CN116438421A - Heat exchanger and refrigeration cycle device - Google Patents

Heat exchanger and refrigeration cycle device Download PDF

Info

Publication number
CN116438421A
CN116438421A CN202080107267.4A CN202080107267A CN116438421A CN 116438421 A CN116438421 A CN 116438421A CN 202080107267 A CN202080107267 A CN 202080107267A CN 116438421 A CN116438421 A CN 116438421A
Authority
CN
China
Prior art keywords
peak
fin
heat exchanger
longitudinal direction
side direction
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.)
Pending
Application number
CN202080107267.4A
Other languages
Chinese (zh)
Inventor
前田刚志
八柳晓
梁池悟
地村启
高桥智彦
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
Publication of CN116438421A publication Critical patent/CN116438421A/en
Pending legal-status Critical Current

Links

Images

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F1/00—Tubular elements; Assemblies of tubular elements
    • F28F1/10—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses
    • F28F1/12—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element
    • F28F1/24—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element and extending transversely
    • F28F1/32—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element and extending transversely the means having portions engaging further tubular elements
    • F28F1/325—Fins with openings
    • 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
    • F28D1/00—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators
    • F28D1/02—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid
    • F28D1/04—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits
    • F28D1/047—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits the conduits being bent, e.g. in a serpentine or zig-zag
    • F28D1/0477—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits the conduits being bent, e.g. in a serpentine or zig-zag the conduits being bent in a serpentine or zig-zag
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F1/00—Tubular elements; Assemblies of tubular elements
    • F28F1/10—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses
    • F28F1/12—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element
    • F28F1/24—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element and extending transversely
    • F28F1/32—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element and extending transversely the means having portions engaging further tubular elements
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F17/00—Removing ice or water from heat-exchange apparatus
    • F28F17/005—Means for draining condensates from heat exchangers, e.g. from evaporators
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F19/00—Preventing the formation of deposits or corrosion, e.g. by using filters or scrapers
    • F28F19/006—Preventing deposits of ice
    • 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
    • F28F2225/00—Reinforcing means
    • F28F2225/06—Reinforcing means for fins

Landscapes

  • 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

The Heat Exchanger (HE) is provided with: a fin (F) configured to extend in a short side direction (D1) along the air flow direction (D0) and in a long side direction (D2) intersecting the air flow direction (D0); and a heat transfer pipe (P) penetrating the fin (F). The fin (F) is provided with Through Holes (TH). The heat transfer pipe (P) is inserted into the Through Hole (TH). Each fin (F) comprises: a plane part (SP); and 1 st peak (MP 1) and 2 nd peak (MP 2), which are configured to protrude from the planar portion (SP). The 1 st peak (MP 1) is configured to bend along the longitudinal direction (D2). The 2 nd peak (MP 2) has an Extension (EP) extending in the longitudinal direction (D2). The Extension (EP) is arranged so as to overlap the center of the Through Hole (TH) in the short-side direction (D1).

