Patent Publication Number: US-11391474-B2

Title: System, components, and methods for air, heat, and humidity exchanger

Description:
CROSS-REFERENCE TO RELATED APPLICATIONS 
     This application claims the benefit of priority under 35 U.S.C. § 119 to U.S. Provisional Patent Application No. 62/620,386, filed on Jan. 22, 2018, and the benefit of priority under 35 U.S.C. § 120 to U.S. patent application Ser. No. 15/228,541, filed on Aug. 4, 2016, all of which are incorporated herein by reference in their entireties. 
    
    
     FIELD OF THE DISCLOSURE 
     Embodiments of the present disclosure include heat and moisture transfer systems and components thereof and, more particularly, heat and moisture exchangers, membranes for exchangers, methods of manufacturing exchangers, energy recovery ventilator (ERV) and evaporative cooling systems employing heat and moisture exchanges, and gas exchange systems and components thereof. 
     BACKGROUND OF THE DISCLOSURE 
     Heat and water vapor exchangers (also sometimes referred to as humidifiers, enthalpy exchangers, or energy recovery wheels) have been developed for a variety of applications. These include building ventilation (HVAC), medical and respiratory applications, gas drying or separation, automobile ventilation, airplane ventilation, and for the humidification of fuel cell reactants for electrical power generation. In various devices intended for the exchange of heat and/or water vapor between two airstreams, it may be desirable to have a thin, inexpensive heat or moisture transfer material. In some devices, it may desirable to transfer moisture across the material. In some devices, it may be desirable to transfer heat across the material. And, in some devices, it may be desirable to transfer both heat and moisture from one stream to the other. In each of these applications, it may be desirable that air and contaminants within one stream are not permitted to migrate to the other stream. 
     Planar plate-type heat and water vapor exchangers may use membrane plates that are constructed using discrete pieces of a planar, water-permeable membrane (for example, Nafion®, natural cellulose, sulfonated polymers or other synthetic or natural membranes) supported by a separator material (which may or may not be integrated into the membrane) and/or frame. The membrane plates may typically be stacked, sealed, and configured to accommodate fluid streams flowing in either cross-flow or counter-flow configurations between alternate plate pairs, so that heat and water vapor is transferred via the membrane, while limiting the cross-over or cross-contamination of the fluid streams. In some heat and water vapor exchanger designs, separate membrane plates may be replaced by a single membrane core made by folding a continuous strip of membrane in a concertina, zig-zag, or accordion fashion, with a series of parallel alternating folds. Similarly, for heat exchangers, a continuous strip of material may be patterned with fold lines and folded along these lines to form a configuration appropriate for heat exchange. 
     Membrane cores may be employed as heat and/or moisture exchanger(s) for ventilation systems, HVAC systems, air filter systems, energy recovery ventilator (ERV) systems, and evaporative cooling systems. The present disclosure is directed to improvements in existing membranes, methods of fabricating them, membrane cores, systems, method of fabricating them, and systems utilizing membrane cores. 
     SUMMARY OF THE DISCLOSURE 
     In accordance with an embodiment, an air handling module may comprise a housing and an exchanger contained within the housing. The air handling module may further comprise a first manifold positioned on a first side of the housing and including a first pair of ports arranged on a first end and a second pair of ports arranged on a second end and a second manifold positioned on a second side of the housing and including a first pair of ports arranged on a first end and a second pair of ports arranged on a second end. The first pair of ports of the first manifold may be in fluid communication with the first pair of ports of the second manifold to transfer air through the exchanger and between the first and second manifolds, and the second pair of ports of the first manifold may be in fluid communication with the second pair of ports of the second manifold to transfer air through the exchanger and between the first and second manifolds. 
     In accordance with another embodiment, a method of manufacturing a membrane material for an enthalpy exchanger may comprise imparting a charge onto microporous particles, coating a first roller and a second roller with the charged microporous particles, feeding a substrate between the first and second rollers, and applying heat and pressure to transfer the charged microporous particles from the first and second rollers onto the substrate. 
     In accordance with another embodiment, an air conditioner may comprise an exchanger including multiple layers of folded membrane material defining a stack of alternating first and second fluid passageways, wherein the first fluid passageways may be configured to receive a first air stream and the second fluid passageways are configured to receive a second air stream. The air conditioner may further comprise a liquid distribution system including a first header including a first distribution channel for delivering a first liquid to the first fluid passageways, a second header including a second distribution channel for delivering a second liquid to the second fluid passageways, a first plurality of porous members in communication with the first distribution channel and in contact with inner surfaces of the first fluid passageways, and a second plurality of porous members in communication with the second distribution channel and in contact with inner surfaces of the second fluid passageways. The first plurality of porous members may be configured to provide a continuous flow of the first liquid onto the inner surfaces of the first fluid passageways, and the second plurality of porous members may be configured to provide a continuous flow of the second liquid onto the inner surfaces of the second fluid passageways. 
     In accordance with another embodiment, an insulating structure may comprise a rotationally-molded shell including an interstitial space and an insulating material disposed within the interstitial space, wherein the insulating material may be one or more of: metal oxide powder; inorganic oxide powder; silica powder; fumed silica powder; and aerogel powder. 
     In yet another embodiment, a method for manufacturing a separator may comprise delivering a sheet of netting material between a first continuous belt having a first corrugated surface and a second continuous belt having a second corrugated surface, mating together the first and second corrugated surfaces, applying heat and pressure to the sheet of netting material to form a corrugated netted sheet, releasing the corrugated netted sheet from the first and second continuous belts, cooling the corrugated netted sheet, and applying a constant tension on the corrugated netted sheet as the corrugated netted sheet is released from the first and second continuous belts. 
    
    
     
       BRIEF DESCRIPTION OF THE DRAWINGS 
         FIG. 1  illustrates a perspective view of an exemplary air handling module having a plurality of modular features, according to an exemplary disclosed embodiment; 
         FIG. 2  illustrates an exploded view of an exemplary air handling module having a plurality of modular features, according to an exemplary disclosed embodiment; 
         FIGS. 3 a -3 d    illustrate cross-sectional perspective views of internal channel tracks of the air handling module, according to an exemplary disclosed embodiment; 
         FIGS. 4 a -4 h    illustrate perspective views of a rotary damper, according to an exemplary disclosed embodiment; 
         FIGS. 5 a  and 5 b    illustrate perspective views of access panels, according to an exemplary disclosed embodiment; 
         FIGS. 6 a -6 h    illustrate cross-sectional views of fan boxes facilitating air flow into and out of the air handling module and interchangeable exchanger dividers facilitating a crossflow airflow pattern, according to an exemplary disclosed embodiment; 
         FIGS. 7 a  and 7 b    illustrate perspective views of an exemplary air handling system, according to an exemplary disclosed embodiment; 
         FIGS. 8 a  and 8 b    illustrate cross-sectional perspective views of an exemplary air handling system, according to an exemplary disclosed embodiment; 
         FIG. 9 a    illustrates a perspective of an exemplary air handling system, according to an exemplary disclosed embodiment; 
         FIGS. 9 b -9 g    illustrate cross-sectional views of an exemplary air handling system in exemplary configurations, according to an exemplary disclosed embodiment; 
         FIGS. 10 a -10 e    illustrate psychrometric charts corresponding to the operations of an air handling system, according to an exemplary disclosed embodiment; 
         FIGS. 11 a  and 11 b    illustrate perspective views of an exemplary process for manufacturing a membrane for an exchanger, according to an exemplary disclosed embodiment; 
         FIG. 12  illustrates a perspective view of one layer of a separator, according to an exemplary disclosed embodiment; 
         FIGS. 13 a -13 d    illustrate perspective views of an exemplary process for manufacturing a separator, according to an exemplary disclosed embodiment; 
         FIGS. 14 a -14 c    illustrate perspective views of air filters with a separator, according to an exemplary disclosed embodiment; 
         FIGS. 15 a -15 c    illustrate perspective views of an evaporative cooling and/or steam regenerating liquid desiccant air conditioner module, according to an exemplary disclosed embodiment; 
         FIGS. 15 d -15 h    illustrate perspective views of a liquid distribution system including first and second distribution headers and related components, according to an exemplary disclosed embodiment; 
         FIGS. 15 i  and 15 j    illustrate perspective views of exemplary configurations of an evaporative liquid desiccant hex shaped exchange module, according to an exemplary disclosed embodiment; 
         FIG. 15 k    illustrates a perspective view of a multiple function remote energy recovery system, according to an exemplary disclosed embodiment; 
         FIG. 15 l    illustrates a psychrometric chart corresponding to the operation of an evaporative cooling and/or steam regenerating liquid desiccant air conditioner module, according to an exemplary disclosed embodiment; 
         FIGS. 16 a -16 d    illustrate perspective views of a wall panel formed of a rotationally molded shell, according to an exemplary disclosed embodiment; 
         FIGS. 16 e  and 16 f    illustrate perspective views of interior and exterior surfaces of a building formed of building panels made of rotationally molded shells, according to an exemplary disclosed embodiment; 
         FIG. 16 g    illustrates a perspective view of a three-way wall connector formed of a rotationally molded shell, according to an exemplary disclosed embodiment; 
         FIG. 16 h    illustrates a perspective view of a corner wall connector formed of a rotationally molded shell, according to an exemplary disclosed embodiment; 
         FIG. 16 i    illustrates a perspective view of a three-way floor connector formed of a rotationally molded shell, according to an exemplary disclosed embodiment; and 
         FIG. 16 j    illustrates a perspective view of a three-way roof connector formed of a rotationally molded shell, according to an exemplary disclosed embodiment. 
     
    
    
     DETAILED DESCRIPTION 
     Reference will now be made in detail to the exemplary embodiments of the present disclosure described above and illustrated in the accompanying drawings. 
     Air Handling Module, Air Handling System, and Rotary Damper 
       FIG. 1  illustrates an air handling module  100  according to the present disclosure. In some embodiments, air handling module  100  may be an energy recovery ventilation (ERV) system and may utilize return air (RA) from a space or a building to precondition outside air (OA) for an HVAC system. Air handling module  100  may include a housing  120  having a top  130 , a bottom  140 , and sides  110 . Furthermore, air handling module  100  may include a first pair of ports  103 ,  104  fluidly connected to a second pair of ports  101 ,  102 , and a third pair of ports  107 ,  108  fluidly connected to a fourth pair of ports  105 ,  106 . 
     Fan box  181  may be coupled to port  101  and may contain one or more fans  189  configured to draw outside air (OA) from ports  103  and/or  104  and through an exchanger  213 . Fan box  186  may be coupled to port  106  and may contain one or more fans  189  configured to draw return air (RA) from a port  108  and through a filter  191 . An access panel  177  may attach to and detach from port  107  via panel connectors  107 . Connectors  107  may include any suitable connection mechanisms, such as, for example, latches, screws, and the like. Access panel  177  may be detached from port  107  to provide access for replacing filter  191 . 
     Ports  101 - 108  may serve as interchangeable attachment points for a number of additional structures, such as, for example, metal ducts, weather hoods, roof curbs, and/or other fluidly connected components of an HVAC system. Ports  101 - 108  may include any suitable means, including, for example, mechanical latches, flanges, friction fit, interference fit, removable fasteners, and the like, to readily connect and disconnect components to air handling module  100 . 
     Air handling module  100  may also include a port  109  that may provide access to electrical, power, and economizer sections of air handling module  100 . Housing  120  may include a plurality of external and internal ports configured to facilitate a modular hydronic distribution and collection system. For example, in some embodiments, housing  120  may include side drain ports  112 , side liquid desiccant drain port  118 , top drain ports  133 , top liquid desiccant port  137 , top liquid desiccant port  138 , and top evaporative port  139 . These ports of the hydronic distribution and collection system may serve as interchangeable attachment points for a plurality of components, including, for example, a condensate drain pipe, an evaporative water supply pipe, an evaporative water drain pipe, a liquid desiccant supply pipe, a liquid desiccant drain pipe, a refrigerant line conduit, a chilled water conduit, a steam pipe, and/or other fluidly connected hydronic components of an HVAC system. In some embodiments, the ports may be threaded and may incorporate gasketed seals. 
     Housing  120  may also include a plurality of external and internal ports configured to facilitate a modular system for components for local communications network, electrical distribution, and power distribution. For example, in some embodiments, housing  120  may include side conduit port  114  and top conduit port  134 . Air handling module  100  may facilitate modular connectivity with additional air handling modules  100  via top anchor ports  136  and bottom anchor ports  146 . 
       FIG. 2  illustrates an exploded view of an air handling module  200  according to the present disclosure. As shown in  FIG. 2 , air handling module  200  may include an exchanger  213  configured to transfer heat and moisture from the treated air stream. Exchanger  213  may be composed of any number of suitable materials to promote various air processing and conditioning objectives including, but not limited to, plastic plates, metal plates, enthalpy ceramic porous plates, cellulous plates, and various combinations thereof. Exchanger  213  may be contained within an exchanger housing  211 . Air handling module  200  may also provide for an integrated electrical cabinet. For example, in some embodiments, air handling module  200  may include a controller  250  configured to readily attach to and detach from housing  211 , an electrical disconnect  252 , and an actuator  232 . An electrical access panel  259  may cover the electrical cabinet and may be disconnected from air handling module  200  to provide access to the electrical cabinet via latches  256  and a disconnect handle  254 . 
     As shown in  FIG. 2 , air handling module  200  may further comprise one or more exchanger dividers  240 . Exchanger divider  240  may be configured to direct airflow into and out of exchanger  213 . Exchanger divider  240  may facilitate various airflow configurations and may be interchangeable with air handling module  200  depending on the application. In some embodiments, for example, exchanger divider  240  may facilitate cross-over airflow for air handling module  200 . In other embodiments, for example, exchanger divider  240  may facilitate parallel airflow. 
     As will be discussed in more detail below, manifolds  220  each flanking an exchanger divider  240  may include internal air channel tracks and an air director  222  to further facilitate air conditioning function modularity. Air handling module  200  may also include heat exchangers  292  and filters  291  contained within manifolds  220 . In some embodiments, heat exchanger  292  may be a suitable coil heat exchanger, such as, for example, condenser coils, evaporator coils, chilled water coils, hot water coils, and steam coils. Filter  291  may be any suitable particulate filter. It should be appreciated that in other embodiments, filter  291  may further include or be substituted for a variety of other components, such as, for example, UV lights, drop-stop filters, droplet separators, and gas absorption filters. As discussed above, the air handling module of the present disclosure may facilitate interchangeably connecting a variety of structures, such as, for example, metal ducts, weather hoods, roof curbs, and/or other fluidly connected components of an HVAC system. 
     As shown in  FIG. 2 , manifolds  220  include plurality of ports which serve as interchangeable attachment points for a number of structures, including, for example, fan box  280  attached via one or more latches  282 , a weather hood  260 , a metal duct  262 , and an access panel  270  attached via one or more latches  272 . Manifolds  220  may further include an aperture port to receive a rotary damper  230 . Rotary damper  230  may be controlled by actuator  232 . 
       FIGS. 3 a -3 d    illustrate perspective view of a manifold  300  of an air handling module according to the present disclosure. As discussed above, manifold  300  may comprise a number of interchangeable attachment points to fluidly connect a variety of components of an HVAC system, including, for example, fan boxes, metal ducts, weather hoods, roof curbs, access panel and/or other. Manifold  300  may include a top channel track  320  and a bottom channel track  322 . Channel track  320  and bottom channel track  322  may be separated by an air director  310  and a manifold divider  324  positioned between the tracks  320 ,  322 . Manifold  300  may further include a top slide channel  350 , a bottom slide channel  352 , and an economizer track  360 . In one embodiment, economizer track  360  may be a bearing track for a rotary damper. 
     Top slide channel  350  may receive an exchanger  390 . Exchanger  390  may slide into and out of top slide channel  350  as indicated by arrow  390   a . Exchanger  390  may be composed of any suitable thermal transfer devices, such as, for example, condensers, evaporators, fluid heat exchangers, and steam humidifiers. In one embodiment, exchanger  390  may be a suitable coil heat exchanger, such as, for example, condenser coils, evaporator coils, chilled water coils, hot water coils, and steam coils. Manifold  300  includes an inlet  392  and an outlet  394  to facilitate the flow of a heat transfer medium to and from exchanger  390 . 
     A heat transfer medium, including, for example, liquid refrigerant, steam, chilled water, or hot water, may enter exchanger  390  thru inlet  392  and may exit exchanger thru outlet  394 . Bottom slide channel  350  may receive a filter  391 . Filter  391  may slide into and out of bottom slide channel  352  as indicated by arrow  391   a . Filter  391  may be any suitable particulate filter. It should be appreciated that in other embodiments, filter  391  may further include or be substituted for a variety of other components, such as, for example, UV lights, drop-stop filters, droplet separators, and gas absorption filters. 
     Manifold  300  may also include a top drain port  332 , a bottom drain port  342 , and a side drain port  312 . Top drain port  332  may facilitate access to top slide channel  350  and may provide a modular hydronic collection system for top slide channel  350 . It should be appreciated that installers at an installation site may thereby access top drain port  332  according to site requirements. Top drain port  332  may be sealed by insulated plug  338 . Bottom drain port  342  may facilitate access to bottom slide channel  352  and may provide a hydronic collection system for bottom slide channel  352 . Side drain port  312  may provide an additional access and hydronic collection point for top channel track  320  in a direction perpendicular to top drain port  332 . In one embodiment, top drain port  332  may have a threaded configuration. For example, top drain port  332  may be threaded with type British Standard Parallel Pipe (BSPP) along with an integrated sealing washer. Persons of ordinary skill in the art would appreciate that BSPP is compatible with other international standards including NPT, NPTS, and BSPT, enabling a global distribution model. 
     Manifold  300  may further comprise top anchor ports  336  and bottom anchor ports  346  configured to provide structural connection to an adjacent manifold or various structural supports. Manifold  300  also includes a plurality of air ports  303 ,  304 ,  305 , and  306 . As shown in  FIG. 3 c   , in one embodiment, a duct  362  may be connected to manifold  300  via port  305 , and port  306  may be covered by an access panel  376 . Access panel  376  may include one or more latches  370  and a seal  371  to provide an air-tight connection to port  306 . 
     Port  303  and port  304  may be positioned perpendicular relative to each other. Likewise, port  305  and port  306  may be positioned perpendicular relative to each other. Such a configuration may facilitate multi-directional installation of components to manifold  300  and adjacent port ready access. Moreover, ports  303 ,  304 ,  305 , and  306  may provide a readily interchangeable and configurable manifold  300  for connecting to various HVAC and air handling components. Manifold  300  may facilitate a number of various on-site installation configuration options. Persons of ordinary skill would appreciate that any suitable number of access ports for manifold  300 , oriented in any suitable configuration, and positioned in any suitable location of manifold  300 , including, for example, the lateral, upper, and lower surfaces, is contemplated by the present disclosure. 
     In some embodiments, a fan box  380  containing one or more fans  389  may be attached to manifold  300  via port  304 . Fan box  380  may include one or more latches  382  and a seal  381  to provide an air-tight connection to port  304 . 
     As shown in  FIG. 4 a -4 h   , the air handling module  100  may also include a rotary damper  430 . Rotary damper  430  may include a rotatable semi-cylindrical member  471 . Rotary damper  430  may be configured to permit air flow in directions along the rotational axis of the semi-cylindrical member  471 . The rotary damper  430  may also be configured to permit air flow in directions other than along the rotational axis of semi-cylindrical member  471 . For example, the rotary damper  430  may permit air flow in directions normal to the rotational axis of semi-cylindrical member  471 . A single rotary damper  430  may eliminate the need for a pair of face and bypass dampers acting in unison. 
     Rotary damper  430  may have at least four potential modes within air handling module  100 . The first mode may be to facilitate a complete or partial economizer bypass around exchanger  213  in order to directly supply outside air (OA) as the supply air (SA), thereby providing free cooling to a building or enclosure. The second mode may be to facilitate a complete or partial defrost bypass around exchanger  213  in order to prevent ice buildup from cold outdoor air (e.g., below freezing). The third mode may be to facilitate a complete or partial bypass around exchanger  213  in order to modulate the sensible-to-latent ratio of supply air with a wrap-around air handling module. The fourth mode may be to facilitate a regeneration cycle within exchanger  213  to drive off water vapor, carbon dioxide, and/or other VOC contaminants. Other uses and modes for rotary damper  430  may be apparent to those skilled in the art and any such function may be used in the practice of the present disclosure. 
     Rotary damper  430  may comprise semi-cylindrical member  471 , shaft mounting plate  486  (which may be secured by bolts  487 ), and shaft  484  with utility tube  485  disposed within. Shaft  484  may be directly connected to rotary damper actuator  432  providing continuous clockwise and/or counterclockwise rotation. Semi-cylindrical member  471  may include an end wall  478  with integrated seal channel  483 , an outer surface  476  with integrated seal channel  482 , an inner surface  477 , and an end ring  479  with integrated seal channel  481 . In some embodiments, rotary damper  430  may be made of an insulating material and/or may be a hollow structure filled with insulating material, such as, for example, urethane foam, metal oxide, or fiberglass, to provide insulating qualities and to avoid condensation or ice accumulation. 
     Rotary damper  430  may be structurally positioned between manifold  400  and exchange divider  440 . Rotary damper  430  may be fluidly positioned between two air inlets. The first air inlet to rotary damper  430  may originate from exchanger  213  and may be physically located in bottom channel track  422  of manifold  400 , represented by arrow  466 . The second air inlet may be located at exchanger divider  440  and may originate from port  401 , represented by arrow  467 . Rotary damper  430  outlet may be fluidly positioned to and face port  404 . 
     For example, rotary damper  430  may be a rotary air damper configured to selectively control the source of the supply air (SA). In some embodiments, rotary damper  430  may be positioned in the bottom channel track  422  of the manifold  400 , as shown in  FIGS. 4 a -4 h   . Rotary damper  430  may be configured to selectively deliver treated air exiting from the exchanger  213  as supply air (SA) or directly deliver outside air (OA) as supply air (SA). Rotary damper  430  may include a manifold section  400  and an exchanger divider section  440  rotatably coupled to the manifold section  400 . The exchanger divider section  440  may include semi-cylindrical member  471  having a first opening  473  in fluid connection to the manifold section  400  and a second opening  472  on the side surface of the semi-cylindrical member  471 . In some embodiments, rotary damper  430  may be disposed within conventional ductwork or HVAC systems. 
