Abstract:
Disclosed is a method and device for a refrigerant-based thermal energy storage and cooling system with integrated multi-mode refrigerant loops. The disclosed embodiments provide a refrigerant-based thermal storage system with increased versatility, reliability, lower cost components, reduced power consumption and ease of installation.

Description:
CROSS REFERENCE TO RELATED APPLICATION 
       [0001]    This application is based upon and claims the benefit of U.S. provisional application No. 61/470,841, entitled “Refrigerant Circuit with Integrated Multi-Mode Thermal Energy Storage,” filed Apr. 1, 2011 and the entire disclosures of which is hereby specifically incorporated by reference for all that it discloses and teaches. 
     
    
     BACKGROUND OF THE INVENTION 
       [0002]    With the increasing demands on peak demand power consumption, Thermal Energy Storage (TES) has been utilized to shift air conditioning power loads to off-peak times and rates. A need exists not only for load shifting from peak to off-peak periods, but also for increases in air conditioning unit capacity and efficiency. Current air conditioning units having energy storage systems have had limited success due to several deficiencies, including reliance on water chillers that are practical only in large commercial buildings and have difficulty achieving high-efficiency. 
         [0003]    In order to commercialize advantages of thermal energy storage in large and small commercial buildings, thermal energy storage systems must have minimal manufacturing costs, maintain maximum efficiency under varying operating conditions, have minimal implementation and operation impact and be suitable for multiple refrigeration or air conditioning applications. 
         [0004]    Systems for providing stored thermal energy have been previously contemplated in U.S. Pat. No. 4,735,064, U.S. Pat. No. 5,225,526, both issued to Harry Fischer, U.S. Pat. No. 5,647,225 issued to Fischer et al., U.S. Pat. No. 7,162,878 issued to Narayanamurthy et al., U.S. Pat. No. 7,854,129 issued to Narayanamurthy, U.S. Pat. No. 7,503,185 issued to Narayanamurthy et al., U.S. Pat. No. 7,827,807 issued to Narayanamurthy et al., U.S. Pat. No. 7,363,772 issued to Narayanamurthy, U.S. Pat. No. 7,793,515 issued to Narayanamurthy, U.S. patent application Ser. No. 11/837,356 filed Aug. 10, 2007 by Narayanamurthy et al., application Ser. No. 12/324,369 filed Nov. 26, 2008 by Narayanamurthy et al., U.S. patent application Ser. No. 12/371,229 filed Feb. 13, 2009 by Narayanamurthy et al., U.S. patent application Ser. No. 12/473,499 filed May 28, 2009 by Narayanamurthy et al., and U.S. patent application Ser. No. 12/335,871 filed Dec. 16, 2008 by Parsonnet et al. All of these patents and applications utilize ice storage to shift air conditioning loads from peak to off-peak electric rates to provide economic justification and are hereby incorporated by reference herein for all they teach and disclose. 
       SUMMARY OF THE INVENTION 
       [0005]    An embodiment of the present invention may therefore comprise: an integrated refrigerant-based thermal energy storage and cooling system comprising: a refrigerant loop containing a refrigerant comprising: a condensing unit, the condensing unit comprising a compressor and a condenser; a thermal energy storage module containing a thermal storage media and a primary heat exchanger that facilitates heat transfer from the refrigerant to the thermal storage media in a charge mode, and the primary heat exchanger that facilitates heat transfer from the thermal storage media to cool the refrigerant in a discharge mode; a storage expansion device connected downstream of the condensing unit and upstream of the thermal energy storage module; an evaporator expansion device connected downstream of the condensing unit and the thermal energy storage module; an evaporator connected downstream of the evaporator expansion device; and, a valve system that facilitates flow of refrigerant to the storage module from the compressor or the condenser or the storage expansion device or the evaporator, the valve system that facilitates flow of refrigerant from the storage module to the compressor or the condenser or the evaporator expansion device. 
