Heat transfer device and method

Abstract

In one aspect, a heat transfer apparatus is provided for an industrial process that requires a process fluid at a process fluid set temperature. The heat transfer apparatus includes a process fluid heat exchange loop having a heat exchanger, a gas flow generator, and a thermal energy reservoir. The controller is configured to operate the process fluid heat exchange loop in a second mode in which the thermal energy reservoir transfers heat between the process fluid and the thermal energy reservoir, and the heat exchanger transfers heat between the process fluid and the air based at least in part on the parameter of the air and the determination of the process fluid heat exchange circuit in the first mode, where the process fluid bypasses the thermal energy reservoir, the process fluid cannot be provided at the process fluid set temperature.

Description

CROSS-REFERENCE TO RELATED APPLICATIONS

[0001] This application claims the benefit of U.S. Provisional Patent Application No. 63 / 355,449, filed on June 24, 2022; U.S. Provisional Patent Application No. 63 / 407,630, filed on September 17, 2022; and U.S. Provisional Patent Application No. 63 / 427,326, filed on November 22, 2022, the entire contents of which are hereby incorporated by reference into this document. Technical Field

[0002] The present disclosure relates to systems for removing heat from process fluids and, more particularly, to packaged cooling systems (eg, cooling towers). Background Art

[0003] Industrial cooling systems are used to remove heat from process fluids in a variety of industrial processes, such as manufacturing processes, HVAC systems in buildings, and heat transfer systems in computer data centers. A common approach for some industrial cooling systems is to install a heat exchanger (such as an air handling unit) in the building to transfer heat to a first process fluid (for example, water or a water-glycol mixture), and install a chiller in the building to remove heat from the first process fluid. The chiller transfers heat from the first process fluid to a second process fluid, which is transported to a heat removal device, such as a cooling tower outside the building. The cooling tower removes heat from the second process fluid and returns the cooled second process fluid to the chiller. Chillers used in industrial cooling systems are typically large, with power ratings typically ranging from 100 horsepower to 300 horsepower.

[0004] One problem with industrial cooling systems that operate year-round is that cooling systems are typically designed with sufficient maximum capacity to provide the required cooling even on the hottest days of the year. In conventional cooling systems, providing sufficient maximum capacity for the hottest days of the year requires the use of larger capacity system components than are required at other times of the year, such as more powerful chillers, fan motors, pumps, etc. Larger capacity system components consume more energy and / or water than smaller capacity components, but are used to provide sufficient maximum capacity for the cooling system.

[0005] Ice storage systems are sometimes used with industrial cooling systems to provide additional cooling capacity during periods of peak energy usage, such as on sunny, wet summer afternoons. An ice storage system has a thermal storage tank that is charged (e.g., ice in the tank is frozen) and released as needed to supplement the chillers and cooling towers of the cooling system. For example, when the local electric utility has low electricity rates, the ice storage system can be operated at night to freeze the water in the tank. The ice storage system is discharged on a sunny, wet summer afternoon, for example, and the ice in the tank is melted by the process fluid flowing through the coils in the ice tank, providing increased cooling capacity for the cooling system.

[0006] One problem with some cooling systems that utilize ice storage is that the cooling systems still rely on large (e.g., 200+ horsepower) chillers in the building to cool the water that is provided to the heat exchangers in the building. These large chillers, while providing adequate maximum capacity, often consume a large amount of energy even when the required cooling capacity is less. Another problem with some ice storage systems is that in order to provide adequate cooling capacity for a large industrial cooling system, one or more ice tanks may occupy an entire room or even a separate building. The size and complexity of large ice storage tanks may be impractical for some facilities. Additionally, ice storage systems utilize glycol as the process fluid, which is more expensive than water, increasing the pumping power required to circulate the process fluid and reducing heat transfer performance. Summary of the invention

[0007] In one aspect of the present disclosure, a heat transfer device is provided for an industrial process that requires a process fluid at a process fluid set temperature. The heat transfer device includes an air inlet, an air outlet, and a process fluid heat exchange circuit to receive a process fluid from the industrial process at a temperature different from the process fluid set temperature and provide the process fluid at the process fluid set temperature to the industrial process. The process fluid heat exchange circuit includes a heat exchanger, an air flow generator, and a thermal energy storage, the air flow generator being operable to cause air to travel from the air inlet to the air outlet and contact the heat exchanger.

[0008] The process fluid heat exchange loop has a first mode in which the process fluid bypasses the thermal energy reservoir and the heat exchanger transfers heat between the process fluid and the air. When the heat exchange capacity of the thermal energy reservoir is limited, the process fluid can bypass the thermal energy reservoir, for example, by conveying around or to the thermal energy reservoir. As another example, when the process fluid is directed through the thermal energy reservoir but the phase change material has been discharged from the thermal energy reservoir, the process fluid can bypass the thermal energy reservoir so that the temperature of the process fluid when it leaves the thermal energy reservoir is substantially the same as the temperature when it enters the thermal energy reservoir. The process fluid heat exchange loop has a second mode in which the thermal energy reservoir transfers heat between the process fluid and the thermal energy reservoir, and the heat exchanger transfers heat between the process fluid and the air. The heat transfer device also includes a controller operably connected to the process fluid heat exchange loop.

[0009] The controller is configured to operate the process fluid heat exchange circuit in the second mode based at least in part on the parameters of the air and determining that the process fluid heat exchange circuit in the first mode is unable to provide the process fluid at the process fluid set temperature. In this manner, the heat transfer device can utilize the thermal energy storage to fine-tune or partially meet the heat transfer load required to provide the process fluid at the process fluid set temperature. By selectively utilizing the thermal energy storage during peak heat transfer loads (e.g., on the hottest days of the year), the heat exchanger can be sized to have a smaller capacity than when the heat exchanger itself meets the peak heat transfer load, which helps the heat exchanger use less water and / or energy during non-peak heat transfer load conditions.

[0010] The present disclosure also provides a method of operating a heat transfer device associated with an industrial process that requires a process fluid at a process fluid set temperature. The heat transfer device includes a process fluid heat exchange circuit for the process fluid, the process fluid heat exchange circuit including a heat exchanger, a fan that moves air relative to the heat exchanger, and a thermal energy storage. The process fluid heat exchange circuit has a first mode in which the process fluid bypasses the thermal energy storage and the heat exchanger transfers heat between the process fluid and the air. The process fluid heat exchange circuit has a second mode in which the thermal energy storage transfers heat between the process fluid and the thermal energy storage, and the heat exchanger transfers heat between the process fluid and the air. The method includes operating the process fluid heat exchange circuit in a second mode based at least in part on a parameter of the air and determining that the process fluid heat exchange circuit in the first mode is unable to provide the process fluid to the industrial process at the process fluid set temperature.

[0011] In one aspect of the present disclosure, a heat transfer device is provided, comprising: a process fluid heat exchange loop including a heat exchanger; an airflow generator operable to contact air with the heat exchanger; a thermal energy storage; and a mechanical cooler. The process fluid heat exchange loop has multiple modes, including a first mode in which the heat exchanger is operable to transfer heat between the process fluid and the air, and a second mode in which the heat exchanger is operable to transfer heat between the process fluid and the air, and the mechanical cooler is operable to remove heat from the process fluid. The multiple modes also include a third mode in which the heat exchanger is operable to transfer heat between the process fluid and the air, and the thermal energy storage is operable to remove heat from the process fluid, and a fourth mode in which the heat exchanger is operable to transfer heat between the process fluid and the air, the mechanical cooler is operable to remove heat from the process fluid, and the thermal energy storage is operable to remove heat from the process fluid. The heat transfer device also includes a controller configured to operate the process fluid heat exchange loop in one of the multiple modes based at least in part on a determination of a heat load of the heat transfer device. In this manner, the controller can operate the process fluid heat exchange circuit in various configurations based at least in part on the heat load, which provides flexibility in adjusting the heat transfer device to effectively remove heat from the process fluid.

[0012] In another aspect of the present disclosure, a heat transfer device is provided, which includes an air inlet, an air outlet, and a process fluid cooling system for cooling a process fluid. The process fluid cooling system includes: a fan assembly to allow air to travel from the air inlet to the air outlet; a dehumidifier having a dehumidification mode and a bypass mode, in which the dehumidifier removes water from the air, and in which the dehumidifier removes less water from the air than when the dehumidifier is in the dehumidification mode; and an adiabatic precooler having a precooler mode and a standby mode, in which the adiabatic precooler reduces the dry bulb temperature of the air, and in which the adiabatic precooler reduces the dry bulb temperature of the air less than when the adiabatic precooler is in the precooler mode. The heat transfer device also includes a heat exchanger that receives the process fluid and is located downstream of the dehumidifier and the adiabatic precooler. The process fluid cooling system has a first mode in which the dehumidifier is in a dehumidifying mode and the adiabatic precooler is in a precooler mode; a second mode in which the dehumidifier is in a bypass mode and the adiabatic precooler is in a precooler mode; and a third mode in which the dehumidifier is in a bypass mode and the adiabatic precooler is in a standby mode. In this manner, the dehumidifier and the adiabatic precooler can be selectively operated to meet the operating criteria of the heat transfer device, such as providing a process fluid at a process fluid set temperature, meeting a heat transfer load, minimizing energy consumption, and / or minimizing water consumption. In addition, the heat transfer device can include a water recovery system to recover water removed from the air by the dehumidifier. As an example, the recovered water can be used by the heat transfer device as make-up water for the adiabatic precooler.

[0013] The present disclosure also provides a heat transfer device having a heat exchanger for cooling a process fluid, the heat exchanger including a liquid distribution system and a fan operable to move air relative to the heat exchanger. The heat exchanger has a wet mode and a dry mode, in which the liquid distribution system distributes liquid in the wet mode; in the dry mode, the liquid distribution system distributes less liquid than in the wet mode. The heat transfer device also includes a thermal energy storage device, which has a heat transfer mode and a bypass mode, in which the thermal energy storage device removes heat from the process fluid in the heat transfer mode, and in the bypass mode, the thermal energy storage device removes less heat from the process fluid than when the thermal energy storage device is in the heat transfer mode. The heat transfer device also includes a controller, which is configured to receive a request to minimize water consumption or a request to minimize energy consumption, and determine a heat load of the heat transfer device from a plurality of heat loads including a lower heat load, an intermediate heat load, and a higher heat load. In response to receiving a request to minimize water consumption, the controller is configured to operate the heat exchanger in a dry mode and the thermal energy storage in a bypass mode based at least in part on the heat load being a lower heat load; operate the heat exchanger in a dry mode and the thermal energy storage in a heat transfer mode based at least in part on the heat load being a medium heat load; and operate the heat exchanger in a wet mode and the thermal energy storage in a heat transfer mode based at least in part on the heat load being a higher heat load. In response to receiving a request to minimize energy consumption, the controller is configured to operate the heat exchanger in a wet mode and the thermal energy storage in a bypass mode based at least in part on the heat load being a lower heat load; and operate the heat exchanger in a wet mode and the thermal energy storage in a heat transfer mode based at least in part on the heat load being a higher heat load. Thus, the controller can operate the components of the heat transfer device in different modes depending on the heat load and the request to minimize water consumption or energy consumption, which allows the heat transfer device to operate accurately and efficiently, for example, to provide a required process fluid set temperature. BRIEF DESCRIPTION OF THE DRAWINGS

[0014] Figure 1 is a schematic diagram of a heat transfer device according to the first method;

[0015] Figure 2 yes Figure 1 A more detailed schematic diagram of the heat transfer device;

[0016] Figure 3 As Figure 1 A schematic diagram of a heat transfer device of a first example of a heat exchanger;

[0017] Figure 4A and Figure 4B It is shown Figure 3 A diagram of the states of the various components of a heat transfer device in different operating modes while the heat transfer device minimizes water consumption and releases energy from the phase change material;

[0018] Figure 5A and Figure 5B It is shown Figure 3 A diagram of the state of components of a heat transfer device in different operating modes while the heat transfer device minimizes energy consumption and releases energy from the phase change material;

[0019] Fig. 6A and Figure 6B It is shown Figure 3 A diagram of the status of components of a heat transfer device in different operating modes while the heat transfer device minimizes water consumption and stores energy in the phase change material;

[0020] Fig. 7A and Figure 7B It is shown Figure 3 A diagram of the status of components of a heat transfer device in different operating modes while the heat transfer device minimizes energy consumption and stores energy in the phase change material;

[0021] Figure 8 yes Figure 1 a schematic diagram of a second example of a heat transfer device;

[0022] Fig. 9A and Fig. 9B It is shown Figure 8 A diagram of the state of components of a heat transfer device in different operating modes while the heat transfer device minimizes water consumption and releases energy from the phase change material;

[0023] Fig. 10A and Fig. 10B It is shown Figure 8 A diagram of the state of components of a heat transfer device in different operating modes while the heat transfer device minimizes energy consumption and releases energy from the phase change material;

[0024] Fig.11A and Fig. 11B It is shown Figure 8 A diagram of the status of components of a heat transfer device in different operating modes while the heat transfer device minimizes water consumption and stores energy in the phase change material;

[0025] Fig. 12A and Fig. 12B It is shown Figure 8 A diagram of the status of components of a heat transfer device in different operating modes while the heat transfer device minimizes energy consumption and stores energy in the phase change material;

[0026] Fig.13 yes Figure 1 A schematic diagram of a third example of a heat transfer device having an auxiliary closed-loop pump to facilitate energy storage of a phase change material;

[0027] Figures 14 to 19 yes Fig.13 Schematic diagram of the heat transfer device in different operation modes;

[0028] Fig. 20A and Fig. 20B It is shown Fig.13 A diagram of the state of components of a heat transfer device in different operating modes while the heat transfer device minimizes water consumption and releases energy from the phase change material;

[0029] 21A and 21B show Fig.13 A diagram of the state of components of a heat transfer device in different operating modes while the heat transfer device minimizes energy consumption and releases energy from the phase change material;

[0030] Fig.22A and Fig. 22B It is shown Fig.13 A diagram of the status of components of a heat transfer device in different operating modes while the heat transfer device minimizes energy consumption and stores energy in the phase change material;

[0031] Fig.23A and Fig. 23B It is shown Fig.13 A diagram of the status of components of a heat transfer device in different operating modes while the heat transfer device minimizes energy consumption and stores energy in the phase change material;

[0032] Fig.24 yes Figure 1 A fourth example of a heat transfer device having a direct heat exchanger and an indirect heat exchanger for removing heat from a process fluid;

[0033] Fig.25 yes Figure 1 A fifth example of a heat transfer device having a direct heat exchanger to remove heat from a process fluid;

[0034] Fig.26 is a schematic diagram of a heat transfer device according to the second method;

[0035] Fig. 27 yes Fig.26 A more detailed schematic diagram of the heat transfer device;

[0036] Fig.28 yes Fig.26 A schematic diagram of a first example of a heat transfer device;

[0037] Figure 29 to Figure 32 yes Fig.28 Schematic diagram of the heat transfer device in different operation modes;

[0038] Fig.33 It is shown Fig.28 A diagram of the state of components of a heat transfer device in different operating modes while the heat transfer device minimizes water consumption and releases energy from the phase change material;

[0039] Fig.34 It is shown Fig.28 A diagram of the state of components of a heat transfer device in different operating modes while the heat transfer device minimizes energy consumption and releases energy from the phase change material;

[0040] Fig.35 It is shown Fig.28 A diagram of the status of components of a heat transfer device in different operating modes while the heat transfer device minimizes water consumption and stores energy in the phase change material;

