Chiller for cooling beverages

Abstract

To provide a chiller having a small form factor and capable of rapidly cooling a beverage in several seconds and continuously distributing the cooled beverage.SOLUTION: Chiller 400 for cooling a beverage includes a reservoir 410 configured to hold a heat exchange fluid and an evaporator coil 460 disposed within reservoir 410. Evaporator coil 460 includes a plurality of windings 462 configured to circulate a refrigerant and projections extending from an outer surface of one or more of the plurality of windings 462. The chiller 400 further includes chiller coils 430 disposed within the reservoir 410, and the beverage is configured to flow through the chiller coils 430. As the refrigerant is circulated through the plurality of windings 462 of evaporator coil 460, a bank of frozen heat exchange fluid forms on windings 462 and on the protrusions.SELECTED DRAWING: Figure 15

Description

[Technical Field]

[0001] The embodiments described herein generally relate to a chiller for cooling beverages having a compact size. Specifically, the 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, the evaporator coil including protrusions for facilitating heat transfer from the chiller coil to the evaporator coil. [Background technology]

[0002] Chillers are used to cool and dispense beverages. Some chillers operate by chilling a quantity of beverage in a reservoir before dispensing the beverage. When a consumer desires a beverage, a portion of the pre-chilled beverage is simply dispensed from the reservoir.

[0003] Chillers that require a reservoir to store pre-chilled beverages have several drawbacks. The reservoir takes up substantial space and increases the size of the chiller, which may be undesirable when providing a chiller for a home or office setting. Furthermore, cooling the quantity of beverage in the reservoir may take an extended period of time. Once the stored quantity of pre-chilled beverage is dispensed, the consumer must wait a period of time until a new batch of beverage is cooled.

[0004] Therefore, there is a need in the art for a chiller that has a small form factor, can rapidly chill beverages in seconds, and can continuously dispense chilled beverages. Summary of the Invention

[0005] Some embodiments described herein relate to a chiller for cooling a beverage, the chiller including a reservoir configured to hold a heat exchange fluid and an evaporator coil disposed within the reservoir. The evaporator coil of the chiller includes a plurality of windings configured to circulate a refrigerant and protrusions extending from an outer surface of one or more of the plurality of windings. The chiller further includes a chiller coil disposed within the reservoir, the beverage configured to flow through the chiller coil, and when the refrigerant is circulated through the plurality of windings of the evaporator coil, a bank of frozen heat exchange fluid is formed on the plurality of windings and on the protrusions.

[0006] In any of the various embodiments described herein, the protrusions may include one or more fins.

[0007] In any of the various embodiments described herein, the protrusions may include one or more rods.

[0008] In any of the various embodiments described herein, the protrusions may include a lattice structure.

[0009] In any of the various embodiments described herein, the evaporator coil may be formed from a first material, the protrusions may be formed from a second material, and the first material may be the same as the second material.

[0010] In any of the various embodiments described herein, the evaporator coil may define a central volume, and the chiller coil may be disposed within the central volume of the evaporator coil.

[0011] In any of the various embodiments described herein, the chiller may further include a second chiller coil disposed within the reservoir, the beverage being configured to flow through the second chiller coil. In some embodiments, the chiller may further include a splitter configured to split the flow of the beverage between the first chiller coil and the second chiller coil, the splitter dividing the flow of the beverage such that a larger portion of the beverage flows through the first chiller coil than through the second chiller coil.

[0012] In any of the various embodiments described herein, the wall thickness of the chiller coil can range from about 0.2 mm to about 1.0 mm.

[0013] In any of the various embodiments described herein, the chiller reservoir can have a total volume of about 3L to about 10L.

[0014] In any of the various embodiments described herein, the chiller further includes an agitator disposed within the reservoir, 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 coil, the agitator chiller configured to operate when the temperature of the chiller coil as detected by the temperature sensor is within a predetermined temperature range.

[0015] Some embodiments described herein relate to a beverage dispenser including a user interface configured to receive a beverage selection and a chiller configured to chill the beverage. The chiller of the beverage dispenser includes a reservoir configured to store a heat exchange fluid and an evaporator coil disposed within the reservoir and configured to circulate a coolant, the evaporator coil including a plurality of windings and protrusions extending from an outer surface of one or more of the plurality of windings of the evaporator coil. The beverage dispenser chiller further includes a chiller coil disposed within the reservoir, the beverage flowing through the chiller coil such that the beverage is cooled as the beverage flows through the chiller coil, and a bank of frozen heat exchange fluid is formed on the evaporator coil and on the protrusions as the coolant is circulated through the evaporator coil. The beverage dispenser further includes a dispensing nozzle in communication with the chiller coil for dispensing the beverage.

[0016] In any of the various embodiments described herein, the beverage dispenser may further include a refrigeration system configured to circulate a coolant, and the refrigeration system may include an evaporator coil.

[0017] In any of the various embodiments described herein, the beverage dispenser may further include a carbonator configured to carbonate the beverage, the carbonator in communication with the chiller coil.

[0018] Some embodiments described herein relate to a chiller for cooling a beverage, the chiller including a reservoir and a heat exchange fluid stored in the reservoir, the heat exchange fluid being an ionic liquid having a freezing point of about 0° C. The chiller further includes an evaporator coil disposed within the reservoir, the evaporator coil including a plurality of windings configured to circulate a refrigerant and protrusions extending from an outer surface of one or more of the plurality of windings. The chiller further includes a chiller coil disposed within the reservoir, the beverage flowing through the chiller coil, and at least a portion of the heat exchange fluid freezing to a solid phase as the refrigerant is circulated through the windings of the evaporator coil.

[0019] In any of the various embodiments described herein, the heat exchange fluid can have a freezing point of about 0.01°C to about 5°C.

[0020] In any of the various embodiments described herein, the ionic liquid may be selected from the group consisting of 1-butyl-3-methylimidazolium-based ionic liquids, imidazolium-based ionic liquids, pyridinium-based ionic liquids, and morpholine-based ionic liquids.

[0021] In any of the various embodiments described herein, the ionic liquid can have a latent heat of fusion in the range of about 200 kJ / kg to about 300 kJ / kg.

[0022] In any of the various embodiments described herein having an ionic liquid, when the refrigerant is circulated through the windings of the evaporator coil, all of the heat exchange fluid may freeze to a solid phase. [Brief explanation of the drawings]

[0023] The accompanying drawings, which are incorporated in and form a part of this specification, illustrate the present disclosure and, together with the description, serve to further explain the principles of the present disclosure and to enable those skilled in the art to make and use the present disclosure. [Figure 1] 1 illustrates a perspective view of a chiller according to one embodiment with the top end of the chiller reservoir removed. [Figure 2] 1 illustrates a schematic diagram of components of a chiller and cooling system according to one embodiment. [Figure 3] 1 shows a schematic cross-sectional view of a chiller according to one embodiment. [Figure 4] A top-down view of the chiller according to Figure 3 is shown. [Figure 5] 1 illustrates a cross-sectional view of an evaporator coil for a chiller including protrusions according to one embodiment. [Figure 6] 1 illustrates a top-down view of an evaporator coil for a chiller including protrusions according to one embodiment. [Figure 7]1 illustrates a cross-sectional view of an evaporator coil for a chiller including protrusions according to one embodiment. [Figure 8] 1 illustrates a top-down view of an evaporator coil for a chiller including protrusions according to one embodiment. [Figure 9] 1 shows a close-up view of protrusions of a reticulated evaporator coil according to one embodiment. [Figure 10] FIG. 1 illustrates a perspective view of a chiller coil having protrusions, according to one embodiment. [Figure 11] 1 shows a schematic cross-sectional view of a chiller according to one embodiment. [Figure 12] 12 shows a perspective view of an evaporator coil having reticulated projections according to one embodiment for use with the chiller of FIG. 11. [Figure 13] FIG. 1 illustrates a top-down view of a chiller with an agitator pump and swirl tube according to one embodiment. [Figure 14] 14 shows a cross-sectional view of the chiller of FIG. 13 taken along line 14-14 of FIG. 13. [Figure 15] 1 illustrates a cross-sectional view of a chiller according to one embodiment. [Figure 16] 15 shows a top-down view of the chiller. [Figure 17] 16 shows a perspective view of the evaporator coil of the chiller of FIG. 15. [Figure 18] 18 shows a side view of the lattice structure of FIG. 17. [Figure 19] 1 illustrates a top-down view of an evaporator coil having a lattice structure, according to one embodiment. [Figure 20] 19 shows a side cross-sectional view of an evaporator coil having a lattice structure according to FIG. [Figure 21] 16 shows a perspective view of the chiller coil of the chiller of FIG. 15. [Figure 22] FIG. 1 illustrates a cross-sectional view of a chiller coil according to one embodiment. [Figure 23] 1 shows a plot of the temperature of the heat exchange fluid in the chiller over time. [Figure 24] 1 illustrates a cross-sectional view of a chiller including an ionic liquid heat exchange fluid, according to one embodiment. [Figure 25] 1 illustrates a diagram of a beverage dispenser including a chiller according to one embodiment. [Figure 26] 1 shows a schematic diagram of components of a beverage dispenser according to one embodiment. [Figure 27] 1 shows a schematic block diagram of an exemplary computer system in which embodiments may be implemented. DETAILED DESCRIPTION OF THE INVENTION

[0024] Reference will now be made in detail to representative embodiments, as illustrated in the accompanying drawings. It should be understood that the following description is not intended to limit the embodiments to a single preferred embodiment. On the contrary, the invention is intended to cover alternatives, modifications, and equivalents, which may be included within the spirit and scope of the embodiments as defined by the appended claims.

[0025] There is an increasing demand for beverage chillers in homes or offices. To provide a chiller for home or office use, the chiller needs to have a small form factor so that the chiller can be installed on a countertop, such as a kitchen counter. Chillers that have a reservoir of pre-chilled beverage, such as carbonated or non-carbonated water, are typically large and impractical for use in a home or office setting.