Description

Heat exchanger and refrigeration cycle device
Technical Field
The present disclosure relates to a heat exchanger and a refrigeration cycle apparatus.
Background
Conventionally, there is a fin-tube heat exchanger including fins and heat transfer tubes penetrating the fins. For example, in the heat exchanger described in japanese patent application laid-open No. 2005-77083 (patent document 1), the fin includes a sheet portion (planar portion) and peak and valley portions. The fin portions are formed concentrically around the outer periphery of the fin collar to guide air flowing around the heat transfer tube so that the wake area is reduced. The front and rear of the tab are open. The peaks and valleys are continuously disposed between the fin collars for imparting a variation to the flow of air.
Prior art literature
Patent literature
Patent document 1: japanese patent laid-open publication No. 2005-77083
Disclosure of Invention
Problems to be solved by the invention
In the heat exchanger described in the above publication, since the peak portions and the valley portions are provided continuously along the flow direction of the air, a boundary layer is formed starting from the peak portions. Therefore, the valley portion becomes a dead water region. As a result, the local heat transfer rate at the valley portion is reduced, and therefore, the heat transfer rate of the fin as a whole is reduced. Further, since the stress concentrates on the flat portions not provided with the peaks and valleys, the strength of the fin is insufficient.
The present disclosure has been made in view of the above-described problems, and an object thereof is to provide a heat exchanger and a refrigeration cycle device that can improve heat transfer efficiency and strength of fins.
Means for solving the problems
The heat exchanger of the present disclosure is provided with: a fin configured to extend in a short side direction along a flow direction of air and a long side direction intersecting the flow direction of air; and a heat transfer tube penetrating the fin. The fins are provided with through holes. The heat transfer tube is inserted into the through hole. The fin includes: a planar portion; and 1 st and 2 nd peaks configured to protrude from the planar portion. The 1 st peak is configured to be curved in the longitudinal direction. The 2 nd peak has an extension portion extending in the longitudinal direction. The extension portion is arranged to overlap with the center of the through hole in the short side direction.
Effects of the invention
According to the heat exchanger of the present disclosure, since the 1 st peak and the 2 nd peak are configured to protrude from the planar portion, the influence of the stagnant water region can be suppressed. Therefore, the heat transfer rate of the fin can be improved. Further, the strength of the fin can be improved by the 1 st peak and the 2 nd peak.
Drawings
Fig. 1 is a perspective view schematically showing the structure of a heat exchanger according to embodiment 1.
Fig. 2 is a sectional view taken along line II-II of region a of fig. 1.
Fig. 3 is an end view along line III-III of fig. 2.
Fig. 4 is an end view along line IV-IV of fig. 2.
Fig. 5 is a refrigerant circuit diagram showing the refrigeration cycle apparatus according to embodiment 1.
Fig. 6 is a cross-sectional view schematically showing the structure of a portion of the heat exchanger according to embodiment 2 corresponding to fig. 2.
Fig. 7 is an end view along line VII-VII of fig. 6.
Fig. 8 is an end view along line VIII-VIII of fig. 6.
Fig. 9 is a cross-sectional view schematically showing the structure of a portion of the heat exchanger according to embodiment 3 corresponding to fig. 2.
Fig. 10 is an end view along the line X-X of fig. 9.
Fig. 11 is an end view along line XI-XI of fig. 9.
Fig. 12 is a cross-sectional view schematically showing the structure of a portion of the heat exchanger according to embodiment 4 corresponding to fig. 2.
Fig. 13 is an end view along line XIII-XIII of fig. 12.
Fig. 14 is an end view along line XIV-XIV of fig. 12.
Detailed Description
Hereinafter, embodiments will be described with reference to the drawings. In the following, the same or corresponding parts are denoted by the same reference numerals, and the description thereof will not be repeated.
Embodiment 1.
The structure of the heat exchanger HE according to embodiment 1 will be described with reference to fig. 1 to 4.
Referring to fig. 1 and 2, the heat exchanger HE includes fins F and heat transfer tubes P. The fin F is configured to extend in a short side direction D1 along the air flow direction D0 and a long side direction D2 intersecting the air flow direction D0. The fin F is formed in a substantially rectangular shape. The heat transfer pipe P penetrates the fin F. The heat transfer pipe P is a circular pipe. The fin F is provided with through holes TH. The through holes TH are formed in a circular shape. The heat transfer pipe P is inserted into the through hole TH.
In the present embodiment, the heat exchanger HE includes a plurality of fins F. The plurality of fins F are stacked with a space therebetween. The heat transfer pipe P penetrates the plurality of fins F in the direction D3 in which the plurality of fins F are stacked. The plurality of fins F are provided with a plurality of through holes TH, respectively. The plurality of through holes TH are aligned in the longitudinal direction D2 of the fin F. The plurality of through holes TH are arranged at intervals in the longitudinal direction D2 of the fin F.
The short side direction D1 of the fin F is perpendicular to the long side direction D2. The short side direction D1 of the fin F may be a horizontal direction. The longitudinal direction D2 of the fin F may be a vertical direction (vertical direction). The direction D3 in which the fins F are stacked is perpendicular to the short-side direction D1 and the long-side direction D2 of the fins F.
The heat transfer pipe P has a plurality of heat transfer portions P1 and a plurality of connection portions P2. The plurality of heat transfer portions P1 penetrate the plurality of fins F, respectively. The plurality of heat transfer portions P1 are inserted into the plurality of through holes TH along the stacking direction D3 of the plurality of fins F, respectively. The plurality of heat transfer portions P1 are linearly formed. The plurality of heat transfer portions P1 extend in the direction D3 in which the plurality of fins F are stacked.
