WO2022113299A1

WO2022113299A1 - Heat exchanger and refrigeration cycle device

Info

Publication number: WO2022113299A1
Application number: PCT/JP2020/044334
Authority: WO
Inventors: 暁八柳; 剛志前田; 悟梁池
Original assignee: 三菱電機株式会社
Priority date: 2020-11-27
Filing date: 2020-11-27
Publication date: 2022-06-02
Also published as: US20230358483A1; EP4253896A1; EP4253896A4; JPWO2022113299A1; CN116457625A

Abstract

A heat exchanger (HE) comprises: a fin (F) that is configured so as to extend in a shortitudinal direction (D1) along an air flow direction (D0) and a longitudinal direction (D2) that intersects the air flow direction (D0); and a heat exchanger tube (P) that passes through the fin (F). The fin (F) includes a flat portion (SP) and a plurality of first mountain portions (MP1) and a plurality of second mountain portions (MP2) configured so as to protrude from the flat portion (SP). The plurality of first mountain portions (MP1) includes a first protrusion (C1) that is configured so as to curve downward along the longitudinal direction (D2) and a second protrusion (C2) that is configured so as to curve upward along the longitudinal direction (D2). Each of the plurality of second mountain portions (MP2) is configured so as to surround each of a plurality of through holes (TH). In the shortitudinal direction (D1), the vertices of the first protrusion (C1) and the second protrusion (C2) are aligned.

Description

Heat exchanger and refrigeration cycle equipment

This disclosure relates to heat exchangers and refrigeration cycle devices.

Conventionally, there is a fin tube type heat exchanger equipped with fins and a heat transfer tube 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 (flat surface portion) and a mountain portion and a valley portion. The seat portion is formed concentrically around the outer periphery of the fin collar in order to guide the air flowing around the heat transfer tube and reduce the wake area. The front and rear of the seat are open. The peaks and valleys are continuously provided between the fin collars to vary the flow of air.

Japanese Unexamined Patent Publication No. 2005-77083

In the heat exchanger described in the above publication, since the peaks and valleys are continuously provided along the flow direction of the air, the boundary layer is formed starting from the peaks. Therefore, the valley becomes a dead water area. As a result, the local heat transfer coefficient in the valley is lowered, so that the heat transfer coefficient of the fin as a whole is lowered. In addition, the strength of the fins is insufficient because the stress is concentrated on the flat surface portion where the peaks and valleys are not provided. In addition, the discharge of water adhering to the fins in the longitudinal direction is hindered.

The present disclosure has been made in view of the above problems, and an object thereof is to provide a heat exchanger and a refrigerating cycle apparatus capable of improving heat transfer efficiency and fin strength. , To provide a heat exchanger and a refrigeration cycle device capable of improving the drainage of water adhering to fins.

The heat exchangers of the present disclosure include fins configured to extend in the lateral direction along the air flow direction and in the longitudinal direction intersecting the air flow direction, and a heat transfer tube penetrating the fins. There is. The fins are provided with a plurality of through holes arranged in the longitudinal direction. The heat transfer tube is inserted into a plurality of through holes. The fin includes a flat surface portion and a plurality of first mountain portions and a plurality of second mountain portions configured to project from the flat surface portion. The plurality of first peaks are arranged between the plurality of through holes and the first convex portion which is arranged so as to be curved downward along the longitudinal direction. It includes a second convex portion configured to be curved upward along the longitudinal direction. Each of the plurality of second mountain portions is arranged between each of the plurality of first mountain portions and each of the plurality of through holes, and is configured to surround each of the plurality of through holes. In the lateral direction, the positions of the vertices of the first convex portion and the second convex portion are aligned.

According to the heat exchanger of the present disclosure, since the first mountain portion and the second mountain portion are configured to protrude from the flat surface portion, the influence of the dead water area can be suppressed. Therefore, the heat transfer coefficient of the fins can be improved. Further, the strength of the fin can be improved by the first mountain portion and the second mountain portion. Further, since the positions of the vertices of the first convex portion and the second convex portion are aligned in the lateral direction, the water flowing from the apex of the first convex portion is guided to both sides from the apex of the second convex portion. Drainage can be improved.

