Abstract
The following invention relates to a dual loop conventional chiller plant, hereafter referred to as the enhanced air conditioning chiller. Where the first loop, primary circuit, typifies refrigeration compression closed loop containing the air conditioning companion stabilizer (“aka” stabilizer); establishing efficiency enhancements. The refrigeration loop is configured to provide refrigerant at a set point temperature amenable to the charging, ice production or freezing brine solution, contained within the ice storage tank static reservoir. The enhanced air conditioning chiller air handler(s) provides space/zones climate control via a fluid at a prescribed temperature, hereafter referred to as a hydronic solution, maintaining the air temperature to the space/zones.
Claims
1. An enhanced air conditioner chiller system, comprising in combination: A refrigerant circuit circulating a refrigerant medium along a closed refrigerant path; Said refrigerant circuit including a compressor providing work, in the form of compression, increasing pressure and temperature on the refrigerant medium, said compressor is located along said refrigerant path; Said refrigerant circuit including a condenser operating on the refrigerant medium removing heat from the refrigerant medium, said condenser located downstream from said compressor along said refrigerant path; Said refrigerant circuit including an electronic expansion valve acting on the refrigerant medium, expanding refrigerant medium, thereby decreasing its pressure and temperature; said expansion valve located downstream from said condenser along said refrigerant path; Said refrigerant circuit includes an evaporator operating on the refrigerant medium; said evaporator located downstream from said expansion valve and upstream of said compressor along said refrigerant path; Said refrigerant circuit having an efficiency which is improved by the inclusion of a stabilizer, in the form of a heat exchanger, located downstream of refrigerant circuit condenser, upstream of refrigerant circuit expansion valve; Said refrigerant circuit efficiency being improved by the inclusion of the system control module, adapted with logic software controlling said stabilizer and evaporator components; A hydronic circuit circulating a hydronic solution along at least one hydronic solution path; Said hydronic circuit includes an air handler, or multiple air handlers in an array, configured to remove heat from the space/zone air or process load by adding heat to the hydronic solution; Said hydronic circuit including a VFD controlled hydronic pump configured to circulate hydronic solution along at least one hydronic solution path; Said hydronic circuit includes an ice storage vessel containing a liquid-to-solid phase changing medium contained within its static reservoir. Where at least one hydronic solution path passing in a heat transfer relationship with said static reservoir medium contained within the ice storage vessel to transfer heat resulting in a phase change to said medium within said static reservoir; Said hydronic and refrigerant circuits having at least a portion of said hydronic solution path passing in a heat transfer relationship through said evaporator of said refrigerant circuit for heat transfer from the hydronic solution to the refrigerant medium; Said hydronic circuit efficiency being improved by the inclusion of the system control module, adapted with logic software controlling said stabilizer and evaporator components.
2. The system of claim 1 wherein said stabilizer includes a refrigerant medium path in heat transfer relationship with a portion of at least one hydronic solution path for heat transfer from the refrigerant medium to the hydronic solution.
3. The system of claim 2 wherein said stabilizer heat exchanger is located within said refrigerant medium circuit between said compressor, downstream of condenser, and upstream of said expansion valve providing a drop in refrigerant medium temperature.
4. The system of claim 1 wherein said hydronic circuit includes a first split junction splitting at least one hydronic solution path to a stabilizer leg routed in heat transfer relationship to refrigerant medium through said stabilizer.
5. The system of claim 1 wherein said hydronic circuit includes a second split junction splitting at least one hydronic solution path to an evaporator leg routed in heat transfer relationship to refrigerant medium through said evaporator.
6. The system of claim 1 wherein said hydronic circuit includes a third split junction splitting of at least one hydronic solution path to an air handler leg routed in heat transfer relationship to the integrated heat exchanger assembly of said air handler; Said hydronic circuit includes a split downstream from said air handler or air handlers, containing an ice storage vessel return leg and a bypass leg upstream of said ice storage vessel.
7. The system of claim 5 wherein a modulation valve is located on said second split of said hydronic circuit evaporator leg. The system of claim 4 wherein a modulation valve located on first split of said hydronic circuit stabilizer leg. Wherein the modulation valve associated with aforementioned hydronic circuit evaporator leg is opened fully when the refrigeration circuit is engaged. Wherein the modulation valve associated with the hydronic circuit stabilizer leg is adjusted, variably between fully open and fully closed positions, allowing for finite hydronic solution flow through said hydronic circuit stabilizer leg. Evaporative and stabilizer hydronic circuit legs are routed in parallel configuration with their respective modulation valves operating simultaneously relative to one another during the refrigeration circuit operation.
8. The system of claim 7 wherein a modulation valve is located on the hydronic circuit stabilizer leg at the first split junction, downstream of said stabilizer. Wherein a modulation valve located on the hydronic circuit evaporator leg at the second split junction downstream of said evaporator. Wherein at least one modulation valve is located on said third split junction at the air handler leg.
9. The system of claim 8 wherein said hydronic circuit air handler leg includes a third split junction downstream from said air handler, including an ice storage vessel return leg and a bypass leg with a modulation valve allowing a portion of hydronic solution delivery downstream of said ice storage vessel. Wherein at least one modulation valve located downstream of said ice storage vessel return leg allows combining of hydronic solution in proportion to said bypass hydronic circuit bypass leg.
10. The system of claim 1 wherein said VFD controlled hydronic pump of said hydronic circuit is located directly upstream of said ice storage vessel allowing for managing control of hydronic solution flow through said ice storage vessel.
11. The system of claim 1 where the chiller system control module hardware is implemented providing finite control of the chiller operation. Said system control module contains thermodynamic refrigerant state property tables utilized in the chiller operational efficiency.
12. The system of claim 11 wherein the system control module interfaces with instrumentation utilized in the performance efficiency of the refrigeration circuit and hydronic circuit.
13. The system of claim 1 where a pressure and temperature sensing devices located upstream of the compressor measures pressure and sensible temperature respectively. Wherein the pressure sensing device is read by the system control module and referenced to the refrigerant state property tables within memory. Wherein the pressure sensing device reading is utilized to determine the correlated refrigerant superheated saturation temperature. Wherein the obtained refrigerant superheated saturation temperature is mathematically compared with the ambient temperature sensing device read by the system control module. Wherein said refrigerant saturation temperature is compared mathematically to the said temperature sensing device reading by the system control module for equality.
14. The system of claim 13 wherein said refrigerant saturation temperature exceeds the ambient temperature sensing device above a predetermined value, the system control module provides a write command instruction modulating the motorized modulation valve of claim 3 associated with the hydronic circuit stabilizer leg to a greater open position. Wherein said ambient temperature sensing device reading compared mathematically to the refrigerant superheated saturation temperature is below a predetermined value, the modulation valve is throttled to the closed position.
15. The system of claim 1 where the absolute temperature difference between the temperature sensing device readings at the entry and exit of the ice storage vessel is monitored by the system control module on a regular interval. Wherein the system control module obtains the power input and power output readings of the compressor by means of a power monitoring device installed in the enhanced air conditioning chiller system of claim 1. Wherein the heat transfer capacity of the evaporator is stored within the memory of the system control module. Wherein the said values are evaluated mathematically to determine the required mass flow rate of the hydronic circuit. Wherein the VFD controlled hydronic pump is modulated to the required mass flow rate by the system control module to maximize the efficiency of the evaporator of the enhanced air conditioning chiller system of claim 1. Wherein said efficiency maximization enhances the refrigeration circuit.