     Rotary damper  430  may permit air flow in a direction along the X-rotational axis of the semi-cylindrical member  471 . Rotary damper  430  may also permit air flow in a direction other than along the X-rotational axis of the semi-cylindrical member  471 . The side surface of the semi-cylindrical member  471  opposite the second opening may block air flow. 
       FIG. 4 c    is a perspective view of rotary damper  430  according to the present disclosure. Rotary damper  430  may facilitate fluid inlet  472  along the X-axis shaft  484 , as well as fluid inlet  473  perpendicular to the X-axis shaft  484 . Fluid outlet  474  may pass through end ring  479  with integrated end sealed channel  481  containing end ring seal  490 . 
       FIG. 4 d    is another perspective view of rotary damper  430  according to the present disclosure. Fluid inlet  472  may pass through end ring  479  with integrated end sealed channel  481  containing end ring seal  490 . Rotary damper  430  may facilitate fluid outlet  475  along the X-axis shaft  484 , as well as fluid inlet  474  perpendicular to the X axis shaft  484 . 
     As shown in  FIG. 4 e   , the semi-cylindrical member  471  may be rotated about X-axis shaft  484  to a first position to adjust the direction of fluid flowing through the first opening  422  represented by fluid inlet  473  and second openings  404  represented by fluid outlet  468 . For example, the semi-cylindrical member  471  may be rotated to a first position, wherein the second fluid outlet  468  faces the outlet port  404  for the supply air (SA) stream. In the first position, treated air exiting from the exchanger  213  may be directed through the manifold  400  and the first and second openings  422 , then through  404  of the semi-cylindrical member  471 , and may then exit the air handling module  100  as supply air (SA). The outside air (OA) entering the air handling module  100  may be blocked by the end wall  478  of the semi-cylindrical member  471  opposite the second opening  404  and facing the direction of the outside air (OA) flow. End wall seal  489  may prevent or restrain fluid flow  473  from leaking thru to port opening  401 . 
     As shown in  FIG. 4 f   , the semi-cylindrical member  471  may be rotated about X-axis shaft  484  to a second position to adjust the direction of fluid flowing through the third opening  401  represented by fluid inlet  473  and second openings  404  represented by fluid outlet  468 . Semi-cylindrical member  471  may seal off passage  422 , and thus block fluid flow thru exchanger  213 . Outside air (OA) flow entering the air handling module  100  may enter the semi-cylindrical member  471  and may be directly delivered as supply air (SA). The rotation of the semi-cylindrical member  471  may be controlled by any suitable power source, such as, for example, a rotary motor  432 . End wall seal  489  may prevent or restrain fluid flow  473  from leaking thru to port opening  401 . 
     As shown in  FIG. 4 g   , the semi-cylindrical member  471  may also be rotated about X-axis shaft  484  to a third position to facilitate the installation or removal of air filter or coil  390 . Filter or coil  390  may slide in or out along bottom slide channel  452  as depicted by arrow  391   a . In this embodiment, end wall seal  489  may be positioned parallel to the bottom slide channel  452 . Rotary damper actuator  432  may include a manual override so that semi-cylindrical member  471  may be manually positioned to minimize any risk of injury or damage during operation. 
       FIG. 4 h    is a side view of rotary damper  430  according to the present disclosure. Rotary damper  430  may facilitate fluid inlet  472  along the X-axis shaft  484  as well as fluid inlet  473  in a direction other than along the X-axis shaft  484 . Fluid outlet  474  may pass through end ring  479  with integrated end sealed channel  481  containing end ring seal  490 . 
     Existing HVAC or ERV systems may employ multiple air dampers to control the direction of air flow. Each damper may be dedicated to controlling the direction of a single source of air flow. Typically, conventional air dampers may be rectangular or square shaped frames with movable louvers to permit and block the flow of air. Rotary damper  430  of the present disclosure may be positioned at the intersection of two different air flows and may regulate the direction of both air flows by rotating the semi-cylindrical member  471 . As a result, rotary damper  430  of the present disclosure obviates the need for multiple or separate air dampers. Semi-cylindrical member  471  of rotary damper  430  may be rotated by any desired amount to proportionally control and vary the mixing ratio of air streams and/or the volume of air passed through rotary damper  430 . 
       FIGS. 5 a  and 5 b    illustrate perspective views of an access panel  570  according to the present disclosure. As discussed above, access panel  570  may readily attach to, and detach from, air ports of an air handling module  500 . Access panel  570  may include one or more latches  572  to engage and hold access panel  570  onto an inner surface  577  of air handling module  500 . In one embodiment, latches  572  may include a screw and thread configuration to engage and disengage latches  572  by tightening or loosening the screw. Access panel  570  may also include a seal  573  disposed on an access panel seal channel. Seal  573  may engage with an outer surface  576  of air handling module  500  to provide an air-tight connection between the access panel  570  and the port. In other embodiments, a single twist handle (not shown) may actuate latches  572  in a linear or semi-circular fashion. Access panel  570  may operate in any orientation and may provide for complete, interchangeable access to internal components of the air handling module. 
       FIGS. 6 a -6 h    illustrate the modularity of the air handling module of the present disclosure by illustrating exemplary configurations of the air handling module.  FIG. 6 a    illustrates a cross-sectional view along the dashed line shown in  FIG. 1  of an air handling module  600  in a first configuration according to the present disclosure. Air handling module  600  may include a fan box  686  coupled to port  606  and a fan box  681  coupled to port  601 . Fan box  686  and fan box  681  may be configured to pull air flow into and out of a housing  620 . Air handling module  600  may include an air-to-air heat exchanger  612  contained within housing  620 . Air handling module  600  may also include a first pair of ports  601 - 602  fluidly connected to a second pair of ports  603 - 604 . One or both of the second pair of ports  603 - 604  may receive outside air (OA). Air may flow through housing  620  and may be discharged from air handing module  600  through one or both of the first pair of ports  601 - 602  as supply air (SA). Air handling module  600  may further include a third pair of ports  605 - 606  fluidly connected to a fourth pair of ports  607 - 608 . One or both of the fourth pair of ports  607 - 608  may receive return air (RA). Exhaust air (EA) may be discharged from air handing module  600  through one or both of the third pair of ports  605 - 606 . 
     Outside air (OA) may enter housing  620 , which may comprise sides  610 , through port  603  and may flow through opening  613 , while paired port  604  may be sealed by an access panel  674 . An air director  622  and an exchanger divider  640  may direct outside air (OA) through filter  691   a , exchanger  612 , and supply air coil  692   a . Exchanger  612  may be any suitable exchanger for promoting a variety of air processing and conditioning objectives, including, but not limited to, sensible plate type, enthalpy plate type, wheel type, heat pipe, indirect evaporation type, direct evaporation type, liquid desiccant type, carbon dioxide scrubbing, VOC scrubbing, and various other types of exchangers know to those skilled in the art. One or more fans  689  may be positioned inside fan box  681  and may pull supply air (SA) from exchanger  612 , through an opening  611 , and out of port  601 , while paired port  602  may be sealed by an access panel  672 . One or more fans  689  may be positioned inside fan box  686  and may pull exhaust air (EA) from exchanger  612  and out of port  606 , while paired port  605  may be sealed by access panel  675 . A rotary damper  631  may seal bypass openings  623 , and a port  609  may be sealed by an access panel  679 . 
     Return air (RA) may enter air handling module  600  through port  608 , while paired port  607  may be sealed by an access panel  677 . An air director  622  and an exchange divider  640  may direct return air (RA) through a filter  691   b , exchanger  612 , and an exhaust air coil  692   b . Supply air coil  692   a  and exhaust air coil  692   b  may be any suitable thermal transfer device for promoting a variety of air processing and conditioning objectives, including, but not limited to, a condenser coil, an evaporator coil, a chilled water coil, a hot water coil, a steam coil, a carbon dioxide scrubber, and/or a VOC scrubber. 
       FIG. 6 b    illustrates a cross-sectional view of air handling module  600  in a second configuration according to the present disclosure. As shown in  FIG. 6 b   , fan box  686  may be coupled to port  606  and fan box  681  may be coupled to port  601 . Fan box  686  and fan box  681  may be configured to push air flow into and out of housing  620 . One or both of third pair of ports  605 - 606  may receive outside air (OA). Air may flow through housing  620  and may be discharged from air handing module  600  through one or both of fourth pair of ports  607 - 608  as supply air (SA). One or both of first pair of ports  601 - 602  may receive return air (RA). Exhaust air (EA) may flow through housing  620  and may be discharged from air handing module  600  through one or more of second pair of ports  603 - 604 . 
     One or more fans  689  of fan box  686  may push outside air (OA) entering at port  606  through housing  620  and exchanger  612 , while paired port  605  may be sealed by access panel  675 . Air director  622  and exchanger divider  640  may direct outside air (OA) through filter  691   a , exchanger  612 , and supply air coil  692   b . One or more fans  689  of fan box  681  may push return air (RA) entering at port  601  through opening  611 , housing  620 , and exchanger  612 , while paired port  602  may be sealed by access panel  672 . Air director  622  and exchange divider  640  may direct return air (RA) through filter  691   b , exchanger  612 , and exhaust air coil  692   c . Supply air (SA) may exit port  608 , while paired port  607  may sealed by access panel  677 . Exhaust air (EA) may flow through opening  613  and exit port  603 , while paired port  604  may be sealed by access panel  674 . Rotary damper  631  may seals bypass openings  623 , and port  609  may be sealed by access panel  679 . 
       FIG. 6 c    illustrates a cross-sectional view of air handling module  600  in a third configuration according to the present disclosure. As shown in  FIG. 6 c   , a fan box  688  may be coupled to port  608  and fan box  681  may be coupled to port  601 . Fan box  688  and fan box  681  may be configured to push and pull air flow into and out of housing  620 . One or both of second pair of ports  603 - 604  may receive outside air (OA). Air may flow through housing  620  and may be discharged from air handing module  600  through one or both of first pair of ports  601 - 602  as supply air (SA). One or both of fourth pair of ports  607 - 608  may receive return air (RA). Exhaust air (EA) may flow through housing  620  and may be discharged from air handing module  600  through one or both of third pair of ports  605 - 606 . 
     Outside air (OA) may enter housing  620  through port  604  and may flow through opening  613 , while paired port  603  may be sealed by access panel  673 . Air director  622  and exchanger divider  640  may direct outside air (OA) through filter  691   a , exchanger  612 , and supply air coil  692   a . One or more fans  689  of fan box  681  may pull supply air (SA) from exchanger  612 , through opening  611 , and out of port  601 , while paired port  602  may be sealed by an access panel  672 . Rotary damper  631  and optional rotary damper  634  may seal bypass openings  623 , and access panel may  679  may seal port  609 . One or more fans  689  may be positioned inside of fan box  688  and may push return air (RA) entering at port  608  through housing  620  and exchanger  612 , while paired port  607  may be sealed by access panel  677 . Air director  622  and exchange divider  640  may direct return air (RA) through filter  691   b , exchanger  612 , and exhaust air coil  692   b . Exhaust air (EA) may exit port  605 , while paired port  606  may be sealed by an access panel  676 . 
       FIG. 6 d    illustrates a cross-sectional view of air handling module  600  in a fourth configuration according to the present disclosure. The embodiment of  FIG. 6 d    provides a configuration of air handling module  600 , wherein one air flow may bypass exchanger  612  to facilitate an economizer, a defrost, and/or a carbon dioxide scrubbing regeneration function. An economizer function may be an energy efficiency measure that may increase ventilation rates due to a lower pressure drop when bypassing exchanger  612 . The economizer function may be implemented during mild weather to reduce the need for mechanical cooling. Further, the economizer function may decrease respiratory issues by supplying a higher percentage of outside air. 
     As shown in  FIG. 6 d   , fan box  688  may be coupled to port  608  and fan box  681  may be coupled to port  601 . Fan box  688  and fan box  681  may be configured to push and pull air flow into and out of housing  620 . One or both of second pair of ports  603 - 604  may receive outside air (OA). Air may flow through housing  620  and may be discharged from air handing module  600  through one or both of first pair of ports  601 - 602  as supply air (SA). One or both of fourth pair of ports  607 - 608  may receive return air (RA). Exhaust air (EA) may flow through housing  620  and may be discharged from air handing module  600  through one or both of third pair of ports  605 - 606 . 
     Outside air (OA) may enter housing  620  through port  604  and may flow through an opening  613 , while paired port  603  may be sealed by an access panel  673 . Rotary damper  631  and optional rotary damper  634  may be actuated to block air path to exchanger  612  and redirect outside air (OA) through bypass openings  623 . One or more fans  689  of fan box  681  may pull supply air (SA) through bypass openings  623  and out of port  601 , while paired port  602  may be sealed by access panel  672 . One or more fans  689  of fan box  688  and may push return air (RA) entering at port  608  through housing  620  and exchanger  612 , while paired port  607  may be sealed by access panel  677 . Air director  622  and exchange divider  640  may direct return air (RA) through filter  691   b , exchanger  612 , and exhaust air coil  692   b . Exhaust air (EA) may exit port  605 , while paired port  606  may be sealed by access panel  676 . 
     One of the main challenges facing fixed plate air-to-air exchangers may be frost generation inside the exchanger during cold temperature conditions. Enthalpy exchangers may have a lower frost threshold temperature than sensible exchangers because enthalpy exchangers may transfer moisture between two airstreams. The rotary damper of the present disclosure may permit air bypass in the air handling module to prevent frost build-up in the exchanger. The rotary damper may modulate the amount of outside air volume by reducing or eliminating cold air flow through the exchanger. As a result, rotary damper may improve the performance of exchanger, resulting in higher temperatures of air supplied inside a room or building. In one exemplary embodiment, as the temperature of the exhaust air (EA) falls below an adjustable frost control set point (e.g., 28° F.), rotary damper  631  may be actuated to maintain the temperature at or above the frost control set point. By keeping the exhaust air (EA) at or above the frost control set point above (e.g., 28° F.), frost may be prevented from forming in exchanger  612 . 
       FIG. 6 e    illustrates a cross-sectional view of air handling module  600  in a fifth configuration according to the present disclosure. As shown in  FIG. 6 e   , fan box  682  may be coupled to port  602  and fan box  686  may be coupled to port  606 . Fan box  686  and fan box  682  may be configured to pull air flow into and out of housing  620 . One or both of second pair of ports  603 - 604  may receive outside air (OA). Air director  622  and exchanger divider  640  may direct outside air (OA) through filter  691   a , exchanger  612 , and supply air coil  692   a . Air may flow through housing  620  and may be discharged from air handing module  600  through one or both of first pair of ports  601 - 602  as supply air (SA). One or both of fourth pair of ports  607 - 608  may receive return air (RA). Exhaust air (EA) may flow through housing  620  and may be discharged from air handing module  600  through one or both of third pair of ports  605 - 606 . 
     One or more fans  689  may be positioned inside fan box  682  and may pull supply air (SA) from exchanger  612 , through opening  611 , and out of port  602 , while paired port  601  may be sealed by an access panel  671 . Return air (RA) may enter housing  620  through port  607 , while paired port  608  may be sealed by an access panel  678 . Air director  622  and exchange divider  640  may direct return air (RA) through filter  691   b , exchanger  612 , and exhaust air coil  692   b . One or more fans of fan box  686  may pull exhaust air (EA) from exchanger  612  and out of port  606 , while paired port  605  may be sealed by access panel  675 . 
       FIG. 6 f    illustrates a cross-sectional view of air handling module  600  in a sixth configuration according to the present disclosure. The embodiment of  FIG. 6 f    provides a configuration of air handling module  600 , wherein interchangeable exchanger  612  may facilitate a cross-flow air pattern within air handling module  600 . Fan box  686  may be coupled to port  606  and may be configured to push air flow into and out of housing  620 . Fan box  682  may be coupled to port  602  and may be configured to pull air flow into and out of housing  620  in series with fan box  686 . Return air (RA) may enter housing  620  through one or both of fourth pair of ports  607 - 608  and may be conveyed through housing  620  and exit though one or both of second pair of ports  603 - 604  as exhaust air (EA). Return air (RA) may be conveyed through and exit housing  620  as exhaust air (EA) by a remote HVAC system fan or building pressure differential. One or both of third pair of ports  605 - 606  may receive outside air (OA). Air may flow through housing  620  and may be discharged from air handing module  600  through one or both of first pair of ports  601 - 602  as supply air (SA). 
     Outside air (OA) may enter housing  620  through port  606 , while paired port  605  may be sealed by an access panel  675 . Air director  622  and exchanger divider  640  may direct outside air (OA) through filter  691   a , exchanger  612 , and supply air coil  692   a . One or more fans  689  of fan box  686  may push outside air (OA) through exchanger  612  and out of port  602  as supply air (SA), while paired port  601  may be sealed by access panel  671 . One or more fans  689  of fan box  682  may pull supply air (SA) out of port  602  in series with fan box  686 . Return air (RA) may enter housing  620  through port  607 , while paired port  608  may be sealed by access panel  678 . Air director  622  and exchange divider  640  may direct return air (RA) thru filter  691   b , exchanger  612 , and exhaust air coil  692   b . Exhaust air (EA) may exit port  603 , while paired port  604  may be sealed by access panel  674 . 
       FIG. 6 g    illustrates a cross-sectional view of air handling module  600  in a seventh configuration according to the present disclosure. As shown in  FIG. 6 g   , the interchangeable exchanger  612  may facilitate a cross-flow air pattern within air handling module  600 . Fan box  681  may be coupled to port  601  and may be configured to pull air flow into and out of housing  620 . A fan box  684  may be coupled to port  604  and may be configured to pull air flow into and out of housing  620 . One or both of third pair of ports  605 - 606  may receive outside air (OA). Air may flow through housing  620  and may be discharged from air handing module  600  through one or both of first pair of ports  601 - 602  as supply air (SA). Return air (RA) may enter housing  620  through one or both of fourth pair of ports  607 - 608  and may be conveyed through housing  620  and exit though one or both of second pair of ports  603 - 604  as exhaust air (EA). 
     Outside air (OA) may enter housing  620  through port  605 , while paired port  606  may be sealed by access panel  676 . Air director  622  and exchanger divider  640  may direct outside air (OA) through filter  691   a , exchanger  612 , and supply air coil  692   a . One or more fans  689  of fan box  681  may push outside air (OA) through exchanger  612  and out of port  601  as supply air (SA), while paired port  602  may be sealed by access panel  672 . Return air (RA) may enter housing  620  through port  608 , while paired port  607  may be sealed by access panel  677 . Air director  622  and exchange divider  640  may direct return air (RA) thru filter  691   b , exchanger  612 , and exhaust air coil  692   b . One or more fans  689  positioned inside fan box  684  may pull exhaust air (EA) out of port  604 , while paired port  603  may be sealed by access panel  673 . 
       FIG. 6 h    illustrates a cross-sectional view of air handling module  600  in an eighth configuration according to the present disclosure. As shown in  FIG. 6 h   , interchangeable exchanger  612  may facilitate a cross-flow air pattern within air handling module  600 . Fan box  681  may be coupled to port  601  and may be configured to pull air flow into and out of housing  620 . Fan box  688  may be coupled to port  608  and may be configured to push air flow into and out of housing  620 . One or both of third pair of ports  605 - 606  may receive outside air (OA). Air may flow through housing  620  and may be discharged from air handing module  600  through one or both of first pair of ports  601 - 602  as supply air (SA). Return air (RA) may enter housing  620  through one or both of fourth pair of ports  607 - 608  and may be conveyed through housing  620  and exit though one or both of second pair of ports  603 - 604  as exhaust air (EA). 
     Outside air (OA) may enter housing  620  through port  606 , while paired port  605  may be sealed by access panel  675 . Air director  622  and exchanger divider  640  may direct outside air (OA) through filter  691   a , exchanger  612 , and supply air coil  692   a . One or more fans  689  of fan box  681  may pull outside air (OA) through exchanger  612  and out of port  601  as supply air (SA), while paired port  602  may be sealed by access panel  672 . Return air (RA) may enter housing  620  through port  608 , while paired port  607  may be sealed by access panel  677 . Air director  622  and exchange divider  640  may direct return air (RA) thru filter  691   b , exchanger  612 , and exhaust air coil  692   b . One or more fans  689  of fan box  688  push return air (RA) into port  608 , while paired port  607  may be sealed by access panel  677 . Return air (RA) may be pushed through exchanger  612  by fan box  688  and may exit out of port  604  as exhaust air (EA), while paired port  603  may be sealed by access panel  673 . 
       FIG. 7 a    illustrates a perspective view of a plurality of air handling modules coupled together to form an air handling system according to the present disclosure. As shown in  FIG. 7 a   , an air handling system  700  may comprise a plurality of air handling modules  710  stacked together. Air handling modules  710  may operate in parallel with each other to achieve a combined conditioning effect greater than, or equal to, a conditioning effect of a single air handling unit with a desired level of redundancy. Air handling module  710  may comprise lightweight plastic construction which may facilitate hand transport by one or more installation personnel  799  without employing cranes and other heavy machinery. Air handling module  710  may preferably weigh under 100 pounds. 
     A bottom  740  of air handling module  710  may be stacked on a top  730  of adjoining air handling module  710 . As discussed above, ports of air handling module  710  may serve as interchangeable attachment points for a variety of structures, such as, for example, fan boxes, metal ducts, weather hoods, roof curbs, access panels, and/or other fluidly connected components of an HVAC system. Components may readily attach and detach from the ports to accommodate multiple combinations for air handling module  710  customizable per installation site requirements. 
     One or more ports  706  of air handling module  710  may serve as interchangeable attachment points for fan boxes  786  containing one or more fans  789 , and one or more ports  701  of air handling module  710  may serve as interchangeable attachment points for fan boxes  781  containing one or more fans  789 . Fan boxes  781  and fan boxes  786  may direct air flow into and out of air handling module  710  through attached ports  701  and ports  706 , respectively. Fan boxes  781  and  786  may readily attach and detach from ports  701  and ports  706  using standard screw drivers or wrenches. Fan boxes  781  and  786  may also include integrated power and communication bus wire harnesses to connect into any of the ports to provide a “plug-and-play” arrangement. 
