US20140174703A1 - Heat exchanger - Google Patents

Heat exchanger Download PDF

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Publication number
US20140174703A1
US20140174703A1 US14/234,563 US201214234563A US2014174703A1 US 20140174703 A1 US20140174703 A1 US 20140174703A1 US 201214234563 A US201214234563 A US 201214234563A US 2014174703 A1 US2014174703 A1 US 2014174703A1
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United States
Prior art keywords
channel
tube
refrigerant
sub
heat exchanger
Prior art date
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Abandoned
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US14/234,563
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English (en)
Inventor
Shun Yoshioka
Ryuhei Kaji
Yoshikazu Shiraishi
Akihiro Fujiwara
Takayuki Hyoudou
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Daikin Industries Ltd
Original Assignee
Daikin Industries Ltd
Shimano Inc
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Application filed by Daikin Industries Ltd, Shimano Inc filed Critical Daikin Industries Ltd
Assigned to SHIMANO INC. reassignment SHIMANO INC. ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: FUJIWARA, AKIHIRO, HYOUDOU, TAKAYUKI, KAJI, RYUHEI, SHIRAISHI, YOSHIKAZU, YOSHIOKA, SHUN
Publication of US20140174703A1 publication Critical patent/US20140174703A1/en
Assigned to DAIKIN INDUSTRIES, LTD. reassignment DAIKIN INDUSTRIES, LTD. CORRECTIVE ASSIGNMENT TO CORRECT THE ASSIGNEE A PREVIOUSLY RECORDED ON REEL 032031 FRAME 0568. ASSIGNOR(S) HEREBY CONFIRMS THE 502648311. Assignors: FUJIWARA, AKIHIRO, HYOUDOU, TAKAYUKI, KAJI, RYUHEI, SHIRAISHI, YOSHIKAZU, YOSHIOKA, SHUN
Abandoned legal-status Critical Current

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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D7/00—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
    • F28D7/0008—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits for one medium being in heat conductive contact with the conduits for the other medium
    • F28D7/0025—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits for one medium being in heat conductive contact with the conduits for the other medium the conduits for one medium or the conduits for both media being flat tubes or arrays of tubes
    • F28D7/0033—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits for one medium being in heat conductive contact with the conduits for the other medium the conduits for one medium or the conduits for both media being flat tubes or arrays of tubes the conduits for one medium or the conduits for both media being bent
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F1/00—Tubular elements; Assemblies of tubular elements
    • F28F1/02—Tubular elements of cross-section which is non-circular
    • F28F1/022—Tubular elements of cross-section which is non-circular with multiple 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
    • F28F1/00—Tubular elements; Assemblies of tubular elements
    • F28F1/02—Tubular elements of cross-section which is non-circular
    • F28F1/025—Tubular elements of cross-section which is non-circular with variable shape, e.g. with modified tube ends, with different geometrical features
    • 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
    • F28F9/0219—Arrangements for sealing end plates into casing or header box; Header box sub-elements
    • F28F9/0221—Header boxes or end plates formed by stacked elements
    • 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
    • F28F9/0243—Header boxes having a circular cross-section
    • 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
    • F28F9/0278—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 stacked distribution plates or perforated plates arranged over end plates
    • 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
    • F25B1/00—Compression machines, plants or systems with non-reversible cycle
    • F25B1/10—Compression machines, plants or systems with non-reversible cycle with multi-stage compression
    • 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
    • F25B2400/00—General features or devices for refrigeration machines, plants or systems, combined heating and refrigeration systems or heat-pump systems, i.e. not limited to a particular subgroup of F25B
    • F25B2400/13—Economisers
    • 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
    • F28D1/05383—Assemblies of conduits connected to common headers, e.g. core type radiators with multiple rows of conduits or with multi-channel conduits

Definitions

  • the present invention relates to a heat exchanger.
  • Heat exchangers that use flat porous tubes to allow heat exchange between a refrigerant and a refrigerant are conventionally used in refrigeration cycles, as disclosed in Patent Document 1 (Japanese Laid-Open Patent Application No. 2007-163004).
  • Two flat porous tubes, through which flow two respective types of refrigerant that are subjected to heat exchange, are bonded together in these heat exchangers.
  • the flat porous tubes in these heat exchangers are linked to a header so that the alignment direction of refrigerant flow-channel holes of the flat porous tubes proceeds along a longitudinal direction of the header.
  • the header must therefore be lengthened in cases where a plurality of the flat porous tubes are linked to the header, and the device is not readily made more compact.
  • a heat exchanger comprises a header, a first flat tube, and a second flat tube.
  • the header has a first primary channel and a second primary channel, a first refrigerant flowing through the first primary channel, and a second refrigerant flowing through the second primary channel.
