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WO2019021345A1 - 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
WO2019021345A1
WO2019021345A1 PCT/JP2017/026674 JP2017026674W WO2019021345A1 WO 2019021345 A1 WO2019021345 A1 WO 2019021345A1 JP 2017026674 W JP2017026674 W JP 2017026674W WO 2019021345 A1 WO2019021345 A1 WO 2019021345A1
Authority
WO
WIPO (PCT)
Prior art keywords
heat exchanger
pipe
recess
flow
heat medium
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.)
Ceased
Application number
PCT/JP2017/026674
Other languages
English (en)
Japanese (ja)
Inventor
健太 村田
徹 小出
悟 梁池
幸大 宮川
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.)
Mitsubishi Electric Corp
Original Assignee
Mitsubishi Electric Corp
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 Mitsubishi Electric Corp filed Critical Mitsubishi Electric Corp
Priority to CN201780092652.4A priority Critical patent/CN110892223B/zh
Priority to JP2019532231A priority patent/JP6735924B2/ja
Priority to EP17919080.6A priority patent/EP3660435B1/fr
Priority to PCT/JP2017/026674 priority patent/WO2019021345A1/fr
Publication of WO2019021345A1 publication Critical patent/WO2019021345A1/fr
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

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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
    • F28D7/02—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
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B30/00—Heat pumps
    • F25B30/02—Heat pumps of the compression type
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D7/00—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
    • F28D7/0008—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
    • 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
    • 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
    • F28F1/06—Tubular elements of cross-section which is non-circular crimped or corrugated in cross-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
    • F28F1/08—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
    • F28F1/42—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being both outside and inside the tubular element
    • F28F1/424—Means comprising outside portions integral with inside portions
    • F28F1/426—Means comprising outside portions integral with inside portions the outside portions and the inside portions forming parts of complementary shape, e.g. concave and convex
    • 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
    • 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
    • F28F2001/027—Tubular elements of cross-section which is non-circular with dimples
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F2210/00—Heat exchange conduits
    • F28F2210/06—Heat exchange conduits having walls comprising obliquely extending corrugations, e.g. in the form of threads

Definitions

  • the present invention relates to a heat exchanger including a first pipe and a second pipe wound around the first pipe, and a refrigeration cycle apparatus including the heat exchanger.
  • a heat exchanger equipped.
  • heat exchange is performed between the first heat medium flowing in the first pipe and the second heat medium flowing in the second pipe.
  • the first pipe may be referred to as a core pipe.
  • the second pipe may be referred to as an outer pipe.
  • the first heat medium includes water or antifreeze.
  • the second heat medium may, for example, be a refrigerant.
  • a first fluid pipe formed by twisting and having a plurality of ridges and valleys in the outer periphery continuously provided spirally for each row, And a second fluid piping spirally wound along the shape of the bottom of the first fluid piping, and the second fluid piping is fitted into the bottom of the first fluid piping to achieve heat transfer.
  • a “twisted-tube type heat exchanger” has been proposed which can be joined to
  • the present invention has been made against the above-mentioned problems as a background, and a heat exchanger designed to improve the heat exchange performance by suppressing the stagnation of the flow of the first heat medium in the first pipe. And, it is an object of the present invention to provide a refrigeration cycle apparatus provided with the heat exchanger.
  • a first pipe in which a first flow path through which a first heat medium flows is formed and a second flow path through which a second heat medium flows is formed, and the first pipe And a second pipe wound around the first pipe, and the first pipe is formed of a mountain portion protruding in the radial direction in which the diameter of the first pipe is expanded, and a portion where the mountain portion is formed
  • the outer diameter is also small, and it includes a valley portion around which the second pipe is wound, and the peak portion is spirally formed in the direction in which the first heat medium of the first flow path flows,
  • the portion includes a recess formed in a spiral shape along the peak portion, formed in a spiral direction which is a formation direction of the valley portion, and recessed in a diameter reducing direction in which the diameter of the first pipe decreases.
  • the first peak portion which is the peak portion of the Nth cycle among the spiral turns of the peak portion and the N + 1th round of the spiral portion of the peak portion
  • a portion of the first pipe including the second peak portion which is a portion and the intermediate valley portion which is the valley portion between the first peak portion and the second peak portion, the first heat medium
  • the recess is positioned such that the apex of the recess is located downstream of the middle point of the middle valley in the flow direction of the first heat medium, in a cross-sectional view taken along the flow direction of It is formed.
  • the flow velocity of the first heat medium in the stagnation portion of the first heat medium in the peak portion on the downstream side of the concave portion is specified by specifying the formation position of the concave portion formed in the valley portion. It is hard to fall off and the heat exchange performance can be improved.
  • FIG. 1 is a schematic configuration view schematically showing an example of a circuit configuration of a refrigeration cycle apparatus 200 provided with a heat exchanger 100 according to Embodiment 1 of the present invention.
  • the refrigeration cycle apparatus 200 will be described with reference to FIG.