     Each paired port  707 - 708  may include an access panel  778  that may readily attach and detach using standard screw drivers or wrenches. This port duality may facilitate numerous air flow directions and may be customized at the site location. In some embodiments, a plurality of ports may be aligned to facilitate the attachment of a single, four-sided rectangular duct. As shown in  FIG. 7 a   , extension flanges outlining ports (e.g., ports  707 ) may be flush along top  730  and bottom sides  740 . 
       FIG. 7 b    illustrates a perspective view of a plurality of air handling modules coupled together to form an air handling system according to the present disclosure. As shown in  FIG. 7 a   , air handling system  700  may comprise a plurality of air handling modules  710 , vertically positioned and adjacently stacked. Air handling modules  710  may operate in parallel with each other to achieve a combined conditioning effect greater than, or equal to, a conditioning effect of a single air handling unit with a desired level of redundancy. Air handling modules  710  of air handling system  700  may be in a vertical orientation to facilitate fluid flow in evaporative cooling and/or steam regeneration liquid desiccant conditioning applications and carbon dioxide scrubbing systems. 
     Fans  789  in fan housing  786  may pull recirculating return air (RA) to be conditioned through a single common duct  757  coupled to ports  707  of air handling modules  710 . Return air (RA) may pass through the exchangers in air handling modules  710  and may exit air handling modules  710  as supply air (SA) through a single common duct  756  coupled to ports  706  of air handling modules  710 . Fans  789  in fan housing  781  may pull outside air (OA) into air handling modules  710  through one or more weather hoods  764  coupled to ports  704  of air handling modules  710 . Outside air (OA) may pass through the exchangers in air handling modules  710  and may exit air handling modules  710  as exhaust air (EA) through one or more weather hoods  761  coupled to ports  701  of air handling modules  710 . 
       FIG. 8 a    illustrates a cross-sectional perspective view as indicated by the dashed line shown in  FIG. 7 b    of an air handling system  800  according to the present disclosure. As shown in  FIG. 8 a   , air handling system  800  may comprise a plurality of air handling modules  812   a - 812   c  stacked in a vertical configuration. Each of air handling modules  812   a - 812   c  may contain a plurality of internal and external ports facilitating a multi-functional hydronic distribution and collection system. 
     Port(s)  839  may be connected to an evaporative water pipe  853  with sealed threads and may facilitate entry, distribution, and discharge of supply water through a plurality of housings  820   a - 820   c  via evaporative water pipe  853 . An exchanger  213  may be contained within each housing  820   a - 820   c  and may include a plurality of plates arranged in a successively stacked configuration with portions thereof having a spaced apart arrangement. A first and second series of discrete alternating passages may be defined at the spaced apart portions. 
     Evaporative water  825  may be delivered into exchanger  213 . The evaporative water  825  may gravitationally flow down the first series of discrete alternating passages until reaching a first drain conduit  832  for collecting the flowing evaporative water  825  from the first series of passages. The first drain conduit  832  may be entirely outside of the exchanger  213  and adjacent to first and second ends of the plurality of plates. The first drain conduit port  832  may be connected to an evaporative water drain pipe  859  with sealed threads and may facilitate entry, distribution, and discharge of water through the plurality of housings  820   a - 820   c.    
     Port(s)  837  may be connected to a liquid desiccant pipe  851  with sealed threads and may facilitate entry, distribution, and exit of liquid desiccant  826  through a plurality of housings  820   a - 820   c  via liquid desiccant pipe  851 . Liquid desiccant  826  may be delivered into exchanger  213 . The liquid desiccant  826  may gravitationally flow down the second series of discrete alternating passages until reaching a second drain conduit  838  for collecting the flowing liquid desiccant  826  from the second series of passages. The second drain conduit  838  may be entirely outside of the exchanger  213  and adjacent to first and second ends of plurality of plates. Second drain conduit  838  may be connected to a liquid desiccant drain pipe  855  with sealed threads and may facilitate entry, distribution, and exit of liquid desiccant through the plurality of housings  820   a - 820   c.    
     In some embodiments, side liquid desiccant drain port(s)  818   a - 818   c  and  819   a - 819   c  may be connected to drain pipe(s)  819   a - 819   c  with sealed threads and may provide an additional or alternate exit for liquid desiccant through drain pipe(s)  819   a - 819   c . In some embodiments, aqueous solutions of alkylamines, other reversibly binding aqueous solutions, lithium chloride, or combinations thereof may flow through the exchangers  213 . 
     In some embodiments, the ports of air handling modules  812   a - 812   c  facilitating the multi-functional hydronic distribution and collection system may be threaded. It should be appreciated that the ports may serve as interchangeable attachment points for a plurality of components including a condensate drain pipe, an evaporative water supply pipe, an evaporative water drain pipe, a liquid desiccant supply pipe, a liquid desiccant drain pipe, a refrigerant line conduit, a chilled water conduit, a steam pipe, reversibly binding aqueous scrubbing pipe, and/or other fluidly connected hydronic components of an HVAC system. The components may readily attach and detach from the ports and may allow customized configuration at the installation site. Gasketed seals may be incorporated between the components and the ports. In some embodiments, the ports may be threaded in accordance with British Standard Parallel Pipe (BSPP) standards with integrated sealing washers to ensure international compatibility with National Taper Pipe (NPT), American Standard Straight Pipe for Mechanical Joints (NPSM), American Standard Straight Pipe (NPS), and British Standard Tapered Pipe (BSTP) standards. In some embodiments, bottom conduit port(s)  844   a - 844   c  may be attached to supply coil pipe  858  and return coil pipe  869  to distribute liquids between a plurality of housings  820   a - 820   c . Supply coil port  861   a - 861   c  and return coil port  863   a - 863   c  may form access points between conduit port(s)  844   a - 844   c.    
       FIG. 8 b    illustrates a cross-sectional perspective view of an air handling system along the dashed line “ 8 B” of  FIG. 7 a   . As shown in  FIG. 8 b   , air handling system  800  may comprise a plurality of adjacently stacked air handling modules  812   a - 812   c . Air handling modules  812   a - 812   c  may contain a plurality of internal and external ports, which may facilitate: (a) multi-functional structural connectivity; (b) “plug-and-play” electrical power distribution; and (c) “plug-and-play” communication bus. The communications bus and power distribution of the air handling system may provide a single point of control connection to synchronously operate the plurality of air handling modules. 
     Air handling modules  812   a - 812   c  may be structurally connected via anchor bolts  865  mating with anchor port(s)  846 . Anchor port(s)  846  may also provide a multi-functional structural connection to the ground or support base  867 . In some embodiments, anchor port(s)  846  that may not be utilized may be sealed and secured with insulated threaded plug(s)  864 . In some embodiments, anchor port(s)  846  may be threaded. Anchor port(s)  846  may serve as interchangeable attachment points for a plurality of attachment structures, such as, for example, structural anchor bolts, module interconnectivity clamps, module seals, and insulated plug seals. These attachment structures may readily attach and detach from anchor port(s)  846 , which may allow for customized configuration at the installation site. 
     Power wire  827  may be connected to a power conduit fitting  833  at threaded port(s)  834 , which may facilitate a “plug-and-play” electrical power distribution. A power harnesses  843  may transfer power between top conduit ports  834  and bottom conduit ports  844 . Electrical and economizer bypass enclosures  857   a - 857   c  may contain a plurality of devices and accommodate multiple combinations of orientations and various numbers of modules per installation site requirements. 
     Electrical enclosure  857   a  may provide a single point electrical disconnect  852  for air handling system  800 . Electrical enclosure  857   b  may provide a single point electrical distribution  848  for powering a central controller  849 . Electrical enclosure  857   c  may be empty. In some embodiments, anchor port(s)  844   c  that may not be utilized in the electrical power distribution may be sealed and secured with insulated threaded plug(s)  864 . Power distribution includes electrical power conduit, electrical disconnect handle, module grounding point, and electrical wire harness connectors. 
     Signal wire  835  may be connected to a signal conduit fitting  841  at threaded port(s)  834 , which may facilitate a “plug-and-play” communications bus. A signal harness  831  may transfer signals between top conduit ports  834  and bottom conduit ports  844 . Electrical enclosure  857   b  may contain a central controller  849  to which all other air handling modules  812  of air handling module system  800  may be slaves. In some embodiments, a plurality of components, including, for example, fan boxes, may be linked to the “plug-and-play” communications bus and electrical power distribution via an AHU power and signal harness  881  and a fan power and signal harness  880 . Interchangeable attachment points may be compatible for a plurality of components, including, for example, a communication bus wire conduit, sensor probes, and communication bus harness connectors. 
     Gasketed seals may be incorporated between the anchor and threaded ports and their mated components. In some embodiments, the anchor and threaded ports may be threaded in accordance with British Standard Parallel Pipe (BSPP) standards with integrated sealing washers to ensure international compatibility with National Taper Pipe (NPT), American Standard Straight Pipe for Mechanical Joints (NPSM), American Standard Straight Pipe (NPS), and British Standard Tapered Pipe (BSTP) standards. 
       FIG. 9 a    illustrates a perspective view of air handling system  900  according to the present disclosure. As shown in  FIG. 9 a   , energy recovery module  912   a  may be fluidly coupled in series to a wrap-around dehumidification module  914   a  to form dual plate air handling module  900   a . Ports  904   a  and  905   a  of energy recovery module  912   a  may be respectively joined to ports  901   a  and  908   a  of  904   b  of dehumidification module  914   a . A dual plate air handling module  900   b  may comprise energy recovery module  912   b  fluidly coupled in series to wrap-around dehumidification module  914   b , and dual plate air handling module  900   c  may comprise energy recovery module  912   c  fluidly coupled in series to a wrap-around dehumidification module  914   c . The plurality of dual plate air handling modules  900   a - 900   c  may be stacked in a vertical configuration to form a dual plate air handling system  900 . Air handling modules  900   a - 900   c  may be configured to operate in parallel with each other to achieve a combined conditioning effect greater than, or equal to, a conditioning effect of a single air handling unit with a desired level of redundancy. 
     Fan(s)  989  in fan housing  986  may pull outside air (OA) through weather hood  964 , and outside air (OA) may enter energy recovery module  912   a  at port  904   a . Outside air (OA) may exit as supply air (SA) through port  906 . A single common supply air (SA) duct  956  may be connected to a plurality of ports  906 . A single common rectangular return duct  957  may be connected to a plurality of ports  907 , and fan(s)  989  in fan housing  985  may pull return air (RA) through the single common return duct  957 . Return air (RA) may exit as exhaust air (EA) through weather hood  965  at port  905 . 
     Air handling module  914  may comprise lightweight plastic construction which may facilitate hand transport by one or more installation personnel  999  without employing cranes and other heavy machinery. Air handling module  914  may preferably weigh under 100 pounds. 
       FIGS. 9 b -9 g    illustrate the modularity of the air handling system of the present disclosure by illustrating exemplary configurations of the air handling system.  FIG. 9 b    illustrates a cross-sectional view of dual plate air handling system  900  according to the present disclosure. As shown in  FIG. 9 b   , air handling system  900  may comprise a sensible heat exchanger  916  in series with an enthalpy exchanger  915  to facilitate lower temperature, frost-free operation of air handling module  900 . Air handling system  900  may include fan box  981  coupled to port  901  and fan box  988  coupled to port  908 . Fan box  981  and fan box  988  may be configured to pull and push air flow into and out of a housing  920  of air handling system  900 . 
     Air handling system  900  may include a series of air-to-air exchangers  916  and  915  contained within housing  920 . Air handling system  900  may also include a first pair of ports  901 - 902  fluidly connected to second pair of ports  903 - 904 . One or both of second pair of ports  903 - 904  may receive outside air (OA). Air may flow through housing  920  and may be discharged from air handling system  900  through one or both of first pair of ports  901 - 902  as supply air (SA). Air handling system  900  may further include third pair of ports  905 - 906  fluidly connected to fourth pair of ports  907 - 908 . One or both of fourth pair of ports  607 - 608  may receive return air (RA). Exhaust air (EA) may be discharged from air handling system  900  through one or both of third pair of ports  905 - 906 . 
     Outside air (OA) may enter housing  920 , which may comprise sides  910 , through port  904 , while paired port  903  may be sealed by access panel  973 . Air director  922  and exchanger divider  940  may direct outside air (OA) through filter  991   a , heat exchanger  916 , enthalpy exchanger  915 , and supply air coil  992   a . One or more fans  989  may be positioned inside fan box  981  and may pull supply air (SA) through exchangers  916 ,  915  and out of port  901 , while paired port  902  may be sealed by access panel  672 . Rotary damper  941  may seal bypass openings  923   a , and access panel  679  may seal port  909 . One or more fans  989  may be positioned inside fan box  988  and may push return air (RA) entering at port  908  through exchangers  916 ,  915  and out port  606 , while paired port  907  may be sealed by access panel  977 . Air director  922  and exchanger divider  940  may direct return air (RA) through filter  991   b , enthalpy exchanger  915 , heat exchanger  916 , and exhaust air coil  992   b . Supply air coil  992   a  and exhaust air coil  992   b  may be any suitable thermal transfer device for promoting a variety of air processing and conditioning objectives, including, but not limited to, a condenser coil, an evaporator coil, a chilled water coil, a hot water coil, and/or a steam coil. Exhaust air (EA) may exit port  905 , while paired port  906  may be sealed by access panel  976 . 
       FIG. 9 c    illustrates a cross-sectional view of another dual plate air handling system  900  according to the present disclosure. As shown in  FIG. 9 c   , air handling system  900  may comprise of energy recovery module  912   a  serially coupled to wrap-around dehumidification module  914   b . Ports  901   a  and  908   a  of energy recovery module  912   a  may be fluidly connected to ports  904   b  and  905   b  of dehumidification module  914   b , respectively. The dual plate air handling system of  FIG. 9 c    may provide energy savings and load reduction of enthalpy recovery for dedicated outdoor air. Furthermore, the sensible/latent ratio control of wrap-around dehumidification may deliver low dewpoint to an application at neutral temperature; which may eliminate space reheat. 
     The dual plate air handling system of  FIG. 9 c    may include exchanger  915  housed in housing  920   a  of energy recovery module  912   a  fluidly connected in series to exchanger  916  housed in housing  920   b  of dehumidification module  914   b . Paired ports  903   a - 904   a  of energy recovery module  912   a  may be fluidly connected to paired ports  905   b - 906   b  of dehumidification module  914   b . One or both of paired ports  903   a - 904   a  may receive outside air (OA). Air may flow through energy recovery module  912   a  and dehumidification module  914   b  (and exchangers  915 ,  916 ) and may be discharged from one or both of paired ports  905   b - 906   b  as supply air (SA). Paired ports  907   a - 908   a  of energy recovery module  912   a  may be fluidly connected to paired ports  905   a - 906   a  of energy recovery module  912   a . One or both of paired ports  907   a - 908   a  may receive return air (RA). Exhaust air (EA) may be discharged from one or both of paired ports  905   a - 906   a.    
     Outside air (OA) may enter housing  920   a  of energy recovery module  912   a , which may comprise sides  910   a , through port  904   a , while paired port  903   a  may be sealed by an access panel  973 . Air director  922   a  and exchanger divider  940   a  may direct outside air (OA) through energy recovery exchanger  915 . Outside air (OA) may exit housing  920   a  through port  901   a  and may enter housing  920   b  of dehumidification module  914   b , which may comprise sides  910   b , through port  904   b . An air director  922   b , an exchanger divider  940   b , and sealed ports  908   b ,  901   b  may direct a first pass of outside air (OA) through sensible exchanger  916  and coil  922   a . One or more fans  989  of fan box  986  may pull outside air (OA) through coil  922   b , which may be arranged in series with coil  922   a , and back through sensible exchanger  916  for a second pass. The air may then exit as supply air (SA) through port  906   b . A fan box  985  may be fluidly coupled to port  905   a . One or more fans  989  positioned inside fan box  985  may pull return air (RA) through port  907   a , while paired port  908   a  may be sealed. Air director  922   a  and exchange divider  940   a  may direct return air (RA) through exchanger  915  and exhaust air coil  992   c.    
     In some embodiments, exhaust air coil  992   c  may be a condenser type coil configured to reject heat from evaporator coils  992   a  and  992   b . A rotary damper  934   a  may seal bypass openings  923   a  and a rotary damper  934   b  may seal bypass openings  923   b . The air pulled by fan box  985  may exit port  905   a  as exhaust air (EA), while paired port  906   a  may be sealed. 
       FIG. 9 d    illustrates a cross-sectional view of another configuration of the dual plate air handling system of  FIG. 9 c    according to the present disclosure. As shown in  FIG. 9 d   , dual-plate air handling module  900  may be arranged to provide energy savings and load reduction through enthalpy exchanger  915 . It may also provide bypass  923   b  around wrap-around heat exchanger  916  to change the sensible/latent ratio depending upon changing site requirements. Rotary damper  934   b  may be opened to permit airflow through bypass opening(s)  923   b , while blocking airflow through the path directed by air director  922   b  and exchange divider  940   b  for the first pass of the outside air (OA) through exchanger  916  as shown in  FIG. 9 c   . As such, rotary damper  934   b  may facilitate outside air (OA) bypassing sensible exchanger  916 . Sealed ports  908   b - 901   b  may direct outside air (OA) to pass through coils  992   b  and then sensible exchanger  916 . One or more fans  989  of fan box  986  may pull this outside air (OA) through sensible exchanger  916  for a single pass. The air may then exit as supply air (SA) through port  906   b . In some embodiments, coils  992   a  may be closed or turned off to prevent freezing due to the lack of airflow. 
       FIG. 9 e    illustrates a cross-sectional view of another dual plate air handling system according to the present disclosure. As shown in  FIG. 9 e   , dual plate air handling system  900  may comprise energy recovery module  912   a  serially coupled to wrap-around dehumidification module  914   b  and arranged to facilitate recirculated return air (RA) optionally entering through a port  938 . This arrangement may provide the energy savings and load reduction of enthalpy recovery, sensible/latent ratio control, low dewpoint air delivered at room neutral temperature, and recirculating air conditioning during unoccupied periods. The dual plate air handling system of  FIG. 9 e    may include port  938  and return air (RA) port rotary damper  936 . Rotary damper  936  may be actuated to open and seal port  938 . When rotary damper  936  is opened, port  938  may be fluidly connected to paired ports  905   b - 906   b  of dehumidification module  914   b.    
       FIG. 9 f    illustrates a cross-sectional view of another configuration of the dual plate air handling system of  FIG. 9 e    according to the present disclosure. As shown in  FIG. 9 f   , rotary damper  936  may be actuated to facilitate a variable percentage of recirculated return air (RA) entering through port  938  and mixing with outside air (OA). This arrangement may provide the energy savings and load reduction of enthalpy recovery for dedicated outdoor air. Furthermore, the sensible/latent ratio control of wrap-around dehumidification may deliver low dewpoint to an application at neutral temperature; which may eliminate space reheat. Incorporating a variable percentage of recirculating air conditioning may reduce energy during unoccupied periods and/or increase space comfort levels. Rotary damper  936  may be at least partially opened to permit return air (RA) to enter through port  938 . When rotary damper  936  is at least partially opened, port  938  may be fluidly connected to ports  901   a  and  904   b  and return air (RA) entering through port  938  may mix with outside air (OA). The mixture of outside air (OA) and return air (RA) then may be supplied to dehumidification arrangement  914   b  through port  904   b . The amount of return air (RA) mixing with outside air (OA) may be modulated by rotary damper  936 . 
     Air director  922   b , exchanger divider  940   b , and sealed ports  908   b - 901   b  may direct the mixture of outside air (OA) and return air (RA) through sensible exchanger  916  and coil  992   a  for a first pass. One or more fans  989  of fan box  986  may pull this mixed air through coil  922   b  and back through sensible exchanger  916  for a second pass. The air may then exit as supply air (SA) through port  906   b . Rotary dampers  934   a  and  931   a  may seal bypass openings  923   a , and rotary dampers  934   b  and  931   b  may seal bypass openings  923   b.    
       FIG. 9 g    illustrates a cross-sectional view of another configuration of the dual plate air handling system of  FIG. 9 e    according to the present disclosure. As shown in  FIG. 9 e   , rotary damper  936  may be actuated to facilitate recirculated return air (RA) entering through port  938 . This arrangement may provide sensible/latent ratio control of wrap-around dehumidification and may deliver low dewpoint to an application at neutral temperature, which may eliminate space reheat. Incorporating a variable percentage of recirculating air conditioning may reduce energy during unoccupied periods and/or increase space comfort levels. For example, many winter vacation homes sit empty during the humid summer months and controlling dew point may be more important than controlling temperature for reduction of mold and elimination of odors. As shown in  FIG. 9 g   , rotary damper  936  may be opened to permit return air (RA) to enter through port  938  and into housing  920   b . Rotary damper  934   b  may be opened to permit airflow through bypass opening(s)  923   b  and facilitate return air (RA) bypassing sensible exchanger  916 . Air director  922   b , exchanger divider  940   b , and sealed ports  908   b - 901   b  may direct return air (RA) through coils  992   b  and sensible exchanger  916 . One or more fans  989  of fan box  986  may pull this return air (RA) through sensible exchanger  916 . The air may then exit as supply air (SA) through port  906   b . One or more fans  989  of fan box  985  may pull outside air (OA) through port  907  and through exchanger  915  and exhaust air coil  992   b . Air director  922   a  and exchange divider  940   a  may direct the outside air (OA) through exchanger  915  and exhaust air coil  992   b . The air pulled by fan box  985  may then exit port  905   a  as exhaust air (EA), while paired port  906   a  may be sealed. Rotary damper  934   a  may be closed to seal bypass opening(s)  923   a.    
       FIG. 10 a    illustrates a psychrometric chart corresponding to the operation of air handling system of  FIG. 9 b    according to the present disclosure.  FIGS. 9 b  and 10 a    depict a first airstream of outside air (OA) to supply air (SA) and a second airstream of return air (RA) to exhaust air (EA). As shown in  FIG. 10 a   , the first airstream may traverse points A, B, C, and D, and the second airstream may traverse points E, F, and G.  FIG. 10 a    charts the estimated temperatures and humidity levels for the first and second airstreams as they traverse these points. 
