WO2002025189A1 - Echangeur thermique et son procede de realisation - Google Patents

Echangeur thermique et son procede de realisation Download PDF

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Publication number
WO2002025189A1
WO2002025189A1 PCT/JP2001/008241 JP0108241W WO0225189A1 WO 2002025189 A1 WO2002025189 A1 WO 2002025189A1 JP 0108241 W JP0108241 W JP 0108241W WO 0225189 A1 WO0225189 A1 WO 0225189A1
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WO
WIPO (PCT)
Prior art keywords
pressure side
flow path
heat exchanger
refrigerant
tube body
Prior art date
Application number
PCT/JP2001/008241
Other languages
English (en)
Japanese (ja)
Inventor
Akihiko Takano
Shunichi Furuya
Original Assignee
Zexel Valeo Climate Control Corporation
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 Zexel Valeo Climate Control Corporation filed Critical Zexel Valeo Climate Control Corporation
Publication of WO2002025189A1 publication Critical patent/WO2002025189A1/fr

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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
    • F28D7/0025—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 flat tubes or arrays of tubes
    • 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
    • F25B40/00—Subcoolers, desuperheaters or superheaters
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F1/00—Tubular elements; Assemblies of tubular elements
    • F28F1/02—Tubular elements of cross-section which is non-circular
    • F28F1/022—Tubular elements of cross-section which is non-circular with multiple channels
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
    • F28F9/02—Header boxes; End plates
    • F28F9/0202—Header boxes having their inner space divided by partitions
    • F28F9/0204—Header boxes having their inner space divided by partitions for elongated header box, e.g. with transversal and longitudinal partitions
    • F28F9/0214—Header boxes having their inner space divided by partitions for elongated header box, e.g. with transversal and longitudinal partitions having only longitudinal partitions
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2309/00—Gas cycle refrigeration machines
    • F25B2309/06—Compression machines, plants or systems characterised by the refrigerant being carbon dioxide
    • F25B2309/061—Compression machines, plants or systems characterised by the refrigerant being carbon dioxide with cycle highest pressure above the supercritical pressure
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B9/00—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point
    • F25B9/002—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point characterised by the refrigerant
    • F25B9/008—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point characterised by the refrigerant the refrigerant being carbon dioxide