  • the first flat tube is linked to the header.
  • the first flat tube is a flat porous tube that has a plurality of first refrigerant-channel holes through which the first refrigerant flows.
  • the second flat tube is linked to the header.
  • the second flat tube is a flat porous tube that has a plurality of second refrigerant-channel holes through which the second refrigerant flows.
  • the header has a sub-channel-forming member.
  • the sub-channel-forming member forms a first sub-channel and a second sub-channel.
  • the first sub-channel allows the first primary channel to be communicated with the first refrigerant-channel holes.
  • the second sub-channel allows the second primary channel to be communicated with the second refrigerant-channel holes.
  • the first flat tube and the second flat tube are in close contact. In the first flat tube and the second flat tube, heat is exchanged between the first refrigerant flowing through the first refrigerant-channel holes and the second refrigerant flowing through the second refrigerant-channel holes.
  • the first primary channel of the header is communicated with the plurality of the first refrigerant-channel holes of the first flat tube via the first sub-channel
  • the second primary channel of the header is communicated with the plurality of the second refrigerant-channel holes of the second flat tube via the second sub-channel.
  • the first flat tube is flat along the alignment direction of the first refrigerant-channel holes.
  • the first primary channel is formed along a longitudinal direction of the header. In cases where the first refrigerant-channel holes are directly communicated with the first primary channel, the first flat tube must be linked to the header so that the flatness direction of the first flat tube proceeds along the longitudinal direction of the header.
  • the header must therefore be long in cases where a plurality of the first flat tubes are linked to the header, and therefore the heat exchanger is not readily made more compact.
  • the refrigerant-channel holes are communicated with the first primary channel via, the first sub-channel, whereby the first flat tube need not be linked to the header so that the flatness direction of the first flat tube proceeds along the longitudinal direction of the header.
  • the case is the same for the second flat tube. Therefore, the header does not need to be lengthened, and the heat exchanger according to the first aspect can be made more compact.
  • a heat exchanger according to a second aspect of the present invention is the heat exchanger according to the first aspect, wherein the first flat tube and the second flat tube are linked to the header so that a cross-sectional longitudinal direction intersects a longitudinal direction of the header, the cross-sectional longitudinal direction being alignment directions of the first refrigerant-channel holes and the second refrigerant-channel holes.
  • a heat exchanger according to a third aspect of the present invention is the heat exchanger according to the second aspect, wherein the first flat tube and the second flat tube are linked to the header so that the cross-sectional longitudinal direction is perpendicular to the longitudinal direction of the header.
  • the first flat tube is linked to the header so that the flatness direction of the first flat tube is perpendicular to the longitudinal direction of the header.
  • the case is the same for the second flat tube.
  • the heat exchanger according to the third aspect can therefore be efficiently made more compact.
  • a heat exchanger according to a fourth aspect of the present invention is the heat exchanger according to any of the first through third aspects, wherein the sub-channel-forming member comprises a tube-adhering member adhered to end parts of the first flat tube and the second flat tube and immobilized on the header.
  • a member for linking the first flat tube to the header and a member for linking the second flat tube to the header can be integrated.
  • the number of components can therefore be minimized in the heat exchanger according to the fourth aspect, and manufacturing costs can therefore be limited.
  • a heat exchanger according to a fifth aspect of the present invention is the heat exchanger according to the fourth aspect, wherein the sub-channel-forming member further comprises a tube-immobilizing member for immobilizing the end parts of the first flat tube and the second flat tube along with the tube-adhering member.
  • a heat exchanger according to a sixth aspect of the present invention is the heat exchanger according to any of the first through fifth aspects, wherein the sub-channel-forming member forms a plurality of the first sub-channels and a plurality of the second sub-channels.
  • a heat exchanger according to a seventh aspect of the present invention is the heat exchanger according to any of the first through sixth aspects, wherein the first refrigerant and the second refrigerant are carbon dioxide.
  • the heat exchanger according to the first through seventh aspects of the present invention can be made more compact.
  • the manufacturing costs of the heat exchanger according to the fourth through sixth aspects of the present invention can be limited.
  • FIG. 1 is a schematic diagram of an air-conditioning device of an embodiment of the present invention
  • FIG. 2 is a front view of an economizer heat exchanger of the embodiment of the present invention.
  • FIG. 3 is a top view of the economizer heat exchanger of the embodiment of the present invention.
  • FIG. 4 is a cross-sectional view in a horizontal direction of the economizer heat exchanger of the embodiment of the present invention.
  • NG. 5 is a cross-sectional view in a horizontal direction of the economizer heat exchanger of the embodiment of the present invention.
  • FIG. 6 is a cross-sectional view in a vertical direction of the economizer heat exchanger of the embodiment of the present invention.