[0026] If the pre-chilled beverage reservoir were eliminated and beverages were instead chilled on demand, i.e., as they are dispensed, the chiller's footprint could be significantly reduced. Beverages can be cooled very rapidly and on demand by passing them through a coil placed in a reservoir containing a heat exchange fluid, such as water, to remove heat from the beverage as it passes through the coil. Some chillers may use a heat exchange fluid to chill beverages, but may rely on large reservoirs of heat exchange fluid, such as 20 liters or more. As a result, beverage dispensers using such chillers are impractical for home or office settings and are instead used in commercial kitchens, such as restaurants or bars. Therefore, to maintain a small footprint, beverage dispenser chillers must use a small chiller reservoir to store the heat exchange fluid.

[0027] However, cooling a volume of liquid to a desired temperature, such as 5°C or below, on demand and with a relatively small amount of heat exchange fluid presents many design and engineering challenges, especially as it becomes desirable to dispense larger volumes or higher flow rates of beverages. Furthermore, because carbon dioxide solubilization decreases significantly with increasing temperature, carbonated beverages must be chilled to 5°C or below to maintain sufficient carbonation in the beverage and avoid excessive effervescence.

[0028] The heat exchange within the chiller must be sufficient to chill the beverage in the few seconds it flows through the chiller, and the chiller must be sufficient to chill a large volume of beverage. Chillers can be rated by their compaction ratio, which refers to the ratio of the maximum volume of chilled water that can be dispensed in one hour at 5°C or below to the volume of the chiller. Therefore, it is desirable to manufacture chillers with a high compaction ratio, indicating that the volume of liquid that can be dispensed in one hour at 5°C or below is large relative to the volume of the chiller.

[0029] The inventors of the present application have discovered that the compactness factor can be increased by maximizing heat exchange within the chiller. By increasing the heat exchange efficiency, the chiller can be designed with a smaller footprint while producing the same volume of chilled beverage, or the volume of chilled beverage that can be dispensed can be increased without increasing the size of the chiller.

[0030] Some embodiments described herein relate to chillers including an evaporator coil with protrusions that allow a bank of frozen heat exchange fluid to be formed on the evaporator coil and, additionally, on the protrusions. In this way, the surface area of ​​the bank of frozen heat exchange fluid can be increased compared 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 can increase heat transfer between the evaporator coil and the chiller coil, facilitating cooling of beverages within the chiller coil. Some embodiments described herein relate to chillers including an evaporator coil with protrusions that include a network structure that facilitates the formation of a frozen bank of heat exchange fluid on the protrusions. The network structure of the protrusions increases the thermal conductivity of the bank of frozen heat exchange fluid, allowing the bank of frozen heat exchange fluid to form more rapidly.

[0031] As used herein, the term "beverage" may refer to any of a variety of consumable liquids, including, but not limited to, carbonated water, non-carbonated water (e.g., still water), flavored or fortified water, juice, coffee- or tea-based beverages, sports drinks, energy drinks, soda, dairy or dairy-based beverages (e.g., milk).

[0032] As used herein, the term "refrigerant" may refer to any fluid configured to reduce the temperature of a heat exchange fluid, such as a refrigerant, particularly a refrigerant with a low global warming potential (GWP) and / or ozone depletion potential (ODP), including R600a, R134a, R290, R744, R32, and mixtures thereof, e.g., an R290 / R744 mixture, among others.

[0033] As used herein, the term "heat exchange fluid" may refer to a substance configured to drive heat exchange from a liquid in a chiller coil, such as a beverage. For example, the heat exchange fluid may include water, a water and alcohol mixture, or an ionic liquid, among others, whose total solids content and / or pH may be varied to affect melting conditions and ice structure.

[0034] In some embodiments, the chillers described herein can be configured to reduce the temperature of a beverage by 20°C or more. The chillers can be configured to reduce the temperature of a beverage to ambient temperature, e.g., about 25°C to 5°C, or below, in less than 10 seconds, less than 8 seconds, or less than 4 seconds. In some embodiments, when the chiller is initially started, a bank of frozen heat exchange fluid can form in the chiller's reservoir in 80 minutes or less, 60 minutes or less, or 40 minutes or less. In this manner, the chiller has a rapid start-up time and can begin cooling beverages immediately after start-up. Additionally, the chiller can quickly regenerate the bank of frozen heat exchange fluid when it becomes depleted.

[0035] Some embodiments herein are directed to a chiller 100 including a reservoir 110 configured to hold a heat exchange fluid, as shown in FIG. 1 . An evaporator coil 160 is disposed within the reservoir 110 and is part of a refrigeration system for circulating a coolant. A chiller coil 130, connected to a beverage source, is disposed within the reservoir 110 and within a central volume 164 of the evaporator coil 160. The chiller coil 130 is configured to chill the beverage and deliver the beverage to a dispenser 105. The dispenser 105 may be disposed on the reservoir 110 or may be separate from the reservoir 110 and connected thereto via a conduit. An agitator or pump 180 may be disposed within the reservoir 110 and configured to circulate the heat exchange fluid within the reservoir 110. During operation, a bank of frozen heat exchange fluid (e.g., an ice bank when the heat exchange fluid is water) forms around the evaporator coil 160 to absorb heat from the beverage in the chiller coil 130. To enhance heat exchange, the evaporator coil 160 may include one or more protrusions 170 that form banks around its periphery, as discussed in more detail herein.

[0036] The reservoir 110 is configured to hold a heat exchange fluid that facilitates heat transfer between the beverage flowing through the chiller coil 130 and the evaporator coil 160 of the chiller 100. In some embodiments, the heat exchange fluid may be water. Using water as the heat exchange fluid may facilitate maintenance of the chiller 100 because water is non-toxic and can be easily drained and replaced by the end user.

[0037] In some embodiments, the reservoir 110 of the chiller 100 can have a total internal volume of about 3 L to about 10 L. The reservoir 110 can 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. Because the overall size of the chiller 100 is largely dependent on the size of the reservoir 110, by using a small reservoir 110 and a small amount of heat exchange fluid, the chiller 100 can 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.

[0038] The reservoir 110 of the chiller 100 may have any of a variety of shapes, and may be shaped as a rectangular prism, a cube, or a cylinder, among others. The reservoir 110 may be insulated to inhibit or minimize the transfer of heat outside the chiller 100 into the chiller 100. The reservoir 110 may include a lid that provides access to the interior volume of the reservoir 110, such as for filling or replacing a heat exchange fluid or for performing maintenance or repair on components within the reservoir 110. However, in some embodiments, the reservoir 110 may be sealed such that the interior volume of the reservoir 110 is not accessible by an end user.

[0039] Components of a chiller 100 according to some embodiments are shown in FIG. 2. The chiller 100 may include a reservoir 110 in which a chiller coil 130 and an evaporator coil 160 are disposed. The chiller coil 130 and the evaporator coil 160 may be arranged in a nested configuration and may be at least partially immersed in a heat exchange fluid within the reservoir 110. A beverage source 700 remote from the chiller 100 may be connected to the chiller coil 130 by a conduit or the like to supply the beverage to the chiller coil 130. The beverage source 700 may be, for example, a municipal water supply, a well, or a beverage reservoir. The chiller 100 may include a dispenser 105, such as a dispensing nozzle, connected to the chiller coil 130 for dispensing the cooled beverage that has flowed through the chiller coil 130. When the dispenser 105 is activated, the beverage flows from the beverage source 700 through the chiller coil 130 and is chilled as it flows through the chiller coil 130, such that the beverage is cooled (e.g., below 5°C) when it is dispensed through the dispenser 105. Thus, the beverage is chilled in an on-demand manner, which may also be referred to as continuous chilling.

[0040] The evaporator coil 160 of the chiller 100 is configured to circulate refrigerant as part of a cooling system 800. The cooling system 800 may be a vapor compression cooling system and may include, in addition to the evaporator coil 160, a compressor 810, a condenser 820, and an expansion valve 830, as will be understood by those skilled in the art. As the refrigerant flows through the evaporator coil 160 and changes from a liquid to a vapor, the heat exchange fluid surrounding the evaporator coil 160 freezes, forming a bank of frozen heat exchange fluid (see, for example, FIG. 3 ). Heat from the beverage flowing through the chiller coil 130 is transferred and absorbed by the bank of frozen heat exchange fluid, resulting in cooling of the beverage. The bank of frozen heat exchange fluid has a high latent heat of fusion and is therefore capable of absorbing a significant amount of heat without a corresponding change in the temperature of the heat exchange fluid.

[0041] In some embodiments, the evaporator coil 160 may be a tube having multiple windings 162 arranged in a stacked configuration, as shown in FIG. 3 , for example. Each winding 162 may have a rectangular configuration when viewed from top to bottom (see, for example, FIG. 4 ). However, in some embodiments, each winding 162 may have a square, circular, or oval configuration when viewed from top to bottom. The windings 162 may extend around a central axis Z of the evaporator coil 160. The windings 162 may be in contact with each other or may be separated by spaces 168. The evaporator coil 160 may follow the inner periphery 112 of the reservoir 110. In some embodiments, the evaporator coil 160 may have a shape that corresponds to the shape of the reservoir 110. For example, if the reservoir 110 has a substantially rectangular configuration, the evaporator coil 160 may have a rectangular configuration to follow the shape of the periphery 112 of the reservoir 110. In another example, if the reservoir 110 has a substantially cylindrical shape (with a circular cross section), the evaporator coil 160 may have a circular shape as well. The evaporator coil 160 defines a central volume 164 outside the evaporator coil 160. The evaporator coil 160 may be formed from a material having a high thermal conductivity. In some embodiments, the evaporator coil 160 may be formed from a metal such as copper.

