DESC:FIELD OF INVENTION
[0001] The present invention relates, in general, to a system and a method for achieving cooling. More particularly, the present disclosure relates to a water based indirect evaporative cooler.
BACKGROUND
[0002] A heating ventilation and cooling (HVAC) system or conventional air conditioning systems, which run on refrigerants and/or coolants, are commonly used to provide cooling within confined spaces. Irrespective of the type of region (e.g., relatively humid or relatively dry) the air conditioning systems are applied in, use of air conditioning systems can be disadvantageous. As an example, excess usage of air conditioning system, e.g., in relatively dry regions like Delhi, India, can lead to skin dryness. Also, air conditioning systems consume relatively more power than several other appliances, leading to commensurate increase in expenses and carbon footprint, making air conditioning systems less than optimal to meet several cooling needs.
[0003] On the other hand, when a direct evaporative cooler (commonly referred to as desert coolers) are used to cool any region, e.g., any confined space, humidity levels in such regions see a noticeable increase after a period of cooler use. An increase in humidity generally leads to an increased heat index within such regions, which may in turn cause discomfort to users in those regions. Such discomfort to users is exacerbated when direct evaporative cooler applications are employed in areas that are characteristically humid and moist, such as Mumbai, India, making direct evaporative coolers also less than optimal to meet several cooling needs.
[0004] US 5,664,433 (prior art) relates to an indirect/direct evaporative cooling system for cooling air for comfort purposes. The system includes a single, variable speed blower positioned below an indirect evaporative cooling stage and a direct evaporative cooling stage. A first portion of the blower discharge is directed horizontally through the indirect evaporative cooling stage, where it is cooled without the addition of moisture thereto and is then further cooled in the direct evaporative stage prior to being supplied to a building. A second portion of the blower discharge is directed vertically through the indirect evaporative cooling stage and serves to cool the first portion as the first portion travels through the indirect stage. The indirect and direct cooling stages share a common sump for collecting water drained therefrom. The indirect stage includes a drip edge to keep the drain water out of the flow of the first portion. A stud-straddle supply duct is attached to the direct cooling stage to facilitate installation of the system in wood-framed walls.
SUMMARY
[0005] In one aspect, the present disclosure discloses a system for achieving cooling in one or more zones. The system includes a first enclosure portion and a second enclosure portion. The first enclosure portion defines a first entry and a first exit. The first enclosure portion includes a first heat exchanger and a first blower. The first heat exchanger defines a first path for passage of a fluid. The first blower draws in first air through the first entry and force the first air to pass through the first heat exchanger and the first exit. When the first air passes through the first heat exchanger, the first air indirectly contacts the fluid such that the heat of the first air entrains onto the fluid and an ensuing cooled first air flows downstream of the first heat exchanger and exits through the first exit. The second enclosure portion defines a second entry and a second exit. The second enclosure portion includes a sump, second heat exchanger, a second blower, and a pump. The second heat exchanger defines a second path for passage of a heated fluid entrained with the heat of the first air. The second blower draws in second air through the second entry and forces the second air to pass through the second heat exchanger and the second exit. When the second air passes through the second heat exchanger, the second air directly contacts the heated fluid such that a volume of the heated fluid is evaporated into the second air and expelled out from the second exit, and an ensuing cooled fluid volume from the second heat exchanger passes into the sump. The pump supplies the cooled fluid volume from the sump to the first heat exchanger for a circulation of the fluid between the first enclosure portion and the second enclosure portion.
[0006] In another aspect, the disclosure relates to a method for achieving cooling in one or more zones. The method includes using a cooling system by applying a first enclosure portion defining a first entry and a first exit and by applying a second enclosure portion defining a second entry and a second exit. The first enclosure portion includes a first heat exchanger and a first blower. The first heat exchanger defines a first path for passage of a fluid. The first blower draws in first air through the first entry and forces the first air to pass through the first heat exchanger and the first exit. When the first air passes through the first heat exchanger, the first air indirectly contacts the fluid such that heat of the first air entrains onto the fluid and an ensuing cooled first air flows downstream of the first heat exchanger and exits through the first exit. The second enclosure portion includes a sump, a second heat exchanger, a second blower, and a pump. The second heat exchanger defines a second path for passage of a heated fluid entrained with the heat of the first air. The second blower draws in second air through the second entry and forces the second air to pass through the second heat exchanger and the second exit. When the second air passes through the second heat exchanger, the second air directly contacts the heated fluid such that a volume of the heated fluid is evaporated into the second air and expelled out from the second exit, and an ensuing cooled fluid volume from the second heat exchanger passes into the sump. The pump supplies the cooled fluid volume from the sump to the first heat exchanger for a circulation of the fluid between the first enclosure portion and the second enclosure portion. The method further includes positioning the first exit towards a first zone of the one or more zones such that the cooled first air is delivered into the first zone for cooling the first zone. Also, the method includes positioning the second exit towards a second zone for expelling the heat carried by the fluid into the second zone.
BRIEF DESCRIPTION OF THE DRAWINGS
[0007] FIG. 1 is a diagrammatic view of a system for achieving cooling in a zone, in accordance with an embodiment of the present disclosure;
[0008] FIG. 2 is a diagrammatic view of another system for achieving cooling in the zone, in accordance with an alternate embodiment of the present disclosure;
[0009] FIG. 3 is a schematic of a control mechanism applicable to control each of the systems of FIGS. 1 and 2, in accordance with an alternate embodiment of the present disclosure;
[0010] FIG. 4 is a psychrometric chart illustrating an ideal comfort area for the zone, in accordance with an alternate embodiment of the present disclosure;
[0011] FIG. 5 is a chart comparing variations in a heat index of the zone when using any one or more of the systems of FIGS. 1 and/or 2 to cool the zone, in accordance with an alternate embodiment of the present disclosure; and
[0012] FIG. 6 is a method for achieving cooling in the zone, in accordance with an alternate embodiment of the present disclosure.