It is a perspective view which shows schematic structure of the heat exchanger which concerns on Embodiment 1. FIG. FIG. 3 is a cross-sectional view taken along the line II-II of region A in FIG. It is an end view along the line III-III of FIG. It is an end view along the IV-IV line of FIG. It is a refrigerant circuit diagram which shows the refrigerating cycle apparatus which concerns on Embodiment 1. FIG. It is sectional drawing which shows schematic the structure of the part corresponding to FIG. 2 of the heat exchanger which concerns on Embodiment 2. FIG. It is an end view along the line VII-VII of FIG. It is an end view along the line VIII-VIII of FIG. It is an enlarged view of the IX part of FIG. It is sectional drawing which shows schematic the structure of the part corresponding to FIG. 2 of the heat exchanger which concerns on Embodiment 3. FIG. It is sectional drawing which follows the XI-XI line of FIG. It is sectional drawing which shows schematic the structure of the part corresponding to FIG. 2 of the heat exchanger which concerns on Embodiment 4. FIG. It is an end view along the XIII-XIII line of FIG. It is sectional drawing which shows schematic the structure of the part corresponding to FIG. 2 of the heat exchanger which concerns on Embodiment 5. FIG. It is an end view along the XV-XV line of FIG. It is an end view along the XVI-XVI line of FIG. It is sectional drawing which shows schematic the structure of the part corresponding to FIG. 2 of the heat exchanger which concerns on Embodiment 6. It is an end view along the XVIII-XVIII line of FIG. It is an end view along the XIX-XIX line of FIG.

Hereinafter, embodiments will be described with reference to the drawings. In the following, the same or corresponding parts are designated by the same reference numerals, and the description thereof will not be repeated.

Embodiment 1.
The configuration of the heat exchanger HE according to the first embodiment will be described with reference to FIGS. 1 to 4.

With reference to FIGS. 1 and 2, the heat exchanger HE includes fins F and a heat transfer tube P. The fin F is configured to extend in the lateral direction D1 along the air flow direction D0 and the longitudinal direction D2 intersecting the air flow direction D0. The fin F is configured to have a substantially rectangular shape. The heat transfer tube P penetrates the fin F. The heat transfer tube P is a circular tube. The fin F is provided with a plurality of through holes TH arranged in the longitudinal direction D2. Each of the plurality of through holes TH is formed in a circular shape. The heat transfer tube P is inserted into a plurality of through holes TH.

In the present embodiment, the heat exchanger HE includes a plurality of fins F. The plurality of fins F are stacked at intervals from each other. The heat transfer tube P penetrates the plurality of fins F in the direction D3 in which the plurality of fins F are stacked. Each of the plurality of fins F is provided with a plurality of through holes TH. The plurality of through holes TH are arranged in the longitudinal direction D2 of the fin F. The plurality of through holes TH are arranged so as to be spaced apart from each other in the longitudinal direction D2 of the fin F.

The lateral direction D1 of the fin F is orthogonal to the longitudinal direction D2. The lateral direction D1 of the fin F may be the horizontal direction. The longitudinal direction D2 of the fin F may be the vertical direction (vertical direction). The direction D3 in which the fins F are stacked is orthogonal to the lateral direction D1 and the longitudinal direction D2 of the fins F.

The heat transfer tube P has a plurality of heat transfer portions P1 and a plurality of connection portions P2. Each of the plurality of heat transfer portions P1 penetrates the plurality of fins F. Each of the plurality of heat transfer portions P1 is inserted into the plurality of through holes TH in the direction D3 in which the plurality of fins F are stacked. The plurality of heat transfer portions P1 are formed in a linear shape. Each of the plurality of heat transfer portions P1 extends in the direction D3 in which the plurality of fins F are stacked.

The plurality of connection portions P2 are portions that connect the plurality of heat transfer portions P1 to each other on the outside of the plurality of fins F. Each of the plurality of connecting portions P2 is configured in a U shape. Each of the plurality of connecting portions P2 connects a plurality of heat transfer tubes P adjacent to each other in the longitudinal direction D2 of the fin F. Each of the plurality of connecting portions P2 is connected to the end portions of the plurality of heat transfer portions P1 in the direction D3 in which the plurality of fins F are stacked. 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 four stages along the longitudinal direction D2 of the fins F.