     The first airstream and the second airstream may pass through heat exchanger  916  and enthalpy exchanger  915  in a counterflow orientation. Point E may represent a typical winter return air condition from a conditioned space. The second airstream may enter an entry port of enthalpy exchanger  915  at point E on  FIG. 10 a    and may flow through enthalpy exchanger  915  to point F. The first airstream may flow simultaneously through enthalpy exchanger  915  from point B to point C in a counterflow orientation in relation to the second airstream flowing through enthalpy exchanger  915  from point E to point F. As the second airstream flows through enthalpy exchanger  915  from point E to point F and the first airstream flows through enthalpy exchanger  915  from point B to C, moisture and heat content may transfer from the second airstream to the first airstream. 
     The second airstream may also enter an entry port of heat exchanger  916  at point F on  FIG. 10 a    and flow through heat exchanger  916  to point G. The first airstream may flow simultaneously through heat exchanger  916  from point A to point B in a counterflow orientation in relation to the second airstream. As the second airstream flows through heat exchanger  916  from point F to point G and the first airstream flows through heat exchanger  916  from point A to point B, heat content may transfer from the second airstream to the first airstream. The first airstream may exit enthalpy exchanger  915  at point C and may enter exhaust air coil  922   a . The first airstream may receive heat from the exhaust air coil  992   c  and be heated to a point D. 
       FIG. 10 b    illustrates a psychrometric chart corresponding to the operation of air handling system of  FIG. 9 c    according to the present disclosure.  FIGS. 9 c  and 10 b    depict a first airstream of outside air (OA) to supply air (SA) and a second airstream of return air (RA) to exhaust air (EA). As shown in  FIG. 10 b   , the first airstream may traverse points A, B, C, D, E, and F, and the second airstream may traverse points G, H, and I.  FIG. 10 b    charts the estimated temperatures and humidity levels for the first and second airstreams as they traverse these points. 
     The first airstream and the second airstream may pass through enthalpy exchanger  915  in a counterflow orientation. Point G may represent a typical summer return air condition from a conditioned space. The second airstream may enter an entry port of enthalpy exchanger  915  at point G on  FIG. 10 b    and may flow through enthalpy exchanger  915  to point H. The first airstream may flow simultaneously through enthalpy exchanger  915  from point A to point B in a counterflow orientation in relation to the second airstream flowing through enthalpy exchanger  915  from point G to point H. As the second airstream flows through enthalpy exchanger  915  from point G to point H and the first airstream flows through enthalpy exchanger  915  from point A to point B, moisture and heat content may transfer from the first airstream to the second airstream. The second airstream may exit enthalpy exchanger  915  at point H and may flow through exhaust air coil  992   c . The second airstream may receive heat from exhaust air coil  992   c  and may be heated to point I. 
     The first airstream may also enter an entry port of heat exchanger  916  and may flow through heat exchanger  916  being sensibly cooled to point C. The first airstream may exit enthalpy exchanger  915  at point C and may flow through evaporator coil  992   a . The first airstream may be cooled and dehumidified by evaporator coil  992  to point D. The first airstream may then be directed through another evaporator coil  992   b . The first airstream may be cooled and dehumidified by evaporator coil  99   b  to point E. The first airstream may again be directed through heat exchanger  916  and may be sensibly heated to point F. 
       FIG. 10 c    illustrates a psychrometric chart corresponding to the operation of the air handling system of  FIG. 9 d    according to the present disclosure.  FIGS. 9 d  and 10 c    depict a first airstream of outside air (OA) to supply air (SA) and a second airstream of return air (RA) to exhaust air (EA). As shown in  FIG. 10 c   , the first airstream may traverse points A, B, and E, and the second airstream may traverse points G, H, and I.  FIG. 10 c    charts the estimated temperatures and humidity levels for the first and second airstreams as they traverse these points. 
     The first airstream and the second airstream may pass through enthalpy exchanger  915  in a counterflow orientation. Point A may represent a typical summer outside air condition. The first airstream may enter an entry port of enthalpy exchanger  915  at point A of  FIG. 10 c    and may flow through enthalpy exchanger  915  to point B. The second airstream may enter an entry port of enthalpy exchanger  915  at point G of  FIG. 10 c    and may flow simultaneously from point G to point H in a counterflow orientation in relation to the first airstream. As the first airstream flows through enthalpy exchanger  915  from point A to point B and the second airstream flows through enthalpy exchanger  915  from point G to point H, moisture and heat content may transfer from the first airstream to the second airstream. The first airstream may then flow through evaporator coil  992   b  and may be cooled and dehumidified to point E. The second airstream may exit enthalpy exchanger  915  at point H and may flow through exhaust air coil  992   c . The second airstream may receive heat from exhaust air coil  992   c  and may be heated to point I. 
       FIG. 10 d    illustrates a psychrometric chart corresponding to the operation of the air handling system of  FIG. 9 f    according to the present disclosure.  FIGS. 9 f  and 10 d    depict a first airstream of outside air (OA) to supply air (SA), a second airstream of return air (RA) to exhaust air (EA), and a third airstream of supply air (SA). As shown in  FIG. 10 d   , the first airstream may traverse points A and B, the second airstream may traverse points H, I, and J, and the third airstream may traverse points C, D, E, F, and G.  FIG. 10 d    charts the estimated temperatures and humidity levels for the first, second, and third airstreams as they traverse these points. 
     The first airstream and the second airstream may pass through enthalpy exchanger  915  in a counterflow orientation. Point A may represent a typical summer outside air condition. The first airstream may enter entry port of enthalpy exchanger  915  at point A of  FIG. 10 d    and may flow through enthalpy exchanger  915  to point B. The second airstream may enter entry port of enthalpy exchanger  915  at point H of  FIG. 10 d    and may flow simultaneously from point H to point I in a counterflow orientation in relation to the first airstream. As the first airstream flows through enthalpy exchanger  915  from point A to point B and the second airstream flows through enthalpy exchanger  915  from point H to point I, moisture and heat content may transfer from the first airstream to the second airstream. The second airstream may exit enthalpy exchanger  915  at point I and may flow through exhaust air coil  992   c . The second airstream may receive heat from the exhaust air coil  992   c  and may be heated to a point J. 
     The outside air (OA) of the first airstream and a partial volume flow of the return air (RA) of the second airstream may mix to form the third airstream in the form of supply air (SA) at point C. The third airstream may enter entry port of heat exchanger  916  at point C of  FIG. 10 d    and may flow through heat exchanger  916  and may be sensibly cooled to point D. The third airstream may then flow through evaporator coil  992   a  and may be cooled and dehumidified to point E. The third airstream may then flow through another evaporator coil  992   b  and may be cooled and dehumidified to point F. The third airstream may then encounter may again enter heat exchanger  916  at point F and may flow through heat exchanger  916  and may be sensibly heated to point G. 
       FIG. 10 e    illustrates a psychrometric chart corresponding to the operation of air handling system of  FIG. 9 g    according to the present disclosure.  FIGS. 9 g  and 10 e    depict a first airstream of outside air (OA) to exhaust air (RA) and a second airstream of return air (RA) to supply air (SA). As shown in  FIG. 10 e   , the first airstream may traverse points H though J, and the second airstream may traverse points A through D.  FIG. 10 e    charts the estimated temperatures and humidity levels for the first and second airstreams as they traverse these points. 
     The first airstream and the second airstream may flow through enthalpy exchanger  915  and heat exchanger  916 , respectively, but may not experience a state change as no opposing airstream may flow in a counterflow orientation. Point A may represent a typical summer return-air condition. The second airstream may flow through evaporator coil  992   b , heat exchanger  916 , and evaporator coil  992   c , and may be cooled and dehumidified to point D. The first airstream may enter enthalpy exchanger  915  at point H, flow through enthalpy exchanger  915 , and flow through exhaust air coil  992   c , receiving heat from exhaust air coil  992   c  and may be heated to point J. 
     Persons of ordinary skill in the art would appreciate that the air handling system of the present disclosure may be modular with respect to the power and velocity of the air flows delivered and supplied by the system. For example, and as shown in  FIGS. 7 a -7 b   , multiple air handling modules may be stacked together (horizontally or vertically) to increase the power, velocity, and capacity of the air flows associated with the system. The power, velocity, and noise of the air flows may be increased or decreased by adjusting the fan speed of the fan boxes. In certain embodiments, the air handling system may be coupled to an existing HVAC unit. One or more air handling modules may be coupled to an HVAC unit to increase the capacity of the HVAC unit. In such an embodiment, the air handling system may act as a pre-treatment stage to remove heat and humidity from air that is supplied to an HVAC unit. 
     Membranes for Exchanger and Related Methods of Manufacture 
     Enthalpy exchangers of the present disclosure may embody a variety of configurations depending on, among other factors, the desired application. For example, an enthalpy exchanger may be a planar heat and moisture plate-type exchanger. The enthalpy exchanger may comprise of membrane plates each constructed of a planar, water-permeable membrane. Membrane plates may be stacked and sealed and may be configured to accommodate air streams flowing in counter-flow configurations between alternate plate pairs. This may facilitate heat- and water vapor-transfer via the membrane, while preventing the air streams from mixing, or otherwise contacting one another. In other embodiments, the enthalpy exchanger may include membrane plates arranged to accommodate air streams flowing in crossflow configurations between alternate plate pairs. 
     In some embodiments, the membrane may permit heat and not moisture to be transferred across the material from one air stream to the other. The membrane of the enthalpy exchanger may, in addition or as an alternative to the membrane plates, comprise a single membrane core made by folding a continuous strip of membrane in a concertina, zig-zag or accordion fashion, with a series of parallel alternating folds. 
     The present disclosure also contemplates an enthalpy exchanger which may have a rotating wheel arrangement. The enthalpy exchanger may comprise a membrane constructed to include a number of parallel pores or opening, such as a honeycomb structure, through which air passes. The enthalpy exchanger may be formed by winding or stacking the membrane into a wheel shape to provide air passageways parallel to the axis of the wheel. 
     The membrane or transfer medium of the present disclosure may be used to form heat and moisture transfer bodies, such as enthalpy exchangers, and may comprise a substrate embedded with microporous particles. The substrate may comprise fibrous materials, including, for example, natural cellulose fibers, as well as synthetic thermoplastic fibers, such as polyvinyl alcohol polymer fibers, bicomponent fibers and microfibers. The substrate may comprise any type of fibrous materials that may hold substantial amounts of liquids and microporous particles. The substrate may be formed by conventional paper making processes into adsorbent paper or desiccant paper having adsorbent or desiccant contained therein. In some embodiments, additives, such as reinforcement fibers, may be added to the substrate. 
     Examples of fibrous materials suitable for use as substrate may include: wood pulp; cellulose fiber; synthetic thermoplastic organic fiber; and mixtures thereof. Inorganic fiber, such as glass or metal fibers and rock wool, may also be used in conjunction with fibrillated organic fiber. The substrate may also comprise synthetic organic thermoplastic fiber including: polymeric fiber, such as polyethylene, polypropylene, polystyrene, polyvinyl chloride, polyester, rayon (cellulose acetate), acrylic, acrylonitrile homopolymer, copolymer with halogenated monomer, styrene copolymer, and mixtures of such polymers. Suitable synthetic thermoplastic organic fiber may be in staple form (chopped yarn), fabricated form (staple form that has been refined), or extruded/precipitated form. In certain embodiments, substrate may comprise one or more of: soft wood fiber, such as Rayonier Poroganier; fiberglass; biocomponent fiber, such as T-201 bicomponent; acrylic fiber, such as Vonnel microfiber; and PVA fiber, such as Kuralon. 
     Microporous particles may be embedded into the substrate and may comprise any material capable of efficiently holding liquids through capillary action, surface tension, or other mechanisms. Microporous particles may be activated for adsorption by removing water from their hydrated precursors. Microporous material may be capable of efficiently adsorbing/desorbing said moisture to a counter-flowing air stream. Microporous material may also be capable of efficiently adsorbing/desorbing said moisture to a crossflowing air stream. 
     Substrate embedded with microporous particles may have liquid sorption capacity for liquids, such as, for example, lithium chloride, water, lithium bromide, tri-ethylene glycol, calcium chloride, potassium formate, zinc-carbon, zinc-chloride, alkaline, nickel oxyhydroxide, lithium-copper oxide, lithium-iron disulfide, lithium-manganese dioxide, lithium-chromium oxide, lithium-silicone, mercury oxide, zinc-air, silver-oxide, magnesium, NiCd, lead-acid, NiMH, NiZn, AgZn, LiFePO4, lithium ion, and mixtures thereof. In some embodiments, the liquid may be a lithium chloride with an amount of lithium chloride in the solution being 8.3% wt. or less. 
     Microporous particles may include activated aluminas, silica gels, molecular sieves, porous titania, or zeolites, activated carbon, and the like, and mixtures of these compounds. In certain embodiments, microporous particles may include transition alumina, such as gamma alumina, due to their inert properties, lower cost, and wide market availability. An example of commercially available gamma alumina is VGL 15 produced by U.O.P. Corporation. 
     An exemplary system and process for manufacturing substrate for use as a membrane or transfer medium according to the present disclosure will now be described with reference to  FIGS. 11 a  and 11 b   . As shown in  FIGS. 11 a  and 11 b   , a roll of substrate  1201  may be continuously fed to coating chamber  1200 . As substrate  1201  is fed through coating chamber  1200 , substrate  1201  may be embedded with microporous particles and may exit coating chamber  1200  as membrane or transfer medium  1206 . Membrane  1206  may be continuously collected and rolled up into a roll of membrane  1260 . 
     Substrate  1201  may be a thermoplastic sheet formed of thermoplastic fibers, such as polypropylene. In some embodiments, additives, such as reinforcement fibers, may be added to the thermoplastic sheet. Alternatively, substrate  1201  may comprise paper formed of natural fibers, such as wood pulp or cellulose. 
     Microporous particles embedded into substrate  1201  may include transition alumina, such as gamma alumina. In some embodiments, membrane  1206  may comprise a thermoplastic sheet containing gamma alumina, and in other embodiments, membrane  1206  may comprise paper containing gamma alumina. The present disclosure contemplates that membrane  1206  may be manufactured by coating or embedding any suitable substrate with any suitable microporous particles, as described above. 
     Coating chamber  1200  may include housing  1210  enclosing first calender roller  1212  and second calender roller  1214 . First coating apparatus  1216  may be positioned proximate first calender roller  1212 , and second coating apparatus  1218  may be positioned proximate second calender roller  1214 . Each of first coating apparatus  1216  and second coating apparatus  1218  may be configured to spray microporous particles (e.g., gamma alumina) in powdered form onto its respective calender roller  1212 ,  1214 . First and second coating apparatuses  1216 ,  1218  may be connected to source  1220  of powdered microporous particles via suitable supply lines  1222 . Powdered microporous particles may be delivered from source  1220 , through supply lines  1222 , and sprayed from first and second coating apparatuses  1216 ,  1218  by any appropriate means, including, for example, compressed air. 
     First and second coating apparatuses  1216 ,  1218  may impart a positive charge onto microporous particles  1222  as they are sprayed out of first and second coating apparatuses  1216 ,  1218  and onto first and second calender rollers  1212 ,  1214 . Each of first and second calender rollers  1212 ,  1214  may be electrically grounded. As such, powdered microporous particles may be electrostatically coated onto first and second calender rollers  1212 ,  1214 . 
     Persons of ordinary skill in the art would appreciate that first and second coating apparatuses  1216 ,  1218  may be configured to control the rate at which charged microporous particles are sprayed and may be configured to control the electrical charge rate of powdered microporous particles as they exit the apparatuses  1216 ,  1218 . First and second coating apparatuses  1216 ,  1218  may include any suitable device for use in electrostatic coating. For example, in some embodiments, first and second coating apparatuses  1216 ,  1218  may include powder coating spray guns. A high degree of uniformity may be achieved as a monolayer of microporous particles  1222  may adhere to rollers  1212 ,  1214 . This uniformity may be achieved because the high electrical potential between microporous particles  1222  and rollers  1212 ,  1214  may diminish exponentially after a first monolayer is deposited. An electrostatic cloud of sprayed microporous particles  1222  may create nearly complete coverage of these monolayer microporous particles  1222  on the top and bottom rollers  1212 ,  1214 . In some embodiments, the microporous particles  1222  loading to the thermoplastic substrate sheet  1201  may be as high as 90% by weight. It should be appreciated that in other embodiments, the loading of the microporous particles  1222  to the substrate  1201  may be 50% to 90% by weight, and in certain embodiments, the loading of the microporous particles  1222  to the substrate  1201  may be 50% to 60% by weight. 
     Each of first and second calender rollers  1212 ,  1214  may be configured to embed powdered microporous particles into substrate  1201 . Substrate  1201  may be fed between rollers  1212 ,  1214 , and rollers  1212 ,  1214  may rotate in a direction toward the feed direction of substrate  1226 . Rollers  1212 ,  1214  may comprise hard, anti-stick material and may be configured to be heated to a suitable temperature. In some embodiments, rollers  1212 ,  1214  may be formed of hardened steel. Persons of ordinary skill in the art would appreciate that rollers  1212 ,  1214  may be diamond coated. As rollers  1212 ,  1214  rotate, rollers  1212 ,  1214  may press onto the top and bottom surfaces of the substrate  1230  and embed the surfaces of substrate  1201  with powdered microporous particles from rollers  1212 ,  1214 . 
     The heat and pressure between rollers  1230  may transfer the powdered microporous particles from rollers  1212 ,  1214  onto substrate  1201  by impregnating the substrate  1201  with microporous particles. In some embodiments, rollers  1212 ,  1214  may be heated to at or near the melting point of the thermoplastic fibers forming a thermoplastic substrate to embed microporous particles with thermoplastic fibers and improve the bond and concentration of the microporous particles on the substrate. For example, when coating a polypropylene substrate with microporous particles, rollers  1212 ,  1214  may be heated up to, but not exceeding, the melting point of polypropylene (160° C.). Line speeds greater than 10 meters per minute may be achieved. In some embodiments, hydraulic pressure at the nip of an 8-inch-wide membrane may be between 2,000 psi and 5,000 psi, and preferably 4,000 psi. A metering-type calender may be advantageous in controlling the thickness of the membrane. 
     Rollers  1212 ,  1214  may be straight rollers. Persons of ordinary skill in the art would appreciate that in other embodiments, the rollers  1212 ,  1214  may have an arch-shaped configuration to, for example, accommodate flexing of the rollers under pressure particularly in impregnating wider substrates. Rollers  1212 ,  1214  may be arched to accommodate pressure while maintaining a straight contact surface. Rollers  1212 ,  1214  may be meter rollers configured to meter the amount of powdered microporous particles transferred onto sheeting structure  1201 . Rollers  1212 ,  1214  may comprise wells or cups etched onto the coating surface of rollers  1212 ,  1214  that carry a certain amount of powdered microporous particles. The wells or cups of rollers  1212 ,  1214  may meter the certain amount of powdered microporous particles transferred onto sheeting structure  1201  with an even and uniform thickness of microporous particles. In other embodiments, rollers  1212 ,  1214  may have a substantially smooth coating surface. 
     Coating chamber  1200  may also include one or more doctor blades  1232  in contact with the coating surfaces of first and second calender rollers  1212 ,  1214 . Doctor blades  1232  may be configured to remove excess microporous particles  1234  that are coated on first and second calender rollers  1212 ,  1214  by wiping first and second calender rollers  1212 ,  1214  as they rotate relative to doctor blades  1232 . By removing excess microporous particles on first and second calender rollers  1212 ,  1214 , doctor blades  1232  may also even out the distribution of microporous particles coated on rollers  1212 ,  1214  and reduce splotching of microporous particles. 
     Doctor blades  1232  may be formed of any suitable material, including, for example, steel or plastic. It should also be appreciated that doctor blades  1232  may be adjusted depending on the conditions of the coating process. For example, the radial positions of doctor blades  1232  relative to rollers  1212 ,  1214 , the positions of doctor blades  1232  relative to the longitudinal axis of rollers  1212 ,  1214 , the angle at which doctor blades  1232  contact rollers  1212 ,  1214 , and the pressure applied by doctor blades  1230  may be adjusted to address the locations and degree of excess microporous particles to be removed. 
     In some embodiments, shrouds  1236  may be coupled to the edges of each of first and second calender rollers  1212 ,  1214 . Shrouds  1236  may extend along the longitudinal axis of each of rollers,  1212 ,  1214  and cover portions of the coating surfaces of rollers  1212 ,  1214  adjacent to their edges. The shrouds  1236  may block microporous particles from coating portions of the coating surfaces covered by shrouds  1236 . Accordingly, shrouds  1236  may frame the coating surface of rollers  1212 ,  1214  to match a given width of substrate  1201  to be deposited with microporous particles. Shrouds  1236  may therefore reduce the amount of wasted microporous particles that may be coated on the edge of rollers  1212 ,  1214  but do not contact and transfer to substrate  1201 . Shrouds  1236  may be adjustable in length relative to the longitudinal axes of the rollers  1212 ,  1214  to accommodate various widths of substrate  1201 . Persons of ordinary skill in the art would also appreciate that shrouds  1236  may be formed of any suitable material that is electrically insulated and anti-stick to avoid microporous particles coating shrouds  1236 . 
     First and second coating apparatuses  1216 ,  1218  may be arranged relative to first and second calender rollers  1212 ,  1214  to regulate the coating properties of microporous particles onto substrate  1201 . For example, the position of first coating apparatus  1216  may be angled relative to first calender roller  1212  and the position of second coating apparatus  1218  may be angled relative to second calender roller  1214  depending on the desired direction the powdered microporous particles are to be sprayed onto first and second calender rollers  1212 ,  1214 . In some embodiments, first coating apparatus  1216  may be angled upwards such that a spray end of first coating apparatus  1224  may be pointed towards an upper portion of first calender roller  1212 , and second coating apparatus  1218  may be angled downwards such that a spray end of second coating apparatus  1218  may be pointed towards a lower portion of second calender roller  1214 . The angle between first coating apparatus  1216  and the longitudinal axis of the feed direction of substrate  1201  may be approximately 45°, and the angle between second coating apparatus  1218  and the longitudinal axis of the feed direction of substrate  1201  may be approximately negative 45°. 