         [0006]    An embodiment of the present invention may also comprise: a method of providing cooling with a thermal energy storage and cooling system comprising: during a first time period: compressing and condensing a refrigerant with a compressor and a condenser to create a high-pressure refrigerant; expanding the high-pressure refrigerant to produce expanded refrigerant and provide storage cooling with a thermal energy storage media via a primary heat exchanger, the primary heat exchanger that is constrained within a thermal energy storage module and in thermal communication with the storage media; and, returning the expanded refrigerant to the compressor; during a second time period: compressing and condensing the refrigerant with the compressor and the condenser to create the high-pressure refrigerant; expanding a first portion of the high-pressure refrigerant to produce the first expanded refrigerant and to provide storage cooling with the thermal energy storage media via the primary heat exchanger, the primary heat exchanger that is constrained within the thermal energy storage module and in thermal communication with the storage media; expanding a second portion of the high-pressure refrigerant to provide cooling to an evaporator to produce the second expanded refrigerant; and, returning the first expanded refrigerant and the second expanded refrigerant to the compressor; during a third time period: compressing the refrigerant with the compressor to create hot, high-pressure gas refrigerant; cooling and condensing a first portion of the hot, high-pressure gas refrigerant with the storage cooling to produce warm liquid refrigerant; condensing a second portion of the high-pressure refrigerant with the condenser; mixing the first portion and the second portion and expanding mixture to provide cooling in an evaporator to produce the expanded refrigerant; and, returning the expanded refrigerant to the compressor; during a fourth time period: compressing the refrigerant with the compressor to create the hot, high-pressure gas refrigerant; cooling and condensing the hot, high-pressure gas refrigerant with the storage cooling to produce the warm liquid refrigerant; condensing the warm liquid refrigerant with the condenser to create subcooled refrigerant; expanding the subcooled refrigerant to provide cooling in an evaporator to produce the expanded refrigerant; and, returning the expanded refrigerant to the compressor; during a fifth time period: compressing and condensing the refrigerant with the compressor and the condenser to create the high-pressure refrigerant; subcooling the high-pressure refrigerant with the storage cooling to produce subcooled liquid refrigerant; expanding the subcooled liquid refrigerant to provide cooling in the evaporator to produce the expanded refrigerant; and, returning the expanded refrigerant to the compressor; during a sixth time period: compressing and condensing the refrigerant with the compressor and the condenser to create the high-pressure refrigerant; expanding the high-pressure refrigerant to provide cooling in the evaporator and produce expanded refrigerant; desuperheating the expanded refrigerant with the storage cooling to produce desuperheated refrigerant; and, returning the desuperheated refrigerant to the compressor; compressing and condensing the refrigerant with the compressor and the condenser to create the high-pressure refrigerant; expanding the high-pressure refrigerant to provide cooling in the evaporator and produce expanded refrigerant; superheating the expanded refrigerant with the storage media to produce the superheated refrigerant; and, returning superheated refrigerant to the compressor; during an eighth time period; compressing and condensing the refrigerant with the compressor and the condenser to create the high-pressure refrigerant; expanding the high-pressure refrigerant to provide cooling in the evaporator and produce expanded refrigerant; returning the expanded refrigerant to the compressor. 
     
    
     
       BRIEF DESCRIPTION OF THE DRAWINGS 
         [0007]    In the drawings, 
           [0008]      FIG. 1  schematically illustrates an embodiment of a refrigerant circuit with integrated multi-mode thermal energy storage. 
           [0009]      FIG. 2  is a schematic illustration of the valve conditions for the embodiment of a thermal energy storage refrigerant circuit capable of multiple charging and discharging modes. 
           [0010]      FIG. 3  schematically illustrates a configuration of an embodiment of a thermal energy storage refrigerant circuit with integrated trickle charge loop. 
           [0011]      FIG. 4  schematically illustrates a configuration of an embodiment of a thermal energy storage refrigerant circuit with full capacity charge loop. 
           [0012]      FIG. 5  schematically illustrates a configuration of an embodiment of a thermal energy storage refrigerant circuit with parallel condenser discharge loop. 
           [0013]      FIG. 6  schematically illustrates a configuration of an embodiment of a thermal energy storage refrigerant circuit with hot vapor desuperheater discharge loop. 
           [0014]      FIG. 7  schematically illustrates a configuration of an embodiment of a thermal energy storage refrigerant circuit with warm liquid subcooler discharge loop. 
           [0015]      FIG. 8  schematically illustrates a configuration of an embodiment of a thermal energy storage refrigerant circuit with cold vapor desuperheater discharge loop. 
           [0016]      FIG. 9  schematically illustrates a configuration of an embodiment of a thermal energy storage refrigerant circuit with suction line charge loop. 
