EP2317269B1 - Échangeur de chaleur, appareil a cycle de réfrigération et appareil de climatisation - Google Patents

Échangeur de chaleur, appareil a cycle de réfrigération et appareil de climatisation Download PDF

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Publication number
EP2317269B1
EP2317269B1 EP09804999.2A EP09804999A EP2317269B1 EP 2317269 B1 EP2317269 B1 EP 2317269B1 EP 09804999 A EP09804999 A EP 09804999A EP 2317269 B1 EP2317269 B1 EP 2317269B1
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EP
European Patent Office
Prior art keywords
tube
refrigerant
ridge
heat
heat transfer
Prior art date
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EP09804999.2A
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German (de)
English (en)
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EP2317269A4 (fr
EP2317269A1 (fr
Inventor
Sangmu Lee
Akira Ishibashi
Takuya Matsuda
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Mitsubishi Electric Corp
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Mitsubishi Electric Corp
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Classifications

    • 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
    • F28F1/10—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses
    • F28F1/40—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only inside the tubular element
    • 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
    • F25B39/00—Evaporators; Condensers
    • F25B39/02—Evaporators
    • F25B39/022—Evaporators with plate-like or laminated elements
    • 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
    • F28D1/047—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 bent, e.g. in a serpentine or zig-zag
    • F28D1/0477—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 bent, e.g. in a serpentine or zig-zag the conduits being bent in a serpentine or zig-zag
    • 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
    • F28F1/10—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses
    • F28F1/12—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element
    • F28F1/24—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element and extending transversely
    • F28F1/32—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element and extending transversely the means having portions engaging further tubular 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
    • F28F1/00—Tubular elements; Assemblies of tubular elements
    • F28F1/10—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses
    • F28F1/42—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being both outside and inside the tubular element
    • 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
    • F28F1/10—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses
    • F28F1/42—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being both outside and inside the tubular element
    • F28F1/422—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being both outside and inside the tubular element with outside means integral with the tubular element and inside means integral with the tubular element
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F13/00—Arrangements for modifying heat-transfer, e.g. increasing, decreasing
    • F28F13/18—Arrangements for modifying heat-transfer, e.g. increasing, decreasing by applying coatings, e.g. radiation-absorbing, radiation-reflecting; by surface treatment, e.g. polishing
    • F28F13/185—Heat-exchange surfaces provided with microstructures or with porous coatings
    • F28F13/187—Heat-exchange surfaces provided with microstructures or with porous coatings especially adapted for evaporator surfaces or condenser surfaces, e.g. with nucleation sites
    • 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
    • F25B2309/00—Gas cycle refrigeration machines
    • F25B2309/06—Compression machines, plants or systems characterised by the refrigerant being carbon dioxide
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2500/00—Problems to be solved
    • F25B2500/01—Geometry problems, e.g. for reducing size
    • 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
    • F28D2021/007—Condensers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • 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
    • F28D2021/0071—Evaporators
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F2275/00—Fastening; Joining
    • F28F2275/12—Fastening; Joining by methods involving deformation of the elements
    • F28F2275/125—Fastening; Joining by methods involving deformation of the elements by bringing elements together and expanding

