JP2020104108A - Dehumidifier with secondary evaporator and condenser coils in single coil pack - Google Patents

Abstract

To reduce or eliminate disadvantages and problems associated with previous systems.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 provides the flow of the refrigerant to the primary condenser.SELECTED DRAWING: Figure 1

Description

(Reference of related application)
This application claims priority to United States Non-Provisional Application No. 15/460,772, entitled "DEHUMIDIFIER WITH SECONDARY EVAPORATOR AND CONDENSER COILS," filed March 16, 2017 by Dwaine Walter Tucker et al. It is a continuation-in-part application, the entire text of which is incorporated herein by reference.

The present invention relates generally to dehumidification, and more specifically to dehumidifiers that include secondary evaporator and condenser coils.

In certain situations it is desirable to reduce the humidity of the air within the structure. For example, in fire and flood recovery applications, it may be desirable to quickly remove water from areas of damaged structure. To accomplish this, one or more (one or more) portable dehumidifiers can be placed in the structure to direct the dry air towards the water loss area. However, current dehumidifiers have proven inefficient in many respects.

Embodiments of the disclosure may reduce or eliminate disadvantages and problems associated with previous systems.

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 the inlet airflow and outputs a first airflow to the primary evaporator. The primary evaporator receives the first air stream and outputs the second air stream to the secondary condenser. The secondary condenser receives the second air stream and outputs a third air stream to the primary condenser. The primary condenser receives the third air stream and outputs a dehumidified air stream. The compressor receives a low temperature, low pressure refrigerant vapor stream from the primary evaporator and supplies a high temperature, high pressure refrigerant vapor stream to the primary condenser.

Certain embodiments of the present disclosure may provide one or more (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 a single refrigeration cycle, thereby reducing the compressor over typical systems without adding additional power to the compressor. Increase capacity. This in turn increases the overall efficiency of the system by providing more dehumidification per kilowatt of power used. The lower humidity of the output air stream may allow for an increased drying potential, which may be beneficial in certain applications (eg fire and flood recovery).

Particular embodiments of the present disclosure may include some, all, or none of the above advantages. One or more other technical advantages may be immediately apparent to those skilled in the art from the drawings, descriptions, and claims contained herein.

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

6 illustrates 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 may 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 may 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 may 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. 3 illustrates an exemplary condenser system for use in 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 in the systems described herein, according to certain embodiments. 6 illustrates an example of a single coil pack for use in the systems described herein, according to certain embodiments. 3 illustrates an example of a primary evaporator that includes three circuits for use in the systems described herein, according to certain embodiments. 3 illustrates an example of a primary evaporator that includes three circuits for use in the systems described herein, according to certain embodiments. 3 illustrates an example of a primary evaporator that includes three circuits for use in the systems described herein, according to certain embodiments. 3 illustrates an example of a primary evaporator that includes three circuits for use in the systems described herein, according to certain embodiments.

In certain situations it is desirable to reduce the humidity of the air within the structure. For example, in fire and flood recovery applications, it may be desirable to remove water from a damaged structure by placing one or more (one or more) portable dehumidifier units within the structure. .. As another example, it may be desirable to install a dehumidification unit within a central air conditioning system in areas experiencing high humidity level weather or in buildings where low humidity levels are required (eg, libraries). In addition, 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 various respects.

To address the inefficiencies and other problems of current dehumidification systems, the disclosed embodiments disclose that some of the refrigerant in a multi-stage system evaporates and condenses twice within one refrigeration cycle. And a dehumidification system including a secondary evaporator and a secondary condenser. This increases the compressor capacity for a typical system without adding any additional power to the compressor. This, in turn, 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 located within structure 102. Structure 102 may include all or a portion of a building or other suitable enclosed space, such as an apartment building, hotel, office space, commercial building, or private residence (eg, house). Evaporator system 104 receives inlet air 101 from within structure 102, reduces moisture in the received inlet air 101, and returns dehumidified air 106 back to structure 102. Evaporator system 104 may distribute dehumidified air 106 through structure 102 via an air duct, as illustrated.

Generally, dehumidification system 100 is a split system in which evaporator system 104 is coupled to remote condenser system 108 located outside 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 pressurizes the flow of refrigerant, thereby increasing the temperature of the refrigerant. The speed of the compressor may be modulated to achieve the desired operating characteristics. The condenser unit 112 cools the compressed refrigerant by receiving the compressed refrigerant vapor flow from the compressor unit 114 and promoting heat transfer from the refrigerant flow to ambient air outside the structure 102. Good. In certain embodiments, remote condenser system 108 may utilize a heat exchanger, such as a microchannel heat exchanger, to remove heat from the refrigerant stream. Remote condenser system 108 may include a fan that draws ambient air from outer structure 102 for use in cooling the flow of refrigerant. In a particular embodiment, the speed of the fan is modulated to achieve the desired operating characteristics. An exemplary embodiment of an exemplary condenser system is shown, for example, in FIG. 7 (described in more detail below).

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

In particular embodiments, the 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 air exiting the evaporator system 104 to various portions of the structure 102. The blower and evaporator system 104 may have separate return inlets that draw in air. In certain embodiments, the air exiting the evaporator system 104 may be mixed with air produced by another component (eg, an air conditioner) and blown by an air blower through an air duct. In other embodiments, the evaporator system 104 may both provide cooling and dehumidification, and thus may be used without conventional air conditioning.

Although particular embodiments of dehumidification system 100 are illustrated and primarily described, the present disclosure contemplates any suitable implementation of dehumidification system 100 according to particular needs. Moreover, although the various components of dehumidification system 100 are depicted as being located in particular locations, the present disclosure is directed to these components being located in any suitable location according to particular needs. Assume

FIG. 2 illustrates an exemplary portable dehumidification system 200 that reduces the humidity of the air within structure 102 in accordance with certain embodiments of the present disclosure. Dehumidification system 200 may be positioned anywhere within structure 102 to direct dehumidified air 106 to areas that require dehumidification (eg, water loss areas). Generally, the dehumidification system 200 receives an inlet airflow 101, removes water from the inlet airflow 101, and discharges dehumidified air 106 back into the structure 102. In particular embodiments, structure 102 includes a flooded space (eg, as a result of a flood or fire). To restore the water damage structure 102, one or more dehumidification systems 200 are provided within the structure 102 to dry the damaged portion of the structure 102 by rapidly reducing the humidity of the air within the structure 102. It may be strategically positioned.

Although a particular implementation of the portable dehumidification system 200 is illustrated and described primarily, the present disclosure contemplates any suitable implementation of the portable dehumidification system 200 according to particular needs. Moreover, although the various components of the portable dehumidification system 200 are depicted as being positioned at particular locations within the structure 102, the present disclosure describes that those components may be arranged according to particular needs. It is assumed that it can be located in any suitable place.

3 and 4 illustrate 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. ing. The 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 and. In some embodiments, dehumidification system 300 may additionally include a sub-cooling coil 350. In a particular embodiment, the sub-cooling coil 350 and the primary condenser 330 are combined into a single coil. As illustrated, the flow of refrigerant 305 is circulated through the dehumidification system 300. Generally, dehumidification system 300 receives an inlet air stream 101, removes water from the inlet air stream 101, and discharges dehumidified air 106. Water is removed from the inlet air 101 using a refrigerant 305 flow refrigeration cycle. However, by including the secondary evaporator 340 and the secondary condenser 320, the dehumidification system 300 vaporizes and condenses at least a portion of the flow of refrigerant 305 twice in a single refrigeration cycle. This increases refrigeration 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 condenser 320. The saturation temperatures of the secondary evaporator 340 and the secondary condenser 320 are generally controlled according to the formula (temperature of the intake air 101+temperature of the second air stream 315)/2. Evaporation occurs in the secondary evaporator 340 because the saturation temperature of the secondary evaporator 340 is lower than the inlet air 101. Condensation occurs in the secondary condenser 320 because the saturation temperature of the secondary condenser 320 is higher than the second air stream 315. 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 outputs the flow of refrigerant 305 to compressor 360. Primary evaporator 310 may be any type of coil (eg, fin tube, microchannel, etc.). The primary evaporator 310 receives the first air stream 345 from the secondary evaporator 340 and outputs the second air stream 315 to the 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 the refrigerant 305 stream, thereby at least partially redirecting the refrigerant 305 stream. Evaporate from liquid 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 outputs the flow of refrigerant 305 to secondary metering device 390. The secondary condenser 320 may 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 outputs a third air stream 325. The third air stream 325 is generally warmer and drier than the second air stream 315 (ie, has the same dew point but lower relative humidity). 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 at least partially directing the stream of refrigerant 305 from a gas to a liquid. To condense.