[0041] Fig.36 It is shown Fig.28 A diagram of the status of components of a heat transfer device in different operating modes while the heat transfer device minimizes energy consumption and stores energy in the phase change material;

[0042] Fig.37 yes Fig.26 a schematic diagram of a second example of a heat transfer device;

[0043] Fig.38 It is shown Fig.37 A diagram of the state of components of a heat transfer device in different operating modes while the heat transfer device minimizes water consumption and releases energy from the phase change material;

[0044] Fig.39 It is shown Fig.37 A diagram of the state of components of a heat transfer device in different operating modes while the heat transfer device minimizes energy consumption and releases energy from the phase change material;

[0045] Fig.40 It is shown Fig.37 A diagram of the status of components of a heat transfer device in different operating modes while the heat transfer device minimizes water consumption and stores energy in the phase change material;

[0046] Fig.41 It is shown Fig.37 A diagram of the state of components of a heat transfer device in an adiabatic cooling mode while the heat transfer device minimizes energy consumption and stores energy in a phase change material;

[0047] Fig.42 yes Fig.26 a schematic diagram of a third example of a heat transfer device;

[0048] Fig.43 yes Fig.26 A schematic diagram of a fourth example of a heat transfer device;

[0049] Fig.44 is a schematic diagram of a heat transfer device according to the third method;

[0050] Fig.45 yes Fig.44 A schematic diagram of a first example of a heat transfer device;

[0051] Figure 46 to Figure 49 yes Fig.45 A schematic diagram of a portion of a heat transfer device showing different modes of operation;

[0052] Fig.50 It is shown Fig.45 A diagram of the status of components of a heat transfer device in different operating modes while minimizing energy consumption;

[0053] Fig.51 It is shown Fig.45 A diagram of the status of the components of the heat transfer device in different operating modes while minimizing water consumption;

[0054] Fig.52 It is shown Fig.45 A diagram of the status of components of a heat transfer device in different operating modes while the heat transfer device produces water;

[0055] Fig.53 yes Fig.44 a schematic diagram of a second example of a heat transfer device;

[0056] Fig.54 It is shown Fig.53 A diagram of the status of components of a heat transfer device in different operating modes while the heat transfer device minimizes energy consumption;

[0057] Fig.55 It is shown Fig.53 A diagram of the status of components of a heat transfer device in different operating modes while minimizing water consumption of the heat transfer device;

[0058] Fig.56 It is shown Fig.53 A diagram of the status of components of a heat transfer device in different operating modes while the heat transfer device produces water;

[0059] Fig.57 yes Fig.44 a schematic diagram of a third example of a heat transfer device;

[0060] Fig.58 yes Fig.44 a schematic diagram of a fourth example of a heat transfer device;

[0061] Fig.59 is a schematic diagram of the heat transfer device in a cooler-on mode;

[0062] Fig.60 yes Fig.59 A schematic diagram of a heat transfer device showing the heat transfer device in a cooler off mode;

[0063] Fig.61is a schematic diagram of a heat transfer device having a condenser coil with a cooler located downstream of the fin coil as air is directed through the heat transfer device;

[0064] Fig.62 and Fig.63 is a schematic diagram of the heat transfer device when the heat transfer device is in a cooler on mode and a cooler off mode;

[0065] Figure 64 to Figure 67 is a schematic diagram of a heat transfer device, showing different modes of the heat transfer device;

[0066] Fig.68 is a schematic diagram of a heat transfer device having an evaporator of a cooler in an external structure of the heat transfer device;

[0067] Fig.69 yes Fig.68 A perspective view of a heat transfer device showing a heat transfer device having a thermal energy storage device arranged side by side with an evaporator;

[0068] Figure 70 to Figure 73 is a schematic diagram of the heat transfer device in its different modes of operation;

[0069] Fig.74 and Fig.75 is a schematic diagram of a heat transfer device having a phase change material, wherein the storage temperature of the phase change material increases in different operation modes of the heat transfer device;

[0070] Fig.76 is a schematic diagram of a heat transfer device having a phase change material tank bypass;

[0071] Fig.77 is a perspective view of a heat transfer device having two stacked air / process fluid heat exchangers and a phase change material tank;

[0072] Fig.78 is a schematic diagram of a heat transfer device having a shell and a phase change material tank in the shell;

[0073] Fig.79 is a schematic diagram of a heat transfer device having a membrane mass exchanger that dehumidifies air before the air reaches the heat exchanger of the heat transfer device;

[0074] Fig.80 is a schematic diagram of a heat transfer device having a membrane mass exchanger located upstream of an adiabatic cooling pad and a fin coil for dehumidifying air and improving the heat transfer efficiency between the fin coil and the airflow;

[0075] Fig.81 is a schematic diagram of a vacuum membrane mass exchanger having a sheet membrane disposed between an air channel and a permeate channel;

[0076] Fig.82 is a schematic diagram of a heat transfer device having a dehumidifier that uses a liquid desiccant to dehumidify air before the air reaches an indirect heat exchanger of the heat transfer device;

[0077] Fig.83 is a schematic diagram of a heat transfer device having a shape memory alloy cooler; and

[0078] Fig.84 : is a graph showing the relationship between the temperature and entropy of the shape memory alloy material of the shape memory alloy cooler. DETAILED DESCRIPTION

[0079] refer to Figure 1 , a heat transfer device 10 according to a first method is provided. The heat transfer device 10 has an external structure (e.g., a housing 12), one or more air inlets 14, and one or more air outlets 16. The heat transfer device 10 has a heat exchanger 19 for transferring heat between a process fluid and air moving from the air inlet 14 to the air outlet 16. The heat exchanger 19 can utilize various air / process fluid flow configurations, such as cross flow, counter flow, parallel flow, or a combination thereof. The heat transfer device 10 also includes a thermal energy storage (TES), such as a phase change material (PCM) tank 26 and a mechanical cooler, such as a heat pump or chiller 28, for providing additional heat transfer to the process fluid. The PCM in the PCM tank 26 can have a fixed or variable freezing temperature. The heat exchanger 19 includes an adiabatic precooler 20 having a precooling pad 22 and an indirect heat exchanger (e.g., a fluid cooling coil 24). The heat transfer device 10 has an air flow generator, such as one or more fans 30, which are operable to cause air to enter from the air inlet 14, pass through the pre-cooling pad 22 and the fluid cooling coil 24, and flow out of the air outlet 16. The one or more fans 30 can be fixed speed fans or variable speed fans. The PCM tank 26 and the chiller 28 provide fine-tuned cooling as needed to meet the cooling load requirements while allowing the fan 30, the adiabatic pre-cooler 20, and the indirect heat exchanger 23 to be sized to be less than the peak cooling load, which reduces the water consumption and / or energy consumption of the non-peak cooling load. Thus, the heat transfer device 10 can meet the peak cooling load or the required process fluid set temperature of the industrial process in a specific geographical location even on the hottest days of the year. In addition, the heat transfer device 10 can be operated to minimize water consumption or energy consumption while meeting the cooling load throughout the year.

[0080] about Figure 2, a more detailed schematic diagram of the heat transfer device 10 is provided. The heat transfer device 10 includes a process fluid inlet 34 to receive a process fluid (e.g., water or a water / ethylene glycol mixture) from an industrial process (e.g., a computer data center). In one embodiment, multiple heat transfer devices 10 can be arranged in parallel so that the process fluid inlet 34 receives a process fluid from an upstream heat transfer device 10. The process fluid received at the process fluid inlet 34 can be a liquid, a gas, or a liquid / gas mixture. The heat transfer device 10 has a process fluid outlet 36 for returning the process fluid to the industrial process or a downstream heat transfer device. As desired in a particular embodiment, the heat transfer device 10 can be operated to cool or heat the process fluid received at the process fluid inlet 34.

[0081] The heat transfer device 10 has a controller 40 having a memory 42, which is a non-transitory computer-readable medium for storing instructions for operating the heat transfer device 10. The controller 40 has a processor 44 for executing the instructions stored in the memory 42 and controlling the heat transfer device 10. The controller 40 also includes a communication circuit 46 for communicating with a remote device, such as an HVAC system controller of a building. The communication circuit 46 receives a process fluid variable, such as at least one of a temperature, a pressure, and a flow rate, that the remote device has requested the heat transfer device 10 to provide. The processor 44 stores the process fluid variable in the memory 42 and operates the heat transfer device 10 to provide a process fluid that satisfies the process fluid variable at the process fluid outlet 36. The communication circuit 46 can receive other data from the remote device and transmit data to the remote device, such as air temperature and / or pressure; process fluid temperature, flow rate, and / or pressure; and / or component status data.

[0082] The adiabatic precooler 20 includes an evaporative liquid distribution system 50 configured to distribute evaporative liquid (e.g., water) onto the precooling pad 22. The evaporative liquid distribution system 50 includes a sump 52 for collecting the evaporative liquid from the precooling pad 22 and a pump 54 for pumping the evaporative liquid from the sump 52 to a liquid distributor (e.g., a nozzle) of the evaporative liquid distribution system 50 to distribute the evaporative liquid onto the precooling pad 22. The evaporative liquid distribution system 50 also includes a replenishment valve 56 that allows water to be added to the sump 52 to compensate for evaporation of the evaporative liquid; a liquid level sensor 58 for detecting the liquid level of the evaporative liquid in the sump 52; a drain valve 60 for draining the sump 52; and a conductivity sensor 62 for monitoring one or more variables of the evaporative liquid in the sump 54.

[0083] The cooler 28 may take different forms, such as a refrigerant-based cooler, a solid-state cooler (e.g., electrocaloric, magnetocaloric, thermoelastic), or a gas-based cooler (reverse Brayton cycle), etc. Figure 2In the embodiment of FIG. 6 , chiller 28 is a refrigerant based chiller and includes a condenser 64 , an evaporator 66 , a compressor 68 , and an expansion valve 70 .

[0084] The heat transfer device 10 has a process fluid distribution system 80 for directing the flow of a process fluid between components of the heat transfer device 10. The process fluid distribution system 80 may include one or more bypass pumps 82, throttling valves 84, and bypass valves 86. Depending on the mode of the heat transfer device 10, a given valve may function as a bypass valve or a throttling valve, as discussed in more detail below.

[0085] The PCM tank 26 includes a phase change material 90 (e.g., ice or another phase change material with a melting temperature greater than 32°F) and a heat exchanger 92 for exchanging heat between the phase change material 90 and a process fluid. As some examples, the phase change material 90 may include ice, paraffin, non-paraffin organic matter, hydrated salts, or metals. The PCM tank 26 also includes a drain valve 94 for draining the PCM tank 26, a flow valve 96 for filling the PCM tank 26, an air pressure sensor 98 for detecting air pressure in the PCM tank 26, a vent valve 100 for releasing air pressure from the PCM tank 26 when the air pressure exceeds a predetermined threshold, and a PCM charge sensor 102. One example of a PCM charge sensor 102 is a level sensor for PCMs having different solid and liquid densities. Another example of a PCM charge sensor 102 is one or more temperature probes located at different locations on the PCM tank 26. The PCM tank 26 also includes a humidity control system 104 for detecting humidity within the PCM tank 26. The humidity control system 104 may include a relative humidity sensor 106 and a humidity control device 108 (eg, a dehumidifier).

[0086] The PCM tank 26 has an air distribution system 101 for blowing air into the PCM tank 26 to agitate the liquid PCM and promote faster and more uniform melting and / or freezing of the PCM. The air distribution system 101 directs air into the PCM at the bottom of the PCM tank 26, and the air agitates the PCM as it rises in the PCM tank 26. To provide this function, the air distribution system 101 may include an air pump, a check valve, a relative humidity sensor, and a humidity control device (e.g., Figure 2 vents shown).

[0087] The heat transfer device 10 of the first method can take various forms. Figure 3, a heat transfer device 110 is provided as a first example of a heat transfer device 10. The heat transfer device 110 includes a process fluid heat exchange loop 111 operable to receive a process fluid from a cooling load 136, cool the process fluid to achieve a desired process fluid variable (e.g., a process fluid set temperature), and direct the cooled process fluid back to the cooling load 136. The heat transfer device 110 has a controller 113 for operating components of the process fluid heat exchange loop 111.

[0088] The process fluid heat exchange loop 111 includes a heat exchanger 112 having an adiabatic precooler 114 and an indirect heat exchanger (e.g., a fluid cooling coil 116). The adiabatic precooler 114 has a precooling pad 118 and an evaporative liquid distribution system 120 for distributing evaporative liquid onto the precooling pad 118. The evaporative liquid distribution system 120 includes a sump 121 for collecting evaporative liquid from the precooling pad 118 and a drain pump 122 operable to pump the evaporative liquid from the sump 121 to the precooling pad 118.

[0089] The heat transfer device 110 includes a fan 124 to generate airflow through the pre-cooling pad 118 and the fluid cooling coil 116. The adiabatic pre-cooler 114 reduces the dry bulb temperature of the air before the air reaches the fluid cooling coil 116, which improves the heat transfer efficiency between the air and the fluid cooling coil 116. The heat transfer device 110 also includes a chiller 130, which has a condenser 132 and an evaporator 134, which are configured to transfer heat to or from a process fluid from a cooling load 136. The heat transfer device 110 has a PCM tank 138 and a closed-loop pump 140 for recharging the PCM tank 138, as discussed in more detail below. The heat transfer device 110 is organized into a base module 142, which can be added to other base modules in series or in parallel to provide the required cooling capacity for the cooling load 136. The components of heat transfer device 110 may be within a single external structure, or may be arranged in multiple external structures as desired for a particular embodiment.

[0090] about Figure 4A and Figure 4B, a method 150 for operating a heat transfer device 110 is provided. The method 150 is provided in a graph organized by heat load 152, which increases from an easy heat load 154 to a difficult heat load 156. The heat load of the heat transfer device 110 can be determined by one or more variables, such as ambient air temperature (e.g., wet bulb and / or dry bulb), ambient air humidity, temperature and / or humidity of air inside the heat transfer device 110, process fluid set temperature, process fluid pressure, process fluid flow rate, time of day, season, or a combination thereof. The method 150 has logic 158 that facilitates switching the heat transfer device 110 between operating modes 160 when the heat load 152 changes. In one embodiment, in response to the heat transfer device 110 in the "easier" operating mode 160 being unable to meet the process fluid set temperature requested by, for example, an HVAC system controller, the controller 113 enters the "harder" operating mode 160 from the "easier" operating mode 160.

[0091] Method 150 also includes variables 162 of components of heat transfer device 110 that change as heat transfer device 110 switches between operating modes 160. In method 150, controller 113 has received a request to minimize water consumption, so that method 150 represents a water conservation sequence option. The request may be received from a remote device via communication circuit 46, or may be determined by controller 113 based on data available to controller 113 (e.g., ambient air variables, process fluid variables, variables indicating the status of components of heat transfer device 110, or a combination thereof). In addition, PCM tank 138 can be discharged in method 150.

[0092] More specifically, the operating modes 160 include a dry cooling mode 164, which may be a default mode that the controller 113 begins in response to a request from the heat transfer device 110 to provide a process fluid at a process fluid set temperature to the cooling load 136. In the dry cooling mode 164, the variables 162 include a fan state 166, a drain pump state 168, a state 170 of whether the process fluid is flowing through the fluid cooling coil 116, a state 172 of whether the evaporator 134 and the PCM tank 138 are bypassed, a state 174 of the chiller 130, a state 176 of the closed loop pump 140, and a state 178 of whether the process fluid is flowing through the condenser 132 of the chiller 130. The variables 162 also include a state 180 of whether the process fluid is flowing through the evaporator 134 of the chiller 130, a state 182 of whether the process fluid is flowing through the PCM tank 138, a storage state 184 of the PCM tank 138, and a state 186 regarding the mode of the PCM tank 138. The state 186 indicates whether the PCM canister 138 may be discharged or charged in the different operating modes 160 of the method 150 .

