WO2015051799A1 - Échangeur thermique à microcanaux - Google Patents

Échangeur thermique à microcanaux Download PDF

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Publication number
WO2015051799A1
WO2015051799A1 PCT/DK2014/050308 DK2014050308W WO2015051799A1 WO 2015051799 A1 WO2015051799 A1 WO 2015051799A1 DK 2014050308 W DK2014050308 W DK 2014050308W WO 2015051799 A1 WO2015051799 A1 WO 2015051799A1
Authority
WO
WIPO (PCT)
Prior art keywords
heat exchanger
valve
micro channel
bellow
channel heat
Prior art date
Application number
PCT/DK2014/050308
Other languages
English (en)
Inventor
Morten Espersen
Original Assignee
Dantherm Cooling A/S
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 Dantherm Cooling A/S filed Critical Dantherm Cooling A/S
Publication of WO2015051799A1 publication Critical patent/WO2015051799A1/fr

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
    • F25B39/028—Evaporators having distributing means
    • 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
    • F25B39/04—Condensers
    • 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
    • F28D1/053—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 the conduits being straight
    • F28D1/0535—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 the conduits being straight the conduits having a non-circular cross-section
    • F28D1/05366—Assemblies of conduits connected to common headers, e.g. core type radiators
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F27/00—Control arrangements or safety devices specially adapted for heat-exchange or heat-transfer apparatus
    • F28F27/02—Control arrangements or safety devices specially adapted for heat-exchange or heat-transfer apparatus for controlling the distribution of heat-exchange media between different channels
    • 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
    • F28F9/0273—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 holes
    • 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
    • F25B13/00—Compression machines, plants or systems, with reversible cycle
    • 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
    • F25B2500/18—Optimization, e.g. high integration of refrigeration components
    • 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
    • F25B2600/00—Control issues
    • F25B2600/25—Control of valves
    • F25B2600/2511—Evaporator distribution valves
    • 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
    • F25B49/00—Arrangement or mounting of control or safety devices
    • F25B49/02—Arrangement or mounting of control or safety devices for compression type machines, plants or systems