Primary condenser 330 receives the flow of refrigerant 305 from compressor 360 and outputs the flow of refrigerant 305 to either primary metering device 380 or subcooling coil 350. The primary condenser 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 outputs 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 completely 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 air stream in addition to the air stream 101. For example, the rightmost edge of primary condenser 330 of FIG. 4 may extend beyond the rightmost edge of secondary evaporator 340, primary evaporator 310, secondary condenser 320, and subcooling coil 350, or Overhang (overhang). This overhanging portion of primary condenser 330 may receive an additional, separate air stream.

Secondary evaporator 340 receives the flow of refrigerant 305 from primary metering device 380 and outputs 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 inlet air 101 and outputs a first air flow 345 to primary evaporator 310. First air stream 345 is generally at a lower temperature than inlet air 101. To cool the incoming inlet air 101, the secondary evaporator 340 transfers heat from the inlet air 101 to the flow of refrigerant 305, thereby at least partially evaporating the flow of refrigerant 305 from liquid to gas. Let

The sub-cooling coil 350, which is an optional component of the dehumidification system 300, sub-cools the liquid refrigerant 305 as it leaves the primary condenser 330. This, in turn, provides the primary metering device 380 with a liquid refrigerant that is 30 degrees (or a temperature above 30 degrees) lower than before the liquid refrigerant entered the sub-cooling coil 350. For example, if the flow of refrigerant 305 entering sub-cooling coil 350 is at 340 psig/105°F/60% steam, the flow of refrigerant 305 will be 340 psig/80 as the flow of refrigerant 305 exits sub-cooling coil 350. May be °F/0% steam. The sub-cooled refrigerant 305 has a higher coefficient of thermal enthalpy as well as density, which results in reduced cycle time and frequency of the evaporation cycle of the refrigerant 305 stream. This results in greater efficiency of dehumidification system 300 and less energy use. Embodiments of dehumidification system 300 may or may not include sub-cooling 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 another type of condenser 330 or Embodiments of dehumidification system 300 utilizing 320 may not include subcooling coil 350. As another example, a dehumidification system 300 utilized within a split system, such as dehumidification system 100, may not include a sub-cooling coil 350.

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

Fan 370 is operable to draw inlet air 101 into dehumidification system 300 and through secondary evaporator 340, primary evaporator 310, secondary condenser 320, subcooling coil 350, and primary condenser 330. , May include any suitable components. The fan 370 may be any type of blower (eg, axial fan, forward tilt impeller, rear tilt impeller, etc.). For example, the fan 370 may be a rearward tilt impeller positioned adjacent to the primary condenser 330, as illustrated in FIG. Although fan 370 is depicted 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. It should be. For example, the fan 370 may be positioned within the air flow path of any one of the air streams 101, 345, 315, 325, 355, or 106. Moreover, dehumidification system 300 may include one or more additional fans positioned within any one or more of these air passages.

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 thermal 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 to allow a change of state or expansion of liquid to vapor within evaporators 310 and 340. The high pressure liquid (or almost liquid) refrigerant entering metering devices 380, 390 is at a higher temperature than liquid refrigerant 305 exiting metering devices 380, 390. For example, if the flow of refrigerant 305 entering primary metering device 380 is at 340 psig/80°F/0% steam, the flow of refrigerant 305 will be 196 psig/68 as it exits primary metering device 380. May be °F/5% steam. As another example, if the flow of refrigerant 305 entering secondary metering device 390 is at 196 psig/68°F/4% steam, then the flow of refrigerant 305 will be when the flow of refrigerant 305 exits secondary metering device 390. And may be 128 psig/44°F/14% steam.

Refrigerant 305 may be any suitable refrigerant such as R410a. Generally, the dehumidification system 300 includes a compressor 360, a primary condenser 330, an (optional) sub-cooling coil 350, a primary metering device 380, a secondary evaporator 340, a secondary condenser 320, a secondary metering device. Utilizing a closed refrigerant loop of refrigerant 305 through 390 and primary evaporator 310. Compressor 360 pressurizes the flow of refrigerant 305, thereby increasing the temperature of refrigerant 305. Primary and secondary condensers 330 and 320, which may include any suitable heat exchangers, are provided for each air flow (ie, fourth) from the flow of refrigerant 305 through the primary and secondary condensers. Cooling the stream of pressurized refrigerant 305 by promoting heat transfer to the air stream 355 and the second air stream 315). The cooled refrigerant 305 stream exiting the primary and secondary condensers 330 and 320 is operable to reduce the pressure of the refrigerant 305 stream, thereby reducing the temperature of the refrigerant 305 stream, Each inflation device (ie, primary metering device 380 and secondary metering device 390) may be entered. Primary evaporator 310 and secondary evaporator 340, which may include any suitable heat exchangers, receive the flow of refrigerant 305 from secondary metering device 390 and primary metering device 380, respectively. The primary evaporator 310 and the secondary evaporator 340 facilitate the transfer of heat from the respective air streams passing through them (ie, the inlet air 101 and the first air stream 345) to the refrigerant 305 stream. 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 refrigeration loop described above may be configured such that evaporators 310 and 340 operate in a flooded condition. In other words, the flow of refrigerant 305 may enter the evaporators 310, 340 in the liquid state, and a portion of the flow of refrigerant 305 may still be in the liquid state as it exits the evaporators 310, 340. is there. 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, and approximately across evaporators 310 and 340. It provides a constant pressure and temperature (resulting in an increased cooling capacity).

In operation of the exemplary embodiment of dehumidification system 300, inlet air 101 may be drawn into dehumidification system 300 by fan 370. The inlet air 101 passes through the secondary evaporator 340, and heat is transferred from the inlet air 101 to the flow of the low temperature refrigerant 305 passing through the secondary evaporator 340. As a result, the inlet air 101 may be cooled. As an example, if the inlet air 101 is at 80°F/60% humidity, the secondary evaporator 340 may output a first air stream 345 at 70°F/84% humidity. This may partially evaporate the flow of refrigerant 305 within the secondary evaporator 340. For example, if the refrigerant 305 flow entering the secondary evaporator 340 is at 196 psig/68°F/5% steam, the refrigerant 305 flow will exit the secondary evaporator 340 at 196 psig/68°F/ It is 38% steam.

The cooled inlet air 101 exits the secondary evaporator 340 as a first air stream 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 stream of cold refrigerant 305 that passes through the primary evaporator 310. As a result, the first air stream 345 may be cooled to or below its dew point temperature to condense water within the first air stream 345 (thereby causing the first air stream 345 to condense). 345 may reduce absolute humidity). As an example, if the first air stream 345 is at 70°F/84% humidity, the primary evaporator 310 may output a second air stream 315 at 54°F/98% humidity. This may partially or completely evaporate the flow of refrigerant 305 within the primary evaporator 310. For example, if the flow of refrigerant 305 entering primary evaporator 310 is at 128 psig/44°F/14% vapor, then the flow of refrigerant 305 is 128 psig/52°F/100% as it exits primary evaporator 310. May be steam. In certain embodiments, liquid condensate from the first air stream 345 may be collected in a drain pan connected to a condensate reservoir, as illustrated in FIG. .. In addition, the condensate reservoir collects condensate collected at continuous or periodic intervals from the dehumidification system 300 (eg, via a drain hose) to an appropriate drain or storage location. A moving condensate condensate pump may be included.

