WO2019175576A1 - Chilling manifold - Google Patents

Chilling manifold Download PDF

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Publication number
WO2019175576A1
WO2019175576A1 PCT/GB2019/050698 GB2019050698W WO2019175576A1 WO 2019175576 A1 WO2019175576 A1 WO 2019175576A1 GB 2019050698 W GB2019050698 W GB 2019050698W WO 2019175576 A1 WO2019175576 A1 WO 2019175576A1
Authority
WO
WIPO (PCT)
Prior art keywords
coolant
arrangement
return
entry
ports
Prior art date
Application number
PCT/GB2019/050698
Other languages
French (fr)
Original Assignee
Ispresso Limited
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Ispresso Limited filed Critical Ispresso Limited
Publication of WO2019175576A1 publication Critical patent/WO2019175576A1/en

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
    • F28F9/02—Header boxes; End plates
    • F28F9/0246—Arrangements for connecting header boxes with flow lines
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
    • F28F9/02—Header boxes; End plates
    • F28F9/0246—Arrangements for connecting header boxes with flow lines
    • F28F9/0251—Massive connectors, e.g. blocks; Plate-like connectors
    • F28F9/0253—Massive connectors, e.g. blocks; Plate-like connectors with multiple channels, e.g. with combined inflow and outflow channels
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25D—REFRIGERATORS; COLD ROOMS; ICE-BOXES; COOLING OR FREEZING APPARATUS NOT OTHERWISE PROVIDED FOR
    • F25D17/00—Arrangements for circulating cooling fluids; Arrangements for circulating gas, e.g. air, within refrigerated spaces
    • F25D17/02—Arrangements for circulating cooling fluids; Arrangements for circulating gas, e.g. air, within refrigerated spaces for circulating liquids, e.g. brine
    • 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
    • F28D1/00—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators
    • F28D1/02—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid
    • F28D1/04—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits
    • F28D1/0408—Multi-circuit heat exchangers, e.g. integrating different heat exchange sections in the same unit or heat exchangers for more than two fluids
    • 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
    • F28D1/00—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators
    • F28D1/02—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid
    • F28D1/04—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits
    • F28D1/0408—Multi-circuit heat exchangers, e.g. integrating different heat exchange sections in the same unit or heat exchangers for more than two fluids
    • F28D1/0417—Multi-circuit heat exchangers, e.g. integrating different heat exchange sections in the same unit or heat exchangers for more than two fluids with particular circuits for the same heat exchange medium, e.g. with the heat exchange medium flowing through sections having different heat exchange capacities or for heating/cooling the heat exchange medium at different temperatures
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
    • F28F9/02—Header boxes; End plates
    • F28F9/026—Header boxes; End plates with static flow control means, e.g. with means for uniformly distributing heat exchange media into conduits
    • F28F9/027—Header boxes; End plates with static flow control means, e.g. with means for uniformly distributing heat exchange media into conduits in the form of distribution pipes
    • F28F9/0275—Header boxes; End plates with static flow control means, e.g. with means for uniformly distributing heat exchange media into conduits in the form of distribution pipes with multiple branch pipes
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
    • F28F9/02—Header boxes; End plates
    • F28F2009/0285—Other particular headers or end plates
    • F28F2009/0295—Other particular headers or end plates comprising cooling circuits

