MXPA06004003A - Refrigeration apparatus - Google Patents

Abstract

Disclosed is an efficient refrigeration apparatus that provides refrigerant based energy storageand cooling. When connected to a condensing unit, the system has the ability to store energy capacity during one time period and provide cooling from the stored energy during a second time period. The system requires minimal energy to operate during either time period, and only a fraction of the energy required to operate the system during the first time period is required to operate the system during the second time period using an optional refrigerant pump.

Description

REFRIGERATION APPARATUS Field of the Invention The present invention relates generally to systems that provide stored energy in the form of ice, and more specifically to ice storage systems used to provide cooling, especially during peak electrical demand or peak electrical demand.

BACKGROUND OF THE INVENTION With the increasing demands of peak energy consumption, ice storage is an environmentally benign method that has been used to alternate air conditioning energy loads to times and cups after peak hours. There is a need not only to alternate the load of periods of greater demand to periods of lower demand, but also of increases in the capacity and efficiency of the air conditioning units. Current air conditioning units that have energy storage systems have had limited success due to several deficiencies that include confidence in water chillers, which are practical only in large commercial buildings, and have difficulty achieving high efficiency. In order to commercialize the advantages of thermal energy storage in large and small commercial buildings, thermal energy storage systems must have minimum manufacturing and engineering costs, maintain maximum efficiency under varied operating conditions, demonstrate simplicity in refrigerant handling design, and maintain flexibility in multiple applications of refrigeration or air conditioning. Systems for providing stored energy have been previously contemplated in U.S. Patent No. 4,735,064, U.S. Patent No. 4,916,916 issued both to Harry Fischer and U.S. Patent No. 5,647,227 issued to Fischer et al. All of these patents use ice storage to alternate the air conditioning loads of electric rates during peak demand to lower demand hours to provide economic justification and thus are specifically incorporated as a reference for everything they teach and describe.

Brief Description of the Invention The present invention overcomes the disadvantages and limitations of the prior art by providing an efficient cooling apparatus that provides cooling and energy storage based on refrigerant. When connected to a condensing unit, the system has the capacity to store energy, capacity for a period of time and to provide cooling of the stored energy during a second period of time. The system requires minimal energy to operate for any period of time, and only a fraction of the energy required to operate the system during the first period of time is required to operate the system during the second period of time using an optional coolant pump . Therefore, one embodiment of the present invention may comprise a cooling apparatus comprising: a condensing unit comprising a compressor and a condenser; an energy storage unit comprising an insulated tank containing a storage heat exchanger and at least partially filled with a phase change liquid, the storage heat exchanger further comprising a lower collection head and a storage head. top pickup connected by at least one thermally conductive member; a charge heat exchanger; a refrigeration management unit connected to the condensing unit, and the energy storage unit and the charge heat exchanger; a container of universal refrigerant handling inside the handling unit of refrigeration comprising: an outlet connection that returns the refrigerant to the condensing unit; an input connection that receives the refrigerant from the charge heat exchanger, a mixed phase regulator, a refrigerant variation and combination oil interruption vessel, and the upper collection head of the storage heat exchanger, a first bottom orifice providing bidirectional flow of refrigerant to a collection header of bottom of the storage heat exchanger, the bottom outlet that supplies liquid refrigerant for connection to the load heat exchanger and the coolant variation and combination oil interrupter vessel; a second bottom hole which is connected to the combination oil coolant variation and interruption vessel; and a solenoid valve connected to the universal refrigerant handling container and the charge heat exchanger that regulates the supply of refrigerant to the charge heat exchanger. One embodiment of the present invention may also comprise a refrigeration apparatus comprising: a condensing unit comprising a compressor and a condenser; an energy storage unit comprising an insulated tank containing an exchanger storage heat and at least partially filled with a phase change liquid; a charge heat exchanger; a refrigeration management unit connected to the condensing unit, the energy storage unit and the charge heat exchanger; and a refrigerant management controller in communication with the refrigeration management unit and comprised of electronic relay-based controllers that use environmental data to regulate the control operation of the refrigeration apparatus. One embodiment of the present invention may also comprise a method for providing cooling with a refrigeration apparatus comprising the steps of: condensing refrigerant with a condensing unit to create a first condensed refrigerant for a first period of time; supplying at least a portion of the first condensed refrigerant to a restricted evaporation unit within a tank that is at least partially filled with a phase change liquid; expanding the first condensed refrigerant within the evaporation unit to freeze a quantity of phase change liquid and form ice within the tank during the first period of time and to produce a first expanded refrigerant; returning at least a portion of the first expanded refrigerant to the condensing unit; circulating a second expanded refrigerant through the evaporation unit within the ice block for a second period of time to condense the second expanded refrigerant and to create a second condensed refrigerant; circulating at least a portion of the second condensed refrigerant from the universal refrigerant handling container to a charge heat exchanger; expanding the second condensed refrigerant within the charge heat exchanger to provide cooling for a second period of time; thereby producing a second additional expanded refrigerant; and controlling the operation of the refrigeration apparatus with a refrigerant management controller that uses external environmental data to regulate the operation. The modalities described offer the advantage of using energy from electric service companies during off-peak hours of low demand, which are usually at night, when these companies use their most efficient equipment. For example, high efficiency electric generators, typically powered by steam, produce one kilowatt-hour (KWH) for approximately 8,900 BTU. In contrast, a high-peak-hour electrical generator, such as a gas turbine, can use as much as 14,000 BTUs to produce the same KWH of electricity.

Second, transmission lines also run colder at night resulting in higher energy efficiency. Finally, for air-cooled air conditioning systems, the operation of the system at night offers greater efficiency by decreasing the temperature of the condensing unit. The refrigerant-based energy storage and cooling system, described, has the advantage of operating at high efficiency providing a complete system that alternates the use of energy without significant losses of total energy and with increased efficiencies of power generation outside peak hours and cooling by compressor based refrigerant outside peak hours, a net reduction in total energy consumption and an individual unit of operation.

