WO2018139162A1

WO2018139162A1 - Heat exchanger

Info

Publication number: WO2018139162A1
Application number: PCT/JP2017/047004
Authority: WO
Inventors: 寿守務吉村; 吉田　育弘; 一普宮; 皓亮宮脇; 典宏米田; 貴博堀
Original assignee: 三菱電機株式会社
Priority date: 2017-01-24
Filing date: 2017-12-27
Publication date: 2018-08-02
Also published as: JPWO2018139162A1; JP6755338B2

Abstract

In this heat exchanger, a plurality of planar fins having collar parts each extending from one surface into a tapered cylindrical shape are stacked, the collar parts of the fins adjacent to each other in the stacking direction are connected to one another so as to constitute a liquid passage tube, and a resin film is formed on the inner surface of the liquid passage tube. Inside the collar parts, second fins that are discontinuous in the peripheral direction of the collar parts are provided.

Description

Heat exchanger

The present invention relates to a plate fin type heat exchanger.

A conventional heat exchanger includes, for example, a plurality of flat plate-shaped fins provided with a plurality of fin collars as disclosed in Patent Document 1. A plurality of fins are laminated so that the hole centers of the plurality of cylindrical fin collars coincide with each other to form a fin core. The fin collars connected to each other are joined and sealed with a resin to form a plurality of liquid passing pipes. The liquid passage tube is anticorrosive on the surface by a resin film formed on the inner peripheral surface.

Japanese Patent Publication No. 61-015359

In the heat exchanger described in Patent Document 1, the resin film formed on the inner peripheral surface of the liquid flow pipe serves as a thermal resistance. For this reason, heat exchange performance falls. In particular, when a relatively high-viscosity fluid such as water or antifreeze flows through the flow tube, or when the flow tube is configured with a small diameter for high heat transfer, the flow of the flow tube is laminar. There is a problem that the heat exchange performance deteriorates.

The present invention is intended to solve the above-described problems, and an object of the present invention is to provide a heat exchanger capable of obtaining high heat exchange performance even when a fluid flowing in a liquid passage tube is easily laminarized. .

In the heat exchanger of the present invention, a plurality of plate-like fins having a collar portion extending in a tapered shape from one surface are stacked, and the collar portions of fins adjacent to each other in the stacking direction are connected to form a liquid flow pipe. In the heat exchanger in which a resin film is formed on the inner surface of the liquid flow pipe, the second fin discontinuous in the circumferential direction of the collar portion is provided inside the collar portion.

According to the heat exchanger of the present invention, the second fins that are discontinuous in the circumferential direction are arranged inside the collar portion, and the resin film is formed on the inner surface of the liquid passage tube, so that it flows in the liquid passage tube. Even when the fluid is easily laminarized, the heat exchange performance is improved by the leading edge effect. In addition, since the second fin is formed discontinuously, a portion without the second fin, specifically a gap, can be formed in the circumferential direction, and flow resistance can be suppressed.

It is a perspective view which shows the external appearance of the heat exchanger which concerns on Embodiment 1 of this invention. FIG. 2 is a front view showing fins when the heat exchanger according to Embodiment 1 of the present invention is viewed from the AA direction of FIG. FIG. 3 is a cross-sectional view showing the heat exchanger according to Embodiment 1 of the present invention when viewed from the BB direction of FIG. It is a perspective view which shows the structure of the fin collar of the heat exchanger which concerns on Embodiment 1 of this invention. It is a perspective view which shows the structure of the fin of the modification of the heat exchanger which concerns on Embodiment 1 of this invention. It is sectional drawing which shows the heat exchanger which concerns on Embodiment 2 of this invention. It is a perspective view which shows the structure of the one part fin collar of the heat exchanger which concerns on Embodiment 2 of this invention. It is sectional drawing which shows the heat exchanger which concerns on Embodiment 3 of this invention. It is a top view which shows the inside of the fin collar of the heat exchanger which concerns on Embodiment 3 of this invention seeing from a liquid direction. It is a perspective view which shows the structure of the fin collar of the heat exchanger which concerns on Embodiment 3 of this invention. It is sectional drawing which shows the heat exchanger which concerns on Embodiment 4 of this invention. It is a top view which sees the inside of the fin collar of the heat exchanger which concerns on Embodiment 4 of this invention from the direction along a liquid pipe. It is a perspective view which shows the structure of the fin collar of the heat exchanger which concerns on Embodiment 4 of this invention. It is sectional drawing which shows the heat exchanger which concerns on Embodiment 5 of this invention. It is a top view which sees the inside of the fin collar of the heat exchanger which concerns on Embodiment 5 of this invention from the direction along a liquid pipe. It is a perspective view which shows the structure of the fin collar of the heat exchanger which concerns on Embodiment 5 of this invention. It is sectional drawing which shows the modification of the heat exchanger which concerns on Embodiment 5 of this invention. It is sectional drawing which shows the heat exchanger which concerns on Embodiment 6 of this invention. It is a top view which sees the inside of the fin collar of the heat exchanger which concerns on Embodiment 6 of this invention from the direction along a liquid pipe. It is sectional drawing which shows the heat exchanger which concerns on Embodiment 7 of this invention. It is a top view which sees the inside of the fin collar of the heat exchanger which concerns on Embodiment 7 of this invention from the direction along a liquid pipe. It is sectional drawing which shows the heat exchanger which concerns on Embodiment 8 of this invention. It is a top view which sees the inside of the fin collar of the heat exchanger which concerns on Embodiment 8 of this invention from the direction along a liquid pipe. It is sectional drawing which shows the heat exchanger which concerns on Embodiment 9 of this invention. It is a top view which sees the inside of the fin collar of the heat exchanger which concerns on Embodiment 9 of this invention from the direction along a liquid pipe. It is a perspective view which shows the structure of the fin collar of the heat exchanger which concerns on Embodiment 9 of this invention. It is a cross-sectional enlarged view which shows the heat exchanger which concerns on Embodiment 10 of this invention.

Hereinafter, a heat exchanger according to an embodiment of the present invention will be described with reference to the drawings. In different embodiments, the same or corresponding elements will be described with the same reference numerals, and the description will not be repeated unless there is a significant difference. In the drawings, the relationship between the sizes of the elements may be different from the actual one. In each embodiment, the shape of each part can be freely changed and can be combined with each other without departing from the spirit of the invention. In the description, the shape of each element such as plate, parallel, and cylinder is not strictly limited to the shape of plate, parallel, cylinder, and the like. In the case where the effects of the invention are obtained, such a state is also included.

<Embodiment 1>
FIG. 1 is a perspective view showing an appearance of a heat exchanger 10 according to Embodiment 1 of the present invention. The heat exchanger 10 has a fin core constituted by a plurality of plate-like fins 1 stacked at intervals and a liquid passage 13 penetrating the plurality of fins 1 in the overlapping direction. FIG. 2 is a front view showing the fin 1 when the heat exchanger 10 according to Embodiment 1 of the present invention is viewed from the AA direction (the overlapping direction of the fins 1) in FIG. Note that the direction in which the fins 1 overlap and the direction in which the fluid flows in the fluid passage 13, that is, the fluid passage direction, are the same direction. Below, especially the description regarding a flow is demonstrated mainly using a liquid flow direction. The heat exchanger 10 performs heat exchange between the air on the surface of the fin 1 and the fluid flowing in the liquid passage 13. Below, the fluid which flows into the liquid flow pipe 13 is demonstrated as water. However, the fluid flowing through the liquid passage 13 may be water or a fluorine-based inert liquid to which a chemical that lowers the freezing point of the fluid is added.

