EP2735832B1 - Échangeur de chaleur et pompe à chaleur utilisant cet échangeur - Google Patents

Échangeur de chaleur et pompe à chaleur utilisant cet échangeur Download PDF

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Publication number
EP2735832B1
EP2735832B1 EP12818246.6A EP12818246A EP2735832B1 EP 2735832 B1 EP2735832 B1 EP 2735832B1 EP 12818246 A EP12818246 A EP 12818246A EP 2735832 B1 EP2735832 B1 EP 2735832B1
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EP
European Patent Office
Prior art keywords
tube
heat exchanger
φin
fluid
flow passage
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EP12818246.6A
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German (de)
English (en)
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EP2735832A4 (fr
EP2735832A1 (fr
Inventor
Ken-Ichi Morita
Osao Kido
Motohiro Suzuki
Kazuhiko Machida
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Panasonic Intellectual Property Management Co Ltd
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Panasonic Intellectual Property Management Co Ltd
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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D7/00—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
    • F28D7/16—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits being arranged in parallel spaced relation
    • 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
    • F25B30/00—Heat pumps
    • F25B30/02—Heat pumps of the compression type
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D7/00—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
    • F28D7/02—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits being helically coiled
    • F28D7/024—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits being helically coiled the conduits of only one medium being helically coiled tubes, the coils having a cylindrical configuration
    • 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
    • F28F1/003—Multiple wall conduits, e.g. for leak detection
    • 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
    • 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
    • F25B2339/00—Details of evaporators; Details of condensers
    • F25B2339/04—Details of condensers
    • F25B2339/047—Water-cooled condensers

