EP3290854A1 - Wärmetauscher und kältekreislaufvorrichtung damit - Google Patents

Wärmetauscher und kältekreislaufvorrichtung damit Download PDF

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Publication number
EP3290854A1
EP3290854A1 EP16786106.1A EP16786106A EP3290854A1 EP 3290854 A1 EP3290854 A1 EP 3290854A1 EP 16786106 A EP16786106 A EP 16786106A EP 3290854 A1 EP3290854 A1 EP 3290854A1
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EP
European Patent Office
Prior art keywords
heat exchanger
pipe
spiral
inner pipe
insertion body
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Granted
Application number
EP16786106.1A
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English (en)
French (fr)
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EP3290854B1 (de
EP3290854A4 (de
Inventor
Kazuki KOISHIHARA
Kazuhiko Machida
Yuuki Yamaoka
Osamu Aoyagi
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Panasonic Intellectual Property Management Co Ltd
Original Assignee
Panasonic Intellectual Property Management Co Ltd
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Publication of EP3290854A1 publication Critical patent/EP3290854A1/de
Publication of EP3290854A4 publication Critical patent/EP3290854A4/de
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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
    • F28F13/00—Arrangements for modifying heat-transfer, e.g. increasing, decreasing
    • F28F13/06—Arrangements for modifying heat-transfer, e.g. increasing, decreasing by affecting the pattern of flow of the heat-exchange media
    • F28F13/12—Arrangements for modifying heat-transfer, e.g. increasing, decreasing by affecting the pattern of flow of the heat-exchange media by creating turbulence, e.g. by stirring, by increasing the force of circulation
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24H—FLUID HEATERS, e.g. WATER OR AIR HEATERS, HAVING HEAT-GENERATING MEANS, e.g. HEAT PUMPS, IN GENERAL
    • F24H9/00—Details
    • 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
    • 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
    • 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
    • F28D7/04—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 spirally coiled
    • 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
    • F28D7/10—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 one within the other, e.g. concentrically
    • 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
    • F28D7/10—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 one within the other, e.g. concentrically
    • F28D7/106—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 one within the other, e.g. concentrically consisting of two coaxial conduits or modules of two coaxial 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
    • F28F21/00—Constructions of heat-exchange apparatus characterised by the selection of particular materials
    • F28F21/06—Constructions of heat-exchange apparatus characterised by the selection of particular materials of plastics material

Definitions

  • the present invention relates to a heat exchanger that exchanges heat between fluids.
  • a heat exchanger has been proposed in which a water pipe and a refrigerant pipe are wound in a double spiral shape (e.g., see PTL 1). Furthermore, a heat exchanger has been proposed in which a refrigerant pipe is wound around a water pipe (e.g., see PTL 2).
  • a heat pump hot water dispenser mounting thereon such a heat exchanger is a device that boils water over a predetermined time mainly during night time, and flow speed of water flowing in the heat exchanger equipped in the hot water dispenser is relatively slow during boiling operation.
  • a flow of the water flowing in the heat exchanger is a laminar flow, so that in order to improve heat transfer performance as a heat exchanger, improving heat transfer performance on a water side is necessary by making the flow of water be disturbed.
  • FIG. 11 is a schematic view (partial cross sectional view) of a conventional heat exchanger described in PTL 1.
  • FIG. 12 is an enlarged view illustrating a cross section of the heat exchanger in FIG. 11 .
  • Heat exchanger 201 includes water pipe 202 and one or more of refrigerant pipe(s) 203 for one water pipe 202.
  • Water pipe 202 is formed in a substantially cylindrical shape by being spirally wound.
  • Refrigerant pipe 203 is spirally wound around an outer periphery of water pipe 202 formed in the substantially cylindrical shape at predetermined pitches. Furthermore, at least one portion of refrigerant pipe 203 is jointed across substantially entire length of water pipe 202.
  • a direction of water flowing in water pipe 202 and a direction of refrigerant flowing in refrigerant pipe 203 are opposed directions.
  • Winding water pipe 202 in a spiral shape as described above makes centrifugal force act on the water flowing in the water pipe, causing a secondary flow as illustrated by arrows in FIG. 12 in a cross section perpendicular to a pipe axis.
  • largeness of the centrifugal force acting on the water flowing in the spiral flow path is described by a following formula based on balance of force.
