Patent Publication Number: US-2011061832-A1

Title: Ground-to-air heat pump system

Description:
CROSS REFERENCE TO RELATED APPLICATIONS 
     The present application claims the benefit of U.S. Provisional Patent Application No. 61/243,445, filed Sep. 17, 2009, which is hereby incorporated by reference in its entirety. 
    
    
     FIELD OF THE INVENTION 
     The present application relates generally to energy transfer to or from a living space and/or to heat water. More particularly, but not exclusively, the present application relates to using the ground as a heat source and/or heat sink in a HVAC system to condition the living environment. 
     BACKGROUND 
     In modern buildings heating, ventilating, and air conditioning (“HVAC”) systems are common to maintain the temperature inside the building at a comfortable level. These HVAC systems can be designed in a variety of ways including using the outside air or the Earth as a heat source or heat sink. The technical community recognizes that certain inefficiencies and cost constraints exist in prior art HVAC systems. 
     SUMMARY 
     One embodiment of the present invention includes a unique technique involving heating and/or cooling for buildings and/or water heaters. Other embodiments include unique methods, systems, devices, and apparatus involving heating and/or cooling. Further embodiments, forms, features, aspects, benefits, and advantages of the present application shall become apparent from the description and figures provided herewith. 
    
    
     
       BRIEF DESCRIPTION OF THE DRAWINGS 
       The description herein makes reference to the accompanying drawings wherein like reference numerals refer to like parts throughout the several views, and wherein: 
         FIG. 1  is an illustrative view of one embodiment of a HVAC system operating in a heating mode; 
         FIG. 2  is an illustrative view of another embodiment of a HVAC system operating in a cooling mode; 
         FIG. 3  is a top view of another embodiment of a HVAC system; 
         FIG. 4  is an illustrative view of another embodiment of a HVAC system with a hot water heater; and 
         FIG. 5  is an illustrative view of another embodiment of a HVAC system with a hot water heater. 
         FIGS. 6-13  illustrate further details regarding aspects of the present application. 
     
    
    
     DETAILED DESCRIPTION 
     For purposes of promoting an understanding of the principles of the invention, reference will now be made to the embodiments illustrated in the drawings and specific language will be used to describe the same. It will nevertheless be understood that no limitation of the scope of the invention is thereby intended, such alterations and further modifications in the illustrated device, and such further applications of the principles of the invention as illustrated therein being contemplated as would normally occur to one skilled in the art to which the invention relates. 
       FIG. 1  shows one embodiment of a HVAC system  10 . A heat pump  12  is located in the basement  14  of a building  16 . As seen in  FIG. 1 , the basement  14  is substantially underneath the ground  18 . The building  16  may be a commercial office building, a residential building, or any other type of building. The basement  14  includes concrete walls  20  and a concrete floor  22 ; however, other materials may be used to construct the walls and floors as known to those skilled in the art. The walls  20  are disposed in a conductive heat transfer relationship with the ground  18 . 
     The heat pump  12  includes a heating unit  24  and a conditioning unit  26 . Although the heat pump  12  of  FIG. 1  is shown as two separate units, it is contemplated herein that the heating unit  24  and the conditioning unit  26  could also be in one device such as in one cabinet  28 , as in  FIG. 3 . As recognized by those skilled in the art, heat transfer involves the transfer of energy and includes whether the result increases or decreases temperature. 
     The operation of a heat pump is well known to one of ordinary skill in the art. A typical heat pump includes four stages. In the first stage, a working fluid, such as a refrigerant, is compressed by a compressor into a relatively high pressure, superheated gas. In the second stage, the relatively high pressure superheated gas is condensed by a condenser, which is a heat exchanger. After passing through the condenser, the refrigerant is in a relatively high pressure subcooled liquid form. In the third stage, the refrigerant passes through an expansion valve, which lowers the pressure and raises the temperature of the refrigerant. In the fourth stage, the relatively low pressure superheated gas passes through another heat exchanger, such as coils, called an evaporator in which the refrigerant evaporates into a gas through heat absorption. The cycle is then repeated. 