  • the first heat medium is water
  • the second heat medium is a refrigerant.
  • the refrigeration cycle apparatus 200 includes a refrigerant circuit A1 and a heat medium circuit A2.
  • the refrigerant circuit A1 and the heat medium circuit A2 are thermally connected via the heat exchanger 100.
  • the heat medium circuit A2 is connected to the water supply circuit A3 via the hot water storage tank 207.
  • the water supply circuit A3 is connected to the hot water supply utilization unit U and configured to supply hot water to the hot water supply utilization unit U.
  • As the hot water supply utilization unit U at least one of various loads for which hot water is required, such as a faucet of a household water tap and a bath, may be mentioned.
  • the water supply circuit A3 is connected to a water pipe or the like, and is configured to be able to supply water.
  • a refrigerant circulates to refrigerant circuit A1 via refrigerant piping 20A.
  • Carbon dioxide can be employed as the refrigerant.
  • the refrigerant circuit A1 is formed to include a compressor 201 for compressing a refrigerant, a heat exchanger 100 functioning as a condenser, a throttling device 202, and a heat exchanger 203 functioning as an evaporator.
  • the compressor 201 compresses a refrigerant.
  • the refrigerant compressed by the compressor 201 is discharged from the compressor 201 and sent to the heat exchanger 100.
  • the compressor 201 can be configured by, for example, a rotary compressor, a scroll compressor, a screw compressor, or a reciprocating compressor.
  • the heat exchanger 100 functions as a condenser, performs heat exchange between the high-temperature high-pressure refrigerant flowing in the refrigerant circuit A1 and the water flowing in the heat medium circuit A2, heats water, and condenses the refrigerant. is there.
  • the heat exchanger 100 is a water-refrigerant heat exchanger that exchanges heat between water and a refrigerant.
  • the heat exchanger 100 will be described in detail later.
  • the heat exchanger 100 corresponds to the heat exchanger of the present invention.
  • the expansion device 202 expands and reduces the pressure of the refrigerant flowing out of the heat exchanger 100.
  • the expansion device 202 may be configured by, for example, an electric expansion valve capable of adjusting the flow rate of the refrigerant.
  • an electric expansion valve capable of adjusting the flow rate of the refrigerant.
  • the expansion device 202 not only a motorized expansion valve but also a mechanical expansion valve employing a diaphragm in a pressure receiving portion, a capillary tube or the like can be applied.
  • the heat exchanger 203 functions as an evaporator, exchanges heat between the low-temperature low-pressure refrigerant flowing out of the expansion device 202 and the air supplied by the blower 203A, and evaporates the low-temperature low-pressure liquid refrigerant or the two-phase refrigerant It is a thing.
  • the heat exchanger 203 is, for example, a fin and tube heat exchanger, a microchannel heat exchanger, a shell and tube heat exchanger, a heat pipe heat exchanger, a double pipe heat exchanger, or a plate heat exchange. It can be configured with a container or the like. Further, a fan 203A is attached to the heat exchanger 203.
  • the heat medium circuit A2 is formed to include the heat exchanger 100 and the pump 205 for transporting water.
  • the refrigeration cycle apparatus 200 includes a control device 60 that generally controls the entire refrigeration cycle apparatus 200.
  • the control device 60 controls the drive frequency of the compressor 201. Further, the control device 60 controls the degree of opening of the expansion device 202 according to the operating state. Further, the control device 60 controls the driving of the blower 203A and the pump 205. That is, based on the operation instruction, the control device 60 uses information sent from each temperature sensor not shown and each pressure sensor not shown, and the compressor 201, the expansion device 202, the fan 203A, the pump 205, etc. Control each actuator.
  • Each functional unit included in control device 60 is configured of dedicated hardware or an MPU (Micro Processing Unit) that executes a program stored in a memory.
  • MPU Micro Processing Unit
  • FIG. 2 is a perspective view schematically showing the configuration of the heat exchanger 100.
  • the heat exchanger 100 includes a first pipe 1 in which a first flow path FP1 through which water as a first heat medium flows is formed, and a second flow path FP2 through which a refrigerant which is a second heat medium flows And a second pipe 2.
  • the second pipe 2 is wound around the outer periphery of the first pipe 1 in one or more lines, and is in contact with the first pipe 1.
  • the first pipe 1 constitutes a part of the heat medium pipe 10A.
  • the second pipe 2 constitutes a part of the refrigerant pipe 20A.
  • the first pipe 1 is formed with a water inlet 1a and a water outlet 1b communicating with the first flow path FP1. Further, in the second pipe 2, an inlet 2a for the refrigerant and an outlet 2b for the refrigerant that are in communication with the second flow path FP2 are formed.
  • the heat exchanger 100 can be connected to the refrigerant circuit A1 and the heat medium circuit A2 such that the direction of the water flowing through the first pipe 1 and the direction of the refrigerant flowing through the second pipe 2 face each other. Thereby, the heat exchange efficiency between the heat medium and the refrigerant is improved.