The plurality of heat transfer units P1 are connected by the plurality of connection units P2 as follows. The heat transfer portion P1 of the first stage is connected to the heat transfer portion P1 of the second stage at the back side of the direction D3 in which a plurality of fins F are stacked by the connection portion P2. The second-stage heat transfer unit P1 is connected to the third-stage heat transfer unit P1 by a connecting portion P2 on the front side in the direction D3 in which a plurality of fins F are stacked. The heat transfer unit P1 of the third stage is connected to the heat transfer unit P1 of the fourth stage at the back side of the direction D3 in which a plurality of fins F are stacked by the connection portion P2. 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 FIGS. 2 to 4.
The fin F includes a flat surface portion SP, a plurality of first mountain portions MP1, a plurality of second mountain portions MP2, and a fin color FC. The flat surface portion SP is configured to be flat. The flat surface portion SP is configured in a flat plate shape.

The plurality of first mountain portions MP1 and the plurality of second mountain portions MP2 are configured to protrude from the flat surface portion SP. In the present embodiment, the plurality of first mountain portions MP1 and the plurality of second mountain portions MP2 project from the plane portion SP in the same direction.

The plurality of first mountain portions MP1 include a first convex portion C1 and a second convex portion C2. The first convex portion C1 is arranged between the plurality of through holes TH. The first convex portion C1 is arranged below each of the plurality of through holes TH. The first convex portion C1 is configured to be curved downward along the longitudinal direction D2 of the fin F. The second convex portion C2 is arranged between the plurality of through holes TH. The second convex portion C2 is arranged above each of the plurality of through holes TH. The second convex portion C2 is configured to be curved upward along the longitudinal direction D2 of the fin F. In the present embodiment, the plurality of first mountain portions MP1 include a plurality of first convex portions C1 and a plurality of second convex portions C2.

The first mountain portion MP1 has a portion extending along the longitudinal direction D2 of the fin F. Further, the first mountain portion MP1 has a portion extending along the lateral direction D1 of the fin F. The first mountain portion MP1 is arranged so as to be offset from the center of the through hole TH in the lateral direction D1 of the fin F. In the present embodiment, the first mountain portion MP1 is configured in an arc shape. In the present embodiment, the widths of the first mountain portions MP1 are equal.

The plurality of first mountain portions MP1 are lined up in the longitudinal direction D2 of the fin F. In the present embodiment, four first mountain portions MP1 are arranged between the two through holes TH in the longitudinal direction D2 of the fin F. In the longitudinal direction D2 of the fin F, two first mountain portions MP1 are arranged on the upper side and two on the lower side of one through hole TH.

Two first convex portions C1 arranged below one through hole TH in the longitudinal direction D2 of the fin F are arranged so as to be adjacent to each other in the longitudinal direction D2 of the fin F. The two second convex portions C2 arranged above the one through hole TH in the longitudinal direction D2 of the fin F are arranged so as to be adjacent to each other in the longitudinal direction D2 of the fin F.

The two first convex portions C1 arranged so as to be adjacent to each other are configured to be curved to the same side along the longitudinal direction D2. Further, the two second convex portions C2 arranged so as to be adjacent to each other are configured to be curved on the opposite side of the two first convex portions C1 along the longitudinal direction D2.

The two first convex portions C1 arranged near the upper through hole TH between the two through holes TH are curved so as to protrude downward. The two second convex portions C2 arranged near the lower through hole TH between the two through holes TH are curved so as to protrude upward. Of the two first convex portions C1 curved so as to protrude downward, the outer first convex portion C1 is among the two second convex portions C2 curved so as to protrude upward. It is arranged at a distance from the outer second convex portion C2.

Each of the plurality of first convex portions C1 is configured to have the same shape. The radii of curvature of each of the plurality of first convex portions C1 are equal to each other. The centers of curvature of each of the plurality of first convex portions C1 are linearly aligned with each other in the longitudinal direction D2 of the fin F. The widths of the plurality of first convex portions C1 are equal to each other. The lengths of the plurality of first convex portions C1 are equal to each other.

