EP2313733A2 - Echangeur de chaleur à micro-canaux à plusieurs circuits intégrés - Google Patents

Echangeur de chaleur à micro-canaux à plusieurs circuits intégrés

Info

Publication number
EP2313733A2
EP2313733A2 EP09798567A EP09798567A EP2313733A2 EP 2313733 A2 EP2313733 A2 EP 2313733A2 EP 09798567 A EP09798567 A EP 09798567A EP 09798567 A EP09798567 A EP 09798567A EP 2313733 A2 EP2313733 A2 EP 2313733A2
Authority
EP
European Patent Office
Prior art keywords
heat exchanger
manifolds
refrigerant
set forth
tubes
Prior art date
Legal status (The legal status 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 status listed.)
Ceased
Application number
EP09798567A
Other languages
German (de)
English (en)
Other versions
EP2313733A4 (fr
Inventor
Michael F. Taras
Alexander Lifson
Allen C. Kirkwood
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Carrier Corp
Original Assignee
Carrier Corp
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 Corp filed Critical Carrier Corp
Publication of EP2313733A2 publication Critical patent/EP2313733A2/fr
Publication of EP2313733A4 publication Critical patent/EP2313733A4/fr
Ceased legal-status Critical Current

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
    • 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
    • F28D1/0426—Multi-circuit heat exchangers, e.g. integrating different heat exchange sections in the same unit or heat exchangers for more than two fluids with units having particular arrangement relative to the large body of fluid, e.g. with interleaved units or with adjacent heat exchange units in common air flow or with units extending at an angle to each other or with units arranged around a central element
    • 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
    • F28D1/05391—Assemblies of conduits connected to common headers, e.g. core type radiators with multiple rows of conduits or with multi-channel conduits combined with a particular flow pattern, e.g. multi-row multi-stage 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
    • 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
    • F28F2009/0297—Side headers, e.g. for radiators having conduits laterally connected to common header
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F2260/00—Heat exchangers or heat exchange elements having special size, e.g. microstructures
    • F28F2260/02—Heat exchangers or heat exchange elements having special size, e.g. microstructures having microchannels

