EP3754284A1 - Échangeur de chaleur et dispositif de cycle de réfrigération - Google Patents

Échangeur de chaleur et dispositif de cycle de réfrigération Download PDF

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Publication number
EP3754284A1
EP3754284A1 EP20158255.8A EP20158255A EP3754284A1 EP 3754284 A1 EP3754284 A1 EP 3754284A1 EP 20158255 A EP20158255 A EP 20158255A EP 3754284 A1 EP3754284 A1 EP 3754284A1
Authority
EP
European Patent Office
Prior art keywords
flow path
heat exchanger
thickness
projection
inner pipe
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
EP20158255.8A
Other languages
German (de)
English (en)
Other versions
EP3754284B1 (fr
Inventor
Kazuki KOISHIHARA
Kazuhiko Machida
Yuki YAMAOKA
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Panasonic Intellectual Property Management Co Ltd
Original Assignee
Panasonic Intellectual Property Management Co Ltd
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Panasonic Intellectual Property Management Co Ltd filed Critical Panasonic Intellectual Property Management Co Ltd
Publication of EP3754284A1 publication Critical patent/EP3754284A1/fr
Application granted granted Critical
Publication of EP3754284B1 publication Critical patent/EP3754284B1/fr
Active legal-status Critical Current
Anticipated expiration legal-status Critical

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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
    • F28D7/0008—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits for one medium being in heat conductive contact with the conduits for the other medium
    • F28D7/0016—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits for one medium being in heat conductive contact with the conduits for the other medium the conduits for one medium or the conduits for both media being bent
    • 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
    • F25B39/04—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
    • 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
    • F28D7/022—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 two or more media in heat-exchange relationship being helically coiled, the coils having a cylindrical configuration
    • 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
    • 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
    • F28F1/00—Tubular elements; Assemblies of tubular elements
    • F28F1/08—Tubular elements crimped or corrugated in longitudinal section
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • 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
    • F28F1/34—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 obliquely
    • F28F1/36—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 obliquely the means being helically wound fins or wire spirals
    • 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
    • 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
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F19/00—Preventing the formation of deposits or corrosion, e.g. by using filters or scrapers
    • 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
    • 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