The cooled first air stream 345 exits the first 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 output a 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 at 196 psig/68°F/38% vapor, the refrigerant 305 flow will exit the secondary condenser 320 at 196 psig/68°F/38°C. It is 4% steam.

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 output 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 at 340 psig/150°F/100% vapor, the refrigerant 305 flow will exit the primary condenser 330 at 340 psig/105°F/60%. May be steam.

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 promotes heat transfer from the flow of the hot refrigerant 305 passing through the sub-cooling coil 350 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 airflow 325 is at 65°F/68% humidity, the sub-cooling coil 350 may output a fourth airflow 355 at 81°F/37% humidity. This may cause the flow of refrigerant 305 to partially or completely condense within the subcooling coil 350. For example, if the refrigerant 305 flow entering the sub-cooling coil 350 is at 340 psig/150°F/60% steam, the refrigerant 305 flow will exit the sub-cooling coil 350 at 340 psig/80°F/0%. May 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 receives and processes any suitable input device, output device, mass storage medium, or data (such as a keypad, touch screen, mouse, or other device capable of accepting information). And may include other suitable components for storing, storing, and communicating. Both input and output devices may be fixed or removable storage media, such as magnetic computer disks, CD-ROMs, or other suitable media that receives input from and provides output to the user. May be included. Each computer system may include a personal computer, workstation, network computer, kiosk, wireless data port, personal digital assistant (PDA), one or more processors in these or other devices, or any other suitable processing device. May be included. Briefly, 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, operating alone or in conjunction with other components of dehumidification system 300, herein. It may provide some or all of the functionality described in the book. The controller may additionally include computer memory (or may be communicatively coupled to the computer memory via wireless or wired communication). The memory may include any memory or database module, magnetic media, optical media, random access storage (RAM), read only storage (ROM), removable media, or any other suitable local or remote memory. It may take the form of volatile or non-volatile memory, including but not limited to components.

Although particular embodiments of dehumidification system 300 have been illustrated and primarily described, the present disclosure contemplates any suitable implementation of dehumidification system 300 according to particular needs. Moreover, although the various components of dehumidification system 300 are depicted as being positioned in particular locations as well as with respect to each other, the present disclosure contemplates that those components may be arranged in accordance with any particular needs. It is assumed that it can be positioned in a suitable place.

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, where the secondary evaporator receives an inlet airflow and outputs a first airflow. In some embodiments, the second evaporator is the second evaporator 340. In some embodiments, the inlet airflow is inlet air 101 and the first airflow is first airflow 345. In some embodiments, the secondary evaporator of step 510 receives the refrigerant flow from a primary metering device, such as the primary metering device 380, and directs the refrigerant flow (in the altered state) to the secondary condenser 320. Supply to a secondary condenser. In some embodiments, the refrigerant stream of method 500 is the refrigerant 305 stream described above.

At step 520, the primary evaporator receives the first air stream of step 510 and outputs a 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 a flow of refrigerant from a secondary metering device, such as secondary metering device 390, and directs the refrigerant flow (in the altered state) to compressor 360. Supply to the compressor.

At step 530, the secondary condenser receives the second air stream of step 520 and outputs a third air stream. In some embodiments, the secondary condenser is secondary condenser 320 and the third air stream is third air stream 325. In some embodiments, the secondary condenser of step 530 receives the flow of refrigerant from the secondary evaporator of step 510 and directs the flow of refrigerant (in the altered state) to a secondary metering device 390. Supply to the weighing device.

At step 540, the primary condenser receives the third air stream of step 530 and outputs a 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 stream from the compressor of step 520 and provides the refrigerant stream (in the altered state) to the primary metering device of step 510. In an alternative embodiment, the primary condenser of step 540 provides a flow of refrigerant (in the altered state) to a sub-cooling coil, such as sub-cooling coil 350, which then cools the flow of refrigerant. (In the changed state) to the primary weighing device of step 510.

At step 550, the compressor receives the flow of refrigerant from the primary condenser of step 520 and provides (in the altered 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, as appropriate. Although this disclosure describes and illustrates certain 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. Moreover, this disclosure describes and illustrates an exemplary dehumidification method for reducing the humidity of air in a structure, including certain steps of the method of FIG. 5. Any suitable method for reducing the humidity of the air in the structure, including any suitable steps that may include all or some of the method steps of FIG. 5 or may not include any of the method steps of FIG. Assuming a different method. Further, although this disclosure describes and illustrates particular components, devices, or systems that perform certain steps of the method of FIG. 5, this disclosure performs any suitable step of the method of FIG. Assume any suitable combination of any suitable components, devices, or systems for execution.

The exemplary method of FIG. 5 is sometimes described above with respect to the dehumidification system 300 of FIG. 3, but the same or similar method is described above for dehumidification systems 600 and 800 of FIGS. 6 and 8 (described below). It should be understood that any of the dehumidification systems described herein, including can be performed. Moreover, with respect to the exemplary method of FIG. 500, references to evaporators or condensers are 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 any single coil pack evaporator or condenser portion may be referred to.

FIG. 6 illustrates an exemplary dehumidification system 600 that may be used in accordance with the split 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 typically indoors, and a condenser system 604 (eg, condenser system 108 in FIG. 1). The dehumidifying 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 condensing. The vessel system 604 includes a primary condenser 630, a compressor 660, an optional sub-cooling coil 650, and a second fan 695.

As illustrated, a flow of refrigerant 605 is circulated through the dehumidification system 600. Generally, dehumidification unit 602 receives inlet air stream 601, removes water from inlet air stream 601, and discharges dehumidified air 625 into a conditioned space. Water is removed from the inlet air 601 using a refrigerant 605 flow refrigeration cycle. The flow of refrigerant 605 through system 600 of FIG. 6 proceeds similar to the flow of refrigerant 305 through dehumidification system 300 of FIG. However, as described herein, the path of airflow through system 600 is different than the path of airflow through system 300. 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 a single refrigeration cycle. This increases refrigeration capacity over a typical system without requiring additional power to the compressor, thereby increasing the overall efficiency of the system.

The split configuration of system 600, including dehumidification unit 602 and condenser system 604, allows heat from the cooling and dehumidification process to be released outdoors or to an unconditioned space (eg, outside the dehumidified space). To be able to be done. This allows the dehumidification system 600 to have a footprint similar to that of a typical central air conditioning system or heat pump. Generally, the temperature of the third air stream 625 output from the system 600 to the conditioned space is significantly reduced compared to the temperature of the air stream 106 output from the system 300 of FIG. Thus, the configuration of system 600 allows dehumidified air to be provided to the conditioned space at a reduced temperature. As such, system 600 may perform the functions of both a dehumidifier (to dehumidify air) and a central air conditioner (to cool air).

Generally, dehumidification system 600 attempts to match the saturation temperature of secondary evaporator 640 to the saturation temperature of secondary condenser 620. The saturation temperatures of the secondary evaporator 640 and the secondary condenser 620 are generally controlled according to the formula (temperature of the inlet air 601 + temperature of the second air stream 615)/2. Evaporation occurs in secondary evaporator 640 because the saturation temperature of secondary evaporator 640 is lower than inlet air 601. Condensation occurs in the secondary condenser 620 because the saturation temperature of the secondary condenser 620 is higher than the second air stream 615. The amount of the refrigerant 605 evaporated in the secondary evaporator 640 is substantially equal to the amount condensed in the secondary condenser 620.

Primary evaporator 610 receives the flow of refrigerant 605 from secondary metering device 690 and outputs the flow of refrigerant 605 to compressor 660. 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 outputs 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, primary evaporator 610 transfers heat from first air stream 645 to a stream of refrigerant 605, thereby at least partially refrigerating stream 605. Evaporate from liquid to gas. Also, this transfer of heat from the first air stream 645 to the flow of refrigerant 605 removes water from the first air stream 645.