Definitions

  • These heat exchangers are provided with a plurality of parallel heat exchange tubes, typically of a non-round shape, among which refrigerant is distributed and flown in a parallel manner.
  • the heat exchange tubes are orientated generally substantially perpendicular to a refrigerant flow direction in inlet, intermediate and outlet manifolds that are in flow communication with the heat exchange tubes.
  • the heat exchange tubes typically have a multi-channel construction, with refrigerant distributed within these multiple channels in a parallel manner.
  • Heat transfer fins may be inter-disposed and rigidly attached to the heat exchange tubes.
  • a dual circuit refrigerant system having two completely separate refrigerant independent circuits with separate compressors and heat exchangers, etc. can be provided to achieve capacity control and efficiency improvement.
  • the provision of the multiple distinct refrigerant circuits utilizing total frontal or cross-sectional area of the heat exchanger has required distinct heat exchangers, at least when a microchannel heat exchanger is used.
  • More traditional heat exchangers such as a round tube and plate fin heat exchangers, can be formed to be of a multi-circuit intertwined configuration utilizing the total frontal area of the heat exchanger, however, microchannel heat exchangers have not been easily tailored to include such multiple circuit configurations.
  • a microchannel heat exchanger includes two separate manifolds leading into a plurality of separate microchannel tube banks.
  • the separate tube banks extend parallel to each other along a first direction through one dimension of a heat exchange area.
  • the banks from the at least two manifolds are interspersed along a second direction which is perpendicular to the first direction.
  • Figure IA is a 3D view of an inventive heat exchanger.
  • Figure IB shows a first schematic that might utilize the inventive heat exchanger.
  • Figure 1C shows a second schematic that might utilize the inventive heat exchanger.
  • Figure 2 shows an enlarged manifold section of the Figure IA heat exchanger.
  • Figure 3 is an end view of Figure 2.
  • Figure 4A shows detail of the manifold section of the inventive heat exchanger.
  • Figure 4B shows an alternate feature of the inventive heat exchanger.
  • Figure 5 is a cross-sectional view of a heat exchange tube.
  • Figure 6A shows a 3D view of another embodiment of the inventive heat exchanger.
  • Figure 6B is an end view of the Figure 6A embodiment.
  • Figure 6C shows an enlarged manifold section of the Figure 6A heat exchanger.
  • Figure 7A shows a 3D view of another embodiment of the inventive heat exchanger.
  • Figure 7B is an end view of the Figure 7A embodiment.
  • Figure 7C shows an enlarged manifold section of the Figure 7A heat exchanger.
  • Figure 1 shows a microchannel heat exchanger 20 having a heat exchanger frontal or cross-sectional surface area 21.
  • An inlet pipe 24 supplies refrigerant into a first inlet manifold 22, and an inlet pipe 28 supplies refrigerant into a second inlet manifold 26.
  • the two inlet pipes 24 and 28 can be connected to completely separate independent refrigerant circuits, or can be connected to a common refrigerant source of a single refrigerant circuit.
  • Outlet manifolds 30 and 32 lead to outlet pipes 29 and 31, communicating the refrigerant downstream to independent refrigerant circuits or to a single refrigerant circuit respectively.
  • any suitable heat transfer fluid such as, for instance, water, ethylene glycol, propylene glycol or oil, and an associated system, can be utilized instead.
  • any suitable heat transfer fluid such as, for instance, water, ethylene glycol, propylene glycol or oil, and an associated system.
  • microchannel heat exchangers of the invention are schematically shown in a single-pass configuration (see for instance Figure IA), any number of passes can be implemented in a similar manner, and all such multi-pass microchannel heat exchangers (see Figure 4B) are within the scope of the invention.
  • inlet pipes 24 and 28 and the outlet pipes 29 and 31 communicate refrigerant to separate independent refrigerant circuits of a refrigerant system, capacity control and efficiency improvement are achieved at part-load operation, as the entire frontal surface area 21 is utilized in heat transfer interaction with the air flowing across heat exchanger external surfaces, while only one of the refrigerant circuits is operating.
  • inlet pipes 24 and 28 and the outlet pipes 29 and 31 communicate refrigerant to a single refrigerant circuit of a refrigerant system, at certain conditions, it may be desired to flow refrigerant only through a portion of the heat exchanger 20, while still utilizing the entire heat exchanger frontal area 21 for better performance.
  • Such conditions may arise, for instance, for the purposes of head pressure control or maintaining minimum refrigerant velocity for proper oil circulation throughout a refrigerant system and return to the compressor.
  • it may be desirable to implement multiple independent refrigerant paths of a single refrigerant circuit through the heat exchanger core to improve refrigerant distribution and the heat exchanger effectiveness.
  • refrigerant distribution is particularly important for two- phase refrigerant flows, such as a refrigerant flow entering an evaporator.
  • Figure IB shows a basic exemplary multi-circuit refrigerant system that might utilize the inventive heat exchanger 20.
  • this multi-circuit refrigerant system there are two entirely separate independent refrigerant circuits 300 and 301, each incorporating its own expansion device 302, separate evaporator heat exchangers 304 and 308, and separate compressors 306.
  • the refrigerant is routed through the single heat exchanger 20.
  • the Figure IB is quite simplified, and the flow through the heat exchanger 20 can be better appreciated from a review of Figure IA.
  • the system may be a heat pump or an air conditioner, and the heat exchanger 20 may be the indoor heat exchanger or the outdoor heat exchanger.
  • the heat exchanger 20 can be utilized for other applications such as a reheat function, as an example, if appropriate refrigerant circuitry is provided.
  • FIG. 1C shows yet another application of the inventive heat exchanger 20.
  • a single refrigerant line 401 leads to branch refrigerant lines 402 and 404, connecting to the refrigerant manifolds associated with the inventive heat exchanger 20.
  • Refrigerant flow control devices such as valves 406 control refrigerant flow to the branch refrigerant lines 402 and 404, and then to the heat exchanger 20.
  • the total volume of refrigerant passing through the heat exchanger 20 refrigerant velocity and heat transfer area utilization for the heat exchanger 20 can be controlled.
  • the various reasons for providing such control are known in the art, but the use of a microchannel heat exchanger providing intertwined refrigerant circuits within a single heat exchanger structure is inventive.
  • FIG. 2 shows a detail of the inlet manifolds 22 and 26.