  • F centrifugal force
  • V cubic volume
  • ⁇ denotes density
  • v denotes rotation speed
  • r radius of rotation
  • a temperature field in the cross section perpendicular to main stream is improved by the secondary flow even when the flow of water is the laminar flow, making it possible to drastically improve heat transfer performance as compared with a heat exchanger having a straight pipe shape in which a water pipe and a refrigerant pipe are jointed.
  • FIG. 13 is a schematic view of a conventional heat exchanger described in PTL 2.
  • Heat exchanger 301 includes water pipe 302 having a straight portion and one or more refrigerant pipe(s) 303 for one water pipe 302.
  • Refrigerant pipe 303 is wound around water pipe 302, and a twisted tape as a heat transfer facilitating means is inserted inside water pipe 302.
  • the configuration in above PTL 1 forms a heat exchanger by winding the pipe in a spiral shape, so that the water pipe can be flattened or buckled depending on a material of the pipe, a diameter of the pipe, and a thickness of the pipe.
  • curvature diameter D of the spiral tube needs to be made large to prevent buckling by increasing a thickness of the water pipe in consideration of thickness reduction due to flattening. This results in increase in cost and unfortunately makes a volume of the heat exchanger large. Furthermore, there is a problem in that heat transfer facilitation effect due to the secondary flow caused by centrifugal force becomes small.
  • the present invention solves the above conventional problems, and aims to provide a heat exchanger that is compact, is superior in economic performance, and has high quality performance and high heat transfer performance.
  • a heat exchanger includes an inner pipe in which first fluid flows, an insertion body inserted in the inner pipe, and an outer pipe in which second fluid flows, the outer pipe being provided at an outer periphery of the inner pipe.
  • the insertion body has a shaft portion and a spiral projection portion formed on an outer surface of the shaft portion.
  • the first fluid flows in a spiral flow path formed by an inner surface of the inner pipe, the shaft portion, and the spiral projection portion.
  • a curvature diameter of the spiral flow path can be set smaller than a curvature diameter of a conventional spiral flow path, making it possible to provide a heat exchanger that has a high heat transfer facilitating effect due the secondary flow and that is compact.
  • the maximum distance from a heat transfer surface of the first fluid is determined by a shaft diameter of the insertion body and a projection portion height of the spiral projection portion.
  • This allows a flow path cross sectional area to be designed by changing a pitch of the spiral projection portion so as to be water pressure loss that can be allowed by a water sending pump. This makes it possible to provide a heat exchanger that drastically reduces a dead water area within a water pressure loss limitation range and that has high heat transfer performance.
  • the present invention makes it possible to provide a heat exchanger that is compact, is superior in economic performance, and has high quality performance and high heat transfer performance.
  • a heat exchanger includes an inner pipe in which first fluid flows, an insertion body inserted in the inner pipe, and an outer pipe in which second fluid flows, the outer pipe being provided at an outer periphery of the inner pipe.
  • the insertion body has a shaft portion and a spiral projection portion formed on an outer surface of the shaft portion.
  • the first fluid flows in a spiral flow path formed by an inner surface of the inner pipe, the shaft portion, and the spiral projection portion.
  • a curvature diameter of the spiral flow path can be made smaller as compared with a curvature diameter of a conventional spiral flow path, making it possible to provide a heat exchanger that has a large heat transfer facilitation effect due to the secondary flow and that is compact.
  • the maximum distance from a heat transfer surface of the first fluid is set to a shaft diameter of the insertion body and a height of the spiral projection portion, and a flow path cross sectional area can be set so as to be a pressure loss that can be allowed by a sending pump, making it possible to provide a heat exchanger having high heat exchange performance in which a dead water area is drastically reduced within a pressure loss limitation range as compared with a conventional heat exchanger.
  • a second invention is configured such that a winding direction of the outer pipe and a spiral direction of the spiral projection portion are same directions, and a flow of the first fluid and a flow of the second fluid are configured to be opposed flows, specifically in the first invention.
  • a third invention is configured such that the outer pipe is disposed at the outer periphery of the inner pipe and at an opposing portion of the spiral flow path, specifically in the first or second invention.
  • a fourth invention includes a joint for fixing the inner pipe and the insertion body, specifically in any one of the first to third inventions.
  • the spiral projection portion includes a plurality of projections in contact with the inner pipe, specifically in any one of the first to fourth inventions.
  • the plurality of projections is sequentially aligned along a shaft direction.
  • This increases a bypass amount of the first fluid that flows in the gap during large flow rate in which centrifugal force acting on the first fluid is large while agitating the flow by the secondary flow.