Definitions

  • the present invention relates to a heat exchanger and a heat pump including the heat exchanger.
  • heat exchangers for exchanging heat between two kinds of fluids water and a refrigerant, or air and a refrigerant, for example have been used widely.
  • Patent Literature 1 describes a double tube heat exchanger including inner tubes and outer tubes.
  • the heat exchanger of Patent Literature 1 includes two double tubes and a header.
  • the header connects the two double tubes in parallel.
  • the double tubes each are composed of one outer tube and two inner tubes.
  • Patent Literature 2 describes a heat exchanger including a housing having a rectangular flow passage, and heat transfer tubes disposed in the flow passage inside the housing.
  • the heat exchanger described in Patent Literature 2 is the same as the heat exchanger described in Patent Literature 1 in that it has a configuration in which the tube having the flow passage for one fluid is disposed in the flow passage for another fluid.
  • a heat exchanger having a configuration in which a flow passage for one fluid is disposed in a flow passage for another fluid is referred to as "a double flow passage heat exchanger".
  • Patent literature 3 disclosing the features included in the preamble of claim 1 attached refers to a water heat exchanger which includes large diameter pipes in which water flows, small diameter pipes in which a refrigerant flows, and intermediate diameter pipes coming into close contact with the outer peripheries of the small diameter pipes and having leakage sensing grooves formed therein.
  • the heat exchanger further includes a plurality of refrigerant pipes comprising the small diameter pipes and the intermediate diameter pipes.
  • a spiral metal wire is wound around the outer periphery of at least one of the plurality of refrigerant pipes, and the plurality of refrigerant pipes are twisted, so as to provide a clearance between the two intermediate diameter pipes (refrigerant pipes).
  • patent literature 4 discloses a dispensing apparatus which is provided for dispensing a semi-frozen product.
  • the dispensing apparatus has at least one freezing barrel defining a freezing chamber wherein the freezing barrel includes a longitudinal extending inner cylinder and an evaporator disposed about at least a portion of an outer surface of that cylinder.
  • the evaporator includes a plurality of channels disposed about the outer surface of the inner cylinder. Each channel defines a heat exchange fluid flow passage so which refrigerant may pass in heat exchange relationship with product in the freezing chamber.
  • patent literature 5 discloses a heat exchanging device which comprises a first heat exchanger tube in which a first fluid flows and a second heat exchanger tube in which a second fluid flows, arranged in the first heat exchanger tube.
  • the second heat exchanger tube is formed by a spirally twisting a plurality of heat exchanger tubes.
  • the heat exchanger tubes are in a double-tube structure consisting of inner tubes and outer tubes, respectively.
  • patent literature 6 refers to a heat exchanger which comprises a first heat transfer tube allowing a first fluid to flow, and second heat transfer tubes arranged in the first heat transfer tube and allowing a second fluid to flow.
  • the second heat transfer tube is composed of a center second heat transfer tube and peripheral second heat transfer tubes spirally wound around the outer periphery of the center second heat transfer tube. Many second heat transfer tubes can be arranged in the first heat transfer tube while maintaining contact surfaces with the first fluid.
  • Patent Literatures 1 and 2 are very heavy because they are made of metal such as copper and stainless steel. Thus, a lighter-weight double flow passage heat exchanger is desired.
  • the present invention is intended to provide a technique for reducing the weight of a double flow passage heat exchanger.
  • the present disclosure provides a heat exchanger for exchanging heat between a first fluid and a second fluid, including:
  • Each of the heat exchange segments is composed of (i) an inner tube assembly that includes two inner tubes each having the first flow passage and that is formed of the two inner tubes twisted spirally, and (ii) an exterior body accommodating the inner tube assembly so that the second flow passage is formed between an inner circumferential surface of the exterior body and an outer circumferential surface of the inner tube assembly.
  • a path number N indicating the number of the heat exchange segments disposed between the first header and the second header is 4 to 8.
  • a gap width G represented by a difference (( ⁇ in / 2) - ⁇ out) between a half of an inner diameter ⁇ in of the exterior body and an outer diameter ⁇ out of the inner tube satisfies 0 ⁇ G ⁇ 0.8 (unit: mm).
  • the path number N and the inner diameter ⁇ in (unit: mm) of the exterior body satisfy one of relationships (1) to (5) below.
  • the present disclosure makes it possible to provide a heat exchanger having a reduced weight even while having a heat exchanging capacity equivalent to those of conventional double flow passage heat exchangers.
  • the heat exchanger of Patent Literature 1 has large dimensions despite its heat exchanging capacity because it has a large space at its center (see FIG. 3 , etc.)
  • the dimensions of the heat exchanger of Patent Literature 1 are affected significantly by the curvature radii of corner portions, for example. Smaller curvature radii of the corner portions can make the overall dimensions smaller. However, the curvature radii of the corner portions have an inevitable limit in accordance with the size of the double tubes, etc. This makes it almost impossible to reduce further the weight of the heat exchanger by contriving the bending shape of the double tubes.