     A working fluid channel/plenum  30  is formed between an outer wall  32  and an inner wall  34 . In one embodiment, the outer wall  32  is the concrete basement wall  20 . The inner wall  34  may be formed from insulated wall material, drywall, fiberglass board or other suitable material know to one of skill in the art for making interior wall structures. It is also contemplated that the basement walls  32  may be lined with a material as long as the material allows heat/energy to be transferred between wall  32  and the working fluid/air in the channel  30 . In one form of the present application the distance between the outer wall  32  and inner wall  34  is about four ( 4 ) inches. However, in another form of the present application the distance between the outer wall  32  and inner wall  34  may be in a range from about one ( 1 ) inch to about six ( 6 ) inches. However, the present application contemplates other wall spacing unless specifically provided to the contrary. The present application contemplates a variety of types and dimensions associated with inner wall  34  and it one non-limiting form the inner wall  34  is approximately two ( 2 ) inches thick. 
     In one form the channel/plenum  30  defines a substantially sealed environment and in another form the channel/plenum  30  is a sealed environment. Many means to create a sealed environment are contemplated herein and in one form the channel/plenum is sealed on at the top  36  and the bottom  38  using headers  40 , which may be formed from the same or different materials as used to fabricate the inner wall  34 . The headers  40  seal the channel  30  such that air generally cannot enter or escape the channel  30 . An opening  42  in the channel/plenum  30  allows air to flow through the heat pump  12  and back inside the channel  30 . Thus, the air inside the channel  30  flows in a closed loop through the heat pump  12 . As previously discussed, in one embodiment the channel  30  is hermetically sealed. While, in another embodiment, the channel  30  is not hermetically sealed, but it is substantially sealed such that little, if any, air enters or escapes the channel  30 . Keeping the channel  30  sealed maintains the temperature of the air inside the channel  30  near or at the same temperature as the ground  18  and basement wall  20 . It is contemplated that from time-to-time the air inside the channel  30  may be purged either outside or into the basement. 
       FIG. 1  shows one embodiment of a HVAC system  10  operating in a heating mode. In this mode of operation, air from the channel/plenum  30  enters the heating unit  24  through an inlet wall duct  44 . The air then flows over coils  46  in the heating unit  24 . The coils  46  are filled with a refrigerant, which absorbs heat from the air entering from the channel/plenum  30 . After the air flows over the coils  46 , a blower  48  forces the air to return to the channel/plenum  30  through an outlet wall duct  50 . The inlet wall duct  44  and the outlet wall duct  50  do not allow air to escape from or enter into the channel  30 . In one form of the present application a closed system is formed by the channel/plenum  30 , inlet wall duct  44 , outlet wall duct  50  and the heating unit  24 . 
     At a depth of about 1.5 to 3 meters (6 to 10 feet) below the surface, the ground  18  remains at a relatively constant temperature between 45° F. (7° C.) to 73° F. (23° C.). Thus, the heat/energy from the ground  18  will be transferred through the concrete walls  20  to heat the cooled air from the heating unit  24 . As discussed previously, the present application fully contemplates the direction of heat/energy being transferred from the ground  18  to the walls  32  and/or from the walls  32  to the ground  18 . A person of ordinary skill in the art will understand that convective heat transfer is a mechanism for transfer of energy/heat between the working fluid/air within the channel/plenum  30  and the walls  32 . 
     During the heating mode, a refrigerant in a relatively low pressure superheated gas state  52  flows from the coils  46  in the heating unit  24  into a four-way reversing valve  54 . The four-way reversing valve  54  allows the heat pump  12  to operate either in a heating mode or a cooling mode by routing the refrigerant to the proper components of the heat pump  12 . It is contemplated that other valves or devices may be used to allow the heat pump  12  to operate in either a heating mode or a cooling mode as known by those skilled in the art. The four-way reversing valve  54  routes refrigerant into the compressor  59  where the relatively low pressure superheated gas  52  is compressed into a relatively high pressure superheated gas  56 . The four-way reversing valve  54  then routes the refrigerant  56  (in its high pressure superheated gas state) to the coils  58  in a conditioning unit  26 . 