BRIEF DESCRIPTION OF THE FIGURES In the figures, Figure 1 illustrates one embodiment of a cooling system and cold storage of high efficiency refrigerant in a mode used to cool a process fluid. Figure 2 illustrates one embodiment of a cooling system and cold storage of high efficiency refrigerant in a configuration for conditioning of air with multiple evaporators. Figure 3 is a table illustrating the state of the components for a mode of a cooling system and cold storage of high efficiency refrigerant. Figure 4 is a mode of a refrigeration apparatus that provides cooling and energy storage.

Detailed Description of the Invention While this invention is susceptible to modalities in many different forms, it is shown in the figures and will be described herein, in detail, specific embodiments thereof with the understanding that the present description is to be considered as an exemplification of the principles of the invention and will not be limited to the specific embodiments described. Figure 1 illustrates one embodiment of a cooling system and cold storage of high efficiency refrigerant. The described embodiments minimize the additional components and use almost no energy beyond that used by the condensing unit to store the energy. The cold storage design of refrigerant is designed to provide flexibility so that it is practicable for a variety of applications. The Modalities may use stored energy to provide chilled water for large commercial applications or to provide air conditioning by direct refrigerant to multiple evaporators. The design incorporates multiple modes of operation, the ability to add optional components, and the integration of intelligent controls that allow energy to be stored and released at maximum efficiency. When a condensing unit is connected, the system stores cooling energy in a first period of time, and uses the stored energy for a second period of time to provide cooling. In addition, both the condensing unit and the cold refrigerant storage system can operate simultaneously to provide cooling for a third period of time. As shown in Figure 1, one embodiment of a high efficiency refrigerant energy cooling and storage system with four main components incorporated into the system is represented. The air conditioning unit 102 is a conventional condensing unit which uses a compressor 110 and a condenser 111 to produce high pressure liquid refrigerant distributed through a high pressure liquid supply line 112 to the liquid handling unit 104. refrigeration. The refrigeration handling unit 104 is connected to the energy storage unit 106 which comprises an insulated tank 140 with ice making coils 142 and is filled with a phase change liquid such as water or other eutectic material. The air conditioning unit 102, the refrigeration handling unit 104 and the energy storage assembly 106 act in concert to provide efficient cooling to the charge heat exchanger 108 (inner cooling spiral assembly) and thereby perform the functions of the main modes of system operation. As further illustrated in Figure 1, the compressor 110 produces high pressure liquid refrigerant distributed through a high pressure liquid supply line 112 to the refrigeration handling unit 104. The high pressure liquid supply line 112 is divided and fed into a pause / oil variation vessel 116 and a pressure operated slide valve 118. The pause / variation vessel 116 is used to concentrate the oil in the low pressure refrigerant and return it to the compressor 110 through the dry suction return 114. Without the pause / variation vessel 116, some of the oil would remain in the accumulator vessel, ultimately causing the compressor 110 to become trapped due to lack of oil, and the heat exchangers become less effective due to the failure. The vapor rises to the top of the pause / variation vessel 116 and out of the vent capillary 128, to be reintroduced in the wet suction return 124. This is done to encourage the flow of steam out of the heat exchanger into the pause / variation vessel 116, and in the preferred direction. The length of the venting cap 128 or similar regulated purging device is used to control the pressure in the pause / variation vessel 116 and hence the boiling speed and the volume of the refrigerant in the system. The pressure operated slide valve 118 also allows a secondary supply of high pressure liquid refrigerant which can bypass the remainder of the refrigerant handling system 104 and supplies liquid refrigerant to a liquid refrigerant pump 120 and directly to the load unit 108 . When activated, the liquid refrigerant pump 120 supplies the evaporator coils of the charge heat exchanger 122 within the charging portion 108 of the cooling and energy storage system with liquid refrigerant. The low-pressure refrigerant returns from the evaporator coils of the charge heat exchanger 122 with the wet suction return 124 to a storage tank or storage container. universal refrigerant (URMV) 164 and the internal heat exchanger composed of spirals 142 cooling / unloading ice. The low pressure vapor leaves the top of the URMV 146 and returns to the air conditioning unit 102 through the dry suction return 114 together with the distilled refrigerant enriched with oil flowing out of the bottom of the pause container 116 / variation through a capillary 148 return oil. The oil return capillary 148 controls the speed at which oil is reintroduced into the system. The liquid refrigerant enriched with oil passes through a trap P 150, which eliminates (blocks) an undesired route for the refrigerant if the pause / variation vessel 116 is emptied. Additionally, the wet suction return 124 is connected to a splitter 130 before the URMV 146. The bifurcator supplies low pressure refrigerant from the mixed phase regulator 132 (TRVT). The mixed phase regulator 132 doses the refrigerant flow within the system by incorporating a valve (orifice) that opens to release the mixed phase refrigerant, only when there is sufficient amount of liquid accumulated in the condenser 111. In this way, the compressor 110 that drives the system needs only to operate to feed the high pressure refrigerant, which can correspond to the cooling load. This mixed phase regulator 132 prevents the purge of steam on the low pressure side (portion of thermal load) of the system and virtually eliminates the steam supply to the URMV 146 from the compressor 110, while also lowering the pressure required from the condenser pressure to the saturation pressure of the evaporator. This results in greater overall system efficiency while simplifying the liquid supercharging characteristics of the refrigerant handling unit. The insulated tank 140 contains spirals 142 cooling / unloading ice dual purpose (nominally geometrically designed helical spirals), arranged for gravity circulation and liquid refrigerant drainage, and connected to a mounting 154 of upper head on top, and to a mount 156 of bottom head in the bottom. The upper head assembly 154 extends outwardly through the insulated tank 140 to the cooling management unit 104. When the refrigerant flows through the ice freeze / discharge coils 142 and the head assemblies 154 and 156, the coils act as an evaporator and the fluid 152 solidifies in the insulated tank 140 for a period of time. The ice cooling / discharging coils 142 and the head assemblies 154 and 156 are connected to the Low pressure side of the refrigerant circuitry and are arranged for circulation by gravity or by pumping and draining of liquid refrigerant. During a second period of time, the hot vapor phase refrigerant circulates through the ice cooling / discharging coils 142 and the head assemblies 154 and 156 and melts the ice 152 providing a refrigerant condensing function. In one embodiment, the insulated tank 140 used in the system is a rotomolded double-walled plastic tank with an insulation value R13 to R35 on the lid, walls, and bottom of the tank. Since the system normally operates in a daily loading and unloading cycle, instead of a weekly cycle, the additional insulation values do not significantly improve the overall performance. The insulated tank 140 integrates the junction points for externally mounted refrigerant handling components and provides discharge from the cooling pipe. The tank is filled with water or eutectic material and incorporates a spill or overflow to maintain the level of fluid during the expansion of fluids. The central device within the refrigerant handling unit 104 is an accumulator vessel called the universal refrigerant handling container or URMV 146. The URMV 146 is on the low pressure side of the refrigerant circuitry and performs various functions. The URMV 146 separates the liquid and vapor refrigerant during the period of energy storage of the refrigerant and during the cooling period. The