[0042] The chiller coil 130 may be disposed within the reservoir 110 of the chiller 100. The chiller coil 130 may be disposed in a nested configuration with the evaporator coil 160. As shown in FIGS. 3 and 4 , the chiller coil 130 may be disposed within a central volume 164 defined by the evaporator coil 160. Thus, the evaporator coil 160 may at least partially surround the chiller coil 130. The chiller coil 130 may be a tube having multiple windings 132 arranged in a stacked configuration. The windings 132 may be in contact with each other or may be separated by spaces 138. The windings 132 may have a shape that corresponds to the shape of the reservoir 110 or that corresponds to the shape of the evaporator coil 160. Thus, if the reservoir 110 has a rectangular configuration, each winding 132 may have a rectangular configuration when viewed from top to bottom (see, for example, FIG. 4 ). However, in some embodiments, the windings 132 may have a square, circular, or oval configuration, among others, when viewed from top to bottom. In some embodiments, the windings 132 may not all have the same shape. The windings 132 of the chiller coil 130 may extend around a central axis. In some embodiments, the central axis of the chiller coil 130 may be the same as the central axis (e.g., axis Z) of the evaporator coil 160 such that the evaporator coil 160 and the chiller coil 130 are concentrically arranged. The chiller coil 130 may be formed of a metal, such as stainless steel, to inhibit corrosion, reduce scale buildup, and prevent or minimize contamination of the beverage within the chiller coil 130.

[0043] In some embodiments, the evaporator coil 160 includes one or more protrusions 170 extending from the outer surface 161 of the evaporator coil 160. The protrusions 170 may extend in a direction from the evaporator coil 160 toward the chiller coil 130, as shown in FIG. 4 . In some embodiments, the protrusions 170 may extend inward into the central volume 164 of the evaporator coil 160. Refrigerant in the evaporator coil 160 does not flow into or through the protrusions 170. A bank of frozen heat exchange fluid 720, referred to herein simply as a “bank,” is formed on the windings 152 of the evaporator coil 160 and on the protrusions 170. Thus, the protrusions 170 serve to increase the total surface area of ​​the bank 720 to facilitate heat exchange with the chiller coil 130 (and the beverage flowing through the chiller coil 130).

[0044] In operation of the chiller 100, refrigerant flows through the evaporator coil 160 and evaporates, freezing the heat exchange fluid 710 surrounding the evaporator coil 160 and forming a bank 720 of frozen or solid phase heat exchange fluid (see, e.g., FIG. 3). The bank 720 extends about the evaporator coil 160 and the protrusions 170 to a thickness t b The evaporator coil 160 and the protrusion 170 are spaced a distance L from the chiller coil 130 so that the bank 720 does not reach the chiller coil 130. Therefore, L is equal to t b If the chiller coil 130 is too close to the evaporator coil 160, the beverage flowing through the chiller coil 130 may freeze, impeding the flow of the beverage through the chiller coil 130. Additionally, spaces are provided between adjacent protrusions 170 to maximize the interface between the heat exchange fluid in its solid and liquid states. The protrusions 170 may be spaced apart by a distance d, where the distance between the protrusions 170 is 2t b It may be larger.

[0045] In some embodiments, the protrusions may be formed as fins 172, as shown in FIGS. 5 and 6. The fins 172 may be substantially planar. The fins 172 may have a generally rectangular shape. The fins 172 may extend along at least a portion of the evaporator coil 160. As shown in FIG. 5, the fins 172 extend along a portion of one or more windings 162 of the evaporator coil 160. The fins 172 may follow the contours of the windings 162 to extend around corners or curved portions of the evaporator coil 160. The fins 172 may not be present on all windings 162 to allow space between the fins 172. The fins 172 are spaced apart so that the banks 720 do not completely fill the spaces between the fins 172. In some embodiments, the fins 172 may be disposed on alternating windings 162. For example, a first winding 162A of the evaporator coil 160 may have fins 172, while a second winding 162B adjacent to the first winding 162A may not have fins. In another example, every third winding may include a fin 172. In some embodiments, each fin 172 may have a thickness of about 1 mm to about 12 mm, or about 2 mm to about 8 mm, or about 3 mm to about 5 mm.

[0046] In some embodiments, the evaporator coil 160 may include protrusions 170 formed as rods 178, as shown in FIGS. 7 and 8, for example. The rods 178 may extend generally perpendicular to the direction of flow through the evaporator coil 160 and may extend generally perpendicular to the axis X of the evaporator coil 160, as best shown in FIG. 8. A first end 177 of the rod 178 may be connected to the outer surface 161 of the evaporator coil 160, and the rod 178 may terminate at a second end 179 opposite the first end 177. The rod 178 may have a length r measured from the first end 177 to the second end 179. The rod 178 has a thickness t measured as the widest dimension of the rod 178 transverse to the length. The rods 178 may be spaced apart from one another by a spacing a. The rods 178 are spaced apart so that when the bank of frozen heat exchange fluid is formed on the evaporator coil 160 and the rods 178, the spaces between the rods 178 are not completely filled by the bank of frozen heat exchange fluid. The rods 178 may each be the same size and dimensions. In some embodiments, the rods 178 may be generally linear along their lengths. In some embodiments, the rods 178 may be generally parallel to one another. In some embodiments, the rods 178 may have a cylindrical, conical, or rectangular prism shape, among others. As will be appreciated by those skilled in the art, the number and spacing of the rods 178 will depend in part on the dimensions (e.g., length and diameter) of the rods. The protrusions 170, whether formed as fins 172, rods 178, etc., may be secured to the outer surface 161 of the evaporator coil 160 via a variety of fastening methods. In some embodiments, the protrusions 170 may be permanently fixed to the evaporator coil 160, and the protrusions 170 may be welded or bonded to the evaporator coil 160, or may be secured by brazing. However, the protrusions 170 may also be secured to the evaporator coil 160 via brackets, mechanical fasteners, or adhesives, among other fastening methods.

[0047] The protrusions 170 may be formed from a material having a high thermal conductivity. The protrusions 170 may be formed from the same material as the evaporator coil 160. For example, in embodiments in which the evaporator coil 160 is formed from copper, the protrusions 170 may also be formed from copper. When the heat exchange fluid freezes around the windings 162 of the evaporator coil 160, the heat exchange fluid may also freeze around the protrusions 170. As a result, the freezing of the heat exchange fluid around the protrusions 170 increases the surface area of ​​the bank of frozen heat exchange fluid.

[0048] In some embodiments, the protrusions 170 may be formed from heat pipes. The heat pipes may help promote the rapid formation of frozen heat exchange fluid on the protrusions 170 and rapid heat transfer adjacent to the chiller coil. The heat pipes may include hollow tubes defining an enclosed interior volume and a working fluid disposed within the interior volume configured to be a vapor and a liquid within the operating temperature range. The working fluid within the heat pipe may be selected based on the operating temperature range and may be, for example, ammonia, alcohol, or water, among other suitable fluids. The heat pipes may be arranged in the same manner as the rods 178 and thus may extend radially from the outer surface of the evaporator coil 160 into the central volume 164 and toward the chiller coil.

[0049] In some embodiments, the protrusions 170 can be solid, such that they have no openings that would allow heat exchange fluid to flow into or through the protrusions 170. In some embodiments, the protrusions 170 can have a network structure, such that the body 171 of the protrusions 170 has a plurality of openings or pores 173, as shown, for example, in FIG. 9 . In this manner, the heat exchange fluid 710 can flow into the body 171 of the protrusions 170 through the pores 173. The pores 173 can be large enough so that the bank of frozen heat exchange fluid does not completely fill the pores 173. The network structure can facilitate freezing of the heat exchange fluid 710 to promote the extension of the bank 720 on and around the protrusions 170. The network structure can also delay the melting of the bank 720. The network structure can increase the thermal conductivity of the bank 720, causing it to form more rapidly. Body 171 has a high thermal conductivity and drives heat exchange within bank 720. As discussed, protrusions 170 may be formed of a metal with a high thermal conductivity, such as copper. In some embodiments, protrusions 170 may be formed from a metal foam, such as copper foam, among other materials, to provide protrusions 170 with a reticulated structure. The reticulated structure may have internal cells or pores, and the cells or pores may have various sizes.

[0050] In some embodiments, the chiller coil 130', rather than the evaporator coil, may include protrusions 170', as shown in FIG. 10 , for example. In such embodiments, the chiller coil 130' may include one or more protrusions having the same structure and characteristics as described with respect to the protrusions 170 of the evaporator coil 160. In such embodiments, the evaporator coil 160 may not have the protrusions 170 to avoid the growth of banks of frozen heat exchange fluid on the protrusions of the chiller coil 130' from growing on the protrusions of the chiller coil 130'. The protrusions 170' of the chiller coil 130' may extend outward from the outer surface of one or more windings 132' of the chiller coil 130' and may extend in a direction toward the evaporator coil. The protrusions 170' on the chiller coil 130' help promote conductive heat transfer. Heat exchange fluid may circulate to transfer heat from the chiller coil 130' to the bank of heat exchange fluid, and conductive heat transfer through the protrusions 170' may transfer heat more rapidly than convective heat transfer through the heat exchange fluid. Additionally, the protrusions 170' may also increase the surface area available for heat transfer.

[0051] In some embodiments, as shown in FIG. 10 , the protrusions 170′ on the chiller coil 130′ may include fins 172′. The fins 172′ may have the same structure and characteristics as described with respect to the fins 172. Thus, the fins 172′ may extend from one or more windings 132′ of the chiller coil 130′. The fins 172′ may be spaced apart from one another, and a fin 172′ may not be present in each winding 132′. The fins 172′ may extend in the plane of the windings 132′ of the chiller coil 130′. In some embodiments, the protrusions 170′ may include alternating rods, such as those described with respect to the rods 178 of the evaporator coil 160, and may have a mesh structure or foam. Additionally, the protrusions 170′ of the chiller coil 130′ may form a lattice structure, as described in further detail herein.

[0052] In another embodiment, the chiller 200 may be formed as shown in FIG. 11 . The chiller 200 is similar to the chiller 100 of FIG. 1 and includes a reservoir 210 configured to hold a heat exchange fluid 710, an evaporator coil 260 for circulating a coolant disposed within the reservoir 210, and a chiller coil 230 through which the beverage flows and also disposed within the reservoir 210. However, the chiller 200 differs from the chiller 100 in that the chiller coil 230 defines a central volume 234 and the evaporator coil 260 is disposed within the central volume 234 of the chiller coil 230. Thus, the positions of the chiller coil 230 and the evaporator coil 260 are transposed compared to the chiller 100. The chiller coil 230 at least partially surrounds the evaporator coil 260. The evaporator coil 260 may be wound around the same axis Y as the chiller coil 230. The evaporator coil 260 and the chiller coil 230 may be arranged concentrically.