The plurality of connection portions P2 are portions connecting the plurality of heat transfer portions P1 to each other outside the plurality of fins F. The plurality of connection portions P2 are each formed in a U shape. The plurality of connection portions P2 connect the plurality of heat transfer tubes P adjacent to each other in the longitudinal direction D2 of the fin F, respectively. The plurality of connection portions P2 are connected to the ends of the plurality of heat transfer portions P1 in the direction D3 in which the plurality of fins F are stacked, respectively. The plurality of heat transfer portions P1 are arranged in a plurality of stages in the longitudinal direction D2 of the fin F. In the present embodiment, the plurality of heat transfer portions P1 are arranged in 4 stages along the longitudinal direction D2 of the fin F.
The plurality of heat transfer portions P1 are connected by a plurality of connection portions P2 as follows. The 1 st heat transfer portion P1 is connected to the 2 nd heat transfer portion P1 by a connection portion P2 on the back side in the direction D3 in which the plurality of fins F are stacked. The 2 nd heat transfer portion P1 is connected to the 3 rd heat transfer portion P1 by a connection portion P2 at a front side in the direction D3 in which the plurality of fins F are stacked. The 3 rd heat transfer portion P1 is connected to the 4 th heat transfer portion P1 by a connection portion P2 on the back side in the direction D3 in which the plurality of fins F are stacked. In this way, the heat transfer tube P is configured to meander in the longitudinal direction D2 of the fin F.
The structure of the fin F will be described in detail with reference to fig. 2 to 4.
The fin F includes a planar portion SP, a 1 st peak MP1, a 2 nd peak MP2, and a fin sleeve FC. The planar portion SP is formed in a planar shape. The planar portion SP is formed in a flat plate shape.
The 1 st peak MP1 and the 2 nd peak MP2 are configured to protrude from the plane portion SP. In the present embodiment, the 1 st peak MP1 and the 2 nd peak MP2 protrude in the same direction from the plane portion SP. In the present embodiment, the fin F includes a plurality of 1 st peak portions MP1 and a plurality of 2 nd peak portions MP2.
The 1 st peak MP1 is curved along the longitudinal direction D2 of the fin F. The 1 st peak MP1 is curved so as to protrude in the longitudinal direction D2 of the fin F. The 1 st peak MP1 has a portion extending in the longitudinal direction D2 of the fin F. The 1 st peak MP1 has a portion extending along the short side direction D1 of the fin F. The 1 st peak MP1 is arranged to be offset from the center of the through hole TH in the short side direction D1 of the fin F. In the present embodiment, the 1 st peak MP1 is formed in an arc shape. In this embodiment, the 1 st peak MP1 has the same width.
The 1 st peak MP1 is arranged in the longitudinal direction D2 of the fin F. The 1 st peak portions MP1 are arranged at intervals in the longitudinal direction D2 of the fin F. In the present embodiment, 21 st peak portions MP1 are arranged between 2 through holes TH in the longitudinal direction D2 of the fin F. The 21 st peaks MP1 are arranged to face each other in the longitudinal direction D2 of the fin F. The 1 st peak portions MP1 facing each other are curved in such a manner as to protrude toward each other.
Each 1 st peak MP1 of the plurality of 1 st peaks MP1 is configured in the same shape except for a direction of bending along the longitudinal direction D2 of the fin F. The respective radii of curvature of the 1 st peak portions MP1 are equal to each other. The centers of curvature of the 1 st peak portions MP1 are aligned with each other in a straight line in the longitudinal direction D2 of the fin F. The respective widths of the 1 st peak portions MP1 are equal to each other. The lengths of the 1 st peak portions MP1 are equal to each other.
In the short side direction D1 of the fin F, each 1 st peak MP1 of the plurality of 1 st peaks MP1 is longer than each 2 nd peak MP2 of the plurality of 2 nd peaks MP2. In the longitudinal direction D2 of the fin F, each 1 st peak MP1 of the plurality of 1 st peaks MP1 is arranged between each 2 nd peak MP2 of the plurality of 2 nd peaks MP2. In the longitudinal direction D2 of the fin F, the center of curvature of each of the 1 st peak portions MP1 and the center of each of the 2 nd peak portions MP2 are aligned in a straight line.
The 2 nd peak MP2 has an extension portion EP extending in the longitudinal direction D2 of the fin F. The 2 nd peak MP2 has a portion extending in the longitudinal direction D2 of the fin F. The extending portion EP is arranged to overlap the center of the through hole TH in the short side direction D1 of the fin F.
In the present embodiment, the 2 nd peak MP2 is disposed between the 1 st peak MP1 and the through hole TH. The 2 nd peak MP2 is formed to surround the through hole TH. The 2 nd peak MP2 is formed in a circular ring shape. The height of the 2 nd peak MP2 protruding from the plane portion SP is higher than the height of the 1 st peak MP1 protruding from the plane portion SP.
Each of the 2 nd peaks MP2 of the plurality of 2 nd peaks MP2 is configured to have the same shape. The centers of the 2 nd peaks MP2 are aligned in a straight line in the longitudinal direction D2 of the fin F. The respective widths of the plurality of 2 nd peaks MP2 are equal to each other. The diameters of the 2 nd peaks MP2 are equal to each other.
The 1 st and 2 nd crests MP1, MP2 protrude from the planar portion SP at a lower height than the fin collar FC protrudes from the planar portion SP.
The fin collar FC is formed in a cylindrical shape. The heat transfer tube P is inserted into the fin sleeve FC. The outer peripheral surface of the heat transfer pipe P is fitted to the inner peripheral surface of the fin sleeve FC. The fin collar FC is configured to protrude from the planar portion SP. In the present embodiment, the fin collar FC protrudes from the planar portion SP in the same direction as the 1 st peak MP1 and the 2 nd peak MP2.
The fin collar FC includes a peripheral wall and a flange. The peripheral wall is configured to protrude from the planar portion SP. The flange is configured to protrude outward from the peripheral wall. The flange is provided at the front end of the peripheral wall on the opposite side of the planar portion SP. In the present embodiment, the fin F includes a plurality of fin collars FC.