URMV 146 provides a column of liquid refrigerant during the refrigerant energy storage period that supports gravity circulation through the ice freeze / discharge coils 142 within the insulated tank 140. The URMV 146 is also a container for steam decoupling and provides coolant storage. The dry suction return 114 to the air conditioning unit 102, the compressor 110 during the energy storage period is provided by an outlet in the upper part of the URMV container 140. The dry suction return 114 is placed in such a manner to prevent the liquid refrigerant from returning to the compressor. A wet suction return 142 is provided through an inlet on top of the URMV 146 for connection to an evaporator (charge heat exchanger 122) during the period of time when the refrigerant energy storage system provides cooling . The first period of time is the period of time for storing refrigerant energy or storing energy on ice. The output of the compressor 110 is high pressure refrigerant vapor which condenses to high pressure liquid (HPL). A valve (not shown) at the outlet of the refrigerant pump 120 is energized to close the connection to the load unit 108. The high pressure liquid is surrounded by low pressure liquid refrigerant in a second refrigerant vessel which is a combination oil pause / variation vessel 116 which reconnects to the underside of the refrigerant system. During the first period of time (energy storage period) the pause / variation vessel 116 is an oil pause and during the cooling period, the pause / oil variation vessel 116 acts as a refrigerant variation vessel. During the energy storage period, an internal heat exchanger, in which the high pressure liquid refrigerant flows from the air conditioning unit 102, maintains everything, if not a small amount of low pressure liquid refrigerant outside the pause vessel 116 / oil variation. The refrigerant that is inside the container bubbles at a speed determined by two capillary tubes. A capillary is the venting capillary 128 which controls the refrigerant level in the pause / oil variation vessel 116. The second, the oil return capillary 148, returns the refrigerant enriched with compressor oil 110 inside the air conditioning unit 102 at a certain speed. The liquid refrigerant column in the URMV 146 is driven by gravity and places the pause / oil variation vessel 116 near the bottom of the URMV 146, the column maintains a stable flow of liquid supply coolant to the pause / variation vessel 116. oil. This container is connected to the low pressure liquid supply line 144 with a trap P 150 which prevents steam from entering the URMV 146 or the liquid refrigerant pump 120. The variation function allows the excess refrigerant during the cooling period to be drained from the cooling / ice discharge coils 142 in the insulated tank 140 keeping the surface area augmented to the maximum to condense the refrigerant. The physical placement of the pause / oil variation vessel 116 is a factor in its performance as a pause and variation vessel. This pause / oil variation vessel 116 additionally provides the route for the return of the oil migrating with the refrigerant which must return to the compressor 110. The high pressure liquid refrigerant slightly subcooled (colder than the temperature of the vapor phase to coolant liquid) the high pressure liquid refrigerant leaving the pause / oil variation vessel 116 flows through a regulator 132 of mixed phase (vapor trap of thermodynamic refrigerant) where the pressure drop occurs. As noted above, the refrigerant handling unit 104 receives high pressure liquid refrigerant from the air conditioning unit via a supply line 112 in high pressure liquid. The high pressure liquid refrigerant flows through the heat exchanger into the pause / oil variation vessel 116, where it is subcooled, and the mixed phase regulator 132 is connected, where the pressure drop of the refrigerant The use of a mixed phase regulator 132 provides very favorable functions in addition to the pressure drop of the liquid refrigerant. The mass amount of the refrigerant passing through the mixed phase regulator 132 will correspond to the boiling speed of the refrigerant in the ice making coils 142 during the energy storage time period. This eliminates the need for refrigerant level control. The mixed phase regulator 132 passes subcooled liquid refrigerant, but closes when it perceives vapor (or inadequate subcooling of liquid) at its inlet. The impulse action of the refrigerant leaving the opening and the closing of the mixed phase regulator 132 creates a hammer effect in the liquid refrigerant as a static sling is produced inside the closed column. This agitates the liquid refrigerant in the ice making coils 142 during the energy storage time period and improves the heat transfer as well as the aid in the segregation of the liquid phase and vapor refrigerant. The mixed phase regulator 132, in conjunction with the URMV 146, also drains the air conditioning unit 102 from the liquid refrigerant keeping its surface area available for condensation. The mixed phase regulator 132 allows the head pressure of an air-cooled condensing unit to float within ambient temperature. The system does not require a superheat or subcooling circuit that is mandatory with most condensing units connected to a direct expansion cooling device. An adjustment to the mixed phase regulator 132 allows the cooling energy storage and cooling system to make or make ice with an average four degree approach. The low pressure liquid refrigerant leaving the mixed phase regulator 132 passes through a bifurcation 130 to an eductor (or injection nozzle) located between the entrance to the URMV 146 and the upper head assembly 154 of the manufacturing coils 142 ice to help with the circulation of refrigerant by gravity. The splitter 130 reduces the pressure and the flow of the liquid refrigerant. During the refrigerant energy storage time period, the eductor creates a drop in pressure as the refrigerant leaves the bifurcate 130, thereby increasing the circulation velocity of refrigerant in the ice making coils 142 and improving performance of the system. The mixed phase regulator 132 also varies the refrigerant flow in response to the evaporator load. It does this by maintaining a constant pressure in the URMV 146. This allows the condensing pressure to float within ambient air temperature. As the ambient air temperature decreases, the head pressure in the compressor 110 decreases. The mixed phase regulator 132 allows the liquid refrigerant to pass but closes when it perceives vapor. Retain the double phase mixture in a "trap". It allows the liquid (which is more dense) to pass but begins to close when less dense gas is passed through. The steam returns to the condenser 111 to become additionally condensed in a liquid. The mixed phase regulator 132 self-regulates (once calibrated) and has no parasitic losses (adiabatic expansion). Additionally, the mixed phase regulator 132 improves the efficiency of the heat transfer in the heat exchanger coils by removing liquid vapor and when creating an impulse action on the low pressure side. As noted above, the mixed phase regulator 132 opens to allow the low pressure liquid passage and then closes to trap steam on the high pressure side and creates an impulse action on the low pressure side of the regulator. This impulse action further moisturizes the inner wall of the sub-circuit to the boiling level, which aids in the transfer of heat. The low pressure liquid enters the URMV 146 vessel and the liquid and vapor components are separated. The liquid component fills the URMV 146 at a certain level and the vapor component is returned to the compressor of the air conditioning unit 102. In a normal direct expansion cooling system, the vapor component circulates from start to finish the system reducing the efficiency With this embodiment, the vapor component is immediately returned to the compressor 110. The liquid refrigerant column in the URMV 146 is driven by gravity and has two routes during the energy storage time period. One route is to the pause / oil variation vessel 116 where the spill rate is metered by the capillary tubes 128 and 148. The second route for the liquid refrigerant column is to the inner head assembly 156, through the coils 142 of ice making and assembly 154 of the upper head, and back to compressor 110 through URMV 146. This gravity circulation in this manner is how energy is stored in the form of ice when the tank is filled with a phase change fluid such as water. A solid column of the liquid refrigerant in the URMV 146 becomes less dense in the ice cooling coils 142, as the refrigerant becomes a vapor. This differential maintains circulation by gravity. Initially steam, and subsequently in the storage cycle