  • the refrigeration cycle apparatus 200 is capable of hot water supply operation based on an instruction from the load side.
  • the operation of each actuator is controlled by the controller 60.
  • the low-temperature low-pressure refrigerant is compressed by the compressor 201 and is discharged from the compressor 201 as a high-temperature high-pressure gas refrigerant.
  • the high-temperature and high-pressure gas refrigerant discharged from the compressor 201 flows into the heat exchanger 100.
  • the refrigerant flowing into the heat exchanger 100 flows through the second pipe 2 and exchanges heat with the water flowing through the first pipe 1.
  • the refrigerant is condensed to be a low temperature and high pressure liquid refrigerant and flows out of the heat exchanger 100.
  • carbon dioxide is used as a refrigerant
  • coolant will change in temperature with a supercritical state.
  • the water flowing into the first pipe 1 is heated by the refrigerant flowing through the second pipe 2 and supplied to the load side.
  • the low-temperature and high-pressure liquid refrigerant flowing out of the heat exchanger 100 becomes a low-temperature and low-pressure liquid refrigerant or a two-phase refrigerant by the expansion device 202 and flows into the heat exchanger 203.
  • the refrigerant flowing into the heat exchanger 203 exchanges heat with the air supplied by the blower 203A attached to the heat exchanger 203, and becomes a low-temperature low-pressure gas refrigerant and flows out from the heat exchanger 203.
  • the refrigerant flowing out of the heat exchanger 203 is again drawn into the compressor 201.
  • FIG. 1 shows an example in which the flow of the refrigerant in the refrigerant circuit A1 is in a fixed direction
  • a flow path switching device is provided on the discharge side of the compressor 201 so that the flow of the refrigerant can be reversed.
  • the heat exchanger 100 also functions as an evaporator
  • the heat exchanger 203 also functions as a condenser.
  • the combination of a two-way valve, the combination of a three-way valve, or a four-way valve can be employ
  • a carbon dioxide is desirable as a refrigerant
  • natural refrigerants such as hydrocarbons or helium, chlorine-free alternative refrigerants such as HFC410A, HFC407C or HFC404A, or fluorocarbon refrigerants used in existing products such as R22 or R134a are also used. It is possible.
  • FIG. 3 is an external view showing an example of the configuration of the first pipe 1 of the heat exchanger 100.
  • FIG. 4 is a schematic view schematically showing a part of an example of the configuration of the first pipe 1 of the heat exchanger 100.
  • FIG. 5 is a schematic view schematically showing a part of an example of the configuration of the heat exchanger 100.
  • FIG. 6 is a schematic cross-sectional view showing a cross section of a part of the heat exchanger 100 in an enlarged manner. The configuration of the heat exchanger 100 will be described in detail with reference to FIGS. 3 to 6.
  • FIG. 6 a part of the cross section which cut the 1st piping 1 and the 2nd piping 2 of the heat exchanger 100 along the flow direction of the 1st heat carrier is roughly expanded and shown. Further, in FIG. 6, the inner circumferential surface S1 of the first pipe 1, the outer circumferential surface S2 of the first pipe 1, the diameter expansion direction DR1, the diameter reduction direction DR2, the first flow path FP1, and the retention portion T Is illustrated.
  • the diameter expansion direction DR1 is a direction from the inner peripheral surface S1 side of the first pipe 1 toward the outer peripheral surface S2 of the first pipe 1.
  • the diameter reducing direction DR ⁇ b> 2 is a direction from the outer peripheral surface S ⁇ b> 2 side of the first pipe 1 toward the inner peripheral surface S ⁇ b> 1 of the first pipe 1.
  • the first flow path FP1 is a flow path of the first pipe 1.
  • the inner circumferential surface S1 of the first pipe 1 is an inner surface that constitutes the inner wall of the first pipe 1.
  • the outer circumferential surface S2 of the first pipe 1 is an outer surface that constitutes the outer wall of the first pipe 1.
  • the stagnant portion T is a region where the flow velocity of the first heat medium is reduced in the first flow passage FP1.
  • the first pipe 1 has a peak portion 3 a that protrudes in the diameter increasing direction DR ⁇ b> 1 in which the diameter of the first pipe 1 is expanded.
  • the peak 3a is formed in a spiral shape in the direction in which the water of the first channel FP1 flows.
  • the first pipe 1 has a valley portion 3 b whose outer diameter is smaller than that of the portion where the peak portion 3 a is formed.
  • the valley portion 3 b is formed in a spiral shape along the peak portion 3 a. That is, the peaks 3a and the valleys 3b are formed in parallel.
  • the second pipe 2 is wound around the valley portion 3 b. Therefore, the second pipe 2 is also wound around the first pipe 1 in a spiral shape.
  • one peak portion 3 a is formed in the first pipe 1 as an example. Therefore, in FIGS. 3 to 5, four peak portions 3a are shown above and below the first pipe 1 so that the formation portion of the peak portion 3a can be easily understood. However, a plurality of peak portions 3 a are not formed in the first pipe 1, and one peak portion 3 a is formed in the first pipe 1 so as to extend in a spiral shape. However, when forming a plurality of ridges 3a, a plurality of ridges 3a are formed so as to extend in a spiral shape.