[0093] In the dry cooling mode 164, the fan 124 is turned on, the drain pump 122 is turned off, the process fluid flows through the fluid cooling coil 116, and the evaporator 134 and the PCM tank 138 of the chiller 130 are completely bypassed. In addition, in the dry cooling mode 164, the chiller 130 is turned off, the closed loop pump 140 is turned off, the process fluid bypasses the condenser 132 of the chiller 130, and the process fluid cannot flow through the evaporator 134 of the chiller 130. Further, in the dry cooling mode 164, the process fluid bypasses the PCM tank 138, and the energy storage of the PCM tank 138 is greater than or equal to 0%.

[0094] When the heat load 152 becomes difficult or the heat load increases, the controller 113 switches from the dry cooling mode 164 to another operating mode 160 based on a determination 188 whether the energy storage of the PCM tank 138 is greater than a predetermined minimum threshold (e.g., 10%, 5%, or 0%). In the method 150, the predetermined minimum threshold is 0%.

[0095] If the energy storage of the PCM tank 138 is greater than the predetermined minimum threshold, the controller 113 enters the dry cooling and phase change material mode 190. In the dry cooling and phase change material mode 190, a portion of the process fluid enters the evaporator 134 and the PCM tank 138 of the chiller 130, and a portion of the process fluid bypasses the evaporator 134 and the PCM tank 138, as shown by reference numerals 192 and 194 in the method 150. In addition, in the dry cooling and phase change material mode 190, the PCM tank 138 is in an energy release mode, as shown by reference numeral 196.

[0096] However, if the controller 113 determines 188 that the energy storage of the PCM tank is not greater than the predetermined minimum threshold, the controller 113 may skip the dry cooling and PCM mode 190 and proceed to the dry cooling chiller mode 200. The dry cooling and chiller mode 200 allows for a greater cooling capacity than the dry cooling mode 164. In the dry cooling and chiller mode 200, a portion of the process fluid flows through the condenser 132 and the evaporator 134 of the chiller 130 (as shown by reference numerals 202, 204), and the chiller 130 is turned on (as shown by reference numeral 206). Since the energy storage of the PCM tank 138 is 0%, the process fluid does not flow through the PCM tank 138, as shown by reference numeral 208.

[0097] If the heat load 152 continues to increase while the heat transfer device 110 is in the dry cooling and chiller mode 200, the controller 113 determines 210 whether the energy storage of the PCM tank is greater than 0%. If the energy storage of the PCM tank is greater than 0%, the controller 113 changes the heat transfer device 110 to the dry cooling, chiller, and PCM mode 212 to accommodate the increase in heat load 152. Figure 4A and Figure 4BAs shown, the controller 113 may enter the dry cooling, cooler and PCM mode 212 from the dry cooling and chiller mode 200 when the energy storage of the tank is 0%, or alternatively, if the energy storage of the PCM tank 138 is greater than zero, the controller 113 may enter the dry cooling, cooler and PCM mode 212 from the dry cooling and PCM mode 190. In the dry cooling, cooler and PCM mode 212, a portion of the process fluid flows through the cooler condenser 132 and the cooler evaporator 134, as shown by reference numerals 214 and 216, and the cooler 130 is turned on, as shown by reference numeral 218. Since the energy storage of the PCM tank 138 is greater than zero, the process fluid is directed through the PCM tank 138 (as shown by reference numeral 220), thereby cooling the process fluid, and the PCM tank 138 is in the energy release mode (as shown by reference numeral 222).

[0098] When the controller 113 determines 226 that the energy storage of the PCM tank is greater than 0% and the heat load 152 continues to increase, the controller 113 can switch the operation of the heat transfer device 110 from the dry cooling, chiller and PCM mode 212 to the adiabatic cooling and PCM mode 224. In the adiabatic cooling and PCM mode 224, the drain pump 122 is turned on (as shown by reference numeral 228) to pump the evaporative liquid to the pre-cooling pad 118. In the adiabatic cooling PCM mode 224, the chiller 130 is turned off (as shown by reference numeral 230), and the process fluid does not flow through the chiller condenser 132 or the chiller evaporator 134 (as shown by reference numerals 232, 234). The process fluid flows through the PCM tank 138, as shown by reference numeral 236, and the PCM tank 138 is in the energy discharge mode 238 to remove heat from the process fluid.

[0099] The method 150 includes the controller 113 switching the heat transfer device 110 from the adiabatic cooling and PCM mode 224 to the adiabatic cooling and chiller mode 240 in response to the controller 113 determining 242 that the energy storage of the PCM tank 138 is greater than 0% and the heat load 152 continues to increase. In the adiabatic cooling and chiller mode 240, the drain pump 122 is turned on (as shown by reference numeral 241) to wet the pre-cooling pad 118 and reduce the dry bulb temperature of the air in the heat transfer device 110 before the air reaches the fluid cooling coil 116. The chiller 130 is turned on and at least a portion of the process fluid flows through the chiller condenser 132 and the chiller evaporator 134, as shown by reference numerals 244, 246, and 248. Since the energy storage of the PCM tank 138 is 0% at step 242, the process fluid does not flow through the PCM tank 138 in the adiabatic cooling and chiller mode 240, as shown by reference numeral 250.

[0100] If the energy storage of the PCM tank is 0%, the heat transfer device 110 may enter the adiabatic cooling and chiller mode 240 from the adiabatic cooling and PCM mode 224. Alternatively, if the controller 113 determines at step 210 or 226 that the energy storage of the PCM tank 138 is 0% and the heat load 152 continues to increase, the heat transfer device 110 may enter the adiabatic cooling and chiller mode 240 from the dry cooling and chiller mode 200 or the dry cooling, chiller, and PCM mode 212.

[0101] In response to the controller 113 determining 242 that the energy storage of the PCM tank 138 is greater than 0% and the heat load 152 increases to the difficulty level 156, the controller 113 can reconfigure the heat transfer device 110 from the adiabatic cooling and PCM mode 224 to the adiabatic cooling, chiller, and PCM mode 252. In the adiabatic cooling, chiller, and PCM mode 252, the drain pump 122 is turned on, as shown at reference numeral 254, the chiller 130 is turned on, as shown at reference numeral 256, at least a portion of the process fluid flows through the chiller condenser 132 and the chiller evaporator 134, as shown at reference numerals 258 and 260, and the process fluid flows through the PCM tank 130, as shown at reference numeral 262. The PCM tank 138 is in the energy discharging mode, as shown at reference numeral 264, and removes heat from the process fluid.

[0102] As heat load 152 increases or decreases, controller 113 may proceed to operating mode 160 according to logic 158. Alternatively, controller 113 may transition from one operating mode 160 to another operating mode (e.g., from mode 164 to mode 252 or vice versa) in response to a sudden change in heat load 152 on heat transfer device 110.

[0103] refer to Figure 5A and Figure 5B , the controller 113 may utilize method 270 to provide fine-tuning cooling in response to receiving a request to minimize energy consumption and the PCM tank 138 being able to discharge energy. The method 270 includes an operating mode 272 that the controller 113 may perform when the heat load 274 changes from an initial or easy 276 level to a maximum or difficult level 278. The method 270 is similar to the method 150 in many respects. One difference is that the method 270 utilizes adiabatic cooling to limit energy consumption in the modes 280, 282, 284, 286.

[0104] refer to Fig. 6A and Figure 6BIn response to the controller 113 receiving a request to minimize water consumption and the PCM tank 138 being able to store energy, the controller may utilize method 300. Method 300 includes an operating mode 302 that the controller 113 performs when the heat load 304 changes. Method 300 is similar in many respects to method 150 discussed above, and includes variables 306 that change as the controller 113 performs mode 302. One difference between methods 150 and 300 is that mode 302 includes a dry cooling closed loop chiller mode 310 in which the process fluid does not flow through the chiller evaporator 134 or the PCM tank 138, as shown by reference numerals 312, 314. Instead, a secondary process fluid (which may be the same or different than the process fluid flowing through the fluid cooling coil 116) is circulated by the closed loop pump 140, as shown by reference numeral 316. The closed loop pump 140 pumps the secondary process fluid between the chiller evaporator 134 (which cools the secondary process fluid) to the PCM tank 138 to cool the phase change material in the PCM tank 138 and to charge the PCM tank 138. In the operating mode 310, the process fluid flows through the fluid cooling coil 116 to meet the heat load on the heat transfer device 110.

[0105] Likewise, in the adiabatic cooling and closed-loop chiller mode 316, the process fluid does not flow through the chiller evaporator 134 and the PCM tank 138, as shown by reference numerals 318, 320. Instead, the secondary process fluid is circulated by the closed-loop pump 140 to allow the chiller evaporator 134 and the secondary process fluid to remove heat from and store energy in the PCM tank 138. In the adiabatic cooling and closed-loop chiller mode 316, the process fluid is cooled via the fluid cooling coil 116 and the adiabatic precooler 114, which precools the air upstream of the fluid cooling coil 116.

[0106] The operating mode 302 of the method 300 includes a dry cooling and chiller mode 309, in which the chiller 130 operates and the process fluid flows through the chiller evaporator 134 to be cooled, as shown at reference numeral 311. In addition, in the dry cooling and chiller mode 309, a portion of the cooled process fluid flows through the PCM tank 138 to store energy in the PCM tank 138, as shown at reference numeral 313.

[0107] The operating mode 302 includes an adiabatic cooling mode 317, in which the chiller 130 is turned off. However, in the adiabatic cooling mode 317, the process fluid cooled by the fluid cooling coil 116 flows to the PCM tank 138 to charge the PCM tank 138, as shown by reference numeral 319. The operating mode 302 also includes an adiabatic cooling and chiller mode 321, in which the process fluid cooled by the fluid cooling coil 116 and the chiller evaporator 134 is delivered to the PCM tank 138 to charge the PCM tank 138, as shown by reference numeral 323.

[0108] refer to Fig. 7A and Figure 7B , the controller 113 may utilize method 330 in response to receiving a request to minimize energy consumption and the PCM tank 138 being able to be charged. Method 330 includes an operating mode 332 that the controller 113 performs in response to an increase in heat load 334 of the heat transfer device 110 .

[0109] Reference Figure 8 , a heat transfer device 350 is provided as a second example of the heat transfer device 10 described above. The heat transfer device 350 has a process fluid heat exchange loop 351 that receives a high temperature process fluid from a cooling load 353 and cools the process fluid so that the process fluid heat exchange loop 351 can return the cooled process fluid to the cooling load 353 at, for example, a process fluid set temperature. The heat transfer device 350 is similar to the heat transfer device 110 in many respects, except that the heat transfer device 350 lacks a closed loop pump and associated valves for circulating a secondary process fluid in a closed loop to recharge the PCM tank 368. The heat transfer device 350 includes an adiabatic precooler 352 having an evaporative liquid distribution system 354 for distributing the evaporative liquid onto a precooling pad 356, and a pump 358 of a sump 360 for pumping the collected evaporative liquid to the precooling pad 356. Heat transfer device 350 also includes fluid cooling coil 362 , fan 364 , chiller 366 , and PCM tank 368 .

[0110] about Fig. 9A and Fig. 9B , a method 380 is provided, which can be used by the controller 370 of the heat transfer device 350 in response to receiving a request to minimize water consumption and the PCM tank 368 being able to discharge energy. The method 380 includes a mode 382, ​​and the controller 370 performs the mode 382 according to logic 384 when the heat load 386 changes between an initial or easy level 388 and a maximum or difficult level 390. The method 380 includes variables 392, which indicate the status of the components of the heat transfer device 350 that change in different modes 382.

[0111] about Fig. 10A and Fig. 10B , a method 400 is provided, which the controller 370 can implement in response to receiving a request to minimize energy consumption and the PCM tank 368 being able to discharge energy. The method 400 includes a mode 402, and the controller 370 performs the mode 402 according to logic 404 when the heat load 406 of the heat transfer device 350 changes. The method 400 includes variables 403 of components of the heat transfer device 350, which vary according to different operating modes 402.

[0112] Refer to Figure 11 and Fig. 11B , a method 410 is provided that the controller 370 may utilize in response to receiving a request to minimize water consumption and the PCM tank 368 being able to be charged. The method 410 has a mode 412 that the controller 370 performs when the heat load 406 of the heat transfer device 350 changes. The method 410 has variables 415 of the components of the heat transfer device 350 that vary according to the different operating modes 412. One difference between the methods 300 and 410 is that the method 410 uses the process fluid received from the cooling load 353 to charge the PCM tank 368, rather than utilizing a closed loop circulation of a secondary process fluid. In this manner, the cooling provided by the fluid cooling coil 362 and / or the chiller 366 can be used to both cool the process fluid and to charge the PCM tank 368. The difference in operation is due to the lack of a closed loop pump in the heat transfer device 350.

[0113] about Fig. 12A and Fig. 12B , a method 420 is provided, which the controller 370 can implement in response to receiving a request to minimize energy consumption and the PCM tank 368 being able to be charged. The method 420 includes an operating mode 422, and the controller 370 switches the operating mode 422 when the heat load 424 of the heat transfer device 350 changes. The method 420 includes variables 426 of the components of the heat transfer device 350, which vary according to the different operating modes 422. In the method 420, the PCM tank 368 is charged using a process fluid in communication with the cooling load 353, rather than performing a closed loop charge operation as in the method 330 described above.

[0114] refer to Fig.13 , a heat transfer device 430 is provided as a third example of the above-described heat transfer device 10. The heat transfer device 430 is similar in many respects to the above-described heat transfer device 110. The heat transfer device 430 has a process fluid heat exchange circuit 431 that can be operated in different modes, for example, to cool a process fluid from a cooling load 433 and to provide the process fluid to the cooling load 433 at a desired process fluid set temperature.

[0115] The heat transfer device 430 has a secondary closed loop pump 432 and valves 434, 436 to facilitate the charging of the PCM tank 438, as discussed in more detail below. The heat transfer device 430 includes an adiabatic precooler 440 having a precooling pad 442, a sump 444, and a pump 446 for pumping the collected evaporated liquid to the precooling pad 442. The heat transfer device 430 also includes a fluid cooling coil 448, a fan 450, and a cooler 452 (having a condenser 454 and an evaporator 456). The fan 450 is operable to draw air 458 through the precooling pad 442 and the fluid cooling coil 448. The heat transfer device 430 includes a primary closed loop pump 460 and valves 462, 464. The heat transfer device 430 has a controller 466 for operating the components of the heat transfer device 430 in different modes.

[0116] For example, the controller 466 may operate the heat transfer device 430 in Mode 1, such as Fig.14 shown. Fig.14 440 is not shown in the figure to provide a less obstructed view. In Mode 1, the controller 466 operates the valves 470, 472, 474, 476 of the process fluid heat exchange loop 431 to bypass the chiller 452 and the PCM tank 438. In Mode 1, the process fluid from the cooling load 433 is cooled only by heat exchange between the airflow blown by the fan 450 through the fluid cooling coil 448. In Mode 1, the adiabatic precooler 440 can be operated as needed to provide adiabatic cooling by reducing the dry bulb temperature of the air upstream of the fluid cooling coil 448.

