WO2020022443A1 - Raccord - Google Patents

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Publication number
WO2020022443A1
WO2020022443A1 PCT/JP2019/029250 JP2019029250W WO2020022443A1 WO 2020022443 A1 WO2020022443 A1 WO 2020022443A1 JP 2019029250 W JP2019029250 W JP 2019029250W WO 2020022443 A1 WO2020022443 A1 WO 2020022443A1
Authority
WO
WIPO (PCT)
Prior art keywords
joint
refrigerant
main body
heat exchanger
tube
Prior art date
Application number
PCT/JP2019/029250
Other languages
English (en)
Japanese (ja)
Inventor
俊 吉岡
祥志 松本
智己 廣川
Original Assignee
ダイキン工業株式会社
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 ダイキン工業株式会社 filed Critical ダイキン工業株式会社
Priority to EP19841770.1A priority Critical patent/EP3828490B1/fr
Publication of WO2020022443A1 publication Critical patent/WO2020022443A1/fr

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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
    • F25B9/00—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point
    • F25B9/002—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point characterised by the refrigerant
    • F25B9/008—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point characterised by the refrigerant the refrigerant being carbon dioxide
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F1/00—Room units for air-conditioning, e.g. separate or self-contained units or units receiving primary air from a central station
    • F24F1/06—Separate outdoor units, e.g. outdoor unit to be linked to a separate room comprising a compressor and a heat exchanger
    • F24F1/14—Heat exchangers specially adapted for separate outdoor units
    • F24F1/16—Arrangement or mounting thereof
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F1/00—Room units for air-conditioning, e.g. separate or self-contained units or units receiving primary air from a central station
    • F24F1/06—Separate outdoor units, e.g. outdoor unit to be linked to a separate room comprising a compressor and a heat exchanger
    • F24F1/14—Heat exchangers specially adapted for separate outdoor units
    • F24F1/18—Heat exchangers specially adapted for separate outdoor units characterised by their shape
    • 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
    • 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
    • F25B31/00—Compressor arrangements
    • F25B31/002—Lubrication
    • F25B31/004—Lubrication oil recirculating arrangements
    • 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
    • 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
    • F25B41/00—Fluid-circulation arrangements
    • 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
    • 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
    • F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
    • F28F9/26—Arrangements for connecting different sections of heat-exchange elements, e.g. of 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
    • F28F9/26—Arrangements for connecting different sections of heat-exchange elements, e.g. of radiators
    • F28F9/262—Arrangements for connecting different sections of heat-exchange elements, e.g. of radiators for radiators
    • F28F9/268—Arrangements for connecting different sections of heat-exchange elements, e.g. of radiators for radiators by permanent joints, e.g. by welding
    • 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
    • F25B2313/00—Compression machines, plants or systems with reversible cycle not otherwise provided for
    • F25B2313/025—Compression machines, plants or systems with reversible cycle not otherwise provided for using multiple outdoor units
    • F25B2313/0252—Compression machines, plants or systems with reversible cycle not otherwise provided for using multiple outdoor units with bypasses
    • 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
    • F25B2313/00—Compression machines, plants or systems with reversible cycle not otherwise provided for
    • F25B2313/025—Compression machines, plants or systems with reversible cycle not otherwise provided for using multiple outdoor units
    • F25B2313/0253—Compression machines, plants or systems with reversible cycle not otherwise provided for using multiple outdoor units in parallel arrangements
    • 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
    • F25B2600/2501—Bypass valves
    • 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
    • F28D21/00—Heat-exchange apparatus not covered by any of the groups F28D1/00 - F28D20/00
    • F28D2021/0019—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for
    • F28D2021/0068—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for for refrigerant cycles
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F2225/00—Reinforcing means
    • F28F2225/04—Reinforcing means for conduits

Definitions

  • a joint that connects a multi-hole flat tube and a circular tube, and allows carbon dioxide refrigerant to pass through.
  • a multi-well flat tube In a refrigeration system using carbon dioxide as the working fluid, a multi-well flat tube is used. On the other hand, when a multi-hole flat tube is used for a refrigerating apparatus, a multi-hole flat tube and a circular tube are sometimes connected, and a joint for connecting these is proposed (for example, Patent Document 1 (WO2014 / 199514)). )).).
  • the joint according to the first aspect is a joint through which a CO 2 refrigerant passes.
  • the joint connects the multi-hole flat tube and the circular tube.
  • the multi-hole flat tube has a thickness T and a width W. W> T.
  • the width of the multi-hole flat tube is a direction in which a plurality of holes are arranged.
  • the thickness direction and the width direction of the multi-hole flat tube are defined as the longitudinal direction and the lateral direction of the joint, respectively.
  • the joint includes a first connection portion and a main body.
  • the first connecting portion covers the outside of the end of the multi-hole flat tube.
  • the main body is continuous from the first connection.
  • the inner diameter of the main body in the vertical direction is larger than the inner diameter of the first connection portion in the vertical direction.
  • the inner diameter in the longitudinal direction of the main body is larger than the inner diameter in the longitudinal direction of the first connecting portion, so that oil stays near the multi-hole flat tube on the inner peripheral surface of the first connecting portion. Hateful.
  • the joint of the second aspect is the joint of the first aspect, in which the main body portion has a region in which the inner diameter in the vertical direction gradually increases as the distance from the first connection portion increases.