the refrigerant liquid and the steam, are returned to the URMV 146. The liquid returns the column and the steam returns the compressor 110 inside the air conditioning unit 102. The circulation by gravity ensures the uniform accumulation of ice. As one of the ice making coils 142 accumulates more ice, its heat flow rate is reduced. The spiral next to it now receives more refrigerant until it has an equal velocity of heat flow. The design of the ice making coils 142 creates an ice build-up pattern that keeps the compressor suction pressure high during the storage period of ice storage. During the final phase of the energy storage time period, rapid ice formation accumulates and the suction pressure drops dramatically. This is the full charge indication that automatically turns off the condensing unit with an adjustable refrigerant pressure switch. When the air conditioning unit 102 is turned off during the energy storage time period, the high pressure liquid refrigerant forces the slide (piston) in the pressure operated slide valve to block the free flow of refrigerant to the exchanger 122 of heat load. When the energy storage system is fully charged and the air conditioning unit 102 closed, the mixed phase regulator 132 allows the pressures of the refrigerant system to be quickly equalized. With the high-pressure liquid that does not push the closed slide any longer, a spring returns the slide to the open position, allowing the refrigerant to flow into the heat exchanger 122 without restriction. In one embodiment, the charge heat exchanger 122 is located below the energy storage system, and the refrigerant flows by gravity to the flooded evaporator in a die and operates as a thermosyphon. In summary, when the tank is filled with water and the refrigerant is circulated through the coils, the coils act as an evaporator, forming ice and storing energy for a period of time. During a Second period of time, the refrigerant circulates through the coils and melts the ice providing a condensing portion of refrigerant. This methodology of energy discharge and storage is known as spiral ice, internal fusion. The time periods are determined by the end user, a utility, or optional intelligent controls incorporated within or attached to the system. Figure 2 illustrates one embodiment of a high efficiency refrigerant cooling and storage system in a configuration for air conditioning with multiple evaporators (including mini-split systems very common in Europe and the Far East). As shown in Figure 2, several efficiency options can be added to the refrigerant cooling and cold storage system. As noted above, a liquid refrigerant pump 120 can be added within the refrigerant handling unit 104 downstream of the pressure operated slide valve 118 to circulate refrigerant to a charge which is represented as mini-evaporators 160. division in this modality. The coils of the heat exchangers within the mini-division evaporators 160 are directly supplied with refrigerant using liquid turbocharging technology. On the line 124 of wet suction return, both the liquid and the steam return to the energy storage unit 106. The vapor is condensed by the discharge coils 142 within the ice 152 and the liquid refrigerant is returned to the inlet of the liquid refrigerant pump 120. Excess refrigerant that may have been used during the energy storage time period is now stored in the pause / oil variation vessel 116. The refrigerant path options represented with the pressure operated slide valve in Figure 2 allow both the air conditioning unit 102 and the energy storage unit 106 to provide condensation for the mini-division evaporators 160 within the unit 108 load. This is called the "Push" mode and operates for a third period of time. The pluralities of coils comprising the ice freeze / discharge coils 142 may have a passive water delamination system consisting of passive stratified tubes 164 in physical contact with the ice freeze / discharge coils 142 that provide a route for the displacement of water outside the ice limit. These passive stripping tubes 164, together with supports which keep the spirals properly separated provide mechanical protection for the spirals during shipping. You can install a Optional air bubbler, water pump, agitator, similar circulator to actively de-stratify the fluid that promotes flow in any direction. Passive demotransformers 162 may also be used in the upper header assembly 154, the lower header assembly 156, or other heat exchange surfaces within the energy storage unit 106 to provide additional delamination and heat exchanger within the fluid. Ice 152. The pluralities of coils may also have a passive water stratification system consisting of tubes in physical contact with the coils providing a route for the displacement of water outside the ice limit. These tubes, together with supports that keep the spirals properly separated, provide mechanical protection for the spirals during shipping. An optional air bubbler, water pump, agitator, circulator or the like can be installed to actively de-scale the fluid that promotes flow in any direction. Figure 3 is a table illustrating the state of the components for a mode of a cooling and cold storage system of high efficiency refrigerant operating in three periods of time and three modes. As shown in Figure 3, the state of the air conditioning unit 102, pause / oil variation vessel 116, ice freeze / discharge coils 142 and pressure operated valve 118 is shown for each of the three time periods and modes described. For example, in the period 1 of time, during the cold storage mode of refrigerant, the air conditioning unit 102 is turned on, the pause / oil variation vessel 116 is operating as an oil pause, the spirals 142 of Freezing / discharge of oil are making ice with coolant flowing from the bottom to the top, and pressure operated valve 118 is closed. During this ice manufacturing (charging) cycle, the air conditioning unit 102 supplies hot liquid refrigerant to the system. The circuit follows the path that starts with the high pressure liquid from the condenser 111, through the mixed phase regulator 132 (float) which changes the refrigerant to a high pressure liquid where it is fed into the URMV 146. The system feeds low pressure liquid to the lower head assembly 156 of the heat exchanger inside the energy storage unit 106 where it freezes gradually the majority of the water in the insulated tank 140. The vapor-phase refrigerant leaves the top-head assembly and flows back to the URMV 146. Any previous liquid falls to the bottom of the URMV 146 and repeats the circuit through the spirals 142 of freezing / unloading of ice. The resulting "dry" low pressure steam exits the URMV 146 and the cycle starts again. In the period 2 of time, during the cooling mode also referred to as the ice cooling or melting cycle (discharge), the air conditioning unit 102 is turned off, the pause / oil variation vessel 116 is operating as a vessel of variation, the ice freeze / discharge coils 142 are condensing with coolant flowing from the top to the bottom, and the refrigerant pump 120 and the pressure operated valve 118 are open. During the periods of highest demand energy, the air conditioning unit 102 connected to the system is turned off and the system discharges the ice created during the ice making cycle. The system discharges the energy dissipation provided by the ice to allow cooling. In the described modes, there are two cooling cycle methods supported by the system module: load change and load leveling. The change of load makes use of an individual refrigeration circuit, the system connected to a spiral Normal evaporator to provide both sensitive and latent cooling. The load leveling mode uses two separate cooling circuits to provide cooling: a sensitive evaporator circuit to provide sensible cooling (which removes heat from the ventilating air); and, a separate ice evaporator to provide latent cooling (moisture removal). A normal air conditioning unit 102 and the past size evaporative coil (load unit 108) comprise the sensing evaporator circuit while the second evaporator coil and the energy storage unit 106 comprise the ice evaporator circuit. The reverse can also be achieved in other modes of the load leveling system. The refrigeration circuit in the charge change mode and the ice evaporator circuit in the charge leveling mode are fundamentally similar with both systems which are connected to an evaporative coil (load unit 108). The difference between the two is that in the charge change mode, the load unit 108 provides both sensible and latent cooling whereas in the load leveling, the load unit 108 mainly provides latent cooling. This allows the same basic spiral design the ability to perform different functions in multiple configurations.