  • the present inventors investigated, through computer simulation, how the weight of the heat exchanger changes when the number of the flow passages in the double flow passage heat exchanger (corresponding to the number of the double tubes in Patent Literature 1), the inner diameter of the outer tube, and the width of the gap between the outer tube and the inner tube are changed while the heat exchanging capacity is kept at a fixed value. As a result, they have found it possible to reduce the weight of the heat exchanger when the number of the flow passages, the inner diameter of the outer tube, and the gap width take specific values, respectively. Based on this finding, the present inventors disclose the following.
  • a first aspect of the present disclosure provides a heat exchanger for exchanging heat between a first fluid and a second fluid, including:
  • Each of the heat exchange segments is composed of (i) an inner tube assembly that includes two inner tubes each having the first flow passage and that is formed of the two inner tubes twisted spirally, and (ii) an exterior body accommodating the inner tube assembly so that the second flow passage is formed between an inner circumferential surface of the exterior body and an outer circumferential surface of the inner tube assembly.
  • a path number N indicating the number of the heat exchange segments disposed between the first header and the second header is 4 to 8.
  • a gap width G represented by a difference (( ⁇ in / 2) - ⁇ out) between a half of an inner diameter ⁇ in of the exterior body and an outer diameter ⁇ out of the inner tube satisfies 0 ⁇ G ⁇ 0.8 mm.
  • the path number N and the inner diameter ⁇ in of the exterior body satisfy one of relationships (1) to (5) below.
  • a second aspect of the present disclosure provides the heat exchanger as set forth in the first aspect, wherein the gap width G satisfies 0.16 ⁇ G ⁇ 0.8 mm. This makes it possible to put smoothly the inner tube assembly into the exterior body.
  • a third aspect of the present disclosure provides the heat exchanger as set forth in the first aspect or the second aspect, wherein the inner tubes and the exterior body each are composed of a copper tube. This makes it possible to exchange heat between the first fluid and the second fluid efficiently.
  • a fourth aspect of the present disclosure provides the heat exchanger as set forth in the first aspect or the second aspect, wherein the inner tubes each are composed of a copper tube and the exterior body is made of a resin.
  • the exterior body made of a resin may make it possible to provide a heat exchanger having a further reduced weight.
  • a fifth aspect of the present disclosure provides the heat exchanger as set forth in any one of the first to fourth aspects, wherein the inner tubes each are a leakage detection tube composed of a smooth-inner-surface tube and an inner-surface-grooved tube provided outside around the smooth-inner-surface tube.
  • the leakage detection tube can prevent the first fluid from flowing into the second flow passage even in the case where the smooth-inner-surface tube is damaged.
  • a sixth aspect of the present disclosure provides the heat exchanger as set forth in any one of the first to fifth aspects, wherein the first fluid is carbon dioxide and the second fluid is water.
  • the first fluid is carbon dioxide and the second fluid is water.
  • Use of carbon dioxide as a refrigerant allows to heat the water to a temperature close to its boiling point.
  • a seventh aspect of the present disclosure provides a heat pump including:
  • a heat exchanger 100 of the present embodiment includes a plurality of heat exchange segments 10, a first header 16 and a second header 22.
  • the first header 16 and the second header 22 are provided respectively at one end and another end of the heat exchange segments 10.
  • each of the heat exchange segments 10 is composed of an inner tube assembly 26 and an outer tube 28 (exterior body).
  • the inner tube assembly 26 includes two inner tubes 24.
  • the two inner tubes 24 each have a first flow passage 24h.
  • the inner tube assembly 26 is formed of the two inner tubes 24 twisted spirally.
  • the inner tube assembly 26 is disposed in the outer tube 28.
  • a second flow passage 28h is formed between an inner circumferential surface of the outer tube 28 and an outer circumferential surface of the inner tube assembly 26.
  • the first flow passage 24h and the second flow passage 28h each have a circular cross-sectional shape.
  • a helical pitch and helix angle of the inner tube assembly 26 are not particularly limited.
  • the helical pitch is adjusted to fall in the range of 20 to 65 mm, for example.
  • the helix angle is adjusted to fall in the range of 13 to 26°, for example.
  • a somewhat large helix angle is desirable, but there is a processing limitation in accordance with an outer diameter of each inner tube 24.
  • the "helical pitch" refers to the length of one cycle of the twisted inner tubes 24.
  • the "helix angle" is an angle defined as follows. When the inner tube assembly 26 is viewed in plan, a center line L 1 of the inner tube assembly 26, and a contact point P between the two inner tubes 24 at a position of an antinode of the inner tube assembly 26 are defined. Further, a tangent L 2 of the inner tubes 24 is defined so as to pass through the contact point P. The angle between the center line L 1 and the tangent L 2 is defined as the "helix angle".
  • the first header 16 is composed of an outlet header 12 and an inlet header 14.
  • the first header 16 serves the role of collecting the second fluid from the second flow passages 28h and introducing the first fluid into the first flow passages.