       
    
    
     DETAILED DESCRIPTION OF THE INVENTION 
       [0017]    While this invention is susceptible to embodiment in many different forms, it is shown in the drawings, and will be described herein in detail, specific embodiments thereof with the understanding that the present disclosure is to be considered as an exemplification of the principles of the invention and is not to be limited to the specific embodiments described. 
         [0018]      FIG. 1  illustrates an embodiment of a refrigerant circuit with integrated multi-mode thermal energy storage. The embodiments shown may function with or without an accumulator vessel (surge vessel) or URMV  102  (universal refrigerant management vessel), and is depicted in  FIG. 1  with the vessel in place. 
         [0019]    As illustrated in  FIG. 1 , a variety of modes may be utilized in the system shown to provide cooling in various conventional or non-conventional air conditioning/refrigerant applications and utilized with an integrated condenser/compressor/evaporator (e.g., off-the-shelf unit or original equipment manufactured [OEM]) as either a retrofit to an existing system or a completely integrated new install. In this embodiment, three charge modes, four discharge modes and one bypass mode are possible with the system as shown. These modes of charging and discharging the storage module include trickle charge, full-capacity charge, parallel condenser discharge, hot vapor desuperheater discharge, warm liquid subcooler discharge, cold vapor desuperheater discharge and suction line charges. 
         [0020]    The charging modes utilize a compressor  110  to compress cold, low pressure refrigerant gas to hot, high-pressure gas. This refrigerant passes through valve V 1   122  to a condenser  112  which removes much of the heat in the gas and discharges the heat to the atmosphere. The refrigerant leaves the condenser  112  as a warm, high-pressure liquid refrigerant delivered through a high-pressure liquid supply line where a portion of the warm liquid refrigerant is diverted by valve V 3   126  to valve V 4   128 , which directs the diverted refrigerant through the storage expansion device  118 . The storage expansion device  118  reduces the pressure of the warm liquid refrigerant to generate a cold mixed-phase refrigerant, which is directed to the heat exchanger  170  within the storage module  116 . 
         [0021]    This storage expansion device  118  may be a conventional or non-conventional thermal expansion valve, a static orifice, a capillary tube, a mixed-phase regulator and surge vessel (reservoir), or the like. In this mode, the heat exchanger  170  in the storage module  116  acts as an evaporator where the cold mixed-phase refrigerant absorbs heat from the storage media  160  that surrounds the heat exchanger  170  and vaporizes. The liquid refrigerant transfers cooling to thermal energy storage media  160  within the thermal energy storage module  116  (as shown, but not limited by way of example via a primary heat exchanger  170  within an insulated tank). Low-pressure vapor phase refrigerant is then returned to the compressor  110  via valve V 7   134  where it is mixed with the portion of the cold vapor refrigerant returning to compressor  110  via valve V 6   132  from the evaporator  114  that was split at valve V 3   126  and passed through valve V 5   130  and an evaporator expansion device  120 . As with the storage expansion device  118 , evaporator expansion device  120  may be a conventional or non-conventional thermal expansion valve, a static orifice, a capillary tube, a mixed-phase regulator and surge vessel (reservoir), or the like. 
         [0022]    In order to meter the amount of refrigerant that is split by valve V 3   126 , a specialized valve and controller that modulates based on downstream pressures, for example, may be used to split the amount of refrigerant that is diverted to provide immediate cooling through evaporator  114  and the amount diverted to TES for providing cooling capacity, which may be utilized at a later time. Alternatively, the storage media  160  used in the storage module  116  can be selected in order to match the refrigerant evaporating temperature of the storage module  116  to that of the evaporator  114 , effectively matching the pressure drop across the storage expansion device  118  and evaporator expansion device  120  resulting in a self-metering trickle charge configuration. 
         [0023]    The thermal energy storage unit  116  shown in  FIG. 1  may typically comprise an insulated tank that houses the primary heat exchanger  170  surrounded by a storage media  160  (e.g., solid, liquid coolant, eutectic or liquid phase material and/or solid phase material or the like [fluid/ice] depending on the current system mode). The primary heat exchanger  170  may typically further comprise a lower header assembly connected to an upper header assembly with a series of freezing and discharge coils to make a fluid/vapor loop within the insulated tank. Such systems are disclosed in the patents and applications referred to above, which are also incorporated by reference. 