     The conditioning unit  26  receives relatively cool air from a source, such as but not limited to the living space  60  of the building  16  or from external to the building  16 . As the relatively cool air flows over the coils  58 , the refrigerant  56 , in its relatively high pressure superheated gas state, is condensed into a relatively high pressure subcooled liquid  62 . Heat/energy is given off by the refrigerant  56  and is transferred from the refrigerant in the coils  58  to the air, which increases the air&#39;s temperature. The relatively high pressure subcooled liquid  62  refrigerant then flows out of the coils  58  in the conditioning unit  26  and through the check valve  64 . In the heating mode, the coils  58  in the conditioning unit  26  are operating as a condenser. 
     As the relatively high pressure subcooled liquid  62  flows from the conditioning unit  26  into the heating unit  24 , it passes through a thermal expansion valve  66 , metering device, or capillary tubes that allow the relatively high pressure subcooled liquid  62  to expand. The refrigerant then flows into the coils  46  of the heating unit  24 . In the heating unit  24 , as warm air flows over the coils  46 , the refrigerant inside the coils  46  absorbs heat/energy from the warm air and is evaporated into a relatively low pressure superheated gas  52  and the process repeats itself. In the heating mode, the coils  46  in the heating unit  24  are operating as an evaporator. 
     One of ordinary skill in the art will recognize that he relatively high pressure superheated gas  56 , the relatively high pressure subcooled liquid  62 , and the relatively low pressure superheated gas  52  are all different phases of a refrigerant. 
     Turning to the conditioning unit  26  in  FIG. 1 , as the relatively cool air from the living space  60  flows over the coils  58 , the relatively cool air is warmed by heat transferring from the refrigerant in the coils  58 . The warmed air then is returned to the living space  60  by a blower  68  in the conditioning unit  26 . 
     As described above, the air flowing through the plenum/channel  30  is in a closed loop and sealed off from ambient air in the basement  14 , the living space  60 , or from outside  70 . The closed loop maintains the air temperature in the plenum/channel  30  at a more consistent temperature as heat is transferred between the ground  18  the walls  20  and the air inside the channel  30 . 
       FIG. 2  shows the HVAC system  10  operating in a cooling mode. Like reference numerals will be used to designate like elements throughout the figures. When operating in a cooling mode, the heat pump  12  receives air from the channel  30  which passes over coils  46  in the heating unit  24 . Heat is transferred from the refrigerant in the coils  46  to the air as it passes over the coils  46 , thus heating the air. After passing over the coils  46 , the heated air is rejected by a blower  48  to the channel  30 . 
     Once the heated air is in the channel  30 , the basement walls  20  absorb heat/energy from the air and transfer the heat/energy to the ground  18 . As in the heating mode, the basement walls  20  are in geothermal communication with the ground  18 . The operation of the heating unit  24  and conditioning unit  26  is similar to the previous heating mode. However, in the cooling mode, the coils  46  of the heating unit are operating as a condenser and the coils  58  of the conditioning unit  26  are operating as an evaporator. 
     In the cooling mode, the refrigerant, in its relatively high pressure subcooled liquid state  62 , flows out of the coils  46  in the heating unit and through a check valve  72 . The refrigerant then flows into the conditioning unit  26 . In the conditioning unit  26 , the relatively high pressure subcooled liquid  62  flows through a thermal expansion valve  74  which lowers the pressure of the refrigerant. 
     The refrigerant flows through the coils  58  in the conditioning unit  26 . During this time relatively warm air from the living space  60  flows over the coils  58  allowing heat to be transferred from the air to the refrigerant in the coils  58 . The refrigerant then becomes a relatively low pressure superheated gas  52  as it exits the coils  58 . This relatively low pressure superheated gas  52  flows from the conditioning unit  26  into the four-way reversing valve  54  where it is routed to the compressor  59 . 