[0053] The chiller coil 230 of the chiller 200 may follow the periphery of the reservoir 210. As a result, the length of the chiller coil 230 within the reservoir 210 may be longer relative to the chiller coil 130 of the chiller 100. Thus, the chiller 200 may have the same footprint as the chiller 100 while allowing a larger volume of beverage to be cooled by the chiller 200 at a given time. Furthermore, the bank 720 formed on the evaporator coil 260 may be more compact in the chiller 200. The bank 720 formed on the evaporator coil 260 may maintain an open central region within the evaporator coil 260 to allow heat exchange fluid to circulate within the central region of the evaporator coil 260 and may provide space for an agitator.

[0054] The evaporator coil 260 of the chiller 200 may include a protrusion 270. The protrusion 270 may have the same arrangement, structure, and characteristics as described above with respect to the evaporator coil 160 and the protrusion 170. However, the protrusion 270 extends in a direction from the outer surface of the evaporator coil 260 toward the chiller coil 230, such that the protrusion 270 extends outward from the evaporator coil 260 toward the chiller coil 230, whereas the protrusion 170 of the evaporator coil 160 of the chiller 100 extends inward toward the central volume 164 of the evaporator coil 160.

[0055] In some embodiments, the evaporator coil 260 of the chiller 200 may include a protrusion 270 including a foam 278, as shown in FIG. 12 , for example. The foam 278 may extend from the evaporator coil 260 toward the central volume of the evaporator coil 260, away from the central volume 264 of the evaporator coil 260, or both. Thus, the foam 278 may be disposed on opposing sides of the evaporator coil 260. The foam 278 may be porous or have a reticulated structure. The foam 278 may help facilitate the rapid formation of a bank of frozen heat exchange fluid on the evaporator coil 260 and the foam 278. In some embodiments, the foam 278 may extend the entire length of the evaporator coil 260. However, in some embodiments, the foam 278 may be disposed on only a portion of the evaporator coil 260. In some embodiments, the foam 278 may be made of the same material as the evaporator coil 260, and in some embodiments, the foam 278 may be a metallic foam, such as copper foam, however, in other embodiments, the foam 278 may be made of a non-metallic material, such as paraffin, among others.

[0056] While the exemplary chillers 100 and 200 are described herein for illustrative purposes, it is understood that other arrangements of the evaporator coil and one or more chiller coils within the chiller's reservoir are possible. It is further understood that the heat exchange efficiency of any chiller having an evaporator coil can be improved by incorporating the protrusions described herein. In some embodiments, the heat exchange efficiency of a chiller having a reservoir, evaporator coil, and chiller coil can be enhanced by attaching one or more protrusions described herein to the outer surface of the evaporator coil. In this manner, as refrigerant is circulated through the evaporator coil, a bank of frozen heat exchange material, such as an ice bank, can rapidly form along the evaporator coil and along the protrusions, increasing the surface area of ​​the bank and therefore the interface between the solid and liquid heat exchange fluid. In some embodiments, the heat transfer efficiency of a chiller having a reservoir, evaporator coil, and chiller coil can be enhanced by attaching protrusions as described herein to the outer surface of the chiller coil. In this manner, the protrusions provide conductive heat transfer and increase the surface area for heat transfer with the chiller coil.

[0057] Some embodiments described herein relate to a chiller 300 having a swirl tube 390 configured to facilitate circulation of a heat exchange fluid 710 within a reservoir 310, as shown in Figures 13 and 14. The chiller 300 may have the same structure and features as described above with respect to the chiller 100. Thus, the chiller 300 may include a reservoir 310, an evaporator coil 360, and a chiller coil 330. The evaporator coil 360 may define a central volume 364 in which the chiller coil 330 is disposed. The evaporator coil 360 may include a protrusion 370 as discussed above with respect to the protrusion 170 of the evaporator coil 160.

[0058] Chiller 300 may further include a pump 380 configured to circulate heat exchange fluid 710 within reservoir 310. Pump 380 may be submerged within heat exchange fluid 710 within reservoir 310. In some embodiments, pump 380 may be disposed at lower end 311 of reservoir 310. Pump 380 may include an inlet 382 configured to draw heat exchange fluid 710 from reservoir 310 into pump 380. Pump 380 and inlet 382 of pump 380 may be positioned to draw heat exchange fluid 710 from a central volume 334 defined by chiller coil 330. Thus, pump 380 or inlet 382 of pump 380 may be positioned within central volume 334 of chiller coil 330. Pump 380 may include one or more outlets for discharging heat exchange fluid 710 so as to circulate heat exchange fluid 710. The outlets may be positioned to direct the heat exchange fluid 710 laterally.

[0059] In some embodiments, the swirl tube 390 may be in communication with the pump 380 and may extend from the pump 380 into the space between the chiller coil 330 and the evaporator coil 360. The chiller coil 330 may be tightly wound such that there is limited space between the windings 332 of the chiller coil 330. As a result, the heat exchange fluid 710 in the central volume 334 of the chiller coil 330 may not easily circulate within the reservoir 310. This may inhibit heat transfer from the heat exchange fluid 710 in the central volume 334 to the evaporator coil 360 and the bank of frozen heat exchange material formed on the protrusions 370.

[0060] In some embodiments, the pump 380 may be configured to draw the heat exchange fluid 710 from the central volume 334 and disperse the heat exchange fluid 710 toward the bank of frozen heat exchange fluid through a swirl tube 390. The swirl tube 390 may include one or more windings. The swirl tube 390 may be constructed of a flexible material. The windings of the swirl tube 390 may be spaced apart more widely than the windings of the chiller coil 330 or the evaporator coil 360, so that the swirl tube 390 does not affect the circulation of the heat exchange fluid 710 within the reservoir 310. The swirl tube 390 may include one or more outlets 392. The swirl tube 390 may include an outlet 392 at an end 394 of the swirl tube 390. Additional outlets 392 may be positioned along the length of the swirl tube 390. Each outlet 392 may be positioned such that heat exchange fluid escaping from the outlet 392 is directed toward a protrusion 370 of the evaporator coil 360. In this way, the relatively warm heat exchange fluid from the central volume 334 of the chiller coil 330 is directed towards the bank of frozen heat exchange fluid 710. This helps induce turbulence, promote heat transfer, and circulate the heat exchange fluid 710 within the reservoir 310. This can help cool the beverage faster during start-up and while the beverage is being dispensed.

[0061] 14 , the pump 380 may be positioned at the lower end 311 of the reservoir 310, and the swirl tube 390 may extend from the pump 380 toward the upper end 313 of the reservoir 310. This may induce the formation of a vortex within the reservoir 310, as the cooler heat exchange fluid is at the upper end 313 of the reservoir 310 and the warmer heat exchange fluid is at the lower end 311, causing the heat exchange fluid 710 to circulate up and down. The beverage may enter the chiller coil 330 at the lower end 311 and exit the chiller coil 330 at the upper end 313, resulting in convective heat exchange with the heat exchange fluid within the reservoir 310. The countercurrent heat exchange may maximize the temperature change of the beverage within the chiller coil by maximizing the temperature difference between the beverage within the chiller coil 330 and the heat exchange fluid within the reservoir 310.

[0062] In some embodiments, chiller 400 is shown, for example, in FIGS. 15-16 . Chiller 400 may include the same structure and features as described with respect to chiller 100, except as otherwise noted herein. Similar to chiller 100, chiller 400 includes a reservoir 410 configured to contain a heat exchange fluid and an evaporator coil 460 disposed within reservoir 410 as part of a refrigeration system for circulating the coolant. Chiller 400 further includes a chiller coil 430 connected to a beverage source and disposed within reservoir 410 within a central volume 464 of evaporator coil 460. Chiller coil 430 is configured to chill the beverage and deliver the chilled beverage to a dispenser. In some embodiments, chiller 400 further includes an agitator 490 configured to circulate the heat exchange fluid within reservoir 410 and optimize heat convection.

[0063] In some embodiments, the evaporator coil 460 of the chiller 400 may be a tube having multiple windings 462 through which refrigerant may flow. The windings 462 may be arranged in a stacked configuration from the bottom end of the reservoir 410 toward the top end of the reservoir 410. The windings 462 may extend around a central axis X. During operation of the chiller 400, the windings 462 are immersed in a heat exchange fluid. The evaporator coil 460 may be arranged along the periphery of the reservoir 410. Thus, the evaporator coil 460 may be positioned adjacent to and in accordance with the inner wall of the reservoir 410. The evaporator coil 460 may have a shape corresponding to the shape of the reservoir 410. For example, if the reservoir 410 has a rectangular shape, the evaporator coil 460 may similarly have a rectangular shape, as best shown in FIG. 16 . In embodiments in which the evaporator coil 460 has a rectangular shape, the windings 462 of the evaporator coil 460 may include a linear portion 461 and a curved portion 463 (see, for example, FIG. 17).

[0064] The evaporator coil 460 may further include protrusions 470 extending from the outer surface of the windings 462 of the evaporator coil 460. In some embodiments, the protrusions 470 may extend into a central volume 464 defined by the evaporator coil 460 toward the chiller coil 430. As shown in FIGS. 17-18 , the protrusions 470 may form a lattice structure 472. The lattice structure 472 may be a two-dimensional or three-dimensional lattice structure. In some embodiments, the lattice structure 472 may include a plurality of fins 474. The fins 474 may be substantially planar or may have a generally rectangular shape. The fins 474 may extend along at least a portion of one or more windings 462 of the evaporator coil 460, such as along a straight portion 461 of the evaporator coil 460. However, in some embodiments, the fins 474 may be disposed along a curved portion 463 of the evaporator coil 460. The fins 474 may be disposed in the plane of the windings 462. The fins 474 may be connected to one another by rods 476. The rods 476 may be positioned generally parallel to the central axis of the evaporator coil 460. Furthermore, the rods 476 may be positioned approximately perpendicular to the fins 474 and parallel to one another. Thus, the fins 474 and rods 476 may form a lattice structure 472 having a grid-like configuration that defines channels 478 or passages through which liquid heat exchange fluid may flow to contact a frozen bank of heat exchange fluid formed on the evaporator 460.

