WO2006064313A1 - Protection d'evaporateur - Google Patents

Protection d'evaporateur Download PDF

Info

Publication number
WO2006064313A1
WO2006064313A1 PCT/IB2005/001466 IB2005001466W WO2006064313A1 WO 2006064313 A1 WO2006064313 A1 WO 2006064313A1 IB 2005001466 W IB2005001466 W IB 2005001466W WO 2006064313 A1 WO2006064313 A1 WO 2006064313A1
Authority
WO
WIPO (PCT)
Prior art keywords
tube
heat exchange
exchange device
compressible means
tubes
Prior art date
Application number
PCT/IB2005/001466
Other languages
English (en)
Inventor
Michel Grabon
Michel El Baz
Original Assignee
Carrier Corporation
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 Carrier Corporation filed Critical Carrier Corporation
Priority to BRPI0519048-7A priority Critical patent/BRPI0519048A2/pt
Priority to EP05742007A priority patent/EP1825205A1/fr
Priority to US11/720,547 priority patent/US20080202727A1/en
Publication of WO2006064313A1 publication Critical patent/WO2006064313A1/fr
Priority to HK08105677.1A priority patent/HK1116243A1/xx

Links

Classifications

    • 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
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B39/00—Evaporators; Condensers
    • F25B39/02—Evaporators
    • 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
    • F28D7/16—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 being arranged in parallel spaced relation
    • 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
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2500/00—Problems to be solved
    • F25B2500/06—Damage
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F2265/00—Safety or protection arrangements; Arrangements for preventing malfunction
    • F28F2265/14—Safety or protection arrangements; Arrangements for preventing malfunction for preventing damage by freezing, e.g. for accommodating volume expansion