  • the present invention increases a flow rate capable of being sent by a pump having a same lifting height, making it possible to assure a flow rate enough to keep an output flow temperature of the first fluid at not more than a predetermined temperature, improving reliability of equipment.
  • a sixth invention satisfies, given that a distal end width and a proximal end width of the spiral projection portion are respectively t1 and t2, a relationship of t1 ⁇ t2 is satisfied, specifically in any one of the first to fifth inventions.
  • a seventh invention is a refrigeration cycle device including a refrigerant circuit in which at least a compressor, the heat exchanger according to any one of the first to sixth inventions, a decompressor, and an evaporator are circularly connected, and a controller.
  • the refrigeration cycle device has a defrosting operation mode for defrosting frost formation of the evaporator, and the insertion body is made of a resin.
  • Making a portion of the flow path for the first fluid be formed by a resin having specific heat larger than that of a metal increases the accumulated heat quantity of the heat exchanger, making it possible to use more heat quantity during defrosting from the heat exchanger. This makes it possible to terminate defrosting operation within a short period, improving defrosting performance of equipment.
  • FIG. 1 is a schematic view (partial cross sectional view) of heat exchanger 11 according to a first exemplary embodiment of the present invention.
  • Heat exchanger 11 according to the first exemplary embodiment of the present invention includes inner pipe 1, outer pipe 3 spirally wound around an outer surface of inner pipe 1 to be in close contact therewith, and insertion body 2 to be inserted inside inner pipe 1.
  • Insertion body 2 includes insertion body shaft portion 21 and spiral projection portion 22.
  • a spiraled winding direction of outer pipe 3 and a spiral direction of spiral protection portion 22 are the same directions, and winding pitches thereof are also same.
  • Heat exchanger 11 makes water that is first fluid and carbon dioxide that is second fluid exchange heat via inner pipe 1 and outer pipe 3.
  • a flow path in which water flows is a spiral flow path formed by an inner surface of inner pipe 1, an outer surface of the insertion body shaft portion 21 and adjacent spiral projection portions 22, and is formed by two parts that are inner pipe 1 and the insertion body 2 to be inserted in inner pipe 1.
  • curvature diameter D of the spiral flow path and heat-transfer coefficient in the pipe will be described.
  • the vertical axis denotes Nusselt number Nu and the lateral axis denotes d/D.
  • the heat-transfer coefficient in the pipe becomes high, improving heat-transfer performance of the heat exchanger.
  • (d/D) of the of the heat exchanger as described in PTL 1 that is mounted on an existing heat pump hot water dispenser is not more than 0.2.
  • the spiral flow path is structured by two parts, enabling curvature diameter D of the spiral flow path in which water flows to be drastically smaller as compared with a curvature diameter of a conventional spiral flow path. This increases (d/D), increasing agitation effect due to the secondary flow. This improves heat-transfer facilitation effect and makes it possible to provide a compact heat exchanger.
  • FIGS. 2A and 2B each are a perspective view illustrating a flow of fluid flowing in heat exchanger 11 according to the first exemplary embodiment of the present invention.
  • Water that is the first fluid flows in the spiral flow path formed by the inner surface of inner pipe 1, the outer surface of insertion body shaft portion 21, and adjacent spiral projection portions 22. Pitches of the spiral projection portion 22 of the insertion body 2 and the wounding direction are synchronized, and carbon dioxide that is the second fluid that flows inside outer pipe 3 wound around an opposing portion of the spiral flow path and water that is the first fluid exchange heat.
  • the water that flows in the spiral flow path between inner pipe 1 and insertion body 2 and the carbon dioxide that flows inside outer pipe 3 are inverse in their flowing directions, making it possible to exchange heat by the opposed flow across the substantially whole area of heat exchanger 11 as indicated by the flows illustrated in FIGS. 2A and 2B , making it possible to provide a high efficient heat exchanger.
  • outer pipe 3 is not necessarily wound around the opposing portion of the spiral flow path as long as heat exchange efficiency required by equipment on which the heat exchanger is mounted can be provided. Furthermore, a plurality of outer pipes 3 in which the second fluid flows may be included and the plurality of outer pipes 3 may be alternately wound around the opposing portion of the spiral flow path.
  • FIG. 3 is a cross sectional view of heat exchanger 11 according to the first exemplary embodiment of the present invention.
  • the water flow path of the heat exchanger includes two parts that are inner pipe 1 and insertion body 2, so that the maximum distance from a water side heat-transfer surface can be designed on the basis of diameter "a" of insertion body shaft portion 21 and projection portion height "th" of spiral projection portion 22.