Definitions

  • the present invention relates to a heat transfer tube or the like for a heat exchanger in which a groove is provided in an inner face of the tube.
  • a heat transfer tube in which a groove is formed in an inner face is arranged with respect to a plurality of fins aligned with a predetermined interval so as to penetrate a through hole provided in each fin.
  • the heat transfer tube becomes a part of a refrigerant circuit in a refrigerating cycle apparatus, and a refrigerant (fluid) flows through inside the tube.
  • the groove in the inner face of the tube is processed so that a tube axial direction and a groove extending direction form a predetermined angle.
  • the tube inner face has recesses and ridges by forming the groove.
  • a space in a recess portion is referred to as a groove portion, while a ridge portion formed by side walls of the adjacent grooves is referred to as a ridge portion.
  • the refrigerant flowing through the above heat transfer tube changes its phase (condensation or evaporation) through heat exchange with air outside the heat transfer tube or the like.
  • phase change heat transfer performance of the heat transfer tube has been improved by increase in a surface area inside the tube, fluid agitation effect by the groove portion, liquid film holding effect between the groove portions through a capillary action of the groove portion and the like (See Patent Document 1, for example).
  • Patent Document 1 Japanese Unexamined Patent Application Publication No. 60-142195 (page 2, Fig. 1 )
  • JP 2001 133 182 A describes a heat transfer pipe with a grooved inner surface for increasing heat transfer performance in pipes while pressing the deformation of a fin in a pipe-spreading process when incorporating into a heat exchanger.
  • US 6,298,909 B1 describes a heat exchange tube having a grooved inner surface.
  • An inner circumferential surface of a metal tube is formed with fins bend at bend portions in a zigzag and extending consecutively around a circumferential direction of the inner circumferential surface. At at least a part of a bend portions of the fins, the height of the fins is set at 30 to 90% of the height of the fins excluding the bent portions.
  • US2007/0089868 A1 also discloses such a heat exchange tube.
  • the above prior-art heat transfer tube uses a metal such as copper or copper alloy as a material in general.
  • a mechanical tube expanding method has been practiced in which a tube expanding ball is pushed into a tube so as to expand the heat transfer tube from the inside so as to bring the fin and the heat transfer tube into close contact and join them.
  • the ridge portion is crushed by the tube expanding ball, pressure loss in the tube is increased, and heat transfer performance in the tube is lowered, which are problems.
  • the present invention was made in order to solve the above problems and has an object to provide a heat exchanger with a heat transfer tube which can obtain predetermined heat transfer performance without increasing an in-tube pressure loss, a refrigerating cycle apparatus using the heat exchanger and the like, as well as an air conditioner using said refrigerating cycle apparatus.
  • a heat exchanger comprising a plurality of fins for expanding an area for heat exchange and a heat transfer tube, wherein the heat transfer tube has high ridges formed with a predetermined height in ten to twenty rows and disposed on an inner face of said tube so that intervals of said high ridges are same and low ridges formed side by side with a height lower than the high ridges in two to six rows between the high ridge and the high ridge, spirally with respect to a tube axial direction on an inner face of the plurality of fins are joined by pressurizing and performing tube expansion from an inner face side of the heat transfer tube, wherein an outer surface of said heat transfer tube after expansion is a polygon and heights of the high ridges are 0.10 to 0.26 mm. tube.
  • the ridge portion in the groove in the tube inner face of the heat transfer tube is constituted by high ridges and low ridges
  • the tube expanding ball is brought into contact with the high ridges, their top portions are crushed by about 0.04 mm and becomes flat and their ridge heights are lowered, but since the heights of the low ridges are lower than those of the high ridges by 0.04 mm or more, the low ridges are not deformed and the in-tube heat transfer performance can be improved without increasing the pressure loss as compared with a prior-art heat transfer tube.
  • an outer face of the heat transfer tube is processed into a polygonal shape, which can suppress spring back in the heat transfer tube to improve adhesion between the heat transfer tube and the fin, which is excellent in efficiency.
  • Fig. 1 is a diagram illustrating a heat exchanger 1 according to Embodiment 1 not covered by the present invention.