Each of the plurality of first convex portions C1 is configured to have the same shape except for each of the plurality of second convex portions C2 and the direction of bending along the longitudinal direction D2 of the fin F. Each of the plurality of second convex portions C2 is configured to have the same shape. The radii of curvature of each of the plurality of second convex portions C2 are equal to each other. The centers of curvature of each of the plurality of second convex portions C2 are linearly aligned with each other in the longitudinal direction D2 of the fin F. The widths of the plurality of second convex portions C2 are equal to each other. The lengths of the plurality of second convex portions C2 are equal to each other.

Each of the plurality of first mountain portions MP1 is longer than each of the plurality of second mountain portions MP2 in the lateral direction D1 of the fin F. In the longitudinal direction D2 of the fin F, each of the plurality of first mountain portions MP1 is arranged between each of the plurality of second mountain portions MP2. The center of curvature of each of the plurality of first mountain portions MP1 is linearly aligned with the center of each of the plurality of second mountain portions MP2 in the longitudinal direction D2 of the fin F.

Of the two first ridges MP1 arranged above the through hole TH in the longitudinal direction D2 of the fin F, the inner first ridge MP1 is adjacent to the second ridge MP2. Of the two first ridges MP1 arranged below the through hole TH in the longitudinal direction D2 of the fin F, the inner first ridge MP1 is adjacent to the second ridge MP2.

Each of the plurality of second mountain portions MP2 is arranged between each of the first mountain portions MP1 and each of the plurality of through holes TH. Each of the plurality of second mountain portions MP2 is configured to surround each of the plurality of through holes TH. The second mountain part MP2 is configured in an annular shape. The height of the second mountain portion MP2 protruding from the flat surface portion SP is higher than that of the first mountain portion MP1.

Each of the plurality of second mountain MP2s is configured to have the same shape. The centers of each of the plurality of second mountain portions MP2 are linearly arranged in the longitudinal direction D2 of the fin F. The widths of the plurality of second mountain MP2s are equal to each other. The diameters of the plurality of second mountain MP2s are equal to each other.

In the lateral direction D1 of the fin F, the positions of the vertices V of the first convex portion C1 and the second convex portion C2 are aligned. The apex V of the first convex portion C1 and the second convex portion C2 is the most protruding portion along the longitudinal direction D2 of the fin F. In the longitudinal direction D2 of the fin F, the positions of the vertices V of the first convex portion C1 and the second convex portion C2 are aligned linearly.

The width of the first mountain part MP1 is narrower than that of the second mountain part MP2. That is, the width of each of the plurality of first mountain portions MP1 is narrower than the width of each of the plurality of second mountain portions MP2.

The summit of the first mountain part MP1 is located in the center of the width of the first mountain part MP1. The summit of the second mountain part MP2 is located in the center of the width of the second mountain part MP2.

The height of the first mountain portion MP1 and the second mountain portion MP2 protruding from the flat surface portion SP is lower than that of the fin collar FC.

The fin color FC is configured in a cylindrical shape. The heat transfer tube P is inserted into the fin collar FC. The outer peripheral surface of the heat transfer tube P is fitted to the inner peripheral surface of the fin collar FC. The fin collar FC is configured to protrude from the flat surface portion SP. In the present embodiment, the fin collar FC protrudes from the flat surface portion SP in the same direction as the first mountain portion MP1 and the second mountain portion MP2.

Fin color FC includes a peripheral wall and a flange. The peripheral wall is configured to protrude from the flat surface portion SP. The flange is configured to project outward from the peripheral wall. The flange is provided at the tip opposite to the flat surface portion SP of the peripheral wall. In this embodiment, the fin F includes a plurality of fin color FCs.