  • the main body portion gradually increases in inner diameter in the vertical direction as the distance from the first connection portion increases, so that the inner peripheral surface of the first connection portion is closer to the multi-hole flat tube. It is difficult for oil to stay.
  • the joint of the third aspect is the joint of the first aspect or the second aspect, and further includes a second connection portion.
  • the second connecting portion is continuous from the main body.
  • the second connecting portion covers the outside of the end of the circular tube.
  • a joint according to a fourth aspect is the joint according to the third aspect, wherein the first connection portion is formed by processing one end of a circular pipe.
  • the joint according to the fourth aspect can be manufactured by processing a circular pipe, so that the manufacturing cost is low.
  • the joint according to the fifth aspect is the joint according to the third aspect or the fourth aspect, wherein the thickness of the pipe of the joint is greater than the thickness of the circular pipe.
  • the circular pipe is intended to be a circular pipe to which the joint is connected.
  • the joint according to the sixth aspect is the joint according to any one of the first to fifth aspects, and further includes a reinforcing portion.
  • the reinforcing portion reinforces the strength of the joint.
  • the joint of the sixth aspect uses the reinforcing portion, the strength is easily maintained even when the refrigerant pressure of the main body portion is high.
  • the joint according to the seventh aspect is any one of the joints according to the first aspect to the sixth aspect, and is formed by bonding two or more members.
  • the joint according to the eighth aspect is the joint according to the first aspect or the second aspect, wherein the main body is a part of a circular pipe.
  • the joint according to the ninth aspect is the joint according to any one of the first to eighth aspects, and further has a flat portion that is continuous from the main body and does not form a refrigerant passage.
  • a joint according to a tenth aspect is the joint according to the sixth aspect, wherein the reinforcing portion extends in the coolant flow path in the vertical direction.
  • the reinforcing portion is arranged to extend in the longitudinal direction in the refrigerant flow path, the expansion in the longitudinal direction inside the main body portion can be suppressed.
  • a joint according to an eleventh aspect is the joint according to the sixth aspect, wherein the reinforcing portion is disposed outside the coolant flow path and in contact with the outer surface of the main body.
  • the joint of the twelfth aspect is the joint of the sixth aspect, and further has a flat portion that is continuous from the main body and does not form a passage for the refrigerant.
  • the reinforcing portion is disposed outside the coolant flow path in contact with the outer surface of the main body 302 and the surface of the flat portion.
  • the heat exchanger of the present disclosure includes the joint according to any one of the first to twelfth aspects and a multi-hole flat tube.
  • the multi-hole flat tube is connected to the joint.
  • the air conditioner of the present disclosure is an air conditioner provided with a heat exchanger.
  • FIG. 2 is a refrigerant circuit diagram of the refrigeration apparatus 1 according to the first embodiment.
  • FIG. 3 is a side view of the heat exchanger 4 according to the first embodiment in the vicinity of the folded portion 33.
  • FIG. 4 is a longitudinal sectional view of the joint 34 according to the first embodiment.
  • FIG. 3 is a cross-sectional view of the joint 34 according to the first embodiment. Sectional drawing in section S of the heat exchanger tube 30 in the heat exchanger of modification 2A. Sectional drawing in section S of heat exchanger tube 30 in heat exchanger 4 of a 2nd embodiment.
  • FIG. 14 is an external perspective view of a joint 34c and a reinforcing portion 304c according to a third embodiment of the third embodiment.
  • FIG. 18 is an external perspective view of a joint 34d and a reinforcing portion 304d according to a fourth embodiment of the third embodiment.
  • FIG. 1 shows a refrigerant circuit configuration of refrigeration apparatus 1 of the first embodiment.
  • the refrigeration apparatus 1 of the present embodiment is an apparatus that performs a two-stage compression refrigeration cycle using carbon dioxide that is a refrigerant that operates in a supercritical region.
  • the refrigerating apparatus 1 of the present embodiment can be used for an air conditioner for performing cooling and heating, a water heater and the like, and the like.
  • the refrigerant circuit of the refrigeration apparatus 1 of the present embodiment mainly includes a compressor 2, a four-way switching valve 3, a heat source side heat exchanger 4, an expansion mechanism 5, a use side heat exchanger 6, and an intercooler 7.
  • a compressor 2 a compressor 2 a four-way switching valve 3
  • a heat source side heat exchanger 4 an expansion mechanism 5 a use side heat exchanger 6, and an intercooler 7.
  • the compressor 2 is a two-stage compressor that compresses the refrigerant in two stages by the two compression elements 2c and 2d.
  • the compressor 2 sucks the refrigerant from the suction pipe 2a, compresses the sucked refrigerant by the first-stage compression element 2c, and discharges the compressed refrigerant to the intermediate refrigerant pipe 8.
  • the refrigerant discharged to the intermediate refrigerant pipe 8 is further drawn into the second stage compression element 2d, compressed, and discharged to the discharge pipe 2b.
  • the discharge pipe 2b is a refrigerant pipe for sending the refrigerant discharged from the compressor 2 to the four-way switching valve 3.
  • the discharge pipe 2b is provided with an oil separator 41 and a check valve 42.
  • the oil separator 41 separates refrigerant oil mixed with the refrigerant discharged from the compressor 2 from the refrigerant.
  • the separated oil is depressurized by the capillary tube 41c and returned to the suction pipe 2a of the compressor 2 via the oil return pipe 41b.
  • the refrigerating machine oil of the present embodiment is not particularly limited as long as it is a refrigerating machine oil used for a CO 2 refrigerant.