Definitions

  • the present invention relates to a heat exchanger that is used in a compression refrigeration cycle that circulates refrigerant and exchanges heat between a high-pressure side and a low-pressure side of the refrigerant, and a method for manufacturing the same.
  • the refrigeration efficiency can be improved by exchanging heat between the high pressure side and the low pressure side of the refrigerant.
  • Heat exchangers for exchanging heat between the high-pressure side and the low-pressure side of the refrigerant are also described in Japanese Patent Application Laid-Open Nos. Hei 9-111, 152, and Hei 11-114,207. o
  • a tube is formed in a spiral shape, and refrigerant inlet portions are provided on the outer side and the center side of the spiral, respectively.
  • the one provided with the outlet portion has a complicated structure for circulating the refrigerant and is very difficult to manufacture.
  • the C 0 2 is adopted as the refrigerant
  • the refrigeration Saikuru is used the pressure inside the radiator exceed the critical point of the refrigerant.
  • a refrigeration cycle in which the pressure inside the radiator exceeds the critical point of the refrigerant requires extremely high pressure resistance, and the heat exchanger described above can improve the heat exchange efficiency and endure the refrigerant pressure. Configuration is required.
  • the present invention has been made in view of the above circumstances, and provides a heat exchanger capable of efficiently exchanging heat between a high pressure side and a low pressure side of a refrigerant and a method for manufacturing the same. It is intended to provide. Disclosure of the invention
  • the invention described in claim 1 of the present application is used in a compression type refrigeration cycle that circulates refrigerant, and in a heat exchanger that exchanges heat between a high pressure side and a low pressure side of the refrigerant, the heat exchanger is A tube body through which the high-pressure side and the low-pressure side refrigerant flows, and performing the heat exchange by heat transmitted to the tube body, wherein the tube body has a line of the high-pressure side refrigerant flow paths.
  • An end of the tube body has an inlet section of the first flow path layer.
  • the heat exchanger has a structure in which a refrigerant and an outlet are provided, and the inlet and the outlet of the second flow path layer are provided. According to such a structure, the high-pressure side and the low-pressure side of the refrigerant are efficiently heated. Exchanged o
  • the tube body by arranging the refrigerant passages on the high pressure side and arranging the refrigerant passages on the low pressure side, the heat transfer surface with the refrigerant on the high pressure side and the refrigerant passage on the low pressure side are arranged.
  • the heat transfer surface of the refrigerant is expanded, and the heat transfer between the two refrigerants is ensured.
  • the diameter of each refrigerant channel is relatively small, it is possible to ensure high pressure resistance.
  • the heat exchanger has a simple configuration. And can be easily manufactured.
  • the one end of the tube body is provided with an inlet of the first flow path layer and an outlet of the second flow path layer.
  • a heat exchanger having a structure in which an outlet of the first flow path layer and an inlet of the second flow path layer are provided at the other end of the tube body.
  • the refrigerant on the side flows from one end of the tube to the other end, and the refrigerant on the low pressure side flows from the other end of the tube to one end.
  • the high-pressure side and the low-pressure side of the coolant flow in directions opposite to each other.
  • the heat exchange efficiency of the heat exchanger is further improved. If the high-pressure refrigerant and the low-pressure refrigerant flow in the same direction, a satisfactory temperature difference is obtained near the outlet of the first flow channel layer and the outlet of the second flow channel layer. In some cases, such an inconvenience is avoided according to the configuration of the present invention.
  • the invention described in claim 3 of the present application is the invention according to claim 1 or 2, wherein the tube body is a heat exchanger configured by a single extruded tube.
  • the road is formed as small as possible.
  • the invention described in claim 4 of the present application is the invention according to claim 1 or 2, wherein the tube body is formed by assembling or brazing a plurality of extruded tubes, and the plurality of extruded tubes are provided with the plurality of extruded tubes.
  • This is a heat exchanger having a configuration in which one of the first flow path layer and the second flow path layer is provided. According to such a configuration, each refrigerant flow path is formed as small as possible. Further, an inlet and an outlet of the first channel layer and an inlet and an outlet of the second channel layer are provided for each tube.
  • the invention described in claim 5 of the present application is the invention according to any one of claims 1 to 4, wherein the tube body includes at least one of the first channel layer and the second channel layer.
  • the second flow path layer or the first flow path layer is interposed between the plurality of first flow path layers or the plurality of second flow path layers. Heat transfer between them is performed more reliably.
  • the tube body in claim 6 of the present application, includes one first flow path layer and two second flow path layers sandwiching the first flow path layer. According to such a configuration, the tube body is configured in a well-balanced manner.
  • the invention described in claim 7 of the present application is the heat exchanger according to any one of claims 1 to 6, wherein the inlet portion and the outlet portion of the first flow path layer are symmetrical to each other. According to such a configuration, the flow velocity distribution of the refrigerant in the first flow path layer is set in a well-balanced manner.
  • the invention described in claim 8 of the present application is directed to any one of claims 1 to 7