Secondary condenser 620 receives the flow of refrigerant 605 from secondary evaporator 640 and outputs the flow of refrigerant 605 to secondary metering device 690. The secondary condenser 620 can be any type of coil (eg, fin tube, microchannel, etc.). The secondary condenser 620 receives the second air flow 615 from the first evaporator 610 and outputs the third air flow 625. The third air stream 625 is generally warmer than the second air stream 615 and drier than the second air stream (ie, the dew point is the same as the second air stream 615). , The relative humidity is lower than the second air flow 615). Secondary condenser 620 produces a third air flow 625 by transferring heat from the flow of refrigerant 605 to a second air flow 615, thereby at least partially directing the flow of refrigerant 605 from a gas to a liquid. To condense. As mentioned above, the third airflow 625 is output into the conditioned space. In another embodiment (eg, as shown in FIG. 8), the third airflow 625 is first subcooled coil 650 before being output into the conditioned space at a further reduced relative humidity. May pass through and/or pass over.

Refrigerant 605 flows to the compressor 660 outdoors or in an unregulated space or condenser system 604. 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 at 128 psig/52°F/100% steam, then the flow of refrigerant 605 will exit compressor 660 at 340 psig/150°F/100% steam. Sometimes there is. 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.

The primary condenser 630 receives the flow of the refrigerant 605 from the compressor 660 and outputs the flow of the refrigerant 605 to the sub cooling coil 650. The primary condenser 630 can be any type of coil (eg, fin tube, microchannel, etc.). The primary condenser 630 and the sub-cooling coil 650 receive the first outside airflow 606 and output the second outside airflow 608. The second outside airflow 608 is generally warmer (ie, has a lower relative humidity than the first outside airflow 606) than the first outside 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 implementations, the primary condenser 630 condenses the stream of refrigerant 605 completely to liquid (ie, 100% liquid). In other embodiments, the 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 a temperature above 30 degrees) lower than before the liquid refrigerant entered the sub-cooling coil 650. For example, if the flow of refrigerant 605 entering sub-cooling coil 650 is at 340 psig/105°F/60% vapor, the flow of refrigerant 605 will exit sub-cooling coil 650 at 340 psig/80°F/0%. May be steam. The sub-cooled refrigerant 605 has a higher thermal enthalpy coefficient as well as a higher density, which improves energy transfer between the air stream and the evaporator, resulting in additional latent heat removal from the refrigerant 605. This further results in higher efficiency of dehumidification system 600 and less energy use. Embodiments of dehumidification system 600 may or may not include subcooling coil 650.

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

Secondary evaporator 640 receives the flow of refrigerant 605 from primary metering device 680 and outputs 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 inlet air 601 and outputs a first air stream 645 to primary evaporator 610. The first air stream 645 is generally at a lower temperature than the inlet air 601. To cool the incoming inlet air 601, the secondary evaporator 640 transfers heat from the inlet air 601 to the stream of refrigerant 605, thereby at least partially liquid to gas. Evaporate.

Fan 670 includes any suitable components operable to draw inlet air 601 into dehumidification unit 602 and through secondary evaporator 640, primary evaporator 610, and secondary condenser 620. Good. The fan 670 may be any type of blower (eg, axial fan, forward tilt impeller, rear tilt impeller, etc.). For example, the fan 670 may be a rearward sloped impeller positioned adjacent to the secondary condenser 620.

Although fan 670 is depicted in FIG. 6 as being positioned adjacent condenser 620, it is understood that fan 670 may be located anywhere along the air flow path of dehumidification unit 602. There must be. For example, fan 670 may be positioned within the air flow path of any one of air streams 601, 645, 615, or 625. Moreover, the dehumidification unit 602 may include one or more additional fans positioned in any one or more of these air flow paths. Similarly, in FIG. 6, fan 695 of condenser system 604 is depicted as being located above primary condenser 630, but fan 695 is optional for condenser 630 and subcooling coil 650. (E.g., upper, lower, side), and thus the long fan 695 is properly positioned to promote the air flow 606 towards the primary condenser 630 and the subcooling coil 650 and Composed.

The rate of airflow produced by fan 670 may be different than the rate produced by fan 695. For example, the flow rate of airflow 606 generated by fan 695 may be higher than the flow rate of airflow 601 generated by fan 670. This difference in flow rate may provide several advantages for the dehumidification system described herein. For example, the large airflow produced by fan 695 may provide improved heat transfer in primary condenser 630 and subcooling coil 650 of condenser system 604. Generally, the velocity of the airflow produced by the second fan 695 is between about 2 and 5 times the velocity of the airflow produced by the first fan 670. For example, the velocity of the airflow produced by the first fan 670 may be about 200-400 cubic feet per minute (cfm). For example, the velocity of the airflow produced by the second fan 695 may 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 (TXV) 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 to allow a change of state or expansion of liquid to vapor in evaporators 610 and 640. The high pressure liquid (or mostly liquid) refrigerant entering metering devices 680 and 690 is at a higher temperature than liquid refrigerant 605 exiting metering devices 680 and 690. For example, if the flow of refrigerant 605 entering the primary metering device 680 is at 340 psig/80°F/0% steam, the flow of refrigerant 605 will exit the primary metering device 680 at 196 psig/68°F/5%. May be steam. As another example, if the flow of refrigerant 605 entering the secondary metering device 690 is at 196 psig/68°F/4% steam, the flow of refrigerant 605 will exit the secondary metering device 690 at 128 psig/44. May be °F/14% steam.

In certain embodiments, the secondary metering device 690 is configured 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 605 (herein “fully open”). (Referred to as the “state”) operates substantially in the open state. For example, the pressure of the refrigerant 605 may be 80%, 90%, 95%, 99%, or up to 100% of the pressure of the refrigerant 605 entering the metering device 690. If the secondary metering device 690 is operated in the “fully open” condition, the primary metering device 680 is the major source of pressure drop in the dehumidification system 600. In this configuration, the air stream 615 is not substantially heated as it passes through the secondary condenser 620 and the secondary evaporator 640, and the primary evaporator 610 and the secondary condenser 620 act as a single evaporator. It works effectively. Although less water may be removed from the air stream 601 when the secondary metering device 690 is operated in the “fully open” state, the air stream 606 causes the secondary metering device 690 to be in the “fully open” state. Outputs to a conditioned space at a lower temperature than when not in. This configuration creates a relatively high sensible heat ratio such that the dehumidification system 600 may produce a cooler airflow 625 with characteristics similar to those of the airflow produced by the central air conditioner. Corresponds to the (SHR) operation mode. If the speed 601 of the airflow is increased to a threshold (eg, by increasing the speed of the fan 670 or one or more other fans of the dehumidification system 600), the dehumidification system 600 removes water from the airflow 601. May be significantly cooled without doing so.

Refrigerant 605 may be any suitable refrigerant such as R410a. Generally, the dehumidification system 600 includes a compressor 660, a primary condenser 630, an (optional) sub-cooling coil 650, a first metering device 680, a secondary evaporator 640, a secondary condenser 620, a secondary metering device. Utilizing a closed refrigerant loop of refrigerant 605 through the device 690 and the first evaporator 610. Compressor 660 pressurizes the flow of refrigerant 605, thereby increasing the temperature of refrigerant 605. The primary condenser 630 and the secondary condenser 620, which may include any suitable heat exchangers, include respective air streams (ie, the first outside air stream 606 and the second outside air stream 606) from the flow of refrigerant 605. Cooling the flow of pressurized refrigerant 605 by promoting heat transfer to the air flow 615). The cooled refrigerant 605 flow exiting the primary and secondary condensers 630 and 620 reduces the pressure of the refrigerant 605 flow, respectively, thereby operable to reduce the temperature of the refrigerant 605 flow. Inflation devices (ie, primary metering device 680 and secondary metering device 690) may be entered. 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. The primary evaporator 610 and the secondary evaporator 640 facilitate the transfer of heat from the respective air streams (ie, the inlet air 601 and the first air stream 645) passing therethrough to the refrigerant 605 stream. The flow of refrigerant 605 exits the primary evaporator 610 and then returns to the compressor 660 and the cycle repeats.