[0013] Persons skilled in the art will appreciate that elements in the figures are illustrated for simplicity and clarity and may have not been drawn to scale. For example, the dimensions of some of the elements in the figure may be exaggerated relative to other elements to help to improve understanding of various embodiments of the present disclosure.
DETAILED DESCRIPTION
[0014] Reference will now be made in detail to specific embodiments or features, examples of which are illustrated in the accompanying drawings. Generally, corresponding reference numbers may be used throughout the drawings to refer to the same or corresponding parts, e.g., 1, 1`, 1``, 101 and 201, could refer to one or more comparable components used in the same or different depicted embodiments.
[0015] Referring to FIGS. 1 and 2, exemplary cooling systems, i.e., a first cooling system 100 and a second cooling system 200 are respectively described. Several components and features and their working of the first cooling system 100 may be similar and/or identical to those of the second cooling system 200. Therefore, similar reference numerals may be used in the drawings wherever possible. For ease of reference and understanding, discussions in the present disclosure shall be mostly directed towards the first cooling system 100. Such discussions may be suitably applied to the second cooling system 200, as well. Wherever needed, reference to the second cooling system 200 shall also be specifically used. Also, difference between the first cooling system 100 and the second cooling system 200 shall be discussed later in the present disclosure. For ease, the first cooling system 100 may simply be referred to as system 100.
[0016] The system 100 may help achieve cooling in a zone, e.g., a first zone 104. Further, a second zone 108 may also be defined away from the first zone 104. In an example, the first zone 104 may include a room, e.g., a living room in which one or more users, such as human subjects, may be present. The first zone 104 may define a closed volume that needs to be cooled, while the second zone 108 may include any environment, but which may be outside to the first zone 104 – in other words, the first zone 104 may be intended to be separated and/or closed to the second zone 108. The system 100 may be used as an indirect evaporative cooler, as an adaptive indirect evaporative cooler, or as both. Aspects related to such usage shall be discussed further below.
[0017] The system 100 includes a first enclosure portion 112 and a second enclosure portion 116. The first enclosure portion 112 may be applied to cool the first zone 104, and the second enclosure portion 116 may be applied to expel heat retrieved from the first zone 104 into the second zone 108. Although not limited, the first enclosure portion 112 may be located, at least in part, within the first zone 104. Although not limited, the second enclosure portion 116 may be located, at least in part, within the second zone 108. Therefore, the first enclosure portion 112 may be referred to as an indoor unit and the second enclosure portion 116 may be referred to as an outdoor unit. Details related to each of the first enclosure portion 112 and the second enclosure portion 116 shall now be discussed in greater detail below.
[0018] The first enclosure portion 112 may define a first inner volume 120, a first entry 124, and a first exit 128. As an example, two first entries 124`, 124`` are exemplarily shown in FIG. 1. The first entry 124 and the first exit 128 may be fluidly coupled with the first inner volume 120 to be in fluid communication with the first inner volume 120. Further, the first enclosure portion 112 may include a first heat exchanger 132 and a first blower 136. In some embodiments, both the first heat exchanger 132 and the first blower 136 may be positioned within the first inner volume 120, although those skilled in the art may contemplate positions of one or more of the first heat exchanger 132 and the first blower 136 to be at least partly or fully outside the first inner volume 120 or outside the first enclosure portion 112, based on the contents of the present disclosure.
[0019] The first heat exchanger may define a first path 140 for passage of a fluid. To this end, the first heat exchanger 132 may be a conventional, fin type heat exchanger, having multiple cooling fins that are spaced apart from one another in a series and through which multiple tubes may be routed. The tubes may collectively define the first path 140, and the fluid (e.g., cooled fluid) may be passed into and/or may run through the tubes in and along the first path 140. In some embodiments, the fluid includes water. Further, the first heat exchanger 132 may define a primary side 144, e.g., a side which receives first air 152 into the first heat exchanger 132, and a secondary side 148, e.g., a side that releases the air processed by the first heat exchanger 132 out from the first heat exchanger 132.
[0020] The first blower 136 may have a hub and a set of blades structured and arrayed around the hub, as shown, that when powered to rotate (e.g., direction, R1) may deliver an air flow, e.g., a first air flow, FF, (e.g., including a cooled first air 138), therethrough. To this end, the first blower 136 may be configured to draw in the first air 152 through the first entry 124 and force the first air 152 to pass through (e.g., sequentially through) the first heat exchanger 132 and the first exit 128 as the cooled first air 138. Although not limited, the first blower 136 may be positioned downstream to the first heat exchanger 132, along a direction, F, of the first air flow from the first entry 124 to the first exit 128. By way of such arrangement of the first blower 136 and the first heat exchanger 132, the first blower 136 may be configured to maintain a relatively low-pressure region within the first inner volume 120, e.g., as compared to an outside of the first enclosure portion 112. Moreover, the first exit 128 may be positioned and/or be directed towards the first zone 104 to cool the first zone 104. The first air 152 may be drawn from an outside of the system 100 or an outside of the first enclosure portion 112. As an example, the first air 152 may be sourced from within the first zone 104.
[0021] Those skilled in the art may contemplate variations in the positions of the first blower 136 and the first heat exchanger 132 based on the contents of the present disclosure. For example, in some cases the first blower 136 may be positioned upstream to the first heat exchanger 132, and, in such cases, the first blower 136 may be conversely configured to maintain a relatively high-pressure region within the first inner volume 120, e.g., as compared to the outside of the first enclosure portion 112. Other variations in the positions of the first heat exchanger 132 and the first blower 136 that may achieve the intended results as are iterated in the present disclosure, may be contemplated by those of skill in the art. All such variations fall within the ambit of the claimed subject matter of the present disclosure.