         [0024]    When operating in full-capacity charge mode, the compressor  110  is energized to compress cold, low pressure refrigerant gas to hot, high-pressure gas. This refrigerant passes through valve V 1   122  and to a condenser  112 , which removes much of the heat in the gas and discharges the heat to the atmosphere. The refrigerant leaves the condenser  112  as a warm, high-pressure liquid refrigerant delivered through a high-pressure liquid supply line where the entirety of the warm liquid refrigerant is diverted by valve V 3   126  to valve V 4   128 , which directs the diverted refrigerant through the storage expansion device  118 . Here, as in the previously described trickle charge mode, the storage expansion device  118  reduces the pressure of the warm liquid refrigerant to generate a cold mixed-phase refrigerant. In this mode, the heat exchanger  170  within the storage module  116  also acts as an evaporator where the cold mixed-phase refrigerant absorbs heat from the storage media  160  and vaporizes and transfers cooling to thermal energy storage media  160  within the thermal energy storage module  116 . Low-pressure vapor phase refrigerant is then returned to the compressor  110  via valve V 7   134 . Thus, the entirety of the cooling provided by the compressor  110  and condenser  112  (typical conventional air conditioning or refrigeration unit) is transmitted, in one contemplated embodiment, from the heat exchanger  170  to the surrounding storage media (e.g., liquid phase material that is confined within an insulated tank and may produce a block of solid phase material (ice) surrounding the freezing coils and storing thermal energy in the process). 
         [0025]    In parallel condenser discharge mode, all basic air conditioning/refrigerant AC/R components are active including the compressor  110 , condenser  112 , evaporator expansion device  120 , and the evaporator  114 . In this mode, the compressor  110  is energized to compress cold, low pressure refrigerant gas to hot, high-pressure gas. This refrigerant passes through valve V 1   122  where a portion of the hot, high-pressure gas is diverted by valve V 1   122  to the storage module  116  and heat exchanger  170 , which acts as a condenser where the hot vapor rejects heat to the storage media  160 , reduces temperature, and condenses. This warm liquid refrigerant is then sent to the evaporator expansion device  120  via valve V 5   130  where it is mixed with warm liquid refrigerant exiting the condenser  112  via valve V 3   126 . The mixed warm liquid refrigerant is then expanded with the evaporator expansion device  120  and evaporator  114  to provide load cooling/refrigeration and returns to compressor  110  through valves V 6   132  and V 7   134  to complete the refrigeration loop. 
         [0026]    Utilizing the heat exchanger  170  within the storage module  116  in this mode as a condenser, allows a greater amount of subcooling prior to the expansion process. This is accomplished by rejecting heat to the cold storage media  160  within the storage module  116 , and improving the effectiveness of the condenser  112  by reducing the mass flow of refrigerant through condenser  112 . Ultimately, the increased subcooling results in an efficiency improvement for the system by increasing the refrigeration effect of the evaporator  114 . This increase in efficiency may allow an increased output by the evaporator  114  thereby effectively increasing the capacity of the AC/R system during high demand periods. This may allow a smaller system to be introduced into a new installation or to increase the capacity of an existing retrofit system application. 
         [0027]    In the hot vapor desuperheater discharge mode, all basic AC/R components are active including the compressor  110 , condenser  112 , evaporator expansion device  120 , and the evaporator  114 . In this mode, the compressor  110  is energized to compress cold, low pressure refrigerant gas to hot, high-pressure gas. This refrigerant passes through valve V 1   122  and is directed to the previously charged storage module  116  acting as a hot vapor desuperheater where the hot vapor refrigerant rejects heat to the storage media  160  via the heat exchanger  170  and reduces temperature. The vapor is then directed to the condenser  112  via valve V 2   124  where additional atmospheric heat rejection and condensation occur. The refrigerant leaves the condenser  112  where the entirety of the subcooled refrigerant is diverted by valve V 3   126  to valve V 5   130  where refrigerant is then directed to the evaporator expansion device  120 . The warm liquid refrigerant is expanded and then evaporated in evaporator  114  before being returned to compressor  110  through valves V 6   132  and V 7   134 . 