  • the heat exchanger 1 is a fin tube heat exchanger widely used as an evaporator and a condenser of a refrigerating apparatus, an air conditioner and the like.
  • Fig. 1(a) is a perspective view when the heat exchanger 1 is cut in a vertical direction, while Fig. 1(b) illustrates a part of a section.
  • the heat exchanger 1 is configured by a plurality of fins 10 for the heat exchanger and heat transfer tubes 20.
  • the heat transfer tubes 20 are provided with respect to the fins 10 arranged in plural with a predetermined interval so as to penetrate through holes provided in each fin 10.
  • the heat transfer tube 20 becomes a part of a refrigerant circuit in a refrigerating cycle apparatus, and a refrigerant flows through the inside of the tube.
  • Fig. 2 is a diagram illustrating a shape of a tube inner face of the heat transfer tube 20 according to Embodiment 1.
  • Fig. 2 expands a portion of A in Fig. 1 .
  • Fig. 2(a) illustrates a state before tube expansion, while Fig. 2(b) illustrates a state after the tube expansion.
  • the tube inner face of the heat transfer tube 20 of this embodiment has a groove portion 21 and a ridge portion 22 by forming grooves.
  • the ridge portion 21 is constituted by two types of ridge portions: a high ridge 22A and a low ridge 22B.
  • a height of the low ridge 22B is lower than that of the high ridge 22A by 0.04 mm or more.
  • Fig. 3 is a diagram illustrating a state of tube expansion by a mechanical tube expanding method.
  • a center part in the longitudinal direction is bent into a hair pin shape with a predetermined bending pitch to manufacture a plurality of hair pin tubes to become the heat transfer tubes 20.
  • the hair pin tube is passed through a through hole of the fin 10
  • the hair pin tube is expanded by the mechanical tube expanding method, and the heat transfer tube 20 is brought into close contact with the fin 10 and joined.
  • the mechanical tube expanding method is a method in which a rod 31 having a tube expanding ball 30 with a diameter slightly larger than an inner diameter of the heat transfer tube 20 at a tip is passed through the inside of the heat transfer tube 20 to expand an outer diameter of the heat transfer tube 20 and bring it into close contact with the fin 10.
  • Fig. 4 is a graph illustrating a relationship between the number of rows of the high ridges 22A and a heat exchange rate.
  • the high ridges 22A and the low ridges 22B are shown alternately for explanation in this embodiment, but in actuality, on the inner face of the heat transfer tube 20, ten to twenty rows of high ridges 22A are spirally formed in succession in the axial direction. Then, moreover, two to six rows of low ridges 22B are formed between the high ridge 22A and the high ridge 22A.
  • the heat exchanger 1 ten to twenty rows of the high ridges 22A of the heat transfer tube 20 is set because when the tube is expanded, the tube expanding ball 30 is brought into contact with the high ridge 22A, its top portion is crushed by about 0.04 mm and becomes flat, and the height of the ridge is lowered, but if the number of rows of the high ridges 22A of the heat transfer tube 20 is smaller than 10, the ridge top portion of the low ridge 22B is also crushed to become flat, and the in-tube heat transfer performance is lowered. Also, if the number of rows of the high ridges is set at not less than 20, the number of rows of the low ridges 22B is decreased, and the in-tube heat transfer performance is lowered.
  • the ridge portion 22 of the tube inner face of the heat transfer tube 20 is constituted by two types of ridge portions, that is, the high ridges 22A having a predetermined height and the low ridge ridges 22B lower than the high ridge 22A by 0.04 mm or more, the high ridges 22A are provided in ten to twenty rows on the tube inner face, and the low ridges 22B are provided in two to six rows between the adjacent high ridge 22A and the high ridge 22A, so that heat transfer performance in the heat transfer tube 20 can be improved.
  • the tube expanding ball 30 expands the tube in contact only with the high ridges 22A, the outer face of the heat transfer tube 20 is processed into a polygonal shape, spring back of the heat transfer tube is suppressed, and close contact between the heat transfer tube and the fin can be achieved. Also, a heat exchange rate (ratio of heat quantities before and after passing through the heat transfer tube) can be increased, and energy saving can be promoted. Also, while decrease and high efficiency of the refrigerant in the refrigerant circuit are maintained, size reduction can be promoted.
  • Fig. 5 is a diagram illustrating a shape of a tube inner face of the heat transfer tube 20 according to Embodiment 2.
  • a configuration of the heat exchanger 1 is the same as Embodiment 1.