[0022] In some embodiments, the system 100 and/or the first enclosure portion 112 includes a humidifier 156 and a de-humidifier 160. The humidifier 156 may include any presently available humidifier and which may be configured to increase the humidity of the first zone 104. As an example, the humidifier 156 may emit water droplets or steam into the first zone 104 to increase a moisture level of the air within the first zone 104 and thus raise humidity in the first zone 104. Other humidifiers now known or in the future developed may be applied. The de-humidifier 160 may include any presently available de-humidifier which may be conversely configured to reduce the humidity of the first zone 104. As an example, the de-humidifier 160 may extract water content or water traces, as may be present, in the first air flow (e.g., the cooled first air 138) that passes through the first exit 128 of the first enclosure portion 112. To this end, the de-humidifier 160 may include condensate dehumidifiers and/or desiccant dehumidifiers. Other de-humidifiers now known or in the future developed may be applied.
[0023] In some embodiments, the system 100 and/or the first enclosure portion 112 may include a first temperature sensor 164 to sense a temperature of the first zone 104. Also, the system 100 and/or the first enclosure portion 112 may include a first relative humidity sensor 168 to detect a first relative humidity of the first zone 104. To this end, the first relative humidity sensor 168 may sense, measure, and/or report a moisture value associated with the first zone 104. As an example, a ratio of moisture in the air in the first zone 104 to the highest amount of moisture at a particular air temperature in the first zone 104 may be used to calculate the relative humidity of the first zone 104.
[0024] The second enclosure portion 116 shall now be discussed. The second enclosure portion 116 may define a second inner volume 180, a second entry 184, and a second exit 188. As an example, two second entries 184`, 184`` are exemplarily shown in FIG. 1. The second entry 184 and the second exit 188 may be fluidly coupled with the second inner volume 180 to be in fluid communication with the second inner volume 180. Further, the second enclosure portion 116 may include a second heat exchanger 192 and a second blower 196. In some embodiments, both the second heat exchanger 192 and the second blower 196 may be positioned within the second inner volume 180, although those skilled in the art may contemplate positions of one or more of the second heat exchanger 192 and the second blower 196 to be at least partly or fully outside the second inner volume 180 or outside the second enclosure portion 116, based on the contents of the present disclosure.
[0025] The second heat exchanger 192 may define a second path 202 for passage of a heated fluid 198 (or heated water) entrained with the heat of the first air 152. In some embodiments, the second heat exchanger 192 may include an evaporative pad 204, such as a foam, etc. The evaporative pad 204 may define a porous structure, e.g., defining numerous pores, through which the heated fluid 198 may seep into the evaporative pad 204, be passed therethrough to move across the evaporative pad 204 (e.g., under gravity and/or capillary action), and exit the evaporative pad 204 or the second heat exchanger 192 as a cooled fluid volume 208. The second path 202 may be defined through the porous structure of the evaporative pad 204. Given the porous structure with the numerous pores of the evaporative pad 204, the second path 202 adopted by the heated fluid 198 to flow therethrough may not necessarily be a definite path, but rather any arbitrary path that offers the least resistance to the flow of the heated fluid 198. Also, the heated fluid 198 passing through the evaporative pad 204 may be open to come into contact with an interior environment 212 defined by the second inner volume 180 surrounding the evaporative pad 204.
[0026] As with the first blower 136, the second blower 196 may have a hub and a set of blades structured and arrayed around the hub, as shown, that when powered to rotate (see direction, R2) may deliver an air flow, e.g., a second air flow, SF, therethrough. The second blower 196 may be configured to draw in a second air 216 through the second entry 184 and force the second air 216 to pass through (e.g., sequentially through) the second heat exchanger 192 and the second exit 188 as expelled air 220 that carries away the heat from the heated fluid 198. Although not limited, the second blower 196 may be positioned downstream to the second heat exchanger 192, along a direction, S, of the second air flow from the second entry 184 to the second exit 188. By way of such arrangement of the second blower 196 and the second heat exchanger 192, the second blower 196 may be configured to maintain a relatively low-pressure region within the second inner volume 180, e.g., as compared to an outside of the second enclosure portion 116. Moreover, the second exit 188 may be positioned and/or be directed towards the second zone 108 for expelling the heat carried by the fluid (e.g., the heated fluid 198) into the second zone 108. The second air 216 may be drawn from an outside of the system 100 or an outside of the second enclosure portion 116, e.g., from the environment of the second zone 108.
[0027] Those skilled in the art may contemplate variations in the positions of the second blower 196 and the second heat exchanger 192 based on the contents of the present disclosure. For example, in some cases the second blower 196 may be positioned upstream to the second heat exchanger 192, and, in such cases, the second blower 196 may be conversely configured to maintain a relatively high-pressure region within the second inner volume 180 defined by the second enclosure portion 116, e.g., as compared to the outside of the second enclosure portion 116. Other variations in the positions of the second heat exchanger 192 and the second blower 196 that achieve the intended results iterated in the present disclosure, may be contemplated by those of skill in the art. All such variations fall within the ambit of the claimed subject matter of the present disclosure.
[0028] The second enclosure portion 116 may include a sump 224 that may catch the cooled fluid volume 208 exiting the evaporative pad 204 and/or the second heat exchanger 192. The sump 224 may be defined within the second enclosure portion 116, e.g., at a bottom of the second enclosure portion 116 such that the cooled fluid volume 208 exiting the evaporative pad 204 under the action of gravity can be caught and collected in the sump 224. The second enclosure portion 116 may also include a pump 228 (e.g., a fixed or a variable displacement pump), as shown. The pump 228 may be coupled with the sump 224 and may be configured to pump or supply the cooled fluid volume 208, collected in the sump 224, to the first heat exchanger 132. In so doing, a circulation of the fluid may be carried out between the first enclosure portion 112 and the second enclosure portion 116.