  • the inlet and outlet of the second flow path layer are heat exchangers that are symmetrical to each other. According to such a configuration, the flow velocity distribution of the refrigerant in the second flow path layer is set in a well-balanced manner. Is done.
  • the heat exchanger in the heat exchanger according to any one of the first to eighth aspects, has a configuration in which a heat insulating material is attached around the tube body. And the heat exchange between the high-pressure refrigerant and the low-pressure refrigerant is promoted. As a result, the performance of the refrigeration cycle is improved.
  • the invention described in claim 10 of the present application is the liquid crystal display device according to any one of claims 1 to 9, wherein, with respect to a cross section of the tube body, a sum of cross sectional areas in the refrigerant flow path on the high pressure side is X, and When the sum of the cross-sectional areas in the refrigerant passage on the low pressure side is Y, these are
  • the flow rates of the high-pressure side and the low-pressure side refrigerant are ensured in a well-balanced manner, and as a result, the heat exchange efficiency is improved.
  • the sum of the cross-sectional areas of the low-pressure side refrigerant flow path is expressed by the cross-sectional area of the high-pressure side refrigerant flow path.
  • the sum X of the cross-sectional area in the refrigerant passage on the high-pressure side and the sum ⁇ of the cross-sectional area in the refrigerant passage on the low-pressure side are: ,
  • the flow rates of the refrigerant on the high-pressure side and the low-pressure side are ensured in a more balanced manner.
  • condition of claim 8 is further limited in terms of numerical values while considering heat exchange efficiency. It is set between 1.7 times and 5.0 times.
  • the present invention is configured such that by setting the equivalent diameter Dl 3 D 2 to such a value, the pressure resistance and the heat exchange property can be suitably secured while suppressing the flow path resistance to a practical range. I have.
  • the invention described in claim 13 of the present application is characterized in that, in the heat exchanger according to any one of claims 1 to 12, the amount of heat transferred between the high pressure side and the low pressure side of the refrigerant is The amount of heat transferred when the temperature difference of
  • the heat exchanger has a configuration of about 60 to 95 [%]. With such a configuration, the performance of the heat exchanger is sufficiently ensured. In other words, the ratio of the amount of heat transferred between the high pressure side and the low pressure side of the refrigerant increases as the length of the tube increases, and decreases as the length of the tube decreases. By setting the amount of heat transferred between the pressure side and the low-pressure side to such a value, it is possible to avoid unnecessary increase in the size and weight of the heat exchanger and to achieve better performance. I have.
  • the invention described in claim 14 of the present application is the heat exchanger according to any one of claims 1 to 13, wherein the refrigeration cycle is configured such that a pressure inside a radiator exceeds a critical point of the refrigerant. It is.
  • the critical point is the limit on the high temperature side (that is, the limit on the high pressure side) where the gas layer and the ⁇ layer coexist, and is the end point of one of the vapor pressure curves.
  • the pressure, temperature, and density at, respectively, are the critical pressure, critical temperature, and critical density. If the pressure exceeds the critical point of the refrigerant inside the radiator, the refrigerant will not condense.
  • the heat exchanger can efficiently exchange heat between the high-pressure side and the low-pressure side of the refrigerant, and is suitably used in a refrigeration cycle in which the pressure inside the radiator exceeds the critical point of the refrigerant. Is done.
  • the invention described in claim 15 of the present application is used in a compression type refrigeration cycle for circulating a refrigerant, and in a method of manufacturing a heat exchanger for exchanging heat between a high pressure side and a low pressure side of the refrigerant, the method comprises:
  • the heat exchanger includes a tube body through which the high-pressure side and the low-pressure side coolant flows, and performs the heat exchange by heat transmitted to the tube body.
  • a second flow path layer in which the low-pressure-side refrigerant flow paths are arranged in a row, and the first flow path layer and the second flow path layer are arranged in a row.
  • a plurality of extruded tubes provided on one side are brazed, and when brazing the plurality of extruded tubes, fins are arranged on the surface of the extruded tube, and then the fins are placed.
  • This is a method of manufacturing a heat exchanger with a According to such a configuration, the plurality of extruded Ji Interview part, is efficiently brazed by heat transmitted to the fins, the heat exchanger is easily manufactured.
  • FIG. 1 is a schematic diagram showing a refrigeration cycle according to a specific example of the present invention.
  • FIG. 2 is a perspective view showing a heat exchanger according to a specific example of the present invention.
  • FIG. 3 is a cross-sectional view illustrating a tube body according to a specific example of the present invention.
  • FIG. 4 is a perspective view illustrating a manufacturing step of the tube body according to a specific example of the present invention.
  • FIG. 5 is a perspective view showing a tube body manufacturing process according to a specific example of the present invention.
  • FIG. 6 is a perspective view showing a tank according to a specific example of the present invention.
  • FIG. 7 is a perspective view showing a heat exchanger according to a specific example of the present invention.
  • FIG. 8 is a perspective view showing a heat exchanger according to a specific example of the present invention.