[0117] The heat transfer device 430 has mode 2, such as Fig.15 4. In Mode 2, valve 470 receives process fluid at inlet 470A and regulates the flow of process fluid through valve 470 such that a portion of the process fluid is directed to condenser 454 of chiller 452, while the remaining process fluid bypasses condenser 454. Valve 472 receives heated process fluid from condenser 454 at inlet 472A and receives process fluid from cooling load 433 at inlet 472B. Valve 472 combines the process fluid streams at outlet 472C, which provides the combined process fluid to fluid cooling coil 448. Valve 470 can be adjusted to direct more or less process fluid to condenser 454 as needed to facilitate adequate cooling by evaporator 456 of chiller 452.

[0118] The adiabatic precooler 440 can be operated as needed to reduce the dry bulb temperature of the air upstream of the fluid cooling coil 448. The fluid cooling coil 448 exchanges heat between the process fluid and the airflow to provide the cooled process fluid to the valve 474. The valve 474 regulates the flow of the process fluid between the outlets 474B and 474C. The outlet 474C directs the cooled process fluid to the evaporator 456 of the chiller 452, which further cools the process fluid. The process fluid from the outlet 474B bypasses the evaporator 456 and the PCM tank 438 before reaching the valve 476. The valve 476 combines the process fluid streams received at the inlets 476A and 476B into a stream that travels from the outlet 476C of the valve 476 to the cooling load 433. In this way, a portion of the cooling load is handled by the fluid cooling coil 448 (and the adiabatic precooler 440 as needed), while a portion of the cooling load is handled by the chiller 452. Mode 2 may be used during high load or high ambient air temperature conditions, and / or when the PCM tank 438 is fully discharged, as a means of meeting the cooling load required by the heat transfer device 430. Mode 2 may also be used to conserve water by using the chiller 452 to provide cooling capacity, thereby reducing the cooling load required by the adiabatic precooler 440 and the fluid cooling coil 448. More specifically, Mode 2 allows the speed of the fan 450 to be reduced, thereby reducing the rate of water evaporation from the pad or other insulation medium of the adiabatic precooler 440.

[0119] about Fig.16 , the controller 466 can operate the heat transfer device 430 in Mode 3, wherein valves 470, 480 bypass the process fluid flow around the chiller 452. Valve 474 directs a portion of the process fluid from the fluid cooling coil 448 to the PCM tank 438, while the remaining portion of the process fluid bypasses the PCM tank 438. In this manner, in Mode 3, a portion of the cooling load 433 is handled by the fluid cooling coil 448 and the adiabatic precooler 440 as needed, while a portion of the cooling load 433 is handled by the discharge of the PCM tank 438. Mode 3 can be used in extremely high cooling load situations, high ambient air temperature situations, and / or can be used to save energy and / or water by reducing the load on the fluid cooling coil 448, the fan 450, and the adiabatic precooler 440.

[0120] about Fig.17, the controller 466 can operate in Mode 4, where valve 470 directs at least a portion of the process fluid from the cooling load 433 to the condenser 454 of the chiller 452. Valve 474 regulates the flow of the process fluid so that a portion of the process fluid flows to the evaporator 456 of the chiller 452, while the remaining process fluid bypasses the chiller 452 and the PCM tank 438. In addition, valves 482, 483 direct the process fluid from the evaporator 456 to the PCM tank 438, while valve 484 combines the cooled process fluid from the PCM tank 438 with the process fluid from the fluid cooling coil 448. In Mode 4, part of the cooling load is handled by the fluid cooling coil 448 and the optional adiabatic precooler 440, part of the cooling load is handled by the chiller 452, and part of the cooling load is handled by the PCM tank 438. Mode 4 may be used in high cooling load situations, high ambient air temperature conditions, as a means of meeting cooling load requirements, and / or may be used to save water by reducing the load on the fluid cooling coil 448, adiabatic precooler 440, or energy by reducing the load on the fan 450.

[0121] about Fig.18 , the controller 466 can operate the heat transfer device 430 in Mode 5, wherein there is a first loop 490 of process fluid traveling between the cooling load 433 and the fluid cooling coil 448, and a second loop 492 of closed-loop process fluid circulating between the evaporator 456 of the chiller 452 and the PCM tank 438 via the main closed-loop pump 460. Valve 470 directs the process fluid from the cooling load 433 through the condenser 454 so that the process fluid absorbs heat from the condenser 454 before traveling to the fluid cooling coil 448. The fluid cooling coil 448 is used to absorb heat from the cooling load 433 and the PCM tank 438 recharge process. The adiabatic precooler 440 can be turned on in Mode 5 to increase the cooling capacity of the fluid cooling coil 448 as needed. Mode 5 can be used to recharge a fully or partially depleted PCM tank 438 while continuing to reject heat from the cooling load 433.

[0122] about Fig.19 , controller 466 may operate heat transfer device 430 in Mode 6, wherein process fluid heat exchange loop 431 has a similar Fig.18 492 in the closed loop 492, and the secondary closed loop 511. More specifically, valves 502, 504 are closed to the cooling load 433, and the secondary closed loop pump 432 circulates the secondary closed loop process fluid 500 between the condenser 454 of the chiller 452 and the fluid cooling coil 448, so that the fluid cooling coil 448 removes heat added to the secondary closed loop process fluid 500 through the condenser 454.

[0123] In Mode 6, the primary closed loop pump 460 circulates the secondary process fluid 512 between the evaporator 450 and the PCM tank 438 throughout the primary closed loop 510. In this manner, the evaporator 450 removes heat from the primary closed loop process fluid, which is then used to recharge the PCM tank 438. Mode 6 can be used to recharge a fully or partially depleted PCM tank 438 when the heat transfer device 430 is not needed to meet the cooling load 433 (e.g., at night). The adiabatic precooler 440 can be operated as needed to provide increased cooling capacity.

[0124] refer to Fig. 20A and Fig. 20B , the controller 466 may utilize method 520 in response to receiving a request to minimize water consumption and the PCM tank 438 being able to discharge energy. The method 520 includes an operating mode 522 and logic 524, and the controller 466 utilizes logic 524 to operate the operating mode 522 in response to a change in the heat load 526 of the heat transfer device 430 determined by the controller 466. The method 520 has variables 528 of components of the heat transfer device 430, which change as the heat transfer device 430 switches between modes 522.

[0125] 21A and 21B , controller 466 may utilize method 530 in response to receiving a request to minimize energy consumption and PCM tank 438 being able to discharge energy. Method 530 includes operating mode 532 and logic 534 that controller 466 utilizes to operate mode 532 as heat load 536 of heat transfer device 430 .

[0126] about Fig.22A and Fig. 22B , the controller 466 may utilize method 540 in response to receiving a request to minimize water consumption and the PCM tank 438 being able to be charged. Method 540 includes an operating mode 542 that the controller 466 may perform when the heat load 544 of the heat transfer device 430 changes. Method 540 has variables 545 of components of the heat transfer device 530 that change as the heat transfer device 530 switches between modes 542. Mode 542 includes variables based on Fig.19 In one embodiment, the heat transfer device 430 includes an actuator to move the adiabatic precooler 440 from an operating position, in which the pads of the adiabatic precooler 440 are located in the airflow path through the heat transfer device 430, to a bypass position in which the pads are not in the airflow path. When the pads are in the bypass position, the energy consumption of the fan 450 can be reduced. The operating mode 542 also includes a closed loop dry cooling mode 546 with adiabatic precooler 440 not operating. In one embodiment, the heat transfer device 430 includes an actuator to move the adiabatic precooler 440 from an operating position to a bypass position in which the pads of the adiabatic precooler 440 are located in the airflow path through the heat transfer device 430. Fig.19The closed loop adiabatic cooling mode 548 corresponds to mode 6 in FIG. 5 , when the adiabatic precooler 440 is operating. In either mode 546 , 548 , the heat transfer device 430 is isolated from the cooling load 433 and the PCM tank 438 can be charged.

[0127] about Fig.23A and Fig. 23B , the controller 466 may utilize the method 550 in response to receiving a request to minimize energy consumption and the PCM tank 438 being able to be charged. The method 550 includes a mode 552 that the controller 466 performs when the heat load 554 of the heat transfer device 430 changes. The method 550 includes variables 556 of components of the heat transfer device 430 that change as the heat transfer device 430 is reconfigured between the operating modes 552. The operating modes 552 include a closed loop adiabatic cooling mode 558, which generally corresponds to Fig.19 Mode 6 in, and the adiabatic precooler is operated to improve the efficiency of the fluid cooling coil 448.

[0128] about Fig.24 , the heat transfer device 560 is Figure 1 560 is similar in structure and operation to the heat transfer device 350 discussed above. One difference is that the heat transfer device 560 has a heat exchanger 562 that includes a direct heat exchanger 564 having an evaporative liquid distribution system 566 that distributes evaporative liquid onto packing 568, a sump 570 for collecting the evaporative liquid, and a pump 572 for pumping the collected evaporative liquid back to the packing 568. The heat transfer device 560 has a fan 574 that generates an airflow 576 relative to the direct heat exchanger 554 so that the evaporative liquid is cooled as it travels along the packing 568 and is contacted by the airflow 576. The pump 572 transfers the cooled evaporative liquid from the sump 570 to an indirect heat exchanger 580 of the heat exchanger 562. The indirect heat exchanger 580 transfers heat between the evaporative liquid and a process fluid 582 received from a cooling load 584.

[0129] about Fig.25 , a heat transfer device 590 is provided as a fifth example of the heat transfer device 10 described above. The heat transfer device 590 is similar to the heat transfer device 560 discussed above. One difference between the heat transfer devices 560 and 590 is that the heat transfer device 590 has a direct heat exchanger 592 that transfers heat from a process fluid 594 received from a cooling load 596 directly to an airflow 598 generated by a fan 600. The direct heat exchanger 592 may include, for example, filler sheets and / or filler blocks. A trickle fill, splash fill, or no fill method may be used.

[0130] refer to Fig.26 , a heat transfer device 610 according to a second method is provided. The heat transfer device 610 includes a heat exchanger 612 and an indirect heat exchanger (e.g., a fluid cooling coil 618), the heat exchanger 612 having an insulated precooler 614 with an insulating pad 616. The heat transfer assembly 610 also includes a thermal energy storage (e.g., a PCM tank 620) to provide fine-tuned cooling to the heat transfer device 610 as needed to meet the heat load on the heat transfer device 610. The heat transfer device 610 has one or more air inlets 622, one or more air outlets 624, and a fan 626, which is operable to move air from the air inlet 622 through the precooling pad 616 and the fluid cooling coil 618 to the air outlet 624.

[0131] about Fig. 27 , provides a more detailed schematic diagram of a heat transfer device 610. The heat transfer device 610 is similar in many respects to the heat transfer device 10 described above, except that the heat transfer device 610 lacks the chiller 28. The heat transfer device 610 includes an external structure, such as a housing 630, which contains a heat exchanger 612, a process fluid distribution system 632, a controller 634, and a PCM tank 620. The PCM tank 620 contains a phase change material, whose melting temperature is, for example, greater than 65°F. The heat transfer device 610 has a process fluid inlet 636 for receiving a heated process fluid from a cooling load, and a process fluid outlet 638 for returning a cooled process fluid to the cooling load.

[0132] about Fig.28 , the heat transfer device 640 is Fig.26 640 has a process fluid heat exchange loop 641 for receiving heated process fluid from a cooling load 654 and returning cooled process fluid to the cooling load 654. The process fluid heat exchange loop 641 includes an adiabatic precooler 642, a fluid cooling coil 644, a closed loop pump 646, a PCM tank 648, and a controller 650. Fig.13 Heat transfer device 640 utilizes adiabatic precooler 642 and fluid cooling coil 644 to provide cooling for process fluid from cooling load 654 and to recharge PCM tank 648, as with cooler 452 of FIG.

[0133] about Fig.29 , the heat transfer device 640 has a Mode 1 in which the controller 650 operates the heat transfer device 640 such that heated process fluid from the cooling load 654 travels to the fluid cooling coil 644 and returns to the cooling load 654 while bypassing the PCM tank 648. When the controller 650 is in Mode 1, the adiabatic precooler 642 can be operated to reduce the dry bulb temperature of the air contacting the fluid cooling coil 644 to provide increased cooling capacity for the heat transfer device 640.

[0134] about Fig.30 , the heat transfer device 640 has a Mode 2 in which both the fluid cooling coil 644 and the PCM tank 648 handle the cooling load 654. The process fluid heat exchange loop 641 includes a valve 660 that regulates the flow of process fluid from the fluid cooling coil 644 so that a portion of the process fluid travels to the PCM tank 648 and is cooled when the PCM tank 648 is discharged. In this way, the PCM tank 648 can be discharged during peak heat loads to supplement the cooling provided by the fluid cooling coil 644. When the controller 650 is in Mode 2, the adiabatic precooler 642 can be operated to reduce the dry bulb temperature of the air contacting the fluid cooling coil 644 to provide increased cooling capacity for the heat transfer device 640.

[0135] about Fig.31 , the heat transfer device 640 has a Mode 3 in which valve 662 regulates the flow of process fluid from the cooling load 654 so that a portion 664 of the process fluid from the cooling load 654 is directed to valve 666 for mixing with process fluid from the fluid cooling coil 644 and PCM tank 648. In Mode 3, an adiabatic precooler 642 may be utilized, which reduces the temperature of the process fluid exiting the fluid cooling coil 644. Since the process fluid temperature from the fluid cooling coil 644 is lower, the PCM tank 648 may be charged. The process fluid exiting the fluid cooling coil 644 and PCM tank 648 is combined with the circulating process fluid 664 via valve 666 so that the process fluid returning to the cooling load 654 still has the same return temperature as in Mode 2. Mode 3 may be employed when ambient and load conditions allow the fluid cooling coil 644 to significantly cool the process fluid. The recirculated portion 664 of the process fluid is used to raise the temperature of the process fluid from the fluid cooling coil 664 and the PCM tank 648 and ensure that the process fluid is returned to the cooling load 654 at the desired process fluid set temperature.

[0136] about Fig.32 , the heat transfer device 640 has a mode 4, in which the valves 670, 672 are closed to the cooling load 654, and the closed loop pump 646 is operated to circulate the closed loop fluid 674 between the fluid cooling coil 644 and the PCM tank 648 to recharge the PCM tank 648. The adiabatic precooler 642 can be operated or not operated as required for a specific situation. By not operating the adiabatic precooler 642, the controller 650 reduces the water consumption of the heat transfer device 640. By operating the adiabatic precooler 642 in mode 4, the controller 650 can minimize the energy consumption of the heat transfer device 640.

[0137] about Fig.33, the controller 650 may utilize method 690 in response to receiving a request to minimize water consumption and the PCM tank 648 being able to discharge energy. As the heat load 696 of the heat transfer device 640 changes, the controller 650 switches between operating modes 692 using logic 694. The method 690 includes variables 698 of the components of the heat transfer device 640 that change as the controller 650 switches between different modes 692.

[0138] about Fig.34 , the controller 650 may utilize method 700 in response to receiving a request to minimize energy consumption and the PCM tank 648 being able to discharge energy. The method 700 includes operating modes 702 and logic 704, and the controller 650 utilizes logic 704 to switch between modes 702 as the heat load 706 of the heat transfer device 640 changes. The method 700 includes variables 708 of the heat transfer device 640, which change as the controller 650 switches between modes 702.

