Patent Application
20210380390
Embodiments described herein generally relate to a chiller for cooling a beverage that has a compact size. Specifically, embodiments described herein relate to a chiller that includes one or more chiller coils through which a beverage flows and an evaporator coil for circulating a coolant that includes projections for facilitating heat transfer from the chiller coils to the evaporator coil.
Chillers are used to cool and dispense a beverage. Some chillers operate by cooling a quantity of a beverage in a reservoir prior to dispensing the beverage. When a consumer desires a beverage, a portion of the pre-cooled beverage is simply dispensed from the reservoir.
Chillers that require a reservoir for storing pre-cooled beverages have several drawbacks. The reservoir consumes substantial space, increasing the size of the chiller. This may be undesirable when providing a chiller for a home or office setting. Further, cooling the quantity of beverage within the reservoir may take an extended period of time. Once the stored quantity of pre-cooled beverage is dispensed, the consumer must wait for a period of time until a new batch of the beverage is cooled.
Accordingly, there is a need in the art for a chiller that has a small form factor and that can rapidly chill a beverage in seconds and dispense the chilled beverage on a continuous basis.
Some embodiments described herein relate to a chiller for cooling a beverage, wherein the chiller includes a reservoir configured to hold a heat exchange fluid, and an evaporator coil arranged within the reservoir. The evaporator coil of the chiller includes a plurality of windings configured to circulate a coolant, and projections extending from an exterior surface of one or more of the plurality of windings. The chiller further includes a chiller coil arranged in the reservoir, wherein the beverage is configured to flow through the chiller coil, and wherein when the coolant is circulated through the plurality of windings of the evaporator coil, a bank of frozen heat exchange fluid forms on the plurality of windings and on the projections.
In any of the various embodiments described herein, the projections may include one or more fins.
In any of the various embodiments described herein, the projections may include one or more rods.
In any of the various embodiments described herein, the projections may include a lattice structure.
In any of the various embodiments described herein, the evaporator coil may be formed from a first material, and the projections may be formed from a second material, and the first material may be the same as the second material.
In any of the various embodiments described herein, the evaporator coil may define a central volume, and the chiller coil may be arranged within the central volume of the evaporator coil.
In any of the various embodiments described herein, the chiller may further include a second chiller coil arranged in the reservoir, wherein the beverage is configured to flow through the second chiller coil. In some embodiments, the chiller may further include a splitter configured to divide a flow of the beverage to the first chiller coil and to the second chiller coil, wherein the splitter divides the flow of the beverage such that a greater portion of the beverage flows to the first chiller coil than to the second chiller coil.
In any of the various embodiments described herein, a wall thickness of the chiller coil may be in a range of about 0.2 mm to about 1.0 mm.
In any of the various embodiments described herein, the reservoir of the chiller may have a total volume of about 3 L to about 10 L.
In any of the various embodiments described herein, the chiller further includes an agitator arranged in the reservoir, wherein the agitator may include an impeller having one or more blades. In some embodiments, the chiller further includes a temperature sensor configured to determine a temperature of the chiller coil, wherein the agitator is configured to operate when a temperature of the chiller coil as detected by the temperature sensor is in a predetermined temperature band.
Some embodiments described herein relate to a beverage dispenser that includes a user interface configured to receive a selection of a beverage and a chiller configured to cool a beverage. The chiller of the beverage dispenser includes a reservoir configured to store a heat exchange fluid, an evaporator coil arranged within the reservoir and configured to circulate a coolant, wherein the evaporator coil includes a plurality of windings and projections extending from an exterior surface of one or more of the plurality of windings of the evaporator coil. The chiller of the beverage dispenser further includes a chiller coil arranged within the reservoir, wherein the beverage flows through the chiller coil such that the beverage is cooled as the beverage flows through the chiller coil, and wherein when the coolant is circulated through the evaporator coil, a bank of frozen heat exchange fluid forms on the evaporator coil and on the projections. The beverage dispenser further includes a dispensing nozzle in communication with the chiller coil for dispensing the beverage.
In any of the various embodiments described herein, the beverage dispenser may further include a cooling system configured to circulate the coolant, and the cooling system may include the evaporator coil.
In any of the various embodiments described herein, the beverage dispenser may further include a carbonator configured to carbonate the beverage, wherein the carbonator is in communication with the chiller coil.
Some embodiments described herein relate to a chiller for cooling a beverage that includes a reservoir, and a heat exchange fluid stored within the reservoir, wherein the heat exchange fluid is an ionic liquid having a freezing point about 0° C. The chiller further includes an evaporator coil arranged within the reservoir, the evaporator coil including a plurality of windings configured to circulate a coolant, and projections extending from an exterior surface of one or more of the plurality of windings. The chiller further includes a chiller coil arranged in the reservoir, wherein the beverage flows through the chiller coil, and wherein when the coolant is circulated through the windings of the evaporator coil, at least a portion of the heat exchange fluid freezes into a solid phase.
In any of the various embodiments described herein, the heat exchange fluid may have a freezing point between about 0.01° C. and about 5° C.
In any of the various embodiments described herein, the ionic liquid may be selected from the group of 1-butyl-3-methylimidazolium based ionic liquids, imidazolium based ionic liquids, pyridinium based ionic liquids, and morpholine based ionic liquids.
In any of the various embodiments described herein, the ionic liquid may have a latent heat of fusion in a range of about 200 kJ/kg to about 300 kJ/kg.
In any of the various embodiments described herein having an ionic liquid, when the coolant is circulated through the windings of the evaporator coil, all of the heat exchange fluid may freeze into a solid phase.
The accompanying drawings, which are incorporated herein and form a part of the specification, illustrate the present disclosure and, together with the description, further serve to explain the principles thereof and to enable a person skilled in the pertinent art to make and use the same.
Reference will now be made in detail to representative embodiments illustrated in the accompanying drawings. It should be understood that the following descriptions are not intended to limit the embodiments to one preferred embodiment. To the contrary, it is intended to cover alternatives, modifications, and equivalents as can be included within the spirit and scope of the described embodiments as defined by the claims.
There is an increasing demand for in-home or in-office beverage chillers. In order to provide a chiller for home or office use, the chiller must have a small form factor so that the chiller can be installed on a countertop, such as a kitchen counter. Chillers having a reservoir of pre-cooled beverage, such as carbonated or non-carbonated water, are typically large and are impractical for use in home or office settings.