With reference to FIG. 5, the configuration of the refrigeration cycle apparatus 100 provided with the heat exchanger HE according to the first embodiment will be described. The refrigeration cycle device 100 is, for example, an air conditioner and a refrigerator. In the first embodiment, an air conditioner will be described as an example of the refrigeration cycle device 100. The refrigeration cycle device 100 includes a refrigerant circuit RC, a refrigerant, a control device CD, and blower devices 6 and 7. The refrigeration cycle device 100 includes a refrigerant circulation device RCD. The refrigerant circulation device RCD is configured to circulate a refrigerant for heat exchange with air in the heat exchanger HE. In the first embodiment, the refrigeration cycle device 100 in which the compressor 1 is incorporated as the refrigerant circulation device 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 above 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 pipes. The refrigerant circuit RC is configured to circulate the refrigerant. The refrigerant circuit RC is configured to perform a refrigerating cycle in which the refrigerant circulates while undergoing a phase change.

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 device 7 are housed in the indoor unit 102.

In the refrigerant circuit RC, 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 during the cooling operation. It is configured as follows. Further, in the refrigerant circuit RC, during the heating operation, the refrigerant is charged 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. It is configured to circulate.

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 control each device of the refrigeration cycle device 100 by performing calculations, instructions, and the like. The control device CD is electrically connected to a compressor 1, a four-way valve 2, a pressure reducing valve 4, a blower device 6, 7, and the like, and is configured to control the operation thereof.

The compressor 1 is configured to compress the refrigerant for heat exchange with air in the heat exchanger HE. The compressor 1 is configured to compress and discharge the sucked refrigerant. The compressor 1 may be configured to have a variable capacity. The compressor 1 may be configured to change its capacity by adjusting the rotation speed of the compressor 1 based on 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 the outdoor heat exchanger (condenser) 3 during the cooling operation. Further, the four-way valve 2 is configured to allow the refrigerant discharged from the compressor 1 to flow to 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 that condenses the refrigerant during the cooling operation and as an evaporator that evaporates the refrigerant during the heating operation.

The pressure reducing valve 4 is configured to reduce the pressure by expanding the refrigerant condensed by the condenser. 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. ing. 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 the 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 as a condenser that condenses the refrigerant during the heating operation.

The blower device 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 device 6 heat exchanges between the refrigerant and air by adjusting the amount of air flowing around the outdoor heat exchanger 3 by adjusting the rotation speed of the blower device 6 based on the instruction from the control device CD. It may be configured to adjust the amount.

The blower device 7 is configured to blow indoor air to the indoor heat exchanger 5. That is, the blower 7 is configured to supply air to the indoor heat exchanger 5. The blower device 7 heat exchanges between the refrigerant and air by adjusting the amount of air flowing around the indoor heat exchanger 5 by adjusting the rotation speed of the blower device 7 based on the instruction from the control device CD. It may be configured to adjust the amount.

Subsequently, the operation of the refrigeration cycle apparatus 100 will be described with reference to FIG. The solid line arrow in FIG. 5 indicates the flow of the refrigerant during the cooling operation, and the broken line arrow in FIG. 5 indicates the flow of the refrigerant during the heating operation.

The refrigeration cycle device 100 can selectively perform cooling operation and heating operation. During the cooling operation, the refrigerant circulates in 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. Heat exchange is performed between the refrigerant flowing through the outdoor heat exchanger 3 and the air blown by the blower device 6. During the cooling operation, the indoor heat exchanger 5 functions as an evaporator. Heat exchange is performed between the refrigerant flowing through the indoor heat exchanger 5 and the air blown by the blower device 7.

In the heating operation, the refrigerant circulates in 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. Heat exchange is performed between the refrigerant flowing through the indoor heat exchanger 5 and the air blown by the blower device 7. During the heating operation, the outdoor heat exchanger 3 functions as an evaporator. Heat exchange is performed between the refrigerant flowing through the outdoor heat exchanger 3 and the air blown by the blower device 6.

Further, the refrigerating cycle device 100 can perform a defrosting operation. During the defrosting operation, the refrigerant temporarily circulates in the refrigerant circuit RC in the same order as during the cooling operation. As a result, the frost generated in the evaporator is melted by the heat of the refrigerant. In this way, the frost generated on the evaporator is removed.