  • the same reference numerals are given to portions performing the same or corresponding roles as those of Embodiment 1 (the same applies to the embodiments below).
  • a difference H between the groove portion 21 and the ridge portion 22 after tube expansion will be described.
  • Fig. 6 is a graph illustrating a relationship between a difference between the groove portion 21 and the ridge portion 22 and the heat exchange rate after tube expansion.
  • the larger the difference H between the groove portion 21 and the ridge portion 22 after the tube expansion is the larger the heat transfer rate becomes such that a surface area in the tube is increased or the like.
  • the difference H between the groove portion 21 and the ridge portion 22 becomes 0.26 mm or more, an increase amount of pressure loss becomes larger than an increase amount of the heat transfer rate, so that the heat exchange rate is lowered.
  • the difference H between the groove portion 21 and the ridge portion 22 is less than 0.1 mm, the heat transfer rate is not improved. From the above, in the heat transfer tube 20, the high ridge 22A and the low ridge 22B are formed so that the difference H between the groove portion 21 and the ridge portion 22 after the tube expansion is 0.1 to 0.26 mm.
  • the heat transfer performance in the heat transfer tube 20 can be improved.
  • Fig. 7 is a diagram illustrating a shape of a tube inner face of the heat transfer tube 20 according to Embodiment 3.
  • a distal end width W1 of a ridge top portion of the high ridge 22A is set in a range of 0.035 to 0.05 mm and a distal end width W2 of the low ridge 22B is set in a range of 0.03 to 0.035 mm in the heat transfer tube 20 after the tube expansion.
  • the distal end width W1 of the high ridge 22A if it is set so that the distal end width W1 after the tube expansion becomes 0.035 mm or less, when the tube is expanded using the tube expanding ball 30, an upper part of the ridge top is crushed, and pressure by insertion is weakened. Thus, the tube expansion of the heat transfer tube 20 is insufficient, adhesion between the heat transfer tube 20 and the fin 10 is deteriorated, and drop in the heat transfer rate becomes remarkable. Also, if the distal end width W1 is made to be 0.05 mm or more, a sectional area is decreased in the groove portion 21, and a liquid film of the refrigerant becomes thick and the heat transfer rate is greatly lowered.
  • a skirt width of the ridge is also narrowly formed, and by thinly forming as a whole, a heat transfer area is increased, and an in-tube heat transfer rate is increased.
  • the heat transfer performance in the heat transfer tube 20 can be improved.
  • Fig. 8 is a diagram illustrating a shape of a tube inner face of the heat transfer tube 20 according to Embodiment 4 of the present invention.
  • an apex angle ⁇ of the high ridge 22A is set at 15 to 30 degrees and the apex angle ⁇ of the low ridge 22B is set at 5 to 15 degrees in the heat transfer tube 20.
  • Fig. 9 is a graph illustrating a relationship between the apex angle ⁇ of the high ridge 22A and a heat exchange rate.
  • the apex angle ⁇ of the high ridge 22A is smaller than 15 degrees, workability at manufacture of the heat exchanger 1 is greatly lowered, and the heat exchange rate is lowered in the end.
  • the apex angle ⁇ is larger than 30 degrees, a sectional area at the groove portion 21 is decreased, the liquid film of the refrigerant overflows the groove portion 21, and even the ridge top portion is covered by the liquid film. Thus, the heat transfer rate is lowered.
  • the skirt width of the ridge is narrowly formed, and by thinly forming as a whole, the heat transfer area is increased, and the in-tube heat transfer rate is increased.
  • Fig. 10 is a configuration diagram of an air conditioner according to Embodiment 5 of the present invention.
  • an air conditioner will be described as an example of a refrigerating cycle apparatus.
  • the air conditioner in Fig. 10 is provided with a heat-source side unit (outdoor unit) 100 and a load-side unit (indoor unit) 200, and they are connected by a refrigerant piping so as to constitute a refrigerant circuit and circulate a refrigerant.
  • piping through which a gas-phase refrigerant (gas refrigerant) flows is gas piping 300, and piping through which a liquid refrigerant (liquid refrigerant.
  • liquid piping 400 It might be a gas-liquid two-phase refrigerant) flows is liquid piping 400.
  • the refrigerant an HC single refrigerant or a mixed refrigerant containing the HC refrigerant, R32, R410A, R407C, tetrafluoropropene (2,3,3,3-tetrafluoropropene, for example), carbon dioxide and the like are supposed to be used.
  • the heat-source side unit 100 in this embodiment is constituted by each device (means) of a compressor 101, an oil separator 102, a four-way valve 103, a heat-source side heat exchanger 104, a heat-source side fan 105, an accumulator 106, a heat-source side throttle device (expansion valve) 107, an inter-refrigerant heat exchanger 108, a bypass throttle device 109, and a heat-source side controller 111.