Definitions

  • the present invention relates to chilling manifolds and more particularly but not exclusively to a chilled distribution manifold to allow optimised thermal transfer.
  • Figure 1 shows the main entry and return of the coolant to and from the heat exchangers
  • Figure 2 shows the main entry and then equal distribution of the coolant
  • FIG. 3 shows the return from the heat exchangers and the main return out.
  • the present invention improves upon the prior approach with sequential distribution by equally distributing coolant simultaneously to all the heat exchangers in a system so all of the heat exchangers are working with equal efficiency continuously.
  • a manifold in accordance with aspects of the present invention achieves more equal distribution by employing a distribution block that allows equal coolant distribution simultaneously.
  • aspects of the present invention have a manifold block that distributes coolant from a pump so that the coolant flow is evenly and simultaneously flows to each of the heat exchangers.
  • a block has a main coolant entry point (1) which is then distributed to the heat exchangers through points (3) (4)(5) and (6). After having flowed through the heat exchangers the coolant then returns through points (7) (8) (9) and (10) and finally links up to the outlet (2).
  • coolant needs to be distributed simultaneously in an equal manner to allow the maximum thermal transfer to occur. It will be understood that most situations for heat exchange will provide greatest emphasis on the construction of the heat exchanger assemblies themselves in terms of best utilising the coolant flow available.
  • aspects of the present invention provide a robust manifold 100 sufficient to accept the relatively massive flow pressure for each heat exchanger.
  • the flow pressure will be relatively high but not huge whilst sufficient to ameliorate any marginal or slight differences in the flow drag of each individual heat exchanger whereby as illustrated a single or main coolant flow entry 1 feeds four coolant exits 3, 4, 5, 6 to respective heat exchangers.
  • each flow path between each heat exchanger is substantially the same or using suitable means adjusted to be substantially the same.
  • the simplest way of achieving this is as illustrated in the figures so the cross-sectional area of the coolant flow exit ports 3, 4, 5, 6 are substantially the same with a similar (perpendicular as depicted) angular aspect to each other whilst the coolant flow return ports 7, 8, 9, 10 are also matched in terms of cross-sectional area to flow and angular aspect to the main coolant return 2.
  • the cross-sectional area of the main coolant entry 1 and main coolant return is less important as each will be the same for all ports 3, 4, 5, 6 and ports 7, 8, 9, 10 respectively.
  • the entry 1 and return 2 need to be sufficient so that there can be adequate flow into the manifold 100 and so to the heat exchangers without choking and throttling which will both inhibit operation of the heat exchangers and/or the relatively high flow pressure rendering any minor differences in coolant flow resistance into each respective heat exchanger set as trivial.
  • the flow rate is fixed by the pump at around 6 litres per minute,
  • the flow rate and/or any pulsed flow rate is relative to a desired level of heat extraction by the coolant in the respective heat exchangers which will depend upon particular desired or necessary performance.
  • a large coolant flow pressure overcomes any differences in flow drag, presented by different heat exchange flow paths.
  • aspects of the present invention are not normally related to a truly pressurised system.
  • the system is sealed though not truly pressurised however a pressurised system may be provided with appropriate adaptation and care taken with regard potential dangers with a pressurised system.
  • the manifold can have grooves to create coolant flow swirl for increasing the surface area and so allowing the coolant to absorb more heat.
  • the coolant may get near the ice threshold but normally it never gets below ambient room temperature and in operation is between ambient and 36 degrees C. Coolant pressures will be determined as required but the size of the heat exchanger is typically linked directly to the dimensions of the Peltier cooling device so roughly 50mm x 50 mm with an area for inlet and for outlet so the cooling chamber is 50mm by 88 mm for an example arrangement in accordance with aspects of the present invention.

Abstract

The present invention relates to a manifold for chilling whereby the coolant is distributed in an equal way to the cooling heat exchangers simultaneously rather than in a sequential way.