         [0028]    In this mode, using the storage module  116 , acting as a hot vapor desuperheater, allows a greater amount of subcooling prior to the expansion process. This is accomplished by rejecting heat to the cold storage media  160  within the storage module  116 , and improving the condenser  112  effectiveness by reducing the amount of heat rejection that must occur in the condenser  112  to desuperheat the hot vapor refrigerant. Instead, more of the condenser  112  heat rejection process is used to subcool the warm liquid refrigerant. Ultimately, the increased subcooling results in an efficiency improvement for the system by increasing the refrigeration effect of the evaporator  114 . This increase in efficiency may also allow an increased output by the evaporator  114 , thereby effectively increasing the capacity of the AC/R system during high demand periods. This may allow a smaller system to be introduced into a new installation or to increase the capacity of an existing retrofit system application. 
         [0029]    In the warm liquid subcooler discharge mode, all basic AC/R components are active including the compressor  110 , condenser  112 , evaporator expansion device  120  and the evaporator  114 . In this mode, the compressor  110  is energized to compress cold, low pressure refrigerant gas to hot, high-pressure gas. This refrigerant passes through valve V 1   122  to a condenser  112 , which removes much of the heat in the gas and discharges the heat to the atmosphere. The refrigerant leaves the condenser  112  as a warm, high-pressure liquid refrigerant delivered through a high-pressure liquid supply line where the entirety of the warm liquid refrigerant is diverted by valve V 3   126  to valve V 4   128 , which directs the refrigerant directly to the heat exchanger within the storage module  116 , acting as a warm liquid subcooler, where the warm liquid refrigerant rejects heat and reduces temperature by transferring heat to the previously cooled thermal storage media  160 . 
         [0030]    The cooled liquid refrigerant is then directed to the evaporator expansion device  120  via valve V 5   130 . The subcooled refrigerant is expanded and then evaporated in evaporator  114  before being returned to compressor  110  through valves V 6   132  and V 7   134 . In this mode, using the storage module  116  as a warm liquid subcooler allows a greater amount of subcooling prior to the expansion process by rejecting heat to the cold storage media  160  within the storage module  116 . Ultimately, the increased subcooling results in an efficiency improvement for the system by increasing the refrigeration effect of the evaporator  114 . This increase in efficiency may allow an increased output by the evaporator  114 , thereby effectively increasing the capacity of the AC/R system during high demand periods. This may allow a smaller system to be introduced into a new installation or to increase the capacity of an existing retrofit system application. 
         [0031]    In cold vapor desuperheater discharge mode, all basic AC/R components are active including the compressor  110 , condenser  112 , evaporator expansion device  120 , and the evaporator  114 . In this mode, the compressor  110  is energized to compress cold, low pressure refrigerant gas to hot, high-pressure gas. This refrigerant passes through valve V 1   122  to a condenser  112 , which removes much of the heat in the gas and discharges the heat to the atmosphere. The refrigerant leaves the condenser  112  as a warm, high-pressure liquid refrigerant delivered through a high-pressure liquid supply line where the warm liquid refrigerant is diverted by valve V 3   126  to valve V 5   130  where refrigerant is then directed to the evaporator expansion device  120 . The refrigerant is expanded and then evaporated in evaporator  114  in a conventional manner and the expanded refrigerant is then diverted by valve V 6   132  to the pre-charged storage module  116  acting as a cold vapor desuperheater where the cold vapor refrigerant rejects heat to the storage media  160  and reduces temperature before being returned to compressor  110  through valve V 7   134 . 
         [0032]    In this mode, using the storage module  116  as a cold vapor desuperheater, allows a greater amount of subcooling prior to the expansion process by rejecting heat to the cold storage media  160  within the storage module  116 , and improving the condenser  112  effectiveness by reducing the amount of heat rejection that must occur in the condenser  112  to desuperheat the hot vapor refrigerant. Instead, more of the condenser  112  heat rejection process is used to subcool the warm liquid refrigerant. Ultimately, the increased subcooling results in an efficiency improvement for the system by increasing the refrigeration effect of the evaporator  114 . This increase in efficiency may allow an increased output by the evaporator  114  thereby effectively increasing the capacity of the AC/R system during high demand periods. This may allow a smaller system to be introduced into a new installation or to increase the capacity of an existing retrofit system application. 
