flow rate of the first air flow generated by the first fan. Is operational,
The dehumidification system according to claim 9. The secondary metering device operates in a substantially open state,
The dehumidification system according to claim 9.

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