  • the second header 22 is composed of an inlet header 18 and an outlet header 20.
  • the second header 22 serves the role of introducing the second fluid into the second flow passages 28h and collecting the first fluid from the first flow passages 24h.
  • Examples of the first fluid include a refrigerant such as carbon dioxide
  • examples of the second fluid include water.
  • Carbon dioxide is suitable for heat pumps as a refrigerant with a low GWP (Global Warming Potential).
  • Use of carbon dioxide as a refrigerant allows to heat the water to a temperature close to its boiling point.
  • the two kinds of fluids to be subjected to heat exchange are not limited to these.
  • a fluorine refrigerant such as hydrofluorocarbon, can also be used as the refrigerant.
  • the inner tubes 24 and the outer tube 28 each are composed of a copper tube. This makes it possible to exchange heat between the first fluid and the second fluid efficiently.
  • the second flow passage 28h may be formed with a member having a shape other than a tube shape.
  • a member may be made of metal or may be made of a material other than metal.
  • the inner tubes 24 each may be made of a copper tube and the member (exterior body) corresponding to the outer tube 28 may be made of a resin.
  • the member (exterior body) corresponding to the outer tube 28 is made of a resin, it may be possible to provide a heat exchanger with a further reduced weight.
  • the member corresponding to the outer tube 28 may be made of, for example, a resin such as polyphenylene sulfide, polyetheretherketone, polytetrafluoroethylene, polysulfone, polyether sulfone, polyarylate, polyamide imide, polyether imide, a liquid crystal polymer, and polypropylene. These resins (thermoplastic resins) have excellent heat resistance and chemical durability and hardly deteriorate even when they are in contact with water. Also, the outer tube 28 may be made of a resin containing a reinforcing material such as a glass filler.
  • the inner tubes 24 each are a leakage detection tube composed of a smooth-inner-surface tube 32 and an inner-surface-grooved tube 30 provided outside around the smooth-inner-surface tube 32.
  • the smooth-inner-surface tube 32 has an outer diameter equal to an inner diameter of the inner-surface-grooved tube 30.
  • the leakage detection tube makes it possible to prevent the first fluid from flowing into the second flow passage 28h even in the case where the smooth-inner-surface tube 32 is damaged.
  • each inner tube 24 does not necessarily have to be a leakage detection tube.
  • the inner tube 24 may be composed only of the smooth-inner-surface tube 32. Dimples (depressions and projections) may be formed on a surface of the inner tube 24. Such dimples increase the heat transfer coefficient on the surface of the inner tube 24.
  • the path number N indicating the number of the heat exchange segments 10 disposed between the first header 16 and the second header 22 is 4 in the present embodiment.
  • the path number N may be changed suitably in the range of 4 to 8 in accordance with the inner diameter of the outer tube 28 and the outer diameter of the inner tube 24.
  • the present inventors investigated in detail the relationship among the number of the flow passages (path number), the inner diameter of the outer tube and the gap width through computer simulation. As a result, they found that when these parameters each take a specific value, it is possible to provide a heat exchanger having a reduced weight even while having a heat exchanging capacity equivalent to those of conventional double flow passage heat exchangers.
  • the heat exchanger 100 of the present embodiment satisfies the following relationships.
  • the path number N is in the range of 4 to 8.
  • the inner diameter ⁇ in of the outer tube 28 is in the range of 6.52 to 9.50 mm.
  • the gap width G represented by a difference (( ⁇ in / 2) - ⁇ out) between a half of the inner diameter ⁇ in of the outer tube 28 and the outer diameter ⁇ out of the inner tube 24 satisfies 0 ⁇ G ⁇ 0.8 (unit: mm).
  • the path number N and the inner diameter ⁇ in (unit: mm) of the outer tube 28 satisfy one of relationships (1) to (5) below.
  • an outer diameter of the inner tube assembly 26 is equal to twice the outer diameter ⁇ out of the inner tube 24.
  • path number N As the path number N increases, the number of soldering points increases and the structures of the headers 16 and 22 become more complex. A path number N exceeding 8 makes mass production difficult even if it accomplishes weight reduction. Moreover, an excessively large path number N makes it difficult for the first fluid and the second fluid to flow through each of the heat exchange segments 10 uniformly. Thus, it is desirable that the path number N is in the range of 4 to 8.
  • the gap width G of zero makes it impossible to put the inner tube assembly 26 into the outer tube 28.
  • the gap width G is 0.16 mm or more.
  • a gap width G exceeding 0.8 mm may lower the heat transfer coefficient on the surface of the inner tube 24 and deteriorate the heat exchanging performance notably.
  • the gap width G has an upper limit of 0.8 mm.
  • Determinations of the inner diameter ⁇ in of the outer tube 28 and the gap width G determine the outer diameter ⁇ out of the inner tube 24.
  • the weight reduction of the heat exchanger 100 can be achieved by reducing the inner diameter ⁇ in of the outer tube 28 and/or the outer diameter ⁇ out of the inner tube 24, and furthermore, by reducing the thickness of the outer tube 28 and/or the thickness of the inner tube 24.
  • the inner tube 24 and the outer tube 28 each need a certain thickness.
  • the detection tube 30 is adjusted to have a thickness (thickness of a portion without a groove) in the range of 0.5 to 0.7 mm, for example.