  • FIG. 9 is a cross-sectional view showing a tube body according to a specific example of the present invention.
  • FIG. 10 is a cross-sectional view showing a tube body according to a specific example of the present invention.
  • FIG. 11 is a cross-sectional view illustrating a main part of a heat exchanger according to a specific example of the present invention.
  • the compression-type refrigeration cycle 1 shown in FIG. 1 is used for in-vehicle cooling mounted on an automobile, and includes a compressor 2 for compressing a refrigerant and a radiator 3 for cooling the refrigerant compressed by the compressor 2.
  • a decompressor 4 that decompresses and expands the refrigerant cooled by the radiator 3, an evaporator 5 that evaporates the refrigerant depressurized by the decompressor 4, and a refrigerant that flows out of the evaporator 5 into a gas layer.
  • An accumulator 6 that separates the refrigerant into a liquid layer and sends the refrigerant in the gas layer to the compressor 2 is provided.
  • the coolant adopts a C 0 2, the internal pressure of the radiator 3, the operating conditions such as air temperature, exceed the critical point of the refrigerant.
  • a heat exchanger 7 for exchanging heat between the high-pressure side and the low-pressure side of the refrigerant is provided between the radiator 3 and the decompressor 4 and between the accumulator 6 and the compressor 2. Is provided.
  • the heat exchanger 7 improves the efficiency of the refrigeration cycle 1 by exchanging heat between the high-pressure side refrigerant and the low-pressure side refrigerant.
  • the white arrow in the drawing indicates the direction in which the high-pressure side refrigerant flows, and the black arrow indicates the direction in which the low-pressure side refrigerant flows.
  • the heat exchanger 7 of the present embodiment includes a tube body 110 through which the high-pressure side and the low-pressure side refrigerant flows, and heat is transferred by the heat transferred to the tube body 7 10.
  • the tube body 7110 has a first flow path layer 711 formed by arranging high-pressure side refrigerant flow paths 711a and a second flow path layer formed by arranging a low-pressure side refrigerant flow path 712a. And two flow path layers 12.
  • the high-pressure side refrigerant flow path 711a and the low-pressure side refrigerant flow path 712a are illustrated in the form of elliptical ones, or they may be circular, elliptical, or square. , Triangular, etc.
  • the equivalent diameter of the high-pressure side refrigerant flow path 71 1a and the equivalent diameter of the low-pressure side refrigerant flow path 71 2a are determined in consideration of pressure resistance, heat exchange property, and flow path resistance. It is set in the range of ⁇ 1.2 [mm].
  • the tube body 7100 is formed by brazing a plurality of flat extruded tubes. Specifically, one extruded tube provided with the first flow path layer 711 and the second flow path Two extruded tubes provided with layers 7 12 are laminated in parallel and alternately, and this is heated and brazed by heating in a furnace.
  • the tube body 7 10 includes one first flow path layer 7 1 1 and two second flow path layers 7 1 2 sandwiching the first flow path layer 7 1 1, and is connected to the high pressure side of the refrigerant. Heat exchange with the low pressure side takes place between these layers.
  • the dimensions of the tube body 70 of this example are 30 to 60 [mm] in width and 4.5 to 9.0 [mm] in thickness.
  • the length is set in consideration of the balance between heat exchange performance and installation space.
  • the inlet 7 2 0 of the first flow path layer 7 1 1 connects the piping 1 10 on the radiator 3 side
  • a joint type joint block 721, a single pipe section 722 extending from the joint block 721, and a sunset section 723 communicating the tip of the pipe section 722 are provided.
  • One end of an extruded tube provided with the first flow path layer 7 11 is inserted into the tank section 7 23 and brazed.
  • the first flow path layer 7 11 communicates with the tank section 7 23.
  • the outlet section 730 of the first flow path layer 111 is a union-type joint block 732 that connects the pipe 120 on the pressure reducer 4 side, and one pipe section extending from the joint block 732.
  • the extruded tube provided with the first flow path layer 7 1 1 and the tank 7 3 3 is provided with a nozzle section 7 3 3 communicating the tip of the pipe section 7 32 The other end is inserted and brazed.
  • the first flow path layer 7 11 communicates with the tank section 7 33.
  • the inlet part 7400 of the second flow path layer 712 is composed of a union type joint work 741 for connecting the pipe 13 on the accumulator 6 side, and two pipe parts 7 extending from the joint work 741. 4 2 and two tank sections 7 4 3 communicating the ends of the pipe sections 7 4 2 with each other, and two extrusions provided with a second flow path layer 7 1 2 for each tank section 7 4 3 One end of the molded tube is inserted and brazed, respectively.
  • the second flow path layer 7 12 communicates with the tank section 7 43.
  • the outlet 750 of the second flow path layer 712 is a union type joint block 715 for connecting the piping 140 on the compressor 2 side, and two pipe sections extending from the joint block 750. 7 5 2 and two tanks 7 5 3 communicating the ends of the pipes 7 52 respectively, and two extrusions provided with a second flow path layer 7 1 2 for each tank 7 5 3 The other end of the molded tube is inserted and brazed, respectively.
  • the second flow path layer 7 12 communicates with the tank section 753.
  • an inlet 720 of the first flow channel layer 711 and an outlet 7500 of the second flow channel layer 7112 are provided at one end of the tube 7 10,
  • the outlet portion 730 of the flow channel layer 711 and the inlet portion 740 of the second flow channel layer 712 are provided at the other end of the tube body 710. Accordingly, the high-pressure side refrigerant flows from one end of the tube: 110 to the other end, and the low-pressure side refrigerant flows from the other end of the tube body 110 to one end. Flows to That is, in the tube body 110, the high-pressure side and the low-pressure side of the refrigerant flow in directions opposite to each other.