  • the mountain portion 3 a is formed in a spiral shape, the mountain portion 3 a is made to go around a plurality of the circumferences of the first pipe 1. Further, the valley portion 3 b is also formed so as to make a plurality of turns around the first pipe 1. Since the valley portion 3b is formed along the peak portion 3a, the valley portion 3b is between the peak portion 3a on the Nth turn in the helical turn and the peak portion 3a on the N + 1th turn in the helical turn. It will be formed. In other words, the mountain portion 3a is formed between the valley portion 3b at the Nth turn in the spiral winding and the peak portion 3a at the N + 1th turn in the spiral winding. N is a natural number. In addition, it is assumed that the Nth round of the spiral circulation is close to the inflow port 1a, and the N + 1th circle of the spiral circulation is close to the outflow port 1b.
  • a recess 3c is formed in the valley 3b.
  • a plurality of concave portions 3c are formed to be aligned in the spiral direction which is the formation direction of the valley portion 3b, and are formed to be recessed in the diameter reducing direction DR2 in which the diameter of the first pipe 1 is reduced.
  • the heat exchanger 100 is positioned between a portion of the heat exchanger 100, that is, the peak portion 3a of the Nth turn of the spiral turns, the peak portion 3a of the N + 1 turn of the spiral turns, and the like.
  • a portion including a valley portion 3b which is a middle valley portion on the Nth turn is illustrated.
  • the mountain portion 3 a in the Nth cycle in the spiral circulation is referred to as a first mountain portion 3 a-1
  • the mountain portion 3 a in the N + 1th circle in the spiral circulation is the second It is called "peak portion 3a-2".
  • a portion of the heat exchanger 100 is further divided into a first region R1 and a second region R2 and illustrated.
  • the first region R1 passes through the apex B1 of the first peak 3a-1, passes through a straight line D1 orthogonal to the first channel FP1, and passes through the center point B4 of the valley 3b, and the first channel FP1 and It is a region between the orthogonal straight line D2. That is, in the cross section shown in FIG. 6, the first region R1 means the region on the upstream side in the flow direction of the first heat medium in the first flow passage FP1 than the central point B4 of the valley portion 3b.
  • the second region R2 is a region between the straight line D2 and a straight line D3 passing through the apex B2 of the second peak 3a-2 and orthogonal to the first flow path FP1. That is, in the cross section shown in FIG.
  • the second region R2 means a region downstream in the flow direction of the first heat medium in the first flow passage FP1 than the central point B4 of the valley portion 3b.
  • the central point B4 of the valley portion 3b means a point located in the middle of the valley portion 3b in the flow direction of the first heat medium in the first flow path FP1.
  • a line segment connecting the vertex B3 of the recess 3c and the vertex B1 of the first peak 3a-1 is defined as a line segment L1, and the vertex B3 of the recess 3c and the second peak 3a-2
  • the line segment connecting the vertex B2 of and is illustrated as a line segment L2.
  • the apex B3 of the recess 3c is the portion of the recess 3c that is most recessed in the diameter reducing direction DR2.
  • the recess 3c is formed in the second region R2. That is, the recess 3c is formed such that the vertex B3 of the recess 3c is located downstream of the center point B4 of the valley 3b in the flow direction of the first heat medium in the first flow passage FP1. In other words, the recess 3c is formed at a position where the line segment L2 is shorter than the line segment L1.
  • the wall surface of the recess 3c on the downstream side in the flow direction of the first heat medium is the inside of the first pipe 1 forming the wall surface of the valley 3b in which the recess 3c is formed.
  • the circumferential surface S1 and the outer circumferential surface S2 are extended. That is, when the apex B2 of the second peak 3a-2 is viewed from the apex B2 of the second peak 3a-2, the line segment L2 of the depression 3c is directed to the upstream side of the flow direction of the first heat medium and the diameter reduction direction It is formed to go to DR2.
  • the line segment L2 of the recess 3c is directed downstream in the flow direction of the first heat medium and in the diameter expansion direction I'm heading for DR1.
  • the flow of the first heat medium tends to be stagnant particularly in the peaks 3a. That is, as shown in FIG. 6, the flow of the first heat medium tends to be stagnant at the portions of the first peak 3a-1 and the second peak 3a-2, and the stagnant portion T is formed. Therefore, the heat exchange performance at the stagnation portion T is lowered. So, in heat exchanger 100, since crevice 3c is formed in valley part 3b, a fall of the flow velocity of the 1st heat carrier in retention part T can be controlled, and heat exchange performance can be improved. Hereinafter, suppression of the decrease in the flow velocity of the first heat medium will be described.
  • FIG. 7 is an explanatory view of the flow velocity distribution of the first heat medium in the first pipe 1 in which the recess 3 c is not formed.