  • the outer tube 28 is adjusted to have a thickness in the range of 0.5 to 0.7 mm, for example.
  • the smooth-inner-surface tube 32 is adjusted to have a thickness in the range of 0.2 to 0.4 mm, for example.
  • the smooth-inner-surface tube 32 (refrigerant tube) is required to have a thickness capable of withstanding the pressure of the refrigerant (first fluid).
  • An excessively large thickness of the smooth-inner-surface tube 32 affects the weight of the heat exchanger 100, costs, and the pressure loss of the refrigerant.
  • the thickness of the smooth-inner-surface tube 32 can be determined in the range of, for example, 12 to 20% (desirably 12 to 16%) of the outer diameter of the smooth-inner-surface tube 32 itself.
  • the heat exchanging capacity of the heat exchanger 100 is not particularly limited. It is in the range of 4.5 to 6.0 kW, for example.
  • the heat exchanger 100 having a heat exchanging capacity of such a magnitude can be used suitably for a home heat pump. Of course, in the case where a heat exchanging capacity larger than this is required, two units of the heat exchanger 100 can be used in parallel.
  • the heat exchange segments 10 are unbent in the present embodiment.
  • Each heat exchange segment 10 has a length of 2 to 5 meters, which depends on the path number N.
  • the heat exchange segment 10 may be bent in a scroll shape. Use of a slim tube for the heat exchange segment 10 may make it possible to decrease its bend radius and reduce a dead space.
  • FIG. 4 is a configuration diagram of a heat pump water heater 200 in which the heat exchanger 100 can be used.
  • the heat pump water heater 200 includes a heat pump unit 201 and a tank unit 203.
  • the hot water made in the heat pump unit 201 is held in the tank unit 203.
  • the hot water is supplied to a hot water tap 204 from the tank unit 203.
  • the heat pump unit 201 includes a compressor 205 for compressing a refrigerant, a radiator 207 for cooling the refrigerant, an expansion mechanism 209 for expanding the refrigerant, an evaporator 211 for evaporating the refrigerant, and refrigerant tubes 213 connecting these devices in this order.
  • the expansion mechanism 209 is an expansion valve. Instead of an expansion valve, a positive displacement expander capable of recovering the expansion energy of the refrigerant may be used.
  • the heat exchanger 100 can be used as the radiator 207.
  • the tank unit 203 includes a hot water storage tank 215 and a water circuit 217.
  • the water circuit 217 serves the role of circulating water through the radiator 207.
  • the weight of the heat exchanger described with reference to FIGs. 1 to 3 was calculated through computer simulation, with the inner diameter ⁇ in of the outer tube being fixed at 7.06 mm or 8.6 mm and the path number N being changed variously.
  • the gap width G was fixed at 0.4 mm.
  • the calculation result of the heat exchanger with the path number N being 2 and the inner diameter ⁇ in of the outer tube being 10.8 mm was prepared. While the heat exchanging capacity was kept at the value of the reference example (about 4.7 kW), the path number N was changed. That is, the length of each heat exchange segment (the length of the outer tube) was set so that the same heat exchanging capacity as that of the reference example was achieved.
  • the simulation conditions were as follows.
  • Table 1 and Table 2 show the results.
  • [Table 1] ⁇ 7.06 x 8 paths ⁇ 7.06 x 12 paths ⁇ 7.06 x 16 paths ⁇ 7.06 x 24 paths ⁇ 7.06 x 36 paths ⁇ 10.8 x 2 paths
  • Outer tube (Water) Outer diam eter [mm] 8.26 8.26 8.26 8.26 8.26 12.00
  • the graphs of FIG. 5 and FIG. 6 show the results in Table 3.
  • the horizontal axis indicates the path number N and the vertical axis indicates weight.
  • the leftmost marks correspond to the results of the reference example.
  • the horizontal axis indicates the inner diameter ⁇ in of the outer tube and the vertical axis indicates the path number N.
  • the horizontal axis indicates the inner diameter ⁇ in of the outer tube and the vertical axis indicates the path number N.
  • Table 4 shows the results in the case of (a).
  • Table 5 shows the results in the case of (b).
  • Table 6 shows the results in the case of (c).
  • FIG. 7 shows the results in Tables 3 to 6.
  • a gap width G exceeding 0.8 mm may lower the heat transfer coefficient on the surface of the inner tube and deteriorate the heat exchanging performance notably. Thus, no simulation was conducted in a range exceeding 0.8 mm.
  • the lower limit of the gap width G is not particularly limited. As shown in Table 6, however, the optimization of the gap width G can reduce the weight of the heat exchanger maximally compared to the case of the reference example.
  • the data obtained when the gap width G was optimized in a range in which the pressure loss of the second fluid (water) did not exceed a certain value indicates the gap width G that can minimize the weight of the heat exchanger.
  • the data obtained when the gap width G was optimized can be regarded as a suitable lower limit.
  • the lowest value of the gap width G is 0.16 mm, and the path number N at that time is 8.
  • the inner diameter ⁇ in of the outer tube when the gap width G is 0 mm is larger than the inner diameter ⁇ in of the outer tube when the gap width G is 0.4 mm.
  • the detection tube and the inner tube are regarded as one integrated tube, the presence of the detection tube does not affect the results of the simulation.
  • the detection tube has a fixed thickness of 0.68 mm. In the case where no detection tube is used, it is necessary to increase the thickness of the smooth-inner-surface tube in order to enhance the corrosion resistance.
  • the heat exchanger of the present invention can be used for apparatuses such as a heat pump type water heater and a hot water heating system.