     The compressor  59  compresses the relatively low pressure superheated gas  52  into a relatively high pressure superheated gas  56  which then flows into the four-way reversing valve  54 . The four-way reversing valve  54  routes the relatively high pressure superheated gas  56  to the coils  46  in the heating unit  24 . As the refrigerant, in its relatively high pressure superheated gas state  56 , flows through the coils  46 , relatively cool air flows over the coils  46  from the channel  30 . This allows heat/energy to be transferred from the refrigerant in the coils  46  to the relatively cool air flowing over the coils  46 . As the refrigerant leaves the coils  46 , the refrigerant is now in the form of a relatively high pressure subcooled liquid  62  and the process repeats itself. In the conditioning unit  26 , after the heat laden air flows over the coils  58  the air temperature is lowered and the cooled air is returned to the living space  60  using a blower  68 . 
       FIG. 3  shows a top plan view of one embodiment of the HVAC system  10 . A heat pump  28  is connected to the inner wall such that air flows into the heat pump  28  from the plenum/channel  30  through an inlet wall duct  44  and exits the heat pump  28  through an outlet wall duct  50 . Although not required,  FIG. 3  shows the air plenum/channel  30  as formed on all four sides of the basement  14 . However, the plenum/channel  30  may be formed on just one or more of the sides of the basement  14 . The efficiency of the system  10  generally increases as more basement wall surface area is utilized define the plenum/channel  30 . This is because the air in the channel  30  is either heated or cooled through thermal convection with the concrete wall  20  and the concrete wall  20  is cooled by thermal conduction with the ground  18 . Headers  40  are positioned vertically near the inlet wall duct  44  and the outlet wall duct  50  of the heat pump  28 . The headers  40  help define the closed loop plenum/channel  30  and prevent air in the channel  30  from flowing out of the channel  30 . More specifically, the headers  40  force the air in plenum/channel  30  to circulate around the entire channel  30  so the air temperature becomes closer to the temperature of the walls  20  and ground  18 . 
     The heat pump  28  includes a blower  48  in order to move air through the heat pump  28  and throughout the channel  30 . Blower  48  is specifically used to provide the necessary motive force to move the air throughout the channel  30 . 
       FIG. 4  shows another embodiment in which a HVAC system  80  includes a hot water heater  82 . In this embodiment, a three-way ball valve  84  allows the heating unit  24  to transfer heat/energy to the hot water tank  82 . It is contemplated that other valves or other mechanical devices may be used in addition to or instead of a three-way ball valve  84  as known by those skilled in the art. 
     The heating unit  24  operates in the same manner as it does in the heating operation mode as described with reference to  FIG. 1 . However, in the embodiments described with reference to  FIG. 4 , the relatively high pressure superheated gas  56  is directed to the hot water tank  82  and not to the conditioning unit  26 . Specifically, the three-way ball valve  84  routes the relatively high pressure superheated gas  56  to the hot water tank  82 . The hot water tank  82  includes has its own heat transfer coils  86  containing refrigerant. Heat/energy is transferred from the refrigerant, in its relatively high pressure superheated gas state  56 , to the water in the tank  82 . The refrigerant then flows from the heat transfer coils  86  within the hot water tank  82  and passes through a check valve  88 . After leaving the hot water tank  82 , the refrigerant is in its relatively high pressure subcooled liquid state  62 . Similar to the operation described with reference to  FIG. 1 , the heat transfer coils  86  in the hot water tank  82  operate as a condenser and the coils  56  of the heating unit  24  operate as an evaporator. After the relatively high pressure subcooled liquid  62  leaves the check valve  88  it flows to the coils  46  in the heating unit where the refrigerant is heated by the air entering through the channel  30 . The process then repeats itself as described above. 