[0139] about Fig.35 , the controller 650 may utilize method 710 in response to receiving a request to minimize water consumption and the PCM tank 648 being able to be charged. Method 710 includes modes 712, and the controller 650 may switch between modes 712 as the heat load 714 of the heat transfer device 640 changes. Mode 712 includes Fig.32 4, wherein the closed-loop pump 646 operates and the closed-loop fluid circulates between the fluid cooling coil 644 and the PCM tank 648 to recharge the PCM tank 648. In the closed-loop dry cooling mode 716, the adiabatic precooler 742 is turned off. In contrast, the operating mode 712 includes the same Fig.32 Mode 4 is similar to the closed loop adiabatic cooling mode 718, where the adiabatic precooler 642 is operating.

[0140] about Fig.36 , the controller 650 may utilize method 720 in response to receiving a request to minimize energy consumption and the PCM tank 648 being able to be charged. The method 720 includes operating modes 722, and the controller 650 may switch between operating modes 722 in response to changes in the heat load 724 of the heat transfer device 640. The method 720 includes a variable 726 of the heat transfer device 640 that changes as the heat transfer device 640 switches between modes 722.

[0141] about Fig.37, a heat transfer device 730 is provided as a second example of the heat transfer device 610 described above. The heat transfer device 730 is similar in many respects to the heat transfer device 640, except that the heat transfer device 730 lacks the closed loop pump 646. The heat transfer device 730 includes a process fluid heat exchange loop 731, which includes an adiabatic precooler 732, a fluid cooling coil 734, a fan 736, and a PCM tank 741. The heat transfer device 730 has a controller 738 that operates the process fluid heat exchange loop 731 to return the process fluid to the cooling load 740 at a specific process fluid variable (e.g., temperature, flow rate, pressure, or a combination thereof). When the PCM tank 741 is operated to meet the maximum heat load condition, the PCM tank 741 removes heat from the process fluid to appropriately reduce water consumption or reduce energy consumption.

[0142] about Fig.38 , the processor 738 may utilize method 750 in response to receiving a request to minimize water consumption and the PCM tank 740 being able to be discharged. The method 750 includes modes 752 and logic 754, and the controller 738 utilizes logic 754 to switch between modes 752 as the heat load 756 of the heat transfer device 730 changes. The method 750 includes variables 760 of components of the heat transfer device 730, which change as the heat transfer device 730 switches between modes 752.

[0143] about Fig.39 , the controller 738 may utilize method 770 in response to receiving a request to minimize energy consumption and the PCM tank 741 being able to be discharged. The method 770 includes operating modes 772 of the heat transfer device 730 and logic 774, and the controller 738 utilizes logic 774 to switch between operating modes 772 as the heat load 776 of the heat transfer device 730 changes. The method 770 includes variables 778 of components of the heat transfer device 730, which change as the controller 738 switches between modes 772.

[0144] about Fig.40 , the controller 738 may utilize method 780 in response to receiving a request to minimize water consumption and the PCM tank 741 being able to be charged. The method 780 includes operating modes 782, and the controller 738 switches between operating modes 782 as the heat load 784 of the heat transfer device 730 changes. The method 780 includes variables 786 of components of the heat transfer device 730, which change as the heat transfer device 730 switches between modes 782.

[0145] about Fig.41, the controller 738 may utilize method 790 in response to receiving a request to minimize energy consumption and the PCM tank 748 being able to be charged. Method 790 includes the controller 738 having an adiabatic cooling mode 792, wherein the drain pump 794 (see Fig.37 ) is opened, and valve 796 directs at least a portion of the cooler process fluid to the PCM tank 741 to energize the PCM tank 741.

[0146] about Fig.42 , heat transfer device 800 is a third example of the heat transfer device 610 described above. Heat transfer device 800 is similar to heat transfer device 640 discussed above, except that heat transfer device 800 has a direct heat exchanger 802 for transferring heat between an airflow 804 generated by a fan 806 and an evaporative liquid. The evaporative liquid is collected and directed through an indirect heat exchanger 808 to transfer heat between a process fluid received from a cooling load 810 and the evaporative fluid of the direct heat exchanger 802.

[0147] about Fig.43 , heat transfer device 810 is a fourth example of the above-mentioned heat transfer device 610. Heat transfer device 810 is similar to heat transfer device 640, except that heat transfer device 810 has a direct heat exchanger 812 for transferring heat between airflow 814 generated by fan 816 and process fluid received from cooling load 818.

[0148] about Fig.44 According to the third method of the present disclosure, a heat transfer device 850 is provided. The heat transfer device 850 includes a housing 851 having one or more air inlets 854, one or more air outlets 857, and one or more fans 859 for generating an air flow 859 from the air inlet 854 to the air outlet 856. The air inlet 854 includes a primary louver 856 and a secondary louver 858, which can be selectively closed to restrict the air flow path through the heat transfer device 850. For example, the primary louver 856 can be closed, while the secondary louver 858 can be opened to allow air to bypass the membrane vacuum dehumidification system 860.

[0149] The heat transfer device 850 has one or more dehumidifiers, such as a membrane vacuum dehumidification system 860, for removing water from the airflow in a region 862 upstream of an adiabatic precooler 864 having a precooling pad 866. The heat transfer device 850 has a heat exchanger, such as a fluid cooling coil 868 downstream of the precooling pad 866. The membrane vacuum dehumidification system 860 removes water from the air and reduces the air wet bulb temperature. The precooling pad 866 cools the air upstream of the fluid cooling coil 868 and reduces the air dry bulb temperature to very close to the air wet bulb temperature. The dry cooling air contacting the fluid cooling coil 868 provides a more efficient heat transfer between the airflow 859 and the fluid cooling coil 868.

[0150] about Fig.45 , the heat transfer device 880 is Fig.44 880 includes a primary louver 882, a secondary louver 884, and a process fluid cooling system 881. The process fluid cooling system 881 includes a membrane vacuum dehumidification system 886, an adiabatic precooler 888, a fluid cooling coil 890, and a fan 892. The heat transfer device 880 also includes a vacuum pump 894 of the membrane vacuum dehumidification system 886 and a controller 896 for controlling the operation of the heat transfer device 880. The adiabatic precooler 888 includes a precooling pad 900, an evaporative liquid distribution system 902, a sump 904, and a drain pump 906. The heat transfer device 880 includes a water collection system 910 having a condensate pump 912 that directs water collected and condensed from the membrane vacuum dehumidification system 886 to the sump 904. In this way, the heat transfer device 880 can utilize at least a portion of the water collected from the membrane vacuum dehumidification system 886 as makeup water for the sump 904, which can reduce the water consumption of the heat transfer device 880. The fluid cooling coil 890 receives hot process fluid from the cooling load 916 and returns the cooled process fluid to the cooling load 916. When the primary louvers 882 are open and the secondary louvers 884 are closed, the fan 892 can be operated to direct air along the first path 920. When the primary louvers 882 are closed and the secondary louvers 884 are open, operating the fan 892 causes air to enter the secondary louvers 884 along the second path 922. The membrane vacuum dehumidification system 886 and the adiabatic precooler 888 can be selectively operated to increase the heat transfer efficiency between the fluid cooling coil 890 and the airflow through the heat transfer device 880.

[0151] about Figures 46 to 50 , shows the heat transfer device 880 in different modes to illustrate the different cooling capacities of the heat transfer device 880 in different modes. Fig.46 , the heat transfer device 880 is in mode 1, where the primary shutters 882 are open, the secondary shutters 920 are closed, the membrane vacuum dehumidification system 886 is running, the adiabatic precooler 888 is operating, and the fluid cooling coil 890 transfers heat between the airflow and the process fluid from the cooling load 916.

[0152] about Fig.47 , the heat transfer device 880 is in mode 2, wherein the primary louvers 882 are closed and the secondary louvers 884 are open, so that the airflow bypasses the membrane vacuum dehumidification system 886. The air travels along the second flow path 922 through the precooling pad 900 and reaches the fluid cooling coil 890. In mode 2, the adiabatic precooler 888 operates so that the precooling pad 900 reduces the dry bulb temperature of the airflow upstream of the fluid cooling coil 890.

[0153] about Fig.48 , the heat transfer device 880 is in Mode 3, wherein the primary louvers 882 are closed, the secondary louvers 884 are open, and air enters the heat transfer device 880 around the second flow path 922 and bypasses the membrane vacuum dehumidification system 886. In Mode 3, the drain pump 906 is turned off so that the evaporative liquid distribution system 902 does not direct liquid onto the pre-cooling pad 900. In this way, the air in the upstream region 930 of the fluid cooling coil 890 has the same wet bulb temperature and dry bulb temperature as the ambient air. Mode 3 may be employed when the cooling load on the heat transfer device 880 is low, or when the heat transfer device 880 is operated to minimize energy consumption.

[0154] about Fig.49 , the heat transfer device 880 is in Mode 4, wherein the primary louvers 882 are open and the secondary louvers 884 are closed. The fan 892 draws air into the heat transfer device 880 along the first flow path 920. The membrane vacuum dehumidification system 886 operates to reduce the humidity of the air upstream of the pre-cooling pad 900. The adiabatic pre-cooler 888 is closed so that the airflow has similar wet bulb and dry bulb temperatures before and after the pre-cooling pad 900. Therefore, in Mode 4, the heat transfer device 880 utilizes the membrane vacuum dehumidification system 886 dry fluid to cool the air upstream of the coil 890. Mode 4 can be used when the heat transfer device 880 is operated to minimize water consumption.

[0155] about Fig.50 , the controller 896 may utilize method 940 in response to receiving a request to minimize energy consumption. As the heat load 944 required by the heat transfer device 880 changes, the heat transfer device 880 may switch between operating modes 942. The method 940 has variables 946 of components of the heat transfer device 880 that change as the controller 896 switches between operating modes 942. The variables 946 may include a variable 947 indicating the operation of the condensate pump 912. In the operating mode 942, the condensate pump 912 is turned off to save energy.

[0156] about Fig.51 , controller 896 may execute method 950 in response to receiving a request to minimize water consumption. When heat load 954 of heat transfer device 880 changes, heat transfer device 880 switches between operating modes 952. Method 950 includes variable 956, which changes as heat transfer device 880 switches between operating modes 952.

[0157] In method 950, when heat transfer device 880 is in dry cooling mode 958, drain pump 906 is turned off to save water. However, when the heat load increases and controller 896 changes to adiabatic cooling and membrane vacuum dehumidification mode 960, drain pump 906 operates to provide additional adiabatic cooling to the air and increase the cooling capacity of heat transfer device 880.

[0158] about Fig.52 , the controller 896 may execute the method 960 in response to receiving a request to produce water via the membrane vacuum dehumidification system 886. The method 960 includes modes 962, and the controller 896 switches between the modes 962 as the heat load 964 of the heat transfer device 880 changes. The method 960 includes variables 966 representing the status of the components of the heat transfer device 880, which change as the heat transfer device 880 switches between the operating modes 962. The variables 966 include a variable 968 indicating whether the condensate pump 912 is operating. Since the controller 896 has received a request to produce water, the condensate pump 912 operates in both operating modes 962.

[0159] about Fig.53 , the heat transfer device 980 is a second example of the heat transfer device 850 described above. The heat transfer device 980 includes a primary shutter 982, a secondary shutter 984, and a tertiary shutter 986, which are selectively operable to bypass the membrane vacuum dehumidification system 988, the adiabatic precooler 990, or both as needed to select the operating mode. The membrane vacuum dehumidification system 988 includes a vacuum pump 992 for promoting dehumidification of the air, and a condensate pump 994 for pumping condensed and collected water from the membrane vacuum dehumidification system 988 to a sump 996 of the adiabatic precooler 990. The adiabatic precooler 990 includes a liquid distribution system 998, a precooling pad 1000, and a drain pump 1002. The heat transfer device 980 also includes a controller 1004, a fan 1006, and a fluid cooling coil 1008 that receives a process fluid from a cooling load 1010.

[0160] about Fig.54 , the controller 1004 may execute the method 1020 in response to receiving the request to minimize energy consumption. The method 1020 includes an operating mode 1022, and the heat transfer device 980 may switch between the operating modes 1022 when the heat load 1024 of the heat transfer device 980 changes. The method 1020 includes variables 1026 indicating the status of the components of the heat transfer device 980, which change as the heat transfer device 980 switches between the modes 1022. The variables 1026 include a variable 1028 indicating whether the three-stage shutter 986 is opened or closed. In the method 1020, when the controller 1004 is in any of the operating modes 1022, the three-stage shutter 986 is closed.

[0161] about Fig.55, the controller 1004 may execute the method 1030 in response to receiving the request to minimize water consumption. The method 1030 includes an operating mode 1032, and the heat transfer device 980 may switch between the operating modes 1032 when the heat load 1034 changes. The method 1030 includes a variable 1034 of the heat transfer device 980, which changes as the controller 1004 switches between the operating modes 1032. The operating mode 1032 includes a dry cooling operating mode 1036, in which the primary louvers 982 and the secondary louvers 984 are closed, and the tertiary louvers 986 are opened, as indicated by variables 1038, 1040, and 1042. By closing the primary louvers 982 and the secondary louvers 984, the air can bypass the membrane vacuum dehumidification system 988 and the adiabatic precooler 990, and instead contact the fluid cooling coil 1008 to remove heat from the process fluid of the cooling load 1010.

[0162] about Fig.56 , the controller 1004 may execute the method 1050 in response to receiving a request to produce water from the membrane vacuum dehumidification system 988. The method 1050 includes operating modes 1052, 1054 with variables 1056, which change as the controller 1004 switches between the operating modes 1052, 1054. As indicated by the variable 1058, the condensate pump 994 operates in either operating mode 1052, 1054.

[0163] about Fig.57 , the heat transfer device 1070 is a third example of the heat transfer device 850 described above. The heat transfer device 1070 is similar in many respects to the heat transfer devices 880, 980 discussed above. The heat transfer device 1070 includes a primary louver 1072 and a secondary louver 1074 and a fan 1076 that generates airflow in the heat transfer device 1070. The heat transfer device 1070 also includes a membrane vacuum dehumidification system 1078, an indirect heat exchanger 1080 (for transferring heat from a process fluid received from a cooling load 1082) and a direct heat exchanger 1084. The direct heat exchanger 1084 includes a packing 1086, a sump 1088, a liquid distribution system 1090 and a drain pump 1092. The drain pump 1092 circulates the secondary liquid to the indirect heat exchanger 1080 to receive heat from the process fluid of the cooling load 1082. The liquid distribution system 1090 distributes (e.g., sprays) the heated secondary liquid onto the packing 1086. The secondary liquid is cooled by the airflow as it travels along the direct heat exchanger 1084. The cooled secondary liquid is then pumped again from the sump 1088 to the indirect heat exchanger 1080.

[0164] about Fig.58, heat transfer device 1100 is a fourth example of the heat transfer device 850 described above. Heat transfer device 1100 is similar in many respects to heat transfer device 1070 described above. One difference is that heat transfer device 1100 includes a direct heat exchanger 1102 that receives a process fluid from a cooling load 1104. Direct heat exchanger 1102 includes a process fluid distribution system 1108 that distributes (e.g., sprays) the process fluid onto packing 1110. The process fluid is cooled by the air flow through direct heat exchanger 1102 and is collected in a sump 1106. Direct heat exchanger 1102 has a drain pump 1108 to direct the cooled process fluid back to the cooling load 1104. The heat transfer device 1100 includes a fan 1120 that is operable to draw air through primary louvers 1122 and secondary louvers 1124 that are selectively closable to control the flow of air through the heat transfer device 1100 .