The footprint of the chiller can be greatly reduced if the reservoir of the pre-cooled beverage is eliminated and instead the beverage is chilled on-demand, i.e., as the beverage is being dispensed. A beverage can be cooled very rapidly and on-demand by passing a beverage through a coil arranged in a reservoir containing a heat exchange fluid, such as water, to remove the heat from the beverage as the beverage passes through the coil. Some chillers may use heat exchange fluid to cool a beverage, but may rely on large reservoirs of 20 L of heat exchange fluid or more. As a result, beverage dispensers that use such chillers are not practical for home or office settings, and are instead used in commercial kitchens, such as in restaurants or bars. Thus, to maintain a small footprint, the beverage dispenser chiller must use a small chiller reservoir for storing the heat exchange fluid.
However, cooling a quantity of liquid to a desired temperature, such as 5° C. or less, in an on-demand basis and with a relatively small quantity of heat exchange fluid presents numerous design and engineering challenges, particularly as larger volumes of beverage or higher flow rates of beverage are desired to be dispensed. Further, as the solubilization of carbon dioxide decreases significantly with increasing temperature, a carbonated beverage has to be chilled to 5° C. or less to maintain sufficient carbonation for carbonated beverages and to avoid excessive foaming.
The heat exchange in the chiller must be sufficient to cool the beverage in a few seconds as the beverage flows through the chiller, and the chiller must be sufficient to cool large volumes of the beverage. A chiller can be rated by its compact ratio coefficient which may refer to the ratio of the maximum cold water volume that can be dispensed at or below 5° C. in one hour to the volume of the chiller. Thus, it is desired to produce a chiller having a high compact ratio coefficient, indicating that the volume of liquid that can be dispensed at or below 5° C. in one hour is large relative to the volume of the chiller.
The inventors of the present application found that the compact ratio coefficient can be increased by maximizing heat exchange within the chiller. By increasing heat exchange efficiency, a chiller can be designed with a smaller footprint while producing the same volume of chilled beverage, or alternatively the volume of chilled beverage that can be dispensed can be increased without increasing the size of the chiller.
Some embodiments described herein relate to a chiller that includes an evaporator coil having projections such that a bank of frozen heat exchange fluid can be formed on the evaporator coil and additionally on the projections. In this way, the surface area of the bank of frozen heat exchange fluid may be increased relative to a bank of frozen heat exchange fluid formed on the evaporator coil alone. The increased surface area of the bank of frozen heat exchange fluid may increase heat transfer between the evaporator coil and chiller coil to promote cooling of the beverage in the chiller coil. Some embodiments described herein relate to a chiller that includes an evaporator coil having projections with a reticular structure that facilitates formation of the frozen bank of heat exchange fluid on the projections. The reticular structure of the projections increases the thermal conductivity of the bank of frozen heat exchange fluid, allowing the bank of frozen heat exchange fluid to form more rapidly.
As used herein, the term “beverage” may refer to any of various consumable liquids, including but not limited to carbonated water, non-carbonated water (e.g., still water), flavored or enhanced waters, juice, coffee or tea-based beverages, sports drinks, energy drinks, sodas, dairy or dairy-based beverages (e.g., milk), among others.
As used herein, the term “coolant” may refer to any fluid configured to reduce the temperature of the heat exchange fluid, such as a refrigerant, particularly a refrigerant with low global warming potential (GWP) and/or ozone depletion potential (ODP), including among others, R600a, R134a, R290, R744, R32, and mixtures thereof, such as a mixture of R290/R744.
As used herein, the term “heat exchange fluid” may refer to a substance configured to drive an exchange of heat from a liquid within the chiller coil, such as a beverage. For example, the heat exchange fluid may include water that may vary in total dissolved solids and/or pH to impact melting conditions and ice structure, a water and alcohol mixture, or ionic liquids, among others.
In some embodiments, a chiller as described herein may be configured to lower the temperature of a beverage by 20° C. or more. The chiller may be configured to lower the temperature of a beverage from ambient temperature, e.g., about 25° C., to 5° C. or less in 10 seconds or less, in 8 seconds or less, or in 4 seconds or less. In some embodiments, when chiller is initially started, a bank of frozen heat exchange fluid may form within the reservoir of the chiller in 80 minutes or less, 60 minutes or less, or 40 minutes or less. In this way, the chiller has a rapid start-up time and can begin cooling beverages shortly after start-up. Further, the chiller can quickly regenerate the bank of frozen heat exchange fluid when depleted.
Some embodiments herein are directed to a chiller 100 that includes a reservoir 110 configured to hold a heat exchange fluid, as shown in
Reservoir 110 is configured to hold a heat exchange fluid that facilitates heat transfer between a beverage flowing through chiller coil 130 and evaporator coil 160 of chiller 100. In some embodiments, the heat exchange fluid may be water. The use of water as the heat exchange fluid may facilitate maintenance of chiller 100, as water is non-toxic and can be easily drained and replaced by the end user.
In some embodiments, reservoir 110 of chiller 100 may have a total interior volume of about 3 L to about 10 L. Reservoir 110 may be configured to hold about 2 L to about 9 L of heat exchange fluid, about 2.5 L to about 8 L of heat exchange fluid, or about 3 L to about 7 L of heat exchange fluid. As the total size of chiller 100 depends largely on the size of reservoir 110, the use of a small reservoir 110 and a small quantity of heat exchange fluid allows chiller 100 to have a compact form factor, suitable for use in a home or office setting, such as on a kitchen countertop, under a kitchen sink, or built-into a kitchen cabinet.
Reservoir 110 of chiller 100 may have any of various shapes, and may be shaped as a rectangular prism, a cube, or a cylinder, among others. Reservoir 110 may be thermally insulated so as to inhibit or minimize transfer of heat external to chiller 100 into chiller 100. Reservoir 110 may include a lid that provides access to an interior volume of reservoir 110, such as for filling or replacing heat exchange fluid or performing maintenance or repair of components within reservoir 110. However, in some embodiments, reservoir 110 may be sealed so that the interior volume of reservoir 110 is not accessible by the end user.