1, the flow direction of the air WF and the flow direction of the water RF that is a heat transfer medium are indicated by arrows. The air WF is generated by, for example, a blower. The air WF may use natural convection or wind generated by other driving force instead of the blower.

Water RF enters from one end of the fin 1 on which the liquid passage 13 of the fin 1 is overlapped and exits from the other end. In FIG. 1, a plurality of liquid passing pipes 13 are provided in the fin 1, and the plurality of liquid passing pipes 13 are connected to each other by a U-shaped pipe (not shown) or the like so as to be reversed and flow in parallel at the other end. A configured example is shown. In FIG. 2, the liquid flow pipes 13 are arranged in two rows in the flow direction (row direction) of the air WF orthogonal to the overlapping direction of the fins 1, and a plurality of the liquid passage tubes 13 are arranged in the vertical direction (stage direction) for each row. The structure is shown. Further, the arrangement structure in which the liquid passage pipes 13 are formed is formed in a staggered arrangement as shown in FIG.

Further, as shown in FIG. 1, since water RF flows into a large number of liquid passages 13 from one end in the overlapping direction, the water RF branches at the inlet header 2 and connects the connection pipes 4 to the respective liquid passages 13. It flows in through. The water RF that is reversed by the U-shaped tube at the other end of the heat exchanger 10 and flows out in parallel from the inflow pipes 13 flowing in the opposite direction to the inflow direction is joined to the outlet header 3 via another connection pipe 4. It flows out after. The liquid passing pipe 13 is formed at a different position in the direction in which the wind flows. However, the water RF flows from the inlet header 2 into the liquid flow pipe 13 positioned on the downstream side of the wind, and the water RF flows out from the liquid flow pipe 13 positioned on the upstream side to the outlet header 3. For this reason, heat exchange becomes favorable. In the above, the water RF is configured so as to reciprocate the fin 1 that is formed by inverting the two liquid-passing tubes 13 at the other end. However, the liquid passage 13 can be variously changed. For example, the water RF may flow out from the outlet header 3 installed at the other end without reciprocating the overlapped fins 1. Further, the water RF may be connected so as to reciprocate a plurality of times while meandering inside the superposed fins 1.

The liquid flow tube 13 of the first embodiment is formed by connecting fin collars formed on the fins 1. The fin 1 is made of metal (for example, aluminum). The fin collar is a portion protruding in a cylindrical shape from one surface of the fin 1 by, for example, drawing. The fin collar is typically cylindrical and protrudes from one surface of the fin 1 in the vertical direction. Further, as will be described later, a part of the fin collar is deformed. However, the fin collar has a cylindrical inner surface and an outer surface that are tapered in the vertical direction from one surface of the fin 1. Hereinafter, the tapered portion of the fin collar is referred to as a collar portion 11. The tip of the collar portion 11 of the fin 1 on the other side in the overlapping direction is inserted into the opening of the collar portion 11 of the fin 1 on one side in the overlapping direction. Thus, the fin collars of the two fins 1 are bonded to each other between the inner surface and the outer surface of the cylindrical portion, so that the liquid passing tube 13 is configured. For adhesion between the collar portions 11 of the two fins 1, for example, a resin adhesive or brazing is used.

A resin film 14 is formed of a resin material on the inner surface of the liquid flow pipe 13 (see FIG. 27). The resin film 14 may be used for joining the collar portion 11. In the case where the fin 1 is a metal whose main component is aluminum, the formation of the resin film 14 can prevent corrosion due to water. In addition, when the same resin is used for bonding, manufacturing becomes easy and productivity is improved.

FIG. 3 is a cross-sectional view showing a cross section of the heat exchanger 10 according to the first embodiment of the present invention as seen from the BB direction of FIG. FIG. 4 is a perspective view schematically showing the shape of the fin collar according to the first embodiment of the present invention. FIG. 3 shows an enlarged view of the vicinity of the portion where the water RF is distributed from the inlet header 2 via the connecting pipe 4 to the liquid passing pipe 13. The connecting pipe 4 has a flange-like portion formed at the tip thereof. The flange-like portion of the connecting pipe 4 is bonded to the exposed surface of the fin 1 exposed on the inlet header 2 side so that the connecting pipe 4 and the liquid passing pipe 13 communicate with each other. The resin film 14 formed on the inner surface of the liquid flow pipe 13 is thin. For this reason, the resin film 14 is omitted in FIG.

3 and 4, the fin collar has second fins 12 that protrude inside the liquid passage tube 13. In the first embodiment, the second fin 12 is a protrusion protruding toward the center of the cross section of the pipe perpendicular to the liquid passing direction of the liquid passing pipe 13. The second fin 12 is made of a material continuous with the collar portion 11. The second fin 12 has a surface portion that is inclined with respect to the tapered surface of the collar portion 11. The tapered surface of the collar portion 11 is a surface formed in a cylindrical shape that is tapered toward the tip. The tapered surface of the collar portion 11 has a surface slightly inclined with respect to the liquid flow direction. The second fins 12 exist as protruding structures that are discontinuous in the circumferential direction and liquid passing direction of the collar portion 11 inside the collar portion 11. The second fins 12 are not continuous in the circumferential direction and the liquid passing direction. For this reason, a portion without the second fin 12 exists somewhere in the circumferential direction or somewhere in the liquid flow direction inside the collar portion 11.

In the first embodiment, inside the single collar portion 11, there are provided second fins 12 that are two protrusions at positions separated in the circumferential direction. The second fins 12, which are two protrusions, are provided at positions where they face each other, that is, at positions that are point-symmetric with respect to the center of the cross section of the tube perpendicular to the liquid passing direction of the collar portion 11. FIG. 3 shows a case where the protrusion of the second fin 12 has a dome-shaped cross section. Note that the second fins 12 may protrude in a columnar shape, a prismatic shape, a rectangular shape, or the like. The longer the length of the second fin 12 protruding toward the inside, the greater the heat transfer area, and at the same time, the effect of promoting heat transfer is obtained in almost the entire area of the enlarged area due to the leading edge effect. improves. However, if the length by which the second fin 12 protrudes toward the inside becomes too long, the flow resistance in the liquid passage tube 13 increases, and the power for flowing the water RF into the tube increases. For this reason, the length by which the second fin 12 projects inward is, for example, about 1/10 of the inner diameter of the collar portion 11 to about ½ of the inner diameter of the collar portion 11 at the maximum. It is good to set.