  • the outlet manifolds 30 and 32 are constructed and connected to the heat exchanger core in a similar manner.
  • connecting tubes 33 from each manifold 22 and 26 alternatively lead to separate independent banks of heat exchange tubes 34 extending perpendicular to the plane of the frontal heat exchange surface area 21 along a first direction.
  • Each manifold has plural connecting tubes 33 connected to plural refrigerant heat exchange tubes 34.
  • the heat exchange tube banks 34 connected to the two manifolds 22 and 26 have an alternating pattern along a second direction along the manifold axis, which is generally perpendicular to the first direction. For instance, in some applications, the first direction is a horizontal direction and the second direction is a vertical direction; in other applications the first direction is a vertical direction and the second direction is a horizontal direction.
  • Figure 3 shows the end view of the heat exchanger 20 and its manifolds 22 and 26 leading to the connecting tubes 33.
  • the manifolds are shown extending generally vertically, with the heat exchange tube banks extending generally horizontally, the manifolds can extend generally horizontally with the heat exchange tube banks extending generally vertically.
  • the heat exchanger 20 typically includes external heat transfer fins, like a standard microchannel heat exchanger construction, but they have been omitted to simplify the understanding of the drawings.
  • FIG 4A shows a detail of the inlet pipe 28 leading into the inlet manifold 26, into the connecting tube 33, and into the bank of heat exchange tubes 34.
  • the heat exchange tube 34 for a microchannel heat exchanger typically has a plurality of parallel refrigerant channels 100 separated by dividing walls 101, as shown in Figure 5.
  • the parallel refrigerant channels 100 each preferably have a hydraulic diameter that is less than 5 mm, and may be less than 3 mm.
  • the term "hydraulic diameter” does not imply that the channels are circular in cross-section.
  • Figure 4B shows an alternative heat exchanger pass arrangement 200.
  • refrigerant flows through the heat exchange tube bank 34 extending from the inlet manifold chamber 205 of the manifold 22 toward the intermediate manifold chamber 207 of the manifold 30, but then reverses flow direction through another heat exchange tube bank 201 to reach the intermediate manifold chamber 208 of the manifold 22, and then reverses direction once again to flow through yet another heat exchange tube bank 202 to reach the outlet chamber 206 of the manifold 30.
  • Divider plates 204 subdivide each of the manifolds 22 and 30 into the manifold chambers 205 and 208 and manifold chambers 207 and 208 respectively.
  • heat exchange tube banks of the other refrigerant circuit would be intertwined with the heat exchange tube banks 34, 201 and 202.
  • Figure 4B is a very simplified view. As can be appreciated, connecting refrigerant tubes 33 extending laterally from the manifolds 22 and 30 would typically be utilized within this embodiment, but are omitted in the Figure 4B for simplicity.
  • FIGS 6A and 6B show another embodiment 75 wherein an inlet manifold 82 has three adjacent connecting tubes 84, and hence three adjacent heat exchange tubes, and an inlet manifold 80 has only two adjacent connecting tubes 86, and hence only two adjacent heat exchange tubes.
  • the alternating pattern repeats itself along the manifold axis.
  • ratios other than 3:2 can be utilized.
  • This unequal circuit split may become advantages, for instance, when refrigerant circuits and associated compression systems are of a different size and capacity, allowing for different stages of capacity modulation and unloading. It has to be understood that a single connecting refrigerant tube 84 or 86 of a larger diameter, that leads to adjacent heat exchange tubes, can be utilized instead.
  • Figure 6C is a perspective 3D view showing a detail of the manifold structure.
  • the power of the inventive system is apparent, in that it provides high flexibility control over capacity modulation by utilizing the distinct number of heat exchange tube banks of a variable size.
  • refrigerant will flow into each of the manifolds 80 and 82, into the respective connecting refrigerant tubes 86 and 84, and then into the associated heat exchange tube banks.
  • This embodiment can utilize the multi-pass alternative as shown in Figure 4B, or can be utilized in a single-pass configuration.
  • Figures 7A and 7B show the power and flexibility of the inventive concept wherein an embodiment 90 has an inlet manifold 92 with associated connecting refrigerant tubes 94, an inlet manifold 96 with associated connecting refrigerant tubes 98, an inlet manifold 110 with associated connecting refrigerant tubes 112, and an inlet manifold 114 with associated connecting refrigerant tubes 116. More than four independent refrigerant circuits flowing through the heat exchanger 90 can be utilized.
  • Figure 7C is a perspective 3D view showing the detail of the manifold arrangement of the Figure 7A. Additional manifolds can be interfit into available space around the heat exchanger structure as shown in Figure 7C. As illustrated, the inlet manifolds 96 and 114 are located on one side of the core heat transfer area 21, while the manifolds 92 and 110 are positioned on an opposed side of the core heat transfer area 21. As before, refrigerant flowing through the several inlet manifolds passes into respective connecting refrigerant tubes, and into respective heat exchange tube banks. Again, multipass configurations such as shown in Figure 4B can also be utilized within this embodiment.
  • the connecting refrigerant tubes 33 may have different cross-sectional areas, including (but not limited to) round, oval, rectangular, and square cross-sections. All these connecting refrigerant tube configurations are within the scope of the invention. Furthermore, in some design arrangements, the connecting refrigerant tubes 33 may not be required, when the heat exchange tubes 34 are bent in an alternating pattern such that they fit directly into different inlet and outlet manifolds positioned as exhibited in multiple Figures illustrating the invention. Such design arrangements, although feasible, may not be desirable from manufacturability and reliability perspectives. Lastly, inlet and outlet manifolds may be positioned at the same end of the heat exchanger core 21, depending on the refrigerant pass arrangement within the heat exchanger core.
  • the inventive heat exchanger can be utilized within all types of refrigerant systems, such as air conditioning systems, refrigeration systems and heat pump systems, as well as within other auxiliary systems, such as, for instance, water cooling or heating systems, process gas/air cooling or heating systems, and oil cooling or heating systems.
  • inventive heat exchanger can be utilized as an evaporator, condenser, gas cooler, reheat heat exchanger or any other heat exchanger within commercial and residential air conditioning and heat pump systems, marine container units, refrigeration truck-trailer units, merchandisers, bottle coolers, supermarket refrigeration systems, etc.

