US20110011569A1 - Heat exchanges for dispensing sub-zero beer - Google Patents
Heat exchanges for dispensing sub-zero beer Download PDFInfo
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- US20110011569A1 US20110011569A1 US12/811,572 US81157209A US2011011569A1 US 20110011569 A1 US20110011569 A1 US 20110011569A1 US 81157209 A US81157209 A US 81157209A US 2011011569 A1 US2011011569 A1 US 2011011569A1
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- heat exchanger
- beverage
- zone
- line
- coolant
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
- F28D7/00—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
- F28D7/0008—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits for one medium being in heat conductive contact with the conduits for the other medium
- F28D7/0016—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits for one medium being in heat conductive contact with the conduits for the other medium the conduits for one medium or the conduits for both media being bent
Definitions
- This invention relates to an improved apparatus for dispensing cooled fluids, in particular beverages, such as beer.
- the beer In most commercial establishments where beer is served, the beer is supplied in barrels or kegs.
- the kegs are stored in a refrigerated cold room or cellar at a temperature range of between 3 and 10 degrees C.
- the beer is normally dispensed through beer dispensing valves/taps located away from the cold room.
- a heat exchanger or some form of extra cooler is also normally included in the system to further cool the beer in line between the cold room and the tap.
- the beer is delivered to the taps from the kegs through a conduit containing the beer delivery lines.
- the conduit also contains coolant transfer lines for recirculation of cold water or water containing a percentage of antifreeze components such as glycol.
- the beer is moved through the beer delivery lines by means of CO 2 gas pressure applied to the barrel or keg.
- the present invention seeks to provide a lower cost and preferably more efficient beverage cooling system.
- a heat exchanger comprising a coolant line and a beverage (typically beer) line embedded in a solid block of a material having a high thermal conductivity (most preferably aluminium, although other materials having high conductivity could be used) with the coolant line in the form of a first coil defining a plurality of turns located in the block and the beer line in the form of a second coil defining a plurality of coils extending around the first coil.
- a heat exchanger comprising a coolant line and a beverage (typically beer) line embedded in a solid block of a material having a high thermal conductivity (most preferably aluminium, although other materials having high conductivity could be used) with the coolant line in the form of a first coil defining a plurality of turns located in the block and the beer line in the form of a second coil defining a plurality of coils extending around the first coil.
- the location of the coolant line typically in the centre of the aluminium block and the physical arrangement of the coolant line in the form of a coil provides a cold core or central cold zone in the solid block.
- the resultant outer area provides a designated beverage cooling zone in which the beer/beverage line is located.
- the invention provides a heat exchanger comprising a coolant line and a beverage line embedded in a solid block of a material having a high thermal conductivity with the beverage line in the form of a first coil having a plurality of turns being located in the centre of the block and defining a designated beverage cooling zone and the coolant line in the form of a second coil defining a plurality of turns and extending around the first coil and defining a cold zone.
- the ratio of the volumes of these two distinct zones within the solid is an important relationship when dispensing beer at critical temperatures, often as low as ⁇ 2 degrees C.
- the volume ratio of the designated zone to the cold zone is about 150:100.
- the cold zone acts as a thermal storage of energy. This thermal storage is used to maintain controlled beverage outlet temperatures and avoid the fluctuations that are typical with existing heat exchangers.
- the coil is typically in the form of a helical coil.
- helical is not to be taken as inferring that the coils of each turn of the helical coil need be circular.
- the coils may be any shape and will typically comprise semi-circular curved ends separated by straight lengths of tubing.
- the coolant used is typically a Freon refrigerant, however the invention can easily be adapted for use with recirculating glycol.
- the coolant tubes are arranged in a helical pattern through the cold zone.
- the distance between the tubes is varied to control the rate of heat transfer from the coolant into the solid material of the cold zone.
- the distance between adjacent tubes is between 3 and 10 mm.
- the diameter of the coolant tubes used in the cold zone for transfer of cold from the coolant to the cold zone is selected based on the energy requirement of the system. Typically the range of tube diameters would be from 6 to 13 mm.
- the distance between the tubes/coils in the beverage line is varied to control the rate of heat transfer from the designated zone into the beverage.
- the distance between adjacent tubes is from 3 to 8 mm.
- the diameter of the beverage tubes used in the designated zone for transfer of heat from the beverage to the solid material is also selected based on the energy requirements of the system. Typically, the diameter may be between 7 to 11 mm.
- the distance between the coolant tubes located in the cold zone and the beverage tubes located in the designated zone affects the heat flow between the two defined solid areas.
- the preferred distance is from 2 to 6 mm.
