WO2009086589A1 - Improvements in heat exchangers for dispensing sub-zero beer - Google Patents
Improvements in heat exchangers for dispensing sub-zero beer Download PDFInfo
- Publication number
- WO2009086589A1 WO2009086589A1 PCT/AU2009/000002 AU2009000002W WO2009086589A1 WO 2009086589 A1 WO2009086589 A1 WO 2009086589A1 AU 2009000002 W AU2009000002 W AU 2009000002W WO 2009086589 A1 WO2009086589 A1 WO 2009086589A1
- Authority
- WO
- WIPO (PCT)
- Prior art keywords
- heat exchanger
- beverage
- zone
- line
- coolant
- Prior art date
Links
Classifications
-
- 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. 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.
- 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 1 1 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.
- 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.
- Figure 1 is a schematic view of an embodiment of a solid block heat exchanger embodying the invention
- Figure 2 is a schematic view of part of the heat exchanger illustrating the gaps between the tubes in the beverage lines;
- Figure 3 is a schematic view of part of the heat exchanger illustrating the gaps between the tubes in the coolant lines;
- Figure 4 is a schematic view illustrating the concepts of the inner cold zone and the designated zone;
- Figure 5 is a schematic view illustrating a variant of the heat exchanger of Figures 1 to 4 in which there are two parallel beverage lines;
- Figure 6 is a schematic view illustrating a yet further embodiment of a heat exchanger in which there are two coolant lines in series;
- Figure 7 is a schematic view of a variant of the solid block heat exchanger of Figures 1 to 4 in which the locations of the cold zone and cooling zones are reversed.
- Figure 8 is a schematic view illustrating a variant of the heat exchanger of Figures 1 to 4 in which there is and additional cooling zone; and Figure 9 is a schematic view of part of the heat exchanger of Figure 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 Figure 4.
- the coil 11 is an inner coil as, extending around the outside of the coil arrangement 1 1 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 1 1 and 13 form coolant inlets 1 1a and coolant outlets l ib, and beverage inlets 13a and beverage outlets 13b, 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 0 C. In a preferred embodiment 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 1 1 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. 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 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 Figures 1 to 4 in which there is a second beverage line 1 13 running parallel to the first beverage line 13.
- Figure 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 213a and a coolant outlet 213b and defines one part 12a 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 223a and a coolant outlet 223b and defines the other part 12b of the inner cold zone 12.
- the coolant inlet 223a is on the opposite side of the block 210 to the coolant outlet 213b of the first coolant line.
- the cold zone 12 is inside the designated beverage cooling zone 14 which has the beverage lines passing though it, it is possible to manufacture a heat exchanger in which the location of the coolant tube coils 31 1 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 Figure 7, although this angle can be varied between 80 and 110 degrees, even between 15 and 120 degrees.
- FIG. 8 it is also possible for additional lines to be present in the centre of the cold core block forming a third or central zone.
- 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 Figure 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.