Definitions

  • the present invention relates to a protector for protecting components of an evaporator from damage due to freezing and in particular for protecting tubes in an evaporator from damage caused by water freezing to form ice.
  • Prior art cooling and/or heating systems may operate in situations where the ambient temperature is below the freezing point of the cooled medium in the system. In such a situation, if the cooled medium is water and if the ambient temperature is below the freezing point of water
  • the refrigerant which just prior to the chiller stopping is located in the evaporator, is subject to a drastic reduction in pressure and therefore the refrigerant will boil at a temperature level corresponding with the ambient air temperature whilst migrating to the coldest chiller system point, i.e. the condenser.
  • the condenser i.e. the condenser.
  • a significant amount of cooling is provided to the water in the evaporator and, particularly if that water is not circulating (for example if the power shortage or safety cut-out stops the entire chiller and/or the water pumps etc.), it will rapidly freeze, forming ice.
  • evaporator used in chillers; direct expansion evaporators in which refrigerant evaporates inside a plurality of tubes and water circulates around the outside of the tubes, and flooded evaporators in which water circulates inside the tubes and refrigerant surrounds the tubes and boils outside them.
  • one common solution is to provide dedicated heaters, such as electrical heaters, which deliver heat to the evaporator, particularly when the chiller or the evaporator is not operating.
  • the heaters increase the evaporator temperature and thus increase the temperature of the water (or whatever coolant is employed) in the evaporator to a temperature above its freezing point.
  • Another known solution to the above problem is to prevent refrigerant migrating from the evaporator to the condenser when the unit is not operating. This can be achieved by providing dedicated valves in the connection between the evaporator and the condenser.
  • a heat exchange device comprising a plurality of tubes for carrying a first medium and compressible means inserted into at least one of the tubes, wherein expansion of said medium causes said compressible means to compress.
  • compressible means in a heat exchange device such as an evaporator for a chiller, which compensates for the change in volume that occurs when a such as water expands during normal operation of the heat exchange device or when the device partly or wholly ceases to operate.
  • a chiller having an evaporator in which tubes carrying water are immersed in a bath of refrigerant As discussed above, when the ambient temperature of the chiller is around freezing point (0° C) or lower, the water in the tubes can freeze, which causes stresses in the tubes and which may then spilt or crack.
  • the compressible material compresses in response to expansion of the medium as it freezes and thus the stresses occurring in the tubes due to expansion of the medium are minimised or eliminated. Therefore it is unnecessary to provide any costly and/or complicated additional mechanisms in the heat exchange device of the present invention to prevent freezing of the medium or to prevent migration of refrigerant in the heat exchange device, since the present invention as claimed overcomes the problems that these mechanisms seek to solve.
  • the compressible means comprises inert resilient material.
  • the means comprises closed cell foam, for example rubber.
  • the compressible means may be capable of compressing by substantially the same volume as the increase in volume that occurs as water freezes.
  • the compressible means may be capable of compressing either by less than or by more than the same volume as the increase in volume that occurs as water freezes.
  • the compressible means compresses less than the volume increase caused by the water freezing, then it must be capable of being compressed by at least a sufficient volume such that the tubes are not damaged by expansion of the medium (i.e. the tubes may be capable of absorbing a degree of stress without being damaged).
  • the compressible means since typically frozen water has a volume of about 10% greater than unfrozen water, it is desirable that the compressible means is capable of at least 10% compression under such conditions as would be encountered in the tubes i.e. by at least 10% under a pressure less than or equal to the pressure generated by water freezing when confined in a tube.
  • the compressible means may reside in only a part or parts of the tubes.
  • the compressible means may comprise a single means at a single location in the tube or a plurality of means regularly or irregularly spaced along the length of the tube.
  • the compressible means is substantially the same length as the length of the tube. This arrangement is advantageous because the compressible means can absorb pressure along the entire length of the tube and the pressure will be applied evenly across the length of the compressible means, thus allowing the compressible means to be efficiently compressed.
  • a first end of the compressible means is attached at a first end of the tube and a second end of the compressible means is attached at a second end of the tube.
  • the compressible means is maintained in a position such that it is substantially coaxially aligned with the tube about a central elongate axis.
  • This provides compressible means that is centrally aligned in the tube such that the cooled medium can flow around the entire outer surface of the compressible means. Not only does this minimise the effect of the presence of the compressible means on the water flow, but also provides a maximum surface area for compression of the compressible means, thereby providing the most efficient compensation for pressure in the tube for a given compressible means.
  • the tubes of the heat exchange device are substantially cylindrical