- the relationship between the plane of the beverage tube coils and the coolant tube coils (“the angle between the tubes”) is important in maximising the heat transfer rate across the solid.
- Adjusting the angle controls the heat transfer rate across the solid. In a preferred embodiment this angle is between 80 and 110 degrees, however the angle is adjustable between 15 and 120 degrees.
- the angle provides three dimensional heat flux within the solid areas and acts as a means of inducing turbulence to the heat flow through the solid areas and maximising the available transfer of cold through the system.
- the efficiency control that is available through the present invention allows for cooling of beer to precise temperatures and even temperatures close to freezing point, using direct expanded Freon refrigeration methods.
- the present invention allows for a complete system including the refrigeration equipment to be packaged into a small area, such as is available under bars and dispensing counters etc., which removes the need for large installations and the associated costs and maintenance of the same.
- the present invention may also eliminate or ameliorate the problems associated with freezing of subzero beverages which has limited the dispensing of low alcohol beverages at temperatures less that 0 degrees C. using existing heat exchanger systems.
- the cold zone may include more than one coolant line, for example two coolant lines in parallel, or two coolant lines in series.
- one or more additional lines may pass through the first coil.
- the additional lines may include one or more lines for cooling glycol.
- the additional lines may include one or more lines for pre-chilling soft drinks, soda or the like.
- the additional lines are generally located in a central zone inside the inner cold zone.
- the ratio of the central zone to the inner cold zone to the outer zone is typically about 150:100:150.
- FIG. 1 is a schematic view of an embodiment of a solid block heat exchanger embodying the invention
- FIG. 2 is a schematic view of part of the heat exchanger illustrating the gaps between the tubes in the beverage lines;
- FIG. 3 is a schematic view of part of the heat exchanger illustrating the gaps between the tubes in the coolant lines;
- FIG. 4 is a schematic view illustrating the concepts of the inner cold zone and the designated zone
- FIG. 5 is a schematic view illustrating a variant of the heat exchanger of FIGS. 1 to 4 in which there are two parallel beverage lines;
- FIG. 6 is a schematic view illustrating a yet further embodiment of a heat exchanger in which there are two coolant lines in series;
- FIG. 7 is a schematic view of a variant of the solid block heat exchanger of FIGS. 1 to 4 in which the locations of the cold zone and cooling zones are reversed.
- FIG. 8 is a schematic view illustrating a variant of the heat exchanger of FIGS. 1 to 4 in which there is and additional cooling zone;
- FIG. 9 is a schematic view of part of the heat exchanger of FIG. 8 .
- FIG. 1 shows a solid block heat exchanger 10 comprising a first coolant line or tube (typically formed from stainless steel) in the form of a “helical” coil arrangement 11 having a plurality of turns/coils.
- a first coolant line or tube typically formed from stainless steel
- the coils are generally rectangular in plan view having semi-circular curved ends separated by straight lengths of tubing. However other coil shapes could be used.
- This coil arrangement locates generally within an cold zone 12 of the heat exchanger 10 within a rectangular box shaped volume also shown in FIG. 4 .
- the coil 11 is an inner coil as, extending around the outside of the coil arrangement 11 is a second “helical” coil arrangement 13 (also typically formed from stainless steel tubes) which in use carries beverage, typically beer, or other carbonated alcoholic drink of a similar alcohol content to beer.
- the coils are generally rectangular in plan view having semi-circular curved ends separated by straight lengths of tubing. Again, other coil shapes could be used.
- This “outer” coil arrangement locates in a zone 14 (the designated cooling zone) outside of the cold zone 12 of the heat exchanger and between that cold zone 12 and the exterior of the heat exchanger.
- the heat exchanger 10 is formed by locating the coils 11 and 13 in a rectangular mould in the arrangement shown and pouring molten aluminium over the coils to form a solid block 15 .
- Such casting techniques are well known for forming solid block heat exchangers and accordingly will not be described in detail herein.
- the open ends of the coils 11 and 13 form coolant inlets 11 a and coolant outlets 11 b, and beverage inlets 13 a and beverage outlets 13 b, respectively.
- the ratio of the volume of the two zones 12 , 14 within the solid block is an important relationship when dispensing beer at critical temperatures, often as low as ⁇ 2° C.
- the volume ratio of the designated beverage cooling zone 14 to the cold zone 12 is about 150:100.
- the cold zone 12 or core acts as a thermal storage of energy.
- This thermal storage is used to maintain controlled beverage outlet temperatures to avoid the fluctuations that are typical with the heat exchangers described in the prior art.
- the distance between the coils of the coolant coil arrangement may be varied to control the rate of heat transfer from the coolant into the solid core.
- the distance “b” between the exteriors of the tubes is between 3 and 10 mm.