  • the compressor 101 has an electric motor 6 described in the above embodiment and intakes the refrigerant and compresses the refrigerant to turn it into a high-temperature and high-pressure gas state and flow it to the refrigerant piping.
  • operation control of the compressor 101 by providing a master-side inverter circuit 2, a slave-side inverter circuit 3 and the like described in the above-mentioned embodiment in the compressor 101 and by changing an operation frequency arbitrarily, for example, a capacity (amount of the refrigerant to be fed out per unit time) of the compressor 101 can be finely changed.
  • the oil separator 102 separates a lubricant discharged from the compressor 101 while being mixed in the refrigerant.
  • the separated lubricant is returned to the compressor 101.
  • the four-way valve 103 switches a flow of the refrigerant depending on a cooling operation and a heating operation on the basis of an instruction from the heat-source side controller 111.
  • the heat-source side heat exchanger 104 is constituted using the heat exchanger 1 described in the embodiments 1 to 4 to perform heat exchange between the refrigerant and air (outside air).
  • the heat exchanger functions as an evaporator in a heating operation and performs heat exchange between a low-pressure refrigerant flowing in through the heat-source side throttle device 107 and the air to evaporate and gasify the refrigerant. Also, it functions as a condenser in a cooling operation and performs heat exchange between a refrigerant flowing in from the four-way valve 103 side and compressed in the compressor 101 and the air to condense and liquefy the refrigerant.
  • a heat-source side fan 105 is provided in order to perform heat exchange between the refrigerant and the air efficiently.
  • the heat-source side fan 105 may also have an inverter circuit (not shown) to arbitrarily change the operation frequency of a fan motor and to finely change a rotation speed of the fan.
  • the inter-refrigerant heat exchanger 108 performs heat exchange between the refrigerant flowing through a major flow passage in the refrigerant circuit and the refrigerant branched from the flow passage and whose flow rate is adjusted by the bypass throttle device 109 (expansion valve). Particularly when there is a need to overcool the refrigerant in the cooling operation, the heat exchanger overcools the refrigerant and supplies it to the load-side unit 200.
  • the inter-refrigerant heat exchanger 108 is also constituted using the heat exchanger 1 described in the embodiments 1 to 4.
  • the accumulator 106 is means for accumulating an excessive liquid refrigerant, for example.
  • the heat-source side controller 111 is constituted by a microcomputer or the like. The controller can perform a wired or wireless communication with a load-side controller 204 and controls operations of the entire air conditioner by controlling each means relating to the air conditioner such as operation frequency control or the like of the compressor 101 by inverter circuit control on the basis of data relating to detection of various detecting means (sensors) in the air conditioner, for example.
  • the load-side unit 200 is constituted by a load-side heat exchanger 201, a load-side throttle device (expansion valve) 202, a load-side fan 203, and a load-side controller 204.
  • the load-side heat exchanger 201 is also constituted using the heat exchanger 1 described in the embodiments 1 to 4 to perform heat exchange between the refrigerant and air in a space to be air-conditioned.
  • the heat exchanger functions as a condenser in the heating operation, performs heat exchange between the refrigerant flowing in from the gas piping 300 and the air, condenses and liquefies the refrigerant(or turns it into gas-liquid two-phase), and flows it out to the liquid piping 400 side.
  • the heat exchanger functions as an evaporator, performs heat exchange between the refrigerant brought into a low-pressure state by the load-side throttle device 202 and the air, makes the refrigerant get rid of heat in the air to evaporate and gasify, and flows it out to the gas piping 300 side.
  • the load-side fan 203 for adjusting flow of air for heat exchange is provided in the load-side unit 200. An operation speed of the load-side fan 203 is determined by a user setting, for example.
  • the load-side throttle device 202 is provided in order to adjust a pressure of the refrigerant in the load-side heat exchanger 201 by changing an opening degree.
  • the load-side controller 204 is constituted by a microcomputer or the like and is capable of performing a wired or wireless communication with the heat-source side controller 111, for example.