     First and second coating apparatuses  1216 ,  1218  may be adjusted to any suitable angle relative to first and second calender rollers  1212 ,  1214 , respectively. In other embodiments, for example, first coating apparatus  1216  may be angled downwards such that a spray end of first coating apparatus  1224  may be pointed towards a lower portion of first calender roller  1212 , and second coating apparatus  1218  may be angled upwards such that a spray end of second coating apparatus  1225  may be pointed towards an upper portion of second calender roller  1214 . 
     Angling the position of first and second coating apparatuses  1216 ,  1218  relative to first and second calender rollers  1212 ,  1214  may improve the uniformity of powdered microporous particles spray coated onto first and second calender rollers  1212 ,  1214 , which in turn may provide a more uniform distribution of microporous particles embedded into substrate  1202  and  1204 . In contrast, first and second coating apparatuses  1216 ,  1218  horizontally positioned relative to first and second calender rollers  1212 ,  1214 , respectively (i.e., substantially parallel to the longitudinal axis of the feed direction of the substrate  1201 ), may result in uneven accumulation and coating of the powdered microporous particles on first and second calender rollers  1212 ,  1214 . This, in turn, may result in an uneven distribution and splotching of microporous particles embedded into substrate  1201 . Uneven distribution and splotching of microporous particles that may be caused by horizontally positioning first and second coating apparatuses  1216 ,  1218  may be avoided by adjusting the proximity of first and second coating apparatuses  1212 ,  1214  relative to first and second calender rollers  1212 ,  1214 , the rate at which powdered microporous particles are sprayed, and the electrical charge rate of powdered microporous particles as they exit the apparatuses. 
     X-axis (horizontal) adjustments of first and second coating apparatuses  1212 ,  1214  may be made via a micrometer  1241 ,  1243 . Y-axis adjustments (vertical) of first and second coating apparatuses  1212 ,  1214  may be made via micrometer  1242 ,  1244 . Angular adjustments of first and second coating apparatuses  1212 ,  1214  may be made via micrometer  1245 ,  1246 . 
     In other embodiments, first and second coating apparatuses  1216 ,  1218  may be vertically positioned relative to first and second calender rollers  1212 ,  1214 , respectively (i.e., substantially perpendicular to the longitudinal axis of the feed direction of the substrate  1201 ). This configuration may avoid excess accumulation of powdered microporous particles on substrate  1201 . 
     The proximity of first and second coating apparatuses  1216 ,  1218  relative to first and second calender rollers  1212 ,  1214  may also affect the density and distribution of powdered microporous particles spray coated onto first and second calender rollers  1212 ,  1214 . In some embodiments, first coating apparatus  1216  may be positioned three (3) to twelve (12) inches on an eight (8) inch wide roller from first calender roller  1212 , and second coating apparatus  1218  may be positioned three (3) to twelve (12) inches on an eight (8) inch wide roller from second calender roller  1214 . The widths of the rollers and spray patterns may be adjusted to accommodate different distances between the rollers and the coating apparatuses. Positioning first and second coating apparatuses  1216 ,  1218  closer to first and second calender rollers  1212 ,  1214  may focus a spray profile of powdered microporous particles and concentrate the amount of powdered microporous particles coated on particular surface areas of first and second calender rollers  1212 ,  1214 . Positioning the first and second coating apparatuses  1216 ,  1218  further away from first and second calender rollers  1212 ,  1214  may expand a spray profile of powdered microporous particles and coat more of the surface areas of first and second calender rollers  1212 ,  1214  with powdered microporous particles. The expanded spray profile may also increase the amount of powdered microporous particles that may pass and not be electrostatically picked up by first and second calender rollers  1212 ,  1214 . 
     Coating chamber  1210  may also include reclamation system  1264  configured to return powdered microporous particles that are not impregnated into substrate  1201  from coating chamber  1210  to source  1220 . Reclamation system  1264  enables the process to recycle and reuse unimpregnated coating material. Reclamation system  1264  may include one or more outlet ports  1265  disposed in coating chamber  1200  connected to source  1220  via suitable conduits  1264 . As the powdered microporous particles are sprayed from first and second coating apparatuses  1212 ,  1214 , any powdered microporous particles that may not have been coated on first and second calender rollers  1212 ,  1214  or deposited onto substrate  1201  may be collected from coating chamber  1200  and returned to source  1220 . Microporous particles may exit through outlet ports  1265  and be delivered through conduits  1264  and to source  1220  by any appropriate means, including, for example, a vacuum source. 
     Persons of ordinary skill in the art would appreciate that the process for manufacturing the membrane of the present disclosure may obviate the use of additives, such as retention aids and binders (e.g., polyvinyl alcohol, hydrophilic latex, and starch) to embed and retain microporous particles within the fiber matrix of substrate  1201 . The process of the present disclosure may manufacture the membrane  1206  by embedding the microporous particles into the substrate  1201  without using or by reducing the amount of additives on substrate  1201 , rollers  1212 , or microporous particles. Accordingly, unspent microporous particles in the coating chamber  1222  that have not been deposited onto substrate  1201  may be reclaimed and reused via reclamation system  1264  without the need for any additional conditioning or other processing of reclaimed microporous particles. In some embodiments, for example, approximately 20-30% of the powdered microporous particles sprayed from first and second coating apparatuses  1216 ,  1218  may be electrostatically coated on rollers  1212 ,  1214 . Of this amount of material deposited on the rollers, approximately 30-40% of microporous particles coated on the rollers  1212 ,  1214  may be deposited onto substrate  1201 . The remaining microporous particles  1234  that were deposited on rollers  1212 ,  1214  but not applied to the substrate  1201  may be wiped off rollers  1212 ,  1214  by doctor blades. This material along with the material that was not deposited on rollers  1212 ,  1214  may be continuously recycled and reused in preparing membrane  1206 . 
     As shown in  FIG. 11 b   , membrane  1206  exiting coating chamber  1200  may be delivered through cooling stage  1268 . Cooling stage  1268  may include any suitable cooling mechanisms to cool membrane  1201  as it is fed from heated calender rollers  1212 ,  1214  of coating chamber  1200 . Cooling stage  1268  may include one or more apparatuses to direct ambient or chilled air, such as, for example, air knives, onto the top and bottom surfaces of the membrane  1201 . In other embodiments, cooling stage  1268  may include one or more outfeed rollers on or between which membrane  1206  may be calendered. The outfeed rollers may be chilled to ambient or cooler temperatures. By cooling the membrane  1206  immediately after it exits coating chamber  1200 , cooling stage  1268  may set warm membrane  1206 , control shrinkage, and preventing crinkles and other surface defects on membrane  1206 . 
     Following cooling stage  1268 , membrane  1206  enters rewinding stage  1270 . Rewinding stage  1270  may include a number of rollers or a festoon that may deliver membrane sheet  1206  to rewinder  1272  configured to wind membrane sheet  1206  into a roll. Rollers and rewinder  1272  of rewinding stage  1270  may be configured to apply a constant tension on membrane sheet  1206  as membrane sheet  1206  is wound into the roll of membrane  1260 . The tension applied on membrane sheet  1206  may be approximately two pounds per linear foot in a warm state. A tension significantly higher than 10 pounds per linear foot applied on membrane sheet  1206  in a warm state may create surface defects in membrane sheet  1206 , such as microfractures, that may result in an undesired increase in the permeability of membrane sheet  1206 . No tension or a tension significantly lower than one pound per linear foot applied on membrane sheet  1206  may disrupt deposition of the microporous particles on membrane sheet  1206 , such as the uniformity and distribution of the microporous particles on the sheet  1206  surfaces. 
     Membrane  1206  manufactured by the manufacturing process of the present disclosure may include a number of advantageous properties when applied as a substrate for heat and/or moisture transfer applications, such as enthalpy exchangers. The coating surface of first calender roller  1212  may contact the entire top surface of substrate  1202 , and the coating surface of  1204  second calender roller  1214  may contact the entire bottom surface of substrate  1201 . In this configuration, the entire surface area of substrate  1201  may be impregnated with microporous particles. Rollers  1212 ,  1214  may promote complete coverage of membrane  1206  with microporous particles. Rollers  1212 ,  1214 , in combination with doctor blades  1232  and shrouds  1236 , may also promote a homogenous and uniform embedding of the microporous particles into the surfaces of substrate  1201 . In some embodiments, microporous particles may form a thin layer on the surfaces of membrane  1206 , such as, for example, approximately 1 mil thick on each side of substrate  1201 , and microporous particles may comprise 80-90 weight percent of the impregnated substrate material. 
     As a substrate material for heat and/or moisture transfer applications, it may be desirable for membrane  1206  to be impermeable to air. In some embodiments of the present disclosure, membrane  1206  may be formed of a paper coated with gamma alumina. In other embodiments, membrane  1206  may be formed of thermoplastic sheet coated with gamma alumina. Alumina may act as a natural release agent while any voids or areas of non-uniform coating will result in immediate adhesion of membrane material. 
     Membrane  1206  formed of a paper coated with gamma alumina may have a wide pore size distribution. An example of commercially available gamma alumina is VGL 15 produced by U.O.P. Corporation. The porosity selected of the gamma alumina-coated paper may permit the flow of moisture across membrane  1206  but block the flow of air. Accordingly, the gamma alumina-coated paper may accommodate both heat and moisture transfer across membrane  1206 . 
     Preferred microporous particles may be a transition alumina, such as gamma alumina, due to their inert properties, electrical charge properties, lower cost, and wide market availability. These materials may be activated for adsorption by removing water from their hydrated precursors. Preferred surface area ranges may be between 100 m 2 /gm and 250 m 2 /gm. Preferred pore volume ranges may be 1.30 cc/g to 1.40 cc/g. Preferred loose bulk density optimized for spraying and imparting electrostatic charges may be between 150 kg/m 3  to 200 kg/m 3 . Friability index values of 9-10 may be preferred. The higher the friability index, the more easily the product may be deagglomerated and may accept a charge more rapidly upon entrance into coating apparatuses. The friability index may be a function of calcination conditions. The friability index is the relative loss of &gt;20-micron particles in a nominal 5 wt % slurry of caused by ultrasonification. 
     Membrane  1206  formed of a thermoplastic sheet coated with gamma alumina of the present disclosure may have a pore volume of approximately 1.36 cc/g. The porosity of the gamma alumina-coated thermoplastic sheet may restrict the flow of both air and moisture across the membrane  1206 . Accordingly, the gamma alumina-coated thermoplastic sheet may accommodate only heat transfer across membrane  1206 . The microporous particles may be any material capable of efficiently holding liquids through capillary action and surface tension while allowing for imparting a charge. The microporous material may also be capable of efficiently adsorbing/desorbing said moisture to a counterflowing air stream. Examples of such microporous particles, include, for example, activated aluminas, silica gels, molecular sieves, porous titania, or zeolites, activated carbon, and mixtures thereof. 
     A single monolayer of microporous particle on the top side and a monolayer of microporous particle on the bottom side with greater than 99% roller coating coverage may be achievable. Coefficient of heat transfers may meet or exceed that of aluminum foils of equivalent thicknesses due to the high surface areas disrupting the boundary layer for fluid flow. Preferable heat transfer coefficients may exceed 59-64 w/m2·K at air velocity of 3 m/s. Preferable membrane thickness may range between 3 and 7 mils. A high tear resistance may be achievable utilizing polyethylene or polypropylene reinforced with various fiber types. Porous particles may be physically embedded onto the surface of a thermoplastic and held in place due to the physical porosity structure of the particle. Preferable weight ranges of a substrate before application of microporous particles may be 15 to 35 grams per square meter. Preferable weight ranges after application of microporous particles may be 60 to 130 grams per square meter. 
     The surfaces of the gamma alumina-coated paper and the gamma alumina-coated thermoplastic sheet may be highly wettable because the gamma alumina may adsorb large quantities of moisture. Moreover, the thermoplastic fibers of the gamma alumina-coated thermoplastic sheet may have low surface tension and promote sheet flow of moisture, including water and a liquid desiccant, such as lithium chloride, along the surfaces of the membrane  1206 . By promoting the flow of a liquid desiccant along the surfaces of the membrane  1206 , the thermoplastic fibers may promote air-to-liquid surface interaction resulting in a higher transfer efficiency from membrane  1206 . In some embodiments, the thermoplastic sheet may be corona treated prior to being coated with the gamma alumina. Corona treating the surfaces of the thermoplastic sheet may further promote bonding of the gamma alumina to the sheet and may increase the wettable properties of membrane  1206 . 
     While membrane  1206  of the present disclosure has been described in applications as a substrate for heat and moisture transfer applications, such as enthalpy exchangers, it would be apparent to persons of ordinary skill in the art that membrane  1206  may be used in other applications. For example, in some applications, membrane  1206  may be used as a battery separator material in an electrochemical cell. 
     Membrane  1206  may be processed under suitable post-manufacturing treatments. In some embodiments, membrane  1206  may be treated with a desiccant to increase the adsorption properties of membrane  1206  and further reduce its permeability. For example, membrane  1206  may be exposed to a brine solution including a liquid hydroscopic salt desiccant, such as lithium chloride, and dried so that desiccant is absorbed and maintained by membrane  1206 . 
     Membrane  1206  may be folded and joined at certain edge locations to form multiple opening exchangers for various applications, including heat and/or water vapor exchangers. The exchangers may be suitable for use as exchangers in energy recovery ventilators (ERV) applications. The exchangers may also be used in heat and/or moisture applications, air filter applications, gas dryer applications, flue gas energy recovery applications, sequestering applications, gas/liquid separator applications, automobile outside air treatment applications, carbon dioxide scrubbing applications, airplane outside air treatment applications, and fuel cell applications. The exchangers typically may be disposed within a housing. 
     For example, in heat and/or moisture transfer applications, such as enthalpy exchangers membrane  1206  may be folded, layered, and sealed at certain edge locations to form an exchanger having multiple membrane layers with a plurality of inlet and outlet passageways in an alternating arrangement, as described in U.S. application Ser. No. 13/426,565; U.S. Pat. Nos. 9,562,726; and 7,824,766, each of which are incorporated herein by reference. 
     Membrane  1206  may be coated with a bonding material. In a preferred embodiment, a thermoplastic material may be extruded onto the edges of membrane  1206 . The thermoplastic material may act as a bonding agent. The membrane  1206  may be folded and sealed at select portions of the edges by welding (e.g., ultrasonic, vibration, or heat) the thermoplastic-coated portions of the edges. 
     In some embodiments, the thermoplastic may be extruded on the edges of both the top surface and the bottom surface of membrane  1206 , and the extruded thermoplastic material on the top surface and the extruded thermoplastic material on the bottom surface may extend laterally and join together. In other embodiments, the thermoplastic material may be extruded on the edges of only one of the top surface and the bottom surface of membrane  1206 , and the extruded thermoplastic material may extend laterally and wrap around the edges of the membrane  1206  and bond to the other of the top surface and the bottom surface. 
     The thermoplastic material may be any suitable thermoplastic, including, for example, polyethylene. The width of the thermoplastic material extruded on membrane  1206  may be approximately 0.125-0.25 inches but may be adjusted to any other width appropriate to achieve a suitable bonding area between folds of membrane  1206 . The microporous particles, such as gamma alumina, impregnated into the surface of substrate  1201  may protect membrane  1206  from potential damage that may otherwise result from the high heat of the edge coating process. For example, the gamma alumina deposited on substrate  1201  may insulate substrate  1201  from the high heat of the extruded polyethylene. 
     Separators for Exchanger and Related Methods of Manufacture 
     The enthalpy exchanger of the present disclosure may comprise membrane  1206  and separator. Separator may be positioned between layers of membrane  1206 . Separator may be disposed in some or all the passageways between adjacent membrane layers and may assist with fluid flow distribution and/or to help maintain separation of the membrane layers. In some embodiments, separator may be a corrugated netting formed of thermoplastic material. Separator may be formed of any suitable material, including, for example, corrugated aluminum inserts, plastic molded inserts, and mesh inserts. In some embodiments, the separator may include porous materials, such as a porous felt, to facilitate wicking and wetting of membrane  1206 . As discussed in more detail below, separator may be inserted during the folding and joining process of membrane  1206  in forming the enthalpy exchanger. Alternatively, separator may be inserted between membrane layers after the enthalpy exchanger has been formed. In particular, separator may be inserted between adjacent membrane layers after membrane  1206  has been folded but before the select edges of membrane  1206  have been joined together. 
       FIG. 12  illustrates a perspective view of one layer  1302  of separator  1300 . Separator  1302  may be a corrugated netting  1304  formed of a thermoplastic material, such as, for example, polypropylene or polyethylene. Persons of ordinary skill in the art would appreciate that corrugated netting  1304  may be formed of any other suitable thermoplastic material. Corrugated netting  1304  preferably has a weight of less than 3 lbs/1,000 ft 2  and, more preferably, less than 1.5 lbs/1,000 ft 2 . Utilizing a thermoplastic material to form corrugated netting  1304  may be advantageous because thermoplastic materials may be resistant to most forms of corrosion, which may allow for operation in air streams containing corrosive chemicals. Further, thermoplastic materials may be compatible with most forms of heat and vapor membranes. 
     Corrugated netting  1304  may include a first plurality of filament members  1306  extending along a first plane (the X-plane) in a sinusoidal pattern. Corrugated netting  1304  may also include a second plurality of filament members  1308  that may extend along a second plane transverse or at an angle to the first plane (the Y-plane) and connect to the first plurality of filament members  1306 . The second plurality of filament members  1308  preferably may be substantially straight and connect to the first plurality of filament members  1306  at 90° angles relative to the X-plane. Separator structure  1300  provides appropriate spacing between membrane  1206  layers. 
     Sinusoidal filament members  1306  may include an amplitude Z. Amplitude Z may define a discrete fluid flow channel within the passageways of the exchanger. In some embodiments, amplitude Z may be 0.8 mm for a type “F” flute at 125 flutes per foot. In other embodiments, amplitude Z may be 1.6 mm for a type of “E” flute at 95 flutes per foot. Additionally, amplitude Z may be 3.2 mm for a type of “B” flute at 49 flutes per foot. Further, amplitude Z may be 4.0 mm for a type of “C” flute at 41 flutes per foot. The size of apertures  1310  of corrugated netting  1304  formed between the filament members  1306 ,  1308  may be selected depending on the desired vapor transmission, pressure drop, and separator strength. 
     For example, decreasing the distance between adjacent sinusoidal filament members  1306  and/or the distance between adjacent connector filament members  1308  may reduce the size of the apertures  1310  and increase the structural strength of the separator  1300 . The reduced size of the apertures  1310  may, however, restrict a desired vapor transmission across membrane  1206  and may contribute to a higher pressure drop of fluid, such as air, flowing through the passageways of the exchanger. Increasing the distance between adjacent sinusoidal filament members  1306  and/or the distance between adjacent connector filament members  1308  may increase the size of apertures  1310 . The increased size of apertures  1310  may accommodate a desired vapor transmission across membrane  1206  and may result in a lower pressure drop of fluid flowing through the passageways of exchanger. The increased size of apertures  1310  may, however, decrease the structural strength of separator  1300 . 
     In a preferred embodiment, Y-axis filament members  1308  may be of similar distance and strength as X-axis filaments  1306 . Filament connections may occur at the apex of each curve. Strand thickness may range between 4-20 mil. Separator  1300  may withstand 12 inches of wg pressure differential at 72° F. 
     Separator  1300  may be used in any appropriate heat and moisture exchanger design. Corrugated netting  1304  of separator  1300  may be produced through an extrusion process. Corrugated netting  1304  of thermoplastic material may be preferably biaxial oriented, which may be lighter in weight and more flexible than extruded square mesh. Orientation “stretches” extruded square mesh in X and Y directions under controlled conditions, which may produce strong, flexible, and light weight netting. Biaxial-oriented corrugated netting  1304  may have improved performance over known heat and water vapor separator materials and techniques. 
     Apertures  1310  of corrugated netting  1304  may provide more membrane surface area to the air stream, and in some applications, may facilitate faster vapor transfer over separators formed of corrugated sheet materials, such as foils, plastics, or paper. In addition, water vapor within an air stream flowing through a passageway of exchanger separated with corrugated netting  1304  may on average travel a shorter distance to interact with membrane  1206  compared to a passageway with a corrugated sheet separator. Further, biaxial-oriented corrugated netting  1304  may facilitate fluid movement in both the X and Y plane directions. Airflow entering a corrugated sheet separator, however, may travel only in a straight-line path. Bi-directional airflow provided by biaxial-oriented corrugated netting  1304  may allow for a broader range of geometric shapes within the context of heat and moisture exchangers. Corrugated netting  1304  may also utilize less material than corrugated sheet separators, which may achieve both cost reduction and better performance in smoke/fire testing. 
     An exemplary process for manufacturing separator  1400  according to the present disclosure will now be described with reference to  FIGS. 13 a -13 d   . A roll of thermoplastic netting material  1402  may be continuously delivered to corrugation chamber  1404 . Corrugation chamber  1404  may include housing  1406  enclosing first continuous belt  1408  and second continuous belt  1410 . First continuous belt  1408  includes first corrugated surface  1412  having corrugation crests and valleys, and second continuous belt  1410  includes second corrugated surface  1414  having corrugation crests and valleys. The corrugation crests of first corrugated surface  1412  may mate with the corrugation valleys of second corrugated surface  1414 , and corrugations crests of the second corrugated surface  1414  may mate with the corrugation valleys of first corrugated surface  1412 . Corrugation chamber  1404  may further include first drive unit  1416  configured to drive first continuous belt  1408  and second drive unit  1418  configured to drive second continuous belt  1410  in synchronous operation. Each of drive units  1416 ,  1418  may include one or more pulleys or rollers  1426 ,  1428  rotatably driven by a suitable power source, such as, for example, a motor. Continuous belts  1408 ,  1410  may be trained over pulleys  1426 ,  1428 , and pulleys  1426 ,  1428  and may rotate and drive continuous belts  1408 ,  1410 , mating together first and second corrugated surfaces  1412 ,  1414 . 
     In some embodiments, rollers  1426 ,  1428  may be at least 0.5 meters in diameter. Corrugated belts  1408 ,  1410  may have amplitudes of between 1.5 mm and 6 mm and widths between 250 mm and 1000 mm. Continuous belts  1408 ,  1410  may first be formed with the sinusoidal profile and then precisely cut to length at the apex of a flute. 