[0029] In some embodiments, the system 100 and/or the second enclosure portion 116 may include a second temperature sensor 232 to sense a second temperature of the second zone 108. General specifications of the second temperature sensor 232 may match with that of the first temperature sensor 164. Further, the system 100 and/or the second enclosure portion 116 may include a second relative humidity sensor 236 to detect a second relative humidity of the second zone 108. General specifications of the second relative humidity sensor 236 may match with that of the first relative humidity sensor 168.
[0030] Referring to FIG. 3, and in some embodiments, the system 100 includes a control system 250. The control system 250 may be communicatively coupled to the first temperature sensor 164, the first relative humidity sensor 168, the humidifier 156, and the de-humidifier 160. The control system 250 may also be communicatively coupled to the second temperature sensor 232 and the second relative humidity sensor 236. The control system 250 may also have access to a memory 254, e.g., to periodically retrieve one or more sets of instruction from the memory 254 in order to perform one or more functions as have been described herein. As an example, the control system 250 may be configured to compare the first relative humidity of the first zone 104 with a humidity range (e.g., see H1 and H2 in FIG. 4) defined by an ideal comfort area 258 (see FIG. 4) determined within a psychrometric chart 262 (see FIG. 4). The control system 250 may be configured to activate the humidifier 156 when at least one of: the first relative humidity is lower than the humidity range (e.g., H1 and H2) (e.g., lower than the lower limit, H2, of said humidity range) of the ideal comfort area 258; or the first relative humidity is within the humidity range (e.g., H1 and H2) of the ideal comfort area 258. Further, the control system 250 may be configured to deactivate the humidifier 156 when the first relative humidity is higher than the humidity range (e.g., H1 and H2) of the ideal comfort area 258.
[0031] Also, the control system 250 may be configured to activate the de-humidifier 160 when the first relative humidity is higher than the humidity range (e.g., H1 and H2) of the ideal comfort area 258. Further, the control system 250 is configured to deactivate the de-humidifier 160 when at least one of: the first relative humidity is lower than the humidity range (e.g., H1 and H2) of the ideal comfort area 258 or the first relative humidity is within the humidity range (e.g., H1 and H2) of the ideal comfort area 258. The arrows annotated as ‘Delhi’ and ‘Mumbai’ in relation to the ideal comfort area 258 in FIG. 4 indicates a general desire of users in those cities to move into zones (rooms, enclosed spaces, etc.) that offer the conditions of the ideal comfort area 258.
[0032] As a working example, if the first temperature is 35 °C and the first relative humidity is 60%, the control system 250 may determine that the first relative humidity is higher than the humidity range (e.g., 40% to 50%) of the ideal comfort area 258. As a result, the control system 250 may activate the de-humidifier 160 to bring the first relative humidity (and/or the heat index) in the first zone 104 to a comfortable range and may also parallelly deactivate the humidifier 156. Other examples may be contemplated. These values are provided for illustrative purposes alone and may include other values.
[0033] Further, the control system 250 may be configured to determine a wet bulb temperature (WBT) based on the second temperature and the second relative humidity. As an example, the WBT may be determined in regular intervals. This may be possible by running an alternate set of instruction from the memory 254. A manner in which the WBT may be determined based on temperature and relative humidity may be known to those skilled in the art and thus shall not be discussed. Further, the control system 250 may be configured to increase a speed of the second blower 196 when the WBT is below a primary WBT threshold (as may be predetermined and stored in the memory 254). Moreover, the control system 250 may also be configured to decrease the speed of the second blower 196 when the WBT is above a secondary WBT threshold (as may be predetermined and stored in the memory 254).
[0034] As a working example, if the second temperature is 40°C and the second relative humidity is 25%, by use of the below formula:

Tw = T*arctan [0. 151977*(RH+8. 313659)^0. 5] + 0. 00391838*(RH^3)^0. 5 *arctan (0. 023101*RH) – arctan (RH-1. 676331) + arctan (T+RH) - 4. 686035,

the WBT may be calculated as 24.4 °C. In such a case, the control system 250 may determine the WBT to be below the primary WBT threshold and thus may increase the speed of the second blower 196. In so doing, the second blower 196 may deliver the second air 216 at a relatively higher flow rate. As an example, if the initial flow rate of the second air 216 were 400 cubic feet per minute (CFM), the control system 250 may increase the speed of the second blower 196 such that the flow rate of the second air 216 may increase to 3500 CFM. Also, the control system 250 may control the pump 228 to increase a flow rate of the fluid (e.g., water) from 1 liter/minute to 10 liters/minute. These values are provided for illustrative purposes alone and may include other values.
[0035] The control system 250 may include a microprocessor-based device, or the control system 250 may be envisioned as an application-specific integrated circuit, or other logic devices, which provide controller functionality, and such devices or systems being known to those with ordinary skill in the art. In some embodiments, the set of instructions may be provided in any computer readable media, for example, any non-transitory computer readable media, and that when executed by the control system 250 may result in one or more of the functions of the control system 250, as has been described herein.
[0036] In one example, it is possible for the control system 250 to include or be representative of one or more controllers or control systems having separate or integrally configured processing units to process a variety of data, such as input or commands or signals incoming from the sensors. In some embodiments, a transmission of data between the sensors 164, 232 and the control system 250 and/or between the control system 250 and various other parts of the system 100 may be facilitated wirelessly or through a standardized CAN bus protocol. Although not limited, the control system 250 may be optimally suited for accommodation within certain panels or portions of the system 100 from where the control system 250 may remain accessible for ease of use, service, calibration, repairs, and replacements.