During the ice melt cycle, the coolant pump 120 is the driving force for the coolant to the load unit 108. A unique aspect of these systems compared to normal air conditioning systems is that the indoor unit (load unit 108 and air handler) can be as far as 150 feet from the energy storage unit 106 (normal are 8 feet maximum). This is possible because the pause / oil variation vessel 116 acts as a liquid receiver and adjusts the additional coolant required to traverse long lines. Normal liquid-thirsty air conditioning systems at these distances and provide poor performance. This allows the described systems to be applied to constructions much larger than the normal division system air conditioners. A main application for these types of refrigeration appliances is in the field of load change in the greatest demands of air conditioning energy in the day. Mainly there are two methods commonly followed to avoid the high electrical demand during peak summer hours. One method is called load spillage in which compressors are closed during peak periods if cooling is supplied by stored energy such as ice to provide cooling. The other practice is called load leveling in which a smaller compressor is operated continuously. During periods of lower demand for cooling, the energy is stored thermally as ice and during periods of moderate demand, the small compressor unit corresponds to the load requirement. During periods of high demand when the small compressor can not supply the necessary energy, the capacity of the system is complemented by the melting of ice to make a difference. The ice freeze period during the low demand for air conditioning can be as long as 12-14 hours, contrasting with the period of higher demand which can be as short as 3 hours or as long as 10 hours. The following describes the refrigerant flow for both the charge change mode and the ice evaporator circuit in the charge level mode. During the ice melting cycle (discharge), the ice freeze / discharge coils in the energy storage unit 106 act as condensers, taking vapor refrigerant from the charge unit 108 and condensing it. The cold liquid refrigerant (32 ° F-58 ° F) is circulated to the charging unit 108 via a liquid refrigerant pump 120. If the load unit 108 is sufficiently close to and below the unit 106 of refrigeration management, the cycle operates completely at density differences (such as thermosyphon), thereby eliminating the need for liquid refrigerant pump 120, and thereby reducing energy consumption (increasing the efficiency of the system). This circuit uses only low pressure liquid and vapor refrigerant. The steps in the ice evaporation circuit are: 1. The liquid refrigerant is pumped from the URMV 146 via the pump 120 of the liquid refrigerant to the unit 108 load. 2. The liquid refrigerant is boiled in the loading unit 108. 3. A vapor / liquid mixture returns from the load unit 108 to the URMV 146 through the wet suction return 124. 4. The liquid refrigerant falls to the bottom of the UVMV 146. 5. Most of the vapor refrigerant component does not enter the URMV 146, but enters the heat exchanger in the energy storage unit 106 due to the suction pressure caused to the condensing the refrigerant in the cooling sub-circuits (spirals). 6. The vapor refrigerant enters the spirals 142 of freezing / discharge of ice and condenses in a liquid in the lower head assembly 156. 7. The liquid refrigerant leaves the lower head assembly 156 and is collected at the bottom of the URMV 146. 8. The cycle is repeated. In the load change mode, the 106 unit of thermal energy is the only cooling system that uses energy during the pre-established moments of greatest demand. Therefore, most energy use (up to 100%) can be changed to other times not during peak hours. The purpose of the load change function is to change the electrical demand to the hours in non-peak hours. The total demand is reduced, the efficiency is increased because the air conditioning unit operates at a lower ambient temperature, and the demand of the hours of higher demand is changed to the hours of lower demand. In charge leveling mode, two separate cooling circuits are used to provide cooling. The first circuit provided is powered by another cooling system and will preferably provide sensitive cooling. The described embodiments are used as part of the second refrigeration circuit, of the ice evaporator circuit. The described systems provide very efficient latent cooling because they run coolant at a much lower temperature (lower pressure) through the load unit 108 compared to the more normal air conditioning systems. The resulting lower dew point brings more moisture (latent energy) out of the air. The use of the system in the air leveling mode to provide latent cooling allows the size of the only sensitive air conditioning system to be reduced. Smaller air handling systems are also possible. Ideally, the objective is to eliminate dehumidification (latent cooling) in the first spiral, and to provide it completely in the second spiral. By improving the efficiency of the first refrigeration circuit and by using the system to supply cooling to the second circuit, the peak demand can be reduced and total efficiency can be improved (compared to the conventional unit air conditioning system) depending on the cooling demand. In the load leveling configuration, the system can still provide the total cooling load during the winter months or highlight when the cooling load is defined or defined by an energy management system to additionally minimize the peak electrical demand . Finally, in the period 3 of time, during the "Push" mode, the air conditioning unit 102 is on, the pause / oil variation vessel 116 is acting as a mixing and oil disruption vessel in combination, the ice freeze / discharge coils 142 are condensing with coolant flowing from the top to the bottom, and the pump 120 of refrigerant and pressure operated valve 118 are open. The "Push" mode allows the compressor 110 associated with the system (for making ice) to provide cooling directly to the load unit 108. This can serve several purposes such as: providing cooling after the ice is depleted; provide additional capacity during peak hours (along with ice; and save ice for later, presumably for improved cost savings.) Nominally, the timing of an ice construction is calculated to meet energy costs alone, for example, the price per kWH However, the calculation can also deal with the efficiency of the system at various times of the night, which indirectly impacts the total energy costs.The efficiency during the night varies with the ambient temperatures and the climatic conditions. Typically, temperatures during the night follow a profile (of being colder just before sunrise), and this can be used to optimize construction accumulation times. However, weather forecasts and other forward feeding mechanisms can also be used to optimize during construction times. The construction time optimization can consider several additional restrictions and factors as well, such as noise, convenience, maximum consumption thresholds, etc. The accumulation of ice can also be optimized around expected cooling needs, that is, it can be advantageously economical not to build ice if the calculations or rules indicate that it will not be needed (for the next cycle) or some period of time. The system does not need to be configured just to cool an installation, that is, for the human community. It can provide cooling for any purpose, such as cooling another liquid in a process. The capacity (proportion) of distribution can also be adjusted via a valve that feeds some output (from liquid coolant pump 120, by way of example) directly back to the system, by bypassing the evaporator or load unit 108. The system generates its own water from the condensation, and is sufficient to not require that the insulated tank 140 be filled due to evaporation. The excess water generated through the condensation is It can drain through a pipe that leads from an elevation above the ice to the ground. To prevent this route from becoming a source of hot air flow to the tank, a water trap or other valve system may be placed in the tube. The block of ice 152 formed inside the insulated tank 140 is designed to sink from the top to the bottom (due to the evaporation of the refrigerant) from the inside of each if the spiral section 142 of cooling / discharging ice from the ice to the outside (the ice that touches the spiral melts first). After all the ice that touches the ice cooling / discharging coils 142 melts, the water, not the ice, is in contact with the spiral, although a "sheath" of water can be trapped on the top or bottom . This sheath slows the rate of heat transfer from the spiral to the ice. Operation and efficiency conditions are improved by circulating water through the sleeve. To affect this flow, two things must be achieved: a complete path must be created along the ice freeze / discharge spirals 142, from the upper water to the open water, and a means to promote the flow must be established. To create a route, passive stratified conductors 164 (thermal conductors such as copper tube) are installed towards the bottom of the assembly. spirals, and physically attached to each spiral 142 of cooling / discharging ice along the length of the conductor. In addition, the passive stratifier tube 164 extends beyond the ice construction area in the open water. Multiple conductors can be added. Each conductor thus creates its own "sheath" of water that starts in the open water and connects to each sheath of the spiral, thus creating the path from the bottom up. At the top of each spiral, a passive stratifier tube 164 is again added to create another sheath extending through the ice at the top. This conductor can be of a different design, such as four rods extending upwards from the heads, or perhaps a thin conductive fin running the full length of each spiral assembly. This method is optimized if the block of ice is built with the water level in the tank such that in a complete construction time, there is open water above the ice (the water level increases substantially during construction due to the lower density). of ice, so that the water level does not need to start above the spiral assembly). Having thus established a water route from the open water, to each spiral, and out of the upper part of the ice block, the issue of promoting the flow of water. Both passive and active methods can be applied. A passive method will use stratification in temperature and density to create a natural flow. The active systems will stimulate the flow additionally by introducing water bubbles in the tank, or upwards of each spiral, or by pumping water to create circulation. Figure 4 illustrates another embodiment of the refrigeration apparatus used as a cold storage and cooling system using a solenoid valve 166. The solenoid valve 166 is designed to replace the pressure operated slide valve 118 of Figure 1 and opens during the ice melting cycle and closes during the ice making cycle. When a valve operated under pressure is used, during the ice making cycle, the pressure in the high pressure liquid supply line 112 of the compressor discharge is high and becomes the spring force within the valve 118 of sliding operated by pressure. The piston inside the valve then is in its farthest position which closes the inlet line to the pump 120 of the liquid refrigerant and prevents the flow of liquid. During the ice melting cycle, the pressure in the high pressure liquid supply line 112 is smaller and the piston is in its closest position. In this condition, both the inlet and outlet to the valve are opened and the refrigerant flows to the pump 120 of the liquid refrigerant and forward to the loading unit 108 as shown in Figure 1. By removing the pressure operated valve valve 118 and the direct access line of the high pressure liquid supply line 112, the refrigerant can always flow from the URMV 146 to the liquid refrigerant pump 120, but the flow is regulated by a solenoid valve 166 (in this downstream mode) of the liquid refrigerant pump). This configuration allows the use of out-of-shelf valves and greater precision and flow control with controllers based on electronic relays instead of relying on pressure switches to regulate the flows. In an embodiment as detailed in Figure 4, the complete control of the refrigeration apparatus can be controlled by a refrigerant handling controller 168 which is in communication with the refrigeration handling unit 104 and is used to control the operation of the system . The refrigerant handling controller 168 may be operated by a PC-type card, IC chip incorporated in a form such as a programmable logic controller (PLC) or programmable microcontroller with analog, digital and relay inputs and outputs.