  • the controller controls each device (means) of the load-side unit 200 so that the inside of a room becomes a predetermined temperature, for example.
  • the controller transmits a signal including data relating to detection by detecting means provided in the load-side unit 200.
  • a high-temperature and high-pressure gas refrigerant discharged from the compressor 101 by a driving operation of the compressor 101 is condensed while passing through the heat-source side heat exchanger 104 from the four-way valve 103 and flows out of the heat-source side unit 100 as a liquid refrigerant.
  • the refrigerant flowing into the load-side unit 200 through the liquid piping 400 is pressure-adjusted by the opening-degree adjustment of the load-side throttle device 202, and a low-temperature and low-pressure liquid refrigerant passes through the load-side heat exchanger 201, evaporates and flows out.
  • the refrigerant passes through the gas piping 300 and flows into the heat-source side unit 100 and is sucked into the compressor 101 through the four-way valve 103 and the accumulator 106, pressurized again and discharged, which makes circulation.
  • the refrigerant is pressure-adjusted by the opening-degree of the load-side throttle device 202, being condensed while passing through the load-side heat exchanger 201, and becomes an intermediate-pressure liquid or a gas-liquid two-phase refrigerant to flow out of the load-side unit 200.
  • the refrigerant flowing into the heat-source side unit 100 through the liquid piping 400 is pressure-adjusted by the opening-degree of the heat-source side throttle device 107, being evaporated while passing through the heat-source side heat exchanger 104, becomes a gas refrigerant and sucked into the compressor 101 through the four-way valve 103 and the accumulator 106 to be circulated by being pressurized and discharged as described above.
  • the heat exchanger 1 of Embodiments 1 to 4 having a high heat exchange rate is used as an evaporator and a condenser for the heat-source side heat exchanger 104 and the inter-refrigerant heat exchanger 108 of the heat-source side unit 100 and the load-side heat exchanger 201 of the load-side unit 200, a COP (Coefficient of Performance: energy consumption efficiency) or the like can be improved, and energy saving or the like can be promoted.
  • COP Coefficient of Performance: energy consumption efficiency
  • Example 1 and Example 2 both have a higher heat exchange rate than the heat exchangers in Comparative Example 1 and Comparative Example 2, and the in-tube heat transfer performance is improved.
  • the heat exchangers 1 with an outer diameter of 7 mm, a bottom thickness of the groove 21 of 0.25 mm, a lead angle of 30 degrees, and groove depths after tube expansion of 0.10 mm and 0.26 mm are produced.
  • heat exchangers with the outer diameter of 7 mm, the bottom thickness of the groove 21 of 0.25 mm, the lead angle of 30 degrees, and groove depths after tube expansion of 0.05 mm and 0.3 mm, respectively are produced (Comparative Example 3 and Comparative Example 4).
  • the heat exchangers 1 of Example 3 and Example 4 both have a higher heat exchange rate than the heat exchangers of Comparative Example 3 and Comparative Example 4, and the in-tube heat transfer performance is improved.
  • Example 5 the heat exchangers with an outer diameter of 7 mm, a bottom thickness of the groove 21 of 0.25 mm, a lead angle of 30 degrees, and ridge-portion distal end widths of high ridges of 0.035 mm, 0.4 mm and 0.5 mm (Example 5, Example 6, and Example 7) are produced. Also, as comparative examples, heat exchangers with the outer diameter of 7 mm, the bottom thickness of the groove 21 of 0.25 mm, the lead angle of 30 degrees, and ridge-portion distal end widths of the high ridges of 0.025 mm and 0.6 mm, are produced (Comparative Example 5 and Comparative Example 6).
  • the heat exchangers 1 with an outer diameter of 7 mm, a bottom thickness of the groove 21 of 0.25 mm, a lead angle of 30 degrees, and apex angles of 15 degrees and 30 degrees are produced from aluminum.
  • heat exchangers with the outer diameter of 7 mm, the bottom thickness of 0.25 mm, the lead angle of 30 degrees, and apex angles of 10 degrees and 40 degrees are produced (Comparative Example 7 and Comparative Example 8).
  • Example 8 and Example 9 both have a higher heat exchange rate than the heat exchangers in Comparative Example 7 and Comparative Example 8, and the in-tube heat transfer performance is improved.
  • the present invention is not limited to these apparatuses but can be applied to other refrigerating cycle apparatus such as a refrigerating apparatus and a heat pump having a heat exchanger constituting a refrigerant circuit and to become an evaporator and a condenser.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Geometry (AREA)
  • Chemical & Material Sciences (AREA)
  • Crystallography & Structural Chemistry (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)