  • the compressible means are substantially cylindrical and each tube and its associated compressible means are substantially coaxially aligned. This arrangement provides a heat exchange device with good flow of the medium through the tubes as well as good compression compensation provided by die uniformly shaped compressible means.
  • the compressible means can have any desired shape and/or size that is suitable for the purpose, and the size and shape may depend, for example on the tube dimensions and shape and also on the medium flowing through the tube.
  • the compressible means has a generally circular cross-section.
  • the shape of the compressible means can contribute to increasing the water side turbulences thereby resulting in am improved overall heat transfer coefficient.
  • the material of the compressible means is distributed throughout the cross-section of the means, but in some embodiments, the compressible means may be at least partially or wholly hollow.
  • the tubes of the device each have an internal diameter and the compressible means each have a cross-sectional diameter (external diameter) when uncompressed of about 10 to 25% of the tube internal diameter.
  • Having compressible means within this range of dimensions is particularly preferred because means with a larger diameter may affect the waterside pressure drop of the heat exchange device (due to reduction of the available area for the water to circulate and thus an increase in velocity of the water flowing within the tubes).
  • each of the tubes of the heat exchange device and each of the compressible means is elongate and has a substantially oval cross-section.
  • the tube and its associated compressible means are substantially coaxially aligned. Being oval in shape, the tube has a maximum internal diameter and a minimum internal diameter and the compressible means has a maximum outer or external diameter and a minimum outer diameter when uncompressed.
  • the compressible means has a maximum outer diameter of about 10 to 25% of the tube maximum internal diameter and a minimum outer diameter of about 10 to 25% of the tube minimum internal diameter.
  • this arrangement is advantageous in that it minimises the effect of the presence of the compressible means and thus minimises the waterside pressure effect.
  • the remaining components of the heat exchange device may comprise any conventional components suitable for use with a heat exchanger.
  • the heat exchange device further comprises an inlet operably connected to a first end of each tube and an outlet operably connected to a second end of each tube, said inlet for supplying said medium to the tubes and to the outlet.
  • water for example, can be provided to the system via the inlet and circulated through the tubes and around the compressible medium before leaving the system via the outlet.
  • the heat exchange device further comprises a shell or housing, with the plurality of tubes housed within said housing and a second medium in the housing and surrounding said tubes.
  • the second medium comprises a refrigerant or other suitable cooling and/or heating medium.
  • the inlet and/or the outlet may be provided as part of the housing, or by separate inlet and outlet manifolds.
  • Figure 1 shows a cross-section of a prior art evaporator unit for a chiller having a plurality of tubes for carrying a medium
  • Figure 2 shows a cross-section of one of the tubes of Figure 1 in various stages of freezing of the medium
  • Figure 3 shows a cross-section of an evaporator unit for a chiller in accordance with an embodiment of the present invention having a plurality of tubes for carrying a medium;
  • Figure 4 shows a cross-section side view of the unit of Figure 3; and Figure 5 shows a cross-section of one of the tubes of Figures 3 and 4 in various stages of freezing of the medium.
  • the evaporator comprises a housing 12 which holds a liquid 30, which is typically a refrigerant as is known in the art.
  • the evaporator also contains a plurality of tubes 20 which are immersed in the refrigerant 30 and are arranged in this embodiment such that the refrigerant completely surrounds each of the tubes 20.
  • the tubes 20 are connected to a supply for providing a medium to be cooled 40 (see Figure 2) through the tubes 20.
  • the medium in an air-cooled chiller is typically water. Heat transfer between the water 40 flowing through the tubes 20 and the refrigerant 30 surrounding the tubes 20 occurs during normal operation of the evaporator 10 to cool the water 40.
  • the internal pressure on the tube 20 is more significant, thereby stressing the tube body 20.
  • the internal tube pressure becomes very high causing the tube to burst or split, as shown at 22 in Figure 2d.
  • the water 40 can mix with the refrigerant 30 in the evaporator 10, causing damage to the chiller and requiring the tube 20 at least to be replaced.
  • FIGS 3 and 4 show an evaporator 10 for a chiller having compressible means
  • the compressible means 60 is preferably an elongate resilient insert, such as a length of closed cell rubber. Each resilient insert 60 is attached at either end of the tube 20 such that it is suspended approximately centrally along the length of the tube 20, dius allowing a clear flow path for the water 40 around the outer periphery of the inset 60.
  • the water 40 enters the evaporator via a water inlet 42, flows along the tubes 20, whilst exchanging heat with the refrigerant 30 surrounding the tubes 20, and passes to the water outlet 44.
  • the ambient temperature falls to a temperature around or below freezing point, and particularly if the evaporator 10 ceases to function, thereby causing the refrigerant 30 surrounding the tubes 20 to boil and thus extracting energy from the tubes 20 and the water 20 they contain, the water 40 begins to freeze at the outer portions of the tubes 20, forming an annular ice section 50.
  • the initial build up of ice 50 has little effect on the tube 20 or on the resilient insert 60, since there is little pressure increase due to the small ring of ice 50.