- the diameter of the tubes used in the coolant coil for transfer of cold from the coolant to the cold zone is selected based on the energy requirement of the system. Typically, the diameter range would range between 6 and 13 mm.
- the distance “a” between the tubes in the beverage coil arrangement 13 is varied to control the rate of heat transfer from the beverage into the defined cold zone 12 .
- the distance between the tubes is from 3 to 8 mm.
- the diameter of the tubes used in the designated cooling zone for transfer of cold from the solid to the beverage is also selected based on the energy requirement of the system. Typically the diameter range for the beverage line tubes would be between 7 and 11 mm.
- the distance between the coolant tubes located in the cold zone and the beverage tubes located in the designated zone is a significant factor in determining the heat flow between the two defined solid areas.
- the preferred distance “c” is between 2 and 6 mm.
- the relationship between the plane of the beverage tube coils and the coolant tube coils (“the angle between the tubes”) is important in maximising the heat transfer rate across the solid.
- Adjusting the angle controls the heat transfer rate across the solid.
- the angle between the plane of the coils in the coolant coil and the beverage coil is 90°. It is preferred that the angle is between 80 and 110 degrees, however the angle may be anywhere between 15 and 120 degrees.
- the angle provides three dimensional heat flux within the solid areas and acts as a means of inducing turbulence to the heat flow through the solid areas and maximising the available transfer of cold through the system.
- the system may also be used to dispense other beverages, particularly soft drinks, such as sodas and the like.
- FIG. 5 shows a variant 110 of the heat exchanger of FIGS. 1 to 4 in which there is a second beverage line 113 running parallel to the first beverage line 13 .
- FIG. 6 shows a further variant 210 in which there are two coolant lines “in series” defining the (inner) cold zone 12 .
- a first coolant line 213 comprises a helical coil and a coolant inlet 213 a and a coolant outlet 213 b and defines one part 12 a of the inner cold zone 12 .
- a second coolant line 223 following on in series from the first coolant line, comprises a helical coil and a coolant inlet 223 a and a coolant outlet 223 b and defines the other part 12 b of the inner cold zone 12 .
- the coolant inlet 223 a is on the opposite side of the block 210 to the coolant outlet 213 b of the first coolant line.
- the cold zone 12 is inside the designated beverage cooling zone 14 which has the beverage lines passing through it, it is possible to manufacture a heat exchanger in which the location of the coolant tube coils 311 and beverage line 313 coils are reversed, so that the cold zone 312 lies outside the beverage coils 313 .
- the ratio of the volume of the cold zone 312 to the beverage line zone 314 remains 100:150, and the coolant and beverage pipe dimensions and spacings remain in the ranges described above as does the relationship between the plane of the beverage tube coils and the coolant tube coils.
- the angle is 90° as shown in FIG. 7 , although this angle can be varied between 80 and 110 degrees, even between 15 and 120 degrees.
- FIGS. 8 and 9 show additional lines in the centre of the cold core block forming a third or central zone.
- the central zone is referenced 20 and shown as rectangular parallelepiped in broken lines.
- the central zone is used for cooling as is the outer designated zone. It may have one or more lines 22 passing through it—see FIG. 6 .
- the line 22 may be a glycol line for cooling glycol, used to cool a beer transfer conduit, and/or beer font or the like.
- the volume ratio of the central zone 20 to the inner cold zone 12 to the outer zone 14 is typically about 150:100:150.
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- Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Thermal Sciences (AREA)
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- General Engineering & Computer Science (AREA)
- Devices For Dispensing Beverages (AREA)
- Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
Abstract
A heat exchanger (10) comprises a coolant line (11) and a beverage line (13), embedded in a solid block of Aluminium (15). The coolant line (11) is in the form of a first helical coil defining a plurality of turns typically located in the centre of the block. The beverage line (13) is in the form of a second helical coil defining a plurality of turns extending around the first coil. The coolant line defines a cold zone (12), typically in the centre of the block, with the volume outside the central zone carrying the beverage line ratio defining an designated beverage cooling zone (14). The volume ratio of the designated zone to the cold zone is about 150:100. The heat exchanger allows for cooling of beer to precise temperatures and even temperatures close to freezing point, using direct expanded Freon refrigeration methods. The complete system including the refrigeration equipment to be packaged into a small area, such as is available under bars and dispensing counters etc., which removes the need for large installations and the associated costs and maintenance of the same. In a variant an additional beverage cooling zone may be located inside the cold zone. The positions of the coolant and beverage lines may also be reversed in certain applications.
Description
- The present application claims priority from Australian Provisional Patent Application No 2008900054 filed on 4 Jan. 2008, the content of which is incorporated herein by reference.