In particular embodiments, the refrigeration loop described above may be configured such that evaporators 610 and 640 operate in a flooded condition. In other words, the flow of refrigerant 605 may enter the evaporators 610, 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, 640. Thus, a phase change in the flow of refrigerant 605 (from liquid to vapor when heat is transferred to the flow of refrigerant 605) occurs across evaporators 610 and 640, and approximately across evaporators 610 and 640. Provides a constant pressure and temperature (and consequently an increased cooling capacity).

In operation of the exemplary embodiment of dehumidification system 600, inlet air 601 may be drawn into dehumidification system 600 by fan 670. The inlet air 601 passes through the secondary evaporator 640, where heat is transferred from the inlet air 601 to the flow of the cold refrigerant 605 that passes through the secondary evaporator 640. As a result, the inlet air 601 may be cooled. As an example, if the inlet air 601 is at 80°F/60% humidity, the secondary evaporator 640 may output a first air stream 645 at 70°F/84% humidity. This may partially evaporate the flow of refrigerant 605 within the secondary evaporator 640. For example, if the flow of refrigerant 605 entering the secondary evaporator 640 is at 196 psig/68°F/5% vapor, the flow of refrigerant 605 will exit the secondary evaporator 640 at 196 psig/68°F/ May be 38% steam.

The cooled inlet air 601 exits the secondary evaporator 640 as a first air stream 645 and enters the primary evaporator 610. Similar to secondary evaporator 640, primary evaporator 610 transfers heat from first air stream 645 to the flow of cold refrigerant 605 that passes through primary evaporator 610. As a result, the first air stream 645 may be cooled to or below its dew point temperature to condense moisture in the first air stream 645 (thereby causing the first air stream 645 to condense). May reduce the absolute humidity of the air stream 645). As an example, if the first air stream 645 is at 70°F/84% humidity, the primary evaporator 610 may output a 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 at 128 psig/44°F/14% vapor, the flow of refrigerant 605 will be 128 psig/52°F/100% as it exits primary evaporator 610. May be steam. In certain embodiments, liquid condensate from first air stream 645 may be collected in a drain pan connected to a condensate reservoir, as illustrated in FIG. In addition, the condensate reservoir moves the collected condensate from the dehumidification system 600 (eg, via a drain hose) to a suitable discharge or storage location, either continuously or at periodic intervals. A product pump may be included.

Cooled first air stream 645 exits 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 at 54°F/98% humidity, the secondary condenser 620 may output a dehumidified air stream 625 at 65°F/68% humidity. This may cause the flow of refrigerant 605 to partially or fully condense within the secondary condenser 620. For example, if the refrigerant 605 flow entering the secondary condenser 620 is at 196 psig/68°F/38% vapor, the refrigerant 605 flow will exit the secondary condenser 620 at 196 psig/68°F/ May be 4% steam. In some embodiments, the second air stream 615 exits the secondary condenser 620 as a dehumidified air stream 625 and is output into the conditioned space.

The primary condenser 630 promotes heat transfer from the flow of the high-temperature refrigerant 605 passing through the primary condenser 630 to the first outside airflow 606. This heats the outside airflow 606, which is output as a second outside airflow 608 to the unconditioned space (eg, outdoors). As an example, if the first outside airflow 606 is at 65°F/68% humidity, the primary condenser 630 may output a second outside 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 at 340 psig/150°F/100% vapor, the refrigerant 605 flow will exit primary condenser 630 at 340 psig/105°F/60%. May be steam.

As mentioned above, some embodiments of the dehumidification system 600 may include a sub-cooling coil 650 in the airflow between the inlet of the condenser system 604 and the primary condenser 630. The sub-cooling coil 650 promotes heat transfer from the flow of the high-temperature coolant 605 passing through the sub-cooling coil 650 to the first outside airflow 606. This heats the first outside air flow 606, thereby increasing the temperature of the first outside air flow 606. As an example, if the first outside airflow 606 is at 65°F/68% humidity, the sub-cooling coil 650 may output an 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 at 340 psig/150°F/60% vapor, the flow of refrigerant 605 will exit subcooling coil 650 at 340 psig/80°F/0%. May be steam.

In the embodiment depicted in FIG. 6, the sub-cooling coil 650 is in the condenser system 604. This configuration minimizes the temperature of the third airflow 625 output in the conditioned space. An alternative embodiment is shown as dehumidification system 800 in FIG. 8 where dehumidification unit 802 includes a sub-cooling coil 650. In this embodiment, the airflow 625 first passes through the sub-cooling coil 650 before being output via the fan 670 as the airflow 855 to the conditioned space. Alternatively, as described herein, the fan 670 may be located anywhere within the dehumidification unit 802 along the airflow path, and one or more additional fans are included in the dehumidification unit 802. be able to.

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

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

The cooled inlet air 601 exits the secondary evaporator 640 as a first air stream 645 and enters the primary evaporator 610. Similar to secondary evaporator 640, primary evaporator 610 transfers heat from first air stream 645 to the flow of cold refrigerant 605 that passes through primary evaporator 610. As a result, the first air stream 645 may be cooled to or below its dew point temperature to condense moisture in the first air stream 645 (thereby causing the first air stream 645 to condense). May reduce the absolute humidity of the air stream 645). As an example, if the first air stream 645 is at 70°F/84% humidity, the primary evaporator 610 may output a 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 at 128 psig/44°F/14% vapor, the flow of refrigerant 605 will be 128 psig/52°F/100% as it exits primary evaporator 610. May be steam. In certain embodiments, liquid condensate from first air stream 645 may be collected in a drain pan connected to a condensate reservoir, as illustrated in FIG. In addition, the condensate reservoir moves the collected condensate from the dehumidification system 800 (eg, via a drain hose) to a suitable discharge or storage location, either continuously or at periodic intervals. A product pump may be included.

Cooled first air stream 645 exits 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 at 54°F/98% humidity, the secondary condenser 620 may output a dehumidified air stream 625 at 65°F/68% humidity. This may cause the flow of refrigerant 605 to partially or fully condense within the secondary condenser 620. For example, if the refrigerant 605 flow entering the secondary condenser 620 is at 196 psig/68°F/38% vapor, the refrigerant 605 flow will exit the secondary condenser 620 at 196 psig/68°F/ May be 4% steam. In some embodiments, the second air stream 615 exits the secondary condenser 620 as a dehumidified air stream 625 and is output into the conditioned space.

Dehumidified air stream 625 enters sub-cooling coil 650, which promotes heat transfer from the flow of hot refrigerant 605 passing through sub-cooling coil 650 to dehumidified air stream 625. This heats the dehumidified air stream 625, thereby further reducing the humidity of the dehumidified air stream 625. As an example, if the dehumidified airflow 625 is at 65°F/68% humidity, the sub-cooling coil 650 may output an airflow 855 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 at 340 psig/150°F/60% vapor, the flow of refrigerant 605 will exit subcooling coil 650 at 340 psig/80°F/0%. May be steam.

The primary condenser 630 promotes heat transfer from the flow of the high-temperature refrigerant 605 passing through the primary condenser 630 to the first outside airflow 606. This heats the outside airflow 606, which is output as a second outside airflow 608 into the unconditioned space. As an example, if the first outside airflow 606 is at 65°F/68% humidity, the primary condenser 630 may output a second outside 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 at 340 psig/150°F/100% vapor, the refrigerant 605 flow will exit primary condenser 630 at 340 psig/105°F/60%. It may be steam.