  • the heat exchange efficiency of the heat exchanger 7 can be further improved by flowing the high-pressure side and the low-pressure side of the refrigerant in directions facing each other. If the high-pressure side refrigerant and the low-pressure side refrigerant flow in the same direction, the outlet section 7300 of the first flow path layer 711 and the outlet section 7500 of the second flow path layer 7 In the vicinity, those temperature differences may not be obtained satisfactorily, but according to the configuration of this example, such inconvenience can be avoided.
  • the tank 723 of the inlet 720 and the tank 734 of the outlet 73.0 are as follows. It has a cylindrical shape along the width direction of the first flow path layer 711.
  • the pipe section 722 of the inlet section 702 and the pipe section 732 of the outlet section 730 communicate with both ends of the tank sections 723, 733 in different directions. ing.
  • the inlet part 720 and the outlet part 730 of the first flow path layer 71 1 are symmetric with each other.
  • the tank part 743 of the inlet part 7400 and the tank part 754 of the outlet part 750 It has a cylindrical shape along the width direction of the second flow path layer 712.
  • the pipe part 742 of the inlet part 7400 and the pipe part 752 of the outlet part 750 communicate with both ends of each tank part 743, 753 in different directions. ing.
  • the inlet 740 and the outlet 7500 of the second flow path layer 712 are symmetric with each other.
  • each joint block 7 2 1, 7 3 1, 7 4 1, 7 5 1 It can be set arbitrarily by bending the middle part of the eve parts 722, 732, 742, 752.
  • the value of ⁇ ⁇ ⁇ ⁇ with respect to X is set between 1.7 times and 5.0 times, and the total X of the cross-sectional areas in the high-pressure side refrigerant flow path and the low-pressure side refrigerant The sum of the cross-sectional areas in the channel is ⁇ ⁇
  • the low-pressure side refrigerant expands more reliably than the high-pressure side refrigerant, by adopting such a configuration in the tube body 710, the flow velocity difference between the high-pressure side and the low-pressure side refrigerant is reduced. The flow rate of the refrigerant has been reduced to ensure a good balance.
  • FIGS. 4 to 5 are perspective views showing the steps of manufacturing the tube body 710.
  • the tube body 710 is constructed by assembling each extruded tube, each pipe section 722, 132, 742, 752, and each tank section 723, 733, 743, 753, and heat-treating this assembly in a furnace. Attached. Prior to the heat treatment, brazing filler metal and flux are provided at key points of each member.
  • the brazing material is Si powder, which is mixed with a flux and applied.
  • fins F are arranged on the surface of each extruded tube during the heat treatment (see FIG. 4). Fin F is removed after brazing (see Fig. 5). However, brazing of multiple extruded tubes is efficiently performed by the heat transmitted to the fins F. In addition, each joint pro- cess 721, 731, 741, 751 is provided by torch brazing after such brazing in a furnace. In other words, thermal deformation due to heat treatment in the furnace is avoided.
  • the heat exchanger 7 of the present embodiment can be easily manufactured, and can efficiently perform heat exchange between the high-pressure side and the low-pressure side of the refrigerant.
  • the temperature difference between the high pressure side and the low pressure side of the refrigerant is about 1 to 10 ° C.
  • the amount of heat that moves between the high-pressure side and the low-pressure side of the refrigerant is approximately 60 to 9 if the amount of heat that moves when the temperature difference is 0 ° C is 100 [%]. 5 [%].
  • the tube body 110 of this example was formed using an extruded tube, or if the required pressure resistance can be satisfactorily secured, a tube formed and brazed plate is used. May be configured.
  • the plate is formed by mouth forming or press forming.
  • the tube body 7 10 of this example is formed by brazing a plurality of extruded tubes. However, if sufficient heat exchange between the extruded tubes can be obtained, such brazing may be omitted. Good. That is, the tube body 7100 may be one in which a plurality of extruded tubes are assembled in close contact.
  • each part of the heat exchanger 7 can be further simplified by reducing the number of parts and using common parts.
  • each of the tank sections 7 2 3 and 7 5 3 at the inlet section 7 20 of the first flow path layer 7 11 and the outlet section 7 50 of the second flow path layer 7 12 it is also possible to constitute with an integral extruded member.
  • a brazing member is brazed to the key of the extruded member.
  • such an extruded member is referred to as each of the tank sections 7 2 3 and 7 5 3 at the outlet section 7 30 of the first channel layer 7 11 and the inlet section 7 40 of the second channel layer 7 12. It is also possible to make them common.
  • the heat exchanger includes the tube body through which the high-pressure side and the low-pressure side refrigerant flows, and is transmitted to the tube body.
  • the tube body is composed of a first flow path layer having a high-pressure side refrigerant flow path and a second flow path having a low-pressure side flow path. Since the inlet and outlet of the first channel layer and the inlet and outlet of the second channel layer are provided at the end of the tube body, the high pressure side of the refrigerant and the low pressure The heat can be exchanged efficiently with the side.
  • the heat transfer surface with the refrigerant on the high pressure side and the refrigerant passage on the low pressure side are arranged.
  • the heat transfer surface can be enlarged, and the heat transfer between the two refrigerants can be reliably performed.
  • the diameter of each refrigerant flow path is relatively small, high pressure resistance can be ensured.
  • the heat exchanger has a simple structure. It can be easily manufactured.