16. The system of claim 15 wherein the second split junction of the hydronic circuit associated with the evaporator leg contains a hydronic solution flow measuring device upstream of the evaporator and a motorized modulation valve downstream of said evaporator. The hydronic flow measuring device serves as a confirmation by the system control module of the required mass flow rate of claim 15.
17. The system of claim 14 encompassing the stabilizer and evaporator, establishes finite control on a simultaneous basis through the system control module achieving improved efficiency of the enhanced air conditioning chiller system refrigeration cycle of claim 1.
18. The system of claim 1 wherein a pressure sensing device is located within the hydronic circuit. Wherein a VFD controlled hydronic pump is located on the hydronic circuit air handler leg. Wherein said pressure sensing device provides the system control module confirmation and control of the required mass flow rate through manufacturer hydronic solution pump curve tables stored within said system control module memory. Wherein the mass flow rate required by the hydronic circuit air handler(s) is stored within the system control module. Wherein the system control module compares the required mass flow rate of the hydronic solution within the hydronic circuit air handler leg with the said hydronic solution pump curve tables. Wherein the system control module manages the VFD associated with the hydronic pump to ensure the said mass flow rate. Wherein said pressure sensing device is located downstream of hydronic VFD pump. Wherein a hydronic solution flow measuring device is located upstream of ice storage vessel in the hydronic circuit air handler leg providing confirmation to the system control module of the said required mass flow rate.
19. The system of claim 1 wherein the enhanced air conditioning chiller system space/zone climate temperature control of claim 9 utilizes a temperature sensing device located upstream of ice storage vessel to maintain finite control of the temperature of the hydronic solution within the hydronic circuit air handler leg serving the air handlers by balancing the motorized modulation valves associated with the third split junction. Wherein the balancing of the motorized modulation valves is managed by the system control module.
20. The system of claim 1 wherein the refrigeration circuit and hydronic circuit associated with the air handler leg operate independently. Wherein independent operation is ensured by the shutdown, or closure, of the valves associated with the bypass leg and return leg modulation valves associated with the hydronic circuit air handler leg upon activation of the refrigeration circuit by the system control module. Wherein independent operation is ensured by the shutdown, or closure, of the motorized modulation valves associated with the hydronic circuit evaporator leg and stabilizer leg upon activation of the space/zone climate temperature control of claim 9 by the system control module. The system control module internal real time clock provides start and stop of the respective said operations based upon user stored values within the system control module.
Description
BRIEF DESCRIPTION OF THE DRAWINGS
[0062] FIG. 1 is a graphical representation of a conventional air conditioning chiller system 10 and its refrigeration and hydronic solution components, with industry standard load shift techniques employed. The dashed lines indicate the hydronic solution portion of a conventional chiller encompassing piping segments 05 through 10, whereas the solid line segments represent the refrigeration portion of the conventional chiller encompassing piping segments 01 through 04. The arrow symbols indicate direction of flow/travel for both the hydronic solution and the refrigerant.
[0063] FIG. 2 is a graphical representation of the operational components of the enhanced air conditioning chiller system 100, integrated with a conventional air conditioning chiller 10 of FIG. 1. FIG. 2 incorporates the addition of the patented sub-cooler, the Air Conditioning Companion Stabilizer referred to as the stabilizer 131, in series with the system fan/coil condenser 112. The dashed lines indicate the hydronic solution portion of the enhanced air conditioning companion chiller encompassing piping segments 05 through 11, including a first split junction, a second split junction, a third split junction, a stabilizer leg, an evaporator leg, and an air handler leg, whereas the solid line segments represent the air conditioning companion refrigeration loop components encompassing piping segments 01 through 04. FIG. 2 additionally features motorized hydronic valves utilized in the improved performance of the stabilizer 131 and evaporator 141. The arrow symbol indicates both refrigerant and hydronic solution paths of travel/flow.
[0064] FIG. 3 is a block diagram of those components of the enhanced air conditioning chiller system 100 integrated with those of a conventional air conditioning chiller system 10 of FIG. 1, including instrumentation associated with the controls necessary to the system operation. The dashed lines indicate the hydronic solution portion of an enhanced air conditioning chiller system 100 encompassing piping segments 05 through 11, including a first split junction, a second split junction, a third split junction, a stabilizer leg, an evaporator leg, and an air handler leg, whereas the solid line segments represent the enhanced air conditioning chiller system 100 refrigeration loop encompassing piping segments 01 through 04. The arrow symbol indicates both refrigerant and hydronic solution paths of travel/flow.
[0065] FIG. 4 is a graphical representation of the operational components of the enhanced air conditioning chiller system 110, integrated with a conventional air conditioning chiller system 10 of FIG. 1. FIG. 4 is typical of FIG. 2 with an addition of a hydronic pump operative during the space air conditioning companion chiller operation. The dashed lines indicate the hydronic solution portion of the enhanced air conditioning chiller system 100 encompassing piping segments 05 through 12, including a first split junction, a second split junction, a third split junction, a stabilizer leg, an evaporator leg, and an air handler leg, whereas the solid line segments represent the enhanced air conditioning chiller system 100 refrigeration loop encompassing piping segments 01 through 04. The arrow symbols indicate both refrigerant and hydronic solution path of travel/flow.
[0066] FIG. 5 is a block diagram reflects those components of an enhanced air conditioning chiller system 110 of FIG. 4, including instrumentation necessary to the controlling of the enhanced air conditioning chiller system 110 operation. The dashed lines indicate the hydronic solution portion of an enhanced air conditioning chiller encompassing piping segments 05 through 12, including a first split junction, a second split junction, a third split junction, a stabilizer leg, an evaporator leg, and an air handler leg, whereas the solid line segments represent the enhanced air conditioning chiller system 110 refrigeration loop encompassing piping segments 01 through 04. The arrow symbol indicates both refrigerant and hydronic solution path of travel/flow.
[0067] FIG. 6 is a block diagram illustrative of the operative components of the enhanced air conditioning chiller system 100 refrigeration loop, where the stabilizer 131 is shown integrated between the stabilizer leg of the hydronic solution loop and the refrigeration loop of a conventional air conditioning chiller system 10 of FIG. 1. The block diagram with focus of the stabilizer 131 is shown inclusive of its associated instrumentation necessary to optimize its operation. The dashed line indicates the hydronic solution loop of the enhanced air conditioning chiller system 100 encompassing piping segments 06 through 09. The solid lines reflect the refrigerant loop of the enhanced air conditioning chiller system 100 encompassing piping segments 01 through 03. The arrow symbols indicate both refrigerant and hydronic solution paths of travel/flow.