Referring to fig. 5, a description will be given of a configuration of a refrigeration cycle apparatus 100 including a heat exchanger HE according to embodiment 1. The refrigeration cycle apparatus 100 is, for example, an air conditioner, a refrigerator, or the like. In embodiment 1, an air conditioner will be described as an example of the refrigeration cycle apparatus 100. The refrigeration cycle apparatus 100 includes a refrigerant circuit RC, a refrigerant, a control device CD, and air blowing devices 6 and 7. The refrigeration cycle apparatus 100 includes a refrigerant cycle apparatus RCD. The refrigerant cycle device RCD is configured to circulate a refrigerant for exchanging heat between the air and the heat exchanger HE. In embodiment 1, a refrigeration cycle apparatus 100 in which a compressor 1 is incorporated as a refrigerant cycle apparatus RCD will be described. The refrigerant circulation device RCD may be a refrigerant pump.
The refrigerant circuit RC includes a compressor 1, a four-way valve 2, an outdoor heat exchanger 3, a pressure reducing valve 4, and an indoor heat exchanger 5. The heat exchanger HE may be applied to at least one of the outdoor heat exchanger 3 and the indoor heat exchanger 5. The compressor 1, the four-way valve 2, the outdoor heat exchanger 3, the pressure reducing valve 4, and the indoor heat exchanger 5 are connected by piping. The refrigerant circuit RC is configured to circulate a refrigerant. The refrigerant circuit RC is configured to perform a refrigeration cycle in which a refrigerant circulates while changing phase.
The compressor 1, the four-way valve 2, the outdoor heat exchanger 3, the pressure reducing valve 4, the control device CD, and the blower device 6 are housed in the outdoor unit 101. The indoor heat exchanger 5 and the blower 7 are housed in the indoor unit 102.
The refrigerant circuit RC is configured such that, during the cooling operation, the refrigerant circulates in the order of the compressor 1, the four-way valve 2, the outdoor heat exchanger (condenser) 3, the pressure reducing valve 4, the indoor heat exchanger (evaporator) 5, and the four-way valve 2. The refrigerant circuit RC is configured such that, during the heating operation, the refrigerant circulates in the order of the compressor 1, the four-way valve 2, the indoor heat exchanger (condenser) 5, the pressure reducing valve 4, the outdoor heat exchanger (evaporator) 3, and the four-way valve 2.
The refrigerant flows through the refrigerant circuit RC in the order of the compressor 1, the condenser, the pressure reducing valve 4, and the evaporator.
The control device CD is configured to perform operations, instructions, and the like to control the respective devices and the like of the refrigeration cycle apparatus 100. The control device CD is electrically connected to the compressor 1, the four-way valve 2, the pressure reducing valve 4, the blower devices 6, 7, and the like, and controls the operations thereof.
The compressor 1 is configured to compress a refrigerant for heat exchange with air in the heat exchanger HE. The compressor 1 compresses and discharges a sucked refrigerant. The compressor 1 may be configured to have a variable capacity. The compressor 1 may be configured to change the capacity by adjusting the rotation speed of the compressor 1 in response to an instruction from the control device CD.
The four-way valve 2 is configured to switch the flow of the refrigerant so that the refrigerant compressed by the compressor 1 flows to the outdoor heat exchanger 3 or the indoor heat exchanger 5. The four-way valve 2 is configured to allow the refrigerant discharged from the compressor 1 to flow to an outdoor heat exchanger (condenser) 3 during cooling operation. The four-way valve 2 is configured to allow the refrigerant discharged from the compressor 1 to flow into the indoor heat exchanger (evaporator) 5 during the heating operation.
The outdoor heat exchanger 3 is configured to exchange heat between the refrigerant flowing inside the outdoor heat exchanger 3 and the air flowing outside the outdoor heat exchanger 3. The outdoor heat exchanger 3 is configured to function as a condenser for condensing the refrigerant during the cooling operation, and to function as an evaporator for evaporating the refrigerant during the heating operation.
The pressure reducing valve 4 is configured to reduce the pressure of the refrigerant condensed by the condenser by expanding the refrigerant. The pressure reducing valve 4 is configured to reduce the pressure of the refrigerant condensed by the outdoor heat exchanger (condenser) 3 during the cooling operation, and to reduce the pressure of the refrigerant condensed by the indoor heat exchanger (evaporator) 5 during the heating operation. The pressure reducing valve 4 is, for example, a solenoid valve.
The indoor heat exchanger 5 is configured to exchange heat between the refrigerant flowing inside the indoor heat exchanger 5 and air flowing outside the indoor heat exchanger 5. The indoor heat exchanger 5 is configured to function as an evaporator that evaporates the refrigerant during the cooling operation, and to function as a condenser that condenses the refrigerant during the heating operation.
The blower 6 is configured to blow outdoor air to the outdoor heat exchanger 3. That is, the blower 6 is configured to supply air to the outdoor heat exchanger 3. The blower 6 may be configured to adjust the amount of air flowing around the outdoor heat exchanger 3 by adjusting the rotation speed of the blower 6 in response to an instruction from the control device CD, thereby adjusting the heat exchange amount between the refrigerant and the air.
The blower 7 is configured to blow indoor air toward the indoor heat exchanger 5. That is, the blower 7 is configured to supply air to the indoor heat exchanger 5. The blower 7 may be configured to adjust the amount of air flowing around the indoor heat exchanger 5 by adjusting the rotation speed of the blower 7 in response to an instruction from the control device CD, thereby adjusting the heat exchange amount between the refrigerant and the air.
Next, the operation of the refrigeration cycle apparatus 100 will be described with reference to fig. 5. In fig. 5, solid arrows indicate the flow of the refrigerant during the cooling operation, and broken arrows in fig. 5 indicate the flow of the refrigerant during the heating operation.
The refrigeration cycle apparatus 100 can selectively perform a cooling operation and a heating operation. During the cooling operation, the refrigerant circulates through the refrigerant circuit RC in the order of the compressor 1, the four-way valve 2, the outdoor heat exchanger 3, the pressure reducing valve 4, the indoor heat exchanger 5, and the four-way valve 2. During the cooling operation, the outdoor heat exchanger 3 functions as a condenser. The refrigerant flowing through the outdoor heat exchanger 3 exchanges heat with air blown by the blower device 6. During the cooling operation, the indoor heat exchanger 5 functions as an evaporator. The refrigerant flowing through the indoor heat exchanger 5 exchanges heat with air blown by the blower 7.