[0165] refer to Fig.59 and Fig.60 , a heat transfer device 1150 is provided, which has a process fluid heat exchange loop 1152, which receives a process fluid from a cooling load 1154 and cools the process fluid to a desired temperature. The process fluid heat exchange loop includes a cooler 1154 and a heat exchanger 1156. The heat exchanger exchanges heat between the process fluid and ambient air. The heat exchanger 1156 may include an adiabatic precooler and an indirect heat exchanger. Fig.59 As shown, heat transfer device 1150 has a cooler on mode, wherein valve 1158 of process fluid heat exchange loop 1152 directs heat from heat exchanger 1156 to cooler 1154. Heat transfer device 1150 also includes Fig.60 1154. Fig.60 Cooler off mode.

[0166] refer to Fig.61, the heat transfer device 1170 includes a housing 1172 having an air inlet 1174, an air outlet 1176, and one or more fans 1178 for generating air flow therebetween. The heat transfer device 1170 has an adiabatic precooler 1180 with a precooling pad 1182, a fin coil 1184, and a condenser coil 1186 of a cooler 1188. The condenser coil 1186 and the evaporator 1190 of the cooler 1188 are in the interior 1192 of the housing 1172, and in one embodiment, the condenser coil 1186 is in the path of air traveling between the air inlet 1174 and the air outlet 1176. In some embodiments, the condenser coil 1186 can eliminate plumes by heating the humid air. In addition, since the condenser coil 1186 and the evaporator 1190 are in the interior 1192 of the housing 1172, the heat transfer device 1170 can have a compact construction. The fin coil 1184 receives the hot process fluid from the return pipe 1194 and directs the cooled process fluid to the valve 1196. The valve 1196 regulates the flow of the cooled process fluid from the fin coil 1184 to the evaporator 1190. The evaporator 1190 further cools the process fluid and directs the cooled process fluid along the conduit 1198 to the cooled process fluid source 1200. The valve 1196 can regulate the flow of the cooled process fluid from the fin coil 1184 so that some, all, or none of the cooled process fluid from the fin coil 1184 travels to the evaporator 1190. Chiller 1188 has an expansion valve 1202 and a compressor 1204 and utilizes a refrigerant to remove heat from the process fluid in evaporator 1190 and transfer the heat to the gas stream via condenser coil 1186. Heat transfer device 1170 lacks a thermal energy storage device.

[0167] about Fig.62 and Fig.63 The heat transfer device 1220 provided includes a cooler 1224 and a heat exchanger 1226, which operate to cool a process fluid from a cooling load 1228. The cooler 1224 includes an evaporator 1230, a condenser 1240, a compressor 1242, and an expansion valve 1244. The heat transfer device 1220 has a pump 1250 that circulates the process fluid from the cooling load 1228 to the condenser 1240, the heat exchanger 1226, the evaporator 1230, and back to the cooling load 1228. The heat transfer device 1220 has a Fig.62 1224 is a heat exchanger 1226. The heat exchanger 1220 also includes a heat exchanger 1224 that further reduces the temperature of the process fluid from the heat exchanger 1226. Fig.63The chiller is shown in an off mode, wherein the compressor 1242 is not circulating refrigerant between the evaporator and the condenser 1240. However, the pump 1250 is still operable to direct the process fluid from the cooling load 1228 to the heat exchanger 1226, wherein the process fluid travels through the condenser 1240 and the evaporator 1230.

[0168] refer to Figure 64 to Figure 67 , a heat transfer device 1300 is provided having a process fluid heat exchange loop 1302, which includes a glycol chiller 1304, a pump 1306, a thermal energy storage (e.g., an ice tank 1308), a heat exchanger 1310 (e.g., a glycol / water heat exchanger), and a heat exchanger 1312 (e.g., an air / water heat exchanger). The heat exchanger 1310 is part of a water loop 1305 that receives heated water from a cooling load 1314. The heat exchanger 1310 transfers heat from the water loop 1305 to the glycol loop 1303.

[0169] exist Fig.64 , heat transfer device 1300 is shown in a cooling load with an ice melt mode, wherein valve 1320 directs glycol from glycol chiller 1304 through ice tank 1308, and valve 1322 directs glycol from ice tank 1308 to glycol / water heat exchanger 1310. Glycol chiller 1304 and ice tank 1308 remove heat from glycol circulating in glycol loop 1303, which absorbs heat from water in water loop 1305 via heat exchanger 1310.

[0170] about Fig.65 , heat transfer device 1300 is shown in a cooling load with an ice forming mode. More specifically, valve 1322 inhibits glycol from flowing from ice tank 1308 to heat exchanger 1310, causing glycol chiller 1304 to remove heat from glycol loop 1303 and return cooled glycol to ice tank 1308 at a temperature below the storage temperature of ice tank 1308 (e.g., 32°F), thereby forming ice in ice tank 1308. Conversely, water loop 1305 includes pump 1330, which allows water from cooling load 1314 to flow to heat exchanger 1312 and be cooled. When the heat load on heat transfer device 1300 is reduced (e.g., overnight), a cooling mode may be used. Fig.65 of cooling loads with icing mode.

[0171] about Fig.66 , heat transfer device 1300 is shown in a cooling load with chiller and ice tank bypass mode. Valves 1320, 1322 prevent glycol from flowing through glycol loop 1303. Pump 1330 circulates water between cooling load 1314 and heat exchanger 1312 to allow heat exchanger 1312 to cool the water. Fig.66The cooling load with chiller and ice tank bypass mode can be used to save energy or when the heat load on the heat transfer device 1300 is low.

[0172] about Fig.67 , heat transfer device 1300 is shown in a cooling load with an ice tank bypass mode. More specifically, valve 1320 blocks glycol from flowing to ice tank 1308. Instead, glycol is circulated from glycol chiller 1304 to heat exchanger 1310 via pump 1306. Thus, the cooling provided by glycol chiller 1304 can be used to cool water in cooling water loop 1305 as the water travels through heat exchanger 1310.

[0173] about Fig.68 and Fig.69 , a heat transfer device 1350 similar to the heat transfer device 1170 is provided. The heat transfer device 1350 includes a housing 1352, an adiabatic precooler 1353 (which includes a precooling pad 1354, a fin coil 1356 and a condenser coil 1358), and an evaporator 1360 of a cooler 1362. Fig.69 , the heat transfer device 1350 is provided in a perspective view to show that the heat transfer device 1350 includes a thermal energy storage, such as an ice tank 1370, which is arranged in parallel with the evaporator 1360 of the cooler 1362.

[0174] about Figure 70 to Figure 73 , a heat transfer device 1390 is provided having a chiller 1392, a thermal energy storage (e.g., a PCM tank 1394), and a heat exchanger 1396 for cooling a process fluid from a cooling load 1398. The PCM tank 1394 contains a phase change material having a storage temperature above 50°F (e.g., 65°F), so that the same process fluid can be used in a first fluid loop 1411 and a second fluid loop 1413 of the heat transfer device 1390 (see Fig.71 ). The storage temperature may refer to the melting temperature or freezing temperature of the phase change material. Depending on the phase change material, the melting temperature and freezing temperature may be the same or different. Examples of phase change materials that may be used include PureTemp 18 from PureTemp LLC and Phase Change Solutions, Inc.

[0175] about Fig.70, the heat transfer device 1390 is shown in a cooling load with PCM discharge mode, wherein valve 1400 directs process fluid from the chiller 1392 through the PCM tank 1394, and valve 1402 directs the cooled process fluid from the PCM tank 1394 to the cooling load 1398. Valve 1404 directs process fluid from the heat exchanger 1396 to the chiller 1392. In this manner, the chiller 1392 and the PCM tank 1394 cool the process fluid to a temperature lower than the process fluid output from the heat exchanger 1396.

[0176] about Fig.71 , the heat transfer device 1390 is shown in a cooling load with PCM charging mode. In this mode, valves 1402, 1404 allow pump 1410 to circulate secondary process fluid between chiller 1392 and PCM tank 1394 in first fluid loop 1411. Chiller 1392 outputs secondary process fluid at a temperature below the freezing temperature of the PCM in PCM tank 1394 to recharge PCM tank 1394. In addition, in Fig.71 In the cooling load with PCM energy storage mode, the heat transfer device 1390 can circulate the main process fluid between the heat exchanger 1396 in the second fluid loop 1413 and the cooling load 1398 through the pump 1414 to provide cooling capacity for the cooling load 1398.

[0177] about Fig.72 , heat transfer device 1390 is shown in a cooling load with PCM bypass tank mode. More specifically, valve 1400 directs process fluid received from chiller 1392 to bypass PCM tank 1394 and direct the process fluid to cooling load 1398. Additionally, valve 1404 allows process fluid from heat exchanger 1396 to pass to chiller 1392.

[0178] about Fig.73 , the heat transfer device 1390 is shown in a cooling load with a chiller and PCM tank bypass mode. More specifically, in Fig.73 In the mode, valves 1402, 1404 are closed to allow the process fluid to bypass the cooler 1392 and the PCM tank 1394.

[0179] about Figure 74 to Figure 76, a heat transfer device 1430 is provided that is similar in many respects to the heat transfer device 1150 described above. One difference between the heat transfer devices 1150, 1430 is that the heat transfer device 1430 has a valve 1432 between the heat exchanger 1434 and the cooling load 1436, and a valve 1438 between the heat exchanger 1434 and the PCM tank 1440. Another difference between the heat transfer devices 1150, 1430 is that the heat transfer device 1150 uses a trim cooler 1154 to provide trim cooling, while the heat transfer device 1430 uses a PCM tank 1440 to provide trim cooling.

[0180] The heat transfer device 1430 includes: Fig.74 The cooling load of the PCM discharge mode shown has Fig.75 The cooling load of the PCM storage mode shown and the Fig.76 Cooling load for PCM tank bypass mode shown. Fig.75 In the cooling mode, valve 1432 can regulate the flow of process fluid from cooling load 1436 to direct some process fluid back to cooling load 1436 and mix with cooled process fluid from PCM tank 1440. The storage temperature of PCM tank 1440 is above 70°F, such as 78°F. Fig.75 The mode uses recirculation of process fluid to increase the temperature of the process fluid, which is then returned to the cooling load 1436.

[0181] The heat transfer devices discussed herein can take a variety of shapes. In some embodiments, the components of the heat transfer device are enclosed in a single housing. In other embodiments, the components can be separate structures that are operably connected. For example, Fig.77 A heat transfer device 1450 is provided which includes two stacked air / process fluid heat exchangers 1452, 1454 and a separate thermal energy storage 1456.

[0182] about Fig.78, a heat transfer device 1460 is provided, which includes a housing 1462 having an air inlet 1464, an air outlet 1466, and one or more fans 1468 operable to generate airflow between the air inlet 1464 and the air outlet 1466. The heat transfer device 1460 includes an adiabatic precooler 1470 having a precooling pad 1472 and an indirect heat exchanger (e.g., a fin coil 1474). The fin coil 1474 receives a hot process fluid via a return line 1476. The heat transfer device 1460 includes a valve 1480 that regulates the flow of a cooling process fluid from the fin coil 1474 to a thermal energy storage (e.g., a PCM tank 1482). The process fluid can travel from the valve 1480 to the PCM tank 1482 and then be returned to a cooling process fluid source 1484 downstream of the valve 1480. The PCM tank 1482 is within an interior 1486 of the housing 1462 , which may be advantageous in some embodiments to allow airflow generated by one or more fans 1468 to cool the PCM tank 1482 .

[0183] about Fig.79 , a heat transfer device 1500 is provided having a process fluid heat exchange loop 1502 including a dehumidifier (e.g., a membrane mass exchanger 1504), a heat exchanger 1506 (e.g., an air / process fluid heat exchanger), and a pump 1508. The membrane mass heat exchanger 1504 receives air 1510 and reduces the wet bulb temperature of the air before the air reaches the heat exchanger 1506. The heat exchanger 1506 receives a process fluid from a cooling load 1512. By dehumidifying the air upstream of the heat exchanger 1506, the operating efficiency of the heat exchanger 1506 can be improved.

[0184] about Fig.80, a heat transfer device 1530 is provided, which includes a housing 1532, a main air inlet 1534 with a main louver 1536, a secondary air inlet 1538 with a secondary louver 1540, and an air outlet 1542. The heat transfer device 1530 also includes a membrane mass exchanger 1550, an adiabatic precooler 1552 with a precooling pad 1554, and an indirect heat exchanger (e.g., a fin coil 1556). The membrane mass exchanger 1550 may include a tubular or sheet-like membrane that allows water vapor to pass through so as to collect and remove water vapor from the air flow, thereby dehumidifying the air upstream of the precooling pad 1554. In a first mode, the secondary louver 1540 can be closed and the main louver 1536 can be opened so that air flows through the membrane mass exchanger 1550 to the precooling pad 1554 and the fin coil 1556. Additionally, heat transfer device 1530 has a second mode in which primary louvers 1536 are closed and secondary louvers 1538 are open so that air can travel through secondary air inlet 1538 to bypass membrane mass exchanger 1550 to pre-cooling pad 1554. Fin coil 1556 receives hot process fluid from return tube 1570 and directs the cooled process fluid to source 1572, which directs the process fluid back to the cooling load.

[0185] about Fig.81 , a membrane mass exchanger 1660 is provided as an example of the membrane mass exchanger 1550 described above. The membrane mass exchanger 1660 includes an array of air channels 1662, sheet membranes 1664, and permeate channels 1666. Air travels into an air inlet 1669 in a direction 1670, travels along the air channels 1662 while contacting the sheet membranes 1664, and leaves the air channels 1662 via an outlet 1672. The membrane mass exchanger 1660 includes a compressor or vacuum pump 1682 that operates to create a vacuum in the permeate channels 1666. A vacuum exists in the permeate channels 1666 on the side of the sheet membrane 1664 opposite the air channels 1662, thereby drawing water vapor in the air flow through the sheet membrane 1664 and into the permeate channels 1666. The water vapor collected in the permeate channels 1666 travels through a conduit 1680 to the vacuum pump 1682 and to a water output port 1684. The water output 1684 may include, for example, an air and water separator, and a condenser for condensing the collected water vapor into liquid water for pumping to the adiabatic precooler 1552 or another process. The condenser may include, for example, a cooled metal surface.

[0186] refer to Fig.82, a heat transfer device 1700 is provided, which includes an air inlet 1702, a dehumidifier 1704 (e.g., a membrane mass exchanger 1706), an adiabatic precooler 1708 (including a precooling pad 1710), an indirect heat exchanger (e.g., a tube-fin heat exchanger 1712), a direct heat exchanger (e.g., a packing 1714), a plenum 1716, and an air outlet 1718 having a fan 1720. The fan 1720 generates an air flow from the air inlet 1702 to the air outlet 1718. The dehumidifier 1704 includes a liquid desiccant supply source 1730 having a pump 1732, which pumps the liquid desiccant collected from the sump 1734 to the membrane mass exchanger 1706. Ambient air enters the air inlet 1702, causing the liquid desiccant in the membrane mass exchanger 1706 to remove water vapor from the air. This reduces the wet bulb temperature of the air in the B region.

[0187] Next, the air travels through the pre-cooling pad 1710, which is wetted with water from a liquid supply 1750 having a pump 1754 that pumps water from a sump 1752. The water on the pre-cooling pad 1710 lowers the dry bulb temperature of region C.

[0188] The dehumidified dry air then travels through the tube-fin heat exchanger 1712 and transfers heat to the process fluid which enters the inlet 1760 of the tube-fin heat exchanger 1712 at an elevated temperature and exits the outlet 1762 of the tube-fin heat exchanger at a reduced temperature.