Landscapes

  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
  • Physical Or Chemical Processes And Apparatus (AREA)

Abstract

L'invention concerne un échangeur thermique (10) et un procédé permettant de compenser les augmentations de pression dans les tubes (20) à l'intérieur de l'échangeur thermique (10). Cet échangeur thermique (10) comprend une pluralité de tubes (20) permettant de transporter un premier milieu (40) et des moyens compressibles (60) pouvant être insérés dans au moins un des tubes (20). La dilatation de ce milieu (40) entraîne la compression des moyens compressibles (60). De préférence, les moyens compressibles (60) comprennent un matériau élastique inerte.
PCT/IB2005/001466 2004-12-14 2005-05-27 Protection d'evaporateur WO2006064313A1 (fr)

Priority Applications (4)

Application Number Priority Date Filing Date Title
BRPI0519048-7A BRPI0519048A2 (pt) 2004-12-14 2005-05-27 dispositivo de troca de calor e mÉtodo de compensar aumentos na pressço de um tubo de um dispositivo de troca de calor
EP05742007A EP1825205A1 (fr) 2004-12-14 2005-05-27 Protection d'evaporateur
US11/720,547 US20080202727A1 (en) 2004-12-14 2005-05-27 Evaporator Protection
HK08105677.1A HK1116243A1 (en) 2004-12-14 2008-05-22 Evaporator protection

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
US63626404P 2004-12-14 2004-12-14
US60/636,264 2004-12-14

Publications (1)

Publication Number Publication Date
WO2006064313A1 true WO2006064313A1 (fr) 2006-06-22

Family

ID=34968627

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/IB2005/001466 WO2006064313A1 (fr) 2004-12-14 2005-05-27 Protection d'evaporateur

Country Status (6)

Country Link
US (1) US20080202727A1 (fr)
EP (1) EP1825205A1 (fr)
CN (1) CN100549611C (fr)
BR (1) BRPI0519048A2 (fr)
HK (1) HK1116243A1 (fr)
WO (1) WO2006064313A1 (fr)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2017211604A1 (fr) * 2016-06-09 2017-12-14 Siemens Aktiengesellschaft Échangeur de chaleur vertical
US20220397351A1 (en) * 2021-06-11 2022-12-15 Zodiac Pool Care Europe Crack mitigation systems and techniques for water-containing housings subject to freezing temperatures

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR566436A (fr) * 1922-08-18 1924-02-14 Air Liquide Perfectionnements aux tubes épais dans lesquels sont produites ou amenées de grandes quantités de chaleur
US1976102A (en) * 1933-02-20 1934-10-09 Young Radiator Co Heat transfer device
FR2717256A1 (fr) * 1994-03-08 1995-09-15 Behr Gmbh & Co Echangeur de chaleur pour un véhicule automobile.
US6207309B1 (en) * 1999-07-16 2001-03-27 International Fuel Cells Llc Environmental compensation method and apparatus for a fuel cell assembly

Family Cites Families (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1946102A (en) * 1930-07-26 1934-02-06 Bendix Brake Co Brake rotor
US5207309A (en) * 1992-08-18 1993-05-04 Simpkin Steven W Concomitant motion control device
US5579828A (en) * 1996-01-16 1996-12-03 Hudson Products Corporation Flexible insert for heat pipe freeze protection
CN2516918Y (zh) * 2001-11-23 2002-10-16 李志领 直冷式渔船微冻保鲜装置及专用蒸发器和冷凝器
CN2615600Y (zh) * 2003-01-17 2004-05-12 清华同方人工环境有限公司 一种过冷抑冰的风侧换热装置
US7201012B2 (en) * 2003-01-31 2007-04-10 Cooligy, Inc. Remedies to prevent cracking in a liquid system

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR566436A (fr) * 1922-08-18 1924-02-14 Air Liquide Perfectionnements aux tubes épais dans lesquels sont produites ou amenées de grandes quantités de chaleur
US1976102A (en) * 1933-02-20 1934-10-09 Young Radiator Co Heat transfer device
FR2717256A1 (fr) * 1994-03-08 1995-09-15 Behr Gmbh & Co Echangeur de chaleur pour un véhicule automobile.
US6207309B1 (en) * 1999-07-16 2001-03-27 International Fuel Cells Llc Environmental compensation method and apparatus for a fuel cell assembly

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2017211604A1 (fr) * 2016-06-09 2017-12-14 Siemens Aktiengesellschaft Échangeur de chaleur vertical
US20220397351A1 (en) * 2021-06-11 2022-12-15 Zodiac Pool Care Europe Crack mitigation systems and techniques for water-containing housings subject to freezing temperatures

Also Published As

Publication number Publication date
EP1825205A1 (fr) 2007-08-29
US20080202727A1 (en) 2008-08-28
BRPI0519048A2 (pt) 2008-12-23
HK1116243A1 (en) 2008-12-19
CN100549611C (zh) 2009-10-14
CN101080604A (zh) 2007-11-28

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