  • the heat exchanger of the present example at one end of the tube body, an inlet of the first flow path layer and an outlet of the second flow path layer are provided, and the other end of the tube body is provided. Since the outlet is provided with the outlet of the first channel layer and the inlet of the second channel layer, the heat exchange efficiency of the heat exchanger can be further improved. If the high-pressure refrigerant and the low-pressure refrigerant flow in the same direction, the temperature difference between the outlets of the first and second flow path layers will not be satisfactory. However, according to the configuration of the present invention, such inconvenience can be avoided.
  • the tube body is formed by assembling or brazing a plurality of extruded tubes, and the plurality of extruded tubes are provided with the first flow path layer and the second flow tube. Since one of the road layers is provided, each of the refrigerant passages can be formed as small as possible. The inlet and outlet of the first channel layer and the inlet and outlet of the second channel layer can be provided for each tube.
  • the tube body includes at least one of the first flow path layer and the second flow path layer, the plurality of first flow path layers or the plurality of first flow path layers are provided.
  • the second channel layer or the first channel layer is interposed between the second channel layers, so that heat transfer between the two refrigerants can be performed more reliably.
  • the tube body includes one first flow path layer and two second flow path layers sandwiching the second flow path layer, so that the tube body can be configured in a well-balanced manner. it can.
  • the inlet and outlet of the first flow path layer are symmetrical with each other, so that the flow velocity distribution of the refrigerant in the first flow path layer can be set in a well-balanced manner.
  • the inlet and outlet of the second flow path layer are symmetrical to each other, so that the flow velocity distribution of the refrigerant in the second flow path layer can be set in a well-balanced manner.
  • the flow rates of the refrigerant on the high-pressure side and the low-pressure side can be ensured in a well-balanced manner, and as a result, the heat exchange efficiency can be improved.
  • the sum of the cross-sectional areas of the low-pressure side refrigerant flow path ⁇ is calculated as the cross-sectional area of the high-pressure side refrigerant flow path.
  • the values of X and ⁇ are more desirably limited while considering the heat exchange efficiency, and the value of ⁇ ⁇ ⁇ ⁇ for X is from 1.7 times. It is set between 5.0 times.
  • the equivalent diameter of the high-pressure side refrigerant flow path and the equivalent diameter D 2 of the low-pressure side refrigerant flow path are as follows:
  • the pressure resistance, the heat exchange property, and the flow path resistance can be set in a well-balanced manner.
  • the amount of heat that moves between the high-pressure side and the low-pressure side of the refrigerant is equal to the amount of heat that moves when the temperature difference becomes 0 ° C. If it is 0 [%], it is about 60-95 [%], so the performance of the heat exchanger can be satisfactorily secured.
  • the pressure inside the radiator exceeds the critical point of the refrigerant.
  • the heat exchanger can efficiently exchange heat between the high-pressure side and the low-pressure side of the refrigerant, and is suitably used in a refrigeration cycle in which the pressure inside the radiator exceeds the critical point of the refrigerant. can do.
  • the heat exchanger 7 of this example is provided around the tube body 7 10. It is equipped with a heat insulator 760.
  • the heat insulating member 760 is for ensuring heat insulation between the tube body 710 and the outside.
  • the heat insulating member 760 is a sponge made of rubber or synthetic resin. Since other configurations are the same as those of the above-described specific example, common members are denoted by the same reference numerals, and description thereof is omitted.
  • the heat exchanger of this example since the heat insulating material is attached around the tube body, heat insulation with the outside is secured, and heat exchange between the high-pressure refrigerant and the low-pressure refrigerant is performed. Can be promoted. As a result, the performance of the frozen cycle can be further improved.
  • the heat exchanger 7 of the present example is formed by bending a tube body 710 into a U-shape. Since other configurations are the same as those of the above-described specific example, common members are denoted by the same reference numerals and description thereof is omitted.
  • the tube body may be appropriately shaped in consideration of the installation space of the heat exchanger.
  • the tube body 110 of the present example is composed of two extruded tubes provided with a first flow path layer 711, and three extruded tubes provided with a second flow path layer 712. Tubes are stacked in parallel and alternately and brazed.
  • the pipe section is used for the inlet section 720 and the outlet section 730 of the first flow path layer 711 and the inlet section 740 and the outlet 750 of the second flow path layer 712.
  • the tube body may be provided with more first and second flow path layers.
  • the tube body 7 10 of the present example is composed of a single extruded tube.
  • Each tank section 72 3, 73 33, 74 43, 75 53 is provided for such a single extruded tube.
  • the ends of the extruded tube, considering each tank section 7 2 3 7 3 3 7 4 3 7 5 3 of assembly property, Note c is subjected to appropriate processing, the other configurations Since this is the same as the specific example described above, common members are denoted by the same reference numerals, and description thereof is omitted.
  • each refrigerant channel can be formed as small as possible. Further, the first channel layer and the second channel layer can be provided integrally without brazing. Industrial applicability
  • the present invention is a heat exchanger and its production method used in a refrigeration cycle generally for automobiles and home air conditioners, among others, to adopt the example C 0 2 as the refrigerant, the critical point of the pressure inside the radiator coolant It is suitable for refrigeration cycles that exceed the above.