     Continuous belts  1408 ,  1410  may be welded end-to-end to form a continuous loop using micro-laser welding techniques. In certain embodiments, the alignment and corrugation intervals may be maintained through the micro-laser weld utilizing fixturing to maintain tolerances while micro-welding. Maintaining an acceptable interval pattern and tolerances may prevent cutting or breaking of the biaxial netting. In other embodiments, welding methods may include WIG, plasma, electron beam or laser welding. Continuous belts  1408 ,  1410  may be made from a 17-7 or 17-4 stainless steel with a high tolerance to repeated flexural and fatigue resistance. Infeed web tension may be maintained between 5 and 20 pounds per linear foot. Higher web tensions may result in a thinner sinusoidal strand. Residence time between inlet and outlet nips is between 5 and 30 seconds depending on thickness of strands. 
     As netting material  1420  is fed through first and second continuous belts  1408 ,  1410  netting material  1420  may be pressed between first and second corrugated surfaces  1412 ,  1414  of continuous belts  1408 ,  1410 . Heat and pressure from continuous belts  1408 ,  1410  may corrugate netting material  1420  and form sinusoidal members  1306  of separator  1300 . Heat may be applied on portions of continuous belts  1408 ,  1410  where netting material  1420  enters. For example, a heat source, such as heat lamps  1422 , may be positioned proximate an entry portion  1424  of continuous belts  1408 ,  1410  to heat corrugated surfaces  1412 ,  1414  as they initially contact and press the sheeting structure  1420 . Additionally, or alternatively, pulleys  1426 ,  1428  proximate the entry portion  1424  of continuous belts  1408 ,  1410  may be heated, via, for example, heating element within the core of pulleys  1426 ,  1428 , and may transfer heat to corrugated surfaces  1412 ,  1414  of continuous belts  1408 ,  1410 . In some embodiments, corrugated surfaces  1412 ,  1414  may be heated to approximately 240° F. to 260° F. for polypropylene and 180° F. to 220° F. for polyethylene. 
     Persons of ordinary skill would understand that other combinations of time, pressure, temperature, and line speed may also be used to form the netting of the present disclosure. Any such combinations of parameters are appropriate which may enable separator  1430  to be formed into the desired shape and substantially to hold this shape through subsequent processing, assembly, and use. 
     Corrugated netting material  1432  may be released and collected as material  1432  exits output portion  1434  of continuous belts  1408 ,  1410 . Corrugated netting material  1432  may be cooled proximate output portion  1434  of continuous belts  1408 ,  1410  to set the corrugations. In some embodiments, cooling source  1438 , such as, for example, one or more air knives, may be positioned proximate output portion  1434  of continuous belts  1408 ,  1410  to cool corrugated netting material  1432 . One or more air knives may direct air at the top and bottom surfaces of corrugated netting material  1432  at an ambient temperature or cooler, such as, for example, 80° F. to 120° F. Additionally, or alternatively, pulleys  1426 ,  1428  proximate output portion  1434  of continuous belts  1408 ,  1410  may be cooled, via, for example, a cooling element within the core of pulleys  1426 ,  1428 , and may remove heat from the corrugated netting material  1432 . 
     As corrugated netting material  1432  is cooled and released from continuous belts  1408 ,  1410 , corrugated netting material  1432  may be collected by collector  1442 . Collector  1442  may include a number of rollers or festoon  1448  that may deliver corrugated netting material  1432  to rewinder  1446  configured to wind corrugated netting material  1432  into roll  1444 . Rollers  1448  and rewinder  1446  of collector  1442  may be configured to apply a constant tension on corrugated netting material  1432  as corrugated netting material  1432  is wound into roll  1444 . The tension applied on the corrugated netting material  1432  may be approximately less than 0.5 pounds per linear foot. Collector  1442  may apply tension on corrugated netting material  1432  to prevent surface irregularities, such as, for example, crinkles, and to maintain the alignment of the sinusoidal members  1306  along a longitudinal axis of corrugated netting material  1432 . 
     The process for manufacturing separator  1432  according to the present disclosure may provide numerous advantageous and improvements over known processes for manufacturing corrugated netting materials. Known processes may employ corrugated rollers to form a corrugated profile on a material fed between the rollers. These known processes, however, may have limitations associated with the surface area provided by the corrugated rollers for corrugating a netting material. Continuous belts  1408 ,  1410  of the present disclosure may provide a larger corrugation surface compared to known corrugated rollers. The larger corrugation surface area of continuous belts  1408 ,  1410  may accommodate a greater output rate of corrugated netting material and may improve the uniformity and alignment of the corrugated profile of the corrugated netting. Continuous belts  1408 ,  1410  may also accommodate a larger heating surface area for forming the corrugations on the netting material. The larger heating surface area may allow continuous belts  1408 ,  1410  to heat a greater area of netting material and at a wider range of temperatures. 
     For example, a higher temperature profile and area may improve the setting of corrugations on netting material, permit a higher amplitude of corrugations, and strengthen corrugations against deformation (i.e., increase the shape memory of the corrugations). Moreover, continuous belts  1408 ,  1410  may provide a dwell section between the heating portion and the cooling portion that may facilitate setting corrugated netting material. Continuous belts  1408 ,  1410  may also produce corrugated netting material  1432  with thicker sinusoidal and connection members  1306 ,  1308  compared to a corrugated netting material  1432  manufactured by known corrugated rollers. The disclosed process may afford a much longer dwell time in which the filaments can be fully heated and then fully cooled before being released, unlike a conventional corrugation roller system. Furthermore, the tension applied to corrugated netting material by collector  1442  may maintain the alignment of sinusoidal members  1306  and may improve the uniformity of corrugated netting material  1432 . 
     While separator  1432  of the present disclosure has been described in applications as a separation structure for membrane layers of heat and moisture transfer bodies, such as enthalpy exchangers, persons of ordinary skill in the art would appreciate that separator  1432  may be utilized as a separation structure in various other applications. For example, in some applications, the separator  1432  may serve as a separation structure for air filters known in the art. As shown in  FIGS. 14 a -14 c   , air filter  1500  may include filter material  1504 , such as, for example, any suitable fibrous material that may remove solid particulates, including, dust, pollen, mold, and bacteria, from the air. In some embodiments, filter material  1504  may include membrane  1206  discussed above. Air filter  1500  may include input side  1514  for receiving air to be filtered and output side  1516  from which filtered air may exit air filter  1500 . The filter material  1504  may be folded to form a plurality of pleats  1508 . As shown in  FIGS. 14 a -14 c   , air filter  1500  may also include separator  1300  positioned on output side  1516  of air filter  1500  and folded with pleats  1508  of filter material  1504 . 
     Air filters with separator  1300  according to the present may provide numerous advantageous and improvements over known air filters. Existing air filters may employ a plurality of bridge structures that may space out and connect adjacent pleats of the filter material via an adhesive or weld. The bridge structures generally may be positioned on the input side of the air filter. This configuration may restrict air flow through the air filter and reduce the filtering performance of the air filter. Separator  1300  of the present disclosure, may provide improved air flow through the air filter. Corrugated netting material  1304  of separator  1300  may be more open than existing bridge structures, which may accommodate more air flow through the filter material. For example, 97-98% of the surface area of corrugated netting material  1304  may be open and provide unrestricted air flow. Moreover, the sinusoidal and connecting members  1306 ,  1308  of corrugated netting material  1304  may be thinner than existing bridge structures to further minimize restrictions to air flow. In some embodiments, for example, the sinusoidal and connecting members  1306 ,  1308  may be approximately 1/16 of an inch thick. Separator  1300  may also be less dense than existing bridging structures and may provide a spacing structure that may be lighter in weight and smaller in size. 
     The compressible property of separator  1300  may also improve the performance of the air filter. As the input side of the air filter receives air, the pleats of the filter material may fan out or open to increase the capacity of the filter material to filter particulates from the input air. Separator  1300  disposed on the output side of the air filter may receive the load from the pleats opening up on the input side and compress. 
     As discussed above, an enthalpy exchanger may be formed of membrane  1206  and separator  1300 . For example, membrane  1206  and separator  1300  may form enthalpy exchangers as described in U.S. application Ser. No. 13/426,565, which is incorporated herein by reference. 
     Air Conditioner Modules and Systems 
       FIGS. 15 a -15 h    illustrate perspective views of an evaporative cooling and/or steam regenerating liquid desiccant air conditioner module  1600  and its related components according to the present embodiment. The present disclosure may be directed to an air conditioning module and system configured to perform various air treatment operations. Such air treatment operations may include, but are not limited to: (1) changing the moisture and/or heat content of the air being processed; (2) absorbing carbon dioxide (CO 2 ), formaldehyde, and other volatile organic compounds (VOC) from the air being processed; (3) regeneration of weak solutions of the liquid desiccant being processed; (4) regeneration of spent liquid sorbents of the reversibly binding aqueous solution being processed; (5) recovery of moisture and/or heat content between two remote air streams; and (6) changing the heat content of a working liquid using indirect/direct evaporative cooling. 
     Air conditioner module  1600  may comprise exchanger housing  211  and exchanger  213 . The entirety of exchanger  213  may be contained inside exchanger housing  211 . Exchanger  213  may be formed of membrane  1206  comprising a thermoplastic sheet embedded with gamma alumina. Exchanger  213  may comprise a plurality of plates  1615  with a plurality of intermittently sealed plate edges  1620  arranged in a successively stacked configuration. Portions of plates  1615  may be spaced apart to provide a first series of discrete alternating passages  1613  and a second series of discrete alternating passages  1614 . 
     A first air stream  1680  may be passed through first series of passages  1613  and a second air stream  1681  may be passed through second series of passages  1614  in a counterflow configuration with respect to first air stream  1680 . First and second air streams  1680 ,  1681  may be maintained physically separate from one another, while maintaining thermal contact between them to allow heat to freely pass therebetween. Air conditioner module  1600  may include first liquid supply conduit  1622  secured in first liquid threaded inlet  1636  and second liquid supply conduit  1624  secured in second threaded inlet  1638 . First liquid  1626  and second liquid  1628  may be feed into first liquid supply conduit  1622  and second liquid supply conduit  1624 , respectively. First liquid  1626  and second liquid  1628  may pass through to adjoining air conditioner module  1600  via first liquid return conduit  1623  and second liquid return conduit  1625 , respectively. 
     First liquid  1626  may exit air conditioner module  1600  through first liquid threaded outlet  1640 , and second liquid  1628  may exit air conditioner module  1600  through second liquid threaded outlet  1642 . These return conduits may facilitate a plurality of air conditioning modules being supplied with first liquid  1626  and second liquid  1628  and may be used to flush module  1600  of impurities that may build up. With appropriate modifications such as the, The air conditioner of the present disclosure may be adapted by, for example, selecting first and second air stream and type of delivered liquids, for using the air conditioner in various applications, including, but not limited to, indirect evaporative cooling, direct evaporative cooling, liquid desiccant dehumidification, carbon dioxide scrubbing, VOC scrubbing, hot water liquid desiccant regeneration, indirect steam liquid desiccant regeneration, hot water regeneration of scrubbing reversibly binding aqueous solutions, indirect steam regeneration of scrubbing reversibly binding aqueous solutions, and the like. 
     Conduits  1622 ,  1623 ,  1624 , and  1625  may extend through a liquid distribution system comprising a stacked configuration of plates including first distribution headers  1632  and second distribution headers  1634 .  FIGS. 15 d -15 h    illustrate perspective views of first and second distribution headers  1632 ,  1634  and their related components according to the present disclosure. In some embodiments, the distribution headers  1632  and  1634  may be made of silicone, urethane, thermoplastics, vital, Teflon, or other non-corroding sealing material. Headers  1632  and  1634  may include silicone leaves having porous members  1630 . First and second distribution headers  1632  and  1634  may be sealed together by compression plates  1645  tied together by compression rods  1644  passing through headers  1632  and  1634 . 
     As illustrated in  FIG. 15 g   , for example, membrane  1206  of exchanger  213  may be positioned between first distribution headers  1632  and second distribution headers  1634 . Membrane  1206  may also include a plurality of membrane conduit holes  1672  aligning with conduits  1622 ,  1623 ,  1624 , and  1625 . First liquid  1626  may be delivered into first distribution headers  1632  and may be discharged through conduit  1622  or  1623  and onto membrane  1206  through membrane conduit holes  1672  aligned with conduit  1622  or  1623 . Second liquid  1628  may be delivered into second distribution headers  1634  and may be discharged through conduit  1624  or  1625  and onto membrane  1206  through membrane conduit holes  1672  aligned with conduit  1624  or  1625 . A suitable alignment mechanism, for example, a tine, may be coupled to headers  1632  and  1634 , membrane conduit holes  1672 , and exchanger housing  211  holes  1640  and  1638  to maintain the alignment and registration of the components of the liquid distribution system. 
     First distribution header  1632  may comprise first liquid feeder channel  1648  and a plurality of feeder holes  1652 . Porous members  1630  may be inserted into feeder holes  1652  by, for example, a press-fit. Porous members  1630  may be, for example, porous wicks or pipette-shaped porous inserts for delivering liquids to membrane  1206  of exchanger  213 . Porous members  1630  may be in direct contact with the inside membrane surfaces of the first series of fluid passages  1613 . Second distribution header  1634  may comprise second liquid feeder channel  1650  and a plurality of feeder holes  1652 . Porous members  1630  may also be inserted into feeder holes  1652  of second distribution header  1634 . First and second liquids  1626 ,  1628  may be dispensed directly to membrane surfaces of first and second passages  1613 ,  1614  via porous members  1630  with the liquids maintaining intimate contact in the transition from feeder holes  1652  to membrane surfaces. 
     Liquids may be dispersed without creating microdroplets which may become entrained within the air streams. Microdroplet entrainment may occur through unrestrained transition between feeder holes  1652  and membrane surfaces without porous members  1630 . Porous members  1630  may provide protection from the aerodynamic forces posed by flowing airstreams at the exit of liquids from feeder holes  1652 . These porous members  1630  may be advantageous for strong hygroscopic liquid desiccants and strong carbon dioxide absorbing alkylamine solutions. Strong liquid desiccants may be highly polar by nature, which may make then even more susceptible to entrainment absent porous members  1630  to maintain fluid flow at the transition to the membrane surfaces. Small amounts of alkylamine solutions entrained into an air stream may create an unpleasant amine smell inside building enclosures. 
     Dispensing liquids via porous members  1630  may be accomplished without spanning or bridging of liquids across the respective airstreams along the inside surfaces of first and second fluid passages  1613 ,  1614 . Spanning or bridging may occur through unrestrained transition between feeder holes  1652  and membrane surfaces absent porous members  1630 . Porous members  1630  may provide protection from the aerodynamic forces posed by flowing airstreams. Aerodynamic forces may arbitrarily focus the flow into various concentrated streams upon wetting of membrane surfaces. Absent porous members  1630 , aerodynamic forces from flowing airstreams may favor one of the two inside surfaces of fluid passages  1613 , 1614  causing uneven flow and reducing performance. The strong polarity of many liquids may further exacerbate the spanning and bridging phenomena. 
     Dispensing liquids via porous members  1630  may also be accomplished, without variance in flow rates, through a plurality of feeder holes  1652 . Flow variance may occur through unrestrained transition inside feeder holes  1652  because of variability in entrance/exit effects, diameter, length, or wall friction. Porous members  1630  may deliver liquids to the membrane surface in a uniform manner across a plurality of feeder holes  1652 . This uniform resistance may ensure that each feeder hole  1652  has the same volume of liquid flowing through it. Porous members  1630  may reduce distribution header pressure and related pump energy. Distribution headers  1632 ,  1634  may operate below 1 psi while still affording full control of variable flow rates. Furthermore, precise dispensing of liquids via porous members  1630  may promote uniform wetting characteristics on the inside membrane surfaces of passages  1613 ,  1614 . Distribution headers  1632  and  1634  and porous members  1630  may be fluidly connected to one of the six sides of exchanger  213 . Liquid dispensing may be accomplished without blocking or interfering with first or second air streams  1680 ,  1681 . 
     Porous members  1630  may include inlet  1654  passing through the walls of first distribution header  1632  and into first liquid feeder channel  1648 . Porous members  1630  may also include outlet  1656  passing through the walls of first distribution header  1632  and positioned outside first distribution header  1632 . First liquid  1626  may enter the pores of porous members  1630  at inlet  1654 . First liquid  1626  may pass through the porous members  1630  and exit the pores of porous members  1630  at outlet  1656  in direct contact with the inside membrane surfaces of first passages  1613 . Porous members  1630  may provide a continuous flow of first fluid  1626  from first end to second end of the first passages  1613  while the first fluid  1626  is in contact with the first air stream  1680 . 
     Second liquid  1628  may enter the pores of porous members  1630  at inlet  1654 . Second liquid  1628  may pass through porous members  1630  and exit the pores of porous members  1630  at outlet  1656  in direct contact with the inside membrane surfaces of second passages  1614 . Porous members  1630  may provide a continuous flow of second liquid  1628  from first end to a second end of second passages  1614  while second liquid  1628  is in contact with second air stream  1681 . 
     Porous members  1630  may include any suitable material capable of capillary action, including, for example ceramic, metal, or plastic such as polypropylene or polyethylene. Porous members  1630  may have an average controlled pore size of between 25 and 60 microns, and preferably 30 microns. Porous members  1630  may comprise microporous particles selected from: porous titania; transition alumina; silica gel; molecular sieve; zeolite; activated carbon; porous polypropylene; or porous polyethylene. Porous members  1630  may also include a width substantially equal to the spacing between the plates  1615  to facilitate direct contact and capillary action on the inside walls of plates  1615 . The motion of liquid flow may be controlled by the porous link between headers  1632 ,  1634  and membrane walls  1206 , whereby the continuous flow of liquid may avoid the formation of droplets by blowing air currents that may be entrained in passing air streams  1680 ,  1681 . 
     Headers  1632 ,  1634  of the present disclosure may provide continuous liquid flow through porous members  1630  by a combination of capillary action, surface tension, adhesion, and little to no additional head pressure beyond given fluid column height and with the porous members  1630  being in intimate contact with the membrane walls  1206 . Liquid may pass through porous members  1630  via a tortuous path, which may result in a uniform deposition of flow characteristics regardless of where an individual porous member  1630  is located within the system. 
     As shown in  FIG. 15 h   , headers  1632  and  1634  may be formed of silicone leaves. Porous members  1630  may be pressed into the silicone leaves and may provide controlled delivery of liquid onto membrane walls  1206 . The components of first and second distribution headers  1632 ,  1634  may provide for a low flow of liquids under low pressure. First and second distribution headers  1632 ,  1634  may deliver continuous flow  1658  of liquid at a time onto the membrane walls  1206  of first and second passages  1613  and  1614 , thereby affording an ultra-low flow conditioner. Continuous flow  1658  of liquid may flow down membrane walls  1206  of first and second passages  1613  and  1614  in a direction perpendicular to first and second air streams  1680  and  1681 . The headers  1632  and  1634  may be integrated into the exchanger  213  during the folding or layering process of membrane  1206 . In one embodiment, for example, header  1632  may be positioned on a layer of membrane  1206  after each folding or layering step of membrane  1206 . Headers  1632  and  1634  may be positioned on the layers of membrane  1206  manually or by an automated process, such as, for example, a 3D printing step between folding steps. 
     Membrane  1206  of exchanger  213  may be formed of a thermoplastic sheet comprising porous material, such as, for example, gamma alumina, disposed along at least a portion of the inside surfaces of the first and/or second series of passages  1613  and  1614 . The thermoplastic sheet comprising porous material on both sides may be about 4 to 7 mils thick. The porous material of membrane  1260  may draw up liquid from the porous members  1630  via capillary action and may provide uniform flow of first and second liquids  1626  and  1628  via gravity from first and second distribution headers  1632  and  1634  to first and second ends of plurality of plates  1615 . As discussed above, the surfaces of the thermoplastic sheet coated with porous material, such as, for example, gamma alumina, may form membrane  1206  and may be highly wettable because the porous material, like gamma alumina, may facilitate large quantities of liquid to flow within its pore structure and adsorb large quantities of moisture. This may also provide a greater surface area for heat transfer within first and second plurality of passageways  1613  and  1614  and improved cooling of first and second air streams  1680  and  1681 . Furthermore, wettable membrane  1206  and the delivery of liquid provided by alternating first and second header array  1632  and  1634  may promote hugging of the liquid to membrane walls and inhibit entrainment of undesired liquids into airstreams  1680  and  1681 . 
     Air conditioner module  1600  may also comprise a liquid collection system for collecting first liquid  1626  and second liquid  1628  flowing out of the plurality of first passages  1613  and plurality of second passages  1614 . The liquid collection system may include first liquid drain conduit  1616  for collecting the flowing first liquid  1626  from first passages  1613  and second liquid drain conduit  1618  for collecting the flowing second liquid  1628  from second passages  1614 . 
     First and second liquid drain conduits  1616 ,  1618  may be located entirely outside of the exchanger  213  and may be adjacent to the second ends of the plurality of plates  1615 . By being wholly outside the exchanger  213 , first and second liquid drain conduits  1616 ,  1618  may facilitate lower manufacturing costs and a compact form factor and may be readily and efficiently inspectable. External liquid drain conduits  1616 ,  1618  may be optimized (e.g., by size and/or number) given the desired number of air conditioner modules  1600  implemented and the anticipated fluid flows corresponding to given building design conditions. The reservoir-less design may also reduce costs and weight, may require less sealing, and may reduce potential mold growth. 
     Although not depicted, a suitable system may be coupled to exchanger  213  to collect, treat, and recycle the cooling medium and liquid desiccant delivered through exchanger  213 . For example, water or water vapor from first passageways  1612  may be collected and recycled through suitable outlet ducts. In some embodiments, the collected water may be further cooled via a refrigerant or the like before being delivered to exchanger  213 . In addition, the cool weak liquid desiccant from second plurality of passageways  1614  may be collected and passed through suitable outlet ducts to regenerator, such as, for example, a boiler. Strong liquid desiccant from regenerator may then be recycled back to exchanger  213 . In some embodiments, exchanger  213  may be used as the regenerator, rather than a conventional boiler. 