[0189] The liquid desiccant supply source 1730 includes a liquid desiccant tank 1770 with an electric heater that heats the liquid desiccant to store energy for the liquid desiccant that has collected water vapor at the membrane mass exchanger 1706. Alternatively or additionally, the liquid desiccant tank 1770 can utilize waste heat (e.g., from manufacturing operations) to heat the liquid desiccant. The liquid desiccant supply source 1730 also includes a pump 1780 for directing the liquid desiccant to a sprayer 1788 onto the packing 1714. The air travels from region D to region E and absorbs the heat of the liquid desiccant. The cooled liquid desiccant is then returned to the membrane mass exchanger 1706 by pump 1732.

[0190] refer to Fig.83, shows a heat transfer device 1800 having a process fluid heat exchange loop 1802, the process fluid heat exchange loop 1802 includes an indirect heat exchanger (e.g., a fluid cooling coil 1804), a thermoelastic cooler (e.g., a Shape Memory Alloy (SMA) cooler 1806), and a thermal energy storage (e.g., a PCM tank 1808), which operate to provide a process fluid to a cooling load 1810 at a desired temperature, pressure, flow rate, or combination thereof. The SMA cooler 1806 has a condenser side 1812 and an evaporator side 1814. The storage temperature of the PCM tank 1808 is 65°F. The SMA cooler 1806 generates heat when deformed by compression, and absorbs heat when the compression is released, and the SMA returns to its original shape, as shown. Fig.84 1806. The SMA cooler 1806 may have a first plurality of SMA alloy boxes compressed to generate heat on the condenser side 1812, and a second plurality of SMA alloy boxes expanded to absorb heat on the evaporator side 1814. The SMA cooler 1806 has a valve that is operable to flip the first and second plurality of SMA alloy boxes between the first plurality of boxes on the condenser side 1812 and the second plurality of boxes on the evaporator side 1814 once the first plurality of SMA alloy boxes are fully compressed and the second plurality of SMA alloy boxes are fully expanded. In this manner, the SMA cooler 1806 may operate as a cooler to further reduce the temperature of the process fluid from the fluid cooling coil 1804 before the process fluid is directed to the PCM tank 1804. It should be understood that the SMA cooler 1806 may be used with other embodiments discussed herein to replace or supplement the refrigerant-based coolers discussed herein. The SMA cooler 1806 and other coolers discussed herein may have their own embedded controller that communicates with the main controller of the heat transfer device.

[0191] Unless otherwise specified herein or clearly contradicted by context, the use of singular terms such as "a", "an" is intended to cover both the singular and the plural. The terms "comprising", "having", "including", "containing" are to be understood as open-ended terms. The phrase "at least one" as used herein is intended to be interpreted in a disjunctive sense. For example, the phrase "at least one of A and B" is intended to cover A, B, or both A and B.

[0192] While particular embodiments of the invention have been illustrated and described, it will be understood that numerous changes and modifications will occur to those skilled in the art, and the invention is intended to cover all such changes and modifications which fall within the scope of the appended claims.

Claims

1. A heat transfer device for use in an industrial process requiring a process fluid at a process fluid set temperature, the heat transfer device comprising: Air inlet and outlet; A process fluid heat exchange circuit for receiving a process fluid from the industrial process at a temperature different from a set temperature of the process fluid and providing the process fluid to the industrial process at the set temperature of the process fluid, the process fluid heat exchange circuit comprising: Heat exchangers; an air flow generator operable to cause air to travel from the air inlet to the air outlet and contact the heat exchanger; and Thermal energy storage, The process fluid heat exchange circuit has: a first mode in which the process fluid bypasses the thermal energy storage and the heat exchanger transfers heat between the process fluid and air; and a second mode, wherein the thermal energy storage transfers heat between the process fluid and the thermal energy storage, and the heat exchanger transfers heat between the process fluid and air; a controller operably connected to the process fluid heat exchange circuit, the controller being configured to operate the process fluid heat exchange circuit in the second mode based at least in part on a parameter of the air and a determination that the process fluid heat exchange circuit in the first mode is unable to provide the process fluid at the process fluid set temperature.

2. The heat transfer device according to claim 1, wherein: The process fluid heat exchange circuit includes a mechanical cooler, the process fluid heat exchange circuit having a third mode, wherein: the process fluid bypassing the thermal energy storage; The heat exchanger transfers heat between the process fluid and air; and The mechanical cooler transfers heat between the process fluid and the mechanical cooler.

3. The heat transfer device according to claim 2, wherein: The controller is configured to operate the process fluid heat exchange circuit in the third mode based at least in part on a determination that the process fluid heat exchange circuit in the third mode meets mechanical chiller operating criteria.

4. The heat transfer device according to claim 3, wherein: The mechanical chiller operating criteria include at least one of the following: whether the process fluid heat exchange circuit in the third mode is capable of providing the process fluid at the process fluid set temperature; whether the capacity of the thermal energy storage is below a predetermined threshold; and Whether the process fluid heat exchange circuit in the third mode reduces the water consumption of the process fluid heat exchange circuit compared to the water consumption of the process fluid heat exchange circuit in at least one of the first mode and the second mode.

5. The heat transfer device according to claim 1, wherein: The process fluid heat exchange circuit includes a mechanical cooler, the process fluid heat exchange circuit having a fourth mode, wherein: The thermal energy storage transfers heat between the process fluid and the thermal energy storage; The heat exchanger transfers heat between the process fluid and air; and The mechanical cooler transfers heat between the process fluid and the mechanical cooler.

6. The heat transfer device according to claim 5, wherein: The controller is configured to operate the process fluid heat exchange circuit in the fourth mode in response to a determination that the process fluid heat exchange circuit in the fourth mode meets mechanical chiller and thermal energy storage operating criteria.

7. The heat transfer device according to claim 6, wherein: The mechanical cooler and thermal energy storage operating standards include at least one of the following: whether the process fluid heat exchange circuit in the fourth mode is capable of providing the process fluid at the process fluid set temperature; and Whether the process fluid heat exchange circuit in the fourth mode reduces the water consumption of the process fluid heat exchange circuit compared to the water consumption of the process fluid heat exchange circuit in at least one of the first mode, the second mode and the third mode.

8. The heat transfer device according to claim 5, wherein: The mechanical cooler comprises a chiller.

9. The heat transfer device according to claim 1, wherein: The process fluid heat exchange circuit includes a mechanical cooler and a pump, the process fluid heat exchange circuit having a fifth mode, wherein: The heat exchanger transfers heat between the process fluid and air; The pump pumps a secondary process fluid in a closed loop between the mechanical cooler and the thermal energy storage; and The thermal energy storage transfers heat between the thermal energy storage and the secondary process fluid to store energy in the thermal energy storage.

10. The heat transfer device according to claim 9, wherein: The controller is configured to operate the process fluid heat exchange circuit in the fifth mode based at least in part on: providing a determination of the process fluid at the process fluid set temperature to the process fluid heat exchange circuit in the fifth mode; and A determination is made that an energy storage level of the thermal energy store is below a threshold energy storage level.

11. The heat transfer device according to claim 1, wherein: the controller being configured to, in response to a determination that the industrial process does not require the heat transfer device to provide the process fluid at the process fluid set point temperature, operate the process fluid heat exchange circuit in a sixth mode; Wherein, when the process fluid heat exchange circuit is in the sixth mode, the heat exchanger transfers heat between the secondary process fluid and the airflow, and the thermal energy storage transfers heat between the thermal energy storage and the secondary process fluid to store energy in the thermal energy storage.

12. The heat transfer device according to claim 11, wherein: The process fluid heat exchange circuit includes a mechanical cooler; and Wherein the mechanical cooler removes heat from the secondary process fluid when the process fluid heat exchange circuit is in the sixth mode.

13. The heat transfer device according to claim 1, wherein: The heat exchanger includes an indirect heat exchanger and an adiabatic precooler, the adiabatic precooler having a wet mode and a dry mode, wherein the wet mode uses liquid to cool air upstream of the heat exchanger, and the dry mode uses less liquid than the wet mode; and Wherein, the adiabatic precooler is capable of operating in the wet mode or the dry mode, wherein the process fluid heat exchange circuit is in the first mode and the second mode.

14. The heat transfer device according to claim 1, wherein: The parameter of the air is the wet bulb temperature of the air; and Wherein, the set temperature of the process fluid is lower than the wet bulb temperature of the air.

15. The heat transfer device according to claim 1, wherein: The process fluid heat exchange circuit includes a shape memory alloy cooler.

16. The heat transfer device according to claim 1, wherein: The thermal energy storage includes a phase change material having a melting temperature of 36°F or greater.

17. The heat transfer device according to claim 1, wherein: The process fluid heat exchange circuit includes a mechanical chiller having an evaporator, a condenser, a compressor and an expansion valve; wherein the condenser is upstream of a heat exchanger in the process fluid heat exchange loop; and Wherein, the evaporator is downstream of the heat exchanger in the process fluid heat exchange circuit.

18. The heat transfer device of claim 1, further comprising an external structure; in, The process fluid heat exchange circuit includes a mechanical cooler; and Wherein, the heat exchanger, thermal energy storage and mechanical cooler are in the external structure.

19. The heat transfer device of claim 1, further comprising a temperature sensor; and in, The parameters of the air include the temperature of the air.

20. The heat transfer device according to claim 1, wherein: The controller includes a communication circuit configured to receive a return process fluid temperature from a remote device.

21. The heat transfer device according to claim 1, wherein: The heat exchanger comprises an indirect heat exchanger.

22. The heat transfer device according to claim 1, wherein: The airflow generator includes at least one fan assembly.

23. The heat transfer device according to claim 1, wherein: The process fluid heat exchange loop includes a membrane mass exchanger.

24. A method of operating a heat transfer device associated with an industrial process requiring a process fluid at a process fluid set point temperature, the heat transfer device comprising a process fluid heat exchange circuit for the process fluid, comprising: Heat exchangers; a fan for moving air relative to the heat exchanger; and Thermal energy storage; The process fluid heat exchange circuit has: a first mode in which the process fluid bypasses the thermal energy storage and the heat exchanger transfers heat between the process fluid and air; and a second mode, wherein the thermal energy storage transfers heat between the process fluid and the thermal energy storage, and the heat exchanger transfers heat between the process fluid and air; the method comprising operating the process fluid heat exchange circuit in the second mode based at least in part on parameters of the air and a determination that the process fluid heat exchange circuit in the first mode is unable to provide the process fluid to the industrial process at the process fluid set temperature.

25. The method according to claim 24, wherein: The process fluid heat exchange circuit includes a mechanical chiller, the method further comprising operating the process fluid heat exchange circuit in a third mode, comprising: the process fluid bypassing the thermal energy storage; The heat exchanger transfers heat between the process fluid and air; and The mechanical cooler transfers heat between the process fluid and the mechanical cooler.

26. The method according to claim 25, wherein: Operating the process fluid heat exchange circuit in the third mode includes operating the process fluid heat exchange circuit in the third mode upon determining that operating the process fluid heat exchange circuit in the third mode satisfies a mechanical chiller operating criterion, the mechanical chiller operating criterion including at least one of: whether the process fluid heat exchange circuit in the third mode is capable of providing the process fluid at the process fluid set temperature; whether the capacity of the thermal energy storage is below a predetermined threshold; and Whether the process fluid heat exchange circuit in the third mode reduces the water consumption of the process fluid heat exchange circuit compared to the water consumption of the process fluid heat exchange circuit in at least one of the first mode and the second mode.

27. The method according to claim 24, wherein: The process fluid heat exchange circuit includes a mechanical chiller, the method further comprising operating the process fluid heat exchange circuit in a fourth mode, comprising: The thermal energy storage transfers heat between the process fluid and the thermal energy storage; The heat exchanger transfers heat between the process fluid and air; and The mechanical cooler transfers heat between the process fluid and the mechanical cooler.

28. The method according to claim 27, wherein: Operating the process fluid heat exchange circuit in the fourth mode includes operating the process fluid heat exchange circuit in the fourth mode upon determining that operating the process fluid heat exchange circuit in the fourth mode satisfies mechanical chiller and thermal storage operating criteria, the mechanical chiller and thermal storage operating criteria including at least one of: whether the process fluid heat exchange circuit in the fourth mode is capable of providing the process fluid at the process fluid set temperature; and Whether the process fluid heat exchange circuit in the fourth mode reduces the water consumption of the process fluid heat exchange circuit compared to the water consumption of the process fluid heat exchange circuit in at least one of the first mode, the second mode and the third mode.

29. The method of claim 24, wherein: The process fluid heat exchange circuit includes a mechanical chiller and a pump, the method further comprising operating the process fluid heat exchange circuit in a fifth mode, wherein: The heat exchanger transfers heat between the process fluid and air; The pump pumps a secondary process fluid in a closed loop between the mechanical cooler and the thermal energy storage; and The thermal energy storage transfers heat between the thermal energy storage and the secondary process fluid to store energy in the thermal energy storage.

30. The method of claim 29, wherein: Operating the process fluid heat exchange circuit in the fifth mode includes operating the process fluid heat exchange circuit in the fifth mode based at least in part on: providing a determination of the process fluid at the process fluid set temperature to the process fluid heat exchange circuit in the fifth mode; and A determination is made that an energy storage level of the thermal energy store is below a threshold energy storage level.

31. The method of claim 24, further comprising operating the process fluid heat exchange circuit in a sixth mode in response to determining that the industrial process does not require the heat transfer device to provide the process fluid at the process fluid set point temperature; and in, Operating the process fluid heat exchange circuit in the sixth mode comprises: The heat exchanger transfers heat between a secondary process fluid and the air; and The thermal energy storage transfers heat between the thermal energy storage and the secondary process fluid to store energy in the thermal energy storage.

32. The method according to claim 31, wherein: The process fluid heat exchange circuit includes a mechanical cooler; and Wherein operating the process fluid heat exchange circuit in the sixth mode includes the mechanical cooler removing heat from the secondary process fluid.

33. The method of claim 24, wherein: The heat exchanger includes an indirect heat exchanger and an adiabatic precooler, the adiabatic precooler having a wet mode and a dry mode, wherein in the wet mode, the adiabatic precooler uses liquid to cool air upstream of the heat exchanger, and in the dry mode, the adiabatic precooler uses less liquid than in the wet mode, the method further comprising: receiving a request to minimize water or energy consumption; and Based at least in part on the request to minimize water or energy consumption, the adiabatic precooler is operated in the wet mode or the dry mode.

34. A heat transfer device comprising: Air inlet and outlet; A process fluid heat exchange circuit, which is used to receive the process fluid, the process fluid heat exchange circuit comprising: Heat exchangers; an air flow generator operable to cause air to travel from the air inlet to the air outlet and contact the heat exchanger; Thermal energy storage; and Mechanical coolers; The process fluid heat exchange circuit has multiple modes, including: a first mode wherein the heat exchanger is operable to transfer heat between the process fluid and air; a second mode, wherein the heat exchanger is operable to transfer heat between the process fluid and air, and the mechanical cooler is operable to remove heat from the process fluid; and a third mode, wherein the heat exchanger is operable to transfer heat between the process fluid and air, and the thermal energy storage is operable to remove heat from the process fluid; and a fourth mode, wherein the heat exchanger is operable to transfer heat between the process fluid and air, the mechanical cooler is operable to remove heat from the process fluid, and the thermal energy storage is operable to remove heat from the process fluid; A controller is operably connected to the process fluid heat exchange circuit, the controller being configured to operate the process fluid heat exchange circuit in one of the plurality of modes based at least in part on a determination of a heat load of the heat transfer device.