This greatly increases the flexibility of the system, and reduces the manufacturing cost while allowing numerous additional applications and "intelligent controls" for the device. The refrigerant management controller 168 can receive real-time data and environmental information from communications with the environmental sensors 172. These environmental sensors 172 can measure variables such as time, temperature, humidity (dew point), energy consumption, costs of energy, state of the power grid or a variety of other variables that may be useful in determining how and when the cooling apparatus should perform. These factors can change times, speeds and specific performance issues in the ice making cycle that can optimize performance or other factors such as when unit noise may be of interest. The refrigerant handling controller 168 may also contain a data collection unit 170 in which historical environmental and performance data can be stored. This data may be used by an outside person or by the refrigerant management controller 168 to make performance changes based on the historical data of the unit. Additional communications can be achieved with the refrigerant handling controller 168 by a communication device 174 which will provide either a wireless link 176 or a wire link to a telecom 180 or network / Internet. In this way, the collected historical data can be downloaded from the system or specific control functions can be programmed into the device such as weather data and forecasts, solar tables and the like. The control inputs, external or data may also be communicated to the refrigerant handling controller 168 based on the current, typical or intended conditions beyond the direct sensing capability of the controller 168, such as regional power supply, cost or consumption data. Historical data (whether captured by the controller or derived externally, environmental data, beyond those presented in the forecast, climate, energy, cost or other data that may significantly impact the efficiency or desired performance and optimization of the Manufacturing / melting times can be used to provide greater optimization of the performance of the apparatus in a multitude of application environments.In these described embodiments, a wide variety of heat load applications can be adapted in conjunction with the modalities mentioned above. Any necessary cooling that can be transferred via refrigerant piping can be used with these systems. For example, daily cooling, plastic injection molding cooling, fresh fish refrigeration, inlet cooling for turbine power generation, watercraft cooling and air conditioning as well as a wide variety of process cooling applications or can benefit from these types of systems.