  • the refrigerator oil include PAG (polyalkylene glycols) and POE (polyol esters).
  • the four-way switching valve 3 can switch the flow of the refrigerant flowing through the path connecting the heat source side heat exchanger 4, the expansion mechanism 5, and the use side heat exchanger 6 between a forward direction and a reverse direction.
  • the refrigerant flowing out of the compressor 2 flows from the heat source side heat exchanger 4 to the use side heat exchanger 6.
  • the heat source side heat exchanger 4 is a radiator, and the use side heat exchanger 6 is an evaporator.
  • the refrigerant flowing out of the compressor 2 flows from the use side heat exchanger 6 to the heat source side heat exchanger 4.
  • the use side heat exchanger 6 is a radiator, and the heat source side heat exchanger 4 is an evaporator.
  • An intermediate cooler 7 and a check valve 15 are provided in the middle of the intermediate refrigerant pipe 8. That is, the refrigerant that has been compressed by the first-stage compression element 2c exchanges heat with air in the intercooler 7, and flows into the second-stage compression element 2d again.
  • the intermediate refrigerant pipe 8 is provided with an intermediate cooler bypass pipe 9 so as to bypass the intermediate cooler 7. That is, the refrigerant flowing through the first-stage compression element 2c and the intercooler bypass pipe 9 flows into the second-stage compression element 2d without passing through the intercooler 7.
  • the flow of the refrigerant to the intercooler 7 or the flow of the refrigerant to the intercooler bypass pipe 9 is switched by the on-off valves 11 and 12.
  • a refrigerant flows through the intermediate cooler 7, and conversely, when the use-side heat exchanger 6 is used as a radiator, the intermediate cooling is used. It controls so that a refrigerant
  • coolant may flow into the container bypass pipe 9. That is, the use of the intercooler 7 is basically for cooling.
  • the refrigerating apparatus 1 of the present embodiment uses a two-stage compression compressor, but the same applies when two compressors are used. Further, a compressor having three or more stages or a compression mechanism may be used.
  • the outdoor unit 10 houses the fan 40, the compressor 2, the heat source side heat exchanger 4, the intercooler 7, the expansion mechanism 5, the four-way switching valve 3, and the oil separator 41 in the casing 20.
  • FIG. 2 is an external perspective view of the outdoor unit 10
  • FIG. 3A is a perspective view of a part of the heat source side heat exchanger 4.
  • the heat source side heat exchanger 4 of the present embodiment is disposed on three inner sides of the casing 20 of the outdoor unit 10, as shown in FIG.
  • the fan 40 rotates, air around the casing 20 is taken in from three sides and passes through the heat source side heat exchanger 4.
  • the air that has entered the casing 20 passes through the fan 40 and is blown out upward from the upper surface of the casing 20. Therefore, the outdoor unit 10 of the present embodiment is a top blow type. The air exchanges heat with the refrigerant while passing through the heat exchanger 4 to be heated or cooled.
  • the heat exchanger 4 includes a heat transfer tube 30 through which a refrigerant flows, and metal fins 50 that promote heat exchange between the refrigerant and air.
  • the heat transfer tube 30 of the present embodiment is a multi-hole flat tube. In the multi-hole flat tube, a plurality of holes through which the refrigerant flows are arranged in the width direction.
  • the refrigerant is introduced into the heat transfer tube 30 from outside the heat exchanger 4 at the first end 4a.
  • the refrigerant flows from the first end 4a to three sides of the heat transfer tube 30 that is bent at 90 degrees at two locations, and reaches the second end 4b.
  • the flow direction is reversed by 180 °, flows again on the three side surfaces, and returns to the first end 4a.
  • the refrigerant flows out of the heat exchanger 4 from the heat transfer tube 30 at the first end 4a.
  • the heat transfer tube forming the refrigerant flow path from the first end 4a to the second end 4b is referred to as a first heat transfer tube 30a, and the heat transfer tube through which the refrigerant flows in the opposite direction is referred to as a second heat transfer tube 30b. .
  • the heat transfer tubes 30 are arranged in two rows with respect to the flow of air. In each row, the first heat transfer tubes 30a and the second heat transfer tubes 30b are alternately arranged vertically.
  • the direction of the flow of the refrigerant in the heat exchanger 4 is basically described in the case where the refrigerant is used as a radiator. When used in an evaporator, the direction of the refrigerant is reversed.
  • FIG. 4 is a longitudinal sectional view of the folded portion 33 of the refrigerant.
  • a portion near the second end 4b of the first heat transfer tube 30a is referred to as a first straight portion 31
  • a portion near the second end 4b of the second heat transfer tube 30b is referred to as a second straight portion 32.
  • the folded portion 33 reverses the direction of the refrigerant flowing through the first straight portion 31 of the heat transfer tube 30 (the multi-hole flat tube 300), and flows the coolant to the second straight portion 32 below the first straight portion 31.
  • the folded portion 33 is formed by using two joints 34a and 34b and a U-shaped tube 350.
  • the joints 34a and 34b connect the heat transfer tube 30 and the U-shaped tube 350.
  • the heat transfer tube 30 may be a multi-hole flat tube or a circular tube, and is not particularly limited.
  • a multi-hole flat tube 300 is used.
  • the multi-hole flat tube has high heat transfer performance between the refrigerant and the heat transfer tube.