  • FIG. 7 is a cross-sectional view in a vertical direction of the economizer heat exchanger of the embodiment of the present invention.
  • FIG. 8 is an exterior view of a channel-forming member of the embodiment of the present invention.
  • FIG. 9 is a cross-sectional view of a first flat porous tube and a second flat porous tube of the embodiment of the present invention.
  • FIG. 10 is a front view of a tube-adhering member of the embodiment of the present invention.
  • FIG. 11 is a front view of a tube-immobilizing member of the embodiment of the present invention.
  • FIG. 12 is a front view of a spacer member of the embodiment of the present invention.
  • FIG. 13 is a drawing showing flow of a refrigerant within the economizer heat exchanger of the embodiment of the present invention.
  • FIG. 14 is an exterior view of a header and flat porous tubes of the economizer heat exchanger of the embodiment of the present invention.
  • FIG. 15 is an exterior view of a header and flat porous tubes of a conventional refrigerant-refrigerant heat exchanger.
  • FIG. 1 is a schematic diagram of an air-conditioning device 1 that serves as an example of a refrigerating device provided with a heat exchanger according to the present invention.
  • the air-conditioning device 1 has a refrigerant circuit 10 configured so as to allow air-cooling operations, uses carbon dioxide or another refrigerant active in the supercritical region, and performs a two-stage compression refrigeration cycle.
  • the refrigerant circuit 10 primarily has a compression mechanism 2 , a heat-source-side heat exchanger 3 , an expansion mechanism 4 , a usage-side heat exchanger 5 , and an economizer heat exchanger 6 . These components will be described next.
  • the compression mechanism 2 compresses refrigerant from a low pressure in the refrigeration cycle to a high pressure in the refrigeration cycle.
  • the compression mechanism 2 is a compressor 21 that uses two compression elements and compresses the refrigerant in two stages.
  • the compressor 21 has an airtight structure that accommodates a compression-element-driving motor 21 b, a drive shaft 21 c, a first-stage compression element 2 c, and a second-stage compression element 2 d in a casing 21 a .
  • the compression-element-driving motor 21 b is linked to the drive shaft 21 c.
  • the drive shaft 21 c is linked to the first-stage compression element 2 c and the second-stage compression element 2 d.
  • the compressor 21 has a uniaxial two-stage compression structure in which the compression-element-driving motor 21 b drives the first-stage compression element 2 c and the second-stage compression element 2 d via the single drive shaft 21 c.
  • the compressor 21 takes in low-pressure refrigerant from an intake tube 2 a, uses the first-stage compression element 2 c to compress the refrigerant taken in, and then discharges compressed intermediate-pressure refrigerant to an intermediate-pressure-refrigerant tube 7 .
  • the compressor 21 then takes in the intermediate-pressure refrigerant discharged to the intermediate-pressure-refrigerant tube 7 , uses the second-stage compression element 2 d to compress the refrigerant taken in, and then discharges the compressed high-pressure refrigerant to a discharge tube 2 b.
  • the heat-source-side heat exchanger 3 is a radiator for cooling the high-pressure refrigerant compressed by the compression mechanism 2 .
  • the heat-source-side heat exchanger 3 causes heat exchange between air, which acts as a coolant source, and the refrigerant flowing within the heat-source-side heat exchanger 3 .
  • the heat-source-side heat exchanger 3 is connected to the compression mechanism 2 via a first high-pressure refrigerant tube 3 a and the discharge tube 2 b.
  • the first high-pressure refrigerant tube 3 a is connected to an inlet of the heat-source-side heat exchanger 3 and to the discharge tube 2 b .
  • the heat-source-side heat exchanger 3 is connected to the economizer heat exchanger 6 and an injection part 8 , which will be described hereinafter, via a second high-pressure refrigerant tube 3 b.
  • the second high-pressure refrigerant tube 3 b is connected to an outlet of the heat-source-side heat exchanger 3 , to an inlet of the economizer heat exchanger 6 (an inlet of a channel for refrigerant sent from the heat-source-side heat exchanger 3 to the expansion mechanism 4 ) and to an inlet of the injection part 8 (an inlet of a channel for refrigerant diverted from the second high-pressure refrigerant tube 3 b ).
  • the expansion mechanism 4 decompresses the high-pressure refrigerant, which was cooled in the heat-source-side heat exchanger 3 and the economizer heat exchanger 6 , to near the low pressure of the refrigeration cycle before sending the refrigerant to the usage-side heat exchanger 5 .
  • the expansion mechanism 4 is, e.g., an electrically operated expansion valve.
  • the expansion mechanism 4 is connected to the economizer heat exchanger 6 via a third high-pressure refrigerant tube 3 c.