Definitions

  • the present invention relates to a micro channel heat exchanger that is configured for hydraulic reversibility for evaporator or condenser, which heat exchanger comprises at least one inlet for refrigerant, which heat exchanger comprises at least one outlet for refrigerant, which heat exchanger comprises at least one inlet distribution tube connected to the inlet, and which heat exchanger comprises at least one collection tube for collecting refrigerant.
  • Micro channel heat exchangers have been used for condenser coils for several years successfully replacing the well-known fin and tube type heat exchanger in many applications.
  • a further object of the invention is to achieve effective evaporation in a micro channel evaporator designed for both condensation and evaporation
  • the object may be achieved by a micro channel heat exchanger configured for hy- draulic reversible operation as a evaporator or condenser and comprising at least one inlet for a refrigerant and at least one outlet for the refrigerant, which heat exchanger comprises at least one inlet distribution tube connected to the inlet, and which heat exchanger comprises at least one collection tube for collecting the refrigerant to at least one outlet, where the inlet distribution tube comprises an inner tube connecting the inlet to the inlet distribution tube via a connection operatively configured to change between evaporator operation and condenser operation by at least one valve and so that in condenser operation, the connection is open for flow from the inner tube to the distribution tube.
  • the object can be fulfilled by a heat exchanger as disclosed in the preamble to claim 1 and further modified in that the inlet distribution tube comprises a inner tube, which inner tube is connected to the inlet, which heat exchanger comprises at least one valve, which valve by evaporator operation closes a connection between the inner tube and the outer distribution tube, which valve by condenser operation is open for flow from the inner tube to the distribution tube.
  • condenser operation mode there is a traditional mainly open flow through the heat exchanger.
  • the pressure of the refrigerant is relative high because the refrigerant has just left, probably, a compressor. Therefore, when entering the condenser the refrigerant is relatively warm and the pressure is relatively high. By condensing, the refrigerant entering the system will be in a gas form and when it leaves it is converted into a liquid. Therefore, relatively large openings are acceptable in the flow of refrig- erant by condensation.
  • valve mechanism it is possible to change between the two kinds of operation.
  • Different valves can be used, for example it would be possible to use a magnetic valve to perform the change, which valve in operation may be connected to a control system, which in the same way controls the shift from evaporation to condensation. This shift is probably used in heat pumps combined with air condition use of same components.
  • many different valves can be used; manual valves are another example where the hand tool is used to change the valve.
  • An automatic valve will of course be the most effective, as that valve is operating without any external connection.
  • the inner tube can comprise a number of bleed holes for limiting the flow towards the distribution tube in evaporator operation.
  • a number of small bleed holes can form jets in different directions from the inner tube into the outer tube.
  • the valve can be pressure activated.
  • valve works automatically. As there is a change in operation pressure between condensation and evaporation, energy for opening or closing can be picked by the pressure difference.
  • valve in evaporator mode of operation can be closed and the bleed holes in the wall on the inner tube are configured to form jets directed towards the micro channels.
  • jets are directed directly to the inlet of the micro channels.
  • most of the channels will get a jet of liquid refrigerant which then on its way through the evaporator will evaporate into a gas and keep the inner of the micro channels, and thereby also the outer of the micro channels, at a low temperature and thus achieve very effective operation of the evaporator.
  • the valve can operate against a valve seat formed at the end of the inner tube, which valve is formed by a bellow, which bellow contains a gas.
  • the bellow will work as an automatic valve actuator.
  • the pressure inside the valve can be selected by the selection of a gas in accordance with the actual pressure and a temperature so that in evaporation mode with low pressure the bellow will expand and close the valve, and in the operation of condenser the higher pressure will perform opening of the valve by compressing the gas inside the bellow.
  • Micro channel heat exchangers have been used for condenser coils for several years, successfully replacing the well-known fin and tube type heat exchanger in many applications. This is mainly due to their high efficiency, low cost, low weight and low refrigerant charge which made them highly successful in automobile applications.
  • using the above type of heat exchanger for evaporators in the HVAC segment has been much more limited.
  • One of the reasons for this is that the heat transfer process for an evaporator is much different from the condensing process.
  • the nature of the condensing process is very much facilitated by the coil geometry, whereas the evaporation process is not.
  • Practices have shown that it is much more difficult to operate an evaporator than a condenser efficiently by using mini channel geometry.
  • Figure 2 shows a cut through of a special coil.
  • the coil has a distributer tube containing jets and is designed for evaporative purpose.
  • the jets are also shown in figure 3.
  • the purpose of the jets is to distribute the coolant evenly into the mini channel geometry which is necessary to facilitate a high efficiency for the process. This construction is associated with a significant pressure drop through the jets.
  • This special geometry is not used in condenser coils as the flow path is reverse and of a nature that does not need any special geometry to be operated. At this time we have no knowledge of mini channel heat exchangers being used for alternating cooling / heat pump operations.
  • the current innovation makes it possible to manufacture a cost efficient multipurpose coil using a simple low cost valve. This valve is shown in figure 4.