Claims (33)

1. CLAIMS 1. Cooling apparatus comprising: a condensing unit comprising a compressor and a condenser; an energy storage unit comprising an insulated tank containing a storage heat exchanger and at least partially filled with a phase change liquid, the storage heat exchanger further comprising a lower collection head and a storage head. top pickup connected by at least one thermally conductive member; a charge heat exchanger; a refrigeration management unit connected to the condensing unit, the energy storage unit and the charge heat exchanger; a universal refrigerant handling container within the refrigeration handling unit comprising: an outlet connection that returns the refrigerant to the condensing unit; an inlet connection that receives the refrigerant from the charge heat exchanger, a mixed phase regulator, a refrigerant variation and combination oil interruption vessel, and the upper collection head of the heat exchanger of
2. storage; a first bottom hole that provides bidirectional flow of refrigerant to a bottom collection head of the storage heat exchanger, the bottom outlet that supplies liquid refrigerant for connection to the load heat exchanger and the coolant variation and interruption vessel of combination oil; a second bottom hole which is connected to the combination oil coolant variation and interruption vessel; and a solenoid valve connected to the universal refrigerant handling container and the charge heat exchanger that regulates the supply of refrigerant to the charge heat exchanger. Cooling apparatus according to claim 1, wherein the second bottom hole is connected to the combination oil coolant variation and interruption vessel through a trap p.
3. 3. Cooling apparatus according to claim 1, wherein the phase change liquid is a eutectic material.
4. 4. Cooling apparatus according to claim 1, wherein the phase change liquid is