Claims (7)

  1. Échangeur de chaleur (1), comprenant :
    une pluralité d'ailettes (10) destinées à augmenter une surface d'échange de chaleur ; et
    un tube de transfert de chaleur (20), dans lequel :
    les arêtes hautes (22A) formées avec une hauteur prédéterminée en dix à vingt rangées, sont disposées sur une face intérieure dudit tube de telle sorte que les intervalles entre lesdites arêtes hautes soient identiques ; et
    les arêtes basses (22B) formées côte à côte avec une hauteur inférieure à celle desdites arêtes hautes (22A) en deux à six rangées entre ladite arête haute (22A) et ladite arête haute (22A), sont disposées sur ladite face intérieure du tube, en spirale par rapport à la direction axiale du tube ;
    dans lequel la pluralité d'ailettes (10) sont jointes en mettant sous pression le tube et en exécutant une expansion de celui-ci, à partir du côté face intérieure dudit tube de transfert de chaleur (20) ; et
    dans lequel la surface extérieure dudit tube de transfert de chaleur après une expansion, est un polygone, et les auteurs desdites arêtes hautes (22A) est comprise entre 0,10 mm et 0,26 mm.
  2. Échangeur de chaleur (1) selon la revendication 1, dans lequel :
    la différence de hauteur entre lesdites arêtes hautes (22A) et lesdites arêtes basses (22B) avant l'expansion du tube, est égale ou supérieure à 0,04 mm.
  3. Échangeur de chaleur (1) selon la revendication 1 ou la revendication 2, dans lequel :
    la largeur de la partie extrémité distale de ladite arête haute (22A) est comprise entre 0,035 mm et 0,05 mm, et la largeur de la partie extrémité distale de ladite arête basse (22B) est comprise entre 0,03 mm et 0,035 mm après l'expansion du tube.
  4. Échangeur de chaleur (1) selon l'une quelconque des revendications 1 à 3, dans lequel :
    l'angle au sommet de ladite arête haute (22A) est formé de façon à être compris entre 15 degrés et 30 degrés, et l'angle au sommet de ladite arête basse (22B) est formé de façon à être compris entre 5 degrés et 15 degrés.
  5. Appareil à cycle de réfrigération constituant un circuit de fluide frigorigène dans lequel un compresseur destiné à comprimer un fluide frigorigène, un condenseur destiné à condenser ledit fluide frigorigène par un échange de chaleur, des moyens d'expansion destinés à décomprimer le fluide frigorigène condensé, et un évaporateur destiné à faire évaporer ledit fluide frigorigène décomprimé par un échange de chaleur, sont connectés par une canalisation destinée à faire circuler ledit fluide frigorigène, dans lequel :
    l'échangeur de chaleur (1) selon l'une quelconque des revendications 1 à 4, est ledit condensateur et / ou ledit évaporateur.
  6. Appareil à cycle de réfrigération selon la revendication 5, dans lequel est utilisé, en tant que dit fluide frigorigène, n'importe quel fluide frigorigène parmi un seul fluide frigorigène HC, un fluide frigorigène mélangé qui contient du HC, du R32, du R410A, du R407C, du tétrafluoropropène, ou du dioxyde de carbone.
  7. Climatiseur, dans lequel :
    le refroidissement / le chauffage d'un espace cible, est exécuté par l'appareil à cycle de réfrigération selon la revendication 5 ou la revendication 6.
EP09804999.2A 2008-08-08 2009-08-05 Échangeur de chaleur, appareil a cycle de réfrigération et appareil de climatisation Active EP2317269B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2008205073A JP2010038502A (ja) 2008-08-08 2008-08-08 熱交換器用の伝熱管、熱交換器、冷凍サイクル装置及び空気調和装置
PCT/JP2009/063859 WO2010016516A1 (fr) 2008-08-08 2009-08-05 Tube de transfert de chaleur pour échangeur de chaleur, échangeur de chaleur, appareil à cycle de réfrigération et appareil de climatisation