[0037] Processing units or any one or more processors associated with the control system 250, to convert or process various input, command, signals, etc., may include, but are not limited to, an X86 processor, a Reduced Instruction Set Computing (RISC) processor, an Application Specific Integrated Circuit (ASIC) processor, a Complex Instruction Set Computing (CISC) processor, an Advanced RISC Machine (ARM) processor, or any other processor now known or in the future developed.
[0038] Examples of the memory 254 may include a hard disk drive (HDD), and a secure digital (SD) card. Further, the memory 254 may include non-volatile/volatile memory units such as a random-access memory (RAM) / a read only memory (ROM), which may include associated input and output buses. The memory 254 may be configured to store various other instruction sets for various other functions of the system 100, along with the set of instruction, described above. Although not limited, the memory 254 may be configured within and may form part of the control system 250, in some cases.
INDUSTRIAL APPLICABILITY
[0039] Referring back to FIGS. 1 and 2, differences between the first cooling system 100 and the second cooling system 200 are discussed. With reference to the first cooling system 100, for example, the first enclosure portion 112 and the second enclosure portion 116 are separate and/or remote from each other. Further, the first enclosure portion 112 may be positioned, e.g., wholly positioned, within the first zone 104, while the second enclosure portion 116 may be positioned, e.g., wholly positioned, within the second zone 108 (and/or outside the first zone 104). If the first zone 104 were to include the room and the second zone 108 were to include the environment, noted above, the first enclosure portion 112 may be separated (e.g., physically separated) from the second enclosure portion 116 by one or more walls (e.g., see wall 266) of the room. Nonetheless, for the first cooling system 100, conduits 270, 274 respectively carrying the heated fluid 198 and the cooled fluid volume 208 may extend between the first enclosure portion 112 and the second enclosure portion 116, e.g., through said walls of the room.
[0040] With reference to the second cooling system 200, for example, the first enclosure portion 112 and the second enclosure portion 116 are integrated with each other to form a unitary structure 278. If the first zone 104 were to include the room and the second zone 108 were to include the environment, noted above, the unitary structure 278 of the first enclosure portion 112 and the second enclosure portion 116 may pass through a window 282 defined in one or more walls (e.g., wall 266) of the room. In so doing, the first enclosure portion 112 may be positioned, e.g., at least partly, within the first zone 104, while the second enclosure portion 116 may be positioned, e.g., at least partly, within the second zone 108. Although integrated to form the unitary structure 278, a divider 286 may demarcate a boundary between the first enclosure portion 112 and the second enclosure portion 116, as shown. The divider 286 may prevent a mixing of the first air 152 with the second air 216. In the second configuration, respective conduits 270`, 274` carrying the heated fluid 198 and the cooled fluid volume 208 may extend between the first enclosure portion 112 and the second enclosure portion 116, e.g., through the divider 286.
[0041] Referring to FIG. 6, and with continued reference to FIGS. 2 and 3, an exemplary method for achieving cooling in the first zone 104 is described. Said method is described by way of a flowchart 600 illustrated in FIG. 6. At block 602 of the flowchart 600, an operator uses the system 100 by applying the first enclosure portion 112 and the second enclosure portion 116. For brevity, details related to the first enclosure portion 112 and the second enclosure portion 116 are not discussed again. Further, at block 604 of the flowchart 600, the operator may position the first exit 128 associated with the first enclosure portion 112 towards the first zone 104 such that the cooled first air 138 is delivered into the first zone 104 for cooling the first zone 104. At block 606 of the flowchart 600, the operator may position the second exit 188 towards the second zone 108 for expelling the heat carried by the heated fluid 198 by way of the expelled air 220 into the second zone 108.
[0042] Generally, during operation, both the first blower 136 and the second blower 196 may be operational and they may correspondingly generate low pressure regions with the first inner volume 120 and the second inner volume 180. The pump 228 may also be active. An active pump (i.e., pump 228) may cause the fluid (e.g., water) to be pumped through the conduits 270, 274, the first heat exchanger 132, the second heat exchanger 192, and, particularly through the passages, i.e., along the first path 140 defined through the tubes and the second path 202 defined through the porous structure of the second heat exchanger 192 or the evaporative pad 204. With the first blower 136 being operational, the first air 152 may be drawn into the first enclosure portion 112 or into the first inner volume 120 and be forced to pass through the first heat exchanger 132, e.g., in a crossflow manner.
[0043] This may cause the fluid (e.g., the cooled fluid volume 208 sourced from the sump 224) passing through the tubes of the first heat exchanger 132 to come into contact (e.g., an indirect contact) with the first air 152, causing heat to be transferred from the first air 152 to said fluid. Consequently, a temperature of the first air 152, flowing downstream relative to the first heat exchanger 132 along a first air flow direction (see direction, FF), drops and/or may be cooled down. The cooled first air 138, as formed, flows downstream to the first heat exchanger 132 which may be then pushed out through the first exit 128 by way of the continued operation of the first blower 136.
[0044] Effectively, when the first air 152 passes through the first heat exchanger 132, the first air 152 indirectly contacts the fluid (e.g., the cooled fluid volume 208 from the sump 224) such that heat of the first air 152 entrains onto the fluid (e.g., water) and the ensuing cooled first air 138 flows downstream of the first heat exchanger 132 (e.g., by a suction generated within the first inner volume 120 by a working of the first blower 136). Cooled first air 138 then exits through the first exit 128. With the first exit 128 positioned towards the first zone 104, the cooled first air 138 exiting out from the first exit 128 of the first enclosure portion 112 into the first zone 104 may cool the first zone 104, in turn resulting in a temperature drop of the first zone 104.