[0065] The fins 474 can be spaced apart by a distance greater than the thickness of the bank of frozen heat exchange fluid formed on the fins 474, so that the bank does not completely fill the space between the fins 474 and liquid heat exchange fluid can flow in the spaces between adjacent fins 474. Similarly, the rods 476 can be spaced apart by a distance greater than the thickness of the bank of frozen heat exchange fluid formed on the rods 476, so that the bank does not completely fill the space between the rods 476 and liquid heat exchange fluid can flow between the rods 476. If the fins 474 or rods 476 are spaced too closely together, the bank of frozen heat exchange fluid may leave little or no space through which the heat exchange fluid can flow. In some embodiments, the fins 474 can be spaced apart by about 10 mm to about 30 mm, about 12 mm to about 28 mm, or about 15 mm to about 25 mm. In some embodiments, the rods 476 can be spaced apart from one another by about 8 mm to about 24 mm, about 10 mm to about 22 mm, or about 12 mm to about 20 mm.

[0066] In some embodiments, the lattice structure 472, including the fins 474 and rods 476, can be formed as a unitary structure. The lattice structure 472 can be joined to the windings 462 of the evaporator coil 460 by welding or brazing, among other fastening methods. In some embodiments, the lattice structure 472 can be formed of the same material as the evaporator coil 460. In this way, heat transfer is the same in the materials of the evaporator coil 460 and the lattice structure 472. In some embodiments, the evaporator coil 460 and the lattice structure 472 can include copper.

[0067] While not wishing to be bound by theory, the formation of a bank of frozen heat exchange fluid, e.g., ice, on the evaporator coil 460 is now described. When the chiller 400 is in use, refrigerant flows through the windings 462 of the evaporator coil 460 and evaporates at a predetermined temperature. The refrigerant evaporation process absorbs a significant amount of heat from the heat exchange fluid, and as a result, a bank of frozen heat exchange fluid begins to form, initially around the exterior of the windings 462 of the evaporator coil 460. As the material of the lattice structure 472 cools, the bank continues to form rapidly along the fins 474 of the lattice structure 472. The bank may proceed to form along the outer surfaces of the rods 476 of the lattice structure 472 that extend between adjacent fins 474.

[0068] The resulting frozen bank of heat exchange fluid defines channels 478 through which liquid heat exchange fluid may flow. The lattice structure 472 functions to increase the surface area of ​​the frozen bank of heat exchange fluid (relative to a bank of heat exchange fluid formed on the windings of the evaporator coil alone) to facilitate heat transfer from the beverage in the chiller coil 430, through the heat exchange fluid, to the frozen bank of heat exchange fluid. Additionally, the lattice structure 472 provides sufficient space to allow liquid heat exchange fluid to flow through the lattice structure 472 and contact the bank of frozen heat exchange fluid.

[0069] In some embodiments, the lattice structure 480 may define cells 488, as shown in FIGS. 19-20 , for example. The lattice structure 480 may include first rods 482 extending outward from the outer surface of one or more windings 462 of the evaporator coil 460. The first rods 482 may extend radially from the evaporator coil 460 and into a central volume of the evaporator coil 460 toward the chiller coil. The second rods 484 may be disposed perpendicular to the first rods 482 or parallel or in-plane with the plane of the windings 462. As shown in FIG. 19 , the second rods 484 may form one or more rings concentric with the windings 462. The lattice structure 480 may further include a third rod 486 parallel to the central axis of the evaporator coil 460. Thus, cells 488 may be defined by first, second, and third rods 482, 484, 486 and may be shaped as substantially open-sided cubes or rectangular prisms. Lattice structure 480 with cells 488 provides additional space for the flow of liquid heat exchange fluid compared to lattice structure 472 with fins 474 and rods 476. However, lattice structure 480 may have slightly less surface area than lattice structure 472 due to the use of first and second rods rather than fins 474.

[0070] In some embodiments, the chiller 400 may include multiple chiller coils 430, 440, each having multiple windings 434, 444 disposed within the reservoir 410. As shown in FIGS. 15-16, the chiller 400 may include a first chiller coil 430 and also a second chiller coil 440. However, it is understood that the chiller 400 may include fewer or additional chiller coils. The use of multiple chiller coils serves to increase the total volume of beverage that can be chilled by the chiller 400 at a given time. However, the number of chiller coils is constrained by the available space within the reservoir.

[0071] The chiller coils 430, 440 may be disposed within a central volume 464 defined by the evaporator coil 460. In this manner, the evaporator coil 460 at least partially surrounds the chiller coils 430, 440. Each chiller coil 430 may include multiple windings 434 arranged in a stacked configuration (see, for example, FIG. 21). The windings 434 may extend around a central axis, such as the central axis of the evaporator coil 460. In some embodiments, the windings 434 of the chiller coil 430 may be spaced apart from one another to allow heat exchange fluid to flow within the spaces between adjacent windings 434. In some embodiments, the windings 434 may be spaced apart by about 0.1 mm to about 1 mm in the direction of the central axis. In some embodiments, the windings 434 may be spaced apart by 0.5 mm. If the spaces between the windings 434 are too small, the chiller coil 430 may form a barrier that inhibits circulation of the heat exchange fluid within the reservoir 410. Increasing the space between the windings 434 reduces the number of windings 434 of the chiller coil 430 that can fit within the reservoir 410, which is undesirable.

[0072] In some embodiments, the chiller coils 430, 440 may be arranged in a nested configuration, as shown in FIG. 21 . In some embodiments, the second chiller coil 440 may be disposed within a central volume defined by the first chiller coil 430. Thus, the first chiller coil 430 may have a first diameter D1, and the second chiller coil 440 may have a second diameter D2 that is smaller than the first diameter D1. The second chiller coil 440 may be separated from the first chiller coil 430 by a gap 438. In some embodiments, the gap 438 may provide space for a liquid heat exchange fluid to flow between the chiller coils 430, 440 to facilitate heat transfer.

[0073] In some embodiments, the total length of the chiller coils 430, 440 within the chiller 400 can be from about 8 meters to about 18 meters, from about 10 meters to about 16 meters, or from about 12 meters to about 14 meters. Increasing the total length of the chiller coils 430 within the reservoir 410 increases the amount of beverage that can be chilled in a given amount of time. The second chiller coil 440 can have a length that is smaller than the length of the first chiller coil 430, for example, as shown in FIG. 21 . As the volume of the reservoir 410 increases, the total length of the chiller coils 430 can increase, so in some embodiments, the ratio of the total length of all chiller coils (in meters) to the total volume of the reservoir 410 (in liters) can range from about 2 meters / liter to about 6 meters / liter.

[0074] In some embodiments, the first chiller coil 430 may include a first inlet 431 and a first outlet 432, and the second chiller coil 440 may include a second inlet 441 and a second outlet 442. The first and second chiller coils 430, 440 may therefore define two separate flow paths through which a beverage may flow to be cooled by the chiller 400. In such embodiments, the chiller 400 may further include a splitter 408 configured to divide the incoming supply of beverage between the chiller coils 430, 440. The first chiller coil 430 may have a greater capacity to transfer heat due to its closer proximity to the evaporator coil 460 and its longer overall length relative to the second chiller coil 440. As a result, the splitter 408 may provide a larger portion of the incoming beverage to the first chiller coil 430 than to the second chiller coil 440. For example, the splitter 408 may provide 60% or more, 65% or more, or 70% or more of the incoming flow of beverage to the first chiller coil 430 and the remainder to the second chiller coil 440. The splitter 408 may divide the flow of beverage between the two chiller coils 430, 440 so that the temperature of the beverage at both outlets 432, 442 is substantially the same.

[0075] In some embodiments, the first outlet 432 of the first chiller coil 430 may communicate with the second inlet 441 of the second chiller coil 440, or vice versa, such that the chiller coils 430, 440 form a single continuous flow path through which the beverage may flow. In such embodiments, the same amount of beverage may be chilled at a given time as in embodiments having first and second chiller coils 430, 440 defining separate flow paths. However, the pressure drop across a single long continuous flow path may be relatively high compared to the pressure drop across two separate flow paths having the same length, requiring a stronger pump to circulate the beverage.

[0076] In some embodiments, the chiller coils 430, 440 may include one or more connectors 450 configured to facilitate heat transfer and maintain spacing between the windings of the chiller coils 430, 440. In some embodiments, the connector 450 may include a first connector 452 connecting the first and second chiller coils 430, 440 to one another. The first connector 452 may extend through the gap 438 and help equalize heat transfer between the first and second chiller coils 430, 440. Because the first chiller coil 430 is closer to the evaporator coil 460, the first chiller coil 430 may tend to have a lower temperature, and the first connector 452 provides conductive heat transfer between the first chiller coil 430 and the second chiller coil 440. The first connector 452 may include a rod or plate having a first end connected to the first chiller coil 430 and a second end connected to the second chiller coil 440. In some embodiments, the plurality of first connectors 452 may be disposed at the upper ends of the chiller coils 430, 440, and the second plurality of first connectors 452 may be disposed at the lower ends of the chiller coils 430, 440. The first connectors 452 may be disposed in a plane generally transverse to the longitudinal axis of the chiller 400. In some embodiments, the first connectors 452 may be the same material as the chiller coils 430, 440, for example, stainless steel. However, in some embodiments, the first connectors 452 may be copper or another metal with high thermal conductivity.

[0077] Additionally, in some embodiments, each chiller coil 430, 440 may include a second connector 454 that extends along the outer surface of the chiller coil 430, 440 in a direction parallel to the central axis of the evaporator coil 460. The second connector 454 may help to equalize heat transfer between different windings of the same chiller coil 430, 440. Additionally, the second connector 454 may help to maintain spacing between adjacent windings 434, 444.

[0078] The chiller coil may be configured to maximize heat transfer between the beverage within the chiller coil and the heat exchange fluid within the reservoir 410. The rate at which heat is extracted from the beverage flowing through the chiller coil 430 depends on several factors, including the material of the chiller coil 430, the inner diameter of the coil 430, and the wall thickness of the chiller coil 430. It is understood that the chiller 400 may have multiple chiller coils, but for simplicity, the following discussion will relate to a single chiller coil 430.