  • the third high-pressure refrigerant tube 3 c is connected to an outlet of the economizer heat exchanger 6 (an outlet of a channel for refrigerant sent from the heat-source-side heat exchanger 3 to the expansion mechanism 4 ) and to an inlet of the expansion mechanism 4 .
  • the expansion mechanism 4 is connected to the usage-side heat exchanger 5 via a first low-pressure refrigerant tube 5 a.
  • the first low-pressure refrigerant tube 5 a is connected to an outlet of the expansion mechanism 4 and to an inlet of the usage-side heat exchanger 5 .
  • the usage-side heat exchanger 5 is an evaporator for heating and evaporating the low-pressure refrigerant that was decompressed by the expansion mechanism 4 .
  • the usage-side heat exchanger 5 causes heat exchange between air, which serves as a heat source, and the refrigerant flowing within the usage-side heat exchanger 5 .
  • the usage-side heat exchanger 5 is connected to the expansion mechanism 4 via the first low-pressure refrigerant tube 5 a .
  • the usage-side heat exchanger 5 is connected to the compression mechanism 2 via a second low-pressure refrigerant tube 5 b.
  • the second low-pressure refrigerant tube 5 b is connected to an outlet of the usage-side heat exchanger 5 and to the intake tube 2 a.
  • the economizer heat exchanger 6 causes heat exchange between the high-pressure refrigerant sent from the heat-source-side heat exchanger 3 to the expansion mechanism 4 and the intermediate-pressure refrigerant flowing through the injection part 8 .
  • the injection part 8 diverts the high-pressure refrigerant flowing from the heat-source-side heat exchanger 3 to the expansion mechanism 4 and returns the refrigerant to the inlet of the second-stage compression element 2 d. Specifically, the injection part 8 diverts refrigerant from the second high-pressure refrigerant tube 3 b and returns the refrigerant to the intermediate-pressure-refrigerant tube 7 .
  • the injection part 8 comprises a first injection tube 8 a and a second injection tube 8 b.
  • the first injection tube 8 a connects the second high-pressure refrigerant tube 3 b with an inlet of the economizer heat exchanger 6 (an inlet of a channel for refrigerant diverted from the second high-pressure refrigerant tube 3 b ).
  • the second injection tube 8 b connects an outlet of the economizer heat exchanger 6 (an outlet of a channel for refrigerant diverted from the second high-pressure refrigerant tube 3 b ) with the intermediate-pressure-refrigerant tube 7 .
  • An injection valve 8 c that functions as a return valve having a controllable opening degree is provided to the first injection tube 8 a.
  • the injection valve 8 c is, e.g., an electrically operated expansion valve.
  • the injection valve 8 c decompresses the high-pressure refrigerant diverted from the second high-pressure refrigerant tube 3 b to around the intermediate pressure of the refrigerant flowing within the intermediate-pressure-refrigerant tube 7
  • the high-pressure refrigerant sent from the heat-source-side heat exchanger 3 to the expansion mechanism 4 is cooled by heat exchange with the intermediate-pressure refrigerant flowing through the injection part 8 .
  • the intermediate-pressure refrigerant flowing through the injection part 8 is heated and evaporated by heat exchange with the high-pressure refrigerant, which is sent from the heat-source-side heat exchanger 3 to the expansion mechanism 4 , while temporarily flowing in a gas-liquid two-phase state.
  • the evaporated intermediate-pressure refrigerant merges with the refrigerant flowing through the intermediate-pressure-refrigerant tube 7 .
  • the action of the air-conditioning device I during air-cooling operations will be described next on the basis of the flow of refrigerant circulating through the refrigerant circuit 10 .
  • the refrigerant at the low pressure of the refrigeration cycle is taken in from the intake tube 2 a to the compression mechanism 2 .
  • the low-pressure refrigerant taken in to the compression mechanism 2 is compressed to the intermediate pressure of the refrigeration cycle by the first-stage compression element 2 c and then discharged to the intermediate-pressure-refrigerant tube 7 , in the intermediate-pressure-refrigerant tube 7 , the intermediate-pressure refrigerant discharged from the first-stage compression element 2 c is merged with the intermediate-pressure refrigerant returned from the second injection tube 8 b .
  • the merged intermediate-pressure refrigerant is taken in to the second-stage compression element 2 d and compressed to the high pressure of the refrigeration cycle by the second-stage compression element 2 d.
  • the compressed high-pressure refrigerant is discharged from the compression mechanism 2 to the discharge tube 2 b.
  • the high-pressure refrigerant discharged from the compression mechanism 2 is sent through the first high-pressure refrigerant tube 3 a to the heat-source-side heat exchanger 3 .