In the overlapping direction of the fins 1, the length of the second fin 12 is shorter than the length of the collar portion 11. In the direction in which the fins 1 are overlapped, the length of the second fins 12 is shorter than the interval between the adjacent fins 1. The second fins 12 are provided in the middle of the overlapping direction of the collar portion 11 in the overlapping direction of the fins 1. The second fins 12 are not formed on the fin 1 side having the second fins 12 and the front end side of the collar portion 11. On the side of the fin 1 having the second fin 12 in the collar portion 11 and the tip side of the collar portion 11, the cylindrical surface of the collar portion 11 is left. As a result, the tapered surfaces of the two collar portions 11 are in close contact with each other between the adjacent fins 1, and the liquid passing tube 13 having excellent sealing performance and strength is configured.

Hereinafter, a method for manufacturing the heat exchanger 10 according to the first embodiment will be described. First, a thin metal plate is prepared as a material for the fin 1, and a fin collar is formed by drawing with a press. Furthermore, the press work which forms the 2nd fin 12 which is protrusion toward the center from the outer side of the taper surface of the collar part 11 in a fin collar is performed. In this way, the fin 1 in which the second fin 12 is formed can be manufactured.

Next, the front end portion of the collar portion 11 provided on the fin 1 is inserted into the opening of the collar portion 11 provided on the adjacent fin 1. The insertion of the tip of the collar portion 11 into the opening of the collar portion 11 is repeated using the other plurality of fins 1, and the plurality of collar portions 11 are sequentially connected to form the liquid passage 13.

Then, a resin material is injected into each of the plurality of liquid pipes 13 from each opening (opening of the collar portion 11) of the fin 1 arranged at one end among the plurality of fins 1 stacked at intervals. The connecting pipe 4 fixed to the inlet header 2 and the outlet header 3 is fitted into each opening after the resin material is injected. Further, as described above, the tip end portion of the collar portion 11 protruding from the fin 1 arranged at the other end of the plurality of fins 1 stacked at intervals is inserted into the U-shaped tube and fixed.

Thereafter, the heat-treated fin 1 is fluidized to fluidize the resin material, and the inner peripheral surface of the liquid passage 13, that is, the entire fin collar interior that is the collar portion 11 and the second fin 12 is fluidized resin. Cover with wood. Then, the resin material is infiltrated and joined to the joining surfaces of the fin fins connected to each other, and the resin material is cooled and solidified to be fixed. In addition, after applying the resin material to the fin collar and sequentially connecting the collar portions 11 to assemble the fin core, the fin core may be heated and cooled to fix the resin material.

Also, another joining method will be described. The tip of another collar portion 11 is inserted into the opening of the collar portion 11 and the adjacent fins 1 are sequentially connected. Thereafter, the contact portions of the collar portions 11 are brazed and joined. Thereafter, a resin material is injected or applied on the inner surface of the liquid passage tube 13, and the inner peripheral surface of the liquid passage tube 13 is covered with the resin material. Then, the covered resin material is solidified by cooling and fixing. For brazing, an aluminum silicon brazing material for aluminum brazing is used. Alternatively, a clad material having a brazing material layer formed on both sides is used as the fin 1.

When the resin film 14 is formed, the heating temperature, the cooling temperature, and the time are adjusted according to the type of the resin material. The film thickness of the resin film 14 formed of a resin material on the inner peripheral surface of the liquid flow pipe 13 is desirably 50 μm or less.

In addition, when the front end portion of the collar portion 11 is inserted into the adjacent collar portions 11 and the plurality of collar portions 11 are sequentially connected, the collar portion 11 has a tapered cylindrical shape with a taper. If the taper shape is adjusted, the distance between the two fins 1 through which air flows is maintained. However, if an assembly spacer jig is inserted between the two fins 1, the distance between the two fins 1 can be maintained with higher accuracy.

Next, the operation of the heat exchanger 10 according to the first embodiment will be described by taking as an example a case where hot water or cold water is used as a heat transfer medium and accommodated in an indoor unit of an air conditioner.

In the heating operation of the air conditioner, the heat transfer medium is heated by heat exchange with the refrigerant in the outdoor unit, and flows into the indoor unit as hot water (here, the flow of water RF is used as the hot water RF). The hot water RF flows in from the inlet header 2 of the heat exchanger 10 accommodated in the indoor unit, and flows through the liquid passage pipes 13 positioned on the downstream side of the air WF via the connection pipes 4. The hot water RF that has flowed through the respective flow pipes 13 on the downstream side of the air WF flows into the respective liquid flow pipes 13 positioned on the upstream side of the air WF via U-shaped pipes. The hot water RF that has flowed through the liquid passages 13 on the upstream side of the air WF joins and flows through the outlet headers 3 through the connection pipes 4 and flows out toward the outdoor unit. In the cooling operation of the air conditioner, the heat transfer medium is cooled by heat exchange with the refrigerant in the outdoor unit, and flows into the indoor unit as cold water (here, the flow of water RF is used as the cold water RF). The heat exchanger 10 flows. The flow of the cold water RF in the heat exchanger 10 is the same as the flow during the heating operation.

In the heating operation, the indoor air WF is sucked by the blower of the indoor unit and blown into the room in the flow direction of the air WF via the heat exchanger 10. The air WF sucked by the blower flows between the fins 1 adjacent to each other in the overlapping direction from the direction orthogonal to the overlapping direction of the fins 1. Then, the air WF exchanges heat with the hot water RF in each flow-through pipe 13 located on the windward side, and exchanges heat with the hot water RF in each liquid-flow pipe 13 located on the leeward side to become warm air. It flows out into the room. In the case of the cooling operation, the air WF heat-exchanged with the cold air is sent into the room by the cold water RF flowing in the liquid passages 13 on the leeward side and the windward side.

In a conventional heat exchanger, when a relatively high viscosity fluid such as water or antifreeze liquid is allowed to flow through the liquid passage pipe, or when the liquid passage pipe is constituted by a small pipe having a small diameter for high heat transfer, There has been a problem that the flow of the liquid passing pipe becomes laminar and the heat exchange performance deteriorates. On the other hand, according to the heat exchanger 10 according to the first embodiment, the second fin 12 is configured so as to block a part of the flow of the fluid flowing along the inner surface of the collar portion 11 inside the liquid passage 13. Is arranged. For this reason, even when there is a laminar flow of the heat transfer medium, the heat transfer rate is improved by the leading edge effect. The leading edge effect is that a thin thermal boundary layer is formed from the leading edge of the tip of the second fin 12 around the second fin 12 placed in isolation in the laminar flow, and the heat transfer coefficient Says the effect of improving. Here, a case where two second fins 12 are arranged in the circumferential direction inside one collar portion 11 is shown. However, the number of the second fins 12 may be one, and the heat transfer promoting effect becomes higher as the number is larger.