[0079] In some embodiments, the chiller coil 430 may be formed of stainless steel, such as 300 or 400 series stainless steel. Stainless steel offers high corrosion resistance and results in little or no contamination of beverages that come into contact with the chiller coil 430. Additionally, stainless steel has a relatively high thermal conductivity to facilitate the transfer of heat through the chiller coil.

[0080] The cross-sectional area of ​​a chiller coil 430 according to one embodiment is shown in FIG. 22. In some embodiments, the chiller coil 430 may have a substantially circular cross-sectional area. However, in some embodiments, the chiller coil 430 may have an elliptical cross-sectional area. A chiller coil 430 having an elliptical cross-sectional area may have the highest heat transfer of any cross-sectional shape. Additionally, the elliptical cross-sectional shape allows a greater number of windings of the chiller coil 430 to fit within the reservoir 410 of the chiller 400 due to the reduced height of the elliptical cross-sectional area relative to the circular cross-sectional area.

[0081] Wall thickness of each chiller coil 430 tw may be selected to facilitate the transfer of heat from the beverage in the chiller coil 430 to the heat exchange fluid in the reservoir 410. As shown in FIG. w The radial distance may be defined as the shortest radial distance from the inner surface 436 of the chiller coil 430 to the outer surface 439 of the chiller coil 430. Generally, conduits for circulating beverages within a beverage dispenser have a wall thickness of approximately 1 mm. In some embodiments, the wall thickness of the chiller coil 430 may range from 0.2 mm to 1.0 mm, and may be approximately 0.5 mm. As the wall thickness increases, the rate of heat transfer decreases due to the additional material in the wall of the chiller coil 430. Further reducing the wall thickness of the chiller coil 430 below 0.2 mm may further increase the heat transfer rate, but a chiller coil 430 with a very thin wall thickness may become impractical and may be prone to cracking when the chiller coil 430 is formed into a desired configuration (e.g., multiple rectangular or circular windings). In some embodiments, the chiller coil 430 has a circular cross-sectional area and a small inner diameter D of about 4.5 mm to about 6.5 mm. i As the inner diameter of the chiller coil 430 decreases, the rate of heat transfer increases.

[0082] In some embodiments, the chiller 400 may provide countercurrent heat exchange of the beverage through the chiller coil 430 in the reservoir 410 to maximize the temperature reduction of the beverage within the chiller coil. In such embodiments, the beverage may flow through the chiller coil 430 from the lower end to the upper end of the chiller coil 430. Thus, the beverage flows in a generally upward direction through the chiller coil 430. The temperature of the heat exchange fluid within the reservoir 410 may be relatively low at the upper end of the reservoir 410 and relatively high at the lower end of the reservoir 410. As a result, the flow of the heat exchange fluid within the reservoir may be from the upper end to the lower end, resulting in countercurrent heat exchange with the beverage flowing through the chiller coil 430.

[0083] In some embodiments, the chiller 400 may include an agitator 490 configured to circulate the liquid heat exchange fluid in the reservoir 410, as best shown in FIGS. 15-16 . Because the liquid heat exchange fluid adjacent to the bank is relatively cool and the liquid heat exchange fluid adjacent to the chiller coil 430 is relatively warm, the agitator 490 helps circulate the heat exchange fluid to enhance thermal convection. The agitator 490 may be positioned along the central axis X of the chiller 400. The agitator 490 may be positioned in a central volume defined by the chiller coils, such as the innermost chiller coil of the plurality of chiller coils 440. In some embodiments, the agitator 490 may be positioned to extend from the upper end 401 of the chiller 400 toward the lower end 403 of the chiller 400. However, in some embodiments, the agitator 490 may be positioned to extend from the lower end 403 of the chiller 400 toward the upper end 401. In some embodiments, the agitator 490 may be submersible.

[0084] In some embodiments, the agitator 490 may include an impeller 492 having one or more blades 494. The impeller 492 may be positioned to extend from the upper end 401 toward the lower end 403 of the chiller 400. In some embodiments, the impeller 492 may extend the entire height of the reservoir 410. In some embodiments, the blades 494 may be positioned at an angle A relative to the central axis X. The angle A determines the flow of heat exchange fluid within the 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 relative to the central axis X to maximize the flow of heat exchange fluid within the reservoir 410.

[0085] The agitator 490 may include a motor 496 configured to cause rotation of the impeller 492. In operation of the chiller 400, the motor 496 may be immersed in the liquid heat exchange fluid in the reservoir 410. In some embodiments, the agitator 490 may include a motor disposed external to the reservoir 410, with the impeller 492 disposed within the reservoir 410, such that the motor 496 is not immersed in the heat exchange fluid. The motor 496 may be a direct current (DC) motor. In some embodiments, the motor 496 may be configured to rotate the impeller 492 at a speed of 8,000 rpm or greater, 9,000 rpm or greater, or 10,000 rpm or greater, and the rotational speed of the impeller 492 may be in the range of 9,000 to 12,000 rpm. Increasing the rotational speed allows the heat exchange fluid to reach a uniform temperature in a shorter period of time, such as a few seconds, to facilitate heat transfer. A lower rotational speed may require a longer time to achieve a uniform temperature of the heat exchange fluid, which may slow or retard heat transfer.

[0086] In some embodiments, the operation of a chiller as described herein can be controlled based on one or more temperature sensors. The chiller may include a control unit that controls the operation of the chiller, which controls the operation of the cooling system, agitator, and other components based on input from the temperature sensors. Operation of the cooling system and agitator of a chiller based on readings from the temperature sensors is described in U.S. Patent Application No. 16 / 875,975 (U.S. Publication No. 2020 / 0361758(A1)), which is incorporated herein by reference in its entirety.

[0087] In some embodiments, the temperature sensor 404 may include a thermistor, such as a negative temperature type thermistor (NTC). In some embodiments, the first temperature sensor (or sensors) 404A may be used to control the operation of a compressor of a cooling system, and the second temperature sensor (or sensors) 404B may be used to control the operation of an agitator 490, as shown in FIG. 15. However, in some embodiments, the chiller 400 may include only the first temperature sensor or the second temperature sensor. For example, in an embodiment without an agitator, the chiller may not include a second temperature sensor used to control the operation of the agitator.

[0088] In some embodiments, the 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 the evaporator toward the chiller coil. The refrigeration system is operated to prevent the bank of frozen heat exchange fluid from growing too close to the chiller coil. When the first temperature sensor 404A detects a temperature within a predetermined temperature range that indicates the growth of the frozen bank of heat exchange fluid to a certain thickness, the compressor may be deactivated to prevent further growth of the frozen bank of heat exchange fluid. As discussed above, if the frozen bank continues to grow, it may approach the chiller coil, resulting in freezing of the beverage within the chiller coil. The first temperature sensor 404A may be positioned a predetermined distance from the evaporator coil 460, and when the bank approaches the temperature sensor, the temperature sensor 404A may detect a low temperature and deactivate the refrigeration system, stopping the circulation of the coolant. The temperature sensor 404A may be positioned so that its outer surface facing the evaporator coil 460 is at the desired wall thickness for the bank. When the bank contacts the temperature sensor 404A, the temperature sensor 404A may detect a temperature below 0° C. and may communicate with the control unit to shut down the cooling system 800.

[0089] In some embodiments, the cooling system may be configured to operate at an upper threshold temperature TUT and the lower threshold temperature T LT The cooling system operates within a predetermined temperature band having a temperature of 0°C (point a). FIG. 23 is provided to illustrate the operation of the cooling system, with the understanding that the change in temperature of the heat exchange fluid may not be linear or constant over time. When the chiller is initially started and the heat exchange fluid is at ambient temperature (point a), the cooling system may operate to form a bank of frozen heat exchange fluid. As the temperature decreases, the temperature may exceed an upper threshold temperature and enter a predetermined temperature band (point b). The cooling system continues to operate to facilitate ice formation. When the temperature reaches a lower threshold temperature (point c), which may be below 0°C, the cooling system may shut down to stop further growth of the bank. As the temperature increases due to consumption or depletion of the bank of frozen heat exchange fluid, the cooling system remains inactive as the temperature rises within the predetermined temperature band. When the temperature reaches an upper temperature threshold (point d), which may be approximately 0°C, the cooling system may operate again to begin restoring the bank of frozen heat exchange fluid. Additionally, the cooling system may be configured to remain activated or deactivated for a predetermined minimum time to prevent frequent activation and deactivation of the cooling system, hi some embodiments, the predetermined minimum time is between 1 minute and 5 minutes.

[0090] In some embodiments, the chiller 400 may further include a second temperature sensor 404B configured to detect the temperature of the beverage within the chiller coil. The second temperature sensor may be positioned immediately adjacent to or in contact with the outer surface of the chiller coil. The second temperature sensor 404B may detect the temperature of the chiller coil and thus may be used to calculate the temperature of the beverage within the chiller coil 430. In embodiments with two or more chiller coils, the second temperature sensor may be positioned adjacent to the outermost chiller coil (the chiller coil positioned closest to the evaporator coil). However, in some embodiments, the sensor may be positioned within the chiller coil 430 and in contact with the beverage to determine the temperature of the beverage. For example, the sensor may include a fiber optic temperature sensor or temperature probe that directly determines the temperature of the beverage at a specific location on the chiller coil 430.

[0091] A chiller agitator, such as agitator 490, can be configured to operate within a predetermined temperature band, including an upper temperature threshold and a lower temperature threshold. During installation, the chiller is filled with heat exchange fluid at ambient temperature. The evaporator coil 460 cools the heat exchange fluid in the reservoir 410, and agitator 490 is not operating when a bank of frozen heat exchange fluid begins to form around the evaporator coil 460. It is undesirable to operate agitator 490 when the cooling system is operating and the temperature of the heat exchange fluid is decreasing from ambient temperature because operating agitator 490 to circulate the heat exchange fluid may prevent or delay the formation of a frozen bank of heat exchange fluid around the evaporator coil 460. However, as the temperature detected by the second temperature sensor 404B falls below the upper threshold temperature and a bank of frozen heat exchange fluid is formed, activating the agitator 490 serves to circulate the liquid heat exchange fluid, facilitating the transfer of heat from the chiller coil 430 and rapidly cooling the beverage flowing through the chiller coil 430. As the temperature detected by the second temperature sensor 404B continues to decrease (i.e., as the temperature of the chiller coil 430 decreases), the agitator 490 may be deactivated when the second temperature sensor 404B detects a temperature below the lower threshold temperature. As the temperature detected by the second temperature sensor 404B reaches the lower threshold temperature, which may range from about 0°C to about 2°C, the agitator 490 is deactivated (i.e., turned off) to prevent unnecessary depletion of the bank of frozen heat exchange fluid. Furthermore, reducing the temperature below the lower threshold temperature may be inefficient and impractical; therefore, the agitator 490 may be deactivated to conserve energy and eliminate heat transfer from the agitator to the heat exchange fluid. As the temperature rises from a lower threshold temperature within a predetermined temperature band, agitator 490 remains deactivated until an upper threshold temperature (e.g., about 1°C to about 5°C) is reached, at which point agitator 490 may be activated again.