In the heating operation, the refrigerant circulates through the refrigerant circuit RC in the order of the compressor 1, the four-way valve 2, the indoor heat exchanger 5, the pressure reducing valve 4, the outdoor heat exchanger 3, and the four-way valve 2. During the heating operation, the indoor heat exchanger 5 functions as a condenser. The refrigerant flowing through the indoor heat exchanger 5 exchanges heat with air blown by the blower 7. During the heating operation, the outdoor heat exchanger 3 functions as an evaporator. The refrigerant flowing through the outdoor heat exchanger 3 exchanges heat with air blown by the blower device 6.
Next, the operational effects of embodiment 1 will be described.
According to the heat exchanger HE of embodiment 1, since the 1 st peak MP1 and the 2 nd peak MP2 are configured to protrude from the flat surface portion SP, the influence of the stagnant water region can be suppressed. Therefore, the heat transfer rate of the fin F can be improved. Further, the strength of the fin F can be improved by the 1 st peak MP1 and the 2 nd peak MP2.
The extension portion EP of the 2 nd peak MP2 extending in the long-side direction D2 is arranged so as to overlap the center of the through hole TH in the short-side direction D1. Therefore, the strength of the fin F can be further improved.
According to the heat exchanger HE of embodiment 1, the 2 nd peak MP2 is disposed between the 1 st peak MP1 and the through hole TH, and is configured to surround the through hole TH. Therefore, the strength of the fin F can be increased so as to surround the through-hole TH by the 2 nd peak MP2.
Embodiment 2.
The heat exchanger HE and the refrigeration cycle apparatus 100 according to embodiment 2 have the same structure, operation, and effects as those of the heat exchanger HE and the refrigeration cycle apparatus 100 according to embodiment 1, unless otherwise specified.
The structure of the fin F of the heat exchanger HE according to embodiment 2 will be described with reference to fig. 6 to 8.
The 2 nd peak MP2 is configured to extend linearly in the longitudinal direction D2 of the fin F. The 2 nd peak MP2 extends continuously from one end to the other end in the longitudinal direction D2 of the fin F. The 2 nd peak MP2 is configured to protrude from the plane portion SP to the opposite side of the 1 st peak MP1. The 2 nd peak MP2 is configured to protrude from the flat portion SP to the opposite side to the fin collar FC.
In the present embodiment, the fin F includes a plurality of 2 nd peaks MP2. Each of the 2 nd peaks MP2 of the plurality of 2 nd peaks MP2 extends parallel to each other along the longitudinal direction D2 of the fin F. The 2 nd peaks MP2 are arranged at both ends of the fin F in the short-side direction D1. The 2 nd peak portions MP2 are arranged so as to sandwich the 1 st peak portions MP1 and the heat transfer pipes P. The respective widths of the plurality of 2 nd peaks MP2 are equal to each other.
Next, the operational effects of embodiment 2 will be described.
According to the heat exchanger HE of embodiment 2, the 2 nd peak MP2 is configured to extend linearly in the longitudinal direction D2 of the fin F. Therefore, the strength of the fin F can be improved in the longitudinal direction D2 of the fin F by the 2 nd peak MP2.
According to the heat exchanger HE of embodiment 2, the 2 nd peak MP2 is configured to protrude from the planar portion SP to the opposite side of the 1 st peak MP1. Thus, peak 1 MP1 is not affected by the stagnant water region in the wake of peak 2 MP2. Therefore, the heat transfer rate of the fin F can be improved.
Embodiment 3.
The heat exchanger HE and the refrigeration cycle apparatus 100 according to embodiment 3 have the same structure, operation, and effects as those of the heat exchanger HE and the refrigeration cycle apparatus 100 according to embodiment 1, unless otherwise specified.
The structure of the fin F of the heat exchanger HE according to embodiment 3 will be described with reference to fig. 9 to 11.
The 2 nd peak MP2 is configured to extend linearly in the longitudinal direction D2 of the fin F. The 2 nd peak portions MP2 are arranged at intervals in the longitudinal direction D2 of the fin F. The 2 nd peak MP2 is separated in the longitudinal direction D2 of the fin F. The 2 nd peak MP2 is configured to protrude from the plane portion SP in the same direction as the 1 st peak MP1. The 2 nd peak MP2 is configured to protrude from the planar portion SP in the same direction as the fin collar FC.
The 2 nd peak MP2 is arranged to be offset from the 1 st peak MP1 in the short side direction D1 of the fin F. The 2 nd peak MP2 is arranged so as not to overlap with the 1 st peak MP1 in the short side direction D1 of the fin F.
In the present embodiment, the fin F includes a plurality of 2 nd peaks MP2. Each of the 2 nd peaks MP2 of the plurality of 2 nd peaks MP2 extends parallel to each other along the longitudinal direction D2 of the fin F. The 2 nd peaks MP2 are arranged at both ends of the fin F in the short-side direction D1. The 2 nd peak portions MP2 are arranged so as to sandwich the 1 st peak portions MP1 and the heat transfer pipes P. The respective widths of the plurality of 2 nd peaks MP2 are equal to each other.
Next, the operational effects of embodiment 3 will be described.
According to the heat exchanger HE of embodiment 3, the 2 nd peak MP2 is arranged so as to be offset from the 1 st peak MP1 in the short side direction D1 of the fin F. Therefore, by disposing the 2 nd peak MP2 at a portion where the 1 st peak MP1 is not formed, that is, at a portion where stress is easily concentrated, the strength of the fin F can be improved.
In addition, the 1 st peak MP1 is not affected by the stagnant water zone in the wake of the 2 nd peak MP2. Therefore, the heat transfer rate of the fin F can be improved.
Embodiment 4.
The heat exchanger HE and the refrigeration cycle apparatus 100 according to embodiment 4 have the same structure, operation, and effects as those of the heat exchanger HE and the refrigeration cycle apparatus 100 according to embodiment 1, unless otherwise specified.
The structure of the fin F of the heat exchanger HE according to embodiment 4 will be described with reference to fig. 12 to 14.
The 1 st peak MP1 is arranged in the longitudinal direction D2 of the fin F. In the present embodiment, 4 1 st peak portions MP1 are arranged between 2 through holes TH in the longitudinal direction D2 of the fin F.
The 21 st peak portions MP1 disposed above the lower through holes TH in the longitudinal direction D2 of the fin F are disposed adjacent to each other in the longitudinal direction D2 of the fin F. The 21 st peak portions MP1 disposed below the upper through holes TH in the longitudinal direction D2 of the fin F are disposed adjacent to each other in the longitudinal direction D2 of the fin F.