In addition to the synergistic effect of the area expansion effect and the leading edge effect, the second fin 12 directly exchanges heat between water and air at the front and back of the expanded area portion. For this reason, unlike the case of providing a normal area expansion fin, for example, a plurality of thin plates on the inner surface of the collar portion 11, the expansion area portion has no heat conduction loss (fin efficiency is almost 100%) and is maximally effective. Heat transfer promotion effect is obtained. By forming the fin 1 and the second fin 12 having no heat conduction loss inside the liquid passage 13, water can flow in the liquid passage 13 compared to the case without the second fin 12. Since the area for heat exchange can be increased efficiently, the heat exchange performance is improved. Furthermore, the more the second fin 12 is dome-shaped (hemispherical), the less disturbed the water flow around the second fin 12 is. In addition, the flow of water tends to be a smooth flow with no flow separation, and the effect of expanding the area of the second fin 12 is more effectively applied.

Further, in the liquid passing direction, a smooth tapered surface in which the second fin 12 is not formed is formed in a portion where the collar portion 11 rises from the fin 1, that is, a base portion (root portion) of the collar portion 11. . For this reason, when the plurality of collar portions 11 are connected to each other, the sealing property and the adhesive strength are improved. Moreover, since the several 2nd fin 12 exists intermittently with respect to the water which flows in a liquid flow direction, and many front edges by the several 2nd fin 12 are made, the heat-transfer promotion effect becomes high.

FIG. 5 is a perspective view showing the structure of the fin 1 of a modification of the heat exchanger 10 according to Embodiment 1 of the present invention. In the modification, a cut-and-raised portion 43 is provided in a part of the fin 1. The configuration is the same as that of the first embodiment except that the cut-and-raised portion 43 is provided. Therefore, sectional views and the like are omitted. FIG. 5 shows a case where the cut and raised portion 43 is trapezoidal. However, the shape of the cut-and-raised portion 43 can be arbitrarily changed. The cut and raised portion 43 may be formed by inserting a plurality of cut portions 44 into the fin 1 and raising the cut portions 44 in the direction in which the fins 1 are overlapped. By forming the cut-and-raised portion 43, heat transfer between the fin 1 and the air WF is promoted by the leading edge effect. In order to enhance the leading edge effect, the cut-and-raised portion 43 is preferably parallel to the flow of the air WF. Further, at the time of manufacturing the heat exchanger 10 of the modified example, the cut and raised portion 43 may be used for holding between the adjacent fins 1. The strength between the adjacent fins 1 can be improved by connecting the raised portions 43 between the adjacent fins 1.

Thus, in the heat exchanger 10 of the first embodiment, the second fins 12 are present, and the resin film 14 is formed on the inner surface of the liquid passage 13. Thereby, even when the flow of the water RF is laminarized, the heat exchange performance can be effectively improved. Moreover, since the 2nd fin 12 is discontinuous in the circumferential direction, the part without a 2nd fin, ie, a clearance gap, can be formed in the circumferential direction, and flow resistance can be suppressed. Water RF, which is a heat transfer medium, due to an increase in the operation frequency of air conditioners during the mid-season when the air conditioning load is relatively small, such as spring or autumn, or a decrease in the air conditioning load due to high thermal insulation of buildings or houses. The flow rate of water is decreasing, and the operation ratio at which the flow of water RF is laminarized is increasing. Therefore, the necessity of improving the heat exchange performance even when the water RF flow is laminarized is becoming more and more important.

<Embodiment 2>
FIG. 6 is a cross-sectional view showing a heat exchanger 10 according to Embodiment 2 of the present invention. FIG. 6 corresponds to a cross-sectional view of the first embodiment viewed from the BB direction in FIG. In addition, the whole structure of the heat exchanger 10 of this Embodiment 2 is the same as that of the perspective view of FIG. 1 of Embodiment 1, and the front view of FIG. 2, and description is abbreviate | omitted. FIG. 7 is a perspective view showing the structure of a part of the fin collar of the heat exchanger according to Embodiment 2 of the present invention. The second fin 12 of the fin collar of FIG. 7 is a protrusion that protrudes inward as in the fin collar shown in FIG. 4 of the first embodiment. However, the second fin 12 of the second embodiment is different from the protrusion of FIG. 4 in that the position of the protrusion is shifted in the circumferential direction. And the heat exchanger 10 of this Embodiment 2 connects the fin collar shown in FIG. 4 and the fin collar shown in FIG. 7 alternately, and the liquid-flow pipe | tube 13 is formed. That is, when viewed from the liquid passing direction, in the fins 1 adjacent to each other in the overlapping direction, the arrangement of the second fins 12 is shifted in the circumferential direction (offset fin arrangement). Therefore, in the plurality of stacked fins 1, the arrangement of the second fins 12 is alternately shifted in the circumferential direction when viewed from the liquid passing direction. Note that the manufacturing method and operation are the same as those in the first embodiment, and a description thereof will be omitted.

In FIG. 6, in the two adjacent fins 1, when viewed from the liquid passing direction, the second fin 12 of the other fin 1 is in the middle of the circumferential pitch of the two second fins 12 of the one fin 1. Is located. That is, in the adjacent fins 1, the second fins 12 are arranged so as to be shifted from each other by a half pitch (half cycle) in the circumferential direction.

Thus, if the pitch is shifted in the circumferential direction, the influence of the wake of the second fins 12 arranged upstream can be suppressed, and the heat transfer performance is further improved. The interval between the second fins 12 at the same position when viewed from the liquid passing direction is the same as that between the fins 1 in the overlapping direction. In Embodiment 1, the 2nd fin 12 existed discontinuously in the liquid flow direction. However, in the first embodiment, the distance between the second fin 12 on the upstream side and the second fin 12 on the downstream side is narrow, and a high leading edge effect may not be obtained with the second fin 12 on the downstream side. is there. Furthermore, in the second embodiment, the density of the second fins 12 is the same as that in the first embodiment, but the second fins 12 seen from the liquid passing direction are doubled, and a high leading edge effect is obtained. .

The above describes the case where there are a plurality of second fins 12 in one collar portion 11. However, when the number of the second fins 12 in one collar part 11 is one, the position of the second fin 12 in the adjacent collar part 11 is a tube cross section orthogonal to the liquid passing direction of the collar part 11. The position may be 180 degrees opposite to the center of. In addition, about the 3 or more fin 1 laminated | stacked continuously, the position of the 2nd fin 12 can also be shifted and offset arrangement | positioning is also possible. In that case, the position of the second fin 12 may be shifted by 1/3 pitch, 1/4 pitch, or the like. However, when the arrangement of the second fins 12 of the adjacent fins 1 is arranged so as to be shifted from each other by a half cycle in the circumferential direction as shown in FIG. 6, this structure improves the heat transfer performance and improves the production. It is very good in terms of ease.

<Embodiment 3>
FIG. 8 is a cross-sectional view showing a heat exchanger 10 according to Embodiment 3 of the present invention. FIG. 8 corresponds to a cross-sectional view of the first embodiment viewed from the BB direction in FIG. In addition, the whole structure of the heat exchanger 10 of this Embodiment 3 is the same as that of the perspective view of FIG. 1 of Embodiment 1, and the front view of FIG. 2, and description is abbreviate | omitted. FIG. 9 is a plan view showing the inside of the fin collar of the heat exchanger 10 according to Embodiment 3 of the present invention when viewed from the liquid direction. FIG. 10 is a perspective view showing the structure of the fin collar of the heat exchanger 10 according to Embodiment 3 of the present invention.