[0092] In some embodiments, the agitator 490 may further initiate operation based on the detection of a user's presence. In such embodiments, the chiller 400 (or a beverage dispenser including a chiller) may include a proximity sensor 498 configured to detect the presence of a user or object within a predetermined distance of the chiller or beverage dispenser (see, for example, FIG. 25). In some embodiments, the predetermined distance may be within 50 cm, within 30 cm, or within 10 cm of the chiller. The predetermined distance is selected to activate when a user who wishes to use the chiller is present, while avoiding activation when someone who does not wish to use the chiller passes by or is in the general area of ​​the chiller 400. In some embodiments, the proximity sensor 498 is activated only if motion is detected for a minimum period of time.

[0093] If the proximity sensor 498 detects a user or object within a predetermined distance, indicating the presence of a user, the agitator 490 of the chiller 400 may activate for a first predetermined time period. The first predetermined time period may range from 5 to 60 seconds, 10 to 40 seconds, or 20 to 30 seconds. In this manner, the chiller 400 may begin circulating the heat exchange fluid in the reservoir 410 in preparation for the user to dispense a beverage from the chiller. The temperature sensor 404B may have a delay or latency in detecting the temperature of the chiller coil 430, and activation of the chiller 400 based on the user's proximity helps ensure that the agitator is activated when the chiller 400 is used to facilitate heat transfer. If the user does not dispense a beverage, the agitator 490 simply deactivates after the first predetermined time period.

[0094] In some embodiments, when a user uses the chiller 400 to dispense a beverage, the agitator 490 may operate for a second predetermined time period, such as from about 30 seconds to about 150 seconds, from about 50 seconds to about 130 seconds, or from about 70 seconds to about 110 seconds. Upon completion of the second predetermined time period, the agitator 490 operates based on the temperature sensor 404B as discussed above. The chiller 400 may operate the agitator 490 for the second predetermined time period whenever the chiller is used to dispense a beverage. While operational logic is discussed with respect to the agitator 490, it is understood that the same operational logic may be applied with other types of agitators.

[0095] In some embodiments, the chillers described herein can include a heat exchange fluid that is an ionic liquid. While it is desirable to have as large a bank of frozen heat exchange fluid as possible to facilitate heat transfer, the size of the bank of frozen heat exchange fluid can be limited by the dimensions of the reservoir and other components within the reservoir. As discussed, a bank of frozen heat exchange fluid can cause freezing of beverages within the chiller coil if the bank is too close to the chiller coil.

[0096] Ionic liquids can be useful as heat exchange fluids in chillers because they can have freezing points higher than that of water. As a result, the ionic liquid in the reservoir can freeze to 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 can be frozen and in a solid phase. The entire volume of the reservoir can become a bank of frozen heat exchange fluid, and heat can be extracted during a phase change of the bank at a constant temperature. As will be appreciated by those skilled in the art, conductive heat transfer can proceed much more efficiently in the solid phase than convective heat transfer via a liquid heat exchange fluid. Furthermore, because the freezing point of ionic liquids is higher than that of water, the bank can form more rapidly compared to water as a heat exchange fluid.

[0097] In some embodiments, ionic liquids can have a freezing point of about 0.01°C to about 5°C at atmospheric pressure, so that the freezing point is higher than that of water to prevent freezing of beverages in chiller coils. Ionic liquids for use as heat exchange fluids can have a high latent heat of fusion, in some embodiments, in the range of 50 kJ / kg to 400 kJ / kg, 150 kJ / kg to 350 kJ / kg, or 200 kJ / kg to 300 kJ / kg. Furthermore, ionic liquids for use as heat exchange fluids can have low vapor tension, can be inert (non-flammable and non-corrosive), can be recyclable or reusable, and can exhibit consistent physical and chemical properties over long periods of time (e.g., one year or more) so that the performance of the heat exchange fluid does not deteriorate over time. In some embodiments, ionic liquids suitable for use as heat exchange fluids in the chillers described herein may be selected from 1-butyl-3-methylimidazolium ionic liquids, such as BMIM-NTF2 or BMIM-PF6, imidazolium-based ionic liquids, pyridinium-based ionic liquids, and morpholine-based ionic liquids, and combinations thereof.

[0098] In some embodiments, chiller 500 includes a reservoir 510 containing a heat exchange fluid that is an ionic liquid 730, as shown in FIG. 24 . Chiller 500 may be configured as described above with respect to any of chillers 100, 200, 300, and 400, except as otherwise described herein. Accordingly, chiller 500 may include an evaporator coil 560 through which a coolant flows and one or more chiller coils 530, 540 through which a beverage flows. Chiller 500 differs primarily in its use of ionic liquid 730 as the heat exchange fluid. Furthermore, the use of ionic liquid 730 allows chiller 500 to be manufactured without a stirrer, as described in more detail below. Furthermore, chiller 500 may have a single temperature sensor 504 located along the central axis of chiller 500 configured to stop the refrigeration system from operating when all of the heat exchange fluid is frozen.

[0099] The reservoir 510 of the chiller 500 may be sealed such that the ionic liquid 730 is contained within the reservoir 510 and is inaccessible to the end user. Thus, the chiller 500 may be assembled, filled with the ionic liquid 730, and sealed. This may help prevent the ionic liquid 730 from escaping during storage or transportation of the chiller 500.

[0100] The evaporator coil 560 of the chiller 500 may include protrusions 570, for example, as described herein with respect to the protrusions 170, 470. The protrusions 570 may help the ionic liquid freeze to a solid phase more quickly than in embodiments without the protrusions 570.

[0101] Additionally, chiller 500 does not include an agitator for circulating the heat exchange fluid. Because ionic liquid 730 may be in a solid phase during operation of chiller 500, an agitator is not necessary to circulate the liquid-phase heat exchange fluid to promote thermal convection in the liquid phase so that the ionic liquid changes phase as quickly as possible. As a result, construction of chiller 500 is simplified by eliminating the agitator (e.g., agitator 490) and second temperature sensor (e.g., 404B). Furthermore, because the agitator takes up space within the reservoir, elimination of the agitator allows a greater amount of heat exchange fluid to be contained in the reservoir relative to chiller embodiments that include an agitator.

[0102] Furthermore, when an ionic liquid is used as the heat exchange fluid, the operational chiller logic of 500 is simplified. Chiller 500 does not require a temperature sensor to monitor the growth of the bank of frozen heat exchange fluid because substantially all ionic liquid freezes to a solid phase, while the beverage continues to flow through chiller coils 530, 540 without risk of freezing. The mixture of ionic liquids as the heat exchange fluid can be carefully selected so that the latent heat of fusion throughout the volume of chiller 500 is greater than that of an ice bank, such as bank 720. Furthermore, because there is no agitator in chiller 500, a temperature sensor (e.g., temperature sensor 404B) is not required to control the operation of the agitator.

[0103] In some embodiments, beverage dispenser 600 may include chillers 100, 200, 300, 400, 500 described herein. As shown in FIG. 25, beverage dispenser 600 may include a housing 610 enclosing a chiller, such as chiller 100. Because beverage dispenser 600 may have a compact configuration, chiller 600 may be placed on a countertop, tabletop, or the like, in a home kitchen or office break room, or the like. Beverage dispenser 600 may be configured to dispense a base liquid, such as hot water, cold water, alkaline water, or sparkling water, and may be configured to dispense flavorings in addition to the base liquid to provide flavored beverages or carbonated soft drinks. A source of base liquid 750 may be located remotely from beverage dispenser 600 (see, for example, FIG. 26). Similarly, the source of flavoring 740 may be remotely located and provided to the beverage dispenser 600 via a conduit, or one or more flavorings may be enclosed within the housing 610 of the beverage dispenser 600. The beverage dispenser 600 may further include a refrigeration system 800 for circulating a refrigerant through the evaporator coil 160 of the chiller 100.

[0104] The housing 610 of the beverage dispenser 600 may define a beverage container receiving area 615. The beverage dispenser 600 may include a nozzle 620 disposed on the housing 610 at the beverage container receiving area 615 for dispensing a beverage, such as a base liquid or a mixed base liquid and flavoring. The nozzle 620 may be disposed on an upper end 614 of the housing 610 at the beverage container receiving area 615. A container 880, such as a cup or bottle, may be disposed in the beverage container receiving area 615 to be filled with a beverage through the nozzle 620. The container 880 may be disposed on a lower end 612 of the housing 610 at the beverage container receiving area 615, which may include a drip tray 619 for collecting excess liquid from the dispenser 105.

[0105] The housing 610 of the beverage dispenser 600 may further include a user interface 640 for receiving user input, as shown in FIG. 26 . The user interface 640 may include one or more actuators 642, such as buttons, switches, levers, knobs, dials, touch panels, touch screens, etc., for receiving user input. The user input may include a beverage selection. In some embodiments, each beverage may have a separate actuator. In some embodiments, the user interface 640 may alternatively or additionally include a display 644 for providing information to the user, such as instructions for operating the beverage dispenser 600, a list of available beverages, or maintenance information. In some embodiments, the display 644 may be a touch screen display for receiving user input.