The 21 st peak portions MP1 arranged adjacent to each other are configured to be bent to the same side along the longitudinal direction D2. Further, the 21 st peak portions MP1 arranged to face each other in the longitudinal direction D2 of the fin F are configured to be curved to opposite sides along the longitudinal direction D2. The 21 st peak MP1 disposed in the vicinity of the upper through hole TH between the 2 through holes TH is curved so as to protrude downward. The 21 st peak MP1 disposed in the vicinity of the lower through hole TH between the 2 through holes TH is bent so as to protrude upward. The 1 st peak MP1 on the outer side of the 21 st peaks MP1 bent to protrude downward is arranged at a distance from the 1 st peak MP1 on the outer side of the 21 st peaks MP1 bent to protrude upward.
Each 1 st peak MP1 of the 1 st peaks MP1 on the outer side is configured in the same shape except for the direction of bending along the longitudinal direction D2 of the fin F. The outer 1 st peak MP1 has the same radius of curvature. The centers of curvature of the 1 st peak MP1 on the outer side are aligned in a straight line in the longitudinal direction D2 of the fin F. The width of each of the 1 st peak portions MP1 on the outer side is equal to each other. The lengths of the 1 st peak portions MP1 on the outer sides are equal to each other.
Each 1 st peak MP1 of the 1 st peaks MP1 on the inner side is configured in the same shape except for the direction of bending along the longitudinal direction D2 of the fin F. The radii of curvature of the 1 st peak MP1 on the inner side are equal to each other. The centers of curvature of the 1 st peak MP1 on the inner side are aligned in a straight line in the longitudinal direction D2 of the fin F. The inner 1 st peak MP1 has the same width as each other. The lengths of the 1 st peak portions MP1 on the inner side are equal to each other.
In the present embodiment, the length of the 1 st peak MP1 on the outer side in the short side direction D1 of the fin F is equal to the length of the 1 st peak MP1 on the inner side in the short side direction D1 of the fin F.
In the short side direction D1 of the fin F, each 1 st peak MP1 of the plurality of 1 st peaks MP1 is longer than each 2 nd peak MP2 of the plurality of 2 nd peaks MP2. In the longitudinal direction D2 of the fin F, each 1 st peak MP1 of the plurality of 1 st peaks MP1 is arranged between each 2 nd peak MP2 of the plurality of 2 nd peaks MP2. In the longitudinal direction D2 of the fin F, the center of curvature of each of the 1 st peak portions MP1 and the center of each of the 2 nd peak portions MP2 are aligned in a straight line.
The 1 st peak MP1 and the 2 nd peak MP2 which are disposed on the inner side of the 21 st peaks MP1 on the upper side of the through hole TH in the longitudinal direction D2 of the fin F are adjacent to each other. The 1 st peak MP1 and the 2 nd peak MP2 which are disposed on the inner side of the 21 st peaks MP1 on the lower side of the through hole TH in the longitudinal direction D2 of the fin F are adjacent to each other.
The 2 nd peak MP2 includes a 1 st MP21 and a 2 nd MP22. The 1 st portion MP21 is disposed between the 1 st peak portion MP1 and the through hole TH. The 1 st portion MP21 is formed to surround the through hole TH. The 1 st portion MP21 is formed in a circular ring shape. The 1 st portion MP21 protrudes from the flat surface portion SP at a higher height than the 1 st peak portion MP1 protrudes from the flat surface portion SP. The 1 st portion MP21 protrudes from the plane portion SP at a lower height than the 2 nd portion MP22 protrudes from the plane portion SP.
The 2 nd portion MP22 is configured to extend linearly in the longitudinal direction D2 of the fin F. The 2 nd portion MP22 extends continuously from one end to the other end in the longitudinal direction D2 of the fin F. The 2 nd portion MP22 is configured to protrude from the plane portion SP to the opposite side to the 1 st portion MP 21. The 2 nd portion MP22 extends from the plane portion SP to the opposite side of the 1 st peak portion MP1 and the fin collar FC.
In the present embodiment, the fin F includes a plurality of 2 nd portions MP22. Each of the 2 nd portions MP22 of the plurality of 2 nd portions MP22 extends parallel to each other in the longitudinal direction D2 of the fin F. The 2 nd portions MP22 are arranged at both ends of the fin F in the short-side direction D1. The 2 nd portions MP22 are arranged so as to sandwich the 1 st peak portions MP1, the 1 st portions MP21, and the heat transfer pipes P. The widths of the 2 nd portions MP22 are equal to each other.
The fin F includes: a 1 st region R1 where the through holes TH are not present in the short side direction D1 of the fin F; and a 2 nd region R2 where the through holes TH are present in the short side direction D1 of the fin F. In the 1 st region R1, the 1 st area of the 1 st peak MP1 and the 2 nd peak MP2 extending in the short side direction D1 of the fin F is larger than the 2 nd area of the 1 st peak MP1 and the 2 nd peak MP2 extending in the long side direction D2 of the fin F, and in the 2 nd region R2, the 1 st area is smaller than the 2 nd area.
Next, the operational effects of embodiment 4 will be described.
According to the heat exchanger HE of embodiment 4, in the 1 st region R1, the 1 st area of the 1 st peak MP1 and the 2 nd peak MP2 extending in the short side direction D1 of the fin F is larger than the 2 nd area of the 1 st peak MP1 and the 2 nd peak MP2 extending in the long side direction D2 of the fin F, and in the 2 nd region R2, the 1 st area is smaller than the 2 nd area. Therefore, it is possible to maximize the improvement of the heat transfer performance at the portion where the air easily flows, and to improve the strength of the fin F at the portion where the air hardly flows.
The presently disclosed embodiments are considered in all respects as illustrative and not restrictive. The scope of the present disclosure is shown not by the above description but by the scope of the claims, and is intended to include all modifications within the meaning and scope equivalent to the scope of the claims.
Description of the reference numerals
1: a compressor; 2: a four-way valve; 3: an outdoor heat exchanger; 4: a pressure reducing valve; 5: an indoor heat exchanger; 100: a refrigeration cycle device; d0: the direction of flow of the air; d1: a short side direction; d2: a long side direction; EP: an extension; f: a fin; HE: a heat exchanger; MP1: peak 1; MP2: peak 2; MP21: part 1; MP22: part 2; p: a heat transfer tube; r1: region 1; r2: region 2; SP: a planar portion; TH: and a through hole.