  • the valve makes it possible to use the jets when the coil operates as an evaporator. In this scenario, the valve is closed forcing refrigerant through the jets. Similarly, the valve makes it possible not to use the jets when the flow is reversed for condenser use.
  • the bellow valve is pressure operated. The valve might also use a spring or the bellow itself might act as a spring. Also, the bellow might be filled with a gas or it might not.
  • the bellow is filled with a gas which is non-condensable in the operating design window.
  • the pressure inside the bellow is fixed at a desired level which is reasonable "constant". In reality it is of course not.
  • the pressure inside the coil is always dominated by the saturation state of the coil. When the coil operates as an evaporator, this pressure is low. It should also be lower than the pressure inside the bellow valve which makes the bellow close the valve forcing the refrigerant through the system of jets. The coil now efficiently operates as an evaporator.
  • valve 5a The state with the valve closed is shown in figure 5a.
  • valve In figure 5b the valve is open and the coil operates as a condenser. Reversing the flow path increases the pressure inside the coil. This higher pressure is higher than the pressure inside the bellow, and the bellow opens the valve. This allows the condensed refrigerant to bypass the jets and enter the tube directly. This is of paramount importance. If the valve was not there, there would be a significant pressure drop through the jets which would facilitate a pressure drop, destroying the possible sub cooled liquid state or even worse make the refrigerant boil compromising the entire system stability as the expansion valve would not function correctly anymore.
  • the bellow valve is shown in figure 4.
  • the bellow is preferably made in a material with a higher melting point than aluminum.
  • the bellow disk is preferably made from aluminum, possible even clad material.
  • This construction allows the bellow to be soldered into the system with the rest of the construction when it runs through the furnace.
  • the bellow valve should be made in such a way that it can be charged with gas either prior to being soldered into the construction or after the soldering process. In the case where it is charged after being soldered into the construction, it should pref- erably have an opening in the disk with a capillary charging tube, a ball type charging facility or similar.
  • the latter construction enables high design flexibility as the pressure inside the bellow to be calibrated for many different design temperatures by means of a very simple gas charging mechanism.
  • FIG. 6 shows schematics of the system. Both coils are of this special alternating type and these are similar for the current construction. The function on the left is reversed compared to the function on the right. Connecting the coils is very easy and needs no additional tubing. Description of the Drawings
  • Figure 1 shows one possible embodiment for a heat exchanger 2.
  • Figure 2 shows the same embodiment for a heat exchanger as figure 1 but in a sectional view.
  • Figure 3 shows an end sectional view of the heat exchanger 2.
  • Figure 4 shows a bellow forming an actuator for the valve.
  • Figure 5a shows an enlarged sectional view of the valve mechanism placed inside a distribution tube and figure 5b shows the same embodiment but in the other way of operation.
  • Figures 6 and 7 disclose, for example, an air condition system having different modes of operation.
  • FIG. 1 shows one possible embodiment for a heat exchanger 2.
  • This heat exchanger comprises an inlet 4 and an outlet 6.
  • a lower distribution tube 8 is indicated as well as a colleting tube 10.
  • a number of micro channels 20 are connected between the lower distribution tube 8 and the upper colleting tube 10. The micro channels have a large surface and therefore, a relative good heat transmission is performed to the surrounding air.
  • Figure 2 shows the same embodiment for a heat exchanger as figure 1 but in a sec- tional view, where the inner part of the heat exchanger is disclosed.
  • the inlet 4 is connected to a tube 12 and it is clearly indicated that micro channels 20 are connecting the distribution tube 8 with the collecting tube 10.
  • the inner tube 12 ends in valve 14 which is pressure activated, which valve 14 is adapted to close the connection between the distribution tube 8 and the inner tube 12.
  • Figure 3 shows an end sectional view of the heat exchanger 2.
  • the distribution tube 8 is indicated and it is clear that micro channels 20 are connected to the distribution tube 8.
  • the inner tube 12 comprises bleed holes 16, which bleed holes 16 are forming jets directed towards the micro channels 20.
  • FIG. 4 shows a bellow 24 forming an actuator for the valve 14.
  • FIG. 5a shows an enlarged sectional view of the valve mechanism placed inside a distribution tube 8.
  • the valve 14, formed by a bellow 24, is closing the inner tube 12.
  • Herby is the refrigerant forced to be distributed in form of jets through the bleed holes 16.
  • With the bellow 24 in a closed situation the pressure in the evaporator will be relative low because the evaporator will probably be connected to the suction side of a compressor.
  • Figure 5b shows the same embodiment but in the other way of operation, probably as a condensation unit.
  • the bellow 24 will be subjected to a higher pressure as the condensation unit is connected to the pressure side of a compressor. This increasing pressure will open the valve 14 by compressing the bellow 24. Because the bellow now has opened the valve, it is possible to see a valve seat 22. Which valve seat is formed at the end of the inner tube 12.
  • Figures 6 and 7 disclose, for example, an air condition system having different modes of operation.
  • a compressor 104 has a suction side 106 and a pressure side 108. Both suction side 106 and pressure side 108 are connected to a shifting valve 110. This is a so-called cross over valve, which contains the flow of the refrigerant.
  • the pressure side 108 is connected through the valve 1 10 into the line 112.
  • This line 112 leads to a condenser 114.
  • a flow restriction such as an expansion valve 116 reduces the pressure before the flow enters an evaporator 118. From the evaporator the gas will flow through line 120 and once again through the valve 110 into the suction line 106.
  • the valve 110 is in its opposite position. Hereby, the previous condenser 114 is now changed into an evaporator. The flow direction is different due to the change of the valve 110.