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 and processes any suitable input device, output device, mass storage medium, or data (such as a keypad, touch screen, mouse, or other device capable of accepting information). Other suitable components for storing, storing, and communicating. Both input and output devices may be fixed or removable storage media, such as magnetic computer disks, CD-ROMs, or other suitable media that receives input from and provides output to the user. May be included. Each computer system may include a personal computer, workstation, network computer, kiosk, wireless data port, personal digital assistant (PDA), one or more processors in these or other devices, or any other suitable processing device. May be included. Briefly, 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, respectively, operating alone or in conjunction with other components of dehumidification systems 600 and 800, Some or all of the functionality described herein may be provided. The controller may additionally include computer memory (or may be communicatively coupled to the computer memory via wireless or wired communication). The memory may include any memory or database module, magnetic media, optical media, random access storage (RAM), read only storage (ROM), removable media, or any other suitable local or remote memory. It may take the form of volatile or non-volatile memory, including but not limited to components.

Although particular embodiments of dehumidification systems 600 and 800 are shown and described primarily, the present disclosure contemplates any suitable implementation of dehumidification systems 600 and 800 according to particular needs. Moreover, although the various components of dehumidification systems 600 and 800 are depicted as being placed in particular locations and relative to each other, the present disclosure is not limited to those components in accordance with particular needs. It is assumed that it will be located in the appropriate place of.

In certain embodiments, the secondary evaporator (340, 640), primary evaporator (310, 610), and secondary condenser (320, 620) of FIG. 3, FIG. 6, or FIG. Installed in the coil pack. A single coil pack may include portions (eg, separate refrigerant circuits) that accommodate the functions of each of the secondary evaporator, primary evaporator, and secondary condenser 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 condenser 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, weighing devices 980 and 990 correspond to primary weighing device 380 and secondary weighing device 390 of FIG.

In general, metering devices 980 and 990 may be any suitable type of metering/inflating device. In some embodiments, metering device 980 is a thermal 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 to allow a change of state or expansion of liquid to vapor within evaporator portions 910 and 940. The high pressure liquid (or almost 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 the metering device 980 is at 340 psig/80°F/0% steam, the flow of refrigerant 905 will exit the primary metering device 980 at 196 psig/68°F/5% steam. May be As another example, if the flow of refrigerant 905 entering the secondary metering device 990 is at 196 psig/68°F/4% steam, the flow of refrigerant 905 will exit the secondary metering device 990 at 128 psig/44. May be °F/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 inlet airflow 901 passes through the secondary evaporator portion 940, where heat is secondary evaporated from the inlet air 901. Is transferred to the flow of cold refrigerant 905 through the vessel portion 940. As a result, the inlet air 901 may be cooled. As an example, if the inlet air 901 is at 80°F/60% humidity, the secondary evaporator portion 940 may output a first air stream at 70°F/84% humidity. This may partially vaporize the flow of refrigerant 905 within the secondary evaporator portion 940. For example, if the flow of refrigerant 905 entering the secondary evaporator portion 940 is at 196 psig/68°F/5% steam, the refrigerant 905 flow will exit the secondary evaporator portion 940 at 196 psig/68°. May be F/38% steam.

The cooled inlet air 901 travels through the coil pack 900 and reaches the primary evaporator section 910. Similar to secondary evaporator portion 940, primary evaporator portion 910 transfers heat from air stream 901 to the flow of cold refrigerant 905 that passes through primary evaporator portion 910. As a result, the air stream 901 may be cooled to or below its dew point temperature to condense moisture within the air stream 901 (which reduces the absolute humidity of the air stream 901). Sometimes). As an example, if the air stream 901 is at 70°F/84% humidity, the primary evaporator portion 910 may cool the air stream 901 to 54°F/98% humidity. This may cause the flow of refrigerant 905 to partially or completely evaporate within the primary evaporator section 910. For example, if the flow of refrigerant 905 entering the primary evaporator portion 910 is at 128 psig/44°F/14% vapor, the flow of refrigerant 905 will exit the primary evaporator portion 910 at 128 psig/52°F/ It may be 100% steam. In certain embodiments, the liquid condensate from the air flow through the primary evaporator portion 910 is drain pan connected to a condensate reservoir (eg, as illustrated in FIG. 4 and described herein). May be collected in. In addition, the condensate reservoir moves the collected condensate, either continuously or at regular intervals, from the coil pack 900 (eg, via a drain hose) to a suitable discharge or storage location. A product pump may be included.

The cooled air stream 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, thereby reducing its relative humidity. As an example, if the airflow 901 is at 54°F/98% humidity, the secondary condenser portion 920 may output an 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 section 920. For example, if the flow of refrigerant 905 entering secondary condenser portion 920 is at 196 psig/68°F/38% vapor, then the refrigerant 905 flow will exit secondary condenser portion 920 at 196 psig/68°. May be F/4% steam. Outlet airflow 925 may enter primary condenser portion 330 or subcooling coil 350 of FIG. 3, for example.

Although particular embodiments of coil pack 900 are illustrated and primarily described, the present disclosure contemplates any suitable embodiment of coil pack 900 according to particular needs. Moreover, although the various components of the coil pack 900 are depicted as being placed in particular locations, the present disclosure is directed to these components being positioned in any suitable location according to particular needs. Assume

In certain embodiments, the secondary evaporator (340, 640) and secondary condenser (320, 620) of FIG. 3, FIG. 6, or FIG. It is incorporated into a single coil pack to include a portion (eg, a separate refrigerant circuit) that accommodates each function of the condenser. 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 condenser portion 1020. As shown in the illustrative example of FIG. 10, primary evaporator 1010 is located between secondary condenser portion 1020 and secondary evaporator portion 1040 of single coil pack 1000. In this exemplary embodiment, a single coil pack 1000 is shown as a "U" shaped coil. However, alternative embodiments may be used as long as flowing air stream 1001 passes sequentially through secondary evaporator portion 1040, primary evaporator 1010, and secondary condenser portion 1020. In general, a single coil pack 1000 can include the same or different coil types as compared to the coil type of primary evaporator 1010. For example, the single coil pack 1000 may include a microchannel coil type, while 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 inlet air 1001 passes through the secondary evaporator portion 1040, where heat is transferred from the inlet air 1001 to the secondary evaporator portion 1040. Is transferred to the flow of cold refrigerant through the vessel portion 1040. As a result, the inlet air 1001 may be cooled. As an example, if the inlet air 1001 is at 80°F/60% humidity, the secondary evaporator portion 1040 may output an airflow at 70°F/84% humidity. This may cause the refrigerant stream to partially evaporate within the secondary evaporator portion 1040. For example, if the refrigerant flow entering the secondary evaporator 1040 is at 196 psig/68°F/5% steam, the refrigerant 1005 flow will exit the secondary evaporator portion 1040 at 196 psig/68°F/ May be 38% steam.

The cooled inlet air 1001 exits the secondary evaporator section 1040 and enters the primary evaporator 1010. Similar to the secondary evaporator portion 1040, the primary evaporator 1010 transfers heat from the air stream 1001 to the cold refrigerant stream passing through the primary evaporator 1010. As a result, the airflow 1001 may be cooled to or below its dewpoint temperature to condense moisture within the airflow 1001 (which reduces the absolute humidity of the airflow 1001). Sometimes). As an example, if the airflow 1001 entering the primary evaporator 1010 is at 70°F/84% humidity, the primary evaporator 1010 may output an airflow at 54°F/98% humidity. This may cause the refrigerant stream to partially or completely evaporate within the primary evaporator 1010. For example, if the refrigerant flow entering the primary evaporator 1010 is at 128 psig/44°F/14% steam, then the refrigerant flow is 128 psig/52°F/100% steam as it exits the primary evaporator 1010. Sometimes there is. In certain embodiments, liquid condensate from air stream 1010 may be collected in a drain pan connected to a condensate reservoir, as illustrated in FIG. In addition, the condensate reservoir collects the collected condensate, either continuously or at regular intervals, from the primary evaporator 1010 and associated dehumidification system (eg, via a drain hose) to a suitable drain or store. A condensate pump may be included to move to the location.