  • the high-pressure refrigerant sent to the heat-source-side heat exchanger 3 is subjected to heat exchange with outside air and cooled by the heat-source-side heat exchanger 3 .
  • a portion of the high-pressure refrigerant cooled by the heat-source-side heat exchanger 3 is diverted in the second high-pressure refrigerant tube 3 b to the first injection tube 8 a.
  • the high-pressure refrigerant diverted to the first injection tube 8 a is decompressed to around the intermediate pressure of the refrigeration cycle by the injection valve 8 c and is then sent to the economizer heat exchanger 6 . Meanwhile, the high-pressure refrigerant subsequent to the diversion to the first injection tube 8 a (i.e., refrigerant flowing through the second high-pressure refrigerant tube 3 b ) is sent to the economizer heat exchanger 6 .
  • the high-pressure refrigerant from the second high-pressure refrigerant tube 3 b is subjected to heat exchange with the intermediate-pressure refrigerant from the first injection tube 8 a and cooled. Meanwhile, the intermediate-pressure refrigerant from the first injection tube 8 a is subjected to heat exchange with the high-pressure refrigerant from the second high-pressure refrigerant tube 3 b, heated, and returned through second injection tube 8 b to the intermediate-pressure-refrigerant tube 7 .
  • the high-pressure refrigerant cooled in the economizer heat exchanger 6 is sent through the third high-pressure refrigerant tube 3 c to the expansion mechanism 4 .
  • the high-pressure refrigerant sent to the expansion mechanism 4 is decompressed by the expansion mechanism 4 , enters a gas-liquid two-phase state at the low pressure of the refrigeration cycle, and is sent through the first low-pressure refrigerant tube 5 a to the usage-side heat exchanger 5 .
  • the low-pressure, gas-liquid two-phase refrigerant sent to the usage-side heat exchanger 5 is subjected to heat exchange with outside air, heated, and evaporated by the usage-side heat exchanger 5 .
  • the low-pressure refrigerant that was heated and evaporated by the usage-side heat exchanger 5 is once again taken in to the compression mechanism 2 through the second low-pressure refrigerant tube 5 b and the intake tube 2 a.
  • the air-conditioning device l thus circulates refrigerant within the refrigerant circuit 10 and performs air-cooling operations.
  • the economizer heat exchanger 6 in the present embodiment is a heat exchanger according to the present invention.
  • FIG. 2 is a front view of the economizer heat exchanger 6 .
  • FIG. 3 is a top view of the economizer heat exchanger 6 .
  • FIG. 2 is a front view from the direction of an arrow II shown in FIG. 3 .
  • FIG. 3 is a top view from the direction of an arrow III shown in FIG. 2 .
  • FIGS. 4 and 5 are cross-sectional views in a horizontal direction cut along cut line IV-IV and cut line V-V, respectively, in FIG. 2 .
  • the economizer heat exchanger 6 primarily comprises a pair of headers 61 , a plurality of first flat porous tubes 64 a, and a plurality of second flat porous tubes 64 b. These components will be described next.
  • the header 61 is positioned so that the longitudinal direction thereof proceeds along the vertical direction.
  • the header 61 has a channel-forming member 62 . and a tube-connecting member 63 .
  • the channel-forming member 62 has, therein, a first primary channel 62 a 1 , a second primary channel 62 a 2 , a plurality of first linking channels 62 b 1 , and a plurality of second linking channels 62 b 2 .
  • the first linking channels 62 b 1 and the second linking channels 62 b 2 are communicated with the first primary channel 62 a 1 and the second primary channel 62 a 2 , respectively, as shown in FIGS. 4 through 7 .
  • FIG. 8 is an exterior view of the channel-forming member 62 seen from an arrow VIII in FIG. 4 .
  • the first linking channels 62 b 1 and the second linking channels 62 b 2 open in alternation along the longitudinal direction of the channel-forming member 62 on an opening surface 62 s of the channel-forming member 62 , as shown in FIG. 8 .
  • the first linking channels 62 b 1 open on the opening surface 62 s along the first primary channel 62 a 1
  • the second linking channels 62 b 2 open on the opening surface 62 s along the second (primary channel 62 a 2 .
  • the high-pressure refrigerant from the second high-pressure refrigerant tube 3 b flows in the first primary channel 62 a 1 and the first linking channels 62 b 1 .
  • the intermediate-pressure refrigerant from the first injection tube 8 a flows in the second (primary channel 62 a 2 and the second linking channels 62 b 2 .
  • Refrigerant in the first primary channel 62 a flows in the vertical direction, and refrigerant in the first linking channels 62 b 1 is diverted from the first primary channel 62 a 1 and flows in a horizontal direction.