     By using a three-way valve  84  as in the embodiment shown in  FIG. 4 , the heat pump system may operate in three modes: a heating cycle (e.g.,  FIG. 1 ), a cooling cycle (e.g.,  FIG. 2 ), and a hot water heater cycle (e.g.,  FIG. 4 ). During operation, the three-way valve  84  routes the refrigerant to the conditioning unit  26  instead of the hot water tank  82  to allow the conditioning unit  26  to either heat or cool the air before returning it to the living space  60 . When water in the tank  82  needs to be heated, the three-way valve  84  then routes the refrigerant to the hot water tank  82  as described above to heat the water. 
       FIG. 5  shows another embodiment in which water in a hot water tank  90  is heated by a heat pump system  92 . The heat pump  92  is dedicated to the hot water tank  90  and is used only for heating the hot water tank  90 . The other heat pump  12  is used for heating and cooling the living space air. As seen in  FIG. 5 , the heat pump  92  has an inlet wall duct  94  that allows air from the channel  30  to flow into the heat pump  92 . Once in the heat pump  92 , heat/energy from the air is transferred to the water in the tank  90 . The heat pump rejects the air to the channel  30  through the outlet wall duct  96 . The heat pump  92  operates in the same way as the heat pump  12  in  FIGS. 1 and 4  operate. After heat has been transferred from the channel air, the relatively cool air is returned to the channel  30  where the air&#39;s temperature increases as it absorbs heat from the ground  18  through the walls  20  of the basement  14 . 
     The heat pumps described in this application operate as air-to-air heat pumps. This is because the heat pumps absorb heat from the air in the channel  30  and transfer that heat to air in the living space  60 . The concrete basement walls  20  operate as a geothermal heat source and heat sink depending on the mode of operation. In the heating mode, the walls  20  operate as a geothermal heat source because heat from the ground  18  is transferred from the ground  18  through the basement walls  20  by conduction and then to the air in the channel  30  by convection. During the cooling mode, the basement walls  20  are operating as a geothermal heat sink because heat from the air in the channel  30  is transferred by convection to the basement walls  20  and then by conduction to the ground  18  from the basement walls  20 . 
     The valves in this application may be actuated in any manner including by hydraulic, pneumatic, manual, solenoid, or motor. It is contemplated that other valves or other fluid regulation devices may be used in place of the four-way reversing valve  54  or the three-way ball valve  84  as known to those ordinarily skilled in the art. 
     One aspect of the present application contemplates the following: 
     The method of utilizing a masonry or concrete exterior wall of a building as a condensing heat exchange medium in a vapor compression cycle, wherein condensing air circulating in a closed loop flows through condensing coils absorbing heat and across the interior surface of a masonry or concrete wall giving up heat to the wall mass, whereby heat is absorbed by the wall mass and conducted to the wall&#39;s exterior surface in thermal continuity with the earth and absorbed therein. 
     The present application relates to heretofore unknown method of utilizing a masonry or concrete exterior wall of a building as a condensing heat exchange medium in a vapor compression cycle, wherein condensing air circulating in a closed loop flows through condensing coils absorbing heat and across the interior surface of a masonry or concrete wall giving up heat to the wall mass, whereby heat is absorbed by the wall mass and conducted to the wall&#39;s exterior surface in thermal continuity with the earth and absorbed therein. 
     The method provides a relatively constant moderate temperature heat exchange medium wherein the vapor compression cycle operates at lower condensing temperature/pressure reducing compressor motor electrical power consumption. The higher the pressure to which a gas is compressed the more power required by the compressor motor to motivate the gas thereby consuming more energy. 
     Conventional air-cooled refrigeration and air conditioning condensers utilize outdoor ambient air as a heat exchange medium. Although this method has been in use since inception of air-cooled condensers it is nevertheless extraordinarily inefficient. The reason being that in order for there to be an exchange of heat from a condensing unit&#39;s condensing coils to outdoor ambient air there must be a temperature differential, that is, the condensing coils must be at a higher temperature than outdoor ambient air flowing over them, thus, the higher the outdoor ambient air temperature the higher the necessary condensing temperature. The consequence of higher condensing temperature is higher condensing pressure (head pressure) resulting in greater the energy consumption. 