- This invention relates to an improved apparatus for dispensing cooled fluids, in particular beverages, such as beer.
- In most commercial establishments where beer is served, the beer is supplied in barrels or kegs. The kegs are stored in a refrigerated cold room or cellar at a temperature range of between 3 and 10 degrees C. The beer is normally dispensed through beer dispensing valves/taps located away from the cold room. A heat exchanger or some form of extra cooler is also normally included in the system to further cool the beer in line between the cold room and the tap.
- The beer is delivered to the taps from the kegs through a conduit containing the beer delivery lines. The conduit also contains coolant transfer lines for recirculation of cold water or water containing a percentage of antifreeze components such as glycol. In practice, the beer is moved through the beer delivery lines by means of CO2 gas pressure applied to the barrel or keg.
- Recently, due to changes in customer preferences and fashions, it has become desirable to serve beer at temperatures below 0 degrees C.
- Existing systems using heat exchangers installed in line between the cold room and the beer dispensing tap, have relied on an external cold source being supplied to circulate coolant at closely controlled temperatures through the conduit and heat exchanger to cool the beer to the sub zero temperature.
- These systems have high maintenance costs associated with the external cold source and a high initial installation costs involving extensive site alterations to the beer system.
- The present invention seeks to provide a lower cost and preferably more efficient beverage cooling system.
- Any discussion of documents, acts, materials, devices, articles or the like which has been included in the present specification is solely for the purpose of providing a context for the present invention. It is not to be taken as an admission that any or all of these matters form part of the prior art base or were common general knowledge in the field relevant to the present invention as it existed before the priority date of each claim of this application.
- According to a first aspect of the present invention there is provided a heat exchanger comprising a coolant line and a beverage (typically beer) line embedded in a solid block of a material having a high thermal conductivity (most preferably aluminium, although other materials having high conductivity could be used) with the coolant line in the form of a first coil defining a plurality of turns located in the block and the beer line in the form of a second coil defining a plurality of coils extending around the first coil.
- The location of the coolant line typically in the centre of the aluminium block and the physical arrangement of the coolant line in the form of a coil provides a cold core or central cold zone in the solid block.
- The resultant outer area provides a designated beverage cooling zone in which the beer/beverage line is located.
- In a second related aspect, the invention provides a heat exchanger comprising a coolant line and a beverage line embedded in a solid block of a material having a high thermal conductivity with the beverage line in the form of a first coil having a plurality of turns being located in the centre of the block and defining a designated beverage cooling zone and the coolant line in the form of a second coil defining a plurality of turns and extending around the first coil and defining a cold zone.
- The ratio of the volumes of these two distinct zones within the solid is an important relationship when dispensing beer at critical temperatures, often as low as −2 degrees C. In a preferred embodiment the volume ratio of the designated zone to the cold zone is about 150:100.
- The cold zone acts as a thermal storage of energy. This thermal storage is used to maintain controlled beverage outlet temperatures and avoid the fluctuations that are typical with existing heat exchangers.
- The coil is typically in the form of a helical coil. As used herein “helical” is not to be taken as inferring that the coils of each turn of the helical coil need be circular. The coils may be any shape and will typically comprise semi-circular curved ends separated by straight lengths of tubing.
- The coolant used is typically a Freon refrigerant, however the invention can easily be adapted for use with recirculating glycol.
- The coolant tubes are arranged in a helical pattern through the cold zone. The distance between the tubes is varied to control the rate of heat transfer from the coolant into the solid material of the cold zone. In the preferred embodiment the distance between adjacent tubes is between 3 and 10 mm.
- The diameter of the coolant tubes used in the cold zone for transfer of cold from the coolant to the cold zone is selected based on the energy requirement of the system. Typically the range of tube diameters would be from 6 to 13 mm.
- The distance between the tubes/coils in the beverage line is varied to control the rate of heat transfer from the designated zone into the beverage. In the preferred embodiment the distance between adjacent tubes is from 3 to 8 mm.
- The diameter of the beverage tubes used in the designated zone for transfer of heat from the beverage to the solid material is also selected based on the energy requirements of the system. Typically, the diameter may be between 7 to 11 mm.
- The distance between the coolant tubes located in the cold zone and the beverage tubes located in the designated zone affects the heat flow between the two defined solid areas. The preferred distance is from 2 to 6 mm.
- This allows for predetermined heat transfer effects with in the solid to facilitate the heat transfer from the coolant to the solid and then across the solid and into the beverage.
- The relationship between the plane of the beverage tube coils and the coolant tube coils (“the angle between the tubes”) is important in maximising the heat transfer rate across the solid.