  • flow path cross sectional area S can be designed by changing winding pitch P of spiral projection portion 22 of insertion body 2 so as to be water pressure loss that can be allowed by a water sending pump for sending water in equipment. This makes it possible to drastically reduce a dead water area within a water pressure loss limitation range.
  • diameter "a" of insertion body shaft portion 21 and projection portion height "th" of spiral projection portion 22 be designed such that heat exchange performance satisfies a predetermined performance within the range of the following (Formula 4). 1.0 ⁇ 10 ⁇ 2 ⁇ th a ⁇ 5
  • the flow path cross section of the spiral flow path that is a water flow path is formed to be a rectangular cross section by the inner surface of inner pipe 1, insertion body shaft portion 21, and spiral projection portion 22, readily generating eddy as compared with the case where the cross section is circular shape, increasing effect by the secondary flow.
  • the water flow path is structured by the two parts that are inner pipe 1 and insertion body 2 having spiral projection portion 22, forming the spiral flow path without winding inner pipe 1.
  • curvature diameter D of the spiral flow path can be drastically reduced as compared with a curvature diameter of a conventional spiral flow path, making it possible to provide a heat exchanger that is compact and that has high heat-transfer performance.
  • the maximum distance from the heat transfer surface of the water side flow path can be designed by diameter "a" of insertion body shaft portion 21 and height "th" of the projection portion of spiral projection portion 22, and flow path cross sectional area S can be designed by changing winding pitch P of spiral projection portion 22 such that water pressure loss becomes within a limitation.
  • FIGS. 5A and 5B each are an enlarged view of spiral projection portion 22 of insertion body 2 of heat exchanger 11 according to a second exemplary embodiment.
  • FIGS. 6A and 6B each are a cross sectional view of the heat exchanger according to the second exemplary embodiment.
  • FIG. 7 is a perspective view of a joint and an insertion body of the heat exchanger according to the second exemplary embodiment.
  • projections 25 that are sequentially aligned are provided along a shaft direction of heat exchanger 11, that is, along a shaft direction of insertion body 2 on the outer surface of spiral projection portion 22 of insertion body 2 forming heat exchanger 11 of the second exemplary embodiment.
  • an end in the shaft direction of insertion body 2 has convex portions 23, and joint 4 has concave portions 24 to be respectively engaged with convex portions 23 at the end of insertion body 2.
  • Insertion body 2 is fixed such that convex portions 23 of the end in the shaft direction of insertion body 2 and concave portions 24 of joint 4 are respectively fitted and projections 25 on the outer surface of spiral projection portion 22 are in contact with inner pipe 1.
  • shapes of fitting portions of insertion body 2 and joint 4 are respectively the convex portion and the concave portion in the second exemplary embodiment, the shapes thereof may be any shapes as long as the portions can be fitted.
  • a gap exists between spiral projection portion 22 excluding projections 25 and inner pipe 1, so that a flow path (bypass flow path 50) communicated along the shaft direction of heat exchanger 11, that is, along the shaft direction of insertion body 2 is formed in addition to the spiral flow path described in the first exemplary embodiment.
  • heat exchanger 11 of the second exemplary embodiment like the first exemplary embodiment, water that is the first fluid that flows in the spiral flow path formed between inner pipe 1 and insertion body 2 and carbon dioxide that is the second fluid that flows inside outer pipe 3 exchange heat by the opposed flow via inner pie 1 and outer pipe 3.
  • heated water can be disadvantageously boiled in heat exchanger 11, so that adjustment is performed such that a temperature of output hot water becomes not more than a predetermined temperature by increasing the flow rate of the water to be sent to heat exchanger 11.
  • heat exchanger 11 of the second exemplary embodiment has bypass flow path 50 communicated along the shaft direction of heat exchanger 11, that is, along the shaft direction of insertion body 2 between an inner surface of inner pipe 1 and spiral projection portion 22 excluding inner pipe 1 and projections 25 as illustrated in FIGS. 6A and 6B .
  • Increase of pressure loss during large flow rate can be thus suppressed as compared with the conventional heat exchanger described in above PTL 1, which reduces power required by a sending pump, improving energy saving performance of the equipment.
  • joint 4 is fitted with insertion body 2, and joint 4 covers inner pipe 1 from outside to be fixed by a fastening body such as insertion pin 5 (see FIG. 1 ), fixing positions of insertion body 2 and inner pipe 1.