[0068] FIG. 7 is a flow chart illustrating the function of the enhanced air conditioning chiller system 100 refrigeration loop operation with focus on stabilizer 131 of FIG. 6 with its instrumentation necessary to controlling the efficiency of the enhanced air conditioning chiller system 100 operation. Arrows pointing towards the system control module represent read instructions from the instrumentation, while arrows pointing towards the instrumentation indicates write functions or commands to the instrumentation.
[0069] FIG. 8 is a block diagram illustrative of the operative components of the enhanced air conditioning chiller system 100 refrigeration loop, with focus on the evaporator 141, typical of evaporator 41 of FIG. 1. The block diagram with focus on evaporator 141 is shown integrated between the evaporator leg of the hydronic solution loop and the refrigeration loop, inclusive of its associated instrumentation necessary to its optimized operation. The dashed line indicates the hydronic solution loop of the enhanced air conditioning chiller system 100 encompassing piping segments 06, 07, 09, 10, and 11. The solid lines reflect the refrigerant loop of the enhanced air conditioning chiller system 100 encompassing piping segments 01 through 03. The arrow symbols indicate both refrigerant and hydronic solution paths of travel/flow.
[0070] FIG. 9 is a flow chart illustrating the function of the enhanced air conditioning chiller system 100 refrigeration loop operation with focus on evaporator 141 of FIG. 8 with its instrumentation necessary to controlling the efficiency of the enhanced air conditioning chiller system 100 operation. Arrows pointing towards the system control module represent read instructions from the instrumentation, while arrows pointing towards the instrumentation indicates write functions or commands to the instrumentation.
DESCRIPTION OF THE PREFERRED EMBODIMENT
[0071] FIG. 1 is a representation of prior art, reflecting a conventional air conditioning chiller system 10 with load shifting techniques employed through the means of an ice storage vessel 21. FIG. 1 hereafter is referred to as a conventional air conditioning chiller with its refrigeration loop components numerically labeled to include instrumentation and other typical features. The conventional air conditioning chiller system 10 refrigeration loop as shown by a solid line, numbered 01 through 04, undergoes a phase changes from superheated hot gas, to liquid, to vapor, defined as partially liquid and partially gaseous in composition, and completing the circuit as a cold superheated gas. The refrigeration loop is recognized as a non-reversible refrigeration compression cycle. The hydronic loop, utilizing a hydronic heat transfer medium, referred to as a hydronic solution, such as a glycol mixture or other solution amendable to heat transfer, is identified by a dashed line with piping segments labeled 05 through 10. The refrigeration loop is isolated from the hydronic solution loop, only interfacing by way of evaporator 41 and its integrated heat exchanger. The closure or opening of motorized modulation valves 52, 62, 32 and 42 serve to control hydronic solution flow during the operation of the refrigeration loop and the hydronic solution loop.
[0072] The operation of the conventional air conditioning chiller 10 is defined by two independently operated cycles, the charging cycle and the space conditioning cycle. The refrigeration loop operation during the charging cycle is defined by the operation of the refrigeration equipment including compressor 11, fan/coil condenser 12, expansion valve 13, and the integration of evaporator 41. The space conditioning cycle is defined by operation of air handler 14. Hydronic solution pump 22 is operative during both cycles, and the ice storage vessel 21 is utilized during both cycles. Ice storage vessel 21 is utilized during the charging cycle as the load source to the evaporator 41, and as a load sink during the space conditioning cycle to air handler 14. Traditionally the operation of the two independent cycles are controlled by a time clock contained within the system control module.
[0073] During the charging cycle, the conventional air conditioning chiller system 10 is tasked with charging the ice storage vessel 21. The refrigerant compressor 11, downstream of evaporator 41, provides the work necessary to support the charging cycle by doing work on the cold refrigerant gas emitted from evaporator 41 through piping element 04 and producing a superheated gas at high pressure to fan/coil condenser 12 through piping segment 01. At fan/coil condenser 12, the refrigerant is interfaced with the ambient air through the use of a fan and an integrated heat exchanger, reducing the temperature of the refrigerant while the pressure remains constant, a sensible temperature change. As the temperature is reduced to the demarcation point, the refrigerant enters a latent phase change process where temperature and pressure are held constant, while the refrigerant transitions from a very hot gas to a hot liquid refrigerant. Upon completion of the latent phase change of the refrigerant, the refrigerant may undergo additional sensible temperature reduction prior to exiting the fan/coil condenser 12. The refrigerant exits fan/ coil condenser 12 through piping segment 02 as liquid refrigerant having undergone a complete phase change under optimal or ideal conditions. This phase change is made possible by drawing cooler ambient air across the fan/coil condenser 12, causing the air to absorb heat energy from the refrigerant received from compressor 11, resulting in a cooled gaseous liquid, or vapor, refrigerant exiting fan/coil condenser 12, or ideally a complete liquid. In order to complete this phase change within the fan/coil condenser 12, it is well established in the refrigeration industry that the refrigerant must enter the fan/ coil condenser at a minimum of 15 degrees above the ambient temperature for single pass condenser coils and 30 degrees for double pass condenser coils. Expansion valve 13 can be either mechanical or electronic, and is located downstream of fan/coil condenser 12 between piping segments 02 and 03. Under optimal conditions, expansion valve 13 receives a hot liquid refrigerant at a high pressure from fan/coil condenser 12 through piping segment 02, at a temperature no less than the ambient temperature due to the second law of thermodynamics, and discharges to the evaporator 41 through piping segment 03 as a low temperature vaporous refrigerant at a low pressure. Evaporator 41, downstream of expansion valve 13, is shared mutually by both the refrigeration and hydronic solution loops through its integrated heat exchanger. Evaporator 41 is tasked with the partial phase change of refrigerant, received from expansion valve 13, from a vapor to a complete superheated gas at a low temperature and pressure. The evaporator receives the required relatively warm hydronic solution from the ice storage vessel 21 as a result of the hydronic solution picking up heat energy from the ice storage vessel 21 static reservoir through its integrated heat exchanger. The integrated heat exchanger within evaporator 41 allows heat energy to be transferred from the warm hydronic solution to the very cold refrigerant received from expansion valve 13, resulting in the hydronic solution exiting the evaporator 41 in a much colder state, conducive to the freezing of the static reservoir of the ice storage vessel 21, and the refrigerant exiting the evaporator 41 in a much warmer, fully gas state. The cooled hydronic solution is then directed through piping segments 10 and 06 to the integrated heat exchanger of the ice storage vessel 21 where heat from the static reservoir is absorbed by the hydronic solution continuously until the static reservoir is in a frozen state. The hydronic fluid is continuously circulated through piping segments 06 through 10 by the hydronic pump 22 during the operation of the charging cycle. The charging cycle continues until the completed freezing of the static reservoir of the ice storage vessel 21.