The components of a chiller 100 according to some embodiments are shown in
Evaporator coil 160 of chiller 100 is configured to circulate a coolant as part of a cooling system 800. Cooling system 800 may be a vapor-compression cooling system and may include, in addition to an evaporator coil 160, a compressor 810, a condenser 820, and an expansion valve 830, as will be appreciated by one of ordinary skill in the art. As coolant flows through evaporator coil 160 changing in phase from liquid to vapor, heat exchange fluid surrounding evaporator coil 160 freezes, forming a bank of frozen heat exchange fluid (see, e.g.,
In some embodiments, evaporator coil 160 may be a tube having a plurality of windings 162 arranged in a stacked configuration as shown for example in
A chiller coil 130 may be arranged within reservoir 110 of chiller 100. Chiller coil 130 may be arranged in a nested configuration with evaporator coil 160. As shown in
In some embodiments, evaporator coil 160 includes one or more projections 170 extending from an exterior surface 161 of evaporator coil 160. Projections 170 may extend from evaporator coil 160 in a direction toward chiller coil 130, as shown in
In operation of chiller 100, coolant flows through evaporator coil 160 and evaporates, causing heat exchange fluid 710 surrounding evaporator coil 160 to freeze and form a bank 720 of frozen or solid-phase heat exchange fluid (see, e.g.,
In some embodiments, projections may be formed as fins 172, as shown in
In some embodiments, evaporator coil 160 may include projections 170 formed as rods 178, as shown for example in
Projections 170 may be formed from a material having a high thermal conductivity. Projections 170 may be formed from the same material as evaporator coil 160. For example, in embodiments in which evaporator coil 160 is formed from copper, projections 170 may also be formed from copper. As heat exchange fluid freezes around windings 162 of evaporator coil 160, heat exchange fluid may also freeze around projections 170. As a result, a surface area of the bank of frozen heat exchange fluid is increased due to the freezing of heat exchange fluid around projections 170.
In some embodiments, projections 170 may be formed from heat pipes. Heat pipes may serve to promote rapid formation of frozen heat exchange fluid on projections 170 as well as rapid heat transfer in proximity of chiller coil. A heat pipe may include a hollow tube defining an enclosed interior volume and a working fluid arranged within the interior volume configured to be a vapor and a liquid in the operating temperature range. The working fluid inside the heat pipe may be selected based on the range of operating temperatures, and may be for example, ammonia, alcohol, or water, among other suitable fluids. The heat pipe may be arranged in the same manner as rods 178, and thus may extend radially from an exterior surface of evaporator coil 160 into central volume 164 towards the chiller coil.
In some embodiments, projections 170 may be solid such that projections 170 have no openings that would allow heat exchange fluid to flow into or through projections 170. In some embodiments, projections 170 may have a reticular structure such the body 171 of projection 170 has a plurality of openings or pores 173, as shown for example in
In some embodiments, chiller coil 130′ rather than evaporator coil may include projections 170′, as shown for example in
In some embodiments, as shown in
In some embodiments, a chiller 200 may be formed as shown in
Chiller coil 230 of chiller 200 may follow a perimeter of reservoir 210. As a result, the length of chiller coil 230 within reservoir 210 may be longer relative to chiller coil 130 of chiller 100. Thus, chiller 200 may have the same footprint as chiller 100 while allowing a greater volume of beverage to be cooled by chiller 200 at a given time. Further, bank 720 formed on evaporator coil 260 may be more compact in chiller 200. Bank 720 formed on evaporator coil 260 may maintain an open central area within evaporator coil 260 to allow heat exchange fluid to circulate within the central area of evaporator coil 260 and to provide space for an agitator.
Evaporator coil 260 of chiller 200 may include projections 270. Projections 270 may have the same arrangement, construction, and features as described above with respect to evaporator coil 160 and projections 170. However, as projections 270 extend from an exterior surface of evaporator coil 260 in a direction toward chiller coil 230, projections 270 extend outward from evaporator coil 260 toward chiller coil 230, whereas projections 170 of evaporator coil 160 of chiller 100 extend inward toward central volume 164 of evaporator coil 160.
In some embodiments, evaporator coil 260 of chiller 200 may include projections 270 that include a foam 278, as shown for example in
While exemplary chillers 100, 200 are described herein for the purposes of illustration, it is understood that other arrangements of an evaporator coil and one or more chiller coils within the reservoir of the chiller are possible. Further, it is understood that the heat exchange efficiency of any chiller having an evaporator coil may be improved by incorporating projections as described herein. In some embodiments, heat exchange efficiency of a chiller having a reservoir, an evaporator coil, and a chiller coil may be enhanced by attaching one or more projections as described herein to an exterior surface of the evaporator coil. In this way, when coolant is circulated through the evaporator coil, a bank of frozen heat exchange material, such as an ice bank, may rapidly form along the evaporator coil and also along the projections to increase the surface area of the bank and thus the interface of the heat exchange fluid in solid and liquid states. In some embodiments, heat transfer efficiency of a chiller having a reservoir, an evaporator coil, and a chiller coil may be enhanced by attaching projections as described herein to an exterior surface of the chiller coil. In this way, the projections provide conductive heat transfer and increase a surface area for heat transfer with chiller coil.
Some embodiments described herein relate to a chiller 300 having a swirl tube 390 configured to facilitate circulation of heat exchange fluid 710 within reservoir 310, as shown in
Chiller 300 may further include a pump 380 configured to circulate heat exchange fluid within reservoir 310. Pump 380 may be submerged within the heat exchange fluid 710 in reservoir 310. In some embodiments, pump 380 may be arranged at a lower end 311 of reservoir 310. Pump 380 may include an intake 382 configured to draw heat exchange fluid 710 from reservoir 310 into pump 380. Pump 380 and intake 382 of pump 380 may be arranged so as to draw heat exchange fluid 710 from a central volume 334 defined by chiller coil 330. Thus, pump 380 or intake 382 of pump 380 may be arranged within central volume 334 of chiller coil 330. Pump 380 may include one or more outlets for ejecting heat exchange fluid 710 so as to circulate heat exchange fluid 710. The outlets may be arranged so as to direct heat exchange fluid 710 in a lateral direction.
In some embodiments, a swirl tube 390 may be in communication with pump 380 and may extend from pump 380 into a space between chiller coil 330 and evaporator coil 360. Chiller coil 330 may be tightly wound so that there is limited space between windings 332 of chiller coil 330. As a result, heat exchange fluid 710 in central volume 334 of chiller coil 330 may not easily circulate within reservoir 310. This may inhibit heat transfer from heat exchange fluid 710 in central volume 334 to the bank of frozen heat exchange material formed on evaporator coil 360 and projections 370.