A plurality of second fins 12 are formed in the circumferential direction inside the collar portion 11 of the fin collar. The second fin 12 of the third embodiment is formed by processing the tip of the fin collar. In the first and second embodiments, the second fin 12 is formed in the middle of the liquid passage direction of the collar portion 11. However, the second fin 12 of the third embodiment is at the tip of the collar portion 11. Therefore, the second fin 12 is a portion that continues from the tip of the collar portion 11. The second fin 12 is a portion bent inward from the tip of the collar portion 11. The cylindrical shape does not change from the base portion of the collar portion 11 rising from the fin 1 to the tip end of the collar portion 11 connected to the second fin 12. For this reason, the surface of the collar portion 11 connecting the two fins 1 remains cylindrical.

The second fin 12 is formed by dividing the tip of the fin collar into a plurality of portions in the circumferential direction and bending the divided portions so as to project inside the collar portion 11. The plurality of second fins 12 are bent so as to incline in the same direction of the liquid flow direction.

The collar portion 11 extends in the vertical direction with respect to one surface of the fin 1. And the 2nd fin 12 of this Embodiment 3 is bent so that the tip may return toward one side of fin 1. The second fin 12 has a shape that is folded at an acute angle so that both surfaces form an acute angle at the tip of the collar portion 11. For this reason, the flow path area inside the liquid flow pipe 13 is ensured widely.

For example, when the collar portion 11 extending in the vertical direction with respect to one surface of the fin 1 is formed, such a fin collar is divided into a plurality in the circumferential direction by forming a slit at the tip thereof. Then, it can form by performing the process which bend | folds the part divided | segmented by the slit toward the one surface of the fin 1. FIG. The tapered surface of the base portion of the fin collar remains as the collar portion 11, and this portion is used for connection with the adjacent collar portion 11. Except for the structure part of the second fin 12, the manufacturing process of the other parts and the operation of the heat exchanger are the same as those in the above embodiment, and thus the description thereof is omitted.

Inside the collar portion 11 of the heat exchanger 10 according to the third embodiment, the tip portions of the plurality of second fins 12 are intermittently present in the circumferential direction, and the tip portions of the plurality of second fins 12 are present. A part of the flow of the water RF that flows along the inner surface of the liquid flow pipe 13 is blocked. For this reason, the flow of the water RF that flows in the vicinity of the collar portion 11 of the liquid flow pipe 13 flows so as to flow between the adjacent second fins 12 or the inner center of the collar portion 11 by colliding with the second fin 12. Change direction. A line with an arrow in FIG. 10 schematically shows how the flow along the inner surface of the collar portion 11 changes.

Since the second fin 12 protrudes into the collar portion 11, the heat exchange performance is improved by the leading edge effect and the effect of increasing the contact area even when the flow of the water RF is laminarized. Further, when a flow in which the flow of the water RF is made into a laminar flow is generated, the surface of the second fin 12 and the end thereof are in contact with the water RF to exchange heat. Since a gap is formed in the circumferential direction between the adjacent second fins 12, heat exchange performance can be improved while suppressing flow resistance. Here, a case where eight second fins 12 are arranged in the circumferential direction of the opening of the collar portion 11 is shown. However, the number of the second fins 12 may be two, and the greater the number of the second fins 12, the higher the heat transfer promoting effect and the easier the bending process.

In the second fin 12, in addition to the synergistic effect of the area expansion effect and the leading edge effect, the area expansion portion where the leading edge effect is obtained and the collar portion 11 are continuous. For this reason, the thermal resistance between the area enlarged portion and the collar portion 11 is relatively small (decrease in fin efficiency is suppressed). As a result, the effect of promoting heat transfer can be obtained as effectively as possible. By forming the second fin 12 having a relatively small heat conduction loss inside the liquid passage 13, the water RF is heated in the liquid passage 13 compared to the case where the second fin 12 is not provided. The exchange area can be increased efficiently, and the heat exchange performance is improved.

In addition to the synergistic effect of the area expansion effect and the leading edge effect, the second fin 12 directly exchanges heat between water and air at the front and back of the expanded area portion. For this reason, unlike the case where a plurality of thin plates are provided on the inner surface of the normal area expansion fin, for example, the collar portion 11, the expansion area portion has no heat conduction loss (fin efficiency is almost 100%). As a result, the effect of promoting heat transfer can be obtained as effectively as possible. By forming the second fin 12 having no heat conduction loss in the liquid passage 13, the water RF exchanges heat in the liquid passage 13 as compared with the case where there is no second fin 12. The area can be increased efficiently and the heat exchange performance is improved.

<Embodiment 4>
FIG. 11 is a cross-sectional view showing a heat exchanger 10 according to Embodiment 4 of the present invention. FIG. 11 corresponds to a cross-sectional view of the first embodiment viewed from the BB direction in FIG. In addition, the whole structure of the heat exchanger 10 of this Embodiment 4 is the same as that of the perspective view of FIG. 1 of Embodiment 1, and the front view of FIG. 2, and description is abbreviate | omitted. FIG. 12 is a plan view showing the inside of the fin collar of the heat exchanger 10 according to the fourth embodiment of the present invention as viewed from the liquid direction. FIG. 13 is a perspective view showing the structure of the fin collar of the heat exchanger 10 according to the fourth embodiment.

The heat exchanger 10 of the fourth embodiment is the same as that of the third embodiment in that there are a plurality of bent second fins at the tip of the collar portion 11. However, the heat exchanger 10 of the fourth embodiment is different in that second fins having different bending directions with respect to the liquid passing direction in the plurality of second fins bent are mixed. Some of the second fins 12 a have a shape that is bent at an acute angle with respect to the collar portion 11 so that the tip is directed to one surface of the fin 1 as in the third embodiment. The second fin 12b that is adjacent to the second fin 12a in the circumferential direction is bent so as to protrude inward from the collar portion 11, and the tip thereof is away from one surface of the fin 1 with respect to the collar portion 11. The shape is bent at an obtuse angle. Therefore, the latter second fin 12 b is inclined in the same direction as the collar portion 11 and is bent inside the collar portion 11 at a slight angle so as to form an obtuse angle with respect to the tapered surface of the collar portion 11. Note that the manufacturing method and operation are the same as those in the third embodiment, and a description thereof is omitted. The 2nd fin 12a is the 1st shape bent so that the tip might approach one side of fin 1. FIG. The 2nd fin 12b is the 2nd shape bent so that the tip may go away from one side of fin 1. FIG. The second fins 12a having the first shape and the second fins 12b having the second shape are alternately arranged in the circumferential direction.

In the fourth embodiment, the

second fins

12a and 12b adjacent to each other in the circumferential direction inside one collar portion 11 are bent in opposite directions in the liquid passing direction. Since it is configured in this way, a larger gap is formed between the second fins 12 than in the third embodiment, and the heat exchange performance can be improved as in the third embodiment while the flow resistance is suppressed. In FIG. 13, the flow of the water RF along the inner surface of the collar portion 11 is changed in the flow direction by the second fins 12 a, flows between the adjacent second fins 12 a, and downstream in the liquid flow direction. The state of flowing on the surface of the existing second fin 12b is schematically shown. Such a flow of water RF also leads to suppression of upstream disturbance. For this reason, the leading edge effect of the second fin 12b on the downstream side can be obtained to the maximum (the influence of the wake can be suppressed to the maximum), and the heat transfer performance is further improved.