Next, the action and effect of the first embodiment will be described.
According to the heat exchanger HE according to the first embodiment, since the first mountain portion MP1 and the second mountain portion MP2 are configured to protrude from the flat surface portion SP, the influence of the dead water area can be suppressed. .. Therefore, the heat transfer coefficient of the fin F can be improved. Further, the strength of the fin F can be improved by the first mountain portion MP1 and the second mountain portion MP2. Further, since the positions of the vertices V of the first convex portion C1 and the second convex portion C2 are aligned in the lateral direction D1 of the fin F, the water flowing from the apex V of the first convex portion C1 is second-convex. Drainage can be improved by guiding from the apex V of the portion C2 to both sides. In addition, this water may be condensed water, or may be defrost water generated at the time of defrosting.

According to the heat exchanger HE according to the first embodiment, the width of the first mountain portion MP1 is narrower than that of the second mountain portion MP2. Therefore, the drainage property can be improved by guiding the water staying in the second mountain portion MP2 to the first mountain portion MP1 by surface tension.

Embodiment 2.
Unless otherwise specified, the heat exchanger HE and the refrigeration cycle apparatus 100 according to the second embodiment have the same configuration, operation, and operation effect as the heat exchanger HE and the refrigeration cycle apparatus 100 according to the first embodiment. There is.

The structure of the fin F of the heat exchanger HE according to the second embodiment will be described with reference to FIGS. 6 to 9.

As shown in FIGS. 6 to 8, in the present embodiment, the top of the mountain of the first mountain portion MP1 is located outside the center of the width of the first mountain portion MP1. The summit of the second mountain part MP2 is located outside the center of the width of the second mountain part MP2. It suffices that the top of the mountain is located outside the center of the width in at least one of the first mountain part MP1 and the second mountain part MP2.

As shown in FIGS. 8 and 9, at least one of the first mountain portion MP1 and the second mountain portion MP2 includes an inner inclined surface IS and an outer inclined surface OS. The inner inclined surface IS is arranged so as to face each of the plurality of through holes TH. The outer inclined surface OS is arranged on the opposite side of each of the plurality of through holes with respect to the inner inclined surface IS. The inner inclination angle θ1 formed by the inner inclined surface IS with respect to the flat surface portion SP is smaller than the outer inclined angle θ2 formed by the outer inclined surface OS with respect to the flat surface portion SP.

Next, the action and effect of the second embodiment will be described.
According to the heat exchanger HE according to the second embodiment, the inner inclination angle θ1 formed by the inner inclined surface IS with respect to the flat surface portion SP is larger than the outer inclined angle θ2 formed by the outer inclined surface OS with respect to the flat surface portion SP. small. Therefore, it is possible to prevent the water adhering to the fin F from staying on the inner inclined surface IS. Therefore, the drainage property can be improved.

Embodiment 3.
Unless otherwise specified, the heat exchanger HE and the refrigeration cycle apparatus 100 according to the third embodiment have the same configuration, operation, and operation effect as the heat exchanger HE and the refrigeration cycle apparatus 100 according to the second embodiment. There is.

The structure of the fin F of the heat exchanger HE according to the third embodiment will be described with reference to FIGS. 10 and 11.

The first mountain portion MP1 is inclined so that the height protruding from the flat surface portion SP toward the center of the first mountain portion MP1 in the lateral direction D1 of the fin F becomes low. The second mountain portion MP2 is inclined so that the height protruding from the flat surface portion SP toward the center of the second mountain portion MP2 in the lateral direction D1 of the fin F becomes lower.

At least one of the first mountain portion MP1 and the second mountain portion MP2 may be inclined so that the height protruding from the flat surface portion SP toward the center of each of the fins F in the lateral direction D1 is lowered. ..

Next, the action and effect of the third embodiment will be described.
According to the heat exchanger HE according to the third embodiment, at least one of the first mountain portion MP1 and the second mountain portion MP2 protrudes from the flat surface portion SP toward the center in the lateral direction D1 of the fin F. It is tilted so that the height is low. Therefore, when the water adhering to the fin F slides downward, it is possible to prevent the water adhering to the fin F from being hindered from sliding down in at least one of the first mountain portion MP1 and the second mountain portion MP2. can. Therefore, the drainage property can be improved.