Claims (7)

1. A heat exchanger, wherein the heat exchanger comprises:
a fin configured to extend in a short side direction along a flow direction of air and a long side direction intersecting the flow direction of air; and
a heat transfer pipe penetrating the fin,
the fin is provided with a through hole,
the heat transfer tube is inserted into the through hole,
the fin includes: a planar portion; and 1 st and 2 nd peaks configured to protrude from the planar portion,
the 1 st peak is configured to be curved in the longitudinal direction,
the 2 nd peak portion has an extension portion extending in the longitudinal direction,
the extension portion is arranged to overlap with a center of the through hole in the short side direction.
2. The heat exchanger of claim 1, wherein,
the 2 nd peak is disposed between the 1 st peak and the through hole, and is configured to surround the through hole.
3. The heat exchanger of claim 1, wherein,
the 2 nd peak is configured to extend linearly in the longitudinal direction.
4. A heat exchanger according to claim 3 wherein,
the 2 nd peak is configured to protrude from the planar portion to a side opposite to the 1 st peak.
5. A heat exchanger according to claim 3 or 4 wherein,
the 2 nd peak is arranged to be offset from the 1 st peak in the short side direction.
6. The heat exchanger according to any one of claims 1 to 5, wherein,
the fin includes: a 1 st region where the through hole is not present in the short side direction; and a 2 nd region where the through hole exists in the short side direction,
in the 1 st region, 1 st areas of the 1 st peak and the 2 nd peak extending in the short side direction are larger than 2 nd areas of the 1 st peak and the 2 nd peak extending in the long side direction,
in the 2 nd region, the 1 st area is smaller than the 2 nd area.
7. A refrigeration cycle device is provided with:
the heat exchanger of any one of claims 1 to 6; and
a refrigerant cycle device,
the refrigerant cycle device is configured to circulate a refrigerant for exchanging heat between the heat exchanger and air.
CN202080107267.4A 2020-11-27 2020-11-27 Heat exchanger and refrigeration cycle device Pending CN116438421A (en)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
PCT/JP2020/044333 WO2022113298A1 (en) 2020-11-27 2020-11-27 Heat exchanger and refrigeration cycle device