Definitions

  • the present invention relates to a heat exchanger which exchanges heat between low temperature liquid and high temperature liquid.
  • a heat exchanger of this kind heats water by refrigerant and produces high temperature water in many cases. It is known that if water becomes high temperature, solubility of gas (oxygen or nitrogen) existing in water is lowered, and the gas is precipitated into water as air bubble.
  • gas oxygen or nitrogen
  • the present invention has been accomplished to solve the conventional problem, and it is an object of the invention to provide a heat exchanger having high heat exchanging efficiency and capable of suppressing local precipitation of scale by simple means.
  • the present invention provides a heat exchanger including: an inner pipe; an insertion body inserted into the inner pipe; and at least one or more outer pipes provided around an outer periphery of the inner pipe and through which second fluid flows, wherein the insertion body is formed from a shaft and a projection formed on an outer surface of the shaft, first fluid flows through a spiral flow path formed from at least an inner surface of the inner pipe and the projection, and a plurality of thickness projections are provided on the spiral flow path at predetermined intervals in a flowing direction of the first fluid, and a flow path area of the spiral flow path is made small at the predetermined intervals in the flowing direction of the first fluid by each of the thickness projections.
  • a first invention provides a heat exchanger including: an inner pipe; an insertion body inserted into the inner pipe; and at least one or more outer pipes provided around an outer periphery of the inner pipe and through which second fluid flows, wherein the insertion body is formed from a shaft and a projection formed on an outer surface of the shaft, first fluid flows through a spiral flow path formed from at least an inner surface of the inner pipe and the projection, and a plurality of thickness projections are provided on the spiral flow path at predetermined intervals in a flowing direction of the first fluid, and a flow path area of the spiral flow path is made small at the predetermined intervals in the flowing direction of the first fluid by each of the thickness projections.
  • the thickness projections are formed by making a thickness of the projection in its axial direction at predetermined intervals in a circumferential direction of the projection thicker than other portions.
  • a line connecting length centers of the plurality of thickness projections in a circumferential direction thereof is in parallel to a center line of the insertion body in its axial direction.
  • an axial thickness of a root of the thickness projection is thicker than that of a tip end of the thickness projection.
  • flow speed of the first fluid can be increased at predetermined intervals without reducing a heat-transfer area on the side of the first fluid, i.e., a heat-transfer area between the inner pipe and the first fluid. Hence, it is possible to suppress the local growth of scale while maintaining performance of the heat exchanger.
  • an axial thickness of a root of the thickness projection is the greatest.
  • the inner pipe is an inner surface grooved pipe.
  • the inner pipe is the inner surface grooved pipe
  • a contact area between the pipe wall of the inner pipe and precipitating and adhering air bubble is reduced as compared with that of the flat pipe. Therefore, air bubble which adheres to the inner surface of the inner pipe can easily separate from the pipe wall. Hence, it becomes easier to wash away air bubble which adheres to the pipe wall of the inner pipe, and it is possible to suppress the local growth of scale.
  • the heat-transfer area on the side of the first fluid i.e., the heat-transfer area between the inner surface of the inner pipe and the first fluid is increased, and flow of water which is first fluid flowing in a spiral form can further be disturbed by the inner surface grove. Therefore, the performance of the heat exchanger can further be enhanced.
  • a seventh invention provides a refrigeration cycle device formed by annularly connecting, to one another, a compressor, a decompressor, an evaporator and the heat exchanger according to any one of the first to sixth inventions.
  • Fig. 1 is a circuit diagram of a refrigeration cycle device using a heat exchanger of the embodiment of the present invention.
  • the refrigeration cycle device 36 is formed by annularly connecting, to one another, a compressor 31 for compressing refrigerant which is second fluid, a heat exchanger 32 to which high temperature refrigerant compressed by the compressor 31 radiates heat and for heating water which is low temperature first fluid, a decompressor 33 for decompressing, to low pressure, high pressure refrigerant compressed by the compressor 31, and an evaporator 34 for absorbing heat by air flow generated by a blower 35.
  • the heat exchanger 32 water and refrigerant flow in directions opposed to each other and exchange heat therebetween.
  • Low temperature water is conveyed to the heat exchanger 32 by a conveying device 37, the water is heated by refrigerant and becomes hot water.
  • a warm water circuit 38 is connected to the heat exchanger 32, the heated hot water is supplied or utilized for heating a room, or the hot water is stored.
  • Fig. 2 is a perspective view of the heat exchanger of the embodiment of the invention.
  • the heat exchanger 32 is composed of an inner pipe 1 through which water flows, an insertion body 2 inserted into the inner pipe 1, and at least one or more outer pipes 3 which come into tight contact with an outer periphery of the inner pipe 1.
  • Refrigerant carbon dioxide
  • the outer pipe 3 is spirally wound around the outer periphery of the inner pipe 1 at a predetermined pitch.
  • the insertion body 2 is composed of a cylindrical shaft 21 and a projection 22 which is spirally provided on an outer periphery of the shaft 21. Water flows through a spiral flow path 23.
  • the spiral flow path 23 has a substantially rectangular cross section formed by an inner surface of the inner pipe 1 and a projection 22 which is adjacent to an outer surface of the shaft 21.
  • Fig. 3(a) is a sectional view of the heat exchanger of the embodiment taken along a surface A of the heat exchanger.
  • the projection 22 of the insertion body 2 in the cross section taken along the surface A is a standard projection 22a formed by a standard thickness.
  • Fig. 3(b) is a sectional view of the heat exchanger of the embodiment taken along a surface B of the heat exchanger.
  • the projection 22 of the insertion body 2 in the cross section taken along the surface B is thickness projections 22b which are thicker than the standard projection 22a in the axial direction.
  • the thickness projections 22b are formed thicker than the standard projection 22a in the axial direction at predetermined intervals in a circumferential direction of the thickness projections 22b.
  • a line which connects length centers of the plurality of thickness projections 22b in the circumferential direction is in parallel to a center line of the cylindrical shaft 21 of the insertion body 2 in the axial direction.
  • the thickness projections 22b provided in the spiral flow path 23 are opposed to each other in the axial direction. Therefore, a flow path area of the spiral flow path 23 becomes smaller at predetermined intervals in a flowing direction of water.
  • a thickness of the thickness projection 22b gradually becomes thicker in the axial direction from a tip end to a root of the thickness projection 22b in its height direction, and a length center of the root in the circumferential direction has the greatest thickness in the axial direction.
  • the thickness projections 22b are formed in the circumferential direction around an axis of the cylindrical shaft 21 of the insertion body 2 at predetermined intervals of 180°.
  • the insertion body 2 is made of resin material, since an axial thickness of a length center of the root of the thickness projection 22b in the circumferential direction is formed most thick, the insertion body 2 can be produced such that two lines connecting length centers of the roots of the plurality of thickness projections 22b in the circumferential direction are formed as dividing surface (PL) of a mold.