[0045] As the heat of the first air 152 is transferred onto the fluid, the heated fluid 198 (entrained with the heat of the first air 152) is formed. A continuous pumping action offered by the pump 228 may push the heated fluid 198 through the conduit 270 such that the heated fluid 198 passes into the second heat exchanger 192 (e.g., into the evaporative pad 204). As a result, the second heat exchanger 192 or the evaporative pad 204 may receive the heated fluid 198 and/or may become drenched with the heated fluid 198. Under the action of gravity, for example, the heated fluid 198 may seep or flow further (e.g., in a downward direction as shown by way of the second path 202) into the second heat exchanger 192 or the evaporative pad 204, according to the second path 202.
[0046] As the heated fluid 198 passes through the second heat exchanger 192 or the evaporative pad 204, the heated fluid 198 may come in contact (e.g., direct contact) with the interior environment 212 surrounding the evaporative pad 204. Therefore, as the second blower 196 draws in the second air 216 into the second inner volume 180, the second air 216 passes through the second heat exchanger 192, directly contacting the heated fluid 198 moving along the second path 202 such that a volume of the heated fluid 198 is evaporated into the second air 216 and expelled out from the second exit 188. This causes a remaining volume of the heated fluid 198 within the second heat exchanger 192 or the evaporative pad 204 to cool down, e.g., to achieve a temperature close and/or equal to a wet bulb temperature (WBT). The ensuing cooled fluid volume 208 from the second heat exchanger 192 then passes into the sump 224, e.g., under gravity. The pump 228 then collects the cooled fluid volume 208 from the sump 224 and recirculates the cooled fluid volume 208 back into the first heat exchanger 132 such that the cooled first air 138 may continue to be delivered into the first zone 104.
[0047] By way of the aforementioned operation, the system 100 is able to achieve an indirect heat transfer between the fluid (e.g., water) and air (e.g., first air 152) via the first heat exchanger 132, utilizing a difference between dry bulb temperatures and wet bulb temperatures to achieve desired cooling in the first zone 104. The first enclosure portion 112 and second enclosure portion 116, as such, or when viewed in concert, may accordingly be an indirect evaporative cooler or a cooling system that supplies cooled first air into the first zone without any direct contact of the first air with any fluid or water. With the additional and/or optional control provided by way of the control system 250 that can increase or decrease the speed of the second blower 196 and/or activate or deactivate the humidifier 156 and de-humidifier 160, the system 100 may thus also be an adaptive indirect evaporative cooler or a cooling system that can change humidity levels in the first zone 104, providing effective humidity control in the first zone 104, e.g., based on the first relative humidity and/or the first temperature associated with the first zone 104, apart from lowering a temperature of the first zone 104.
[0048] In some embodiments, the control system 250 may be switched (e.g., by way of a switch) (not shown) between a power-off state and a power-on state. In the powered-on state of the control system 250, the system 100 may be used as the adaptive indirect evaporative cooler, providing improved cooling and humidity control. In the power-off state of the control system 250, the system 100 may be used as the indirect evaporative cooler.
[0049] Referring to FIG. 5, a graph 500 indicates an exemplary heat index variation in the first zone 104. The graph 500 includes three (3) curves, as shown, each of which are illustrated with respect to time and heat index – e.g., a first curve 504 illustrates a heat index variation associated with a conventional direct evaporative cooler over a period; a second curve 508 illustrates a heat index variation associated with the in-direct evaporative cooler as may be applied through the system 100 over a period, a third curve 512 illustrates a heat index variation associated with the adaptive indirect evaporative cooler as may be applied through the system 100 over a period.
[0050] Observing the first curve 504 for the normal direct evaporative cooler, it may be noted that in the first zone 104, the heat index decreases for an initial period but increases or curves upwards after the initial period. This is because the first zone 104 may become saturated with the humidity offered by the direct evaporative cooler after a period of use of the direct evaporative cooler, thus resulting in an increase in the heat index and discomfort to the users in the first zone 104. With the increase in the heat index, users in the first zone 104 may need to open windows, doors, etc., as may be available in the first zone 104, after said period of use of the direct evaporative cooler to retain comfort in the first zone 104.
[0051] Observing the second curve 508 for the in-direct evaporative cooler, it may be noted that in the first zone 104, the heat index decreases (e.g., continuously decreases according to a linear profile indicated by the second curve 508 and generally proportionally with time), and refrains from increase even after a period of use of the in-direct evaporative cooler. This is because moisture from any fluid associated with the system 100 is not transferred into the first zone 104 owing to an indirect contact of air (e.g., the first air 152) with a fluid (e.g., water or the cooled fluid volume 208). Therefore, the in-direct evaporative cooler applicable through the system 100 is advantageous over the normal direct evaporative cooler.
[0052] Observing the third curve 512 for the adaptive in-direct evaporative cooler, it may be noted that in the first zone 104, a rate of heat index reduction is even higher than what is achieved by way of the in-direct evaporative cooler for an initial period. Moreover, a continuous decrease in the heat index may be noted (e.g., also according to a linear profile as indicated by the third curve 512 and generally proportionally with time) even after said initial period and said heat index refrains from any increase even after a period of use of the adaptive in-direct evaporative cooler. This is because moisture from any fluid associated with the system 100 is not transferred into the first zone 104 owing to the indirect contact of air (e.g., the first air 152) with a fluid (e.g., water or the cooled fluid volume 208). Moreover, with the control system 250 adaptively humidifying and de-humidifying the first zone 104 based on the first temperature and the first relative humidity of the first zone 104, greater comfort is retained in the first zone 104. Accordingly, the adaptive indirect evaporative cooler applicable through the system 100 offers further advantages over the in-direct evaporative cooler.
[0053] The below tables, i.e., Table 1 and Table 2, show how the system 100 or the water based in-direct evaporative cooler lowers the temperature of the first zone 104 resepctively for two different conditions, e.g., Delhi & Mumbai. More particualrly, the tables exemplarily illustrate the effects of direct evaporative cooling, indirect evaporative cooler, indirect evaporative cooler with the humidifier and/or dehumidifier for 30 minutes of operation time in a closed room. The data is generated based on testing and/or multiple experiments.