In some embodiments, pump 380 may be configured to draw heat exchange fluid 710 from central volume 334 and disperse heat exchange fluid 710 toward the bank of frozen heat exchange fluid via a swirl tube 390. Swirl tube 390 may include one or more windings. Swirl tube 390 may be composed of a flexible material. Windings of swirl tube 390 may be spaced to a greater extent than windings of chiller coil 330 or evaporator coil 360 so that swirl tube 390 does not impact circulation of heat exchange fluid 710 within reservoir 310. Swirl tube 390 may include one or more outlets 392. Swirl tube 390 may include an outlet 392 at a terminal end 394 of swirl tube 390. Additional outlets 392 may be arranged along a length of swirl tube 390. Each outlet 392 may be arranged so that heat exchange fluid that escapes outlet 392 is directed toward a projection 370 of evaporator coil 360. In this way, the relatively warm heat exchange fluid from central volume 334 of chiller coil 330 is directed to the bank of frozen heat exchange fluid 710. This helps to induce turbulence and promote heat transfer and circulate heat exchange fluid 710 within reservoir 310. This may help to cool down the beverage faster at start-up and while beverage is being dispensed.
In some embodiments, as shown in
In some embodiments, a chiller 400 is shown for example at
In some embodiments, evaporator coil 460 of chiller 400 may be a tube having a plurality of windings 462 through which a coolant may flow. Windings 462 may be arranged in a stacked configuration from a lower end of reservoir 410 toward an upper end of reservoir 410. Windings 462 may extend around a central axis X. In operation of chiller 400, windings 462 are submerged in the heat exchange fluid. Evaporator coil 460 may be arranged along a perimeter of reservoir 410. Thus, evaporator coil 460 may be arranged adjacent to and follow an interior wall of reservoir 410. Evaporator coil 460 may have a shape that corresponds to a shape of reservoir 410. For example, if reservoir 410 has a rectangular shape, evaporator coil 460 may similarly have a rectangular shape, as best shown in
Evaporator coil 460 may further include projections 470 extending from an exterior surface of windings 462 of evaporator coil 460. In some embodiments, projections 470 may extend into central volume 464 defined by evaporator coil 460 and toward chiller coil 430. As shown in
Fins 474 may be spaced from one another at a distance greater than a thickness of the bank of frozen heat exchange fluid to be formed on fins 474 so that bank does not completely fill space between fins 474 and liquid heat exchange fluid may flow in a space between adjacent fins 474. Similarly, rods 476 may be spaced from one another at a distance that is greater than a thickness of the bank of frozen heat exchange fluid to be formed on rods 476 so that bank does not completely fill space between rods 476 and liquid heat exchange fluid may between rods 476. If fins 474 or rods 476 are spaced too closely together, bank of frozen heat exchange fluid may leave little or no space through which heat exchange fluid may flow. In some embodiments, fins 474 may be spaced from one another by about 10 mm to about 30 mm, by about 12 mm to about 28 mm, or by about 15 mm to about 25 mm. In some embodiments, rods 476 may be spaced from one another by about 8 mm to about 24 mm, by about 10 mm to about 22 mm, or by about 12 mm to about 20 mm.
In some embodiments, lattice structure 472 including fins 474 and rods 476 may be formed as a unitary structure. Lattice structure 472 may be joined to windings 462 of evaporator coil 460 by welding or brazing, among other fastening methods. In some embodiments, lattice structure 472 may be formed of the same material as evaporator coil 460. In this way, heat transfer is the same in the material of evaporator coil 460 and lattice structure 472. In some embodiments, evaporator coil 460 and lattice structure 472 may include copper.
Without being desired to be bound by theory, the formation of bank of frozen heat exchange fluid, e.g., ice, on evaporator coil 460 will now be described. When chiller 400 is in use, coolant flows through windings 462 of evaporator coil 460 and evaporates at a predetermined temperature. The process of evaporation of the coolant absorbs a significant amount of heat from the heat exchange fluid and as a result a bank of frozen heat exchange fluid first begins to form around an exterior of windings 462 of evaporator coil 460. As material of lattice structure 472 is cooled, bank quickly continues to form along fins 474 of lattice structure 472. Bank may proceed to form along an external surface of rods 476 of lattice structure 472 extending between adjacent fins 474.
The resulting frozen bank of heat exchange fluid defines channels 478 through which liquid heat exchange fluid may flow. Lattice structure 472 serves to increase the surface area of the frozen bank of heat exchange fluid (relative to a bank of heat exchange fluid formed on windings of evaporator coil alone) in order to promote heat transfer from a beverage in chiller coil 430 through heat exchange fluid and to the frozen bank of heat exchange fluid. Further, lattice structure 472 provides sufficient space to allow liquid heat exchange fluid to flow through lattice structure 472 to contact bank of frozen heat exchange fluid.
In some embodiments, lattice structure 480 may define cells 488, as shown for example in
In some embodiments, chiller 400 may include a plurality of chiller coils 430, 440 each having a plurality of windings 434, 444 arranged in reservoir 410. As shown in
Chiller coils 430, 440 may be arranged in a central volume 464 defined by evaporator coil 460. In this way, evaporator coil 460 at least partially surrounds chiller coils 430, 440. Each chiller coil 430 may include a plurality of windings 434 arranged in a stacked configuration (see, e.g.,
In some embodiments, chiller coils 430, 440 may be arranged in a nested configuration, as shown in
In some embodiments, a total length of chiller coils 430, 440 in chiller 400 may be about 8 meters to about 18 meters, about 10 meters to about 16 meters, or about 12 meters to about 14 meters. Increasing the total length of chiller coil 430 in reservoir 410 increases the amount of beverage that can be cooled in a given time. Second chiller coil 440 may have a length that is smaller than that of the first chiller coil 430 as the second chiller coil 440 may have a smaller diameter than first chiller coil 430, as shown for example in
In some embodiments, first chiller coil 430 may include a first inlet 431 and a first outlet 432, and second chiller coil 440 may include a second inlet 441 and a second outlet 442. Thus, first and second chiller coils 430, 440 may define two separate flow paths through which a beverage may flow in order to be cooled by chiller 400. In such embodiments, chiller 400 may further include a splitter 408 configured to divide an incoming supply of beverage between chiller coils 430, 440. First chiller coil 430 may have a greater ability to transfer heat due to its closer proximity to evaporator coil 460 and longer total length relative to second chiller coil 440. As a result, splitter 408 may provide a greater portion of the incoming beverage to first chiller coil 430 than to second chiller coil 440. For example, splitter 408 may provide 60% or more, 65% or more, or 70% or more of the incoming flow of beverage to first chiller coil 430 and the remainder to second chiller coil 440. Splitter 408 may divide the flow of the beverage between the two chiller coils 430, 440 so that the temperature of the beverage at both outlets 432, 442 is substantially the same.