<Embodiment 5>
FIG. 14 is a cross-sectional view showing a heat exchanger 10 according to Embodiment 5 of the present invention. 14 corresponds to a cross-sectional view of the first embodiment viewed from the BB direction in FIG. In addition, the whole structure of the heat exchanger 10 of this Embodiment 5 is the same as that of the perspective view of FIG. 1 of Embodiment 1, and the front view of FIG. 2, and description is abbreviate | omitted. FIG. 15 is a plan view showing the inside of the fin collar of the heat exchanger 10 according to the fifth embodiment of the present invention as viewed from the liquid direction. FIG. 16 is a perspective view showing the structure of the fin collar of the heat exchanger 10 according to the fifth embodiment of the present invention.

The heat exchanger 10 of the fifth embodiment is the same as the third and fourth embodiments in that there are a plurality of bent second fins at the tip of the collar portion 11. However, in the heat exchanger 10 of the fifth embodiment, the shapes of the

second fins

12a and 12b are different. The

second fins

12a and 12b according to the fifth embodiment are configured by

second fins

12a and 12b that are bent portions in which a part of the circumferential direction is bent in the liquid passing direction and a flat portion 12c that is orthogonal to the liquid passing direction. Is done. The flat portion 12c is formed in a fan-shaped shape that protrudes from a part in the circumferential direction at the tip of the collar portion 11 toward the center side of the tube cross section orthogonal to the liquid direction. The flat part 12c is bent so as to have a surface substantially orthogonal to the liquid flow direction. Further, the

second fins

12a and 12b, which are bent portions, are provided at both ends of the flat portion 12c. When viewed from the liquid passing direction, the second fin 12a that is the bent portion and the second fin 12b that is the bent portion are at opposite ends in the circumferential direction with respect to the flat portion 12c. The second fin 12a that is a bent portion is a portion that is bent toward the upstream side in the liquid passing direction. The second fin 12b, which is a bent portion, is a portion bent toward the downstream side in the liquid passing direction. 15 and 16, the second fin 12a, which is a bent portion, is located at the end in the clockwise direction with respect to the flat portion 12c when viewed from the upstream side in the liquid passing direction to the downstream side. The second fin 12b that is a bent portion is located at the end in the counterclockwise direction with respect to the flat portion 12c when viewed from the upstream side in the liquid passing direction to the downstream side. Note that the

second fins

12a and 12b, which are bent portions, may be arranged in reverse. Moreover, although the flat part 12c was fan-shaped, it may be formed in a shape such as a triangle, a trapezoid, or a rectangle.

The flat portion 12c and the

second fins

12a and 12b, which are bent portions at the ends thereof, together constitute one second fin body. 15 and 16 show a configuration in which two second fin bodies are located at different positions in the circumferential direction inside one fin collar. When viewed from the liquid passing direction, the inner periphery of the collar portion 11 includes a region where two second fin bodies are formed and a region where the second fin bodies are not formed between them. Exists. The 2nd fin 12a is the 1st shape bent so that the tip might approach one side of fin 1. FIG. The 2nd fin 12b is the 2nd shape bent so that the tip may go away from one side of fin 1. FIG. The second fins 12a having the first shape and the second fins 12b having the second shape are alternately arranged in the circumferential direction.

For manufacturing such a fin collar, for example, when the fin collar is formed on the fin 1, a slit is formed at the tip of the fin collar for the

second fins

12 a and 12 b that are bent portions and the flat portion 12 c. It can be manufactured by bending each part after that. The tapered surface of the base portion of the fin collar remains as the collar portion 11, and this portion is used for connection with the adjacent collar portion 11. Except for the structural part of the second fin body, the manufacturing process of the other parts and the operation of the heat exchanger are the same as those in the above embodiment, and thus the description thereof is omitted.

Also in the fifth embodiment, the flow of the water RF along the inner surface of the collar portion 11 changes as shown by the line with an arrow in FIG. Since the second fin body protrudes inside, the heat exchange performance is improved by the leading edge effect as in the above embodiment. Further, the second fin body has different height portions in the liquid passing direction in different circumferential directions in the collar portion 11. Thereby, the flow of the water RF generates an asymmetric flow in the circumferential direction, and as a result, a flow in the circumferential direction is generated. The water RF that flows toward the flat portion 12c with respect to the upstream end of the second fin 12a that is the bent portion collides with the flat portion 12c, and then is opposite to the second fin 12a that is the bent portion along the circumferential direction. And flows downstream from the second fin 12b, which is a bent portion. At this time, a flow that rotates through the liquid passing pipe 13 is generated, and an action of changing the flow also occurs with respect to the water RF that flows through the gap between the two second fin bodies. The heat exchange is promoted by changing the flow direction of the water RF.

Note that the ends of the

second fins

12a and 12b, which are the bent portions, are bent in opposite directions. However, the tips of the

second fins

12a and 12b that are the bent portions may be bent in the same direction. In that case, although the promotion effect by rotation of the flow of water RF cannot be obtained, the effect of improving the heat transfer performance by the leading edge effect is obtained. FIG. 17 is a cross-sectional view showing a modified example in which both ends of the flat portion 12c are second fins 12a which are bent portions bent toward the inlet header 2 side. Since the bent tip of the second fin 12a faces the upstream side of the flow, the leading edge effect is enhanced. In the fin collar connected to the outlet header 3 side, both ends of the flat portion 12c are bent to the opposite side of the outlet header 3, so that the bent tip of the second fin 12a faces the upstream side and the leading edge effect is enhanced. It is done. When the direction in which the water RF flows changes, the performance change due to the flow direction of the water RF may be smaller when the second fins with different bending directions are mixed as shown in FIG. That is, only the second fin 12a having the first shape that is bent so that the tip approaches one surface of the fin 1 may be provided. Further, as described later in the sixth embodiment, only the second fin 12b having the second shape whose tip is bent so as to be away from one surface of the fin 1 may be provided.

As the area of the

second fins

12a and 12b increases, the effect of improving heat transfer and reducing flow resistance due to the leading edge effect can be obtained. In Embodiments 3 and 4, since the second fin is divided in the circumferential direction (perpendicular to heat transfer), there is no influence that heat transfer is reduced by the division. However, since the

second fins

12a and 12b, which are the bent portions in the fifth embodiment, are divided in the radial direction (heat transfer direction) from the collar portion 11, there is a possibility that heat conduction loss will increase if it is made too large. There is. Therefore, for example, the area of the

second fins

12a and 12b, which are the bent portions, is preferably set to an appropriate size, such as smaller than the flat portion 12c.