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

Abstract

La présente invention concerne un échangeur thermique (7) et un procédé permettant sa réalisation. L'échangeur thermique, utilisé dans un cycle de réfrigération à compression à circulation d'agent réfrigérant (1), et permettant l'échange de chaleur entre des zones haute pression et basse pression de l'agent réfrigérant, comprend un corps tubulaire (710) permettant à l'agent réfrigérant de le traverser dans les zones haute pression et basse pression afin de réaliser un échange de chaleur par utilisation de la conduction thermique à travers le corps tubulaire. Ledit corps tubulaire comprend également une première couche de passage de flux (711) formée grâce à la mise en place d'un passage de flux d'agent réfrigérant côté haute pression (711), et une seconde couche de passage de flux formée grâce à la mise en place d'un passage de flux d'agent réfrigérant côté basse pression (712a), la partie d'entrée (720) et la partie de sortie (730) de la première couche de passage de flux, et la partie d'entrée (740) et la partie de sortie (750) de la seconde couche de passage de flux, se trouvant dans la partie d'extrémité du corps tubulaire.
PCT/JP2001/008241 2000-09-25 2001-09-21 Echangeur thermique et son procede de realisation WO2002025189A1 (fr)

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JP2000-290454 2000-09-25
JP2000290454A JP2002098486A (ja) 2000-09-25 2000-09-25 熱交換器及びその製造方法

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Cited By (5)

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FR2823839A1 (fr) * 2001-04-24 2002-10-25 Modine Mfg Copmpany Echangeur de chaleur
WO2004033947A1 (fr) * 2002-09-20 2004-04-22 Erbslöh Aluminium Gmbh Echangeur de chaleur, procede pour produire un echangeur de chaleur, et profile composite extrude utilise dans un tel procede
FR2863044A1 (fr) * 2003-11-27 2005-06-03 Valeo Climatisation Module pour l'echange de chaleur entre fluides en circulation
FR2907888A1 (fr) * 2007-01-16 2008-05-02 Air Liquide Procede de vaporisation d'un liquide cryogenique dans un echangeur de chaleur, et echangeur de chaleur operant selon un tel procede
FR2926877A1 (fr) * 2008-01-30 2009-07-31 Air Liquide Echangeur de chaleur et dispositif de refroidissement comprenant un tel echangeur