  • wettability Property that liquid adheres to a surface of a solid object is called "wettability".
  • a length of the inner surface of the inner pipe 1 which forms a cross section of a flow path of the spiral flow path 23 through which water flows is defined as a wetting length of a heat-transfer surface.
  • a wetting length Lb of the heat-transfer surface of the thickness projection 22b is about the same as a wetting length La of a heat-transfer surface of the standard projection 22a, and the inner surface of the inner pipe 1 is an inner surface grooved pipe which is finely grooved.
  • the heat exchanger 32 configured as described above is mounted in a CO 2 heat pump hot water supply system. Operation and effects of the heat exchanger 32 will be described below.
  • the heat exchanger flows, in opposed directions, high temperature carbon dioxide flowing through the outer pipe 3 and low temperature water flowing through the spiral flow path 23 formed between the inner pipe 1 and the insertion body 2, exchanges heat between the carbon dioxide and the low temperature water, and produces high temperature hot water.
  • heating temperature of water can be made high.
  • the projection 22 of the insertion body 2 has the thickness projections 22b which are thick in the axial direction at predetermined intervals as shown in Figs. 3(a) and 3(b) .
  • the spiral flow path 23 through which water flows is formed by the inner surface of the inner pipe 1, the outer surface of the shaft 21 and the outer surface of the standard projection 22a.
  • the spiral flow path 23 is formed by the inner surface of the inner pipe 1 and the outer surface of the thickness projection 22b.
  • the thickness of the projection 22 in the axial direction is formed such that the thickness of the thickness projection 22b is greater than that of the standard projection 22a, a cross section of the flow path through which water flows becomes smaller when water passes through the thickness projection 22b.
  • the thickness projections 22b are provided on the spiral flow path 23 at predetermined intervals in the flowing direction of water, and the cross section of the flow path is made small by narrowing a width of the flow path on the side of the outer surface of the shaft 21 instead of a width of the flow path on the side of the inner surface of the inner pipe 1.
  • the spiral flow path 23 through which water flows is formed by the inner surface of the inner pipe 1, the outer surface of the shaft 21 and the outer surface of the standard projection 22a. That is, a cross section of the flow path formed on the cross section A is defined as S1.
  • the spiral flow path 23 through which water flows is formed by the inner surface of the inner pipe 1 and the outer surface of the thickness projection 22b. That is, a cross section formed on the cross section B is defined as S2.
  • the thickness of the thickness projection 22b in the axial direction from the tip end to the root in the height direction gradually becomes thicker, and the axial thickness of the length center of the root in the circumferential direction is formed greatest.
  • the wetting length Lb of the heat-transfer surface of the thickness projection 22b is about the same as the wetting length La of the heat-transfer surface of the standard projection 22a.
  • the cross section of the flow path can be varied without varying the length of the inner surface of the inner pipe 1 which forms the cross section of the flow path of the spiral flow path 23 through which water flows.
  • the flow speed of water can be made greater by reducing the cross section area of the flow path as compared with a case where the spiral flow path 23 is formed by the standard projection 22a.
  • Fig. 4(a) is a conceptual diagram of flow speed distribution of the first fluid taken along the surface A of the heat exchanger of the embodiment of the invention.
  • the projection 22 of the insertion body 2 in the cross section taken along the surface A is the standard projection 22a having a standard thickness.
  • Fig. 4(b) is a conceptual diagram of flow speed distribution of the first fluid taken along the surface B of the heat exchanger of the embodiment of the invention.
  • the projection 22 of the insertion body 2 in the cross section taken along the surface B is the thickness projection 22b which is thicker in the axial direction than the standard projection 22a.
  • ⁇ shearing stress of viscose fluid
  • ⁇ viscosity coefficient
  • du/dz velocity gradient in a direction perpendicular to flow.
  • the shearing stress ⁇ of viscose fluid is proportional to velocity gradient in the direction perpendicular to flow.
  • velocity gradient near the wall surface of the spiral flow path 23 is greater when the spiral flow path 23 is formed by the thickness projections 22b. Therefore, when the spiral flow path 23 is formed by the thickness projections 22b, the shearing stress of water flowing through the spiral flow path 23 is also greater as compared with a case where the spiral flow path 23 is formed by the standard projection 22a.
  • the axial thicknesses of the thickness projections 22b are formed thicker than the standard projection 22a, and the thickness projections 22b are formed around the axis of the cylindrical shaft 21 of the insertion body 2 at predetermined intervals of 180°.
  • the line which connects length centers of the plurality of thickness projections 22b in the circumferential direction is in parallel to the center line of the cylindrical shaft 21 of the insertion body 2 in the axial direction.
  • the thickness projections 22b provided on the spiral flow path 23 are opposed to each other in the axial direction, the flow path area of the spiral flow path 23 becomes small every half around.
  • flow speed of water flowing through the spiral flow path 23 becomes greater at least every half around, and shearing stress also becomes greater.
  • Fig. 5(a) is a conceptual diagram of air bubble adhered to the inner surface of the inner pipe in the embodiment of the invention which is the grooved pipe.
  • Fig. 5(b) is a conceptual diagram of air bubble adhered to an inner surface of an inner pipe which is a flat pipe to compare with Fig. 5(a) .
  • the inner pipe 1 is an inner surface grooved pipe whose inner surface is finely grooved.
  • a contact area between the heat-transfer surface and air bubble which adheres to the heat-transfer surface when the inner pipe 1 is the inner surface grooved pipe is smaller than a contact area between the heat-transfer surface and air bubble which adheres to the heat-transfer surface when the inner pipe 1 is a flat pipe.
  • the inner pipe 1 is the inner surface grooved pipe
  • a contact area between the pipe wall of the inner pipe 1 and air bubble which is precipitates and adhered is reduced as compared with that of the flat pipe, and air bubble adhered to the inner surface of the inner pipe 1 can be separated from the pipe wall more easily. Therefore, it is possible to more easily wash away air bubble adhered to the pipe wall of the inner pipe 1, and to suppress the local growth of scale.
  • carbon dioxide is used as refrigerant which flows in the outer pipe 3, it is possible to use hydrocarbon-based refrigerant or HFC-based (R410A, R32 and the like) refrigerant, or alternative refrigerant thereof.
  • the thickness projections 22b are formed around the axis of the cylindrical shaft 21 of the insertion body 2 at predetermined intervals of 180°, but even if other angle is employed, the same effect can be obtained.
  • the heat exchanger of the present invention can suppress the local precipitation of scale by simple means and can realize high heat exchanging efficiency. Therefore, the heat exchanger can be applied to an air conditioner, a hot water supply system and the like.
EP20158255.8A 2019-05-31 2020-02-19 Échangeur de chaleur et dispositif de cycle de réfrigération Active EP3754284B1 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
JP2019101916A JP7129602B2 (ja) 2019-05-31 2019-05-31 熱交換器及びそれを備えた冷凍サイクル装置