  • a plurality of holes are arranged in a line, the arrangement direction of the holes of the multi-hole flat tube is defined as the width direction, and the width direction and the direction perpendicular to the flow direction of the refrigerant are defined as the thickness direction. Call. If the thickness (length in the thickness direction) of the multi-hole flat tube is T and the width (length in the width direction) is W, W> T.
  • the refrigerant that has flowed through the flow passages that are the plurality of holes of the multi-hole flat tube 300 is collected in one flow passage at the folded portion 33. Therefore, the homogenization of the refrigerant is measured in the folded portion 33, that is, the joints 34a and 34b and the U-shaped tube.
  • the thickness T of the heat transfer tube 30 in the vertical direction is 3 mm or less.
  • the vertical distance DP between the center of the first straight portion 31 and the center of the second straight portion 32 is 0 mm to 21 mm.
  • the first straight portion 31 and the second straight portion 32 sandwiching the folded portion 33 of the heat transfer tube 30 are arranged close to each other. Therefore, temperature unevenness of the passing air can be suppressed. Therefore, the heat exchange efficiency is also improved.
  • the vertical distance DP between the center of the first straight portion 31 and the center of the second straight portion 32 is not more than five times the thickness T of the heat transfer tube 30 in the vertical direction.
  • the first straight portion 31 and the second straight portion 32 sandwiching the folded portion 33 of the heat transfer tube 30 are arranged close to each other. Therefore, temperature unevenness of the passing air can be suppressed.
  • the heat exchanger 4 of the present embodiment further includes a plurality of fins 50.
  • the fins 50 are fixed to the heat transfer tubes 30 and promote heat exchange between the heat transfer tubes 30 and air.
  • the fin pitch of the plurality of fins 50 is at least 1.3 mm, preferably at least 1.4 mm.
  • the heat exchange efficiency can be improved by setting the vertical thickness T of the heat transfer tube 30 to 3 mm or less and setting the fin pitch to 1.3 mm or more.
  • the temperature difference between the refrigerant inlet temperature and the refrigerant outlet temperature of the heat exchanger 4 is 40 ° C. or more.
  • a CO 2 refrigerant is used as the refrigerant.
  • the CO 2 refrigerant is a supercritical refrigerant, and the temperature of the refrigerant in the radiator greatly decreases. It will be over 40 ° C. Since the temperature difference between the refrigerants is large, the effect of arranging the first straight portion 31 and the second straight portion 32 so as to be close to each other is also great.
  • the second straight portion 32 is located above or below the first straight portion 31.
  • the first straight portion 31 and the second straight portion 32 are located above and below, the distance between them is short, and the temperature unevenness of the passing air can be further suppressed. Further, since the fins 50 are connected above and below the heat transfer tube 30, the surrounding temperature approaches through the fins 50.
  • FIG. 5A is a longitudinal sectional view of the joint 34
  • FIG. 5B is a transverse sectional view of the joint 34.
  • the joint 34 of the present embodiment connects the multi-hole flat tube 300 and the circular tube 35.
  • the circular tube 35 is a U-shaped tube 350.
  • the refrigerant passing therethrough is a CO 2 refrigerant.
  • the joint 34 has a first connection portion 301, a main body portion 302, and a second connection portion 303.
  • the first connection part 301 covers the outside of the end of the multi-hole flat tube 300.
  • the main body part 302 is continuous from the first connection part 301.
  • the second connection portion 303 is continuous from the main body.
  • the second connection portion 303 covers the outside of the end of the circular tube 35.
  • the vertical inner diameter L 301 of the first connection portion 301 is slightly larger than the thickness T of the multi-hole flat tube 300.
  • the inner diameter L 302 of the main body 302 in the vertical direction is larger than the inner diameter L 301 of the first connection part 301 in the vertical direction. Further, the main body portion 302, follow away from the first connecting portion 301, the longitudinal direction of the inner diameter L 302 increases, at a certain portion, becomes constant.
  • the lateral inner diameter W 301 of the first connection portion 301 is slightly larger than the width W of the multi-hole flat tube 300.
  • the lateral inner diameter W 302 of the main body 302 is smaller than the lateral inner diameter W 301 of the first connection portion 301.
  • the main body portion 302 follow away from the first connecting portion 301, the lateral inner diameter W 302 decreases, at some portions, it becomes constant.
  • the portion where the horizontal inner diameter W 302 is constant has the same length as the portion where the vertical inner diameter L 302 is constant.
  • the longitudinal inner diameter L 302 of the main body 302 of the joint 34 is larger than the longitudinal inner diameter L 301 of the first connecting portion 301, the inner peripheral surface of the first connecting portion 301 is close to the multi-hole flat tube 300. Oil does not easily accumulate in oil.
  • the inner diameter of the circular pipe 35 connected to one of the joints 34 is the thickness of the hole of the multi-hole flat tube 300 connected to the other of the joints 34 in the thickness direction. Larger than the diameter.
  • the thickness of the pipe of the joint 34 is larger than the thickness of the circular pipe 35.
  • the joint 34 of the present embodiment further includes a reinforcing portion 304 that extends in the longitudinal direction in the refrigerant flow path.
  • the reinforcing section 304 is configured by a reinforcing member.
  • the reinforcing part 304 is arranged near the first connection part 301.
  • the first reinforcing portion 304 connects the upper and lower sides of the pipe constituting the joint 34, and in FIG. 5A, has a role of reinforcing both when receiving a tensile stress and when receiving a compressive stress from above and below the pipe. Since the pressure of the CO 2 refrigerant is high and the first connection portion 301 has a flat shape, it is preferable to use a reinforcing portion.