In some embodiments, first outlet 432 of first chiller coil 430 may be in communication with second inlet 441 of second chiller coil 440, or vice versa, so that chiller coils 430, 440 form one continuous flow path through which a beverage may flow. In such embodiments, the same quantity of beverage may be cooled at a given time as in embodiments having first and second chiller coils 430, 440 defining separate flow paths. However, the pressure drop over one long, continuous flow path may be relatively high in comparison to the pressure drop over two separate flow paths having the same length, which may require a stronger pump to circulate the beverage.
In some embodiments, chiller coils 430, 440 may include one or more connectors 450 configured to facilitate heat transfer and to maintain the spacing of the windings of chiller coils 430, 440. In some embodiments, connectors 450 may include first connectors 452 that connect first and second chiller coils 430, 440 to one another. First connectors 452 extend through gap 438 and may help to equalize heat transfer of first and second chiller coils 430, 440. As first chiller coil 430 is closer to evaporator coil 460, first chiller coil 430 may tend to have a lower temperature and first connector 452 provides conductive heat transfer between first and second chiller coils 430, 440. First connectors 452 may include a rod or plate having a first end connected to a first chiller coil 430 and a second end connected to second chiller coil 440. In some embodiments, a plurality of first connectors 452 may be arranged at upper end of chiller coils 430, 440 and a second plurality of first connectors 452 may be arranged at lower end of chiller coils 430, 440. First connectors 452 may be arranged in a plane that is generally transverse to a longitudinal axis of chiller 400. In some embodiments, first connectors 452 may be the same material as chiller coils 430, 440, e.g., stainless steel. However, in some embodiments, first connectors 452 may be copper or another metal having a high thermal conductivity.
Further, in some embodiments, each chiller coil 430, 440 may include a second connector 454 that extends along an exterior surface of chiller coil 430, 440 in a direction parallel to a central axis of evaporator coil 460. Second connector 454 may help to equalize heat transfer among the different windings of the same chiller coil 430, 440. Further, second connector 454 may help to maintain spacing between adjacent windings 434, 444.
Chiller coils may be constructed to maximize heat transfer between the beverage within chiller coils and heat exchange fluid in reservoir 410. The rate at which heat is extracted from the beverage flowing through chiller coil 430 depends on several factors, including the material of chiller coil 430, an inner diameter of the coil 430, and a wall thickness of chiller coil 430. While it is understood that chiller 400 may have multiple chiller coils, for simplicity the following discussion will refer to a single chiller coil 430.
In some embodiments, the chiller coil 430 may be formed of stainless steel, such as a 300-series or 400-series stainless steel. Stainless steel provides a high corrosion resistance and results in little to no contamination of the beverage in contact with chiller coil 430. Further, stainless steel has a relatively high thermal conductivity to facilitate transfer of heat through chiller coils.
A cross sectional area of a chiller coil 430 according to an embodiment is shown in
The wall thickness tw of each chiller coil 430 may be selected to facilitate transfer of heat from a beverage within chiller coil 430 to heat exchange fluid in reservoir 410. Wall thickness tw may be defined as the shortest distance in a radial direction from an inner surface 436 of chiller coil 430 to an exterior surface 439 of chiller coil 430, as shown in
In some embodiments, chiller 400 may provide countercurrent heat exchange of beverage through chiller coil 430 in reservoir 410 to maximize the decrease in temperature of the beverage in chiller coil. In such embodiments, beverage may flow through chiller coil 430 from lower end toward an upper end of chiller coil 430. Thus, the beverage flows in a generally upward direction through chiller coil 430. Temperature of heat exchange fluid in reservoir 410 may be relatively low at upper end of reservoir 410 and relatively high at the lower end of reservoir 410. As a result, a flow of heat exchange fluid in reservoir may be from the upper end toward the lower end, resulting in countercurrent heat exchange with the beverage flowing through chiller coil 430.
In some embodiments, chiller 400 may include an agitator 490 configured to circulate liquid heat exchange fluid in reservoir 410, as best shown in
In some embodiments, agitator 490 may include an impeller 492 having one or more blades 494. Impeller 492 may be arranged to extend from upper end 401 toward lower end 403 of chiller 400. In some embodiments, impeller 492 may extend the full height of the reservoir 410. In some embodiments, blades 494 may be arranged at an angle A relative to a central axis X. The angle A determines the flow of heat exchange fluid within reservoir and the torque of the motor. In some embodiments, the angle A is about 15 to about 45 degrees, about 17 to about 35 degrees, or about 20 to about 30 degrees with respect to central axis X to maximize the flow of heat exchange fluid within the reservoir 410.
Agitator 490 may include a motor 496 configured to cause rotation of impeller 492. In operation of chiller 400, motor 496 may be submerged in liquid heat exchange fluid in reservoir 410. In some embodiments, agitator 490 may include a motor arranged exterior to reservoir 410 with an impeller 492 arranged within reservoir 410, such that motor 496 is not submerged in heat exchange fluid. Motor 496 may be a direct current (DC) motor. In some embodiments, motor 496 may be configured to rotate impeller 492 at a rate of 8,000 rpm or more, 9,000 rpm or more, or 10,000 rpm or more, and the rate of rotation of impeller 492 may be in the range of 9,000 to 12,000 rpm. Increasing the rotation rate allows the heat exchange fluid to reach a uniform temperature in a shorter period of time, on the order of a few seconds to facilitate heat transfer. Lower rotation rates may require a longer time to achieve uniform temperature of the heat exchange fluid, which may slow or delay heat transfer.