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  • 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)
  • Quick-Acting Or Multi-Walled Pipe Joints (AREA)

Abstract

L'invention concerne un échangeur de chaleur à micro-canaux qui comporte au moins deux collecteurs, lesdits au moins deux collecteurs communiquant avec l'une d'une première et d'une seconde pluralité de bancs de tubes d'échange de chaleur. La première et la seconde pluralité de bancs de tubes d'échange de chaleur sont entrelacées dans un simple noyau d'échangeur de chaleur à micro-canaux.
EP09798567.5A 2008-07-15 2009-07-07 Echangeur de chaleur à micro-canaux à plusieurs circuits intégrés Ceased EP2313733A4 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
US8078008P 2008-07-15 2008-07-15
PCT/US2009/049736 WO2010008960A2 (fr) 2008-07-15 2009-07-07 Echangeur de chaleur à micro-canaux à plusieurs circuits intégrés

Publications (2)

Publication Number Publication Date
EP2313733A2 true EP2313733A2 (fr) 2011-04-27
EP2313733A4 EP2313733A4 (fr) 2014-02-26

Family

ID=41550968

Family Applications (1)

Application Number Title Priority Date Filing Date
EP09798567.5A Ceased EP2313733A4 (fr) 2008-07-15 2009-07-07 Echangeur de chaleur à micro-canaux à plusieurs circuits intégrés

Country Status (4)

Country Link
US (1) US20110056667A1 (fr)
EP (1) EP2313733A4 (fr)
CN (1) CN102099651B (fr)
WO (1) WO2010008960A2 (fr)

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Also Published As

Publication number Publication date
US20110056667A1 (en) 2011-03-10
CN102099651A (zh) 2011-06-15
EP2313733A4 (fr) 2014-02-26
CN102099651B (zh) 2013-12-25
WO2010008960A3 (fr) 2010-04-08
WO2010008960A2 (fr) 2010-01-21

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