  • FIG. 8 is an explanatory view of the flow velocity distribution of the first heat medium in the first pipe 1 of the heat exchanger 100.
  • FIG. 7 is a comparative example, for convenience of explanation, the same reference numerals as those of the heat exchanger 100 are added.
  • the flow of the first heat medium in the first pipe 1 is illustrated by arrows as a flow FL1, a flow FL2, and a flow FL3. Further, in FIGS. 7 and 8, the flow velocity of the first heat medium is assumed to be low in the order of the flow FL1, the flow FL2, and the flow FL3.
  • the flow FL1 is formed, and the flow velocity is high. Further, as shown in FIG. 7, a flow FL2 is formed in a portion along the inner circumferential surface S1 of the first pipe 1, and the flow velocity is lower than the flow FL1. Moreover, as shown in FIG. 7, in the formation part of the retention part T of the 1st piping 1, flow FL3 is formed and the flow velocity is still lower than flow FL2.
  • the flow FL2 is formed in a portion along the inner peripheral surface S1 of the first pipe 1, but the flow FL2 becomes the flow velocity close to the flow FL1 compared to FIG. 7. . That is, the first heat medium avoids the recess 3c and flows in the direction of the peak 3a, and the flow velocity of the flow FL2 increases accordingly.
  • the flow FL3 is formed in the formation portion of the stagnant portion T of the first pipe 1, but the flow FL3 becomes the flow velocity close to the flow FL2 as compared with FIG. 7. That is, the first heat medium avoids the concave portion 3c and flows in the direction of the peak portion 3a, and the flow velocity of the flow FL3 in the retention portion T increases accordingly.
  • the heat exchanger 100 in which the recess 3 c is formed compared with the heat exchanger in which the recess 3 c is not formed, in the heat exchanger 100 in which the recess 3 c is formed, the inner circumferential surface of the first pipe 1 Even on the S1 side, the flow velocity is less likely to drop.
  • the heat exchanger 100 since the concave portion 3c is formed, the flow velocity does not easily decrease even in the retaining portion T, and the heat exchange performance can be improved.
  • FIG. 9 is an explanatory view as a comparative example of the streamlines of the first heat medium in the first pipe 1 in which the recess 3 c is formed in the central portion of the valley portion 3 b.
  • FIG. 10 and FIG. 11 are explanatory diagrams of streamlines of the first heat medium in the first pipe 1 of the heat exchanger 100.
  • FIG. FIG. 10 schematically shows the internal state of the first pipe 1.
  • FIG. 11 has shown roughly the case where the state inside the 1st piping 1 is seen from the exterior.
  • FIG. 9 is a comparative example, for convenience of explanation, the same reference numerals as those of the heat exchanger 100 are added. In FIG.
  • FIGS. 10 and 11 the flow of a part of the first heat medium in the first pipe 1 is illustrated by an arrow as a vortex flow FL4.
  • the eddy current FL4 remains along the inner circumferential surface S1 of the first pipe 1 on the downstream side of the recess 3 c in the flow direction of the first heat medium.
  • the occurrence of corrosion in the first pipe 1 is a concern due to the eddy current FL4. This is considered to be one of the factors that the corrosion resistance of the portion decreases because the oxide film is not formed on the inner circumferential surface S1 of the first pipe 1 in the portion where the vortex flow FL4 occurs.
  • the recess 3c is formed in the central portion of the valley 3b, the inner circumferential surface S1 of the first pipe 1 constituting the valley 3b continuously to the recess 3c exists on the downstream side of the recess 3c. become. Therefore, the eddy current FL4 generated by the concave portion 3c is generated along the inner circumferential surface S1 of the first pipe 1 constituting the valley portion 3b, which causes the formation of the oxide film in this portion to be prevented. ing.
  • the vortex flow FL5 is generated on the downstream side of the flow direction of the first heat medium of the recess 3c.
  • the inner circumferential surface S1 of the first pipe 1 does not exist immediately downstream of the recess 3c on the downstream side in the flow direction of the first heat medium.
  • the vortex flow FL5 is not generated by the flow of the peak 3a. That is, the vortex flow FL5 generated by the concave portion 3c does not stay in the vicinity of the inner circumferential surface S1 of the first pipe 1 constituting the valley portion 3b, and becomes a flow FL5a shown in FIG. It does not prevent the formation of an oxide film on the part.
  • the eddy current FL5 generated on the downstream side of the flow direction of the first heat medium of the recess 3c is the inner periphery of the first pipe 1. Since no stagnation occurs in the vicinity of the surface S1, a reduction in corrosion resistance can be suppressed also in this portion.
  • the recess 3c can be formed by dimple processing. That is, the recess 3 c is recessed in a circular shape in plan view. In addition, it does not limit to forming the recessed part 3c by dimple process.
  • the recess 3 c may be recessed in a planar view shape. That is, the recess 3 c may be formed in a groove shape.
  • the recessed part 3c was demonstrated as what is a planar view circular shape, it is not limited to it, It may be polygonal shapes, such as planar view triangle shape, square shape, etc. FIG.