Publications (3)

Publication Number Publication Date
EP2317269A1 EP2317269A1 (fr) 2011-05-04
EP2317269A4 EP2317269A4 (fr) 2014-04-02
EP2317269B1 true EP2317269B1 (fr) 2018-06-06

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EP09804999.2A Active EP2317269B1 (fr) 2008-08-08 2009-08-05 Échangeur de chaleur, appareil a cycle de réfrigération et appareil de climatisation

Country Status (6)

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US (1) US20110113820A1 (fr)
EP (1) EP2317269B1 (fr)
JP (1) JP2010038502A (fr)
CN (1) CN102112838B (fr)
ES (1) ES2677347T3 (fr)
WO (1) WO2010016516A1 (fr)

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ES2731748T3 (es) 2011-09-26 2019-11-18 Mitsubishi Electric Corp Intercambiador de calor y dispositivo de ciclo de refrigeración que incluye el intercambiador de calor
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WO2014147788A1 (fr) * 2013-03-21 2014-09-25 三菱電機株式会社 Échangeur de chaleur, dispositif à cycle de réfrigération, et méthode de production pour échangeur de chaleur
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US20150323230A1 (en) * 2014-03-11 2015-11-12 Brazeway, Inc. Tube pattern for a refrigerator evaporator
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JP6878918B2 (ja) * 2017-01-30 2021-06-02 株式会社富士通ゼネラル 冷凍サイクル装置
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Also Published As

Publication number Publication date
EP2317269A4 (fr) 2014-04-02
CN102112838B (zh) 2013-04-17
WO2010016516A1 (fr) 2010-02-11
US20110113820A1 (en) 2011-05-19
EP2317269A1 (fr) 2011-05-04
JP2010038502A (ja) 2010-02-18
CN102112838A (zh) 2011-06-29
ES2677347T3 (es) 2018-08-01

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