  • the first manufacturing method of the joint 34 is a method using a circular pipe.
  • the circular pipe is a normal circular pipe having a constant inner diameter.
  • the thickness of the circular pipe of the raw material is greater than the thickness of the circular pipe 35 to be connected.
  • To make the first connection portion 301 one end of the circular tube is crushed flat.
  • the lateral inner diameter W 301 is slightly smaller than the width W of the multi-hole flat tube 300 such that the longitudinal inner diameter L 301 of the end portion is slightly larger than the thickness T of the multi-hole flat tube 300. Process so that it becomes larger.
  • the second manufacturing method of the joint 34 is a method using a bonding method.
  • the reinforcing portion 304 is previously bonded to the upper portion or the lower portion by brazing or the like.
  • the upper part and the lower part are bonded together by brazing or the like to form the joint 34.
  • Intercooler 7 The arrangement of the intercooler 7 of the present embodiment will be described with reference to a top view of FIG. 8A and a cross-sectional view of FIG. 8B.
  • the intercooler 7 of the present embodiment is arranged on the windward side of the heat exchanger 4 and inside the casing 20 independently of the heat exchanger 4.
  • the term “independent” means that the fins 50 of the heat exchanger 4 and the fins (not shown) of the intercooler 7 are not connected, and the heat exchanger 4 and the intercooler 7 are separate.
  • the intercooler is disposed at a height higher than half of the height at which the heat exchanger 4 is disposed.
  • the fan 40 is disposed above the heat exchanger 4 and the intercooler 7, and the wind speed increases as the side of the heat exchanger 4 goes upward.
  • the intercooler 7 is arranged on the upstream side of the heat exchanger 4, so that a sufficient temperature difference between the air and the refrigerant can be secured, and the heat exchange amount can be increased.
  • the intercooler 7 is arranged at the upper part, the air flow is relatively large, and the heat exchange amount can be increased.
  • the joint 34 of the present embodiment is used in the refrigeration apparatus 1 using a CO 2 refrigerant. And the multi-hole flat tube 300 and the circular tube 35 are connected.
  • the joint 34 has a first connection portion 301, a main body portion 302, and a second connection portion 303.
  • the first connection portion 301 covers the outside of the end of the multi-hole flat tube.
  • the main body part 302 is continuous from the first connection part 301.
  • the second connecting portion 303 is continuous from the main body and covers the outside of the end of the circular tube.
  • the longitudinal direction of the inner diameter L 302 of the main body portion 302 is larger than the longitudinal direction of the inner diameter L 301 of the first connecting portion. Therefore, oil does not easily stay around the connection portion on the inner peripheral surface of the joint 34.
  • the main body 302 further has a region where the inner diameter in the vertical direction gradually increases as the distance from the first connection portion 301 increases.
  • the joint 34 of the present embodiment is formed by processing one end of a circular pipe.
  • the thickness of the circular pipe of this raw material is larger than the thickness of the circular pipe 35 to be connected.
  • the original portion of the circular tube of the raw material is a portion of the main body portion 302 and a portion having constant inner diameters L 302 and W 302 .
  • the joint 34 of the present embodiment can be manufactured by adding a simple process to a circular pipe, the manufacturing cost can be suppressed.
  • the wall thickness of the pipe of the joint 34 of the present embodiment is larger than the thickness of the circular pipe 35.
  • the reason why the thickness of the pipe of the joint 34 is increased is that the joint 34 requires a higher strength than the circular pipe 35 because the joint 34 has a flat portion.
  • the joint according to the present embodiment further includes a reinforcing portion 304.
  • the reinforcing portion 304 is disposed in the refrigerant flow path of the joint 34 so as to extend in the vertical direction.
  • the reinforcing part 304 connects the upper part and the lower part of the inner wall of the joint 34. There is a reinforcing role in both cases where tensile stress and compressive stress are received from above and below the joint 34. Since the pressure of the CO 2 refrigerant is high and the first connection portion 301 has a flat shape, it is preferable to use the reinforcing portion 304.
  • the joint 34 of the present embodiment may be manufactured by bonding two or more members. By manufacturing by bonding, it is possible to easily manufacture a joint having a complicated structure such as including the reinforcing portion 304.
  • the joint 34 of Modification 1A has the same features as (3-1) to (3-3) and (3-5), similarly to the joint 34 of the first embodiment.
  • the joint 34a, the U-shaped pipe 350, and the joint 34b may be formed as an integrated body as the folded portion 33 as shown in FIG.
  • FIGS. 7A and 7B are side views of the first end 4a and the second end 4b viewed from the direction in which the refrigerant flows, and are cross-sectional views perpendicular to the direction in which the refrigerant flows in the middle between the first end 4a and the second end 4b.
  • FIG. 6B shows a cross-sectional view at S.
  • the first heat transfer tube 30a is a heat transfer tube for flowing the refrigerant from the first end 4a to the second end 4b
  • the second heat transfer tube 30b is the opposite.
  • the flow of the refrigerant will be described assuming that the heat exchanger 4 is used as a radiator. When used as an evaporator, the flow of the refrigerant is reversed.
  • the heat transfer tube is a multi-hole flat tube.
  • the thickness T of the heat transfer tube 30 in the vertical direction is 3 mm or less.
  • the refrigerant enters the first refrigerant port 401 shown in FIG. 7A.