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 and thereby reduces its relative humidity. As an example, if the airflow 1001 entering the secondary condenser portion 1020 is at 54°F/98% humidity, the secondary condenser 1020 may output an airflow 1025 at 65°F/68% humidity. is there. 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 at 196 psig/68°F/38% vapor, the refrigerant flow will exit the secondary condenser 1020 at 196 psig/68°F/4. May be% steam. Outlet airflow 925 may enter primary condenser 330 or subcooling coil 350 of FIG. 3, for example.

Although particular embodiments of coil pack 1000 are illustrated and described primarily, the present disclosure contemplates any suitable implementation of coil pack 1000 according to particular needs. Moreover, although the various components of the coil pack 1000 are depicted as being placed in particular locations, the present disclosure will place them in any suitable location according to particular needs. Imagine that.

In certain embodiments, one or both of the secondary evaporator (340, 640) and the primary evaporator (310, 610) of FIG. 3, 6, or 8 has two or more (two or more). ) Circuit. In such an embodiment, each circuit of the subdivided evaporator(s) is supplied with refrigerant by a corresponding metering device. The weighing device may include a passive weighing device, an active weighing 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 may be configured to supply refrigerant to each circuit within the evaporator at a desired mass flow rate. A 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 replace one or both of metering devices 380 and 390. Good.

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

In operation of the exemplary embodiment of portion 1100 of the dehumidification system, the flow of cooled (or subcooled) refrigerant is provided, for example, from subcooling coil 350 or primary condenser 330 of dehumidification system 300 of FIG. Received at entrance 1102. The primary metering device 1180 determines the flow rate of refrigerant into the secondary evaporator 1140. Although FIGS. 11, 12, 13, and 14 are shown to have a single primary metering device 1180, other embodiments (e.g., secondary evaporator 1140 provides refrigerant flow). Due to, multiple primary weighing devices can be included in parallel (if they include more than one circuit).

As the cooled refrigerant passes through the secondary evaporator 1140, heat is exchanged between the refrigerant and the airflow passing through the secondary evaporator 1140 to cool the inlet air. As an example, if the inlet air is at 80°F/60% humidity, the secondary evaporator 1140 may output an air stream at 70°F/84% humidity. This may cause the refrigerant stream to partially evaporate within the secondary evaporator 1140. For example, if the refrigerant flow entering the secondary evaporator 1140 is at 196 psig/68°F/5% vapor, then the refrigerant flow will exit the secondary evaporator 1140 at 196 psig/68°F/38%. May be steam.

Secondary condenser 1120 receives the warmed refrigerant from secondary evaporator 1140 via tube 1106. The secondary condenser 1120 facilitates heat transfer from the hot refrigerant stream through the secondary condenser 1120 to the air stream. This reheats the air stream, thereby reducing its relative humidity. As an example, if the airflow rate is at 54°F/98% humidity, the secondary condenser 1120 may output the airflow rate at 65°F/68% humidity. This may partially or completely condense the refrigerant stream within the secondary condenser 1120. For example, if the refrigerant flow entering the secondary condenser 1120 is at 196 psig/68°F/38% vapor, the refrigerant flow will exit the secondary condenser 1120 at 196 psig/68°F/4%. May be steam.

The cooled refrigerant exits the secondary condenser at 1108 and is received by metering devices 1190a-1190c, which distribute the refrigerant flow into three circuits of primary evaporator 1110. FIG. 14 shows a diagram including the circuit of the primary evaporator 1110. The airflow passing through the primary evaporator 1110 may be cooled to or below its dewpoint temperature to condense water in the airflow (thus reducing the absolute humidity of the air). Sometimes). As an example, if the airflow is at 70°F/84% humidity, the primary evaporator 1110 may output the airflow at 54°F/98% humidity. This may cause partial or complete evaporation of the refrigerant stream within the primary evaporator 1110.

Each of secondary metering devices 1190a, 1190b, and 1190c is configured to provide a flow of refrigerant to each circuit of primary evaporator 1110 at a desired flow rate. For example, the flow rate provided to each circuit may be optimized to improve the performance of the primary evaporator 1110. For example, under certain operating conditions, it may be beneficial to prevent all flow of refrigerant from passing through the entire evaporator, as occurs in conventional evaporator coils. Refrigerant flowing through such evaporators may undergo a change from a liquid phase to a vapor phase before exiting the coil, resulting in poor performance in those parts of the evaporator that contact only the gaseous refrigerant. To significantly reduce or eliminate this problem, the present disclosure provides a desired flow of refrigerant through each circuit. The desired flow rate may be predetermined during operation (eg, based on known design criteria and/or operating conditions) and/or variable (eg, manually and/or automatically adjustable in real time). May be The flow rates may be configured such that the flow of refrigerant exits its respective circuit immediately after transition to gas. For example, the velocity of the airflow near the edge of the evaporator may be less than near the center of the evaporator. Accordingly, the secondary metering devices 1190a-1190c may provide a lower velocity refrigerant stream 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, also or alternatively, the secondary evaporator 1110 may be split into more than one circuit. It is also understood that the circuits illustrated by FIGS. 11, 12, 13, and 14 can also be achieved in a single coil pack, such as the single coil packs shown in FIGS. 9 and 10. Should be.

Although particular implementations of portion 1100 of the dehumidification system are illustrated and described primarily, the present disclosure contemplates any suitable implementation of portion 1100 of the dehumidification system, according to particular needs. Moreover, although the various components of the dehumidification system portion 1100 are depicted as being placed in particular locations, the present disclosure will position those components in any suitable location according to particular needs. Is supposed to be.

As used herein, a computer-readable non-transitory storage medium or media is one or more, as appropriate, such as a field programmable gate array (PPGA) or an application specific integrated circuit (ASIC). Semiconductor based or other integrated circuit, hard disk drive (HDD), hybrid hard drive (HHD), optical disk, optical disk drive (ODD), magneto-optical disk, magneto-optical drive, floppy diskette, 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 different from the context. Thus, herein, "A or B" means "A, B, or both" unless the content clearly dictates otherwise or the context dictates otherwise. .. Moreover, “and” is both a bond and some, unless the context clearly indicates otherwise or the context indicates otherwise. Thus, as used herein, "A and B" are "combined or individually, A and B," unless expressly indicated otherwise or different by context. Means The scope of this disclosure includes all changes, substitutions, variations, changes, and modifications to the exemplary embodiments described or illustrated herein as will be understood by those skilled in the art. The scope of this disclosure is not limited to the exemplary embodiments described or illustrated herein. Moreover, although this disclosure describes and illustrates each embodiment herein as including a particular component, element, configuration, function, operation, or step, any of these embodiments Or a combination or substitution of any of the components, elements, configurations, functions, acts, or steps described or exemplified anywhere herein, as would be understood by a person of ordinary skill in the art. May be included. Furthermore, the device or system, or a component of the device or system, in the appended claims, is adapted, configured, enabled, operable, or operational to perform a particular function. Reference to, or to the extent that the device, system, or component is so adapted, arranged, capable, configured, validated, operational, or operational, The device, the system, the component, the device, the system, the component, regardless of whether the features of the device are activated, turned on, or unlocked. In addition, although this disclosure describes or illustrates certain embodiments as providing certain advantages, certain embodiments may not provide any of these advantages or may provide one or more of these advantages. Part or all may be provided.