  • a fastening body such as insertion pin 5 (see FIG. 1 ), fixing positions of insertion body 2 and inner pipe 1.
  • the second exemplified embodiment has projections 25 sequentially aligned along the shaft direction of heat exchanger 11 on the outer surface of spiral projection portion 22 of insertion body 2, and inner pipe 1 and insertion body 2 are fixed by joint 4 such that projections 25 and the inner surface of inner pipe 1 are in contact.
  • This makes it possible to form a flow path also in the shaft direction of heat exchanger 11 in addition to the spiral flow path, making it possible provide heat exchanger 11 that suppresses increase of water pressure loss also in the case where water that flows in heat exchanger 11 is large flow rate. This improves energy saving performance of equipment mounting thereon heat exchanger 11 of the second exemplary embodiment.
  • FIG. 8 is a cross sectional view of a heat exchanger according to a third exemplary embodiment. Note that the same numeral references are assigned to the same parts as those in the first and second exemplary embodiments of the present invention, and their detailed description will be omitted.
  • the heat exchanger according to a fourth exemplary embodiment of the present invention is configured such that the relationship between distal end width t1 and proximal end width t2 of spiral projection portion 22 of insertion body 2 satisfies t1 ⁇ t2.
  • water that is the first fluid that flows in the spiral flow path formed between inner pipe 1 and insertion body 2 and carbon dioxide that is the second fluid that flows inside outer pipe 3 exchange heat by the opposed flow via inner pie 1 and outer pipe 3.
  • Width L of a heat transfer surface for water that is the first fluid that flows in the spiral flow path formed between inner pipe 1 and insertion body 2 with respect to carbon oxide that is the second fluid that flows inside outer pipe 3 of heat exchanger 11 is P - t1 obtained by subtracting distal end width t1 of spiral projection portion 22 from spiral pitch P of spiral projection portion 22 as illustrated in FIG. 8 .
  • the shape of spiral projection portion 22 of insertion body 2 is formed to satisfy t1 ⁇ t2. This makes it possible to increase width L of the heat transfer surface for water that is the first fluid that flows in the spiral flow path formed between inner pipe 1 and insertion body 2 with respect to carbon dioxide that is the second fluid that flows inside outer pipe 3 as compared with the case where a thickness of the spiral projection portion 22 is constant while keeping water side flow path cross sectional area S same as that in the case where a thickness of the spiral projection portion 22 is constant as illustrated in FIG. 3 for the first exemplary embodiment.
  • heat transfer area for water that is the first fluid that flows in the spiral flow path formed between inner pipe 1 and insertion body 2 with respect to carbon dioxide that is the second fluid that flows inside outer pipe 3 increases, making it possible to provide a heat exchanger having higher transfer performance.
  • FIG. 9 illustrates a relationship between insertion projection distal end width t1 and heat exchange capability Q under the conditions in which a length of the spiral flow path formed between inner pipe 1 and insertion body 2 and water side flow path cross sectional area S are constant, that is, under the condition in which water side pressure loss is equivalent.
  • the heat transfer area for water that is the first fluid that flows in the spiral flow path formed between inner pipe 1 and insertion body 2 with respect to carbon oxide that is the second fluid that flows inside outer pipe 3 becomes larger as distal end width t1 of spiral projection portion 22 becomes smaller. This improves heat exchange performance.
  • a proximal shape of spiral projection 22 may be R-character shape to suppress separation of the secondary flow at a proximal portion and reduce water side pressure loss. This makes it possible to reduce friction loss of water due to eddy, making it possible to improve energy efficiency of the heat exchanger of the present exemplary embodiment or equipment mounting thereon the heat exchanger of the present exemplary embodiment.
  • the relationship between distal end width t1 and proximal end width t2 of the spiral projection 22 of insertion body 2 satisfies t1 ⁇ t2.
  • This makes it possible to lengthen the length of heat transfer surface for water that is the first fluid that flows in the spiral flow path formed between inner pipe 1 and insertion body 2 with respect to carbon oxide that is the second fluid that flows inside outer pipe 3 without changing water side flow path conditions (length of the spiral flow path formed between inner pipe 1 and insertion body 2 and water side flow path cross sectional area S), that is, under an equivalent water side pressure loss condition.
  • This makes it possible to increase the heat transfer area, making it possible to provide a heat exchanger having high heat exchange performance.
  • FIG. 10 is a configuration diagram of a refrigeration cycle device according to a fourth exemplary embodiment.