     In one aspect conventional air-cooled condensers are capable of operating within a wide outdoor ambient air temperature span, typically between 70° F. (21° C.) to 110° F. (43° C.). Consider a conventional air-cooled condensing unit (utilizing refrigerant R-410A) operating at 70° F. (21° C.). At 70° F. the corresponding condensing pressure (head pressure) is 201 psig. The same condensing unit operating at 110° F. (43.3° C.), which is the standard design condition, the corresponding condensing pressure is 365 psig. Operating at 201 psig head pressure is more efficient than at 365 psig, in fact 45% more efficient. This is merely one non-limiting example of aspects of a conventional air-cooled condenser. 
     At a depth of about 1.5 to 3 m (6 to 10 feet) the earth remains at a relatively constant temperature between 45° F. (7° C.) to 73° F. (23° C.) which at its worst will provide 70° F. condensing temperature. The method may also be applicable to air-source heat pumps provided certain technical issues relating to frosting and icing can be overcome. 
       FIGS. 7 ,  8 ,  9 ,  10 ,  11 ,  12 , and  13  illustrate one embodiment of the present application. 
       FIG. 6  illustrates one form of a conventional open-air condensing unit enclosure wherein the condensing fan draws in air through open air condensing inlets ( 200 ) across condensing coils discharging heat laden air from discharge outlet ( 300 ) to open atmosphere. 
       FIG. 7  illustrates one form of a closed loop condensing unit ( 400 ) wherein the condensing inlets ( 200 ) and discharge outlet ( 300 ) of conventional condensing enclosure ( 100 ) are adapted to include air inlet plenum ( 500 ) and air discharge plenum ( 600 ) forming a closed loop enclosure. 
       FIG. 8  is cutaway view of one form of a typical basement wall illustrating elements comprising one form of an enclosed wall surface heat exchange means. The view includes a detailed magnified view showing basement wall ( 110 ) inner wall surface ( 1000 ) top and bottom caps ( 170 ) metallic air-to-wall heat sink means ( 210 ) and air flow space ( 140 ). Also shown is the non-insulated exterior wall surface ( 200 ) in direct contact with ground ( 220 ) substantially below ground surface ( 230 ). The non-magnified view shows upper and lower air flow chambers paths ( 180   a ) and ( 180   b ) separated by partition ( 150 ). This is a non-limiting example of aspects contemplated by the present application. 
       FIG. 9  is a cross-sectional view of one form of a typical basement illustrating a section of wall with a wall surface mounted heat exchange enclosure ( 800 ) attached. The view shows enclosed wall surface mounted heat exchange enclosure air inlet port ( 700 ) and air outlet port ( 900 ). Dotted line represents said partition ( 150 ) as shown in  FIG. 8 . Open area ( 190 ) in partition ( 150 ) provides unencumbered air flow path ( 160 ) between upper and lower air flow chambers ( 180   a ) and ( 180   b ). 
       FIG. 10  is a cross-sectional view of one form of a typical basement illustrating a section of wall with said wall surface mounted heat exchange enclosure ( 800 ) attached to said wall surface ( 100 ) and further showing said closed loop condensing unit ( 400 ) air inlet plenum ( 500 ) connected to said outlet port ( 700 ) and air discharge plenum ( 600 ) connected to said air inlet port ( 900 ) of said enclosed wall surface heat exchanger means ( 800 ). 
       FIG. 11  in view “B” shows interior of wall surface mounted heat exchange enclosure ( 800 ) without metallic air-to-wall heat sink means ( 210 ). 
       FIG. 11  in view “C” shows exterior of wall surface mounted heat exchange enclosure ( 800 ). 
       FIG. 12  in view “D” shows interior of wall surface mounted heat exchange enclosure ( 800 ) with metallic air-to-wall heat sink means ( 210 ) showing cutaway view ( 240 ). 