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

Claims (7)

  1. Échangeur de chaleur (100) pour échanger de la chaleur entre un premier fluide et un deuxième fluide, comprenant :
    une pluralité de segments d'échange de chaleur (10) possédant chacun un premier passage d'écoulement (24h) et un deuxième passage d'écoulement (28h) ;
    un premier collecteur (16) disposé à une extrémité des segments d'échange de chaleur (10) de telle sorte que le premier fluide est introduit dans le premier passage d'écoulement (24h) et que le deuxième fluide est collecté à partir du deuxième passage d'écoulement (28h) ; et
    un deuxième collecteur (22) disposé à une autre extrémité des segments d'échange de chaleur (10) de telle sorte que le premier fluide est collecté à partir du premier passage d'écoulement (24h) et que le deuxième fluide est introduit dans le deuxième passage d'écoulement (28h),
    dans lequel chacun des segments d'échange de chaleur (10) est composé de (i) un ensemble tube interne (26), qui comprend deux tubes internes (24) présentant chacun le premier passage d'écoulement (24h) et qui est formé des deux tubes internes (24) torsadés en spirale, et de (ii) un corps externe (28) recevant l'ensemble tube interne (26) de telle sorte que le deuxième passage d'écoulement (28h) est formé entre une surface circonférentielle interne du corps externe et une surface circonférentielle externe de l'ensemble tube interne (26),
    caractérisé en ce que
    un nombre de trajets N indiquant le nombre des segments d'échange de chaleur (10) disposés entre le premier collecteur (16) et le deuxième collecteur (22) est de 4 à 8,
    une largeur d'interstice G représentée par une différence ((φin / 2) - φout) entre une moitié d'un diamètre interne φin du corps externe (28) et un diamètre externe φout du tube interne (24) satisfait à 0 < G ≤ 0,8 mm, et
    le nombre de trajets N et le diamètre interne φin du corps externe (28) satisfont à l'une parmi les relations (1) à (5) ci-dessous :
    (1) N = 4 et 8,20 ≤ φin ≤ 9,50 mm
    (2) N = 5 et 7,58 ≤ φin ≤ 8,90 mm
    (3) N = 6 et 7,14 ≤ φin ≤ 8,50 mm
    (4) N = 7 et 6,78 ≤ φin ≤ 8,20 mm
    (5) N = 8 et 6,52 ≤ φin ≤ 7,90 mm
  2. Échangeur de chaleur (100) selon la revendication 1, dans lequel la largeur d'interstice G satisfait à 0,16 ≤ G ≤ 0,8 mm.
  3. Échangeur de chaleur (100) selon la revendication 1, dans lequel les tubes internes (24) et le corps externe (28) sont constitués chacun d'un tube en cuivre.
  4. Échangeur de chaleur (100) selon la revendication 1, dans lequel les tubes internes (24) sont constitués chacun d'un tube en cuivre et le corps externe (28) est fabriqué à partir d'une résine.
  5. Échangeur de chaleur (100) selon la revendication 1, dans lequel les tubes internes (24) sont chacun un tube de détection de fuite composé d'un tube à surface interne lisse (32) et d'un tube à surface interne rainurée (30) disposé à l'extérieur autour du tube à surface interne lisse (32).
  6. Échangeur de chaleur (100) selon la revendication 1, dans lequel le premier fluide est du dioxyde de carbone et le deuxième fluide est de l'eau.
  7. Pompe à chaleur comprenant :
    un compresseur (205) pour comprimer un réfrigérant ;
    un radiateur (207) pour refroidir le réfrigérant comprimé, le radiateur (207) étant composé de l'échangeur de chaleur (100) selon l'une quelconque des revendications 1 à 6 ;
    un mécanisme de détente (209) pour détendre le réfrigérant refroidi ;
    un évaporateur (211) pour évaporer le réfrigérant détendu ; et
    un circuit d'eau (217) pour faire circuler l'eau à travers le radiateur (207).
EP12818246.6A 2011-07-22 2012-07-20 Échangeur de chaleur et pompe à chaleur utilisant cet échangeur Active EP2735832B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2011160927 2011-07-22
PCT/JP2012/004636 WO2013014899A1 (fr) 2011-07-22 2012-07-20 Echangeur de chaleur et pompe à chaleur utilisant cet échangeur