     Exchanger  213  may comprise at least one separator  1300  disposed on each of the inside surfaces of first and second passages  1613  and  1614  for maintaining the space therebetween. Separator  1300  may be formed of a high temperature thermoplastic able to withstand high temperatures (e.g., between 212° F. and 300° F.) in applications where the exchanger  213  is used in a steam regenerating liquid desiccant module. In some embodiments, separator  1300  height may be 0.062 inches to ensure no bridging of fluids and optimize heat transfer. First and second distribution headers  1632  and  1634  may deliver an interchangeable plurality of first and second liquids  1626  and  1628 , such as, for example, strong liquid desiccant, weak liquid desiccant, directly evaporating water, indirectly evaporating water, hot water, cooling tower water, steam condensate, antimicrobial cleaner, or combinations thereof. Delivered liquids may also include those that absorb or adsorb certain air contaminants, such as, for example, carbon dioxide scavengers, formalydyde absorbers, materials that absorb other contaminants, and combinations thereof. 
     Air conditioner module  1600  may provide an interchangeable plurality of air conditioning effects to first and second air streams  1680  and  1681 . The air streams may be conditioned by air conditioner module  1600  to provide, for example: (1) dehumidified or humidified process air; (2) sensibly cooled or heated process air; (3) indirectly and/or directly evaporatively cooled process air; (4) indirectly and/or directly evaporatively cooled working liquid using outside air; (5) remote heat and/or moisture recovery between exhaust air and outside air; (6) steam and/or hot water regeneration of a weak desiccant; and (7) direct and/or indirect fired air regeneration of a weak desiccant. 
     In some embodiments, exchanger  213  may be utilized in evaporative liquid desiccant air conditioning applications. For example, exchanger  213  may be used in air handling modules described in  FIG. 8 a    and air conditioner module described in the  FIG. 15 a -15 h   . In such applications, exchanger  213  may be used in the modules that may provide an evaporative cooling and steam heating air conditioner. 
     Membrane  1206  of the exchanger  213  may be formed of a thermoplastic sheet embedded with gamma alumina. First air stream  1680  may pass through first plurality of passageways  1613  of exchanger  213 . First air stream  1680  may be, for example, outside air, and may undergo direct evaporative cooling within first plurality of passageways  1613 . To that end, a cooling medium, such as, for example, water, may flow on membrane walls defining first plurality of passageways  1613 . The cooling medium may cool outside air  1680 . The outside air  1680  may evaporate the cooling medium and may be released from the first plurality of passageways  1613  as cool moist air. 
     Second air stream  1681  may pass through second plurality of passageways  1614  of exchanger  213 . Second air stream  1681  may be supply air and may be dehumidified as it passes through second plurality of passageways  1614 . 
     In some embodiments, fresh supply air stream  1681  may be super dry air exiting the second plurality of passageways  1614  and may be directed through a direct evaporation device to bring it to supply conditions using vapor compression-based cooling of 55° F. and 100% humidity. In other embodiments, supply air stream  1681  may be cooled, moist air exiting first plurality of passageways  1613  and redirected through second plurality of passageways  1614 . In further embodiments, supply air stream  1681  may be a separate stream of air, such as, for example, recirculated air from the system, such as from a building. In such embodiments, cool moist air from first plurality of passageways  1613  may indirectly cool the recirculation supply air stream  1681 , whereby cool moist air may remove heat from recirculation supply air stream  1681  through membrane walls  1206 . To remove moisture from supply air stream  1681 , liquid desiccant, such as, for example, lithium chloride, may flow onto membrane walls  1206  defining second plurality of passageways  1614 . Lithium chloride flowing wholly within the porosity of the gamma alumina embedded in membrane  1206 , may dehumidify the supply air stream  1681  by adsorbing moisture from supply air stream  1681 . 
     As discussed above and described in  FIGS. 15 d -15 h   , exchanger  213  may also include first and second liquid distribution headers  1632  and  1634  configured to deliver cooling medium and liquid desiccant onto internal membrane walls  1206  forming first and second plurality of passageways  1613 ,  1614  of exchanger  213 . First liquid distribution headers  1632  may deliver cooling medium, such as, for example, water, along first plurality of passageways  1613 . Porous members  1630  may deliver a continuous flow of water onto internal membrane walls  1206  forming first plurality of passageways  1613 , and the water may flow down membrane walls  1206  in a direction perpendicular to outside air flow  1680 . 
     Second liquid distribution headers  1634  may deliver liquid desiccant, such as, for example, lithium chloride, along second plurality of passageways  1614 . Porous members  1630  may deliver a continuous flow of lithium chloride onto the internal membrane walls  1206  forming second plurality of passageways  1614 , and the lithium chloride may flow down membrane walls  1206  in a direction perpendicular to supply air flow  1681 . In some embodiments, flow of water delivered by the headers  1632  may be 1/16 of an inch, and flow of lithium chloride delivered by headers  1634  may be 1/16 of an inch. 
     Air conditioner module  1600  with exchanger  213  and first and second liquid distribution headers  1632 ,  1634  may also be configured to provide indirect evaporative cooling. In such a configuration, a liquid cooling medium, such as water, may be delivered onto internal membrane walls  1206  of both first and second plurality of passageways  1612 ,  1614 . As a result, supply air stream  1681  may be cooled but relatively humid. 
     In some embodiments, air conditioner module  1600  may function as a highly-efficient liquid desiccant regenerator. First liquid  1626  delivered to air conditioner module  1600  may be a weak liquid desiccant, such as, for example, lithium chloride. The lithium chloride may contact first air stream  1680 , which may be atmospheric air. Second air stream  1681  may be directly heated and physically separate from first air stream, while maintaining thermal contact to allow heat to freely pass therebetween and directly warm the lithium chloride through membrane walls  1206 . Heating the lithium chloride may drive off part of the water vapor previously absorbed in the evaporatively cooled module, thus regenerating it. The regenerated liquid desiccant may be returned to conditioner module  1600  to again remove moisture. Water vapor may be discharged from the regenerator module  1600  to the atmosphere. 
     Regenerator module  1600  may implement one or more sources of energy to heat second air stream  1681 . In one embodiment, steam from a boiler may be applied directly to second air stream  1681  in a closed loop to provide uniform heat (e.g., 212° F.) across membrane walls  1206 . Steam condensate forming and flowing down the membrane walls may be collected and reheated. Steam may provide a uniform thermal heating across the entire membrane surface, thereby creating ideal regeneration conditions for driving water molecules out of the lithium chloride. 
     In another embodiment, hot water between 160° F. and 210° F., may be employed within regenerator module  1600  to regenerate lithium chloride. Hot water may be distributed via second distribution header  1634  directly warming the lithium chloride through membrane walls  1206 . In some embodiments, hot water may be used in conjunction with steam heat depending upon the available energy available at a given time period. In other embodiments, second air stream is heated via direct fire combustion to between 200° F. and 300° F., thereby regenerating the lithium chloride. 
     The previously described desiccant regenerator module  1600  may present a substantial surface area flowing with weak lithium chloride to the rejecting atmospheric air stream. This large surface area serves to lower required thermal temperatures and reduce energy use compared to existing regeneration boilers. Furthermore, exchanger  213  comprises the same materials and components and, therefore, allows the regenerator module  1600  to change modes of operation and provide a different function for the building altogether (e.g., during a different season). 
     In a preferred embodiment of an air handling system, a further air handling module comprised of a sensible air-to-air plate exchanger (not depicted) may preheat the first air stream to further enhance the rejection of water molecules out of the liquid desiccant and may also pass back through the said sensible air-to-air plate exchanger. This embodiment advantageously reduces the amount of thermal energy lost to the atmosphere from first air stream  1680 . 
     Although not depicted, a suitable system may be coupled to exchanger  213  to collect, treat, and recycle the cooling medium and liquid desiccant delivered through exchanger  213 . For example, water or water vapor from first passageways  1613  may be collected and recycled through suitable threaded ports. In some embodiments, the collected water may be further cooled via a refrigerant or the like before being delivered to exchanger  213 . In addition, the cool weak liquid desiccant from second plurality of passageways  1614  may be collected and passed through suitable threaded ports to a regenerator, such as, for example, a boiler. The strong liquid desiccant from the regenerator may then be recycled back to the exchanger. 
     Multiple functions and multiple modes may be alternated between, depending on the driving requirements of the conditioned building space. Exchanger  213  with alternating header arrays  1632  and  1634  and supply system may be instantly configured to provide indirect evaporative cooling. In such a configuration, a liquid cooling medium, such as water, may be delivered onto membrane walls of both first and second plurality of passageways  1613  and  1614 . 
     Evaporative liquid desiccant air conditioner modules  1600  may be adjacently stacked in a vertical orientation to form an evaporative liquid desiccant air conditioner system. With reference to  FIG. 8 a   , for example, each module  812   a ,  812   b , and  812   c  may air conditioner modules  1600  may contain the components of air conditioner module  1600  described in  FIGS. 15 a   - 15   h.    
       FIG. 15 i    illustrates a perspective view of an evaporative liquid desiccant hex shaped exchange module  1660  according to the present disclosure. Exchange module  1660  may accommodate airflows in a counterflow configuration. Exchange module  1660  may comprise a plurality of plates  1615  having a plurality of intermittently sealed plate edges  1620  and arranged in a successively stacked configuration. Portions of plates  1615  may be spaced apart to provide first series of discrete alternating passages  1613  and second series of discrete alternating passages  1614 . A first air stream  1680  may be passed through first series of passages  1613  and a second air stream  1681  may be passed through second series of passages  1614  in a counterflow configuration with respect to the first air stream  1680 . Exchange module  1660  may include an air stream divider  1662  to separate the first and second air streams  1680 ,  1681 . 
     Exchange module  1660  may include first liquid supply conduit  1622  secured in first liquid threaded inlet  1636  and second liquid supply conduit  1624  secured in second threaded inlet  1638 . First liquid  1626  and second liquid  1628  may be fed into first liquid supply conduit  1622  and second liquid supply conduit  1624 , respectively. First liquid distribution headers  1632  may deliver first liquid  1626  from first liquid supply conduit  1622  to first series of passages  1613 . Second liquid distribution headers  1634  may deliver second liquid  1628  from second liquid supply conduit  1624  to second series of passages  1614 . First and second liquid distribution headers  1632 ,  1634  may be positioned within first and second passages  1613 ,  1614  of plates  1615 . Positioning first and second liquid distribution headers  1632 ,  1634  within first and second passages  1613 ,  1614  may provide a compact shape and may maintain a hexagonal shape compatible with applications utilizing existing hex counterflow plate-type exchangers. 
     Exchange module  1660  may also include a liquid collection system for collecting first liquid  1626  and second liquid  1628  flowing out of the plurality of first passages  1613  and plurality of second passages  1614 . The liquid collection system may include first liquid drain conduit  1616  for collecting flowing first liquid  1626  from first passages  1613  and second liquid drain conduit  1618  for collecting flowing second liquid  1628  from second passages  1614 . First and second liquid drain conduits  1616 ,  1618  may be located entirely outside of exchanger  213  and may be adjacent to the second ends of the plurality of plates  1615 . 
       FIG. 15 j    illustrates a perspective view of another configuration of evaporative liquid desiccant hex shaped exchange module  1660  according to the present disclosure. As shown in  FIG. 15 j   , first and second liquid distribution headers  1632 ,  1634  may be positioned outside of first and second passages  1613 ,  1614  of plates  1615 . Positioning first and second liquid distribution headers  1632 ,  1634  outside of first and second passages  1613 ,  1614  may provide an obstruction-free pathway for counterflowing first and second air streams  1680  and  1681 . 
     The present disclosure contemplates a multiple function remote energy recovery system. With reference to  FIG. 15 k   , in some embodiments, a system  1690  may be implemented for multiple function remote energy recovery. System  1690  may be configured to recover heat and moisture between two or more detached airstreams. System  1690  may comprise first liquid desiccant recovery exchange module  1691  and second liquid desiccant recovery exchange module  1692 . First and second liquid desiccant recovery exchange modules  1691 ,  1692  may embody exchange module  1660  described in  FIGS. 15 i    and  15   j.    
     First air stream  1680 , which may be, for example, process supply air to a building, may pass through first liquid desiccant recovery exchange module  1691  and may be dehumidified and cooled by first liquid  1626 , which may be, for example, a strong desiccant, and may be cooled by second liquid  1628 , which may be, for example, water evaporating into a second air stream  1681 , such as, for example, atmospheric air, passed through first liquid desiccant recovery exchange module  1691 . 
     With respect to the second liquid desiccant recovery exchange module  1692 , first air stream  1680 , which may be, for example, exhaust air from the building, may pass through module  1692 . First liquid  1626 , which may be a weak desiccant, may remotely extract energy from the exhaust air, while second liquid  1628 , which may be, for example, water evaporating into second air stream  1681 , such as, for example, atmospheric air, passed through second liquid desiccant recovery exchange module  1692 , may simultaneously cool the exhaust air. 
     First liquid desiccant recovery exchange module  1691  may be connected to second liquid desiccant recovery exchange module  1692  via conduit pipes and an enthalpy pump may facilitate flow of liquid desiccant between modules  1691 ,  1692 . First liquid drain conduit  1616  on first exchange module  1691  may collect weak desiccant. The weak desiccant may be pumped to second exchange module  1692  via weak desiccant pump  1664  powered by motor  1665 . Weak desiccant may be delivered to second exchange module  1692  via weak desiccant conduit  1668 . 
     First liquid drain conduit  1616  on second exchange module  1692  may collect strong desiccant. Strong desiccant may be pumped to first exchange module  1691  via strong desiccant pump  1666  powered by motor  1667 . Strong desiccant may be delivered to first exchange module  1691  via strong desiccant conduit  1670 . Second liquid drain conduits  1618  connected to each of first and second exchange modules  1691 ,  1692  may collect excess water that may not be evaporated, and the excess water may be returned back to liquid distribution headers  1632 ,  1634  of modules  1691 ,  1692 . 
     In some embodiments, an evaporatively cooled liquid desiccant air handling unit of the present disclosure may process outdoor air at a temperature of about 86° F. and a humidity ratio of 135 grains. The liquid desiccant used may be a 45% lithium chloride solution. Six hundred cfm may be passed through air handling unit having 0.063″ gaps between plates. The resulting supply air exiting the unit may have a temperature of 80° F. and a humidity ratio of 35 grains. 
     Water or salt water, such as lithium chloride, may be the most common solvent used to remove inorganic contaminants, such as formaldehyde and other VOCs. In some embodiments, the disclosed evaporative cooling and steam regenerating module  1600 , may, independently or concurrently, function as a regenerable scrubber system. 
     In some embodiments, and with reference to  FIG. 15 k   , air handling system  1690  may be implemented for controlling carbon dioxide (CO 2 ), formaldehyde, and volatile organic compound (VOC) emissions from a building enclosure. CO 2  liquid sorbent may flow within the exchanger and may be regenerated by thermal means to release and capture the absorbed CO 2 . Amines are well-known for their reversible reactions with CO 2 , which may make them ideal for CO 2  capture from several gas streams, including flue gas. Systems for controlling and eliminating the CO 2  from a breathable air supply may be utilized in submarines, space vehicles, space suits, and various types of building enclosures. In this respect, selective CO 2  absorption by aqueous alkanolamines may be energy intensive and the absorbant may be corrosive. 
     Physical absorption of pollutant molecules may depend on properties of the gas stream and liquid solvent, such as density and viscosity, as well as specific characteristics of the pollutant(s) in the gas and the liquid stream, including diffusivity and equilibrium solubility. For most regenerative sorbents, these properties may be temperature dependent. Lower temperatures may generally favor absorption of gases by the solvent. Absorption may be enhanced by greater contact surface area, higher liquid gas ratios, and higher concentrations in the gas stream. Chemical absorption may be limited by the rate of reaction, although the rate-limiting step may be typically the physical absorption rate, not the chemical reaction rate. Cold solutions of alkylamines may bind CO 2 , but the binding may be reversed at higher temperatures. The integrated, indirect evaporation of the present disclosed may cool the amines solution, while the integrated secondary air flow path filled with steam indirectly may heat the amines solution. This may create a large enough temperature differential to remove the majority of carbon dioxide continuously from a process air stream. This may be done in concert with the lithium chloride water vapor removal, reducing the need for outside air. 
     Carbon dioxide from a process air stream may be absorbed by a solution of an amine, with the amine solution subsequently being regenerated by heating, and the resulting desorbed carbon dioxide may be rejected to a second gas stream. The concentrated gas stream may subsequently be discharged to the atmosphere or solidified by a combination of compression and low temperature condensation. 
     Amines and other organics may be frequently coated in thin layers but may be found subject to physical losses by carry over or entrainment as vapor or liquid. The dispensing of amines may be accomplished without the creation of microdroplets which may become entrained within the air streams. During an absorption cycle, a parallel portion of excess water vapor of the air may in turn be absorbed by a mixture of aqueous solutions of alkylamines and lithium chloride. It may be advantageous to perform the absorption portion of the cycle at the wet bulb temperature of the atmosphere. Indirect evaporation in summer conditions and indirect free airside cooling in winter conditions may bring a low energy utilization to carbon dioxide scrubbing. Air passing through the absorber may then be returned or supplied to the building, with only a small amount of its original carbon dioxide and water vapor content. 
     For the purposes of regeneration for reuse, the exchanger may be indirectly heated to a temperature at or slightly above 200° F. via hot water or steam. The carbon dioxide, formaldehydes, VOC compounds, and chemically absorbed water contained in the reversibly binding aqueous solutions may be driven off. The warm aqueous solutions of alkylamines may be subsequently cooled by indirect evaporation and process air. A liquid-to-liquid heat exchanger (not depicted) may be used to preheat solution contained within conduit  1668  and pre-cool solution contained within conduit  1670 . The liquid-to-liquid heat exchanger may be made of a material compatible with corrosive salts and strong alkylamine solutions, including, for example, polymers, stainless steel, nickel, titanium, or carbon. 
     System  1690  of the present disclosure may be used to absorb the carbon dioxide and to desorb into a separate gas stream in a higher concentrated form. By this application, carbon dioxide may be rejected from an enclosed environment to the atmosphere, but the resulting concentrated air stream may afford other opportunities and uses. The system  1690  of the present disclosure may help occupants improve their wellness, productivity, and comfort, improve performance of mental and/or physical tasks, increase their alertness, quality of life and pleasure, reduce their drowsiness, and aid in curing and preventing disease by decreasing the percentage of carbon dioxide in the enclosed space to a beneficial and safe level. 
     Formaldehyde is a common indoor pollutant that is an irritant and has been classified as a carcinogen. Adsorption technology may be safe and stable and may remove formaldehyde efficiently but its short life span and low adsorption capacity may limit its indoor application. The system  1690  of the present disclosure may remove unwanted air pollutant molecules via absorption into liquid solvent, reaction with a sorbent or reagent solution, or by inertial or diffusional impaction. 
     System  1690  of the present disclosure may remove inorganic fumes, vapors, and gases (e.g., chromic acid, hydrogen sulfide, ammonia, chlorides, fluorides, and SO 2 ); volatile organic compounds (VOC); and particulate matter (PM), including PM less than or equal to 10 micrometers (μm) in aerodynamic diameter (PM 10 ), PM less than or equal to 2.5 μm in aerodynamic diameter (PM 2.5 ), and hazardous air pollutants (HAP) in particulate form (PM HAP ). 
     Absorption may be used as a raw material and/or product recovery technique in separation and purification of gaseous streams containing high concentrations of VOC, especially water-soluble compounds, such as methanol, ethanol, isopropanol, butanol, acetone, and formaldehyde. Hydrophobic VOC can be absorbed using an amphiphilic block copolymer dissolved in water. However, as an emission control technique, it may be more commonly employed for controlling inorganic gases than for VOC. When using absorption as the primary control technique for organic vapors, the spent solvent must be easily regenerated or disposed of in an environmentally acceptable manner per Environmental Protection Agency regulations. 
     The suitability of gas absorption as a pollution control method may generally be dependent on the following factors: (1) availability of suitable solvent; (2) required removal efficiency; (3) pollutant concentration in the inlet vapor; (4) capacity required for handling waste gas; and (5) recovery value of the pollutant(s) or the disposal cost of the unrecoverable solvent. 
     Air handling and scrubbing system  1690  may maintain the indoor air quality at an acceptable level within various enclosed spaces by providing comfortable and healthy conditions and cleanliness. HVAC systems may constitute a significant part of a building&#39;s energy budget, particularly in extreme climates. System  1690  of the present disclosure may provide a practical, modular, and scalable system for removing contaminants from the circulating air in an HVAC system, utilizing regenerable absorbent materials and a continuous absorption-desorption cycle being isothermally cooled and isothermally heated, respectively. 
     Treating large volumes of indoor air having low concentrations of organic and inorganic contaminants may require bringing large volumes of absorbent materials into intimate contact with large volumes of circulating indoor air. It may also be advantageous to use air treatment systems, such as air handling unit  100 , that are scalable and relatively compact in size so as to be readily installed in existing buildings by human operators. Furthermore, different buildings may have different air flow requirements and contaminant levels. To efficiently and practically manufacture and deploy air treatment systems adaptable to a wide variety of buildings, it may be advantageous to provide a modular air treatment system design, based on one size that is easily manufactured and combined to provide scalable solutions for different building sizes and air quality requirements. It may also be advantageous to make air treatment systems that are easily integrated with existing HVAC systems rather than replacing existing infrastructure. 
     A building according to the present disclosure may include, without limitation, an office building, residential building, store, mall, hotel, hospital, restaurant, airport, train station and/or school. A vehicle according to the present disclosure may include, without limitation, an automobile, ship, train, plane, or submarine. 
     Scrubbing system  1690  of the present disclosure may be configured to remove unwanted gases, vapors, and contamination, including, without limitation, volatile organic compounds (VOC) and CO2 produced within human-occupied space by human occupants. Other contaminants that may be removed include without limitation carbon monoxide, sulfur oxides and/or nitrous oxides. 
     With reference to  FIG. 15 k   , multiple function air handling and scrubbing system  1690  may be configured to remove carbon dioxide. System  1690  may comprise first carbon dioxide scrubbing module  1691  and second regeneration module  1692 . First and second modules  1691 ,  1692  may embody exchange module  1660  described in  FIGS. 15 i    and  15   j.    
     First air stream  1680 , which may be, for example, process supply air to a building, may pass through first carbon dioxide scrubbing module  1691  and carbon dioxide may be removed and cooled by first liquid  1626 , which may be, for example, an aqueous solution of alkylamines, and may, in turn, be cooled by second liquid  1628 , which may be, for example, water evaporating into a second air stream  1681 , such as, for example, atmospheric air, passed through first carbon dioxide scrubbing module  1691 . 