35. The heat transfer device of claim 34, wherein: The controller is configured to determine a stored energy of the thermal energy storage; and Wherein the controller is configured to operate the process fluid heat exchange circuit in one of the plurality of modes based at least in part on a determination of the heat load of the heat transfer device and the energy storage of the thermal energy storage.

36. The heat transfer device of claim 34, wherein: The controller is configured to receive a request to minimize water consumption or energy consumption; and Wherein the controller is configured to operate the process fluid heat exchange circuit in one of the plurality of modes based at least in part on a determination of the heat load of the heat transfer device and a request to minimize water or energy consumption.

37. The heat transfer device of claim 34, wherein: The process fluid heat exchange circuit has a fifth mode, wherein: The heat exchanger is operable to transfer heat between the process fluid and air; and The mechanical cooler is operable to store energy in the thermal energy storage.

38. The heat transfer device of claim 37, wherein: The process fluid heat exchange circuit in the fifth mode is configured to conduct a closed loop process fluid between the mechanical cooler and the thermal energy storage.

39. The heat transfer device of claim 37, wherein: The mechanical cooler includes a condenser and an evaporator; The process fluid heat exchange circuit in the fifth mode comprises: A first process fluid closed loop includes the evaporator of the mechanical cooler, the thermal energy storage, and a first closed loop pump for circulating a first process fluid between the evaporator and the thermal energy storage.

40. The heat transfer device of claim 34, wherein: The process fluid heat exchange circuit has a sixth mode in which the heat exchanger and mechanical cooler are operable to store energy in the thermal energy storage.

41. The heat transfer device of claim 40, wherein: The mechanical cooler includes a condenser and an evaporator; Wherein, the process fluid heat exchange circuit in the sixth mode includes: a first process fluid closed loop comprising an evaporator of the mechanical chiller, the thermal energy storage, and a first closed loop pump for circulating a first process fluid between the evaporator and the thermal energy storage; and A second process fluid closed loop includes a condenser of the mechanical chiller, the heat exchanger, and a second closed loop pump for circulating a second process fluid between the condenser and the heat exchanger.

42. The heat transfer device of claim 34, wherein: The controller is configured to determine whether the thermal energy storage has sufficient stored energy; and Wherein the controller is configured to prevent the process fluid heat exchange circuit from being in the third mode or the fourth mode in response to the thermal energy storage not having sufficient stored energy.

43. The heat transfer device of claim 34, wherein: The heat exchanger has a wet mode and a dry mode; and Wherein, the heat exchanger is capable of operating in the wet mode or the dry mode, wherein the process fluid heat exchange circuit is in the first mode, the second mode, the third mode and the fourth mode.

44. The heat transfer device of claim 34, wherein: The process fluid heat exchange circuit is configured to direct the process fluid around the thermal energy store in the first mode and the second mode.

45. The heat transfer device of claim 34, wherein: The process fluid heat exchange circuit is configured to direct the process fluid around the mechanical cooler in the first mode and the third mode.

46. ​​The heat transfer device of claim 34, wherein: The mechanical cooler is off when the process fluid heat exchange circuit is in the first mode and the third mode.

47. The heat transfer device of claim 34, wherein: The mechanical cooler includes a condenser, an evaporator, a compressor and an expansion valve.

48. The heat transfer device of claim 47, wherein: The condenser and the evaporator are configured to receive the process fluid.

49. The heat transfer device of claim 34, wherein: The heat exchanger includes an indirect heat exchanger and an adiabatic precooler.

50. The heat transfer device of claim 34, wherein: When the process fluid heat exchange circuit is in the first mode, the mechanical chiller and the thermal energy storage are inoperable to remove heat from the process fluid.

51. The heat transfer device of claim 34, wherein: The mechanical cooler includes a condenser configured to contact the airflow after the airflow contacts the heat exchanger as the airflow travels from the air inlet to the air outlet.

52. The heat transfer device of claim 34, further comprising an external structure; and The heat exchanger, mechanical cooler and thermal energy storage are in an external structure.

53. The heat transfer device of claim 34, wherein: The mechanical cooler includes a shape memory alloy cooler.

54. A method of operating a heat transfer device comprising a process fluid heat exchange circuit, comprising: Heat exchangers; Thermal energy storage; and Mechanical coolers; The process fluid heat exchange circuit has multiple modes, including: a first mode wherein the heat exchanger is operable to transfer heat between a process fluid and air; a second mode, wherein the heat exchanger is operable to transfer heat between the process fluid and air, and the mechanical cooler is operable to remove heat from the process fluid; a third mode, wherein the heat exchanger is operable to transfer heat between the process fluid and air, and the thermal energy storage is operable to remove heat from the process fluid; and a fourth mode, wherein the heat exchanger is operable to transfer heat between the process fluid and air, the mechanical cooler is operable to remove heat from the process fluid, and the thermal energy storage is operable to remove heat from the process fluid; The method comprises: determining a heat load of the heat transfer device; and The process fluid heat exchange circuit is operated in one of the plurality of modes based at least in part on a heat load of the heat transfer device.

55. The method of claim 54, further comprising determining a stored energy of the thermal energy storage; and in, Operating the process fluid heat exchange circuit in one of the plurality of modes includes operating the process fluid heat exchange circuit in one of the plurality of modes based at least in part on a heat load of the heat transfer device and energy storage of the thermal energy storage.

56. The method of claim 54, further comprising receiving a request to minimize water or energy consumption; and in, Operating the process fluid heat exchange circuit in one of the plurality of modes includes operating the process fluid heat exchange circuit in one of the plurality of modes based at least in part on a heat load of the heat transfer device and the request to minimize water or energy consumption.

57. The method of claim 54, further comprising operating the process fluid heat exchange circuit in a fifth mode, wherein: The heat exchanger transfers heat between the process fluid and air; and The mechanical cooler stores energy in the thermal energy storage.

58. The method of claim 54, further comprising determining a stored energy of the thermal energy storage; and in, Operating the process fluid heat exchange circuit in one of the plurality of modes includes not operating the thermal energy store in the third mode or the fourth mode in response to the thermal energy store not having sufficient stored energy.

59. The method of claim 54, wherein: The heat exchanger has a wet mode and a dry mode; and Wherein, operating the process fluid heat exchange circuit in one of the plurality of modes includes operating the heat exchanger in the wet mode or the dry mode.

60. A heat transfer device comprising: Air inlet and outlet; A process fluid cooling system for cooling a process fluid, the process fluid cooling system comprising: a fan for moving air from the air inlet to the air outlet; a dehumidifier having a dehumidification mode in which the dehumidifier removes water from the air and a bypass mode in which the dehumidifier removes less water from the air than when the dehumidifier is in the dehumidification mode; an adiabatic precooler having a precooler mode in which the adiabatic precooler reduces the dry bulb temperature of the air and a standby mode in which the adiabatic precooler reduces the dry bulb temperature of the air less than when the adiabatic precooler is in the precooler mode; and a heat exchanger receiving the process fluid, the heat exchanger being located downstream of the dehumidifier and the adiabatic precooler; The process fluid cooling system has: a first mode wherein the dehumidifier is in the dehumidification mode and the adiabatic precooler is in the precooler mode; a second mode wherein the dehumidifier is in the bypass mode and the adiabatic precooler is in the precooler mode; and A third mode wherein the dehumidifier is in the bypass mode and the adiabatic precooler is in the standby mode.

61. The heat transfer device of claim 60, further comprising a water recovery system operably connected to the dehumidifier and adiabatic precooler; The process fluid cooling system has: A fourth mode, wherein the dehumidifier is in the dehumidification mode, the adiabatic precooler is in the standby mode or the precooler mode, and the water recovery system collects water removed from the air by the dehumidifier.

62. The heat transfer device of claim 60, further comprising a controller operably connected to the dehumidifier and the adiabatic precooler, the controller being configured to operate the process fluid cooling system in the second mode based at least in part on a request received by the controller to minimize energy consumption.

63. The heat transfer device of claim 60, further comprising a controller operably connected to the dehumidifier and the adiabatic precooler, the controller being configured to operate the process fluid cooling system in the third mode based at least in part on a request received by the controller to minimize water consumption.

64. The heat transfer device of claim 60, wherein: The air inlet includes a primary air inlet having a primary louver for selectively allowing air to flow to the dehumidifier and a secondary air inlet having a secondary louver for selectively allowing air to bypass the dehumidifier and enter the adiabatic precooler; wherein, when the process fluid cooling system is in the first mode, the primary shutter is opened and the secondary shutter is closed; and Wherein, when the process fluid cooling system is in the second mode, the primary shutter is closed and the secondary shutter is opened.

65. The heat transfer device of claim 60, further comprising a water recovery system operably connected to the dehumidifier and the adiabatic precooler; the process fluid cooling system having a fourth mode wherein the dehumidifier is in the dehumidification mode, the adiabatic precooler is in the standby mode or the precooler mode, and the water recovery system collects water removed from the air by the dehumidifier for use by the adiabatic precooler; in, The air inlet includes a primary air inlet having a primary louver for selectively allowing air to flow to the dehumidifier and a secondary air inlet having a secondary louver for selectively allowing air to bypass the dehumidifier and enter the adiabatic precooler; wherein, when the process fluid cooling system is in the third mode, the primary shutter is closed and the secondary shutter is opened; and Wherein, when the process fluid cooling system is in the fourth mode, the primary shutter is opened and the secondary shutter is closed.

66. The heat transfer device of claim 60, wherein the air inlet comprises: a main air inlet having a main louver for selectively allowing air flow to the dehumidifier; a secondary air inlet having a secondary louver for selectively allowing air to bypass the dehumidifier and enter the adiabatic precooler; and a three-stage air inlet having a three-stage louver for selectively allowing air to bypass the dehumidifier and the adiabatic precooler and enter the heat exchanger; and Wherein, when the process fluid cooling system is in the third mode, the primary shutter and the secondary shutter are closed, and the tertiary shutter is opened.

67. The heat transfer device of claim 60, wherein: the adiabatic precooler comprising a liquid absorbent material and a liquid distribution system for providing liquid to the liquid absorbent material, the liquid absorbent material being configured to contact the air as the air travels from the air inlet to the air outlet; wherein, when the adiabatic precooler is in the precooler mode, the liquid distribution system distributes liquid onto the absorbent material; and Wherein, when the adiabatic precooler is in the standby mode, the liquid distribution system distributes less liquid onto the absorbent material than when the adiabatic precooler is in the precooler mode.

68. The heat transfer device of claim 60, wherein: The dehumidifier comprises a membrane vacuum dehumidifier.

69. The heat transfer device of claim 60, wherein: The heat exchanger comprises an indirect heat exchanger.

70. The heat transfer device of claim 60, wherein: The dehumidifier is configured to remove water vapor from the air using a liquid desiccant.

71. The heat transfer device of claim 60, wherein: The adiabatic precooler is located downstream of the dehumidifier.

72. A heat transfer device comprising: a heat exchanger for cooling a process fluid, the heat exchanger comprising a liquid distribution system; a fan operable to move air relative to the heat exchanger and facilitate the heat exchanger to transfer heat from the process fluid to the air; The heat exchanger has a wet mode and a dry mode, wherein the liquid distribution system distributes liquid in the wet mode and the liquid distribution system distributes less liquid in the dry mode than in the wet mode; a thermal energy store having a heat transfer mode in which the thermal energy store removes heat from the process fluid and a bypass mode in which the thermal energy store removes less heat from the process fluid than when the thermal energy store is in the heat transfer mode; a controller operably connected to the heat exchanger and the thermal energy storage, the controller being configured to: receiving a request to minimize water consumption or a request to minimize energy consumption; determining a heat load of the heat transfer device from a plurality of heat loads including a lower heat load, a medium heat load, and a higher heat load; In response to receiving the request to minimize water consumption: operating the heat exchanger in the dry mode and the thermal energy storage in the bypass mode based at least in part on the heat load being a lower heat load; operating the heat exchanger in the dry mode and the thermal energy storage in the heat transfer mode based at least in part on the heat load being a medium heat load; operating the heat exchanger in the wet mode and the thermal energy storage in the heat transfer mode based at least in part on the heat load being a higher heat load; and In response to receiving the request to minimize energy consumption: operating the heat exchanger in the wet mode and the thermal energy storage in the bypass mode based at least in part on the heat load being a lower heat load; and Based at least in part on the heat load being a higher heat load, operating the heat exchanger in the wet mode and operating the thermal energy storage in the heat transfer mode.

73. The heat transfer device of claim 72, wherein: The controller is configured to determine a stored energy of the thermal energy storage; and Wherein the controller is configured to operate the heat exchanger in the dry mode or the wet mode and to operate the thermal energy storage in the heat transfer mode or the bypass mode based at least in part on the heat load and the energy storage of the thermal energy storage.

74. The heat transfer device of claim 72, wherein: The controller is configured to determine the heat load based on at least one of a process fluid set point temperature, a wet bulb temperature, a dry bulb temperature, and relative humidity.

75. The heat transfer device of claim 72, wherein: When the thermal energy store is in the bypass mode, the process fluid is directed around the thermal energy store.

76. The heat transfer device according to claim 72 further includes a mechanical cooler, wherein the mechanical cooler has a cooling mode and a standby mode, wherein in the cooling mode, the mechanical cooler removes heat from the process fluid, and in the standby mode, the mechanical cooler removes less heat from the process fluid than when the mechanical cooler is in the cooling mode.

77. The heat transfer device of claim 76, wherein the plurality of heat loads comprises: a lower-middle heat load, which is greater than the lower heat load and less than the middle heat load; and an upper-middle heat load, which is greater than the middle load and less than the higher heat load; In response to receiving the request to minimize water consumption, the controller is configured to: When the heat load is a medium-low heat load, the heat exchanger is operated in the dry mode, the thermal energy storage is operated in the bypass mode, and the mechanical cooler is operated in the cooling mode; and When the heat load is a medium to high heat load, the heat exchanger is operated in the dry mode, the thermal energy storage is operated in the heat transfer mode, and the mechanical cooler is operated in the cooling mode.

78. The heat transfer device of claim 76, wherein: In response to receiving the request to minimize energy consumption, the controller is configured to operate the heat exchanger in the wet mode, operate the thermal energy storage in the heat transfer mode, and operate the mechanical chiller in the cooling mode when the heat load is a higher heat load.

79. The heat transfer device of claim 78, wherein: The plurality of heat loads include: a middle-lower heat load and a middle-upper heat load, both of which are greater than the lower heat load and less than the higher heat load; In response to receiving the request to minimize energy consumption, the controller is configured to: When the heat load is a medium to low heat load, operating the heat exchanger in the wet mode, operating the thermal energy storage in the heat transfer mode, and operating the mechanical cooler in the standby mode; and When the heat load is a medium to high heat load, the heat exchanger is operated in the wet mode, the thermal energy storage is operated in the bypass mode, and the mechanical cooler is operated in the cooling mode.

80. The heat transfer device of claim 72, wherein: The controller is configured to determine a stored energy of the thermal energy storage; and Wherein, the controller is operable to control the fan and the heat exchanger to store energy in the thermal energy storage.

81. The heat transfer device of claim 72, further comprising a mechanical chiller having an evaporator, a condenser, a compressor, and an expansion valve; in, the heat exchanger being downstream of the condenser to allow the heat exchanger to receive process fluid that has absorbed heat from the condenser; and The heat exchanger is upstream of the evaporator to allow the evaporator to further cool the process fluid that has been cooled by the heat exchanger.

82. The heat transfer device of claim 72, wherein the heat exchanger comprises: Adiabatic precooler; and Indirect heat exchanger.

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