  • Refrigerant in the second primary channel 62 a 2 flows in the vertical direction, and refrigerant in the second linking channels 62 b 2 is diverted from the second primary channel 62 a 2 and flows in the horizontal direction.
  • the tube-connecting member 63 connects the channel-forming member 62 , the first flat porous tubes 64 a, and the second flat porous tubes 64 b.
  • the detailed configuration of the tube-connecting member 63 will be described hereinafter.
  • the first flat porous tubes 64 a have a plurality of first refrigerant-channel holes 65 a .
  • the first flat porous tubes 64 a are positioned so that the alignment direction of the first refrigerant-channel holes 65 a is in the horizontal direction, i.e., so that the normal to the flat surface indicates the vertical direction.
  • the second flat porous tubes 64 b have a plurality of second refrigerant-channel holes 65 b.
  • the second flat porous tubes 64 b are positioned so that the alignment direction of the second refrigerant-channel holes 65 b is in the horizontal direction, i.e., so that the normal to the flat surface indicates the vertical direction.
  • Pairs of a single one of the first flat porous tubes 64 a and a single one of the second flat porous tubes 64 b, which are brought into close contact at the flat surfaces, are positioned at a plurality of stages along the longitudinal direction of the header 61 in the present embodiment, as shown in FIG. 2 . Both end parts of the first flat porous tubes 64 a and the second fiat porous tubes 64 b are linked respectively to the pair of the headers 61 .
  • FIG. 9 is a cross-sectional view of the first flat porous tubes 64 a and the second flat porous tubes 64 b cut along a cut line IX-IX in FIG. 3 .
  • the alignment direction of the first refrigerant-channel holes 65 a of the first flat porous tubes 64 a and the alignment direction of the second refrigerant-channel holes 65 b of the second flat porous tubes 64 b are perpendicular to the longitudinal direction of the headers 61 , as shown in FIG. 9 .
  • the tube-connecting member 63 is configured from a tube-adhering member 63 a, a tube-immobilizing member 63 b, and a spacer member 63 c, as shown in FIGS. 4 through 7 .
  • FIG. 10 is a front view of the tube-adhering member 63 a.
  • FIG. 11 is a front view of the tube-immobilizing member 63 b.
  • FIG. 12 is a front view of the spacer member 63 c.
  • FIGS. 10 through 12 are all external views from an arrow VIII in FIG. 4 .
  • the tube-adhering member 63 a has a U-shaped cross-section when viewed along the vertical direction, as shown in FIGS. 4 through 7 .
  • a plurality of flat-tube-fitting insertion holes 63 a 1 are positioned in the vertical direction, as shown in FIG. 10 .
  • End parts of the first fiat porous tubes 64 a and the second flat porous tubes 64 b are fit into the respective flat-tube-fitting insertion holes 63 a 1 .
  • the flat-tube-fitting insertion holes 63 a 1 immobilize the end parts of the first flat porous tubes 64 a and the second fiat porous tubes 64 b.
  • the tube-immobilizing member 63 b is a plate-shaped member positioned in close contact with the tube-adhering member 63 a and the spacer member 63 c in a space surrounded by the tube-adhering member 63 a and the channel-forming member 62 , as shown in FIGS. 4 through 7 .
  • a plurality of flat-tube-fastening holes 63 b 1 are positioned in the vertical direction in the tube-immobilizing member 63 b, as shown in FIG. 11 .
  • the flat-tube-fastening holes 63 b 1 have two convex parts 63 b 2 at a center part in the horizontal direction.
  • the convex parts 63 b 2 immobilize the end parts of the first flat porous tubes 64 a and the second flat porous tubes 64 b.
  • the height of the convex parts 63 b 2 is less than the thickness of the first flat porous tubes 64 a and the second flat porous tubes 64 b.
  • the spacer member 63 c is a plate-shaped member positioned in close contact with the tube-immobilizing member 63 b and the opening surface 62 s of the channel-forming member 62 in a space surrounded by the tube-adhering member 63 a and the channel-forming member 62 , as shown in FIGS. 4 through 7 .
  • a plurality of spacer holes 63 c 1 are positioned in the vertical direction, as shown in FIG. 12 .
  • a portion of the end surface of the first flat porous tubes 64 a and the second flat porous tubes 64 b contacts the end surface of the spacer member 63 c, as shown in FIGS. 4 and 5 .
  • the height-wise positions of the first linking channels 62 b 1 and the second linking channels 62 b 2 that open on the opening surface 62 s of the channel-forming member 62 in the present embodiment are equivalent to the height-wise positions of the flat-tube-fitting insertion holes 63 a 1 , flat-tube-fastening holes 63 b 1 , and the spacer holes 63 c 1 .