  • each recessed part 3c was demonstrated as what is the same shape, it is not limited to it and each may be a different shape.
  • the number of ridges 3a and the valley portion 3b is not particularly limited.
  • a plurality of ridges 3 a and valleys 3 b may be formed in the first pipe 1.
  • FIG. 12 is a cross-sectional view schematically showing a cross section of the first pipe 1 of the heat exchanger 100 according to the first modification taken along the flow direction of the first heat medium.
  • FIG. 13 is a cross-sectional view schematically showing a cross section orthogonal to the flow direction of the first heat medium of the first pipe 1 of the heat exchanger 100 according to the first modification.
  • the 1st piping 1 in which three peak parts 3a and valley parts 3b are formed is shown in figure.
  • three ridges 3a and valleys 3b are formed. That is, the mountain portion 3a1, the mountain portion 3a2 and the mountain portion 3a3 are formed in the first pipe 1. Further, in the first pipe 1, a valley portion 3b1, a valley portion 3b2, and a valley portion 3b3 are formed. And valley part 3b1 will be located between peak part 3a1 and peak part 3a2. In addition, the valley portion 3b2 is located between the peak portion 3a2 and the peak portion 3a3. Furthermore, the valley 3b3 is located between the mountain 3a3 and the mountain 3a1.
  • the ridge portion 3a As for the ridge portion 3a, when the number of threads increases, the amount of protrusion of the diameter increasing direction DR1 decreases. That is, when the number of ridges 3a increases, the first heat medium is not easily retained in the retaining portion T, and it is easy to suppress the decrease in flow velocity in the retaining portion T in addition to the formation position of the recess 3c. As a result, if the ridges 3a are three lines, the heat exchange performance can be further improved.
  • FIG. 14 is a cross-sectional view schematically showing a cross section of the first pipe 1 of the heat exchanger 100 according to the second modification taken along the flow direction of the first heat medium.
  • FIG. 15 is a cross-sectional view schematically showing a cross section orthogonal to the flow direction of the first heat medium of the first pipe 1 of the heat exchanger 100 according to the first modification.
  • FIGS. 14 and 15 illustrate the first pipe 1 in which four ridges 3 a and valleys 3 b are formed.
  • valleys 3 b are formed in the first pipe 1, the peak 3 a 1, the peak 3 a 2, the peak 3 a 3, and the peak 3 a 4 are formed. Further, in the first pipe 1, a valley portion 3 b 1, a valley portion 3 b 2, a valley portion 3 b 3, and a peak portion 3 a 4 are formed. And valley part 3b1 will be located between peak part 3a1 and peak part 3a2. In addition, the valley portion 3b2 is located between the peak portion 3a2 and the peak portion 3a3. Further, the valley portion 3b3 is located between the peak portion 3a3 and the peak portion 3a4. Furthermore, the valley 3b4 is located between the mountain 3a4 and the mountain 3a1.
  • the first heat medium is not easily retained in the retention portion T, and the decrease in flow velocity in the retention portion T is suppressed in addition to the formation position of the recess 3c. It becomes easy to do.
  • the ridges 3a have four lines, the heat exchange performance can be further improved.
  • the recess 3c is formed at a position where the line segment L2 is shorter than the line segment L1, the recess 3c is formed in the second region R2, and the retention portion It is possible to suppress the decrease in flow velocity at T.
  • the line segment L2 is directed to the upstream side in the flow direction of the first heat medium and , Is formed to be directed in the diameter reducing direction DR2. Therefore, it becomes clear that the recess 3c is further recessed in the diameter reducing direction DR2 than the valley portion 3b, and it is possible to suppress the decrease in the flow velocity in the retaining portion T without forming the recess 3c in a complicated shape.
  • the recess 3c is formed in a circular shape in a plan view, the recess 3c can be formed by dimple processing, and it is not necessary to form the recess 3c by a complicated and expensive mechanism.
  • the heat exchanger 100 since a plurality of ridges 3a and valleys 3b are formed, retention of the first heat medium in the retention portion T can be further suppressed.
  • FIG. 16 is an explanatory diagram of flow lines of the first heat medium in the first piping 1 of the heat exchanger according to Embodiment 2 of the present invention.
  • the streamlines of the first heat medium in the first pipe 1 of the heat exchanger according to the second embodiment will be described based on FIG.
  • differences from the first embodiment will be mainly described, and the same parts as the first embodiment will be assigned the same reference numerals and descriptions thereof will be omitted.
  • the shape of the recess 3c is different from the shape of the recess 3c described in the first embodiment.
  • the shape of the recess 3 c is in a streamlined cross-sectional shape. That is, the portion of the recess 3c along the flow direction of the first heat medium is longer than the portion of the recess 3c orthogonal to the flow direction of the first heat medium, and the elongated portion is curved smoothly.