  • FIG. 10 is a refrigeration cycle device to be mounted on, for example, a heat pump hot water dispenser.
  • the refrigeration cycle device includes compressor 101, radiator 102 that is heat exchanger 11 according to any of first to third exemplary embodiments of the present invention, decompressor 103 that is an electronic expansion valve, and evaporator 104, which are circularly connected to form refrigerant circuit 105.
  • the refrigerant circuit includes evaporator outlet port temperature detection means 107 for detecting a temperature of refrigerant flown away from evaporator 104, and the refrigeration cycle device has controller 110 and a defrosting operation mode.
  • Carbon oxide as refrigerant is enclosed in refrigerant circuit 105, and a high-pressure side of compressor 101 is operated in a super criticality state during operation of compressor 101.
  • insertion body 2 having spiral projection portion 22 structuring radiator 102 (heat exchanger 11 according to the first exemplary embodiment or the second exemplary embodiment of the present invention) is made of a resin having volumetric specific heat larger than that of a metal (copper: 0.04 J/m 3 ⁇ K, PPS: 0.65J/m 3 ⁇ K).
  • the refrigerant compressed to be a high pressure to be ejected is sent to radiator 102 to release heat by exchanging heat with low temperature water sent by water sending pump 113 via inflow water pipe 111.
  • the refrigerant flown away from radiator 102 is supplied to decompressor 103 to be decompressed and expanded to be sent to evaporator 104, and the refrigerant exchanges heat with air introduced by air blower 106 to be evaporated to be gasified.
  • the gasified refrigerant is suctioned in compressor 101.
  • controller 110 performs defrosting operation for defrosting the frost attached to evaporator 104 to recover heat exchange performance of evaporator 104.
  • the defrosting operation is performed when frost is attached to evaporator 104 and the temperature detected by evaporator outlet port temperature detection means 107 falls below a predetermined temperature.
  • the defrosting operation will be specifically described.
  • controller 110 makes water sending pump 113 for sending water to radiator 102 and air blower 106 stop their operation to reduce a flow path friction of decompressor 103.
  • the high temperature refrigerant compressed by compressor 101 passes through radiator 102 and decompressor 103, flows in evaporator 104 to perform defrosting by heat owned by the refrigerant, and suctioned in compressor 101.
  • evaporator 104 is defrosted by utilizing heat quantity accumulated in radiator 102 in addition to heat quantity of the refrigerant ejected from compressor 101.
  • Making insertion body 2 that is a portion of the flow path for radiator 102 be made of a resin having specific heat larger than that of a metal (copper: 0.04 J/m 3 ⁇ K, PPS: 0.65J/m 3 ⁇ K) increases heat quantity accumulated in radiator 102, making it possible to utilize larger heat quantity from radiator 102 during defrosting. This makes it possible to terminate the defrosting operation in a short period, improving defrosting performance of equipment.
  • insertion body 2 having spiral projection portion 22 shall be made of a resin (PPS), but the same function effect can be expected as long as a resin other than PPS or a material having large volumetric specific heat is used.
  • PPS resin
  • the refrigerant that flows in outer pipe 3 shall be carbon oxide, but the same function effect can be expected by using refrigerant of hydrocarbon system or HFC system (R410A, etc.) or substitute refrigerant thereof.
  • the heat exchanger according to the present invention makes it possible to provide a heat exchanger that is compact, superior in economic performance, and high in quality performance and heat exchange performance. Therefore, the present invention is applicable to equipment mounting thereon a heat exchanger that exchanges heat between fluids.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
EP16786106.1A 2015-04-28 2016-04-05 Wärmetauscher und kältekreislaufvorrichtung damit Active EP3290854B1 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2015091026 2015-04-28
PCT/JP2016/001909 WO2016174826A1 (ja) 2015-04-28 2016-04-05 熱交換器およびそれを用いた冷凍サイクル装置

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EP3290854A1 true EP3290854A1 (de) 2018-03-07
EP3290854A4 EP3290854A4 (de) 2018-05-02
EP3290854B1 EP3290854B1 (de) 2021-12-22

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JP (1) JP6687022B2 (de)
CN (1) CN107532870B (de)
WO (1) WO2016174826A1 (de)

Cited By (1)

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EP3754284A1 (de) * 2019-05-31 2020-12-23 Panasonic Intellectual Property Management Co., Ltd. Wärmetauscher und kühlzyklusvorrichtung

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EP3290854B1 (de) 2021-12-22
EP3290854A4 (de) 2018-05-02
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