         [0033]    In suction line charge mode, all basic AC/R components are active including the compressor  110 , condenser  112 , evaporator expansion device  120 , and the evaporator  114 . In this mode, the compressor  110  is energized to compress cold, low pressure refrigerant gas to hot, high-pressure gas. This refrigerant passes through valve V 1   122  to a condenser  112 , which removes much of the heat in the gas and discharges the heat to the atmosphere. The refrigerant leaves the condenser  112  as a warm, high-pressure liquid refrigerant delivered through a high-pressure liquid supply line where the warm liquid refrigerant is diverted by valve V 3   126  to valve V 5   130  where refrigerant is then directed to the evaporator expansion device  120 . The refrigerant is expanded and then evaporated in evaporator  114  in a conventional manner and the expanded refrigerant is then diverted by valve V 6   132  to the uncharged storage module  116  acting as a cold vapor superheater where residual cooling that remains in the effluent cold vapor refrigerant leaving the evaporator  114 , is transferred to the storage media  160 , and the temperature of the cold vapor refrigerant increases. The superheated vapor refrigerant exits the storage module  116  and returns to compressor  110  through valve V 7   134 . 
         [0034]    In this mode, using the storage module  116  as a cold vapor superheater, allows an amount of charging (cooling) of the thermal storage media  160  prior to compressing the superheated refrigerant. This places more strain on the compressor  110 , but allows an additional mode of charging the storage module while providing conventional cooling with the evaporator  114 . 
         [0035]    An additional loop may be utilized in the embodiment described in  FIG. 1 , which does not utilize TES. A bypass mode  199  may be achieved that acts as a standard AC/R system without utilization of the storage module  116 . In this mode, the compressor  110  is energized to compress cold, low pressure refrigerant gas to hot, high-pressure gas. This refrigerant passes through valve V 1   122  to a condenser  112 , which removes much of the heat in the gas and discharges the heat to the atmosphere. The refrigerant leaves the condenser  112  as a warm, high-pressure liquid refrigerant delivered through a high-pressure liquid supply line where the warm liquid refrigerant is diverted by valve V 3   126  to valve V 5   130  where refrigerant is then directed to the evaporator expansion device  120 . The refrigerant is expanded and then evaporated in evaporator  114  in a conventional manner and the expanded refrigerant is then diverted by valve V 6   132  before being returned to compressor  110  through valve V 7   134 . In this mode, conventional AC/R may be utilized in situations where TES is not needed or desired. 
         [0036]    As illustrated in  FIG. 1 , a variety of modes may be utilized in the system shown to provide cooling in various conventional or non-conventional air conditioning/refrigerant applications. This system may be a single integrated system with all of the above disclosed modes present, or the contemplated system may include various combinations thereof. 
         [0037]      FIG. 2  is a schematic illustration of the valve conditions for the embodiment of a thermal energy storage refrigerant circuit capable of multiple charging modes  180  and discharging modes  190  depicted in  FIG. 1 . As shown in  FIG. 2 , the valve state conditions are depicted for each of the seven valves V 1   122 -V 7   134 . For example, in the trickle charge mode, valve V 1   122  allows flow from the compressor to the condenser and is depicted as condition (=). Valve V 2   124  does not allow flow, or is inconsequential with regard to the flow condition and is depicted with a small box as condition (□). Valve V 3   126  allows metered and proportional flow to both the storage expansion device  118  and the evaporator expansion device  120  and is depicted as condition (         ). Thus, each of the charge mode  180  valve configurations is shown, and in a similar manner the four discharge modes  190  and a bypass mode  199  are schematically illustrated. 
         [0038]      FIG. 3  illustrates an AC/R trickle charge loop. In this particular charging loop, a compressor  110  compresses cold, low pressure refrigerant gas to hot, high-pressure gas. This refrigerant passes to a condenser  112 , which removes much of the heat in the gas and discharges the heat to the atmosphere. The refrigerant leaves the condenser  112  as a warm, high-pressure liquid refrigerant delivered through a high-pressure liquid supply line where a portion of the warm liquid refrigerant is diverted by a valve, which directs the diverted refrigerant through the storage expansion device  118 . The storage expansion device  118  reduces the pressure of the warm liquid refrigerant to generate a cold mixed-phase refrigerant. In this loop, the storage module acts as an evaporator where the cold mixed-phase refrigerant absorbs heat from the storage media  160  and vaporizes. This storage expansion device  118  may be a conventional or non-conventional thermal expansion valve, a static orifice, a capillary tube, a mixed-phase regulator and surge vessel (reservoir), or the like. 