[0106] The beverage dispenser 600 may include a control unit 650 for controlling the operation of the beverage dispenser 600. The control unit 650 may communicate with the user interface 640 such that user input received by the user interface 640 is communicated to the control unit 650, which may dispense a beverage based on the user input, such as by operating one or more pumps and valves 660 to drive and control the flow of base liquid and / or flavorings. In some embodiments, the control unit 650 may further communicate with the cooling system 800 to circulate the coolant. The control unit 650 may also communicate with a chiller to implement the chiller's operating logic, such as by receiving input from a temperature sensor and activating or deactivating the cooling system and agitator based on the input from the temperature sensor, as discussed herein.

[0107] In some embodiments, beverage dispenser 600 may include additional processing units for processing the base liquid, such as a carbonator 670, an alkaline cartridge, a water filter, or a mixer for combining the base liquid with flavorings. The processing units may be located upstream or downstream of chiller 100. In some embodiments, a water filter may filter water before it is chilled by chiller 100. In some embodiments, carbonator 670 may be located downstream of the chiller so that the water is chilled before carbonation. 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 or before reaching the dispensing nozzle. However, in some embodiments, water may be mixed with flavorings, then chilled by chiller 100, and then carbonated.

[0108] 27 illustrates an exemplary computer system 900 in which embodiments or portions thereof may be implemented as computer readable code. The control unit 650 discussed herein may be a computer system having all or some of the components of computer system 900 for performing the processes discussed herein.

[0109] Where programmable logic is used, such logic may be executed on a commercially available processing platform or a special purpose device. Those skilled in the art will appreciate that embodiments of the disclosed subject matter may be practiced with a variety of computer system configurations, including multi-core multiprocessor systems, minicomputers and mainframe computers, computers linked or clustered with distributed functionality, and pervasive or small computers that may be embedded in virtually any device.

[0110] For example, at least one processor device and memory may be used to implement the above embodiments. The processor device may be a single processor, multiple processors, or a combination thereof. The processor device may have one or more processor "cores."

[0111] Various embodiments may be implemented in terms of this example computer system 900. After reading this specification, it will become apparent to one skilled in the art how to implement one or more of the present inventions using other computer systems and / or computer architectures. While operations may be described as sequential processes, some of the operations may in fact be performed in parallel, concurrently, and / or in a distributed environment, and may be performed by program code stored locally or remotely for access by single or multi-processor machines. Additionally, in some embodiments, the order of operations may be rearranged without departing from the spirit of the disclosed subject matter.

[0112] The processor device 904 may be a dedicated or general-purpose processor device. As will be appreciated by those skilled in the art, the processor device 904 may also be a single processor in a multi-core / multi-processor system operating alone or in a cluster of computing devices operating in a cluster or server farm. The processor device 904 is connected to a communications infrastructure 906, such as a bus, message queue, network, or multi-core message passing scheme.

[0113] The computer system 900 also includes a main memory 908, e.g., random access memory (RAM), and may also include a secondary memory 910. The secondary memory 910 may include, for example, a hard disk drive 912 or a removable storage drive 914. The 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. The removable storage unit 918 may include a floppy disk, a magnetic tape, an optical disk, a universal serial bus (USB) drive, or the like, which is read from and written to by the removable storage drive 914. As will be appreciated by those skilled in the art, the removable storage unit 918 includes a computer-usable storage medium having stored thereon computer software and / or data.

[0114] The computer system 900 (optionally) includes a display interface 902 (which may include input and output devices such as a keyboard, mouse, etc.) that transfers graphics, text, and other data to be displayed on a display 940 from a communications infrastructure 906 (or from a frame buffer, not shown).

[0115] 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 interface 920. Examples of such means may include program cartridges and cartridge interfaces (such as those found in video game devices), removable memory chips (such as EPROMs or PROMs) and associated sockets, and other removable storage units 922 and interfaces 920 that can transfer software and data from the removable storage unit 922 to computer system 900.

[0116] Computer system 900 may also include a communications interface 924. Communications interface 924 allows software and data to be transferred between computer system 900 and external devices. Communications interface 924 may include a modem, a network interface (such as an Ethernet card), a communications port, a PCMCIA slot and card, or the like. The software and data transferred via communications interface 924 may be in the form of signals, which may be electronic, electromagnetic, optical, or other signals capable of being received by communications interface 924. These signals may be provided to communications interface 924 via communications path 926. Communications 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 communications channel.

[0117] As used herein, the terms "computer program medium" and "computer usable medium" are used generally to 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 memory, such as main memory 908 and secondary memory 910, which may be memory semiconductors (e.g., DRAM, etc.).

[0118] 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 communications interface 924. When executed, such computer programs enable computer system 900 to implement the embodiments discussed herein. Specifically, when executed, the computer programs enable processor device 904 to perform the processes of the embodiments discussed herein. Such computer programs thus represent controllers of computer system 900. When an embodiment is 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 communications interface 924.

[0119] Embodiments of the present invention may also be directed to computer program products including software stored on any computer-usable medium. Such software, when executed on one or more data processing devices, causes the data processing devices to operate as described herein. Embodiments of the present invention may employ computer-usable or readable media. Examples of computer-usable media 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 and optical storage devices, MEMS, nanotechnology storage devices, etc.).

[0120] It is understood 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 invention as contemplated by the inventors, and thus are not intended to limit the scope of the invention and the appended claims in any way.

[0121] The present invention has been described above with the aid of functional building blocks that illustrate implementations of certain functions and their relationships. The boundaries of these functional building blocks have been arbitrarily defined herein for the convenience of the description. Alternative boundaries can be defined so long as the certain functions and their relationships are appropriately performed.

[0122] The foregoing description of specific embodiments makes the general nature of the present invention fully apparent, and others, by applying the knowledge of those skilled in the art, may readily modify and / or adapt such specific embodiments for various uses without undue experimentation and without departing from the general concept of the present invention. Such adaptations and modifications are therefore 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 used herein is for the purpose of description and not of limitation, and therefore should be interpreted by those skilled in the art in light of the teaching and guidance provided herein.

[0123] The breadth and scope of the present invention 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.

Claims

1. 1. A chiller for cooling beverages, comprising: a reservoir configured to hold a heat exchange fluid; an evaporator coil disposed within the reservoir, the evaporator coil comprising: a plurality of windings configured to circulate a coolant; and an evaporator coil including a protrusion extending from an outer surface of one or more of the plurality of windings; a chiller coil disposed within the reservoir, the beverage being configured to flow through the chiller coil; When the refrigerant is circulated through the plurality of windings of the evaporator coil, a bank of frozen heat exchange fluid is formed on the windings and on the protrusions.

2. The chiller of claim 1 , wherein the protrusion comprises one or more fins.

3. The chiller of claim 1 , wherein the protrusion comprises one or more rods.

4. The chiller of claim 1 , wherein the protrusions include a lattice structure.

5. 2. The chiller of claim 1, wherein the evaporator coil is formed from a first material and the protrusions are formed from a second material, the first material being the same as the second material.

6. The chiller of claim 1 , wherein the evaporator coil defines a central volume, and the chiller coil is disposed within the central volume of the evaporator coil.

7. The chiller of claim 1 , further comprising a second chiller coil disposed within the reservoir, the beverage configured to flow through the first chiller coil and the second chiller coil.

8. 8. The chiller of claim 7, further comprising a splitter configured to split the flow of the beverage between the first chiller coil and the second chiller coil, the splitter dividing 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.

9. The chiller of claim 1 , wherein the wall thickness of the chiller coil ranges from about 0.2 mm to about 1.0 mm.

10. The chiller of claim 1 , wherein the reservoir comprises a total volume of about 3 L to about 10 L.

11. The chiller of claim 1 , further comprising an agitator disposed within the reservoir, the agitator comprising an impeller having one or more blades.

12. 12. The chiller of claim 11, further comprising a temperature sensor configured to determine a temperature of the chiller coil, and wherein the agitator is configured to operate when the temperature of the chiller coil as detected by the temperature sensor is within a predetermined temperature range.

13. 1. A beverage dispenser comprising: a user interface configured to receive a beverage selection; 1. A chiller configured to chill a beverage, said chiller comprising: a reservoir configured to store a heat exchange fluid; an evaporator coil disposed within the reservoir and configured to circulate a refrigerant, the evaporator coil comprising a plurality of windings and protrusions extending from an outer surface of one or more of the plurality of windings of the evaporator coil; and a chiller comprising a chiller coil disposed within the reservoir, the beverage flowing through the chiller coil such that the beverage is cooled as it flows through the chiller coil, and a bank of frozen heat exchange fluid being formed on the evaporator coil and on the protrusions as the coolant is circulated through the evaporator coil; a dispensing nozzle in communication with the chiller coil for dispensing the beverage.

14. 14. The beverage dispenser of claim 13, further comprising a refrigeration system configured to circulate the coolant, the refrigeration system comprising the evaporator coil.

15. 14. The beverage dispenser of claim 13, further comprising a carbonator configured to carbonate the beverage, the carbonator in communication with the chiller coil.

16. 1. A chiller for cooling beverages, comprising: a reservoir; a heat exchange fluid stored in the reservoir, the heat exchange fluid being an ionic liquid having a freezing point of about 0°C; an evaporator coil disposed within the reservoir, the evaporator coil comprising: a plurality of windings configured to circulate a coolant; and an evaporator coil including a protrusion extending from an outer surface of one or more of the plurality of windings; a chiller coil disposed within the reservoir, the beverage flowing through the chiller coil; A chiller wherein at least a portion of the heat exchange fluid freezes to a solid phase when the refrigerant is circulated through the windings of the evaporator coil.

17. 17. The chiller of claim 16, wherein the heat exchange fluid comprises a freezing point of about 0.01°C to about 5°C.

18. 17. The chiller of claim 16, wherein the ionic liquid is selected from the group consisting of 1-butyl-3-methylimidazolium-based ionic liquids, imidazolium-based ionic liquids, pyridinium-based ionic liquids, and morpholine-based ionic liquids.

19. 17. The chiller of claim 16, wherein the ionic liquid comprises a latent heat of fusion in the range of about 200 kJ / kg to about 300 kJ / kg.

20. 17. The chiller of claim 16, wherein all of the heat exchange fluid freezes to a solid phase when the refrigerant is circulated through the windings of the evaporator coil.

Images