Embodiment 4.
Unless otherwise specified, the heat exchanger HE and the refrigeration cycle apparatus 100 according to the fourth embodiment have the same configuration, operation, and operation effect as the heat exchanger HE and the refrigeration cycle apparatus 100 according to the second embodiment. There is.

The structure of the fin F of the heat exchanger HE according to the fourth embodiment will be described with reference to FIGS. 12 and 13.

Fin F includes the middle mountain part MM. The intermediate mountain portion MM is configured to protrude from the flat surface portion SP. The intermediate mountain portion MM protrudes from the flat portion SP in the same direction as the first mountain portion MP1 and the second mountain portion MP2.

The intermediate mountain portion MM is configured to extend linearly in the longitudinal direction D2 of the fin F. The intermediate mountain portion MM is configured to connect the vertices of the first convex portion C1 and the second convex portion C2 to each other. The width of the middle mountain part MM is narrower than that of the first mountain part MP1.

Next, the action and effect of the fourth embodiment will be described.
According to the heat exchanger HE according to the fourth embodiment, the intermediate mountain portion MM is configured to connect the vertices of the first convex portion C1 and the second convex portion C2 to each other. Therefore, since the intermediate mountain portion MM functions as a drainage route, it is possible to suppress the water adhering to the fins from staying in the first mountain portion MP1. Therefore, the drainage property can be improved.

Embodiment 5.
Unless otherwise specified, the heat exchanger HE and the refrigeration cycle apparatus 100 according to the fifth embodiment have the same configuration, operation, and operation effect as the heat exchanger HE and the refrigeration cycle apparatus 100 according to the second embodiment. There is.

The structure of the fin F of the heat exchanger HE according to the fifth embodiment will be described with reference to FIGS. 14 to 16.

Fin F contains the third Yamabe MP3. The fin F is configured to protrude from the flat surface portion SP. The third mountain portion MP3 protrudes from the plane portion SP in the same direction as the first mountain portion MP1 and the second mountain portion MP2. The third mountain portion MP3 is configured to extend linearly in the longitudinal direction D2 of the fin F. The third mountain portion MP3 continuously extends from one end to the other end of the fin F in the longitudinal direction D2.

The third mountain portion MP3 is arranged outside the first mountain portion MP1 in the lateral direction D1 of the fin F. The third mountain portion MP3 is arranged outside the second mountain portion MP2 in the lateral direction D1 of the fin F. The third mountain portion MP3 is narrower than the first mountain portion MP1 and the second mountain portion MP2.

In the present embodiment, the fin F includes a plurality of third mountain parts MP3. Each of the plurality of third mountain portions MP3 extends parallel to each other in the longitudinal direction D2 of the fin F. The plurality of third mountain portions MP3 are arranged at both ends of the fin F in the lateral direction D1. The plurality of third mountain portions MP3 are arranged so as to sandwich the plurality of first mountain portions MP1 and the plurality of second mountain portions MP2. The third mountain portion MP3 is arranged at a distance from the first mountain portion MP1 and the second mountain portion MP2 in the lateral direction D1 of the fin F. The widths of the plurality of third mountain MP3s are equal to each other.

Next, the action and effect of the fifth embodiment will be described.
According to the heat exchanger HE according to the fifth embodiment, the third mountain portion MP3 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 third mountain portion MP3.

The third mountain portion MP3 is arranged outside the first mountain portion MP1 in the lateral direction D1 of the fin F, and is narrower than the first mountain portion MP1 and the second mountain portion MP2. Therefore, water adhering to the fin F can be guided from the first mountain portion MP1 to the third mountain portion MP3 by surface tension. Then, the water adhering to the fin F can be flowed along the third mountain portion MP3. Therefore, the drainage property can be improved.

Embodiment 6.
Unless otherwise specified, the heat exchanger HE and the refrigeration cycle apparatus 100 according to the sixth embodiment have the same configuration, operation, and operation effect as the heat exchanger HE and the refrigeration cycle apparatus 100 according to the fifth embodiment. There is.

The structure of the fin F of the heat exchanger HE according to the sixth embodiment will be described with reference to FIGS. 17 to 19.