   Water.
5. 5. Cooling apparatus according to claim 1, further comprising: a liquid refrigerant pump located within the refrigeration handling unit.
6. Cooling apparatus according to claim 1, further comprising: a first regulated purging device connected to, and located between the inlet connection of the universal refrigerant handling container and the combination oil coolant variation and interruption vessel .
7. 7. Cooling apparatus according to claim 6, wherein the first regulated purging device is a return capillary oil.
8. Cooling apparatus according to claim 1, further comprising: a second regulated purge device connected to, and located between the inlet connection of the universal refrigerant handling container and the combination oil coolant variation and interruption vessel .
9. 9. Cooling apparatus according to claim 8, wherein the first regulated purging device is a venting capillary.
10. 10. Cooling apparatus according to claim 1, wherein the storage heat exchanger further comprises passive de-stressing tubes.
11. 11. Cooling apparatus according to claim 1, wherein the storage heat exchanger further comprises passive de-scaler fins.
12. 12. Cooling apparatus according to claim 1, wherein the charge heat exchanger is at least a mini-partition evaporator.
13. 13. Cooling apparatus comprising: a condensing unit that purchases a compressor and a condenser; an energy storage unit comprising an insulated tank containing a storage heat exchanger and at least partially filled with a phase change liquid; a charge heat exchanger; a refrigeration management unit connected to the condensing unit, the energy storage unit and the charge heat exchanger; and a refrigerant management controller in communication with the refrigeration management unit and comprised of relay-based controllers

    electronic devices that use environmental data to regulate the control operation of the refrigeration appliance.
14. 14. Cooling apparatus according to claim 13, wherein the refrigerant handling controller uses environmental data in real time to regulate the control operation of the refrigeration apparatus.
15. 15. Cooling apparatus according to claim 13, wherein the refrigerant handling controller uses projected environmental data to regulate the control operation of the refrigeration apparatus.
16. 16. Cooling apparatus according to claim 13, wherein the refrigerant handling controller further comprises: at least one sensor that transmits environmental data to the refrigerant handling controller.
17. 17. Cooling apparatus according to claim 13, wherein the refrigerant handling controller further comprises: a data collection unit that can record historical environmental and operating data of the refrigeration apparatus.
18. 18. Cooling apparatus according to claim 17, wherein the refrigerant handling controller uses historical environmental data and

    operation to adjust the current operation of the refrigeration appliance.
19. 19. Cooling apparatus according to claim 13, wherein the refrigerant handling controller further comprises: a communication device for allowing the refrigerant handling controller to communicate with external sources.
20. 20. Cooling apparatus according to claim 19, wherein communication with external sources is performed with a wire link.
21. 21. Cooling apparatus according to claim 19, wherein communication with external sources is performed with a wireless link.
22. 22. Cooling apparatus according to claim 19, wherein the control operation of the cooling apparatus can be performed with communication with external sources.
23. 23. Cooling apparatus according to claim 22, wherein communication with external sources is performed using a normal industry protocol.
24. 24. Cooling apparatus according to claim 19, wherein the historical environmental and operating data of the refrigeration apparatus can be transmitted with communication with external sources.
25. 25. Cooling apparatus according to claim 19, wherein the refrigerant handling controller uses one or more weather forecast data, energy cost data or availability forecast data to adjust the operation of the refrigeration apparatus.
26. 26. Cooling apparatus comprising: a condensing unit that purchases a compressor and a condenser; an energy storage unit comprising an insulated tank containing a storage heat exchanger and at least partially filled with a phase change liquid, the storage heat exchanger further comprising a lower collection head and a storage head. top pickup connected by at least one thermally conductive member; an intereambiador of heat of load; a refrigeration management unit connected to the condensing unit, the energy storage unit and the charge heat exchanger; a universal refrigerant handling container within the refrigeration handling unit comprising: an outlet connection that returns the refrigerant to the condensing unit;

    an inlet connection receiving the refrigerant from the charge heat exchanger, a mixed phase regulator, a refrigerant variation and combination oil interruption vessel, and the upper collection head of the storage heat exchanger; a first bottom hole that provides bidirectional flow of refrigerant to a bottom collection head of the storage heat exchanger, the bottom outlet that supplies liquid refrigerant for connection to the load heat exchanger and the coolant variation and interruption vessel of combination oil; a second bottom hole that is connected to the combination oil coolant variation and interruption vessel; a solenoid valve connected to the universal refrigerant handling container and the charge heat exchanger that regulates the supply of refrigerant to the heat exchanger; and a refrigerant handling controller in communication with the refrigeration handling unit to control the operation of the refrigeration apparatus.
27. 27. Method for providing cooling with a cooling apparatus comprising the steps of:

    condensing refrigerant with a condensing unit to create a first condensed refrigerant during a first period of time; supplying at least a portion of the first condensed refrigerant to a restricted evaporation unit within a tank that is at least partially filled with a phase change liquid; expanding the first condensed refrigerant within the evaporation unit to freeze a quantity of phase change liquid and to form ice within the tank during the first period of time and to produce a first expanded refrigerant; returning at least a portion of the first expanded refrigerant to the condensing unit; circulating a second expanded refrigerant through the evaporation unit within the ice block for a second period of time to condense the second expanded refrigerant and to create a second condensed refrigerant; circulate at least a portion of the second condensed refrigerant from the universal refrigerant handling container to a charge heat exchanger; expand the second condensed refrigerant inside the charge heat exchanger to provide

    cooling during the second period of time, thereby producing second additional expanded refrigerant; and controlling the operation of the refrigeration apparatus with a refrigerant management controller that uses external environmental data to regulate the operation. The method of claim 27, wherein the step of circulating at least a portion of the second condensed refrigerant to a charge heat exchanger is performed with a liquid refrigerant pump. 29. The method of claim 27, further comprising the step of: generating external environmental data in real time using environmental sensors in communication with the refrigerant handling controller. 30. The method according to claim 27, further comprising the step of: generating external environmental data based on forecast data projections. 31. The method according to claim 27, further comprising the step of: generating external environmental data based on historical data. 32. Method according to claim 27, which

    further comprises the step of: communicating with the refrigerant handling controller to transmit data to and from the refrigeration apparatus. 33. The method of claim 27, further comprising the step of: controlling the operation of the refrigeration apparatus with remote communication with the refrigerant handling controller.