Publications (3)

Publication Number Publication Date
EP2735832A1 EP2735832A1 (fr) 2014-05-28
EP2735832A4 EP2735832A4 (fr) 2015-04-08
EP2735832B1 true EP2735832B1 (fr) 2020-02-05

Family

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EP12818246.6A Active EP2735832B1 (fr) 2011-07-22 2012-07-20 Échangeur de chaleur et pompe à chaleur utilisant cet échangeur

Country Status (4)

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EP (1) EP2735832B1 (fr)
JP (1) JP6037235B2 (fr)
CN (1) CN103562665B (fr)
WO (1) WO2013014899A1 (fr)

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Publication number Priority date Publication date Assignee Title
JP6400367B2 (ja) * 2014-07-23 2018-10-03 日野自動車株式会社 オゾン発生装置
CN106168451A (zh) * 2016-08-27 2016-11-30 山东绿泉空调科技有限公司 高效毛细管套管换热器
KR102134187B1 (ko) * 2016-10-20 2020-07-15 히다카 세이키 가부시키가이샤 열교환기용 핀 성형체의 반송 장치
NO345004B1 (en) * 2018-08-20 2020-08-17 Teknotherm Marine As Norway Evaporator and refrigeration system with evaporator
US11255614B2 (en) * 2019-07-29 2022-02-22 Hamilton Sundstrand Corporation Heat exchanger with barrier passages

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Publication number Priority date Publication date Assignee Title
JP3811123B2 (ja) * 2002-12-10 2006-08-16 松下電器産業株式会社 二重管式熱交換器
JP3919699B2 (ja) * 2003-06-03 2007-05-30 松下電器産業株式会社 熱交換装置及びヒートポンプ給湯装置
JP2005024109A (ja) 2003-06-30 2005-01-27 Hitachi Cable Ltd 熱交換器
JP4414197B2 (ja) * 2003-11-18 2010-02-10 株式会社ティラド ２重管式熱交換器
JP2007139284A (ja) * 2005-11-17 2007-06-07 Matsushita Electric Ind Co Ltd 熱交換装置およびそれを用いたヒートポンプ給湯装置
JP2008057859A (ja) * 2006-08-31 2008-03-13 Matsushita Electric Ind Co Ltd 熱交換装置およびそれを用いたヒートポンプ給湯装置
JP2008164245A (ja) * 2006-12-28 2008-07-17 Kobelco & Materials Copper Tube Inc 熱交換器
JP4921410B2 (ja) * 2007-03-31 2012-04-25 株式会社コベルコ マテリアル銅管 銅合金部材及び熱交換器
JP2009210232A (ja) * 2008-03-06 2009-09-17 Panasonic Corp 熱交換器
JP2009216315A (ja) * 2008-03-11 2009-09-24 Showa Denko Kk 熱交換器
US20120104046A1 (en) * 2009-06-26 2012-05-03 Carrier Corporation Semi-frozen product dispensing apparatus
JP2011085274A (ja) * 2009-10-13 2011-04-28 Panasonic Corp 熱交換器

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Also Published As

Publication number Publication date
JP6037235B2 (ja) 2016-12-07
EP2735832A4 (fr) 2015-04-08
WO2013014899A1 (fr) 2013-01-31
CN103562665A (zh) 2014-02-05
JPWO2013014899A1 (ja) 2015-02-23
CN103562665B (zh) 2015-10-21
EP2735832A1 (fr) 2014-05-28

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