In some embodiments, operation of a chiller as described herein may be controlled based on one or more temperature sensors. Chiller may include a control unit that controls operation of chiller, and that controls operation of cooling system, agitator and other components, based on input from the temperature sensors. Operation of a cooling system and an agitator of a chiller based on readings from temperature sensors is described in U.S. application Ser. No. 16/875,975 (U.S. Publication No. 2020/0361758 A1), incorporated herein by reference in its entirety.
In some embodiments, temperature sensor 404 may include a thermistor, such as a negative temperature type thermistor (NTC). In some embodiments, a first temperature sensor (or sensors) 404A may be used to control operation of a compressor of a cooling system, and a second temperature sensor (or sensors) 404B may be used to control operation of agitator 490, as shown in
In some embodiments, a first temperature sensor 404A is used to control the thickness of the bank of frozen heat exchange fluid. The bank may continue to grow outward from evaporator and toward chiller coil. The cooling system is operated in order to prevent the bank of frozen heat exchange fluid from growing too close to chiller coil. When first temperature sensor 404A detects a temperature in a predetermined range of temperatures indicating the growth of the frozen bank of heat exchange fluid to a certain thickness, compressor may be deactivated to prevent further growth of frozen bank of heat exchange fluid. As discussed, if frozen bank continues to grow, frozen bank of heat exchange fluid may approach chiller coil resulting in freezing of the beverage within the chiller coil. First temperature sensor 404A may be placed a predetermined distance from evaporator coil 460 and when bank approaches temperature sensor, temperature sensor 404A may detect the low temperature and cause cooling system to deactivate and stop circulating coolant. The temperature sensor 404A may be arranged so that its outer facing surface that faces evaporator coil 460 is at the desired wall thickness for the bank. When bank contacts temperature sensor 404A, temperature sensor 404A may detect a temperature of 0° C. or below and may communicate with a control unit that deactivates cooling system 800.
In some embodiments, cooling system operates within a predetermined temperature band having an upper threshold temperature TUT and a lower threshold temperature TLT, as shown for example in
In some embodiments, chiller 400 may further include a second temperature sensor 404B configured to detect a temperature of beverage within chiller coil. Second temperature sensor may be arranged immediately adjacent exterior surface of chiller coil or may be in contact with exterior surface of chiller coil. Second temperature sensor 404B may detect a temperature of chiller coil and thus may be used to calculate a temperature of beverage within chiller coil 430. In embodiments having more than one chiller coil, second temperature sensor may be arranged adjacent the outermost chiller coil (the chiller coil positioned closest to the evaporator coil). However, in some embodiments, a sensor may be arranged within chiller coil 430 and in contact with beverage to determine a temperature of beverage. For example, sensor may include a fiber optic temperature sensor or a temperature probe that directly determines the temperature of the beverage at a specific location in chiller coil 430.
An agitator of chiller, such as agitator 490, may be configured to operate within a predetermined temperature band including an upper temperature threshold and a lower temperature threshold. Upon installation of chiller, chiller is filled with heat exchange fluid at ambient temperature. As evaporator coil 460 cools heat exchange fluid in reservoir 410 and bank of frozen heat exchange fluid begins to form around evaporator coil 460, agitator 490 is inactive. It is undesirable to activate agitator 490 as cooling system is operating and the temperature of the heat exchange fluid is decreasing from ambient temperature, as operation of the agitator 490 to circulate heat exchange fluid may disrupt or slow formation of frozen bank of heat exchange fluid around evaporator coil 460. However, as the temperature detected by second temperature sensor 404B falls below the upper threshold temperature, and the bank of frozen heat exchange fluid is formed, operating agitator 490 helps to circulate liquid heat exchange fluid to facilitate transfer of heat from chiller coil 430 to the bank in order to rapidly cool the beverage flowing through chiller coil 430. As the temperature detected by second temperature sensor 404B continues to decrease (i.e., as temperature of chiller coil 430 decreases), agitator 490 may be deactivated when second temperature sensor 404B detects a temperature at or below a lower threshold temperature. As temperature detected by second temperature sensor 404B reaches the lower threshold temperature, which may be in a range of about 0° C. to about 2° C., agitator 490 is deactivated (i.e., turned-off) to prevent unnecessary depletion of the bank of frozen heat exchange fluid. Further, reducing temperature below the lower threshold temperature may be inefficient and impractical and thus agitator 490 may be deactivated to conserve energy and eliminate heat transfer from agitator to heat exchange fluid. As temperature increases from lower threshold temperature within the predetermined temperature band, agitator 490 remains inactive until the upper threshold temperature is reached (e.g., about 1° C. to about 5° C.), at which point agitator 490 may again activate.
In some embodiments, agitator 490 may further begin operating based on detection of a presence of a user. In such embodiments, chiller 400 (or a beverage dispenser including chiller) may include a proximity sensor 498 configured to detect presence of a user or an object within a predetermined distance of chiller or beverage dispenser (see, e.g.,
When proximity sensor 498 detects a user or object within the predetermined distance, indicating the presence of a user, agitator 490 of chiller 400 may activate for a first predetermined time. The first predetermined time may be in a range of 5 seconds to 60 seconds, 10 seconds to 40 seconds, or 20 seconds to 30 seconds. In this way, chiller 400 may begin to circulate heat exchange fluid within reservoir 410 in preparation for a user to dispense a beverage from chiller. Temperature sensors 404B may have a delay or latency in detecting temperature of chiller coil 430, and activation of chiller 400 based on the user's proximity helps to ensure agitator is activate when chiller 400 is in use to facilitate heat transfer. In the event the user does not dispense a beverage, the agitator 490 simply deactivates after the first predetermined time.
In some embodiments, if the user uses the chiller 400 to dispense a beverage, the agitator 490 may activate for a second predetermined time, such as about 30 seconds to about 150 seconds, about 50 seconds to about 130 seconds, or about 70 seconds to about 110 seconds. Once predetermined second time is complete, agitator 490 operates based on temperature sensor 404B as discussed above. Chiller 400 may activate agitator 490 for the second predetermined time anytime chiller is used to dispense a beverage. While the operating logic is discussed with respect to agitator 490, it is understood that the same operating logic may be applied with other types of agitators.