[0074] During the space conditioning cycle the conventional air conditioning chiller system 10 is tasked with maintaining the space or zone temperature associated with air handler 14. The load source of the space conditioning cycle is the air handler 14, which may be a single air handler or a series or array of air handlers. The space conditioning cycle maintains the space or zone temperature by drawing warm air from the conditioned space or zone across its fan/coil assembly that interfaces the conditioned space or zone air with the cold hydronic solution received from ice storage vessel 21 through pipe element 07, depositing the heat from the space or zone to the hydronic solution. The hydronic solution is circulated by a hydronic pump 22, or multiple pumps, upstream of air handler 14, that is managed through a variable frequency drive, hereafter referred to as a VFD. Modulation of the drive frequency or speed is determined by the heat load demands emanating from space or zone thermostat, or other similar temperature sensing device, activating the air handler 14 fan operation. By the operation of pump 22, the elevated temperature hydronic solution exiting air handler 14, through pipe elements 05 and 06, deposits heat energy from the space or zone to the static reservoir of the ice storage vessel 21 through its integrated heat exchanger. The motorized modulation valve 52 allows a metered amount of hot or warmed hydronic solution emitted from the air handler 14 to be bypassed from the ice storage vessel 21 and deposited downstream of the ice storage vessel 21, mixing with the hydronic solution within piping segment 07, prior to entering air handler 14 to ensure the supply temperature to the air handler matches manufacturer and design specifications. Motorized modulation valve 52 is modulated to allow more or less hydronic solution to bypass ice storage vessel 21 based upon the conventional air conditioning chiller control system monitoring the supply temperature within piping segment 07 by way of a temperature sensing device. The motorized modulation valve 62 operates in opposing manner to motorized modulation valve 52, allowing the remainder of the warm or hot hydronic solution emanating from the air handler 14 to return to the ice storage vessel 21, where the solution can be cooled and heat deposited to the static reservoir heat exchanger component, prior to exiting through piping segment 07. The space conditioning cycle is only operative when the thermostat or other temperature measuring devices indicates the requirement of cooling the space or zone.
[0075] FIG. 2 is a schematic representation of the operational components of the enhanced air conditioning chiller system 100, integrated with a conventional air conditioning chiller system 10 of FIG. 1. The enhanced air conditioning chiller system 100 includes the same components typical of the conventional air conditioning chiller system 10, including the evaporator 141 being like that of evaporator 41, the compressor 111 being like that of compressor 11, fan/coil condenser 112 being like that of fan/coil condenser 12, air handler 114 like that of air handler 14, ice storage vessel 121 like that of ice storage vessel 21, and hydronic pump 122 like that of hydronic pump 22. FIG. 2 adds to the conventional air conditioning system 10 by the addition of a sub-cooler, the patented Air Conditioning Companion Stabilizer System of Patent US10,168,091B2, hereafter referred to as stabilizer 131, along with the necessary control system and instrumentation, in series or downstream of the system fan/coil condenser 112. The stabilizer 131 is positioned to enhance and complete, as required, the condensing circuit unique to the enhanced air conditioning chiller system 100. The solid line segments represent the refrigeration loop including piping segments 01 through 04 typical of the conventional air conditioning chiller system 10, where the dashed lines indicate the hydronic solution loop of the enhanced air conditioning chiller system 100 including piping segments 05 through 11, modified from the conventional air conditioning chiller system 10. FIG. 2 shows the path of travel and flow direction of refrigerant and hydronic solution indicated by arrow symbols on the piping segments connecting their associated components. Components contained within the refrigeration and hydronic solution loops are additionally numerically referenced. FIG. 2 additionally features an additional modulating motorized valve 132 and motorized modulating valve 142 of FIG. 1, indicated downstream of the stabilizer 131 and evaporator 141 respectively, utilized in the finite control of hydronic solution to and from their respective components. The enhanced air conditioning chiller system 100 features an ice storage vessel 121 positioned downstream of the hydronic solution hydronic pump 122, typical of conventional air conditioning chiller system 10 and is tasked with the function of load shifting operations as seen in FIG. 1. The ice storage vessel 121 is designed to facilitate storage of ice or solid brine type solution in a static reservoir. It is contemplated that other methods of energy storage may be utilized in place of the traditional ice storage vessel to accomplish the same load shifting operations. The enhanced air conditioning chiller system 100 is differentiated from the conventional air conditioning chiller system 10 in that the distribution of the hydronic solution, upon exiting the ice storage vessel has two parallel paths of travel to the evaporator 141 and to the stabilizer 131. Evaporator 141 is charged with the function of freezing the water or brine solution contained within the static reservoir of the ice storage vessel 121, which in turn acts as the load source for the evaporator 141. The stabilizer 131, upstream of the expansion valve 113 and downstream of fan/coil condenser 112, receives relatively low temperature hydronic solution from the ice storage vessel 121 by way of hydronic pump 122 operation. This reduced temperature hydronic solution entering stabilizer 131 interfaces with the hot refrigerant exiting fan/ coil condenser 112, ideally a liquid, through a brazed plate heat exchanger or similar assembly, resulting in a lower temperature liquid refrigerant exiting the stabilizer 131 prior to entering expansion valve 113. It is contemplated in conditions where the condensing circuit is operating at less than ideal conditions, the stabilizer 131 can additionally act as an enhancement to complete the condensing of the refrigerant in the case that the fan/coil condenser 112 is unable to fully condense the refrigerant prior to exiting, resulting in a complete liquid refrigerant as well as artificially lowering the temperature of the refrigerant. The parallel hydronic solution loop paths shown within FIG. 2 are subsequently combined prior to returning to the ice storage vessel 121 where it is interfaced with its static reservoir. The enhanced air conditioning chiller system 100 control system guarantees that the hydronic solution returns to the ice vessel storage 121 at a temperature necessary to the formation of ice or other solid energy storage medium through temperature sensing devices or other energy management controls. The stabilizer 131 is a brazed plate heat exchanger, ideally operating with both the refrigerant and hydronic solution in a liquid state, whereas the evaporator 141 is a phase change heat exchanger, operative to complete the transition of refrigerant vapor to gas prior to allowing the refrigerant to enter the compressor 111.
[0076] The hydronic solution loop of FIG. 2 provides cooling to the conditioned space as described in FIG. 1. The enhanced air conditioning chiller system 100 refrigeration loop of FIG. 2 is designed to operate when ambient temperatures allow for optimal operation of said refrigeration loop. The enhanced air conditioning chiller system 100 refrigeration loop operates during off peak power usage hours which traditionally coincide with late evening to early morning hours, when the ambient temperatures are at their lowest. The enhanced air conditioning chiller system 100 space conditioning cycle of FIG. 2 is operative when the space or zone is occupied or requires cooling due to other conditions present. Isolation of the hydronic portion of the space conditioning loop from the hydronic portion of the refrigeration loop is accomplished by closing motorized modulation valves 152 and 162 during space conditioning operation, and opening motorized modulation valves 132 and 142. Isolation of the enhanced air conditioning hydronic refrigeration loop from the hydronic space conditioning loop is accomplished by the closing of motorized modulation valves 132 and 142 during refrigeration loop operation, and opening motorized modulation valves 152 and 162.