  • the refrigerant flowing from the first refrigerant inlet / outlet 401 through the first heat transfer tube 30a exchanges heat with air via three side surfaces of the heat exchanger 4 and reaches the second end 4b.
  • the refrigerant that has reached the second end 4b is returned by the return portion 33 to another row (here, an adjacent windward side row).
  • the vertical distance DP between the center of the first heat transfer tube 30a (the first straight portion 31) and the center of the second heat transfer tube 30b (the second straight portion 32) is 21 mm or less.
  • the configuration of the folded portion 33 of the present embodiment is the same as the configuration of the modified example 1A.
  • the first heat transfer tube 30a and the second heat transfer tube 30b are composed of two joints 34 and a U-shaped tube 350 connecting them. Connected by
  • the heat transfer tubes 30a and 30b of the present embodiment are vertically arranged at a period P.
  • the vertical distance DP between the center of the first heat transfer tube 30a (first straight portion 31) and the center of the second heat transfer tube 30b (second straight portion 32) is set to be greater than 0 and smaller than DP. Have been. That is, 0 ⁇ DP ⁇ P.
  • the refrigerant returned at the second end 4b flows through the second heat transfer tube 30b, exchanges heat with air while passing through the three side surfaces, and reaches the first end 4a.
  • the refrigerant that has reached the first end flows out from the second refrigerant port 402 into the refrigerant circuit outside the heat exchanger 4.
  • the case where the first heat transfer tube 30a is placed on the leeward side and the second heat transfer tube 30b is placed on the leeward side has been described.
  • the arrangement may be reversed.
  • the heat transfer tube 30 makes only one reciprocation between the first end 4a and the second end 4b has been described.
  • the present invention is also effective when making two or more round trips.
  • the heat exchanger of the second embodiment is similar to the heat exchanger of the first embodiment (3-1) to (3-3), (3--3). 5) to (3-7).
  • the first heat transfer tube 30a and the second heat transfer tube 30b before and after the folded portion 33 of the heat exchanger 4 of the second embodiment are another adjacent row. Therefore, when viewed in the same row, the first heat transfer pipe 30a and the second heat transfer pipe 30b having different refrigerant temperatures are not arranged side by side, and the temperature distribution in the row is suppressed.
  • the first heat transfer tubes 30a and the second heat transfer tubes 30b before and after the turn-back portion 33 are another adjacent row, and the first heat transfer tubes 30a (the first straight portion 31).
  • the vertical distance DP between the center of the second heat transfer tube 30b (the second straight portion 32) and the center thereof is set to be larger than 0 and smaller than DP.
  • the second heat transfer tube 30b is not obstructed by the second heat transfer tube 30b even on the leeward first heat transfer tube 30a, and the heat exchange between the air and the refrigerant is promoted.
  • first refrigerant port 401 and the second refrigerant port 402 of the present embodiment are arranged in different rows. Therefore, for example, when a refrigerant collecting pipe is separately provided at the inlet / outlet of the refrigerant, it is easy to simply configure the connection pipe.
  • FIG. 6A is a cross-sectional view of a cross section S perpendicular to the direction in which the refrigerant flows in the middle of the first end 4a and the second end 4b of the heat exchanger 4 of Modification Example 2A.
  • Modified example 2A is that the center of the first heat transfer tube 30a (the first straight portion 31) and the center of the second heat transfer tube 30b (the second straight portion 32) in the folded portion 33 of the refrigerant at the second end 4b.
  • the difference from the second embodiment is that the vertical distance DP is 0.
  • the other points are the same as the second embodiment.
  • the heat exchanger of Modification 2A has the same features as the heat exchanger 4 of the second embodiment, and (6-1) and (6-3).
  • ⁇ Third embodiment> Structure of the Joint of the Third Embodiment (8-1) Overall Structure of the Joint of the Third Embodiment
  • the joints 34a to 34e of the third embodiment connect the multi-hole flat tube 300 and the circular tube 35. , CO 2 refrigerant.
  • Each of the joints 34a to 34e has a first connection portion 301, a main body portion 302 continuous from the first connection portion 301, and reinforcing portions 304a to 304e.
  • the first connection portion 301 covers the outside of the end of the multi-hole flat tube 300.
  • the main body part 302 is continuous from the first connection part 301.
  • the reinforcing portions 304a to 304e reinforce the strength of the joints 34a to 34e.
  • the joints 34a to 34e of the present embodiment are connected to the multi-hole flat tube 300, they have a flat shape, and stress tends to concentrate locally. Further, since the CO 2 refrigerant is used at a high pressure, a large stress is applied to the joint. Furthermore, in consideration of stacking and using the multi-hole flat tubes 300, the thickness of the tube wall of the main body 302 cannot be unnecessarily increased. Since the joints 34a to 34e of the present embodiment have the reinforcing portions 304a to 304e, the joints 34a to 34e can be deformed or broken even if the inside of the joints 34a to 34e becomes high pressure by using CO 2 refrigerant. Can be suppressed.
  • the joint 34e of the present embodiment may further include a flat portion 305 that is continuous from the main body 302 and does not form a passage for the refrigerant.
  • the thickness T and the width W (W> T) of the multi-hole flat tube 300 are defined as in the first embodiment. Then, the thickness direction and the width direction of the multi-hole flat tube 300 are defined as the longitudinal direction and the lateral direction of the joint 34, respectively.