     Referring to  FIGS. 6 ,  7 ,  8 ,  9 ,  10 ,  11 ,  12 , and  13  the present application comprises, among other things, two elements, a closed-loop condensing unit  400  and a wall surface mounted heat exchange enclosure  800 . Condensing  400  is relatively mechanically identical to conventional condensing  100  with the exception of air flow method, wherein conventional condensing  100  is of open-air circulation and condensing  400  is closed-loop air circulation. Said closed loop comprising condensing unit  400 , air inlet plenum  500  and air discharge plenum  600  wherein, air inlet plenum  500  connects to outlet port  700  of chamber  180   a , and air discharge plenum  600  connecting to air inlet port  900  of chamber  180   b.    
     Wall surface mounted heat exchange enclosure  800  comprises elements  120 ,  150 ,  170 ,  210  and space  140 . Element  120  is a substantially rigid insulation board or similar material forming the outer wall surface of said wall surface mounted heat exchange enclosure  800 . Element  170  and  170   a  is constructed of sheet metal, or equivalent material, formed to provide a top, bottom and end cap, wherein in combination with element  120  and wall surface  1000  form a substantially air tight space  140 , air space  140  depth about 1 to 2 inches. Element  210  is a metallic material formed to function as a thermal heat sink to promote efficient heat transfer between air circulating through air space  140  and in thermal continuity contact with wall surface  100 . Wall surface mounted heat exchange enclosure  800  air space  140  being further subdivided top to bottom by partition  150  into upper air flow chamber  180   a  and lower air flow chamber  180   b  said partition  150  being open at end  190  to allow air flow to crossover from said upper chamber  180   a  to lower chamber  180   b  as depicted by arrow  160 . 
     Referring to  FIGS. 8 and 10  in operation condensing  400  discharges heat laden air through plenum  600  into air inlet port  900  of wall surface mounted heat exchange enclosure  800 . As said heat laded air flows through upper air flow chamber  180   a  said heat laden air impinges wall surface  1000  and metallic heat sink means  210  in thermal continuity with both the air and wall surface  1000 , wherein at least a portion of the heat is absorbed from said heat laden air by wall  110  and conducted to wall surface  2000  in thermal continuity with earth  220  and absorbed therein by means of thermal conductivity. Said partially cooled heat laden air flows through opening  190  of partition  150  into lower air chamber  180   b  wherein as the air impinges wall surface  1000  and metallic heat sink means  210  wherein the remaining heat is absorbed. Exiting port  900  the air flows into plenum  600  and across condensing coils of condensing  400  absorbing heat of condensation from said condensing coils for another pass through wall surface mounted heat exchange enclosure  800  wherein air circulation continues for duration of the cooling cycle. 
     The required surface area of wall  1000  per unit of cooling capacity is calculated based on the thermal conductivity of concrete and earth (ground). Thermal Conductivity is the specific travel rate that heat moves through a material. The travel rate is dependent upon the material itself. Some materials allow heat to move quickly through them while others very slowly. When heat is applied to a portion of a material, that heat will move through the material. The composition of the atoms of that material will determine the rate of travel. For instance, heat moves very quickly through a metal spoon. Placing one end of the spoon in boiling water will make the entire spoon hot very quickly. Additionally, according to the Second Law of Thermodynamics, when two objects of different temperature contact one another there is an exchange of thermal energy. This exchange is known as heat of conduction, wherein heat flows from the warmer object into the cooler object. 
     The thermal energy of an object is a measure of the speed of the object&#39;s particles. When two objects of different temperatures come into contact with one another, the faster moving particles collide with the slower moving particles, and energy is exchanged. The faster moving particles give up some energy and therefore slow down and the slower moving particles gain some energy and therefore speed up. This process, known as heat conduction, continues until temperature equilibrium is reached. This equilibrium temperature must be somewhere in between the two objects&#39; original temperatures. Therefore, the warmer object cools and the cooler object warms. The thermal current is directly proportional to a material&#39;s coefficient of thermal conductivity. 