[0077] FIG. 3 is a block diagram of those components of an enhanced air conditioning chiller system 100 of FIG. 2 including instrumentation affiliated with the system control module necessary to the enhanced air conditioning chiller system 100 operation. The solid line represent the refrigeration loop piping segments 01 through 04, where the dashed lines indicate the hydronic solution loop piping segments 05 through 11. The arrow symbol indicates path of flow for both the refrigerant piping segments and the hydronic solution piping segments of the enhanced air conditioning chiller system 100. Pressure sensing device 207 and temperature sensing device 207 are located downstream of the compressor 111, providing feedback signals to the system control module measuring pressure and temperature respectively to provide finite control of the hydronic solution flow rate, volume, and temperature to stabilizer 131. The rate of flow provided to stabilizer 131 is managed through the downstream motorized modulating valve 132 by the system control module. The stabilizer 131 is positioned downstream of the fan/coil condenser 112 and receives warm or hot liquid refrigerant under ideal conditions due to a complete condensing process obtained from fan/coil condenser 112. Upstream of the stabilizer 131 is located a pressure sensing device with accompanying temperature sensing device 205, measuring pressure and temperature respectively by the system control module. Downstream of the stabilizer 131 is located pressure sensing device 210 and temperature sensing device 210, indicating the pressure and temperature of the refrigerant after being interfaced with the relatively cool hydronic solution received from ice storage vessel 121 within said stabilizer 131 heat exchanger. The interfacing of the relatively cool hydronic solution with the hot refrigerant within the heat exchanger of stabilizer 131 results in a lower temperature liquid refrigerant at the exit of stabilizer 131. The temperature of the refrigerant as it exits stabilizer 131 will be lowered beyond the temperature that can otherwise be obtained by the fan/coil condenser 112 alone, enhancing the entire charging cycle operation. The lower temperature refrigerant then enters expansion valve 113, where it is expanded rapidly into a very low pressure and temperature vapor state. The expansion valve 113 is contemplated to be of electronic type rather than mechanical due to increased flexibility and control, including but not limited to control of the superheat value, and is located downstream of the stabilizer 131. The electronic expansion valve 113 as embodied within the enhanced air conditioning chiller system 100 of FIG. 2 and FIG. 3 includes an integrated control module that contains tabulated refrigerant tables, and utilizes its associated pressure sensing device and temperature sensing device 200 positioned downstream of evaporator 141 to enable control of the refrigerant flow rate entering the evaporator 141. The cold refrigerant from the electronic expansion valve 113 that is interfaced with a warmer hydronic solution received from ice storage vessel 121 within evaporator 141 undergoes a partial phase change in order to completely transform refrigerant vapor to a gas phase prior to its entry into the compressor 111. The electronic expansion valve and its associated controls and instrumentation work to ensure only gas refrigerant enters compressor 111 in the same manner as the conventional air conditioning chiller system 10. Hydronic solution loop monitoring device 300, contemplated to be a flow meter or similar device, is positioned downstream of evaporator 141 to measure the flow rate of hydronic solution to evaporator 141, providing a feedback signal to the system control module. Motorized modulation valve 142, downstream of evaporator 141, provides flow control through evaporator 141 by the system control module. Motorized modulation valves 142 and 132 are in the open, full or partial, position when the charging cycle is operative. Motorized modulation valves 142 and 132 are in the closed position when the charging cycle is inoperative or not needed. Motorized modulation valves 152 and 162 are in the open, full or partial, position when the space conditioning cycle is operative. Motorized modulation valves 152 and 162 are in the closed position when the space conditioning cycle is inoperative. Pressure sensing device and temperature sensing device 215, positioned upstream of hydronic pump 122, provide for pressure and temperature monitoring by the system control module of the hydronic solution exiting the evaporator 141 and stabilizer 131 when the charging cycle is operative, and additionally the pressure and temperature of the hydronic solution when the space conditioning cycle is operative. Hydronic pump 122 is managed by a variable frequency drive, or VFD. Frequency, or operational run speed, of the VFD associated with hydronic pump 122 dictates the hydronic solution flow rate. The system control module manages the frequency of the VFD, and in turn the flow rate, of the hydronic solution based upon a pressure/flow rate table or formula provided by the manufacturer of hydronic pump 122. The system control module is programmed with the associated pressure/flow rate table for the installed hydronic pump 122 and utilizes the table in determining the desired VFD frequency. The hydronic pump 122 is positioned upstream of the ice storage vessel 121. When the charging cycle is operative, the ice storage vessel 121 receives cold, sub-freezing temperature hydronic solution from evaporator 141. The hydronic solution from evaporator 141 is mixed with warmer hydronic solution from stabilizer 131 prior to entering ice storage vessel 121. The system control module monitors temperature sensing device 215 to ensure that the combined hydronic solution temperature remains at sub-freezing temperatures, or a temperature conducive to the freezing of the static reservoir and its storage medium. The cold hydronic solution that enters the ice storage vessel 121 picks up heat energy from the warm static reservoir, resulting in a colder static reservoir until the static reservoir is frozen. When the space conditioning cycle is operative, air handler 114, either a single or multiple air handlers in an array, receives cold hydronic solution from ice storage vessel 121, where it is interfaced with the warm ambient air through the use of a mechanical fan through an integrated heat exchanger, resulting in warm hydronic solution exiting the air handler 114. Ice storage vessel 121 receives the warmed hydronic solution from air handler 114 where the frozen static reservoir absorbs heat energy from the hydronic solution, resulting in cold hydronic solution being returned to air handler 114. Downstream of the air handler 114 are located two motorized modulation valves 152 and 162 ensuring proper mixing of the hydronic solution to piping segment 07 prior to the entry of air handler 114. The bypass motorized modulation valve 152 is opened to a position, calculated by the system control module, to allow warm hydronic solution emitted from the air handler 114 to bypass ice storage vessel 121, mixing with the cold hydronic solution exiting ice storage vessel 121 ensuring the proper temperature required by air handler 114. Motorized modulation valve 162 is opened to a position, calculated by the system control module, to allow the remainder of the warm hydronic solution from air handler 114 to return to the ice storage vessel 121. Temperature sensing device 220, downstream of the ice storage vessel, measures temperature of the hydronic solution prior to the entry of air handler 114, and is utilized by the system control module to modulate motorized valves 152 and 162, providing an ideal temperature of hydronic solution in order to maintain optimal performance of air handler 114. Upstream of ice storage vessel 121 is located a temperature sensing device 225 that is monitored by the system control module in order to manage the hydronic solution temperature profile entering the ice storage vessel 121. Downstream of the ice stage vessel 121 is located a hydronic loop monitoring device 305, contemplated to be a flow meter or similar device, monitored by the system control module to verify proper hydronic solution flow rates as required by air handler 114 as determined by the manufacturer.
[0078] FIG. 4 is a schematic representation of FIG. 2 with the addition of hydronic pump 123, either a single or multiple pumps, downstream of air handler 114, either a single or multiple air handlers. The secondary hydronic pump 123 is provided to exclusively serve the space conditioning cycle. In this configuration, hydronic pump 122 exclusively serves the charging cycle. The solid line segments represent the refrigeration loop encompassing piping segments 01 through 04, where the dashed lines indicate the hydronic solution portion encompassing piping segments 05 through 12. The arrow symbol indicates path of flow for both the refrigerant piping segments and the hydronic solution piping segments of the enhanced air conditioning chiller. Both loop entries to the ice storage vessel 121 are shown combined prior to the ice storage vessel 121 at piping segments 06 and 12. The independent loops are isolated from each other by the opening and closing of modulation valves 132, 142, 152, and 162 and enabling and disabling of hydronic pumps 122 and 123 in accordance with the programming of the system control module as described in FIG. 2.