Publications (1)

Publication Number Publication Date
CN116438421A true CN116438421A (en) 2023-07-14

Family

ID=81755417

Family Applications (1)

Application Number Title Priority Date Filing Date
CN202080107267.4A Pending CN116438421A (en) 2020-11-27 2020-11-27 Heat exchanger and refrigeration cycle device

Country Status (5)

Country Link
US (1) US20230417495A1 (en)
EP (1) EP4253895A4 (en)
JP (1) JPWO2022113298A1 (en)
CN (1) CN116438421A (en)
WO (1) WO2022113298A1 (en)

Family Cites Families (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS5730591U (en) * 1980-07-25 1982-02-17
JPS5730589U (en) * 1980-07-25 1982-02-17
JPS61235693A (en) * 1985-04-10 1986-10-20 Matsushita Electric Ind Co Ltd Finned tube type heat exchanger
KR100518854B1 (en) 2003-09-02 2005-09-30 엘지전자 주식회사 Heat exchanger
JP6337742B2 (en) * 2014-11-04 2018-06-06 パナソニックＩｐマネジメント株式会社 Finned tube heat exchanger
JP2019163909A (en) * 2018-03-20 2019-09-26 東京電力ホールディングス株式会社 Fin tube type heat exchanger
CN110726325A (en) * 2019-11-19 2020-01-24 广东美的暖通设备有限公司 Fin for tube-fin heat exchanger, tube-fin heat exchanger and air conditioner

Also Published As

Publication number Publication date
US20230417495A1 (en) 2023-12-28
EP4253895A4 (en) 2023-12-27
WO2022113298A1 (en) 2022-06-02
JPWO2022113298A1 (en) 2022-06-02
EP4253895A1 (en) 2023-10-04

Similar Documents

Publication Publication Date Title
US9328973B2 (en) Heat exchanger and air conditioner
JP6615316B2 (en) Finless type heat exchanger, outdoor unit of air conditioner equipped with the finless type heat exchanger, and indoor unit of air conditioner equipped with the finless type heat exchanger
US20120031601A1 (en) Multichannel tubes with deformable webs
US20110030932A1 (en) Multichannel heat exchanger fins
JP6890509B2 (en) Air conditioner
US20110120177A1 (en) Heat exchanger for shedding water
WO2021025156A1 (en) Heat exchanger and heat pump device
EP3644002B1 (en) Heat exchanger, refrigeration cycle device, and air conditioner
JP6719657B2 (en) Heat exchanger and refrigeration cycle device
JP2001027484A (en) Serpentine heat-exchanger
CN112567192A (en) Heat exchanger, heat exchanger unit, and refrigeration cycle device
KR101572674B1 (en) Heat exchanger improving the drainage
CN116438421A (en) Heat exchanger and refrigeration cycle device
EP3789697B1 (en) Heat exchanger and refrigeration cycle device
CN116547490A (en) Heat exchanger and refrigeration cycle device
CN116457625A (en) Heat exchanger and refrigeration cycle device
KR100893746B1 (en) Air conditioner
WO2021234957A1 (en) Heat exchanger and air conditioner comprising said heat exchanger
US20230175747A1 (en) Heat exchanger and refrigeration cycle apparatus
KR200314025Y1 (en) Fin tube type heat exchanger and airconditioner and refrigerator using the heat exchanger
US20230148118A1 (en) Heat exchanger and air-conditioning apparatus including the heat exchanger
CN108332295B (en) Cabinet type indoor unit and air conditioner
KR20020048366A (en) Fin tube type heat exchanger and airconditioner and refrigerator using the heat exchanger

Legal Events

Date Code Title Description
PB01 Publication
PB01 Publication
SE01 Entry into force of request for substantive examination
SE01 Entry into force of request for substantive examination