Temperature (°C) Humidity (%RH) Heat Index
(°C)
Initial Conditions 40 25 41
Direct Evaporative Cooling 35 66 48
Water based Indirect Evaporative Cooling 35 35 36
Water based Indirect Evaporative Cooling + Humidifier 30 50 31
Table 1 – Delhi

Temperature (°C) Humidity (%RH) Heat Index
(°C)
Initial Conditions 35 60 45
Direct Evaporative Cooling 32 85 47
Water based Indirect Evaporative Cooling 33 67 42
Water based Indirect Evaporative Cooling + De-Humidifier 33 40 34
Table 2 - Mumbai

[0054] It may be noted that the humidifier 156 and/or de-humidifier 160 may interact with the air within the first zone 104 (which may be circulated through the first enclosure portion of the indirect evaporative cooler as applied by way of the system 100). A combination of the indirect evaporative cooling with the humidifier 156 and/or de-humidifier 160 helps cool the air of the first zone 104 while also optimizing the humidity within the first zone 104.
[0055] Effectively, the system 100 provides separate control over the temperature and humidity and also adaptively controls them to easily reach the ideal comfort area 258 for the users irrespective of the thermal conditions of the surrounding environment. The fluid being water (and not necessarily any conventional coolant or refrigerant applied in air conditioners) makes the system 100 compact, easy to maintain, and economical to use and own. Also, because the only things utilizing power are the pump and blowers, power consumption is relatively low, e.g., when compared with conventional air conditioning systems.
[0056] The in-direct contact between the fluid (e.g., water) passing through the first path 140 and the first air 152 refrains the cooled first air from creating sweatiness to users inside the first zone 104, as no moisture from the fluid is passed into the first zone 104. One or more of the aforementioned aspects make the system 100 applicable in a myriad of environmental condition (e.g., in both dry and humid climates as has been exemplarily illustrated in Table 1 and Table 2 above). Additionally, with no conventional coolant or refrigerant usage, the system 100 is environment friendly and reduces the overall carbon footprint, otherwise generally associated and/or observed with conventional air conditioning systems. In brevity, the system 100 combines the strengths of a conventional air conditioning system and an evaporative cooler, in turn establishing a way of providing enhanced providing comfort to users at reasonable costs.
[0057] Unless explicitly excluded, the use of the singular to describe a component, structure, or operation does not exclude the use of plural such components, structures, or operations or their equivalents. The use of the terms “a” and “an” and “the” and “at least one” or the term “one or more,” and similar referents in the context of describing the disclosure, especially in the context of the following claims, are to be construed to cover both the singular and the plural, unless otherwise indicated herein or clearly contradicted by context. The use of the term “at least one” followed by a list of one or more items (for example, “at least one of A and B” or one or more of A and B”) is to be construed to mean one item selected from the listed items (A or B) or any combination of two or more of the listed items (A and B; A, A and B; A, B and B), unless otherwise indicated herein or clearly contradicted by context. Similarly, as used herein, the word "or" refers to any possible permutation of a set of items. For example, the phrase "A, B, or C" refers to at least one of A, B, C, or any combination thereof, such as any of: A; B; C; A and B; A and C; B and C; A, B, and C; or multiple of any item such as A and A; B, B, and C; A, A, B, C, and C; etc.
[0058] It will be apparent to those skilled in the art that various modifications and variations can be made to the method or system of the present disclosure without departing from the scope of the disclosure. Other embodiments will be apparent to those skilled in the art from consideration of the specification and practice of the method or system disclosed herein. It is intended that the specification and examples be considered as examples only, with a true scope of the disclosure being indicated by the following claims and their equivalent. ,CLAIMS:1. A system (100) for achieving cooling in one or more zones, the system (100) comprising:
a first enclosure portion (112) defining a first entry (124) and a first exit (128), the first enclosure portion (112) including:
a first heat exchanger (132) defining a first path (140) for passage of a fluid;
a first blower (136) to draw in first air (152) through the first entry (124) and force the first air (152) to pass through the first heat exchanger (132) and the first exit (128),
wherein when the first air (152) passes through the first heat exchanger (132), the first air (152) indirectly contacts the fluid such that heat of the first air (152) entrains onto the fluid and an ensuing cooled first air (138) flows downstream of the first heat exchanger (132) and exits through the first exit (128);
a second enclosure portion (116) defining a second entry (184), a second exit (188), the second enclosure portion (116) including:
a sump (224);
a second heat exchanger (192) defining a second path (202) for passage of a heated fluid (198) entrained with the heat of the first air (152);
a second blower (196) to draw in second air (216) through the second entry (184) and force the second air (216) to pass through the second heat exchanger (192) and the second exit (188),
wherein when the second air (216) passes through the second heat exchanger (192), the second air (216) directly contacts the heated fluid (198) such that a volume of the heated fluid (198) is evaporated into the second air (216) and expelled out from the second exit (188), and an ensuing cooled fluid volume (208) from the second heat exchanger (192) passes into the sump (224); and
a pump (228) to supply the cooled fluid volume (208) from the sump (224) to the first heat exchanger (132) for a circulation of the fluid between the first enclosure portion (112) and the second enclosure portion (116).

2. The system (100) of claim 1, wherein
the first enclosure portion (112) either is integrated to the second enclosure portion (116) or is remote to the second enclosure portion (116);
the first exit (128) is positionable towards a first zone (104) of the one or more zones such that the cooled first air (138) is delivered into the first zone (104) for cooling the first zone (104); and
the second exit (188) is positionable towards a second zone (108) for expelling the heat carried by the fluid into the second zone (108).