- Adjusting the angle controls the heat transfer rate across the solid. In a preferred embodiment this angle is between 80 and 110 degrees, however the angle is adjustable between 15 and 120 degrees.
- The angle provides three dimensional heat flux within the solid areas and acts as a means of inducing turbulence to the heat flow through the solid areas and maximising the available transfer of cold through the system.
- The efficiency control that is available through the present invention allows for cooling of beer to precise temperatures and even temperatures close to freezing point, using direct expanded Freon refrigeration methods.
- The present invention allows for a complete system including the refrigeration equipment to be packaged into a small area, such as is available under bars and dispensing counters etc., which removes the need for large installations and the associated costs and maintenance of the same.
- The present invention may also eliminate or ameliorate the problems associated with freezing of subzero beverages which has limited the dispensing of low alcohol beverages at temperatures less that 0 degrees C. using existing heat exchanger systems.
- There may be a plurality of beverage lines in the designated zone. There may also be a plurality of coolant lines in the cold zone. The cold zone may include more than one coolant line, for example two coolant lines in parallel, or two coolant lines in series.
- In one embodiment one or more additional lines may pass through the first coil. The additional lines may include one or more lines for cooling glycol. Alternatively the additional lines may include one or more lines for pre-chilling soft drinks, soda or the like.
- The additional lines are generally located in a central zone inside the inner cold zone. The ratio of the central zone to the inner cold zone to the outer zone is typically about 150:100:150.
- A specific embodiment of the present invention will now be described, by way of example only, and with reference to the accompanying drawings, in which:
-
FIG. 1 is a schematic view of an embodiment of a solid block heat exchanger embodying the invention; -
FIG. 2 is a schematic view of part of the heat exchanger illustrating the gaps between the tubes in the beverage lines; -
FIG. 3 is a schematic view of part of the heat exchanger illustrating the gaps between the tubes in the coolant lines; -
FIG. 4 is a schematic view illustrating the concepts of the inner cold zone and the designated zone; -
FIG. 5 is a schematic view illustrating a variant of the heat exchanger ofFIGS. 1 to 4 in which there are two parallel beverage lines; -
FIG. 6 is a schematic view illustrating a yet further embodiment of a heat exchanger in which there are two coolant lines in series; -
FIG. 7 is a schematic view of a variant of the solid block heat exchanger ofFIGS. 1 to 4 in which the locations of the cold zone and cooling zones are reversed. -
FIG. 8 is a schematic view illustrating a variant of the heat exchanger ofFIGS. 1 to 4 in which there is and additional cooling zone; and -
FIG. 9 is a schematic view of part of the heat exchanger ofFIG. 8 . - Referring to the drawings
FIG. 1 shows a solidblock heat exchanger 10 comprising a first coolant line or tube (typically formed from stainless steel) in the form of a “helical”coil arrangement 11 having a plurality of turns/coils. As shown the coils are generally rectangular in plan view having semi-circular curved ends separated by straight lengths of tubing. However other coil shapes could be used. - This coil arrangement locates generally within an
cold zone 12 of theheat exchanger 10 within a rectangular box shaped volume also shown inFIG. 4 . In this embodiment, thecoil 11 is an inner coil as, extending around the outside of thecoil arrangement 11 is a second “helical” coil arrangement 13 (also typically formed from stainless steel tubes) which in use carries beverage, typically beer, or other carbonated alcoholic drink of a similar alcohol content to beer. - As shown, the coils are generally rectangular in plan view having semi-circular curved ends separated by straight lengths of tubing. Again, other coil shapes could be used.
- This “outer” coil arrangement locates in a zone 14 (the designated cooling zone) outside of the
cold zone 12 of the heat exchanger and between thatcold zone 12 and the exterior of the heat exchanger. - The
heat exchanger 10 is formed by locating thecoils solid block 15. Such casting techniques are well known for forming solid block heat exchangers and accordingly will not be described in detail herein. When cast, the open ends of thecoils form coolant inlets 11 a and coolant outlets 11 b, andbeverage inlets 13 a andbeverage outlets 13 b, respectively. - The ratio of the volume of the two
zones beverage cooling zone 14 to thecold zone 12 is about 150:100. - In use, the
cold zone 12 or core acts as a thermal storage of energy. This thermal storage is used to maintain controlled beverage outlet temperatures to avoid the fluctuations that are typical with the heat exchangers described in the prior art. - The distance between the coils of the coolant coil arrangement may be varied to control the rate of heat transfer from the coolant into the solid core. With reference to
FIG. 3 , in the preferred embodiment the distance “b” between the exteriors of the tubes is between 3 and 10 mm. - The diameter of the tubes used in the coolant coil for transfer of cold from the coolant to the cold zone is selected based on the energy requirement of the system. Typically, the diameter range would range between 6 and 13 mm.