  • the recessed part 3c into a cross-sectional view flow linear shape, generation
  • the recess 3c can be formed by dimple processing. That is, the recess 3 c may be formed by forming the mold of the recess 3 c formed by dimple processing into a streamlined cross-sectional shape. Further, all of the recesses 3c may have a streamlined cross-sectional shape, or all of the recesses 3c may not have a streamlined cross-sectional shape. Further, the first modification or the second modification described in the first embodiment can be applied to the second embodiment.
  • FIG. 17 is an explanatory view as a comparative example of the streamlines of the first heat medium in the first pipe 1 in which the recess 3 c having a circular shape in plan view is formed.
  • FIG. 18 is an explanatory diagram of flow lines of the first heat medium in the first piping 1 of the heat exchanger according to Embodiment 3 of the present invention.
  • the streamlines of the first heat medium in the first pipe 1 of the heat exchanger according to the third embodiment will be described based on FIGS. 17 and 18.
  • differences from the first embodiment and the second embodiment will be mainly described, and the same parts as the first embodiment and the second embodiment will be assigned the same reference numerals and descriptions thereof will be omitted. It shall be.
  • FIG. 17 the structure of the 1st piping 1 of the heat exchanger 100 which concerns on Embodiment 1 is shown as a comparative example.
  • the flow of the first heat medium in the first pipe 1 is illustrated by an arrow as a flow FL6.
  • the flow of the first heat medium in the first pipe 1 is illustrated by an arrow as a flow FL7.
  • the shape of the recess 3c is different from the shape of the recess 3c described in the first embodiment.
  • the shape of the recess 3c is elliptical in plan view. That is, the concave portion 3c is formed in an elliptical shape in which the spiral direction of the concave portion 3c is the minor axis ma1 and the direction perpendicular to the spiral direction of the concave portion 3c is the major axis ma2.
  • the spiral direction means a direction parallel to the straight line L3 shown in FIG.
  • the straight line L3 is a straight line connecting vertices of the mountain portion 3a connected to the upper and lower sides of the drawing.
  • the concave portion 3 c functions more as a weir to the flow of the first heat medium along the spiral direction. That is, the recess 3 c is a wall of the flow of the first heat medium along the spiral direction with the width of the major axis ma2. Therefore, when the concave portion 3c has an elliptical shape in a plan view, the effect of the flow FL7 guiding to the peak portion 3a shown in FIG. 18 is larger than the flow FL6 shown in FIG. That is, since the flow velocity in the retention portion T of the first heat medium does not easily decrease, improvement in heat exchange performance can be expected.
  • the recess 3c can be formed by dimple processing. That is, the recess 3c may be formed by forming the recess 3c formed by dimple processing into an elliptical shape in plan view. Further, all of the concave portions 3c may have an elliptical shape in plan view, or all of the concave portions 3c may not have an elliptical shape in plan view. Further, the first modification or the second modification described in the first embodiment can be applied to the third embodiment.
  • the recess 3c is formed in an elliptical shape in plan view with the minor axis ma1 as the spiral direction and the major axis ma2 as the direction perpendicular to the spiral direction.
  • the recess 3c functions more as a weir to the flow. Therefore, according to the heat exchanger of the third embodiment, the effect of the flow guided to the mountain portion 3a is large.
  • FIG. 19 is an explanatory view of the recess 3 c in the first pipe 1 of the heat exchanger according to Embodiment 4 of the present invention.
  • FIG. 20 is a schematic cross-sectional view schematically showing a cross-sectional configuration of the recess 3c in the first pipe 1 of the heat exchanger according to Embodiment 4 of the present invention. Based on FIG. 19 and FIG. 20, the recessed part 3c in the 1st piping 1 of the heat exchanger which concerns on Embodiment 4 is demonstrated.
  • differences from the first embodiment, the second embodiment, and the third embodiment will be mainly described, and the first embodiment, the second embodiment, and the third embodiment can be used. The same parts will be denoted by the same reference numerals and the description thereof will be omitted.
  • FIG. 20 is a schematic enlarged view of the cross section in the spiral direction including the recess 3 c of the first pipe 1. Further, in FIG. 20, the flow along the spiral direction of the first heat medium from the inflow port 1a to the outflow port 1b of the first flow path FP1 is illustrated by an arrow as a flow FL8.
  • the shape of the recess 3c is different from the shape of the recess 3c described in the first embodiment. Specifically, as shown in FIG. 19 and FIG. 20, the position of the apex B3 of the recess 3c is shifted to the upstream side of the center of the recess 3c with respect to the advancing direction of the spiral direction. By shifting the apex B3 of the recess 3c to the upstream side with respect to the center with respect to the advancing direction of the spiral direction, the recess 3c has a streamlined shape with respect to the flow FL8 shown in FIG. Therefore, as in the second embodiment, the generation of the eddy current in the recess 3 c can be suppressed. Therefore, according to the heat exchanger of the fourth embodiment, further suppression of the decrease in corrosion resistance can be expected.
  • the first modification or the second modification described in the first embodiment can be applied to the fourth embodiment.