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JP2004177006A (ja) * 2002-11-27 2004-06-24 Japan Climate Systems Corp 内部熱交換器
JP4348113B2 (ja) 2003-05-23 2009-10-21 株式会社ヴァレオサーマルシステムズ 熱交換器
JP3821113B2 (ja) * 2003-05-23 2006-09-13 株式会社デンソー 熱交換用チューブ
JP4196774B2 (ja) 2003-07-29 2008-12-17 株式会社デンソー 内部熱交換器
JP4536459B2 (ja) * 2004-08-25 2010-09-01 株式会社ティラド 熱交換器用チューブおよび熱交換器
JP4561305B2 (ja) * 2004-10-18 2010-10-13 三菱電機株式会社 熱交換器
ES2447776T3 (es) * 2006-04-14 2014-03-12 Mitsubishi Denki Kabushiki Kaisha Intercambiador de calor y acondicionador de aire refrigerante
JP2009079781A (ja) * 2007-09-25 2009-04-16 Mitsubishi Electric Corp 熱交換器及びこの熱交換器を用いたヒートポンプ給湯機またはヒートポンプ空気調和機
WO2010084732A1 (fr) * 2009-01-20 2010-07-29 ダイキン工業株式会社 Échangeur de chaleur à eau et dispositif de source d'eau chaude
US20110277494A1 (en) * 2009-01-22 2011-11-17 Tomonori Kikuno Heat exchanger and heat pump type hot water supply apparatus equipped with same
JP5141730B2 (ja) * 2010-07-23 2013-02-13 三菱電機株式会社 熱交換器及び冷凍空調装置
JP2013127346A (ja) * 2011-12-19 2013-06-27 Daikin Industries Ltd 熱交換器
WO2013114435A1 (fr) * 2012-01-31 2013-08-08 三菱電機株式会社 Échangeur de chaleur et système de pompe à chaleur
WO2013132544A1 (fr) * 2012-03-07 2013-09-12 三菱電機株式会社 Echangeur de chaleur et système de pompe à chaleur avec échangeur de chaleur
JP5784215B2 (ja) * 2012-03-07 2015-09-24 三菱電機株式会社 熱交換器および冷凍サイクル装置
WO2015025365A1 (fr) * 2013-08-20 2015-02-26 三菱電機株式会社 Échangeur de chaleur, climatiseur et dispositif à cycle frigorifique
JP5749786B2 (ja) * 2013-11-28 2015-07-15 株式会社前川製作所 熱交換器
JP7281059B2 (ja) * 2020-06-02 2023-05-25 三菱電機株式会社 熱交換器及びヒートポンプ装置

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JPH08303899A (ja) * 1995-04-28 1996-11-22 Matsushita Seiko Co Ltd 空調機用変換器
JPH10267565A (ja) * 1997-03-28 1998-10-09 Mitsubishi Electric Corp 熱交換器
JPH1183349A (ja) * 1997-08-29 1999-03-26 Hitachi Cable Ltd 自己温度制御機能を有する２層パイプ及びこれを用いた熱交換器
JP2001343173A (ja) * 2000-05-31 2001-12-14 Matsushita Electric Ind Co Ltd Ｃｏ２冷媒用冷凍サイクル装置

Cited By (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2823839A1 (fr) * 2001-04-24 2002-10-25 Modine Mfg Copmpany Echangeur de chaleur
AU784140B2 (en) * 2001-04-24 2006-02-09 Modine Manufacturing Company Heat exchanger header construction
WO2004033947A1 (fr) * 2002-09-20 2004-04-22 Erbslöh Aluminium Gmbh Echangeur de chaleur, procede pour produire un echangeur de chaleur, et profile composite extrude utilise dans un tel procede
FR2863044A1 (fr) * 2003-11-27 2005-06-03 Valeo Climatisation Module pour l'echange de chaleur entre fluides en circulation
WO2005064258A1 (fr) * 2003-11-27 2005-07-14 Valeo Climatisation Module pour l'echange de chaleur entre fluides en circulation
FR2907888A1 (fr) * 2007-01-16 2008-05-02 Air Liquide Procede de vaporisation d'un liquide cryogenique dans un echangeur de chaleur, et echangeur de chaleur operant selon un tel procede
FR2926877A1 (fr) * 2008-01-30 2009-07-31 Air Liquide Echangeur de chaleur et dispositif de refroidissement comprenant un tel echangeur

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