In the lateral direction D1 of the fin F, the first convex portion C1 is arranged farther from the third mountain portion MP3 than the second convex portion C2. In the lateral direction D1 of the fin F, the first convex portion C1 is shorter than the second convex portion C2.

Next, the action and effect of the sixth embodiment will be described.
According to the heat exchanger HE according to the sixth embodiment, in the lateral direction D1 of the fin F, the first convex portion C1 is arranged farther from the third mountain portion MP3 than the second convex portion C2. Therefore, it becomes easy to guide the water adhering to the fin F from the second convex portion C2 to the third mountain portion MP3. Further, it is possible to suppress the movement of water adhering to the fin F from the third mountain portion MP3 to the first convex portion C1. Therefore, the drainage property can be improved.

The embodiments disclosed this time should be considered to be exemplary in all respects and not restrictive. The scope of this disclosure is set forth by the claims rather than the description above and is intended to include all modifications within the meaning and scope of the claims.

1 Compressor, 2 Four-way valve, 3 Outdoor heat exchanger, 4 Pressure reducing valve, 5 Indoor heat exchanger, 100 Refrigeration cycle device, C1 1st convex part, C2 2nd convex part, D0 Air flow direction, D1 Short Direction, D2 longitudinal direction, F fin, HE heat exchanger, IS inner inclined surface, MP1 1st mountain part, MP2 2nd mountain part, MP3 3rd mountain part, OS outer inclined surface, P heat transfer tube, SP flat part, TH through hole, V apex.

Claims

Fins configured to extend in the lateral direction along the air flow direction and in the longitudinal direction intersecting the air flow direction.
A heat transfer tube that penetrates the fins is provided.
The fins are provided with a plurality of through holes arranged side by side in the longitudinal direction.
The heat transfer tube is inserted into the plurality of through holes, and the heat transfer tube is inserted into the plurality of through holes.
The fin includes a flat surface portion and a plurality of first mountain portions and a plurality of second mountain portions configured to project from the flat surface portion.
The plurality of first mountain portions are arranged between the plurality of through holes and between the first convex portion configured to be curved downward along the longitudinal direction and the plurality of through holes. Includes a second convex portion that is arranged in and configured to curve upward along the longitudinal direction.
Each of the plurality of second mountain portions is arranged between each of the plurality of first mountain portions and each of the plurality of through holes, and is configured to surround each of the plurality of through holes. And
A heat exchanger in which the positions of the vertices of the first convex portion and the second convex portion are aligned in the lateral direction.
The heat exchanger according to claim 1, wherein the first mountain portion is narrower than the second mountain portion.
At least one of the first mountain portion and the second mountain portion has an inner inclined surface arranged so as to face each of the plurality of through holes, and each of the plurality of through holes with respect to the inner inclined surface. Includes an outer sloping surface located on the opposite side of the
The heat exchanger according to claim 1 or 2, wherein the inner tilt angle formed by the inner inclined surface with respect to the flat surface portion is smaller than the outer inclined angle formed by the outer inclined surface with respect to the flat surface portion.
According to claim 3, at least one of the first mountain portion and the second mountain portion is inclined so that the height protruding from the flat surface portion becomes lower toward the center of each in the lateral direction. The heat exchanger described.
The fins include an intermediate ridge configured to project from the flat surface.
Claims 1 to 1, wherein the intermediate mountain portion is configured to extend linearly in the longitudinal direction and is configured to connect the apex of the first convex portion and the second convex portion to each other. The heat exchanger according to any one of 4.
The fins include a third ridge configured to project from the flat surface.
The heat exchanger according to any one of claims 1 to 5, wherein the third mountain portion is configured to extend linearly in the longitudinal direction.
The heat exchange according to claim 6, wherein the third mountain portion is arranged outside the first mountain portion in the lateral direction and is narrower than the first mountain portion and the second mountain portion. vessel.
The heat exchange according to claim 6 or 7, wherein the first convex portion is arranged farther from the third mountain portion than the second convex portion in the lateral direction.
The heat exchanger according to any one of claims 1 to 8.
Equipped with a refrigerant circulation device,
The refrigerant circulation device is a refrigerating cycle device configured to circulate a refrigerant for exchanging heat with air in the heat exchanger.