- With reference to
FIG. 2 , the distance “a” between the tubes in thebeverage coil arrangement 13 is varied to control the rate of heat transfer from the beverage into the definedcold zone 12. Typically the distance between the tubes is from 3 to 8 mm. - The diameter of the tubes used in the designated cooling zone for transfer of cold from the solid to the beverage is also selected based on the energy requirement of the system. Typically the diameter range for the beverage line tubes would be between 7 and 11 mm.
- The distance between the coolant tubes located in the cold zone and the beverage tubes located in the designated zone is a significant factor in determining the heat flow between the two defined solid areas. With reference to
FIG. 3 , the preferred distance “c” is between 2 and 6 mm. - This allows for predetermined heat transfer effects within the solid to facilitate the heat transfer from the
cold zone 12 to the coolant and also from the beverage into the solid. - The relationship between the plane of the beverage tube coils and the coolant tube coils (“the angle between the tubes”) is important in maximising the heat transfer rate across the solid.
- Adjusting the angle controls the heat transfer rate across the solid. As shown in the described embodiment the angle between the plane of the coils in the coolant coil and the beverage coil is 90°. It is preferred that the angle is between 80 and 110 degrees, however the angle may be anywhere between 15 and 120 degrees.
- The angle provides three dimensional heat flux within the solid areas and acts as a means of inducing turbulence to the heat flow through the solid areas and maximising the available transfer of cold through the system.
- Although the foregoing describes the beverage being dispensed as being alcoholic, it will be appreciated that the system may also be used to dispense other beverages, particularly soft drinks, such as sodas and the like.
- Although the above describes a heat exchanger having a single beverage line, and single coolant line, it will be appreciated that more than one beverage line may be provided in the designated
cooling zone 14 and more than one coolant line in thecold zone 12. - For example,
FIG. 5 shows avariant 110 of the heat exchanger ofFIGS. 1 to 4 in which there is asecond beverage line 113 running parallel to thefirst beverage line 13. -
FIG. 6 shows a further variant 210 in which there are two coolant lines “in series” defining the (inner)cold zone 12. Afirst coolant line 213 comprises a helical coil and a coolant inlet 213 a and a coolant outlet 213 b and defines one part 12 a of theinner cold zone 12. Asecond coolant line 223 following on in series from the first coolant line, comprises a helical coil and acoolant inlet 223 a and a coolant outlet 223 b and defines the other part 12 b of theinner cold zone 12. Thecoolant inlet 223 a is on the opposite side of the block 210 to the coolant outlet 213 b of the first coolant line. - Although in the preferred embodiment, as described above, the
cold zone 12 is inside the designatedbeverage cooling zone 14 which has the beverage lines passing through it, it is possible to manufacture a heat exchanger in which the location of the coolant tube coils 311 andbeverage line 313 coils are reversed, so that thecold zone 312 lies outside the beverage coils 313. In this embodiment, the ratio of the volume of thecold zone 312 to thebeverage line zone 314 remains 100:150, and the coolant and beverage pipe dimensions and spacings remain in the ranges described above as does the relationship between the plane of the beverage tube coils and the coolant tube coils. In a typical embodiment the angle is 90° as shown inFIG. 7 , although this angle can be varied between 80 and 110 degrees, even between 15 and 120 degrees. - It is also possible for additional lines to be present in the centre of the cold core block forming a third or central zone. This is illustrated in
FIGS. 8 and 9 , where the central zone is referenced 20 and shown as rectangular parallelepiped in broken lines. With reference toFIG. 6 also, the central zone is used for cooling as is the outer designated zone. It may have one or more lines 22 passing through it—seeFIG. 6 . In one embodiment the line 22 may be a glycol line for cooling glycol, used to cool a beer transfer conduit, and/or beer font or the like. In an alternative application there may be up to twenty additional lines 22 for pre-chilling e.g. soda or soft drinks. - As shown in
FIGS. 8 and 9 , where the central zone is present and used for cooling, the volume ratio of thecentral zone 20 to theinner cold zone 12 to theouter zone 14 is typically about 150:100:150. - It will be appreciated by persons skilled in the art that numerous variations and/or modifications may be made to the invention as shown in the specific embodiments without departing from the scope of the invention as broadly described. The present embodiments are, therefore, to be considered in all respects as illustrative and not restrictive.
Claims (19)
1. A heat exchanger comprising a coolant line and a beverage line embedded in a solid block of a material having a high thermal conductivity with the coolant line in the form of a first coil defining a plurality of turns, and the beverage line in the form of a second coil defining a plurality of turns and extending around the first coil.