  • the first refrigerant-channel holes 65 a and the second refrigerant-channel holes 65 b are thereby communicated with the first linking channels 62 b 1 and the second linking channels 62 b 2 , respectively, via the spacer holes 63 c 1 .
  • first sub-channels 62 c 1 are spaces that, along with the first linking channels 62 b 1 , allow the first refrigerant-channel holes 65 a to be communicated with the first primary channel 62 a 1 .
  • the second sub-channels 62 c 2 are spaces that, along with the second linking channels 62 b 2 , allow the second refrigerant-channel holes 65 b to be communicated with the second primary channel 62 a 2 .
  • Heat exchange in the economizer heat exchanger 6 will be described with reference to FIG. 13 .
  • the high-pressure refrigerant that is cooled by the heat-source-side heat exchanger 3 and made to flow through the second high-pressure refrigerant tube 3 b is provided to the first primary channel 62 a 1 within one of the headers 61 of the economizer heat exchanger 6 .
  • the high-pressure refrigerant flowing through the first primary channel 62 a 1 is split into the first sub-channels 62 c 1 via the first linking channels 62 b 1 and flows into the first refrigerant-channel holes 65 a of the first flat porous tubes 64 a.
  • the intermediate-pressure refrigerant which was diverted from the second high-pressure refrigerant tube 3 b , decompressed by the injection valve 8 c, and made to flow through the first injection tube 8 a, is supplied to the second (primary channel 62 a 2 within the header 61 on the opposite side from the header to which the high-pressure refrigerant is supplied.
  • the intermediate-pressure refrigerant flowing through the second primary channel 62 a 2 is split into the second sub-channels 62 c 2 via the second linking channels 62 b 2 and flows into the second refrigerant-channel holes 65 b of the second flat porous tubes 64 b.
  • the high-pressure refrigerant flowing through the first refrigerant-channel holes 65 a of the first flat porous tubes 64 a exchanges heat with the intermediate-pressure refrigerant O flowing through the second refrigerant-channel holes 65 b of the second flat porous tubes 64 b that are in close contact with the first flat porous tubes 64 a.
  • the direction of flow of the high-pressure refrigerant in the first refrigerant-channel holes 65 a is opposite from the direction of flow of the intermediate-pressure refrigerant in the second refrigerant-channel holes 65 b , as shown in FIG. 13 .
  • the high-pressure refrigerant that has passed through the first refrigerant-channel holes 65 a and been subjected to heat exchange flows into the first primary channel 62 a 1 within the header 61 on the opposite side. Finally, the high-pressure refrigerant is sent from the first primary channel 62 a 1 to the third high-pressure refrigerant tube 3 c. Meanwhile, the intermediate-pressure refrigerant that has passed through the second refrigerant-channel holes 65 b and been subjected to heat exchange flows into the second primary channel 62 a 2 within the header 61 on the opposite side. Finally, the intermediate-pressure refrigerant is sent from the second primary channel 62 a 2 to the second injection tube 8 b.
  • the high-pressure refrigerant that flows through the first primary channel 62 a 1 of the header 61 is split into the first sub-channels 62 c 1 and then flows into the first refrigerant-channel holes 65 a of the first flat porous tithes 64 a.
  • the intermediate-pressure refrigerant that flows through the second primary channel 62 a 2 of the header 61 is split into the second sub-channels 62 c 2 and then flows into the second refrigerant-channel holes 65 b of the second flat porous tubes 64 b.
  • the first sub-channels 62 c 1 and the second sub-channels 62 c 2 are spaces formed by the tube-connecting member 63 .
  • the first flat porous tubes 64 a and the second flat porous tubes 64 b are linked to the headers 61 on that the alignment direction of the first refrigerant-channel holes 65 a of the first flat porous tubes 64 a and the alignment direction of the second refrigerant-channel holes 65 b of the second flat porous tubes 64 b are perpendicular to the longitudinal direction of the headers 61 , as shown in FIG. 14 .
  • the tube-connecting member 63 that forms the first sub-channels 62 c 1 and the second sub-channels 62 c 2 is used in the present embodiment, whereby the first flat porous tubes 64 a and the second flat porous tubes 64 b can be linked to the headers 61 , as shown in FIG. 14 .
  • a plurality of flat porous tubes are linked to headers so that the alignment direction of refrigerant-channel holes within the flat porous tubes proceeds along a longitudinal direction of the headers.
  • the headers in this heat exchanger must be long in order to link the plurality of the flat porous tubes to the headers, and this heat exchanger is therefore not readily made more compact.
  • the economizer heat exchanger 6 of the present embodiment as shown in FIG. 14 , the plurality of the flat porous tubes 64 a, 64 b can be efficiently linked to the headers 61 , and therefore the length of the header 61 can be reduced in comparison to the conventional heat exchanger shown in FIG. 15 .