  • the reinforcing portions 304a and 304b of the present embodiment may be arranged in the refrigerant flow path so as to extend in the vertical direction.
  • the reinforcing portions 304c to 304e of the present embodiment may be arranged outside the coolant flow path and in contact with the outer surface of the main body 302.
  • the reinforcing portions 304c to 304e do not become a resistance to the flow of the refrigerant. Further, it is relatively easy to manufacture to arrange the reinforcing portions 304c to 304e on the outer surface of the main body 302.
  • the reinforcing portion 304e of the present embodiment may be arranged outside the coolant flow path in contact with the outer surface of the main body 302 and the surface of the flat portion 305.
  • the reinforcing portion 304e By arranging the reinforcing portion 304e not only on the outer surface of the main body 302 but also on the surface of the flat portion 305, the strength against the expansion of the main body 302 due to the internal pressure is more reliably secured.
  • the joints 34 a to 34 e of the present embodiment may further include a second connection portion 303 which is continuous from the main body 302 and covers the outside of the end of the circular tube 35.
  • first connection portions 301 of the joints 34a to 34e of the present embodiment may be formed by processing one end of the circular pipe 35.
  • the longitudinal inner diameter (L 302 ) of the main body 302 may be larger than the longitudinal inner diameter (L 301 ) of the first connection portion 301.
  • the main body 302 of the joint 34 of the present embodiment may have a region in which the inner diameter in the vertical direction gradually increases as the distance from the first connection portion 301 increases.
  • the thickness of the pipes of the joints 34a to 34e may be larger than the thickness of the circular pipe 35.
  • the material of the joints 34a to 34e is metal.
  • the metal is aluminum, copper, iron, or an alloy containing them.
  • the material of the multi-hole flat tube 300 and the circular tube 35 is metal.
  • the metal is aluminum, copper, iron, or an alloy containing them.
  • the first manufacturing method of the joints 34a to 34e is a method using a circular pipe.
  • Circular pipe is a normal circular pipe with a constant inner diameter.
  • the thickness of the circular pipe of the raw material is greater than the thickness of the circular pipe 35 to be connected.
  • FIGS. 11 and 12 show examples of the joints 34c and 34d created by the first manufacturing method.
  • the second method of manufacturing the joints 34a to 34e is a method using a bonding method.
  • a joint is formed by deforming and bonding the two plates.
  • the joint 34e in FIG. 13 is formed by bonding two deformed plates 3413 and 3414 to form a joint main body 302, a first connection portion 301, and a second connection portion 303.
  • the material of the reinforcement is metal.
  • the metal is aluminum, copper, iron, or an alloy containing them.
  • the material of the reinforcing portion may be the same as the material of the main body. In this case, there is an advantage that a battery reaction hardly occurs.
  • the material of the reinforcement may be different from the material of the body.
  • a material having good thermal conductivity may be used as a material of the main body portion, and a material having high mechanical strength may be used as a material of the reinforcing portion.
  • the material having good heat conductivity is, for example, aluminum or copper, and the material having high strength is, for example, stainless steel (an alloy containing iron).
  • FIG. 9 is a cross-sectional view of the joint 34a and the reinforcing portion 304a of Example 1 of the third embodiment.
  • the reinforcing portion 304a is a rod, and protrusions are arranged at both ends.
  • the rod penetrates the upper and lower portions of the main body portion 302 of FIG. 9 at two places.
  • a hole is formed in the main body portion 302 of the joint 34a and the hole is closed.
  • the rod is inserted, protrusions are formed at both ends of the rod, and the holes are formed by sealing the holes of the main body 302 by brazing or the like.
  • a rod having a protrusion at one end of a bolt may be inserted from one end of the main body 302, and a nut-like object may be attached at the other end to form a protrusion at the other end.
  • the reinforcing portion 304a according to the first embodiment suppresses the protrusion from being deformed so that the main body 302 expands even when the refrigerant inside the main body 302 becomes high pressure and pushes the wall of the main body 302 outward. I do.
  • the number of bars of the reinforcing portion 304a according to the first embodiment may be one or more.
  • the reinforcing portion 304 may be plate-shaped. In this case, it is preferable that the heat exchanger extends along the flow path of the refrigerant.
  • the joint 34a of the first embodiment may be a deformed circular tube or a structure obtained by bonding two plates.
  • joint 34b 8-3-2
  • Reinforcing portion 304b of joint 34b of the second embodiment may be formed by deforming a circular tube or by bonding two plates.
  • the reinforcing portion 304b of the second embodiment is obtained by deforming the main body portion 302 of the joint 34b and bonding the deformed body portion at the abutted portion.
  • the bonding method is, for example, brazing. Therefore, the reinforcing portion 304b has the bonding portion 3041.
  • the number of the reinforcing portions 304b in the second embodiment may be one or more.
  • the bonding portion 3041 of the reinforcing portion 304b according to the second embodiment may be a dot-like portion or may extend linearly. When extending in a straight line, it is preferable to extend along the flow path in which the refrigerant flows.
  • joint 34c (8-3-3) Reinforcing part 304c of joint 34c of the third embodiment
  • the joint 34c according to the third embodiment is obtained by deforming a circular pipe.
  • the reinforcing portion 304c of the third embodiment is a plate (rib) attached to the outside of the main body 302 of the joint 34c as shown in FIG.
  • the plate is attached so that the thickness direction of the plate is along the surface of the main body 302.
  • the main body 302 and the reinforcement 304c are adhered by brazing.