[0079] FIG. 5 is a block diagram of those components of an enhanced air conditioning chiller system 110 of FIG. 4 including instrumentation associated with the system control module necessary to operation. The solid line represents the refrigeration loop encompassing piping segments 01 through 04, where the dashed lines indicate the hydronic solution loop encompassing piping segments 05 through 12. The arrow symbol indicates path of flow for both the refrigerant piping segments and the hydronic solution piping segments. FIG. 5 is a schematic representation of FIG. 4 with the addition of hydronic pump 123, a single or multiple pumps, downstream of air handler 114, either a single or multiple air handlers. The secondary hydronic pump 123 is provided to exclusively serve the space conditioning cycle. In this configuration, hydronic pump 122 exclusively serves the charging cycle as described in FIG. 1. The independent loops are isolated from each other by the opening and closing of modulation valves 132, 142, 152, and 162 and enabling and disabling of hydronic pumps 122 and 123 in accordance with the programming of the system control module as described in FIG. 2.
[0080] FIG. 6 is a diagram illustrative of the operative components of the enhanced air conditioning chiller system 100 and 110 charging cycle where the patented stabilizer 131 is shown in relation to the fan/coil condenser 112 and associated instrumentation including temperature sensing devices 205, 207, and 210. The controls necessary to the optimization of enhanced air conditioning chiller system 100 and 110 efficiency are comprised of a hydronic pump 122 controlled by a Variable Frequency Drive, or VFD, a flow measurement device 300, ice storage vessel 121, temperature measuring devices 215 and 220, and motorized modulation valve 132. Control of the hydronic solution flow rate to stabilizer 131 is managed by the system control module through the opening and closing of motorized modulation valve 132. The opening and closing of motorized modulation valve 132 by the system control module is based upon pressure and temperature sensing device 207, located upstream of fan/coil condenser 112 and stabilizer 131. The pressure sensing device 207 allows the system control module to access and correlate the pressure with a saturation temperature within the refrigerant tables, accommodating glide or drift as appropriate for the refrigerant, which is then compared with the ambient temperature to ensure that the saturation temperature is at least 15/30 degrees above the ambient temperature to ensure complete condensing through the fan/ coil 112. The correlated saturation temperature is additionally compared to the sensible temperature read by temperature sensing device 207. Based upon this comparison, the system control module opens and closes modulation valve 132 appropriately. The VFD associated with hydronic pump 122 is managed by the system control module. During the charging cycle operation, the hydronic solution emanating from the ice storage vessel 121 at a relatively cold temperature gets warmed by being interfaced with the hot refrigerant that enters stabilizer 131 received from fan/coil condenser 112. Temperature sensing device 220, located downstream of ice storage vessel 122, is monitored by the system control module to assess the temperature of hydronic solution discharged from ice storage vessel 121 after interfacing with the relatively cool static reservoir through its integrated heat exchanger. Temperature sensing device 215, located upstream of the ice storage vessel 121, is monitored by the system control module to assess the temperature of the hydronic solution as it enters ice storage vessel 121. Temperature sensing device 205, located downstream of fan/coil condenser 112, is monitored by the system control module to assess the temperature of the refrigerant discharged from fan/coil condenser 112, whereas thermocouple 210, located downstream of stabilizer 131, measures the temperature of refrigerant at the discharge of stabilizer 131.
[0081] FIG. 7 depicts a block diagram representative of FIG. 6 communications with instrumentation and equipment utilized in the optimization of the enhanced air conditioning chiller system 100 utilizing stabilizer 131 made possible through the system control module. The system control module houses refrigerant tables including various properties of refrigerants utilized in the control of stabilizer 131, including but not limited to super heat pressure and temperature correlation tables. The arrows indicate input and output signals to and from the system control module, with an arrow pointing towards the system control module indicating an input or feedback signal, and an arrow pointing toward the device indicating an output signal from the system control module.
[0082] Temperature sensing device and pressure sensing device 207 located on piping segment 01 of FIG. 3, provides a measure of temperature and pressure respectively to the system control module. The temperature signal is typically based upon a resistance feedback loop and the pressure is communicated on the basis of a feedback signal to the system control module. The system control module obtains the pressure reading from pressure sensing device 207 and calculates the enthalpy, or energy available, and superheat saturation temperature based upon internal refrigerant properties tables. The superheat saturation temperature calculated signifies the transition point of hot gas refrigerant to its liquid state. The system control module additionally calculates the sub-cool temperature to identify the completion of the refrigerant gas transition to a complete liquid state, obtained from the internal refrigerant properties tables. It is well established by the mechanical/HVAC industry that the superheat saturation temperatures of the refrigerant exiting the compressor 111 prior to entering fan/coil condenser 112 must be 15 degrees greater than the ambient or outside temperature in order to achieve a full transition of the refrigerant from a gas state to a liquid state as it exits the condenser 112. The sensible, or physical, temperature determined by temperature sensing device 207 should be ideally equal to the superheat saturation temperature to achieve complete saturation of the refrigerant, or transition from a complete gas to a complete liquid, for single composition refrigerants. Refrigerants having a composition or mixture of multiple refrigerants require consideration for glide, or temperature differences caused as a result of mixing refrigerants, associated with the sub-cool value obtained from the refrigerant manufacturer. The system control module is programmed to maintain the refrigerant temperature at a point where the difference between saturation and sensible refrigerant temperatures match the glide value provided by the refrigerant manufacturer. The calculated refrigerant saturation temperature is compared to sensible refrigerant temperature associated with temperature sensing device 207 by the system control module, and in turn opens and closes motorized modulation valve 132 to a calculated value. The modulation of valve 132 adjusts the flow rate of the hydronic solution to stabilizer 131, in turn optimizing the charging cycle of the enhanced air conditioning chiller system 100.
[0083] The system control module monitors the hydronic solution emanating from the ice storage vessel 121 by temperature sensing device 220. Relatively low temperature glycol solution emanating from the ice storage vessel 121 is utilized by the stabilizer 131 to artificially reduce the temperature of the refrigerant that exits the fan/coil condenser 112. The temperature of the glycol solution exiting stabilizer 131 is monitored by temperature sensing device 215.
[0084] The system control module calculates both the superheat saturation temperature and sub-cool saturation temperatures using the integrated refrigeration properties tables. The system control module is able to identify points of demarcation associated with the transition of gas refrigerant to a complete liquid state, allowing it to determine the upper and lower values for enthalpy (H), or a thermodynamic quantity equivalent to the total heat content of a system. The absolute difference between the upper and lower enthalpy values reflects the amount of heat energy (Q) rejected to the ambient air by the fan/coil condenser 112. The system control module determines the sub-cool saturation temperature and the physical temperature of liquid refrigerant exiting stabilizer 131, allowing it to be able to obtain the upper and lower enthalpy values from the refrigerant properties tables contained within the system control module. The absolute difference between the upper and lower enthalpy values indicates the amount of additional heat energy (Q) removal by patented stabilizer 131.