2. A heat exchanger as claimed in claim 1 wherein the coolant line defines a cold zone in the centre of the block, with the volume outside the zone carrying the beverage line defining a designated beverage cooling zone.
3. A heat exchanger comprising a coolant line and a beverage line embedded in a solid block of a material having a high thermal conductivity with the beverage line in the form of a first coil having a plurality of turns being located in the centre of the block and defining a designated beverage cooling zone and the coolant line in the form of a second coil defining a plurality of turns and extending around the first coil and defining a cold zone.
4. A heat exchanger as claimed in claim 1 wherein the volume ratio of the designated zone to the cold zone is about 150:100.
5. A heat exchanger as claimed in claim 1 wherein the coils are in the form of helical coils.
6. A heat exchanger as claimed in claim 5 wherein the coolant line comprises tubes arranged in a helical pattern and wherein the distance between adjacent turns in the coolant line is between 3 and 10 mm.
7. A heat exchanger as claimed in claim 1 wherein the coolant line comprises tubes having a diameter between 6 to 13 mm.
8. A heat exchanger as claimed in claim 1 wherein tubes forming the beverage line are arranged in a helical pattern and wherein the distance between adjacent tubes in the beverage line is from 3 to 8 mm.
9. A heat exchanger as claimed in claim 8 wherein the diameter of the tubes used in the beverage line is from 7 to 11 mm.
10. A heat exchanger as claimed in claim 8 wherein the distance between the coolant tubes located in the cold zone and the beverage tubes located in the designated zone is from 2 to 6 mm.
11. A heat exchanger as claimed in claim 1 wherein the angle between a plane defined by the beverage tube coils and a plane defined by coolant tube coils is between 80 and 110 degrees.
12. A heat exchanger as claimed in claim 1 wherein the coolant line carries a Freon refrigerant.
13. A heat exchanger as claimed in claim 2 wherein there are a plurality of beverage lines in the designated zone.
14. A heat exchanger as claimed in claim 2 wherein there are a plurality of coolant lines in the cold zone.
15. A heat exchanger as claimed in claim 1 when dependent on claims 1 or 2 , wherein one or more additional lines pass through the first coil.
16. A heat exchanger as claimed in claim 15 wherein the additional lines include one or more lines for cooling a secondary cooling media.
17. A heat exchanger as claimed in claim 15 wherein the additional lines include one or more lines for cooling soft drinks, soda or the like.
18. A heat exchanger as claimed in claim 15 wherein the additional lines are generally located in a central zone inside the cold zone.
19. A heat exchanger as claimed in claim 18 wherein the volume ratio of the central zone to the cold zone to the designated zone is about 150:100:150.
Applications Claiming Priority (3)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
AU2008900054 | 2008-01-04 | ||
AU2008900054A AU2008900054A0 (en) | 2008-01-04 | Improvements in heat exchangers for dispensing sub-zero beer | |
PCT/AU2009/000002 WO2009086589A1 (en) | 2008-01-04 | 2009-01-02 | Improvements in heat exchangers for dispensing sub-zero beer |
Publications (1)
Publication Number | Publication Date |
---|---|
US20110011569A1 true US20110011569A1 (en) | 2011-01-20 |
Family
ID=40852698
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
US12/811,572 Abandoned US20110011569A1 (en) | 2008-01-04 | 2009-01-02 | Heat exchanges for dispensing sub-zero beer |
Country Status (6)
Country | Link |
---|---|
US (1) | US20110011569A1 (en) |
EP (1) | EP2238399A4 (en) |
AU (1) | AU2009203886B2 (en) |
CA (1) | CA2711492A1 (en) |
NZ (1) | NZ586788A (en) |
WO (1) | WO2009086589A1 (en) |
Cited By (7)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US20100276443A1 (en) * | 2007-07-09 | 2010-11-04 | Benjamin Paul Baker | System and method for dispensing iced beverages |
US20150053373A1 (en) * | 2013-08-23 | 2015-02-26 | Savannah River Nuclear Solutions, Llc | Thermal cycling device |
US20170097194A1 (en) * | 2014-06-30 | 2017-04-06 | Modine Manufacturing Company | Heat Exchanger and Method of Making the Same |