         [0039]    The liquid refrigerant transfers cooling to thermal energy storage media  160  within the thermal energy storage module  116  (shown here as a primary heat exchanger  170  within an insulated tank). Low-pressure vapor phase refrigerant is then returned to the compressor  110  where it is mixed with the portion of the cold vapor refrigerant returning to compressor  110  from the evaporator  114  that was split at the valve and passed through an evaporator expansion device  120 . As with the storage expansion device  118 , evaporator expansion device  120  may be a conventional or non-conventional thermal expansion valve, a static orifice, a capillary tube, a mixed-phase regulator and surge vessel (reservoir), or the like. 
         [0040]    As was described in  FIG. 1 , in order to meter the amount of refrigerant that is split, a specialized valve may be used to meter the amount of refrigerant that is diverted to each branch to provide immediate cooling through evaporator  114 , and to the amount diverted to TES for providing cooling capacity, which may be utilized at a later time (e.g., a valve and controller that modulates based on downstream pressures). Alternatively, the storage media  160  used in the storage module  116  can be selected in order to match the refrigerant evaporating temperature of the storage module  116  to that of the evaporator  114 , effectively matching the pressure drop across the storage expansion device  118  and evaporator expansion device  120  and resulting in a self-metering trickle charge configuration. 
         [0041]    The thermal energy storage unit  116  shown in FIGS.  1  and  3 - 9  may typically comprise an insulated tank that houses the primary heat exchanger  170  surrounded by, for example, solid, liquid coolant, eutectic or liquid phase material and/or solid phase material or the like, (fluid/ice) depending on the current system mode). The primary heat exchanger  170  may typically further comprise a lower header assembly connected to an upper header assembly with a series of freezing and discharge coils to make a fluid/vapor loop within the insulated tank. Such systems are disclosed in the patents and applications referred to above, which are incorporated by reference. 
         [0042]      FIG. 4  illustrates an AC/R full-capacity charge loop. In this particular charging loop, the compressor  110  is energized to compress cold, low pressure refrigerant gas to hot, high-pressure gas. This refrigerant passes to a condenser  112 , which removes much of the heat in the gas and discharges the heat to the atmosphere. The refrigerant leaves the condenser  112  as a warm, high-pressure liquid refrigerant delivered through a high-pressure liquid supply line where the entirety of the warm liquid refrigerant is directed to the storage expansion device  118 . Here as in the previously described trickle charge loop, the storage expansion device  118  reduces the pressure of the warm liquid refrigerant to generate a cold mixed-phase refrigerant. In this mode, the storage module also acts as an evaporator where the cold mixed-phase refrigerant absorbs heat from the storage media  160  and vaporizes and transfers cooling to thermal energy storage media  160  within the thermal energy storage module  116 . Low-pressure vapor phase refrigerant is then returned to the compressor  110 . Thus, the entirety of the cooling provided by the compressor  110  and condenser  112  (typical conventional air conditioning or refrigeration unit) is transmitted, in one contemplated embodiment, from the freezing coils to the surrounding liquid phase material that is confined within an insulated tank and may produce a block of solid phase material (ice) surrounding the freezing coils and storing thermal energy in the process. 
         [0043]      FIG. 5  illustrates an AC/R parallel condenser discharge loop. In this particular discharge loop, the compressor  110  is energized to compress cold, low pressure refrigerant gas to hot, high-pressure gas. This refrigerant passes through a valve where a portion of the hot, high-pressure gas is diverted to the storage module  116 , which acts as a condenser where the hot vapor rejects heat to the storage media  160 , reduces temperature, and condenses. This warm liquid refrigerant is then sent to the evaporator expansion device  120  where it is mixed with warm liquid refrigerant exiting the condenser  112 . The mixed warm liquid refrigerant is then expanded with the evaporator expansion device  120  and evaporator  114  to provide load cooling/refrigeration and returns to compressor  110  to complete the refrigeration loop. 