<Embodiment 6>
FIG. 18 is a cross-sectional view showing a heat exchanger 10 according to Embodiment 6 of the present invention. FIG. 18 corresponds to a cross-sectional view of the first embodiment viewed from the BB direction in FIG. In addition, the whole structure of the heat exchanger 10 of this Embodiment 6 is the same as that of the perspective view of FIG. 1 of Embodiment 1, and the front view of FIG. 2, and description is abbreviate | omitted. FIG. 19 is a plan view showing the inside of the fin collar of the heat exchanger 10 according to the sixth embodiment of the present invention when viewed from the liquid direction.

The second fin 12 of the sixth embodiment has a shape in which the second fin 12a of the fourth embodiment is removed and only the second fin 12b is left. In other words, the second fin 12 is bent inside the collar portion 11 at a slight angle so as to form an obtuse angle with respect to the tapered surface of the collar portion 11, and is inclined in the same direction as the tapered surface of the collar portion 11. . A plurality of second fins 12 are provided at intervals in the circumferential direction. The manufacturing method and operation are the same as those in the third and fourth embodiments, and the description thereof is omitted.

In the sixth embodiment, no second fin is formed between the second fins 12 adjacent in the circumferential direction. For this reason, the improvement in heat exchange performance is slightly inferior to that of the fourth embodiment. However, the flow resistance can be further suppressed. The sixth embodiment is effective when the diameter of the liquid passage pipe 13 is reduced.

18 and 19 show that water flows from the inlet header 2. For this reason, the front-end | tip of the 2nd fin 12 has faced the downstream of the liquid flow direction. However, if it replaces with the outlet header 3 instead of the inlet header 2, the 2nd fin 12 will face the upstream of a liquid flow direction. In this case, the leading edge effect at the tip of the second fin 12 is increased, and the heat exchange performance is improved.

<Embodiment 7>
FIG. 20 is a cross-sectional view showing a heat exchanger 10 according to Embodiment 7 of the present invention. 20 corresponds to a cross-sectional view of the first embodiment viewed from the BB direction in FIG. In addition, the whole structure of the heat exchanger 10 of this Embodiment 7 is the same as that of the perspective view of FIG. 1 of Embodiment 1, and the front view of FIG. 2, and description is abbreviate | omitted. FIG. 21 is a plan view showing the inside of the fin collar of the heat exchanger 10 according to the seventh embodiment of the present invention as viewed from the liquid direction.

The second fin 12 of the seventh embodiment is inclined in the same direction as the tapered surface of the collar portion 11 and inside the collar portion 11 as in the sixth embodiment. A plurality of second fins 12 are provided at intervals in the circumferential direction. In the seventh embodiment, the positions of the second fins 12 in the circumferential direction are shifted between the two fins 1 connected to each other. In FIG. 21, when viewed from the liquid flow direction, the second fin 12 of the fin 1 on the upstream side in the front liquid flow direction indicated by the solid line is connected to the downstream side in the liquid flow direction immediately behind the second fin 12 indicated by the broken line. It is shown that the second fin 12 of the fin 1 is displaced in the circumferential direction of the center of the tube cross section perpendicular to the liquid passing direction of the collar portion 11. As viewed in the liquid flow direction, the space region between the adjacent second fins 12 of the fin 1 on the upstream side in the front liquid flow direction indicated by the solid line is connected to the downstream side in the liquid flow direction immediately behind that indicated by the broken line. There is one second fin 12 of the fin 1.

In the seventh embodiment, no second fin is formed between the second fins 12 adjacent in the circumferential direction. For this reason, flow resistance can be suppressed. Further, the fins 1 connected to each other have second fins 12 at different circumferential positions. Thereby, the water flowing in the vicinity of the inner surface of the collar portion 11 can easily come into contact with the second fin 12 of any one of the fins 1 and the heat exchange performance is improved.

In addition, when it sees from a liquid flow direction like FIG. 21, it arrange | positions so that the clearance gap between the 2nd fins 12 of the fin 1 connected may overlap in the circumferential direction. Thereby, a high leading edge effect is obtained. However, the second fins 12 of the fins 1 connected to each other may be slightly overlapped so that no gap can be seen in the circumferential direction when viewed from the liquid passing direction.

<Eighth embodiment>
FIG. 22 is a cross-sectional view showing a heat exchanger 10 according to Embodiment 8 of the present invention. 22 corresponds to a cross-sectional view of the first embodiment viewed from the BB direction in FIG. In addition, the whole structure of the heat exchanger 10 of this Embodiment 8 is the same as that of the perspective view of FIG. 1 of Embodiment 1, and the front view of FIG. 2, and description is abbreviate | omitted. FIG. 23 is a plan view showing the inside of the fin collar of the heat exchanger 10 according to the eighth embodiment of the present invention when viewed from the liquid direction.

In the second fin 12 of the eighth embodiment, the tip of the fin collar is formed in a concavo-convex shape such as a triangle shape. The second fin 12 is formed by bending the concavo-convex portion in the center direction of the tube cross section perpendicular to the airflow direction of the fin collar. The tapered tubular portion of the fin collar that is not bent remains as the collar portion 11. The cylindrical tip of the collar portion 11 is parallel to one surface of the fin 1 and has a smooth ring shape. At the height in the liquid passing direction from one surface of the fin 1, the bending positions of the uneven portions of the plurality of jagged portions are the same. For this reason, the airtightness by the connection of the collar portion 11 is improved. In other embodiments as well, the tip of the collar portion 11 is preferably formed in a smooth ring shape.

In the second fin 12 of the eighth embodiment, a large number of small uneven portions are formed at the tip of the collar portion 11 in the circumferential direction, for example, 12 or more as shown in FIGS. Further, the concave and convex shape of the second fin 12 is formed into a shape such as a triangle that becomes narrower toward the center side of the cross section of the tube orthogonal to the ventilation direction. For this reason, a high leading edge effect can be obtained and the heat exchange performance can be improved while the area where the second fin 12 blocks the liquid passage 13 is reduced.

<Embodiment 9>
FIG. 24 is a cross-sectional view showing a heat exchanger 10 according to Embodiment 9 of the present invention. 24 corresponds to a cross-sectional view of the first embodiment viewed from the BB direction in FIG. In addition, the whole structure of the heat exchanger 10 of this Embodiment 9 is the same as that of the perspective view of FIG. 1 of Embodiment 1, and the front view of FIG. 2, and description is abbreviate | omitted. FIG. 25 is a plan view showing the inside of the fin collar of the heat exchanger 10 according to the ninth embodiment of the present invention as seen from the liquid direction. FIG. 26 is a perspective view showing the structure of the fin collar of the heat exchanger 10 according to the ninth embodiment of the present invention.