US9771252B2 (en) * | 2013-10-15 | 2017-09-26 | Streamline Beverage Pty Ltd | Beverage dispenser |
US10094284B2 (en) | 2014-08-22 | 2018-10-09 | Mohawk Innovative Technology, Inc. | High effectiveness low pressure drop heat exchanger |
US10267557B2 (en) * | 2017-04-13 | 2019-04-23 | Keith Taboada | Cooler cold tap adapter |
US20220049904A1 (en) * | 2020-08-13 | 2022-02-17 | General Electric Company | Heat exchanger having curved fluid passages for a gas turbine engine |
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ITMI20062160A1 (en) * | 2006-11-10 | 2008-05-11 | Vin Service Srl | DRINK REFRIGERATION UNIT |
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- 2009-01-02 EP EP09701140A patent/EP2238399A4/en not_active Withdrawn
- 2009-01-02 CA CA2711492A patent/CA2711492A1/en not_active Abandoned
- 2009-01-02 NZ NZ586788A patent/NZ586788A/en not_active IP Right Cessation
- 2009-01-02 US US12/811,572 patent/US20110011569A1/en not_active Abandoned
- 2009-01-02 AU AU2009203886A patent/AU2009203886B2/en not_active Ceased
- 2009-01-02 WO PCT/AU2009/000002 patent/WO2009086589A1/en active Application Filing
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US3011323A (en) * | 1957-10-23 | 1961-12-05 | Carbonic Dispenser Inc | Ice plate |
US4617807A (en) * | 1985-07-08 | 1986-10-21 | Booth, Inc. | Involute coil cold plate |
US4888961A (en) * | 1988-07-11 | 1989-12-26 | Lancer Corporation | Cold plate apparatus |
US20030066306A1 (en) * | 2001-09-06 | 2003-04-10 | Renken Richard K. | Low volume beverage dispenser |
US20070245766A1 (en) * | 2006-04-05 | 2007-10-25 | Younkle Matthew C | In-line beverage chilling apparatus |
US20080250810A1 (en) * | 2007-04-12 | 2008-10-16 | Yen Sun Technology Corp. | Cooling module applied for liquid containers |
Cited By (13)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US8464903B2 (en) | 2007-07-09 | 2013-06-18 | Tempak International Pty Ltd | Method for dispensing iced beverages |
US20100276443A1 (en) * | 2007-07-09 | 2010-11-04 | Benjamin Paul Baker | System and method for dispensing iced beverages |
US20150053373A1 (en) * | 2013-08-23 | 2015-02-26 | Savannah River Nuclear Solutions, Llc | Thermal cycling device |
US10436516B2 (en) * | 2013-08-23 | 2019-10-08 | Savannah River Nuclear Solutions, Llc | Thermal cycling device |
US9771252B2 (en) * | 2013-10-15 | 2017-09-26 | Streamline Beverage Pty Ltd | Beverage dispenser |
US10060680B2 (en) | 2014-06-30 | 2018-08-28 | Modine Manufacturing Company | Heat exchanger and method of making the same |
CN106574827A (en) * | 2014-06-30 | 2017-04-19 | 摩丁制造公司 | Heat exchanger and method of making the same |
US10317143B2 (en) * | 2014-06-30 | 2019-06-11 | Modine Manufacturing Company | Heat exchanger and method of making the same |
US20170097194A1 (en) * | 2014-06-30 | 2017-04-06 | Modine Manufacturing Company | Heat Exchanger and Method of Making the Same |
US10094284B2 (en) | 2014-08-22 | 2018-10-09 | Mohawk Innovative Technology, Inc. | High effectiveness low pressure drop heat exchanger |
US10267557B2 (en) * | 2017-04-13 | 2019-04-23 | Keith Taboada | Cooler cold tap adapter |
US20220049904A1 (en) * | 2020-08-13 | 2022-02-17 | General Electric Company | Heat exchanger having curved fluid passages for a gas turbine engine |
US11662150B2 (en) * | 2020-08-13 | 2023-05-30 | General Electric Company | Heat exchanger having curved fluid passages for a gas turbine engine |
Also Published As
Publication number | Publication date |
---|---|
EP2238399A1 (en) | 2010-10-13 |
WO2009086589A1 (en) | 2009-07-16 |
AU2009203886A1 (en) | 2009-07-16 |
CA2711492A1 (en) | 2009-07-16 |
NZ586788A (en) | 2012-09-28 |
AU2009203886B2 (en) | 2014-01-30 |
EP2238399A4 (en) | 2010-12-22 |
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Legal Events
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AS | Assignment |
Owner name: TEMPAK INTERNATIONAL PTY LTD, AUSTRALIA Free format text: ASSIGNMENT OF ASSIGNORS INTEREST;ASSIGNOR:BAKER, BENJAMIN PAUL;REEL/FRAME:024960/0284 Effective date: 20100901 |
|
STCB | Information on status: application discontinuation |
Free format text: ABANDONED -- FAILURE TO RESPOND TO AN OFFICE ACTION |