3. The system (100) of claim 2 further including:
a humidifier (156);
a first temperature sensor (164) to sense a first temperature of the first zone (104);
a first relative humidity sensor (168) to detect a first relative humidity of the first zone (104); and
a control system (250) configured to:
compare the first relative humidity of the first zone (104) with a humidity range defined by an ideal comfort area (258) determined within a psychrometric chart (262);
activate the humidifier (156) when at least one of: the first relative humidity is lower than the humidity range of the ideal comfort area (258), the first relative humidity is within the humidity range of the ideal comfort area (258); and
deactivate the humidifier (156) when the first relative humidity is higher than the humidity range of the ideal comfort area (258).

4. The system (100) of claim 2 further including:
a de-humidifier (160);
a first temperature sensor (164) to sense a first temperature of the first zone (104);
a first relative humidity sensor (168) to detect a first relative humidity of the first zone (104); and
a control system (250) configured to:
compare the first relative humidity of the first zone (104) with a humidity range defined by an ideal comfort area (258) determined within a psychrometric chart (262);
activate the de-humidifier (160) when the first relative humidity is higher than the humidity range of the ideal comfort area (258); and
deactivate the de-humidifier (160) when at least one of: the first relative humidity is lower than the humidity range of the ideal comfort area (258) or the first relative humidity is within the humidity range of the ideal comfort area (258).

5. The system (100) of claim 2 further including:
a second temperature sensor (232) to sense a second temperature of the second zone (108);
a second relative humidity sensor (236) to detect a second relative humidity of the second zone (108); and
a control system (250) configured to:
determine a wet bulb temperature (WBT) based on the second temperature and the second relative humidity;
increase a speed of the second blower (196) when the WBT is below a primary WBT threshold; and
decrease the speed of the second blower (196) when the WBT is above a secondary WBT threshold.

6. The system (100) of claim 1, wherein the fluid includes water, the second heat exchanger (192) includes an evaporative pad (204) and the heated fluid (198) passing through the evaporative pad (204) is open and in contact with an interior environment (212) surrounding the evaporative pad (204), and both the first air (152) and the second air (216) are drawn from an outside of the system (100).

7. A method for achieving cooling in one or more zones, the method comprising:
using a cooling system (100), including:
applying a first enclosure portion (112) defining a first entry (124) and a first exit (128), the first enclosure portion (112) including:
a first heat exchanger (132) defining a first path (140) for passage of a fluid;
a first blower (136) to draw in first air (152) through the first entry (124) and force the first air (152) to pass through the first heat exchanger (132) and the first exit (128),
wherein when the first air (152) passes through the first heat exchanger (132), the first air (152) indirectly contacts the fluid such that heat of the first air (152) entrains onto the fluid and an ensuing cooled first air (138) flows downstream of the first heat exchanger (132) and exits through the first exit (128);
applying a second enclosure portion (116) defining a second entry (184) and a second exit (188), the second enclosure portion (116) including:
a sump (224);
a second heat exchanger (192) defining a second path (202) for passage of a heated fluid (198) entrained with the heat of the first air (152);
a second blower (196) to draw in second air (216) through the second entry (184) and force the second air (216) to pass through the second heat exchanger (192) and the second exit (188),
wherein when the second air (216) passes through the second heat exchanger (192), the second air (216) directly contacts the heated fluid (198) such that a volume of the heated fluid (198) is evaporated into the second air (216) and expelled out from the second exit (188), and an ensuing cooled fluid volume (208) from the second heat exchanger (192) passes into the sump (224);
a pump (228) to supply the cooled fluid volume (208) from the sump (224) to the first heat exchanger (132) for a circulation of the fluid between the first enclosure portion (112) and the second enclosure portion (116);
positioning the first exit (128) towards a first zone (104) of the one or more zones such that the cooled first air (138) is delivered into the first zone (104) for cooling the first zone (104); and
positioning the second exit (188) towards a second zone (108) for expelling the heat carried by the fluid into the second zone (108).

8. The method of claim 7, wherein the cooling system (100) includes:
a humidifier (156);
a first temperature sensor (164) to sense a first temperature of the first zone (104);
a first relative humidity sensor (168) to detect a first relative humidity of the first zone (104); and
a control system (250) configured to:
compare the first relative humidity of the first zone (104) with a humidity range defined by an ideal comfort area (258) determined within a psychrometric chart (262);
activate the humidifier (156) when at least one of: the first relative humidity is lower than the humidity range of the ideal comfort area (258), the first relative humidity is within the humidity range of the ideal comfort area (258); and
deactivate the humidifier (156) when the first relative humidity is higher than the humidity range of the ideal comfort area (258).

9. The method of claim 7, wherein the cooling system (100) includes:
a de-humidifier (160);
a first temperature sensor (164) to sense a first temperature of the first zone (104);
a first relative humidity sensor (168) to detect a first relative humidity of the first zone (104); and
a control system (250) configured to:
compare the first relative humidity of the first zone (104) with a humidity range defined by an ideal comfort area (258) determined within a psychrometric chart (262);
activate the de-humidifier (160) when the first relative humidity is higher than the humidity range of the ideal comfort area (258); and
deactivate the de-humidifier (160) when at least one of: the first relative humidity is lower than the humidity range of the ideal comfort area (258) or the first relative humidity is within the humidity range of the ideal comfort area (258).

10. The method of claim 7, wherein the cooling system (100) includes:
a second temperature sensor (232) to sense a second temperature of the second zone (108);
a second relative humidity sensor (236) to detect a second relative humidity of the second zone (108); and
a control system (250) configured to:
determine a wet bulb temperature (WBT) based on the second temperature and the second relative humidity;
increase a speed of the second blower (196) when the WBT is below a primary WBT threshold; and
decrease the speed of the second blower (196) when the WBT is above a secondary WBT threshold.