[0085] FIG. 8 is a diagram illustrative of the operative components of the enhanced air conditioning chiller system 100 or 110 charging cycle where the evaporator 141 is operative, including the instrumentation required to monitor and optimize evaporator 141 and compressor 111 performance is shown, including temperature sensing device and pressure sensing devices 200 and 210. The controls necessary to the optimization of evaporator 141 efficiency are comprised of a hydronic pump 122 controlled by a Variable Frequency Drive, or VFD, a flow measurement device 300, ice storage vessel 121, temperature sensing devices 215 and 220, and motorized modulation valve 142.
[0086] The system control module maintains modulation valve 142 in the open position in order to maximize the volume of hydronic solution received by evaporator 141 during the charging cycle. Flow measuring device 300 is monitored by the system control module in order to validate the proper flow required by evaporator 141. The system control module manages the variable frequency drive that operates hydronic pump 122 to a flow rate value as deemed appropriate through the system control module programming to optimize the performance of evaporator 141 and ice storage vessel 121. Temperature measuring device 215 and 220 are monitored by the system control module to confirm the hydronic solution temperatures entering and exiting ice storage vessel 121, ensuring the proper operation of the heat exchanger elements within the ice storage vessel 121 and evaporator 141. Temperature sensing device and pressure sensing devices 200 is monitored directly by the electronic expansion valve 113 integrated control panel, which is read by the system control module. Temperature sensing device and pressure sensing device 210 is monitored by the system control module to ensure that the temperature of refrigerant entering evaporator 141 is in a sub freezing temperature state in order to provide the required heat exchange with the warm hydronic solution received from ice storage vessel 121 and subsequently to provide sub freezing temperature hydronic solution to the static reservoir of the ice storage vessel 121. The compressor 111 is equipped with a power monitoring device, with an output value of power to the system control module. With the power consumption of the compressor 111 determined, the system control module is able to compare the power consumption of the compressor 111 and that of the evaporator 141, adjusting various instrumentation and controls in order to minimize the power differential between them allowing the charging cycle of the enhanced air conditioning chiller system 100 or 110 to operate at maximum efficiency. The power monitoring device of compressor 111 additionally allows the system control module to calculate system performance, commonly referred to as EER, or Energy Efficiency Ratio.
[0087] FIG. 9 depicts a block diagram representative of FIG. 8 communications with instrumentation and equipment utilized in the optimization of evaporator 141. The system control module houses refrigerant tables including various properties of refrigerants utilized in the optimized control of the evaporator 141, including but not limited to super heat pressure and temperature correlation tables. The arrows indicate input and output signals to and from the system control module, with an arrow pointing towards the system control module indicating an input signal, and an arrow pointing toward the device indicating an output signal from the system control module.
[0088] Temperature sensing device and pressure sensing device 200 are monitored by the system control module for temperature and pressure respectively. The system control module obtains the pressure reading from pressure sensing device 200 and calculates the enthalpy, or energy available, and refrigerant superheat saturation temperature based upon internal refrigerant properties tables. The refrigerant superheat saturation temperature calculated signifies the transition point of the cold vapor refrigerant to its complete gas state. The refrigerant transition process completion is identified by the system control module when the reading from the temperature sensing device 200 is between 1 and 5 degrees above the calculated refrigerant superheated temperature value.
[0089] The hydronic solution emanating from the ice storage vessel 121, upstream of stabilizer 141, is monitored by temperature sensing device 220 by the system control module. The temperature of the hydronic solution exiting stabilizer 141 integrated heat exchanger is monitored by temperature sensing device 215 to ensure sub-freezing temperature hydronic solution required to charge the static reservoir of the ice storage vessel 121.
[0090] Motorized modulation valve 142 is maintained at a 100% open position through the system control module during the entirety of the charging cycle. Hydronic pump 122, downstream of motorized modulation valve 142, is controlled by a variable frequency drive (VFD). The VFD is controlled by the system control module to maintain and set the hydronic solution flow rate required by evaporator 141. The system control module determines the appropriate flow rate through a mathematical formula, with validation of flow rate by reading flow monitoring device 300 at a regular interval.
[0091] Consideration is made by the system control module to accommodate the effect of the flow rate of hydronic solution by stabilizer 131. Upon the opening or closing of the motorized modulation valve 132, the system control module reads flow monitoring device 300 on a regular interval to ensure proper glycol solution flow rate to evaporator 141. Additionally, as the system control module makes adjustments to the VFD controlling hydronic pump 122, consideration is given to a potential delay in response from flow monitoring device 300, and allows a pre-determined timed delay between adjustments being made to the VFD through the system control module.
[0092] FIG. 2 is a schematic representation of the operational components of the enhanced air conditioning chiller system 100, integrated with a conventional air conditioning chiller system 10 of FIG. 1 in accordance with a first embodiment. The enhanced air conditioning chiller system 100 includes the same components typical of the conventional air conditioning chiller system 10, including the evaporator 141 being like that of evaporator 41, the compressor 111 being like that of compressor 11, fan/coil condenser 112 being like that of fan/coil condenser 12, air handler 114 like that of air handler 14, ice storage vessel 121 like that of ice storage vessel 21, and hydronic pump 122 like that of hydronic pump 22. FIG. 2 adds to the conventional air conditioning system 10 by the addition of a sub-cooler, the patented Air Conditioning Companion Stabilizer System of Patent US10,168,091B2, hereafter referred to as stabilizer 131, along with the necessary control system and instrumentation, in series or downstream of the system fan/coil condenser 112. The stabilizer 131 is positioned to enhance and complete, as required, the condensing circuit unique to the enhanced air conditioning chiller system 100. The solid line segments represent the refrigeration loop including piping segments 01 through 04 typical of the conventional air conditioning chiller system 10, where the dashed lines indicate the hydronic solution loop of the enhanced air conditioning chiller system 100 including piping segments 05 through 11, modified from the conventional air conditioning chiller system 10. FIG. 2 shows the path of travel and flow direction of refrigerant and hydronic solution indicated by arrow symbols on the piping segments connecting their associated components. Components contained within the refrigeration and hydronic solution loops are additionally numerically referenced. FIG. 2 additionally features an additional modulating motorized valve 132 and motorized modulating valve 142 of FIG. 1, indicated downstream of the stabilizer 131 and evaporator 141 respectively, utilized in the finite control of hydronic solution to and from their respective components. The enhanced air conditioning chiller system 100 features an ice storage vessel 121 positioned downstream of the glycol solution hydronic pump 122, typical of conventional air conditioning chiller system 10 and is tasked with the function of load shifting operations as seen in FIG. 1. The ice storage vessel 121 is designed to facilitate storage of ice or solid brine type solution in a static reservoir. It is contemplated that other methods of energy storage may be utilized in place of the traditional ice storage vessel to accomplish the same load shifting operations. The enhanced air conditioning chiller system 100 is differentiated from the conventional air conditioning chiller system 10 in that the distribution of the hydronic solution, upon exiting the ice storage vessel has two parallel paths of travel to the evaporator 141 and to the stabilizer 131. Evaporator 141 is charged with the function of freezing the water or brine solution contained within the static reservoir of the ice storage vessel 121, which in turn acts as the load source for the evaporator 141. The stabilizer 131, upstream of the expansion valve 113 and downstream of fan/coil condenser 112, receives relatively low temperature hydronic solution from the ice storage vessel 121 by way of hydronic pump 122 operation. This reduced temperature hydronic solution entering stabilizer 131 interfaces with the hot refrigerant exiting fan/coil condenser 112, ideally a liquid, through a brazed plate or similar assembly, resulting in a lower temperature liquid refrigerant temperature exiting the stabilizer 131 prior to entering expansion valve 13. It is contemplated in conditions where the condensing circuit is operating at less than ideal conditions, the stabilizer 131 can additionally act as an enhancement to complete the condensing of the refrigerant in the case that the fan/coil condenser 112 is unable to fully condense the refrigerant prior to exiting, resulting in a complete liquid refrigerant as well as artificially lowering the temperature of the refrigerant. The parallel hydronic solution loop paths shown within FIG. 2 are subsequently combined prior to returning to the ice storage vessel 121 where it is interfaced with its static reservoir. The enhanced air conditioning chiller system 100 control system guarantees that the hydronic solution returns to the ice vessel storage 121 at a temperature necessary to the formation of ice or other solid energy storage medium through temperature sensing devices. The stabilizer 131 is a brazed plate heat exchanger, ideally operating with both mediums in a liquid state, whereas the evaporator 141 is a phase change heat exchanger, operative to complete the transition of refrigerant vapor to gas prior to allowing the refrigerant to enter the compressor 111.