  • the reinforcing portion 304c of the third embodiment is arranged outside the main body portion 302, it does not become a resistance of the refrigerant flow path.
  • the number of the reinforcing portions 304c of the third embodiment may be one or more.
  • the reinforcing portion 304d of the fourth embodiment is a plate (rib) attached to the outside of the main body 302 of the joint 34d.
  • the plate is attached so that the surface of the plate is along the surface of the main body 302.
  • the main body 302 and the reinforcement 304c are adhered by brazing.
  • the reinforcing portion 304d of the fourth embodiment is arranged outside the main body portion 302, it does not become a resistance of the refrigerant flow path.
  • the reinforcing portion 304d of the fourth embodiment may be singular or plural.
  • the effect of the reinforcing portion 304d of the fourth embodiment is similar to the case where the thickness of the main body of the pipe of the joint is increased. However, compared to the case where the thickness of the main body of the pipe of the joint is simply increased, it is possible to realize a configuration in which only the wall to which pressure is applied is increased, and the portion where pressure is not applied is reduced.
  • the joint 34e of the fifth embodiment further has a flat portion 305.
  • the size of the flat portion 305 is arbitrary. It does not have to be as large as shown in FIG.
  • the four reinforcing portions 304e of the fifth embodiment are plates (ribs) stuck across the boundary between the main body 302 of the joint 34c and the four flat portions 305.
  • the plate is attached so that the thickness direction of the plate is along the surface of the main body 302.
  • the main body 302 and the reinforcement 304c are adhered by brazing.
  • the reinforcing portion 304e of the fifth embodiment is disposed outside the main body portion 302, it does not become a resistance of the refrigerant flow path.
  • the joint 34 and the reinforcing portion 304 of the first embodiment disclosed in FIGS. 5A and 5B are also examples of the joint and the reinforcing portion of the third embodiment.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Geometry (AREA)
  • Chemical Kinetics & Catalysis (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
  • Other Air-Conditioning Systems (AREA)

Abstract

L'invention aborde un problème pouvant survenir dans un raccord reliant un tube plat à trous multiples à un tuyau circulaire, concernant l'accumulation d'huile au voisinage d'une partie de raccordement. Dans un dispositif de réfrigération utilisant du dioxyde de carbone en tant que fluide frigorigène, pour lequel l'huile est de haute importance, ce problème peut être considérable. La solution de l'invention concerne un raccord (34) muni d'une première section de raccordement (301) recouvrant l'extérieur d'une partie d'extrémité d'un tube plat à trous multiples (300), et d'une section de corps principal (302) suivant immédiatement la première section de raccordement (301), le diamètre interne (L302) de la section de corps principal (302) dans la direction longitudinale étant supérieur au diamètre interne (L301) de la première section de raccordement (301) dans la direction longitudinale. La direction longitudinale est la direction de l'épaisseur du tube plat à trous multiples (300) (épaisseur T, largeur W, W>T).
PCT/JP2019/029250 2018-07-25 2019-07-25 Raccord WO2020022443A1 (fr)

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Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2020203589A1 (fr) * 2019-03-29 2020-10-08 ダイキン工業株式会社 Échangeur de chaleur, procédé pour fabriquer un échangeur de chaleur, et procédé pour fabriquer un ensemble collecteur
US11421246B2 (en) 2013-08-21 2022-08-23 Commonwealth Scientific And Industrial Research Organisation Rust resistance gene

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2010185614A (ja) * 2009-02-12 2010-08-26 Mitsubishi Electric Corp 扁平管継手
JP2011127831A (ja) * 2009-12-17 2011-06-30 Mitsubishi Electric Corp 熱交換器及びこれを備えた冷凍サイクル装置
WO2014199514A1 (fr) 2013-06-14 2014-12-18 三菱電機株式会社 Unité extérieure pour climatiseur et procédé de production pour unité extérieure pour climatiseur
JP2016038141A (ja) * 2014-08-07 2016-03-22 三菱電機株式会社 熱交換器

Family Cites Families (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH07125529A (ja) * 1993-11-02 1995-05-16 Kansai Pipe Kogyo Kk 管継手の製造方法

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2010185614A (ja) * 2009-02-12 2010-08-26 Mitsubishi Electric Corp 扁平管継手
JP2011127831A (ja) * 2009-12-17 2011-06-30 Mitsubishi Electric Corp 熱交換器及びこれを備えた冷凍サイクル装置
WO2014199514A1 (fr) 2013-06-14 2014-12-18 三菱電機株式会社 Unité extérieure pour climatiseur et procédé de production pour unité extérieure pour climatiseur
JP2016038141A (ja) * 2014-08-07 2016-03-22 三菱電機株式会社 熱交換器

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
See also references of EP3828490A4

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US11421246B2 (en) 2013-08-21 2022-08-23 Commonwealth Scientific And Industrial Research Organisation Rust resistance gene
US12037595B2 (en) 2013-08-21 2024-07-16 Commonwealth Scientific And Industrial Research Organisation Rust resistance gene
WO2020203589A1 (fr) * 2019-03-29 2020-10-08 ダイキン工業株式会社 Échangeur de chaleur, procédé pour fabriquer un échangeur de chaleur, et procédé pour fabriquer un ensemble collecteur

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EP3828490B1 (fr) 2023-03-08
EP3828490A1 (fr) 2021-06-02
EP3828490A4 (fr) 2021-09-15

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