     With respect to the second regeneration module  1692 , first air stream  1680 , which may be, for example, atmospheric air, may pass through module  1692 . First liquid  1626 , which may be a carbon dioxide saturated alkylamine, may release carbon dioxide, while air stream  1681  may be, for example, steam saturated running in a closed loop (not shown), and may simultaneously heat the saturated alkylamine. 
     First carbon dioxide scrubbing module  1691  may be connected to second regeneration module  1692  via conduit pipes and a liquid pump may facilitate flow of alkylamine between the modules  1691 ,  1692 . First liquid drain conduit  1616  on first exchange module  1691  may collect saturated alkylamine. The saturated alkylamine may be pumped to second regeneration module  1692  via saturated alkylamine pump  1664  powered by motor  1665 . Saturated alkylamine may be delivered to second regeneration module  1692  via saturated alkylamine conduit  1668 . 
     First liquid drain conduit  1616  on second exchange module  1692  may collect regenerated alkylamine. The regenerated alkylamine may be pumped to first exchange module  1691  via regenerated alkylamine pump  1666  powered by motor  1667 . The regenerated alkylamine may be delivered to first exchange module  1691  via a regenerated alkylamine conduit  1670 . Second liquid drain conduits  1618  connected to each of the first and second exchange modules  1691 ,  1692  may collect excess water that may not be evaporated, and the excess water may be returned back to liquid distribution headers  1632 ,  1634  of modules  1691 ,  1692 . 
       FIG. 15 l    illustrates a psychrometric chart corresponding to the operation of the evaporative cooling and/or steam regenerating liquid desiccant air conditioner module of the present disclosure.  FIG. 15 l    depicts a first airstream of outside air (OA) to supply air (SA), a second airstream of return air (RA) to exhaust air (EA), and a third regeneration airstream. The first airstream may traverse points C and D, the second airstream may traverse points A and B, and the third airstream may traverse points C, E, and F.  FIG. 15 a    charts the estimated temperatures and humidity levels for the first, second, and third airstreams as they traverse these points. 
     The first airstream and the second airstream may flow through the heat exchanger in a counterflow orientation. Point A may represent a summer return air condition from a conditioned space. The second airstream may enter an entry port of the heat exchanger at point A of  FIG. 15L  and may flow through the heat exchanger to point B. The second airstream may be exposed to a liquid desiccant solution which may flows along the membrane surfaces of the heat exchanger. The liquid desiccant may act to dehumidify the second airstream. The first airstream may flow simultaneously through the heat exchanger from point C to point D in a counterflow orientation in relation to the second airstream. As the second airstream flows through the heat exchanger from point A to point B and the first airstream flows through the heat exchanger from point C to point D, heat content may transfer from the second airstream to the first airstream. The third regeneration airstream may be heated by a heat source from point C to point E and may draw moisture from liquid desiccant solution from point E to point F which may flow along the membrane surfaces of the heat exchanger. Drawing moisture from the liquid desiccant solution from point E to point F may re-concentrate the liquid desiccant solution. 
     The exchanger  213  of the present disclosure may be used in various types of heat and water vapor exchangers. For example, as mentioned above, exchanger  213  can be used in energy recovery ventilators for transferring heat and water vapor between air streams entering and exiting a building. This may be accomplished by flowing the streams on opposite sides of the counter-pleated exchanger  213 . Membrane  1206  of exchanger  213  may allow the heat and moisture to transfer from one stream to the other while substantially preventing the air streams from mixing or crossing over. Other potential applications for exchanger  213  may include, but are not limited to, the applications described in U.S. application Ser. No. 13/426,565, which is incorporated herein by reference. 
     Rotationally-Molded Hollow Shells 
       FIGS. 16 a -16 d    illustrates a perspective view of a rotationally molded shell  1700  according to the present disclosure. Shell  1700  may comprise interstitial space  1701  filled with insulating material  1702 . Insulating material  1702  may include powdered metal oxides, powdered inorganic oxides, silica powder, fumed silica powder, and/or aerogel powder. Powdered ceramic may be superior to conventional urethane foams, as foams degrade in their thermal performance as the inert gases trapped inside their pore structure leak out over time. Powdered ceramic may provide insulation and prevent heat build-up. 
     Walls of shell  1700  may be rotationally molded (rotomolded). Shell  1700  may be formed of cross-linked or non-cross-linked polyolefins, including, for example, polyethylene (PE), polypropylene, filled polypropylene, polybutylene (PB), cross-linked polyethyene (PEX), polyam ides, polysuphones, poly-ether ketones, polyethylene terephthalate (PET), and mixtures thereof. Walls of rotationally-molded shell  1700  may be furthermore modified with additives, fillers, and reinforcements, including, for example, boron fibers, carbon fibers, glass fibers, Kevlar fibers, silanes, titanates, chlorides, bromines, phosphorous, metallic salts, calcium carbonate, silicas, clays, chromates, carbon black, pigments, or combinations thereof. In certain embodiments, the outer and inner walls of shell  1700  may be formed of a non-brittle thermoplastic, such as polypropylene. The polypropylene may also be carbon-impregnated to provide UV protection and heat deflection. 
     In some embodiments, interstitial space  1701  of shell  1700  may be under a vacuum to provide further insulation and may be filled with unmolded, loose, powdery insulating material  1702 . Thermal conductivity of less than 0.010 W/(m*K) may be measured, and preferably less than 0.004 W/(m*K), under vacuum. 
     In certain embodiments, filled shell  1700  may be used to make building components, such as, for example, wall panel  1703 . A typical wall using two-by-four wall studs may be 3.5 inches thick, with an inside of ½ inch thick drywall and ½ inch thick exterior plywood and/or siding, for a total wall thickness of 4.5 inches. Assuming four inches of modest vacuum insulation, wall panel  1703  formed from filled shell  1700  may provide an R value of 100 or greater. 
     In other embodiments, the air handling module, the energy recovery module, and the dehumidification module of the present disclosure may be insulated by forming the components of the modules with the filled rotationally molded shell  1700 . Components of the modules, including, for example, the exchanger housing, the air director, manifolds, fan boxes, access panels, and electrical access panels, may be rotationally molded (rotomolded). The rotationally-molded components may include outer wall, inner wall, and hollow interstitial space between the outer and inner walls. The hollow interstitial space may be filled with appropriate insulation material including, for example, a powdered ceramic, such as fumed silica or preferably aerogel powder. The rotomolded components of the modules may be lighter than existing components of air handling and conditioning systems. As a result, the modules of the present disclosure may readily be moved and transported by an operator without employing heavy machinery and the like. 
     Shells  1700  may also be useful in construction of building walls, building basements, building roofs, airplane shells, automobile enclosures, HVAC air handling modules, energy recovery ventilators, and air ducts. It may be advantageous to have molded features allowing for a plurality of interconnected hollow shells to snap or otherwise structurally seal in these applications. 
     As shown in  FIGS. 16 a -16 d   , wall panel  1703  may be formed of rotationally molded shell  1700  having interstitial space  1701  filled with insulating material  1702 . Wall panel  1703  may include an electrical wire conduit, a communication bus conduit, electrical outlets, water piping, hot water piping, window wells, skylight wells, shelves, structural supports, and wall hangers. 
     Wall panel  1703  may comprise inside surface  1704 , outside surface  1705 , interconnecting left side  1706 , interconnecting right side  1707 , interconnecting top side  1708 , and interconnecting bottom side  1709 . In some embodiments, interstitial space  1701  may be under a vacuum while insulating material  1702  may provide the compressive structure necessary to keep inside surface  1704  and outside surface  1705  from collapsing inward. Wall panel  1703  may be manufactured under a vacuum, whereby shell  1700  may be free of all defects and manufactured from thermoplastics that inhibit molecules to pass or leak in. The interstitial space  1701  of wall panel  1703  may be linked, through a plurality of sealed, interconnected ports to a centralized vacuum generator. Furthermore, a partial vacuum may be maintained throughout the lifetime of the building structure during which age, wear, and tear may generate microfractures or penetrations into wall panel  1703  reducing or eliminating the original partial vacuum. 
     A partial vacuum, controlled by the centralized vacuum generator, may be adjusted given the temperature gradient between the inside and outside of the building. During times of extreme cold or extreme heat, a greater vacuum may be desirable while during times of more moderator environmental temperatures a lesser vacuum or no vacuum may be desirable. The ability to maintain and/or change the thermal resistance of structure&#39;s wall may be advantageous by optimizing the energy characteristics at a specific site with specific environmental conditions. 
     In certain embodiments, wall panel  1703  may include hydronic distribution and collection system  1710 . The hydronic distribution and collection system  1710  may employ a plurality of interconnecting ports on horizontal, vertical, and sides of wall panel  1703 . The ports may serve as interchangeable attachment points for a plurality of structures, including, for example, a hot water pipe, a potable water pipe, a refrigerant line pipe, a sewer/septic pipe, a liquid desiccant pipe, a chilled water conduit, a steam pipe, vacuum lines, and/or other fluidly connected hydronic components found within a commercial, residential, or industrial building. Furthermore, the port may be threaded and/or incorporate gasketed seals. The ports may also readily attach and detach to a plurality of appliances, including, for example, sinks, bathtubs, toilets, washers, dishwashers, boilers, condensers, and evaporators. 
     Hydronic distribution and collection system  1710  may be positioned along a bottom portion of wall panel  1703  and may include a sewer conduit with at least two ports disposed on each end and at least one port therebetween. For example, first sewer water edge port  1717  may be positioned on left side  1706 , second sewer water edge port  1717  may be positioned on the right side  1707 , and third inside port  1719  may be positioned on inside surface  1704 . A sewer water pipe  1718  may be freely disposed of within sewer conduit and may allow for the proper pipe angle to facilitate gravitational draining. 
     Wall panel  1703  may include hot water pipe  1713  comprising interconnecting first and second edge ports  1712  and inside port. Wall panel  1703  may also include potable water pipe  1715  including interconnecting first and second edge ports  1714  and inside port  1716 . These ports may be threaded and/or may incorporate gasketed seals between a plurality of wall panels  1703  to maintain seals between liquids, pressure, and vacuum conditions. In some embodiments, the ports may be threaded in accordance with British Standard Parallel Pipe (BSPP) standards with integrated sealing washers to ensure international compatibility with National Taper Pipe (NPT), American Standard Straight Pipe for Mechanical Joints (NPSM), American Standard Straight Pipe (NPS), and British Standard Tapered Pipe (BSTP) standards. 
     The present disclosure contemplates any suitable number of pipes and ports for wall panel  1703 , and ports may be arranged on any suitable location of the wall panel  1703 , including, for example, lateral, upper, and lower surfaces. The conduit and hermetically sealed port connections of the hydronic distribution and collection system  1710  may additionally serve as the means of evacuating the interstitial space  1701  of wall panel  1703  linked to a centralized vacuum generator. 
     In certain embodiments, wall panel  1703  may include communication bus  1720 . Communication bus  1720  may employ a plurality of interconnecting ports on horizontal, vertical, and sides of wall panel  1703 . Interconnecting ports may serve as attachment points for a plurality of communication wire types, including, for example, electrical wire, communication bus wire, sensor probe wire, wire harness connectors, TV cable, DSL/internet cable, telephone cable, security/camera wire, and combinations thereof. Communication bus  1720  may include communication bus conduit  1723  including interconnecting first and second edge ports  1722  and inside port  1724 . 
     The present disclosure contemplates any suitable number of bus bars and bus ports for wall panel  1703 , and ports may be arranged on any suitable location of wall panel  1703 , including, for example, lateral, upper, and lower surfaces. The conduit and hermetically sealed port connections of communication bus  1720  may additionally serve as the means of evacuating interstitial space  1701  of wall panel  1703  linked to a centralized vacuum generator. 
     In some embodiments, wall panel  1703  may include electrical power distribution  1730 . Electrical power distribution  1730  may employ a plurality of interconnecting ports on horizontal, vertical, and sides of wall panel  1703 . Interconnecting ports may serve as attachment points for a plurality of electrical wire types, including, for example, AC power wires, DC power wires, grounding wires, light switches, appliance outlets, and electrical wire harness connectors. Electrical power distribution  1730  may include a receptacle conduit  1733  including interconnecting first and second edge ports  1732  and inside port  1734 . Electrical power distribution  1730  may also include lighting conduit  1736  comprising interconnecting first and second edge ports  1735  and inside port  1737 . 
     The present disclosure contemplates any suitable number of power conduits and ports for wall panel  1703 , and ports may be arranged on any suitable location of wall panel  1703 , including, for example, lateral, upper, and lower surfaces. The conduit and hermetically sealed port connections of electrical power distribution system  1730  may additionally serve as the means of evacuating the interstitial space  1701  of wall panel  1703  linked to a centralized vacuum generator. 
     In certain embodiments, wall panel  1703  may include an air distribution system  1740 . Air distribution system  1740  may employ a plurality of interconnecting ports having ducts. The interconnecting ports of air distribution system  1740  may be positioned on horizontal, vertical, and sides of wall panel  1703 . The interconnecting ports serve as attachment points for a plurality of structures, including, for example, diffuser vents, return vents, supply and exhaust fans, metal ducts, access panels, and/or other fluidly connected components of an HVAC system. A first air duct  1761  may have at least two duct ports  1742  disposed on each end of air duct  1761  and at least one inside port  1743  therebetween. Second air duct  1762  may have at least two duct ports  1744  disposed on each end of air duct  1762  and at least one inside port  1745  therebetween. A third air duct  1763  may have at least two duct ports  1746  disposed on each end of air duct  1763  and at least one inside port  1747  therebetween. 
     An evaporative liquid desiccant air conditioner module  1600 ,  1660  may be positioned between first and second air ducts  1761 ,  1762  and may connect first air duct  1761  with second air duct  1762  to provide sensible cooling, dehumidification, heating, humidification, and ventilation to an enclosure, such as a building. Air conditioner module  1600 ,  1660  may be connected to and powered via first fluid port  1748  and second fluid port  1749 . 
     By way of example, a first portion of air duct  1761  may carry outside air through air conditioner module  1600 ,  1660 , and first portion of air duct  1762  may deliver conditioned outside air to a space through inside air duct port  1745 . A second portion of air duct  1761  may draw return air through inside air duct port  1743  and through air conditioner module  1600 , and stale air may be exhausted through second portion of air duct  1762 . First fluid port  1748  may flow a strong lithium chloride salt to dry outside air while second fluid port  1749  may flow water for indirect evaporative cooling of the outside air using return air. 
     Although not shown, one or more air moving systems may be coupled via the hermetically sealed ducts to a centralized system. Additionally, natural ventilation and natural buoyancy of air may provide the means of delivering conditioned outside air into a building or enclosure. In some embodiments, the size of air conditioner module  1600 ,  1660  may encompass most, if not all, of the interstitial space of wall panel  1703  depending on specific site requirements. The present disclosure contemplates any suitable number of air ducts and ports for wall panel  1703 , and ports may be arranged on any suitable location of wall panel  1703 , including, for example, lateral, upper, and lower surfaces. The ducts and hermetically sealed port connections of air distribution system  1741  may additionally serve as the means of evacuating interstitial space  1701  of wall panel  1703  linked to a centralized vacuum generator. 
     In certain embodiments, wall panel  1703  may comprise structural connector  1750  including a plurality of interconnecting ports and tabs on horizontal and vertical sides of said wall panel. The interconnecting ports and tabs may align and attach a plurality of adjacent wall panels  1703  and may include, for example, structural anchor bolts, module interconnectivity clamps, module seals, tongue-and-groove hermetic seals, and combinations thereof. For example, male interconnecting tabs  1752  on interconnecting left side  1706  may be structurally and hermetically sealed to female interconnecting tabs  1753  on right side  1707 . A plurality of structural pin holes  1754  may structurally lock wall panels  1703  in place and may keep the panels  1703  from coming loose. These structural pin holes  1754  may be slotted to facilitate expansion and contraction of the panels  1703  given changing environmental conditions. The interconnecting ports and structural tabs of structural connector  1750  may additionally serve as the means of evacuating the interstitial space  1701  of wall panel  1703  linked to a centralized vacuum generator. 
     The present disclosure contemplates any suitable types of interior textures or colors  1771  applied to inside surface  1704  during the molding process. Drywall found in typical building wall construction may be eliminated. Furthermore, surfaces of wall panel  1703 , molded out of polypropylene, for example, may have their surface color changed after manufacturing/installation by using primers specific for low surface energy plastics. 
     As shown in  FIG. 16 c   , a number of components may be installed on wall panel  1703  to create a finished interior look and function. For example, sewer cover plate  1781  may attach over sewer water inside port  1719 . Communications cover plate  1782  may attach over communication bus inside port  1724 . Receptacle cover plate  1783  may attach over receptacle inside port  1734 . Lighting cover plate  1784  may attach over lighting inside port  1737 . First HVAC grill  1785  may attach over first air duct inside port  1743 . Second HVAC grill  1786  may attach over second air duct inside port  1745 . Third HVAC grill  1787  may attach over third air duct inside port  1747 . 
     As shown in  FIG. 16 d   , the present disclosure contemplates any suitable types of exterior textures or colors  1772  to outside surface  1705  of wall panel  1703 . Exterior siding, trim, stucco, and various other elements typically found in exterior building wall construction may be eliminated. Furthermore, surfaces of wall panel  1703 , molded out of polypropylene, for example, may have their surface color changed after manufacturing/installation by using primers specific for low surface energy plastics. 
     A first air duct outside port  1764  may connect to first air duct  1761  with first air duct port  1742  on ends of first air duct  1761 . A second air duct outside port  1765  may connect to second air duct  1762  with second air duct port  1744  on ends of second air duct  1744 . The present disclosure contemplates any suitable number of exterior components to facilitate the purpose and intent of specific building types or enclosures. 
     As shown in  FIG. 16 e   , the present disclosure contemplates the use of rotationally molded hollow shells  1700  on all interior and exterior surfaces of building enclosures using interlocking structural tabs and a plurality of interconnecting ports. For example, a plurality of basement wall panels  1797  may attach horizontally to a plurality of three-way wall connectors  1790 . Wall panel  1703  may be positioned in a substantially horizontal orientation to form a roof of a commercial, residential, or industrial building. In such a configuration the roof may be formed of the lightweight and durable panel  1703  and may accommodate all types of weather conditions, including hail. Textures, colors, and port locations may be selected to provide underfloor air distribution and underfloor utility distribution. 
     A plurality of floor panels  1794  may attach horizontally to a plurality of three-way floor connectors  1792 . A plurality of wall panels  1703  may attach vertically to a plurality of three-way roof connectors  1793 . A plurality of interior wall panels  1795  may attach to a plurality of three-way wall connectors  1790 . A plurality of roof panels  1796  may connect vertically to a plurality of three-way roof connectors  1793 . All interconnecting ports may be preserved through the transition between various types of rotationally molded hollow shells  1700 . Structural additives, such as, for example, carbon fiber, may be added to subterranean basement panels  1797  or roof panels  1796  to accommodate high structural loading. Numerous modifications and variations in the combination of these wall panel types may be readily apparent to persons skilled in the art and may be combined to form a wide range of building shapes and sizes. 
       FIG. 16 f    illustrates an exterior perspective view of building system  1725  comprising a plurality of rotationally molded hollow shells  1700  having interstitial space  1701  filled with insulating material  1702 . As shown in  FIG. 16 f   , a ground line  1799  provides reference to molded hollow shells  1700  being particularly advantageous in their use in subterranean environments. A corner wall connector  1791  may attach to a plurality of wall panels  1703  to form an exterior corner. The present disclosure contemplates any suitable types of exterior structures, such as, for example, windows, doors, intake vents, basement window wells, and exhaust vents. A window panel  1798  may attach to a plurality of wall panels  1703 . Numerous modifications and variations in the combination of these wall panel types may be readily apparent to persons skilled in the art and may be combined to form a wide range of building shapes and sizes. 
     As shown in  FIG. 16 g   , three-way wall connector  1790  may be formed from a rotationally molded hollow shell  1700  having interstitial space  1701  filled with insulating material  1702 . Three-way wall connector  1790  may include interconnecting inside surface  1704 , outside surface  1705 , interconnecting left side  1706 , interconnecting right side  1707 , interconnecting top side  1708 , and interconnecting bottom side  1709 . All interconnecting ports may be preserved through the transition between various types of rotationally molded hollow shells  1700  facilitated by three-way wall connector  1790 . 
     As shown in  FIG. 16 h   , corner wall connector  1791  may be formed from a rotationally molded hollow shell  1700  having interstitial space  1701  filled with insulating material  1702 . Corner wall connector  1791  may include two outside surfaces  1705 , interconnecting left side  1706 , interconnecting right side  1707 , interconnecting top side  1708 , and interconnecting bottom side  1709 . All interconnecting ports may be preserved through the transition between various types of rotationally molded hollow shells  1700  facilitated by corner wall connector  1791 . 
     As shown in  FIG. 16 i   , three-way floor connector  1792  may be formed from a rotationally molded hollow shell  1700  having interstitial space  1701  filled with insulating material  1702 . Three-way floor connector  1792  may include outside surfaces  1705 , interconnecting inside surface  1704 , interconnecting left side  1706 , interconnecting right side  1707 , interconnecting top side  1708 , and interconnecting bottom side  1709 . All interconnecting ports may be preserved through the transition between various types of rotationally molded hollow shells  1700  facilitated by three-way floor connector  1792 . 
     As shown in  FIG. 16 j   , three-way roof connector  1793  be formed from a rotationally molded hollow shell  1700  having interstitial space  1701  filled with insulating material  1702 . Three-way roof connector  1793  may include extended outside surfaces  1705 , interconnecting inside surface  1704 , interconnecting left side  1706 , interconnecting right side  1707 , interconnecting top side  1708 , and interconnecting bottom side  1709 . All interconnecting ports may be preserved through the transition between various types of rotationally molded hollow shells  1700  facilitated by three-way roof connector  1793 . 
     Numerous modifications and variations will readily occur to persons skilled in the art. The present disclosure is not limited to the exact construction and operation illustrated and described. All suitable modifications and equivalents may be resorted to, falling within the scope of the present disclosure.