  • the economizer heat exchanger 6 of the present embodiment can therefore readily be made more compact.
  • the economizer heat exchanger 6 was described as the heat exchanger according to the present invention in the present embodiment, but the heat exchanger according to the present invention can be applied generally to heat exchangers for causing heat exchange between a refrigerant and a refrigerant.
  • the first flat porous tubes 64 a and the second flat porous tubes 64 b are linked to the headers 61 so that the alignment directions of the first refrigerant-channel holes 65 a and the second refrigerant-channel holes 65 b are perpendicular to the longitudinal direction of the header 61 , but it may be applicable as long as the alignment directions of the first refrigerant-channel holes 65 a and the second refrigerant-channel holes 65 b intersect the longitudinal direction of the header 61 .
  • the plurality of the flat porous tubes 64 a, 64 b can be efficiently linked to the headers 61 in comparison to a conventional heat exchanger such as shown in FIG. 15 , and therefore the length of the headers 61 can be reduced.
  • the economizer heat exchanger 6 of the present modification can therefore also be readily made more compact.
  • the heat exchanger according to the present invention can be readily made more compact.
  • Patent Document 1 Japanese Laid-Open Patent Application No 2007-163004

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Geometry (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
  • Details Of Heat-Exchange And Heat-Transfer (AREA)
US14/234,563 2011-07-28 2012-07-19 Heat exchanger Abandoned US20140174703A1 (en)

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JP2011165034A JP5287949B2 (ja) 2011-07-28 2011-07-28 熱交換器
JP2011-165034 2011-07-28
PCT/JP2012/068296 WO2013015186A1 (fr) 2011-07-28 2012-07-19 Appareil échangeur de chaleur

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JP (1) JP5287949B2 (fr)
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US20140262143A1 (en) * 2013-03-15 2014-09-18 Rodney Koch Single exchanger hvac unit and power machines using the same
US20170234587A1 (en) * 2014-10-16 2017-08-17 Daikin Industries, Ltd. Refrigerant evaporator
US20180238627A1 (en) * 2017-02-22 2018-08-23 Hamilton Sundstrand Corporation Heat exchangers with installation flexibility
EP3405735A4 (fr) * 2016-01-21 2019-09-25 Etalim Inc. Appareil et système d'échange de chaleur avec un fluide
US20200217591A1 (en) * 2019-01-08 2020-07-09 Meggitt Aerospace Limited Heat exchangers and methods of making the same
EP3722720A1 (fr) * 2019-04-09 2020-10-14 Pfannenberg GmbH Agencement d'échangeur de chaleur et procédé de fabrication d'un agencement d'échangeur de chaleur
US20210270498A1 (en) * 2019-06-12 2021-09-02 Carrier Corporation Two stage single gas cooler hvac cycle
US20230052183A1 (en) * 2021-08-10 2023-02-16 Mahle International Gmbh Heat exchanger
US20230116443A1 (en) * 2021-10-12 2023-04-13 Hamilton Sundstrand Corporation Header for high-pressure heat exchanger
US11725889B1 (en) * 2019-02-26 2023-08-15 National Technology & Engineering Solutions Of Sandia, Llc Refractory high entropy alloy compact heat exchanger
US11802736B2 (en) 2020-07-29 2023-10-31 Hamilton Sundstrand Corporation Annular heat exchanger
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JP6889618B2 (ja) * 2017-06-02 2021-06-18 サンデンホールディングス株式会社 熱交換器
CN111936815B (zh) * 2018-04-05 2022-02-11 三菱电机株式会社 分配器以及热交换器
EP4354069A1 (fr) * 2021-06-07 2024-04-17 Mitsubishi Electric Corporation Échangeur de chaleur et unité extérieure

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US11879691B2 (en) * 2017-06-12 2024-01-23 General Electric Company Counter-flow heat exchanger
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US11725889B1 (en) * 2019-02-26 2023-08-15 National Technology & Engineering Solutions Of Sandia, Llc Refractory high entropy alloy compact heat exchanger
EP3722720A1 (fr) * 2019-04-09 2020-10-14 Pfannenberg GmbH Agencement d'échangeur de chaleur et procédé de fabrication d'un agencement d'échangeur de chaleur
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JP5287949B2 (ja) 2013-09-11
EP2738507A4 (fr) 2015-04-01
ES2731727T3 (es) 2019-11-18
EP2738507B1 (fr) 2019-03-27
WO2013015186A1 (fr) 2013-01-31
EP2738507A1 (fr) 2014-06-04
JP2013029244A (ja) 2013-02-07
CN103717989A (zh) 2014-04-09
CN103717989B (zh) 2016-08-31
TR201909098T4 (tr) 2019-07-22

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