Landscapes
- Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Thermal Sciences (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Devices For Dispensing Beverages (AREA)
- Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
Abstract
Description
Claims
Priority Applications (5)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
NZ586788A NZ586788A (en) | 2008-01-04 | 2009-01-02 | Improvements in heat exchangers for dispensing sub-zero beer where the cooling and beverage lines are embedded in a soild block of material having high thermal conductivity |
CA2711492A CA2711492A1 (en) | 2008-01-04 | 2009-01-02 | Improvements in heat exchangers for dispensing sub-zero beer |
US12/811,572 US20110011569A1 (en) | 2008-01-04 | 2009-01-02 | Heat exchanges for dispensing sub-zero beer |
EP09701140A EP2238399A4 (en) | 2008-01-04 | 2009-01-02 | Improvements in heat exchangers for dispensing sub-zero beer |
AU2009203886A AU2009203886B2 (en) | 2008-01-04 | 2009-01-02 | Improvements in heat exchangers for dispensing sub-zero beer |
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
AU2008900054A AU2008900054A0 (en) | 2008-01-04 | Improvements in heat exchangers for dispensing sub-zero beer | |
AU2008900054 | 2008-01-04 |
Publications (1)
Publication Number | Publication Date |
---|---|
WO2009086589A1 true WO2009086589A1 (en) | 2009-07-16 |
Family
ID=40852698
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
PCT/AU2009/000002 WO2009086589A1 (en) | 2008-01-04 | 2009-01-02 | Improvements in heat exchangers 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) |
Families Citing this family (7)
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 |
US10436516B2 (en) * | 2013-08-23 | 2019-10-08 | Savannah River Nuclear Solutions, Llc | Thermal cycling device |
GB2519384B (en) * | 2013-10-15 | 2020-07-01 | Streamline Beverage Pty Ltd | A beverage dispenser |
CN106574827A (en) * | 2014-06-30 | 2017-04-19 | 摩丁制造公司 | 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 |
US11662150B2 (en) * | 2020-08-13 | 2023-05-30 | General Electric Company | Heat exchanger having curved fluid passages for a gas turbine engine |
Citations (6)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
GB649892A (en) * | 1947-11-10 | 1951-02-07 | Spacarb Inc | Improvements in or relating to a device for refrigerating components of mixed drinks |
GB703662A (en) * | 1950-07-20 | 1954-02-10 | Heat X Changer Co Inc | Improvements in or relating to an electric heater for fluids |
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 |
US20070245766A1 (en) * | 2006-04-05 | 2007-10-25 | Younkle Matthew C | In-line beverage chilling apparatus |
WO2008056232A2 (en) * | 2006-11-10 | 2008-05-15 | Vin Service S.R.L. | Cooling unit for beverages |
Family Cites Families (5)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US3011323A (en) * | 1957-10-23 | 1961-12-05 | Carbonic Dispenser Inc | Ice plate |
DE7736972U1 (en) * | 1977-12-03 | 1978-03-16 | Kuehltex Kuehl- Und Ausschankgeraete Gmbh, 5657 Haan | HEAT EXCHANGER FOR A BEVERAGE COOLER |
US4781310A (en) * | 1986-12-19 | 1988-11-01 | The Coca-Cola Company | Beverage dispenser |
WO2003022728A2 (en) * | 2001-09-06 | 2003-03-20 | Manitowoc Foodservice Companies, Inc. | Low volume beverage dispenser |
JP3135012U (en) * | 2007-04-12 | 2007-08-30 | 元山科技工業股▲分▼有限公司 | Beverage feeder cooling module |
-
2009
- 2009-01-02 US US12/811,572 patent/US20110011569A1/en not_active Abandoned
- 2009-01-02 NZ NZ586788A patent/NZ586788A/en not_active IP Right Cessation
- 2009-01-02 AU AU2009203886A patent/AU2009203886B2/en not_active Ceased
- 2009-01-02 EP EP09701140A patent/EP2238399A4/en not_active Withdrawn
- 2009-01-02 WO PCT/AU2009/000002 patent/WO2009086589A1/en active Application Filing
- 2009-01-02 CA CA2711492A patent/CA2711492A1/en not_active Abandoned
Patent Citations (6)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
GB649892A (en) * | 1947-11-10 | 1951-02-07 | Spacarb Inc | Improvements in or relating to a device for refrigerating components of mixed drinks |
GB703662A (en) * | 1950-07-20 | 1954-02-10 | Heat X Changer Co Inc | Improvements in or relating to an electric heater for fluids |
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 |
US20070245766A1 (en) * | 2006-04-05 | 2007-10-25 | Younkle Matthew C | In-line beverage chilling apparatus |
WO2008056232A2 (en) * | 2006-11-10 | 2008-05-15 | Vin Service S.R.L. | Cooling unit for beverages |
Non-Patent Citations (1)
Title |
---|
See also references of EP2238399A4 * |
Also Published As
Publication number | Publication date |
---|---|
AU2009203886B2 (en) | 2014-01-30 |
EP2238399A1 (en) | 2010-10-13 |
AU2009203886A1 (en) | 2009-07-16 |
NZ586788A (en) | 2012-09-28 |
EP2238399A4 (en) | 2010-12-22 |
US20110011569A1 (en) | 2011-01-20 |
CA2711492A1 (en) | 2009-07-16 |
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