Publications (2)

Publication Number Publication Date
EP3754284A1 true EP3754284A1 (fr) 2020-12-23
EP3754284B1 EP3754284B1 (fr) 2022-03-23

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EP20158255.8A Active EP3754284B1 (fr) 2019-05-31 2020-02-19 Échangeur de chaleur et dispositif de cycle de réfrigération

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JP (1) JP7129602B2 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN112944959A (zh) * 2021-03-09 2021-06-11 格力电器（武汉）有限公司 旋流扰动装置及换热管结构

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP2148161A2 (fr) * 2008-07-24 2010-01-27 Delphi Technologies, Inc. Ensemble d'échangeur thermique interne
WO2017158938A1 (fr) 2016-03-16 2017-09-21 三菱電機株式会社 Système d'échange de chaleur et procédé de suppression de tartre pour système d'échange de chaleur
EP3290854A1 (fr) * 2015-04-28 2018-03-07 Panasonic Intellectual Property Management Co., Ltd. Échangeur de chaleur et dispositif à cycle de réfrigération utilisant celui-ci
EP3614074A1 (fr) * 2018-07-20 2020-02-26 Valeo Japan Co., Ltd. Échangeur thermique à double tuyau

Family Cites Families (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP4423956B2 (ja) 2003-12-10 2010-03-03 パナソニック株式会社 熱交換器およびそれを備えた衛生洗浄装置
JP6471353B2 (ja) 2015-04-28 2019-02-20 パナソニックＩｐマネジメント株式会社 熱交換器およびそれを用いたヒートポンプ給湯機

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP2148161A2 (fr) * 2008-07-24 2010-01-27 Delphi Technologies, Inc. Ensemble d'échangeur thermique interne
EP3290854A1 (fr) * 2015-04-28 2018-03-07 Panasonic Intellectual Property Management Co., Ltd. Échangeur de chaleur et dispositif à cycle de réfrigération utilisant celui-ci
WO2017158938A1 (fr) 2016-03-16 2017-09-21 三菱電機株式会社 Système d'échange de chaleur et procédé de suppression de tartre pour système d'échange de chaleur
EP3614074A1 (fr) * 2018-07-20 2020-02-26 Valeo Japan Co., Ltd. Échangeur thermique à double tuyau

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN112944959A (zh) * 2021-03-09 2021-06-11 格力电器（武汉）有限公司 旋流扰动装置及换热管结构
CN112944959B (zh) * 2021-03-09 2022-05-24 格力电器（武汉）有限公司 旋流扰动装置及换热管结构

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JP7129602B2 (ja) 2022-09-02
JP2020197311A (ja) 2020-12-10
EP3754284B1 (fr) 2022-03-23

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