In some embodiments, a chiller as described herein may include a heat exchange fluid that is an ionic liquid. While it is desirable to have a bank of frozen heat exchange fluid that is as large as possible to promote heat transfer, the size of the bank of frozen heat exchange fluid may be limited by the dimensions of the reservoir and by the other components within the reservoir. As discussed, the bank of frozen heat exchange fluid may cause freezing of the beverage within the chiller coil if the bank is too close to the chiller coil.
Ionic liquids may be useful as heat exchange fluids in a chiller as ionic liquids may have a freezing point that is higher than that of water. As a result, the ionic liquid in the reservoir may freeze into a solid phase without freezing the beverage flowing through the chiller coil. As a result, substantially all of the heat exchange fluid in the reservoir may freeze and may be in a solid phase. The entire volume of reservoir may become a bank of frozen heat exchange fluid and the heat can be extracted during the change of phase of the bank at a constant temperature. As will be appreciated by one of ordinary skill in the art, conductive heat transfer may proceed much more efficiently in the solid phase rather than convective heat transfer through the liquid heat exchange fluid. Further, as the freezing point of the ionic liquid is higher than water, the bank may form more rapidly relative to water as the heat exchange fluid.
In some embodiments, ionic liquids may have a freezing point between about 0.01° C. and about 5° C. at atmospheric pressure so that the freezing point is above the freezing point of water to prevent freezing of the beverage within the chiller coil. The ionic liquid for use as a heat exchange fluid may have a high latent heat of fusion, and in some embodiments may have a latent heat of fusion in a range of 50 kJ/kg to 400 kJ/kg, 150 kJ/kg to 350 kJ/kg, or 200 kJ/kg to 300 kJ/kg. Further, the ionic liquid for use as a heat exchange fluid may have a low vapor tension, may be inert (non-flammable and not corrosive), may be recyclable or reusable, and may exhibit consistent physical and chemical properties over an extended period of time (such as one or more years) so that the performance of the heat exchange fluid does not degrade over time. In some embodiments, ionic liquids suitable for use as a heat exchange fluid for a chiller as described herein may be selected from 1-butyl-3-methylimidazolium ionic liquid, such as BMIM-NTF2 or BMIM-PF6, imidazolium based ionic liquids, pyridinium based ionic liquids, and morpholine based ionic liquids, and salts and combinations thereof.
In some embodiments, chiller 500 includes a reservoir 510 containing a heat exchange fluid that is an ionic liquid 730, as shown in
Reservoir 510 of chiller 500 may be sealed such that ionic liquid 730 is enclosed within reservoir 510 and is inaccessible to the end user. Thus, chiller 500 may be assembled, filled with ionic liquid 730, and sealed. This may help to prevent ionic liquid 730 from escaping during storage or transportation of chiller 500.
Evaporator coil 560 of chiller 500 may include projections 570 as described herein, for example, with respect to projections 170, 470. Projections 570 may help the ionic liquid to freeze into a solid phase more rapidly than in embodiments with no projections 570.
Further, chiller 500 does not include an agitator for circulating heat exchange fluid. As the ionic liquid 730 may be in a solid phase during operation of chiller 500, an agitator is not required to circulate a liquid phase heat exchange fluid to promote heat convection in the liquid phase so that ionic liquid changes phases as fast as possible. As a result, the construction of chiller 500 is simplified by elimination of the agitator (e.g., agitator 490) as well as a second temperature sensor (e.g., 404B). Further, as an agitator occupies space within reservoir, elimination of the agitator allows for a greater quantity of heat exchange fluid to be included in reservoir relative to embodiments of chiller having an agitator.
Additionally, the operating logic of chiller 500 is simplified when an ionic liquid is used as the heat exchange fluid. Chiller 500 does not require temperature sensors to monitor the growth of a bank of frozen heat exchange fluid as substantially all ionic liquid freezes into solid phase while the beverage continues to flow within the chiller coil(s) 530, 540 without risk of freezing. The mixture of ionic liquids as heat exchange fluid may be carefully selected so that its latent heat of melting in the entire volume of chiller 500 is greater that the latent heat of the ice bank, such as bank 720. Further, a temperature sensor (e.g., temperature sensor 404B) is not required to control operation of an agitator, as no agitator is present in chiller 500.
In some embodiments, a beverage dispenser 600 may include a chiller 100, 200, 300, 400, 500 as described herein. Beverage dispenser 600, as shown in
Housing 610 of beverage dispenser 600 may define a beverage container receiving area 615. Beverage dispenser 600 may include a nozzle 620 arranged on housing 610 at beverage container receiving area 615 for dispensing a beverage, such as a base liquid or a base liquid and a flavoring mixed together. Nozzle 620 may be arranged at an upper end 614 of housing 610 in beverage container receiving area 615. A container 880, such as a cup or bottle, may be placed in beverage container receiving area 615 to be filled with a beverage via nozzle 620. Container 880 may be placed on a lower end 612 of housing 610 in beverage container receiving area 615, which may include a drip tray 619 for collecting excess liquid from dispenser 105.
Housing 610 of beverage dispenser 600 may further include a user interface 640 for receiving a user input, as shown in
Beverage dispenser 600 may include a control unit 650 for controlling operation of beverage dispenser 600. Control unit 650 may be in communication with user interface 640, such that a user input received by user interface 640 is communicated to control unit 650, and control unit 650 may cause a beverage to be dispensed based on the user input, such as by actuating one or more pump and valves 660 for driving and controlling a flow of a base liquid and/or flavoring. In some embodiments, control unit 650 may further be in communication with cooling system 800 for circulating coolant. Control unit 650 may also be in communication with the chiller for implementing the operating logic for the chiller, such as by receiving input from temperature sensors and activating or deactivating the cooling system and agitator based on the input from the temperature sensors, as discussed herein.
In some embodiments, beverage dispenser 600 may include additional treatment units for treating the base liquid, such as a carbonator 670, an alkaline cartridge, a water filter, or a mixer for combining the base liquid with a flavoring. The treatment units may be arranged upstream or downstream of chiller 100. In some embodiments, a water filter may filter water prior to water being chilled by chiller 100. In some embodiments, carbonator 670 may arranged downstream of chiller such that water is chilled prior to being carbonated. In some embodiments, carbonator 670 may be located within chiller 100. In some embodiments, the chilled and carbonated water may then be mixed with flavorings to form a flavored beverage or carbonated soft drink in the dispensing nozzle or prior to reaching the dispensing nozzle. However, in some embodiments, water may be mixed with flavorings and then cooled by chiller 100 and subsequently carbonated.