  • the apex B3 of the recess 3c is formed on the upstream side of the central portion with respect to the traveling direction of the spiral direction in the flow direction of the first heat medium of the first pipe 1. ing. Therefore, according to the heat exchanger according to the fourth embodiment, like the heat exchanger according to the second embodiment, the generation of the eddy current in the recess 3c can be further suppressed, and the further suppression of the decrease in corrosion resistance is achieved. I can expect it.

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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)
  • Details Of Fluid Heaters (AREA)

Abstract

Dans cet échangeur de chaleur, lorsque la section transversale (découpée le long de la direction du flux d'un premier milieu de transfert de chaleur) d'une partie d'un premier tuyau comprenant une première arête, une seconde arête, et un creux intermédiaire est vu selon une vue en coupe transversale, la première arête étant une arête sur la nième rotation hélicoïdale des crêtes, la seconde arête étant une arête sur la (N +1)ème rotation hélicoïdale des crêtes, et le creux intermédiaire étant une section de creux entre la première arête et la seconde arête, puis un évidement est formé de telle sorte que le sommet de l'évidement soit positionné plus loin en aval que le premier point central du creux dans la direction du flux du premier milieu de transfert de chaleur.
PCT/JP2017/026674 2017-07-24 2017-07-24 Échangeur de chaleur et dispositif de cycle de réfrigération Ceased WO2019021345A1 (fr)

Priority Applications (4)

Application Number Priority Date Filing Date Title
CN201780092652.4A CN110892223B (zh) 2017-07-24 2017-07-24 热交换器及制冷循环装置
JP2019532231A JP6735924B2 (ja) 2017-07-24 2017-07-24 熱交換器及び冷凍サイクル装置
EP17919080.6A EP3660435B1 (fr) 2017-07-24 2017-07-24 Échangeur de chaleur et dispositif de cycle de réfrigération
PCT/JP2017/026674 WO2019021345A1 (fr) 2017-07-24 2017-07-24 Échangeur de chaleur et dispositif de cycle de réfrigération

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JPH10103887A (ja) * 1996-09-13 1998-04-24 Hosan:Kk 伝熱管及びその製造方法
WO2008029639A1 (fr) * 2006-09-08 2008-03-13 Tsinghua University tube ondulÉ pour Échangeur thermique destinÉ À une alimentation en eau chaude
JP2008190787A (ja) * 2007-02-05 2008-08-21 Furukawa Electric Co Ltd:The スパイラル管およびこれを用いた熱交換器
JP2009041880A (ja) * 2007-08-10 2009-02-26 Sumitomo Light Metal Ind Ltd 給湯機用水熱交換器
JP2010091266A (ja) 2004-08-26 2010-04-22 Mitsubishi Electric Corp 捩り管形熱交換器
JP2011208824A (ja) * 2010-03-29 2011-10-20 Furukawa Electric Co Ltd:The 熱交換器、及び、伝熱管
JP2015045482A (ja) * 2013-08-29 2015-03-12 株式会社コベルコ マテリアル銅管 管内単相流用伝熱管

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JP2005164166A (ja) * 2003-12-04 2005-06-23 Kobelco & Materials Copper Tube Inc 熱交換器
JP3953075B2 (ja) * 2005-05-16 2007-08-01 ダイキン工業株式会社 熱交換器
JP6057154B2 (ja) * 2012-09-28 2017-01-11 パナソニックＩｐマネジメント株式会社 熱交換器
CN105277021A (zh) * 2014-07-18 2016-01-27 上海交通大学 同轴缠绕式换热器

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH10103887A (ja) * 1996-09-13 1998-04-24 Hosan:Kk 伝熱管及びその製造方法
JP2010091266A (ja) 2004-08-26 2010-04-22 Mitsubishi Electric Corp 捩り管形熱交換器
WO2008029639A1 (fr) * 2006-09-08 2008-03-13 Tsinghua University tube ondulÉ pour Échangeur thermique destinÉ À une alimentation en eau chaude
JP2008190787A (ja) * 2007-02-05 2008-08-21 Furukawa Electric Co Ltd:The スパイラル管およびこれを用いた熱交換器
JP2009041880A (ja) * 2007-08-10 2009-02-26 Sumitomo Light Metal Ind Ltd 給湯機用水熱交換器
JP2011208824A (ja) * 2010-03-29 2011-10-20 Furukawa Electric Co Ltd:The 熱交換器、及び、伝熱管
JP2015045482A (ja) * 2013-08-29 2015-03-12 株式会社コベルコ マテリアル銅管 管内単相流用伝熱管

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Also Published As

Publication number Publication date
JP6735924B2 (ja) 2020-08-05
EP3660435B1 (fr) 2021-07-14
EP3660435A4 (fr) 2020-08-26
EP3660435A1 (fr) 2020-06-03
CN110892223B (zh) 2021-03-23
JPWO2019021345A1 (ja) 2020-01-09
CN110892223A (zh) 2020-03-17

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