         [0044]      FIG. 6  illustrates an AC/R hot vapor desuperheater discharge loop. In this particular discharge loop, the compressor  110  is energized to compress cold, low pressure refrigerant gas to hot, high-pressure gas. This refrigerant is directed to the previously charged storage module  116  acting as a hot vapor desuperheater where the hot vapor refrigerant rejects heat to the storage media  160  and reduces temperature. The vapor is then directed to the condenser  112 , where additional atmospheric heat rejection and condensation occur. The refrigerant leaves the condenser  112 , where the entirety of the desuperheated refrigerant is directed to the evaporator expansion device  120 . The warm liquid refrigerant is expanded and then evaporated in evaporator  114  before being returned to compressor  110 . 
         [0045]      FIG. 7  illustrates an AC/R warm liquid subcooler discharge loop. In this particular discharge loop, the compressor  110  is energized to compress cold, low pressure refrigerant gas to hot, high-pressure gas. This refrigerant passes to a condenser  112 , which removes much of the heat in the gas and discharges the heat to the atmosphere. The refrigerant leaves the condenser  112  as a warm, high-pressure liquid refrigerant delivered through a high-pressure liquid supply line where the entirety of the warm liquid refrigerant is directed to the storage module  116 , which acts as a warm liquid subcooler where the warm liquid refrigerant rejects heat to the storage media  160  and reduces temperature by transferring heat to the previously cooled thermal storage media  160 . The cooled liquid refrigerant is then directed to the evaporator expansion device  120 . The subcooled refrigerant is expanded and then evaporated in evaporator  114  before being returned to compressor  110 . 
         [0046]      FIG. 8  illustrates an AC/R cold vapor desuperheater discharge loop. In this particular discharge loop, the compressor  110  is energized to compress cold, low pressure refrigerant gas to hot, high-pressure gas. This refrigerant passes to a condenser  112 , which removes much of the heat in the gas and discharges the heat to the atmosphere. The refrigerant leaves the condenser  112  as a warm, high-pressure liquid refrigerant delivered through a high-pressure liquid supply line where the warm liquid refrigerant is then directed to the evaporator expansion device  120 . The refrigerant is expanded and then evaporated in evaporator  114  in a conventional manner and the expanded refrigerant is then diverted to the pre-charged storage module  116 , acting as a cold vapor desuperheater where the cold vapor refrigerant rejects heat to the storage media  160  and reduces temperature before being returned to compressor  110 . 
         [0047]      FIG. 9  illustrates an AC/R suction line charge loop. In this particular charging loop, the configuration of the loop is the same as the cold vapor desuperheater discharge loop illustrated in  FIG. 8 , except that the storage module  116  is being charged instead of being discharged. In this loop, the compressor  110  is energized to compress cold, low pressure refrigerant gas to hot, high-pressure gas. This refrigerant passes to a condenser  112 , which removes much of the heat in the gas and discharges the heat to the atmosphere. The refrigerant leaves the condenser  112  as a warm, high-pressure liquid refrigerant delivered through a high-pressure liquid supply line where the warm liquid refrigerant is diverted by valve V 3   126  through valve V 5   130  to the evaporator expansion device  120 . The evaporator expansion device  120  reduces the pressure of the warm liquid refrigerant to generate a cold mixed-phase refrigerant. In this mode, the evaporator  114  provides cooling as during typical AC/R operation. The cold vapor refrigerant exits the evaporator  114  and is diverted by valve V 6   132  to the storage module  116  where residual cooling that remains in the effluent refrigerant leaving the evaporator  114  is transferred to the storage media  160 , and the temperature of the cold vapor refrigerant increases. The superheated vapor refrigerant exits the storage module  116  and returns to compressor  110 . 
         [0048]    The disclosed system may utilize a relatively small capacity condenser compressor (air conditioner) and have the ability to deliver high capacity cooling utilizing thermal energy storage. This variability may be further extended by specific sizing of the compressor and condenser components within the system. Whereas the aforementioned refrigerant loops have been described as having a particular direction, it is shown and contemplated that these loops may be run in either direction whenever possible. 
         [0049]    The foregoing description of the invention has been presented for purposes of illustration and description. It is not intended to be exhaustive or to limit the invention to the precise form disclosed, and other modifications and variations may be possible in light of the above teachings. The embodiment was chosen and described in order to best explain the principles of the invention and its practical application to thereby enable others skilled in the art to best utilize the invention in various embodiments and various modifications as are suited to the particular use contemplated. It is intended that the appended claims be construed to include other alternative embodiments of the invention except insofar as limited by the prior art.