If programmable logic is used, such logic may execute on a commercially available processing platform or a special purpose device. One of ordinary skill in the art may appreciate that embodiments of the disclosed subject matter can be practiced with various computer system configurations, including multi-core multiprocessor systems, minicomputers, and mainframe computers, computer linked or clustered with distributed functions, as well as pervasive or miniature computers that may be embedded into virtually any device.
For instance, at least one processor device and a memory may be used to implement the above described embodiments. A processor device may be a single processor, a plurality of processors, or combinations thereof. Processor devices may have one or more processor “cores.”
Various embodiments may be implemented in terms of this example computer system 900. After reading this description, it will become apparent to a person skilled in the relevant art how to implement one or more of the invention(s) using other computer systems and/or computer architectures. Although operations may be described as a sequential process, some of the operations may in fact be performed in parallel, concurrently, and/or in a distributed environment, and with program code stored locally or remotely for access by single or multi-processor machines. In addition, in some embodiments the order of operations may be rearranged without departing from the spirit of the disclosed subject matter.
Processor device 904 may be a special purpose or a general purpose processor device.
As will be appreciated by persons skilled in the relevant art, processor device 904 may also be a single processor in a multi-core/multiprocessor system, such system operating alone, or in a cluster of computing devices operating in a cluster or server farm. Processor device 904 is connected to a communication infrastructure 906, for example, a bus, message queue, network, or multi-core message-passing scheme.
Computer system 900 also includes a main memory 908, for example, random access memory (RAM), and may also include a secondary memory 910. Secondary memory 910 may include, for example, a hard disk drive 912, or removable storage drive 914. Removable storage drive 914 may include a floppy disk drive, a magnetic tape drive, an optical disk drive, a flash memory, or the like. The removable storage drive 914 reads from and/or writes to a removable storage unit 918 in a well-known manner. Removable storage unit 918 may include a floppy disk, magnetic tape, optical disk, a universal serial bus (USB) drive, etc. which is read by and written to by removable storage drive 914. As will be appreciated by persons skilled in the relevant art, removable storage unit 918 includes a computer usable storage medium having stored therein computer software and/or data.
Computer system 900 (optionally) includes a display interface 902 (which can include input and output devices such as keyboards, mice, etc.) that forwards graphics, text, and other data from communication infrastructure 906 (or from a frame buffer not shown) for display on display 940.
In alternative implementations, secondary memory 910 may include other similar means for allowing computer programs or other instructions to be loaded into computer system 900. Such means may include, for example, a removable storage unit 922 and an interface 920. Examples of such means may include a program cartridge and cartridge interface (such as that found in video game devices), a removable memory chip (such as an EPROM, or PROM) and associated socket, and other removable storage units 922 and interfaces 920 which allow software and data to be transferred from the removable storage unit 922 to computer system 900.
Computer system 900 may also include a communication interface 924. Communication interface 924 allows software and data to be transferred between computer system 900 and external devices. Communication interface 924 may include a modem, a network interface (such as an Ethernet card), a communication port, a PCMCIA slot and card, or the like. Software and data transferred via communication interface 924 may be in the form of signals, which may be electronic, electromagnetic, optical, or other signals capable of being received by communication interface 924. These signals may be provided to communication interface 924 via a communication path 926. Communication path 926 carries signals and may be implemented using wire or cable, fiber optics, a phone line, a cellular phone link, an RF link or other communication channels.
In this document, the terms “computer program medium” and “computer usable medium” are used to generally refer to media such as removable storage unit 918, removable storage unit 922, and a hard disk installed in hard disk drive 912. Computer program medium and computer usable medium may also refer to memories, such as main memory 908 and secondary memory 910, which may be memory semiconductors (e.g. DRAMs, etc.).
Computer programs (also called computer control logic) are stored in main memory 908 and/or secondary memory 910. Computer programs may also be received via communication interface 924. Such computer programs, when executed, enable computer system 900 to implement the embodiments as discussed herein. In particular, the computer programs, when executed, enable processor device 904 to implement the processes of the embodiments discussed here. Accordingly, such computer programs represent controllers of the computer system 900. Where the embodiments are implemented using software, the software may be stored in a computer program product and loaded into computer system 900 using removable storage drive 914, interface 920, and hard disk drive 912, or communication interface 924.
Embodiments of the invention(s) also may be directed to computer program products comprising software stored on any computer useable medium. Such software, when executed in one or more data processing device, causes a data processing device(s) to operate as described herein. Embodiments of the invention(s) may employ any computer useable or readable medium. Examples of computer useable mediums include, but are not limited to, primary storage devices (e.g., any type of random access memory), secondary storage devices (e.g., hard drives, floppy disks, CD ROMS, ZIP disks, tapes, magnetic storage devices, and optical storage devices, MEMS, nanotechnological storage device, etc.).
It is to be appreciated that the Detailed Description section, and not the Summary and Abstract sections, is intended to be used to interpret the claims. The Summary and Abstract sections may set forth one or more but not all exemplary embodiments of the present invention(s) as contemplated by the inventors, and thus, are not intended to limit the present invention(s) and the appended claims in any way.
The present invention has been described above with the aid of functional building blocks illustrating the implementation of specified functions and relationships thereof. The boundaries of these functional building blocks have been arbitrarily defined herein for the convenience of the description. Alternate boundaries can be defined so long as the specified functions and relationships thereof are appropriately performed.
The foregoing description of the specific embodiments will so fully reveal the general nature of the invention(s) that others can, by applying knowledge within the skill of the art, readily modify and/or adapt for various applications such specific embodiments, without undue experimentation, and without departing from the general concept of the present invention(s). Therefore, such adaptations and modifications are intended to be within the meaning and range of equivalents of the disclosed embodiments, based on the teaching and guidance presented herein. It is to be understood that the phraseology or terminology herein is for the purpose of description and not of limitation, such that the terminology or phraseology of the present specification is to be interpreted by the skilled artisan in light of the teachings and guidance herein.
The breadth and scope of the present invention(s) should not be limited by any of the above-described exemplary embodiments, but should be defined only in accordance with the following claims and their equivalents.
| Number | Date | Country | |
|---|---|---|---|
| 63035136 | Jun 2020 | US |