Description

Chilling Manifold
The present invention relates to chilling manifolds and more particularly but not exclusively to a chilled distribution manifold to allow optimised thermal transfer.
It is an objective to improve the efficiency of a cooling systems so that they optimise thermal transfer by even and simultaneous coolant distribution to matched heat exchangers.
Currently coolant distribution is in a sequential manner so that each heat exchanger is connected in series allowing flow from one to another. This prior approach is not efficient and the coolant temperature increase as it progresses around the system The last heat exchanger in the system subsequently receives water that has already had thermal exchange and so is less efficient at cooling the system.
Aspects of the present invention relate to a chilling manifold as defined in claim 1. Other features and aspects of the present invention are outlined in the dependent claims to claim 1 below.
An embodiment of aspects of the present invention is described by way of example with reference to the accompanying drawings in which: -
Figure 1 shows the main entry and return of the coolant to and from the heat exchangers;
Figure 2 shows the main entry and then equal distribution of the coolant; and,
Figure 3 shows the return from the heat exchangers and the main return out.
The present invention improves upon the prior approach with sequential distribution by equally distributing coolant simultaneously to all the heat exchangers in a system so all of the heat exchangers are working with equal efficiency continuously. A manifold in accordance with aspects of the present invention achieves more equal distribution by employing a distribution block that allows equal coolant distribution simultaneously. Aspects of the present invention have a manifold block that distributes coolant from a pump so that the coolant flow is evenly and simultaneously flows to each of the heat exchangers.
In accordance with aspects of the present invention a block has a main coolant entry point (1) which is then distributed to the heat exchangers through points (3) (4)(5) and (6). After having flowed through the heat exchangers the coolant then returns through points (7) (8) (9) and (10) and finally links up to the outlet (2). To cool the heat exchanger efficiently, coolant needs to be distributed simultaneously in an equal manner to allow the maximum thermal transfer to occur. It will be understood that most situations for heat exchange will provide greatest emphasis on the construction of the heat exchanger assemblies themselves in terms of best utilising the coolant flow available. However, in some situations which are relatively small and contained, such as a chilling arrangement for a confection, a number of heat exchangers will be provided to give a cooling or chilling effect all around and consistently about a carton or bowl of confection during making. In such circumstances each heat exchanger will be substantially matched to give even cooling and chilling effects. In such circumstances within tolerance limits the flow drag resistance upon each heat exchanger will be substantially the same. Furthermore, the flow pressure due to pumping action can and is relatively massive compared to the flow resistance of each and the combined coolant flows into, through and out of the heat exchangers.
Aspects of the present invention provide a robust manifold 100 sufficient to accept the relatively massive flow pressure for each heat exchanger. The flow pressure will be relatively high but not huge whilst sufficient to ameliorate any marginal or slight differences in the flow drag of each individual heat exchanger whereby as illustrated a single or main coolant flow entry 1 feeds four coolant exits 3, 4, 5, 6 to respective heat exchangers. As the flow pressure is high there will normally be a high coolant flow rate thorough the respective heat exchangers - the marginal difference in flow rate between each heat exchange then manifests as relatively trivial differences in terms of actual heat exchange as seen in the chilling or cooling effect to a confection or the like as made.
As will be appreciated the coolant flow out of the respective heat exchangers must be similarly matched so the coolant return outlets 7, 8, 9, 10 for the manifold will be substantially the same so that the coolant flow is again matched between these heat exchangers. For matching purposes, it will be appreciated that each flow path between each heat exchanger is substantially the same or using suitable means adjusted to be substantially the same. The simplest way of achieving this is as illustrated in the figures so the cross-sectional area of the coolant flow exit ports 3, 4, 5, 6 are substantially the same with a similar (perpendicular as depicted) angular aspect to each other whilst the coolant flow return ports 7, 8, 9, 10 are also matched in terms of cross-sectional area to flow and angular aspect to the main coolant return 2. The cross-sectional area of the main coolant entry 1 and main coolant return is less important as each will be the same for all ports 3, 4, 5, 6 and ports 7, 8, 9, 10 respectively. However, the entry 1 and return 2 need to be sufficient so that there can be adequate flow into the manifold 100 and so to the heat exchangers without choking and throttling which will both inhibit operation of the heat exchangers and/or the relatively high flow pressure rendering any minor differences in coolant flow resistance into each respective heat exchanger set as trivial.
In accordance with aspects of the present invention the flow rate is fixed by the pump at around 6 litres per minute, However the flow rate and/or any pulsed flow rate is relative to a desired level of heat extraction by the coolant in the respective heat exchangers which will depend upon particular desired or necessary performance.
A large coolant flow pressure overcomes any differences in flow drag, presented by different heat exchange flow paths. However, aspects of the present invention are not normally related to a truly pressurised system. Typically, the system is sealed though not truly pressurised however a pressurised system may be provided with appropriate adaptation and care taken with regard potential dangers with a pressurised system.
In accordance with aspects of the present invention the manifold can have grooves to create coolant flow swirl for increasing the surface area and so allowing the coolant to absorb more heat.
Typically, it will be understood that the coolant may get near the ice threshold but normally it never gets below ambient room temperature and in operation is between ambient and 36 degrees C. Coolant pressures will be determined as required but the size of the heat exchanger is typically linked directly to the dimensions of the Peltier cooling device so roughly 50mm x 50 mm with an area for inlet and for outlet so the cooling chamber is 50mm by 88 mm for an example arrangement in accordance with aspects of the present invention.
Reference annotations (1) main coolant entry
(2) main coolant return
(3) coolant exit to heat exchanger (4) coolant exit to heat exchanger
(5) coolant exit to heat exchanger
(6) coolant exit to heat exchanger
(7) coolant return from heat exchanger
(8) coolant return from heat exchanger (9) coolant return from heat exchanger
(10) coolant return from heat exchanger