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

Abstract

La présente invention concerne un échangeur thermique à microcanaux (2), lequel échangeur thermique à microcanaux (2) ayant une réversibilité hydraulique pour un évaporateur ou un condenseur. L'échangeur thermique (2) comprend au moins un tube de distribution d'entrée (4) relié à l'entrée. Un objectif de l'invention est de réaliser un changement automatique entre la condensation évaporation. Un autre objectif de l'invention est d'effectuer une évaporation efficace dans un évaporateur à microcanaux (2) conçu à la fois pour une condensation et une évaporation. L'objectif peut être réalisé par le fait que le tube de distribution d'entrée (4) comprend un tube interne (12), lequel tube interne (12) étant relié à l'entrée (4), lequel échangeur thermique (2) comprenant au moins une vanne (14), laquelle vanne (14) par fonctionnement de condenseur est ouverte pour un écoulement du tube interne (12) vers le tube de distribution (8). Ainsi la possibilité de changement entre deux modes différents de fonctionnement peut être obtenue. En mode de fonctionnement condenseur, il y a un écoulement classique principalement ouvert à travers l'échangeur thermique (2). La pression du fluide frigorigène est relativement élevée car le fluide frigorigène vient de quitter, probablement, un compresseur, en fonctionnement en tant qu'évaporateur, une distribution de l'écoulement de liquide est nécessaire.
PCT/DK2014/050308 2013-10-09 2014-10-01 Échangeur thermique à microcanaux WO2015051799A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DKPA201370570 2013-10-09
DKPA201370570 2013-10-09

Publications (1)

Publication Number Publication Date
WO2015051799A1 true WO2015051799A1 (fr) 2015-04-16

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Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US10465949B2 (en) * 2017-07-05 2019-11-05 Lennox Industries Inc. HVAC systems and methods with multiple-path expansion device subsystems
WO2020176746A1 (fr) * 2019-02-27 2020-09-03 Dantherm Cooling Inc. Échangeur de chaleur passif à bobine à microcanal unique

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20030192340A1 (en) * 2002-04-16 2003-10-16 Diflora Michael A. Heat exchanger having improved header
WO2006083450A2 (fr) * 2005-02-02 2006-08-10 Carrier Corporation Echangeur de chaleur a mini-canaux comprenant un collecteur a dimension reduite
WO2006083446A2 (fr) * 2005-02-02 2006-08-10 Carrier Corporation Echangeur de chaleur dote d'un dispositif d'expansion de fluide dans un collecteur
WO2006083426A1 (fr) * 2005-02-02 2006-08-10 Carrier Corporation Insert tubulaire et dispositif a ecoulement double destine a un collecteur d'une pompe a chaleur
EP2631183A1 (fr) * 2010-10-21 2013-08-28 Ibérica del Espacio, S.A. Dispositif de régulation thermique régulé par la pression

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20030192340A1 (en) * 2002-04-16 2003-10-16 Diflora Michael A. Heat exchanger having improved header
WO2006083450A2 (fr) * 2005-02-02 2006-08-10 Carrier Corporation Echangeur de chaleur a mini-canaux comprenant un collecteur a dimension reduite
WO2006083446A2 (fr) * 2005-02-02 2006-08-10 Carrier Corporation Echangeur de chaleur dote d'un dispositif d'expansion de fluide dans un collecteur
WO2006083426A1 (fr) * 2005-02-02 2006-08-10 Carrier Corporation Insert tubulaire et dispositif a ecoulement double destine a un collecteur d'une pompe a chaleur
EP2631183A1 (fr) * 2010-10-21 2013-08-28 Ibérica del Espacio, S.A. Dispositif de régulation thermique régulé par la pression

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US10465949B2 (en) * 2017-07-05 2019-11-05 Lennox Industries Inc. HVAC systems and methods with multiple-path expansion device subsystems
US11255582B2 (en) 2017-07-05 2022-02-22 Lennox Industries Inc. HVAC systems and methods with multiple-path expansion device subsystems
WO2020176746A1 (fr) * 2019-02-27 2020-09-03 Dantherm Cooling Inc. Échangeur de chaleur passif à bobine à microcanal unique
AU2020227818B2 (en) * 2019-02-27 2023-08-10 Dantherm Cooling Inc. Passive heat exchanger with single microchannel coil

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