Claims (25)

A primary weighing device,
A secondary weighing device,
Coil pack with sub cooling coil,
A compressor,
Including fans and
The coil pack includes a secondary evaporator portion, a primary evaporator portion, and a secondary condenser portion,
The secondary evaporator portion is
Receives a flow of refrigerant from the primary metering device,
Receives an inlet airflow and outputs a first airflow,
Is capable of working like
The first air stream includes air that is cooler than the inlet air stream, the first air stream from the inlet air stream as the inlet air stream passes through the secondary evaporator portion. Produced by transferring heat to the flow of the refrigerant,
The primary evaporator portion is
Receiving the flow of the refrigerant from the secondary metering device,
Receiving the first air stream and outputting a second air stream,
Is capable of working like
The second air stream comprises air that is cooler than the first air stream, and the second air stream is the first air stream when the first air stream passes through the primary evaporator portion. Generated by transferring heat from one air stream to the refrigerant stream,
The secondary condenser part is
Receiving a flow of the refrigerant from the secondary evaporator section,
Receiving the second air stream and outputting a third air stream,
Is capable of working like
The third air stream comprises air that is hotter and less humid than the second air stream, the third air stream being such that when the second air stream passes through the secondary condenser section. Generated by transferring heat from the refrigerant stream to the third air stream,
The sub-cooling coil,
Receives a flow of the refrigerant from a primary condenser,
Outputting the flow of the refrigerant to the primary metering device,
Receiving the third air stream and outputting a fourth air stream,
Is capable of working like
The fourth air stream comprises air at a higher temperature and a lower humidity than the third air stream, the fourth air stream comprising: when the third air stream passes through the sub-cooling coil; Generated by transferring heat from the refrigerant stream to the fourth air stream,
The primary condenser is
Receives the flow of the refrigerant from the compressor,
Receiving the fourth air stream and outputting a dehumidified air stream,
Is capable of working like
The dehumidified air stream comprises air that is hotter and less humid than the fourth air stream, and the dehumidified air stream comprises: when the fourth air stream passes through the primary condenser; Produced by transferring heat from the refrigerant stream to the dehumidified air stream,
The compressor is operable to receive a flow of the refrigerant from the primary evaporator and provide a flow of the refrigerant to the primary condenser, the flow of the refrigerant provided to the primary condenser being , Including a pressure higher than the flow of the refrigerant received at the compressor,
The fan is operable to generate the inlet airflow, the first airflow, the second airflow, the third airflow, the fourth airflow, and a dehumidified airflow. Is
Dehumidification system. The dehumidification system of claim 1, wherein the primary evaporator portion of the coil pack and/or the secondary evaporator portion of the coil pack includes two or more circuits for refrigerant flow. .. 3. A passive and/or active metering device operable to provide a subdivided flow of refrigerant to the primary evaporator portion and/or the secondary evaporator portion of the coil pack. The dehumidification system described in. The primary metering device and the secondary metering device are operable to provide a subdivided flow of the refrigerant to the primary evaporator portion and/or the secondary evaporator portion of the coil pack. Item 2. The dehumidifying system according to Item 2. The dehumidification system according to claim 1, wherein the dehumidification system is included in a self-contained, portable dehumidification unit. The dehumidification system of claim 1, wherein the dehumidification system is operable to evaporate and twice condense the refrigerant in a single refrigeration cycle. The dehumidification system of claim 1, wherein the secondary metering device is operated in a substantially open state. A compressor,
A primary condenser,
A coil pack including a primary evaporator portion, a secondary evaporator portion, and a secondary condenser portion,
The secondary evaporator portion is operable to receive an inlet air stream and output a first air stream, the first air stream comprising air cooler than the inlet air stream, The first air stream is generated by transferring heat from the inlet air stream to a refrigerant stream as the inlet air stream passes through the secondary evaporator section;
The primary evaporator portion is operable to receive the first air stream and output a second air stream, the second air stream having a lower temperature than the first air stream. Air, and the second air stream is generated by transferring heat from the first air stream to the refrigerant stream as the first air stream passes through the primary evaporator portion. ,
The secondary condenser portion is operable to receive the second air stream and output a third air stream, the third air stream having a higher temperature than the second air stream. Air with low humidity, the third air flow transfers heat from the refrigerant flow to the third air flow when the second air flow passes through the secondary condenser portion. Is generated by
The primary condenser is operable to receive the third air stream and output a dehumidified air stream, the dehumidified air stream having a lower humidity than the third air stream. The dehumidified air stream containing hot air is generated by transferring heat from the refrigerant stream to the dehumidified air stream as the third air stream passes through the primary condenser. Is
The compressor is operable to receive the flow of refrigerant from the primary evaporator portion of a single coil pack and provide the flow of refrigerant to the primary condenser.
Dehumidification system. 9. The dehumidification system of claim 8, wherein the primary evaporator portion of the coil pack and/or the secondary evaporator portion of the coil pack includes two or more circuits for refrigerant flow. .. 10. A passive and/or active metering device operable to provide subdivided refrigerant flow to the primary evaporator portion and/or the secondary evaporator portion of the coil pack. The dehumidification system described in. A primary weighing device,
Further comprising a secondary weighing device,
The primary metering device and the secondary metering device are operable to provide a subdivided flow of refrigerant to the primary evaporator portion and/or the secondary evaporator portion of the coil pack,
The dehumidification system according to claim 9. The secondary metering device is a fixed or variable inflation device,
The primary metering device is a fixed or variable inflation device,
The dehumidification system according to claim 11. 10. The fan of claim 9, further comprising a fan operable to produce the inlet air stream, the first air stream, the second air stream, the third air stream, and the dehumidified air stream. Dehumidification system described. 10. The dehumidification system of claim 9, wherein the dehumidification system is contained within a self-contained, portable dehumidification unit. The dehumidification system of claim 9, wherein the dehumidification system is operable to evaporate the refrigerant twice and condense it twice in a single refrigeration cycle. The dehumidification system of claim 11, wherein the secondary metering device is operated in a substantially open state. A compressor,
A primary condenser,
A primary evaporator,
A coil pack including a secondary evaporator portion and a secondary condenser portion,
The secondary evaporator portion is operable to receive an inlet air stream and output a first air stream, the first air stream comprising air cooler than the inlet air stream, The first air stream is generated by transferring heat from the inlet air stream to a refrigerant stream as the inlet air stream passes through the secondary evaporator section;
The primary evaporator is operable to receive the first air stream and output a second air stream, the second air stream being cooler than the first air stream. The second air stream is generated by transferring heat from the first air stream to the refrigerant stream as the first air stream passes through the primary evaporator;
The secondary condenser portion is operable to receive the second air stream and output a third air stream, the third air stream having a higher temperature than the second air stream. Air with low humidity, the third air flow transfers heat from the refrigerant flow to the third air flow when the second air flow passes through the secondary condenser portion. Is generated by
The primary condenser is operable to receive the third air stream and output a dehumidified air stream, the dehumidified air stream having a lower humidity than the third air stream. The dehumidified air stream containing hot air is generated by transferring heat from the refrigerant stream to the dehumidified air stream as the third air stream passes through the primary condenser. Is
The compressor is operable to receive the flow of refrigerant from the primary evaporator of a single coil pack and provide the flow of refrigerant to the primary condenser.
Dehumidification system. 18. The dehumidification system of claim 17, wherein the primary evaporator and/or the secondary evaporator portion of the coil pack includes two or more circuits for refrigerant flow. 18. A stationary and/or variable metering device operable to provide a subdivided flow of refrigerant to the primary evaporator and/or the secondary evaporator portion of the coil pack. Dehumidification system. A primary weighing device,
Further comprising a secondary weighing device,
The primary metering device and the secondary metering device are operable to provide a subdivided flow of refrigerant to the secondary evaporator portion of the primary evaporator and/or the coil pack.
The dehumidification system according to claim 17. The secondary metering device is a fixed or variable inflation device,
The primary metering device is a fixed or variable inflation device,
The dehumidification system according to claim 17. 18. The method of claim 17, further comprising a fan operable to produce the inlet air stream, the first air stream, the second air stream, the third air stream, and the dehumidified air stream. Dehumidification system described. 18. The dehumidification system of claim 17, wherein the dehumidification system is contained within a self-contained, portable dehumidification unit. 18. The dehumidification system of claim 17, wherein the dehumidification system is operable to evaporate and twice condense the refrigerant in a single refrigeration cycle. 21. The dehumidification system of claim 20, wherein the secondary metering device is operated in a substantially open condition.

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