Claims

Claims
1. A manifold arrangement for chilling confections, the manifold arrangement having a coolant entry to a plurality of coolant exit ports for respective substantially flow matched heat exchangers in terms of thermal transfer effect and a coolant return connected to a reciprocal plurality of coolant return ports from the heat exchangers, the cross-sectional area of each coolant exit port in the plurality of coolant exit ports along with angular attitude of the coolant exit ports to the coolant entry being substantially the same and the cross-sectional area of each coolant return port and the angular attitude of each coolant return ports to the coolant return are the same so allow the equal and simultaneous distribution of coolant to the heat exchangers.
2. An arrangement as claimed in claim 1 wherein the angular attitude of each coolant exit port and each coolant return port is perpendicular to the respective coolant entry and the coolant return.
3. An arrangement as claimed in claim 1 or claim 2 wherein the plurality of coolant exit ports is four.
4. An arrangement as claimed in any of claims 1 to 3 wherein the cross-sectional area of the coolant entry and the coolant return are substantially the same.
5. An arrangement as claimed in any preceding claim wherein the coolant entry is connected to a pump for coolant to force coolant flow through the coolant entry, the pump configured to provide a sufficient coolant pressure whereby any variations in coolant flow range for each coolant exit ports and associated heat exchanger is insignificant.
6. An arrangement as claimed in any preceding claim wherein the coolant entry, coolant exit ports, heat exchangers, coolant return ports and coolant return are in a closed circulation loop.
7. An arrangement as claimed in claim 5 and claim 6 in which the coolant pump is provided between the coolant entry and the coolant return.
8. An arrangement as claimed in any preceding claim wherein the arrangement is associated with a coolant block with each heat exchanger associated with a surface of the block.
9. An arrangement as claimed in any preceding claim wherein the arrangement is formed with a structural integrity sufficient that at a relatively high coolant flow pressure is provided to the coolant entry to minimise difference in drag within the heat exchangers.10. An arrangement as claimed in any preceding claim wherein the plurality of coolant return ports is four.
PCT/GB2019/050698 2018-03-13 2019-03-13 Chilling manifold WO2019175576A1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
GB1803971.9A GB2574573A (en) 2018-03-13 2018-03-13 Chilling manifold
GB1803971.9 2018-03-13

Publications (1)

Publication Number Publication Date
WO2019175576A1 true WO2019175576A1 (en) 2019-09-19

Family

ID=61972703

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/GB2019/050698 WO2019175576A1 (en) 2018-03-13 2019-03-13 Chilling manifold

Country Status (2)

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GB (1) GB2574573A (en)
WO (1) WO2019175576A1 (en)

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB1220654A (en) * 1968-07-23 1971-01-27 Daimler Benz Ag Heat-exchanger apparatus for motor-vehicle heating
WO2002061358A1 (en) * 2001-01-31 2002-08-08 Bennardo Marioli Multi-circuit heat exchanger
WO2016190445A1 (en) * 2015-05-27 2016-12-01 株式会社ティラド Heat exchanger tank structure and production method therefor

Family Cites Families (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP4023459B2 (en) * 2004-03-04 2007-12-19 株式会社デンソー Heat exchanger
JP4023458B2 (en) * 2004-03-04 2007-12-19 株式会社デンソー Heat exchanger
DE102005010261A1 (en) * 2005-03-07 2006-09-21 Robert Bosch Gmbh Making heat exchanger for confectionery masses, prepares laser-cut non-circular segments to form spiral guide with elongated holes carrying parallel tubes

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB1220654A (en) * 1968-07-23 1971-01-27 Daimler Benz Ag Heat-exchanger apparatus for motor-vehicle heating
WO2002061358A1 (en) * 2001-01-31 2002-08-08 Bennardo Marioli Multi-circuit heat exchanger
WO2016190445A1 (en) * 2015-05-27 2016-12-01 株式会社ティラド Heat exchanger tank structure and production method therefor

Also Published As

Publication number Publication date
GB2574573A (en) 2019-12-18
GB201803971D0 (en) 2018-04-25

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