     The Coefficient of Thermal Conductivity of concrete stated in the ‘Trane Air Conditioning Manual’ is 12 Btu/in/hr/° F. Generally, concrete and the ground have about the same coefficient of thermal conductivity. Thus, at 10° F. delta-T we get 12 Btu/lin/hr/° F./10° F.=120 Btu/ft°/hr wherein thickness factor (in) in the formula is ignored because wall ( 110 ) in contact with the ground ( 220 ) combines to form a heat sink of infinite thickness. Thus, dividing a unit of cooling capacity, i.e. 12,000 Btu/hr by 120 Btu/hr/ft 2  we get 100 ft 2  of required wall surface area ( 1000 ) per ton of capacity. Dividing 100 ft 2  by 7 foot high wall (typical) equals 14.3 linear feet of wall ( 110 ) per ton of cooling capacity. 
     At a depth of about 1.5 to 3 m (6 to 10 feet) the earth remains at a relatively constant temperature between 45° F. (7° C.) to 73° F. (23° C.) for an average of about 59° F. Thus, adding 10° F. delta-T would provide 69° F. air flowing across wall surface mounted heat exchange enclosure ( 800 ). Referring to an R-41OA P/T chart (Pressure/Temperature) we find that 69° F. equates to 200 psig condensing pressure. In contrast, a conventional air-cooled condenser at 110° F. design condensing temperature will be operating at 365 psig. Thus, 200 psig divided by 365 psig equals a significant 45% reduction in compressor load and corresponding reduction in energy consumption. 
     Of course, as outdoor temperature drops the percent of decrease in energy consumption diminishes accordingly until equal with ground temperature where there is no further decrease. However, at outdoor ambient temperatures even a few degrees above ground temperature there is a worthwhile reduction in percent, i.e., per the above example: at 79° F. outdoor ambient temperature the conventional unit condensing pressure would be 234 psig, thus, dividing 200 psig (from above) by 234 psig would still yield a worthwhile 15% reduction in electrical energy. 
     In one embodiment, an apparatus for removing heat of condensation from the discharge air of an air-cooled refrigeration condenser is provided which includes a air-cooled refrigeration condensing unit adapted to include an air inlet plenum and air outlet plenum for connecting to a heat exchange means; and a heat exchange means adapted to include an air-inlet means and air-outlet means for connecting to said air-inlet plenum and air-outlet plenum of said air-cooled refrigeration unit. The heat exchange means may further includes an outer wall means. Furthermore, the outer wall means may be a substantially ridged material. The substantially ridged material may be a substantially insulating material. The heat exchange means may include a top and bottom cover means and side cover means. The top and bottom cover means and side cover means may be substantially ridged material. The heat exchange means may include a heat sink means. The heat sink means may be a metallic material. The heat exchange means may further include a partition dividing the heat exchange means into at least two interconnected parts. The partition may be open at one end. The partition is optional. Another embodiment includes a method of removing heat of condensation from the discharge air of an air-cooled refrigeration condenser. 
     While the invention has been described in connection with what is presently considered to be the most practical and preferred embodiment, it is to be understood that the invention is not to be limited to the disclosed embodiment(s), but on the contrary, is intended to cover various modifications and equivalent arrangements included within the spirit and scope of the appended claims, which scope is to be accorded the broadest interpretation so as to encompass all such modifications and equivalent structures as permitted under the law. Furthermore it should be understood that while the use of the word preferable, preferably, or preferred in the description above indicates that feature so described may be more desirable, it nonetheless may not be necessary and any embodiment lacking the same may be contemplated as within the scope of the invention, that scope being defined by the claims that follow. In reading the claims it is intended that when words such as “a,” “an,” “at least one” and “at least a portion” are used, there is no intention to limit the claim to only one item unless specifically stated to the contrary in the claim. Further, when the language “at least a portion” and/or “a portion” is used the item may include a portion and/or the entire item unless specifically stated to the contrary.