[0093] The hydronic solution loop of FIG. 2 provides cooling to the conditioned space as described in FIG. 1. The enhanced air conditioning chiller system 100 refrigeration loop of FIG. 2 is designed to operate when ambient temperatures allow for optimal operation of said refrigeration loop. The enhanced air conditioning chiller system 100 refrigeration loop operates during off peak power usage hours which traditionally coincide with late evening to early morning hours, when the ambient temperatures are at their lowest. The enhanced air conditioning chiller system 100 space conditioning cycle of FIG. 2 is operative when the space or zone is occupied or requires cooling due to other conditions present. Isolation of the hydronic portion of the space conditioning loop from the hydronic portion of the refrigeration loop is accomplished by closing motorized modulation valves 152 and 162 during space conditioning operation, and opening motorized modulation valves 132 and 142. Isolation of the enhanced air conditioning hydronic refrigeration loop from the hydronic space conditioning loop is accomplished by the closing of motorized modulation valves 132 and 142 during refrigeration loop operation, and opening motorized modulation valves 152 and 162.
Alternate Embodiment
[0094] FIG. 4 is a schematic representation of FIG. 2 with the addition of hydronic pump 123, either a single or multiple pumps, downstream of air handler 114, either a single or multiple air handlers in accordance with a second embodiment. The secondary hydronic pump 123 is provided to exclusively serve the space conditioning cycle. In this configuration, hydronic pump 122 exclusively serves the charging cycle. The solid line segments represent the refrigeration loop encompassing piping segments 01 through 04, where the dashed lines indicate the hydronic solution portion encompassing piping segments 05 through 12. The arrow symbol indicates path of flow for both the refrigerant piping segments and the hydronic solution piping segments of the enhanced air conditioning chiller. Both loop entries to the ice storage vessel 121 are shown combined prior to the ice storage vessel 121 at piping segments 06 and 12. The independent loops are isolated from each other by the opening and closing of modulation valves 132, 142, 152, and 162 and enabling and disabling of hydronic pumps 122 and 123 in accordance with the programming of the system control module as described in FIG. 2.
[0095] This disclosure is provided to reveal a preferred embodiment of the invention and a best mode for practicing the invention. Having thus described the invention in this way, it should be apparent that various different modifications can be made to the preferred embodiment without departing from the scope and spirit of this invention disclosure. When embodiments are referred to as “exemplary” or “preferred” this term is meant to indicate one example of the invention, and does not exclude other possible embodiments. When structures are identified as a means to perform a function, the identification is intended to include all structures which can perform the function specified. When structures of this invention are identified as being coupled together, such language should be interpreted broadly to include the structures being coupled directly together or coupled together through intervening structures. Such coupling could be permanent or temporary and either in a rigid fashion or in a fashion which allows pivoting, sliding or other relative motion while still providing some form of attachment, unless specifically restricted. When a structure is “upstream” of another structure, this includes both directly upstream with no intervening equipment and indirectly upstream with intervening equipment. When a structure is “downstream” of another structure, this includes both directly downstream and indirectly downstream
Glossary
[0096] For ease of reference, the following glossary is provided relating to terms and concepts discussed above.
[0097] Latent Thermodynamic Process: Defined as a constant pressure/temperature process from the saturated liquid line to the saturated vapor line, whereby a thermal dynamic process of changing a substance phase, Pressure-Enthalpy diagram.
[0098] Enthalpy: A quantity associated with a thermodynamic system, expressed as the internal energy of a system plus the product of the pressure and volume of the system, having the property that during an isobaric process, the change in the quantity is equal to the heat transferred during the process.
[0099] Isobaric: Having or showing equal barometric pressure.
[0100] Isothermal: Occurring at constant temperature.
[0101] Isotropic: Of equal physical properties along all axes.
[0102] Entropy: [0103] a. (on a macroscopic scale) a function of thermodynamic variables, as temperature, pressure, or composition, that is a measure of the energy that is not available for work during a thermodynamic process. A closed system evolves toward a state of maximum entropy. [0104] b. (in statistical mechanics) a measure of the randomness of the microscopic constituents of a thermodynamic system.
[0105] Sensible Thermodynamic Process: Heat exchanged by a body or thermodynamic system that changes the temperature, and some macroscopic variables of the body, but leaves unchanged certain other macroscopic variables, such as volume or pressure.
[0106] Subcool: The measure of the temperature difference between saturated vapor (or liquid) and vapor, at constant pressure, as it applies to the condensing coil of an air conditioning unit.
[0107] Superheat: The measure of the temperature difference between saturated vapor (or liquid) and vapor, at a constant pressure, as it applies to the evaporative coil of an air conditioning unit.
[0108] 2nd Law of Thermodynamics: States that the entropy of an isolated system never decreases, because isolated systems always evolve toward thermodynamic equilibrium, a state with maximum entropy; heat always transfers higher temperature medium to a lower temperature medium.
[0109] VFD: A type of motor controller that drives an electric motor by varying the frequency and voltage supplied to the electric motor. Other names for a VFD are variable speed drive, adjustable speed drive, adjustable frequency drive, AC drive, microdrive, and inverter.
[0110] Hydronic: Denoting a cooling or heating system in which heat is transported using circulating water.
[0111] EER: The Energy Efficiency Ratio of an HVAC cooling device is the ratio of output cooling energy (in BTU) to input electrical energy (in watts) at a given operating point.
[0112] COP: Coefficient of Power defined as the relationship between the power (kW) that is drawn out of the heat pump as cooling or heat, and the power (kW) that is supplied to the compressor.