The ninth embodiment is similar to the fifth embodiment, but the shape of the second fin 12 is different. The second fin 12 is formed with a rectangular plate portion or the like at the tip of the collar portion 11, bent toward the center of the tube cross section perpendicular to the ventilation direction of the collar portion 11, It is formed by bending one corner of the shaped plate piece portion so as to approach one surface of the fin 1 and bending the other corner of the plate piece portion toward the side away from one surface of the fin 1. Therefore, as in the fifth embodiment, the second fin 12 includes a flat portion 12c that protrudes from the tip of the collar portion 11 toward the center of the tube cross section perpendicular to the ventilation direction of the opening portion, and the collar portion 11. A second fin 12a that is a bent portion that is bent toward one end in the liquid passing direction at an end of the flat portion 12c on one side in the circumferential direction, and a second fin that is a bent portion at the opposite end of the flat portion 12c. And a second fin 12b that is a bent portion that is bent in the opposite direction to the fin 12a. The 2nd fin 12a is the 1st shape bent so that the tip might approach one side of fin 1. FIG. The 2nd fin 12b is the 2nd shape bent so that the tip may go away from one side of fin 1. FIG. The second fins 12a having the first shape and the second fins 12b having the second shape are alternately arranged in the circumferential direction. The second fin 12 corresponds to the second fin body of the fifth embodiment.

Note that the

second fins

12a and 12b, which are the bent portions, are not bent perpendicularly to the flat portion 12c as in the fifth embodiment, and are bent at a smaller angle than a right angle. For this reason, the

2nd fin

12a, 12b which is a bending part with respect to a liquid flow direction has a slope which inclines. In addition, the bending part between the

2nd fins

12a and 12b and the flat part 12c which are bending parts may be formed in a continuous curved surface. The

2nd fins

12a and 12b which are a bending part may be formed in a curved surface.

The

second fins

12a and 12b, which are bent portions, are formed by bending the corners of the plate pieces. The flat part 12c is formed in a triangular or trapezoidal shape with a thinner central side. For this reason, these inclined surfaces are directed to the inner center of the liquid passage 13. In addition, the shape used as the origin of the 2nd fin 12 demonstrated in the example made into the rectangular shape. However, the shape on which the second fin 12 is based may be another shape.

According to the ninth embodiment, since one of the

second fins

12a and 12b, which are the bent portions, has an end portion on the upstream side of the flow, the heat exchange performance is improved by the leading edge effect. Further, since the second fin 12a that is the bent portion is opposite in the liquid passing direction, the second fin 12a has an action of rotating the liquid and changes the flow of the liquid, so that the same effect as in the fifth embodiment can be obtained. . In particular, since at least one of the

second fins

12a and 12b, which are the bent portions, has its inclined surface inclined toward the inner center of the liquid pipe 13, the water RF flowing near the center of the liquid pipe 13 flows. It is guided near the inner wall of the collar portion 11. For this reason, heat exchange at the tube wall of the liquid flow tube 13 can also be promoted.

The flat portion 12c and the

second fins

12a and 12b which are bent portions at both ends thereof constitute one second fin 12 (second fin body). However, the second fin 12a that is the bent portion is formed at one end of the flat portion 12c and the second fin 12b that is the bent portion is not provided at the other end, or one end of the flat portion 12c is not provided. A similar effect can be obtained when the second fin 12b, which is a bent portion, is formed at the end on the side, and the second fin 12a, which is a bent portion, is not provided at the other end. That is, only the second fin 12a having the first shape that is bent so that the tip approaches one surface of the fin 1 may be provided. Further, only the second fin 12b having the second shape bent so that the tip is away from one surface of the fin 1 may be provided. A part of the flat portion 12c may be bent toward the liquid passing direction. When the bent surface of the second fin 12 is configured to face the circumferential direction, the projected area when viewed from the liquid passing direction is reduced, and a high heat exchange effect such as a leading edge effect is obtained. Road resistance can be reduced.

<Embodiment 10>
In each of the above embodiments, the resin film 14 formed on the second fin 12 may be thinner than the resin film 14 formed on the collar portion 11. Alternatively, at least part of the resin film 14 in the resin film 14 formed on the second fin 12 may not cover the second fin. The region where the resin film 14 of the second fin 12 is thin or not covered is not necessarily the entire surface of the second fin 12 and may be only a part.

FIG. 27 is an enlarged cross-sectional view showing the heat exchanger 10 according to Embodiment 10 of the present invention. FIG. 27 shows, as an example, a structure in which the thickness and adhesion of the resin film 14 are changed depending on the site in the structure of the seventh embodiment shown in FIG. Compared to the resin film 14 attached to the inner surface of the collar portion 11, the resin film 14 of the second fin 12 protruding toward the inner center of the liquid passage 13 is thin or has a structure in which a part of the resin film 14 is not attached. This example shows a structure in which the resin film 14 becomes thinner toward the tip of the second fin 12, that is, toward the inner center of the liquid passage 13, and there is no resin film 14 at the tip of the second fin 12. . Similar structures can be used for other embodiments.

As a method for changing the thickness of the resin film 14 as described above, for example, after the resin film 14 is formed inside the liquid passage tube 13, the resin film 14 of the second fin 12 is attached with a brush inserted into the liquid passage tube 13. There is a way to rub. A brush having a size smaller than the inner diameter of the collar portion 11 and capable of rubbing the second fin 12 may be used. Alternatively, a solvent that gradually dissolves the resin film 14 instead of the brush may be used so that the solvent flows vigorously in the central portion of the liquid passage 13.

When the resin film 14 adhering to the second fin 12 is thin or the resin film 14 is not adhering, the heat exchange performance between the second fin 12 and the fluid flowing through the liquid passage 13 is remarkably improved. In particular, when the second fin 12 has a structure in which the tip of the collar portion 11 is bent toward the inner center of the liquid passage tube 13, the collar portion 11 constituting the liquid passage tube 13 is protected even when the resin film 14 becomes thin. Therefore, heat exchange performance can be improved while maintaining reliability.

1 fin, 2 inlet header, 3 outlet header, 4 connection pipe, 10 heat exchanger, 11 collar part, 12 second fin, 12a second fin, 12b second fin, 12c flat part, 13 liquid pipe , 14 resin film, 43 cut and raised part, 44 cut part.

Claims

A plurality of plate-like fins having collar portions extending in a tapered shape from one surface are stacked, and the collar portions of fins adjacent to each other in the stacking direction are connected to form a liquid flow pipe, and the inner surface of the liquid flow pipe In a heat exchanger in which a resin film is formed,
A heat exchanger having second fins that are discontinuous in the circumferential direction of the collar portion inside the collar portion.
The heat exchanger according to claim 1, wherein the second fins are intermittently disposed in the circumferential direction.
The heat exchanger according to claim 1 or 2, wherein the collar portion has a region in which the second fin is formed in the circumferential direction and a region in which the second fin is not formed.
The heat exchanger according to any one of claims 1 to 3, wherein the second fins of the fins adjacent to each other in the overlapping direction are displaced in the direction when viewed from the overlapping direction.
A plurality of the second fins are arranged in the circumferential direction,
The heat exchanger according to any one of claims 1 to 4, wherein the second fins of the fins adjacent to each other in the overlapping direction are shifted by a half cycle in the circumferential direction when viewed from the overlapping direction.
6. The heat according to claim 1, wherein the second fin is a projection that is located in the middle of the collar portion in the overlapping direction, and a part of the collar portion protrudes inward. Exchanger.
The heat according to any one of claims 1 to 5, wherein the second fin is a portion that is continuous from the tip of the collar portion, and is a portion that is bent inward from the collar portion that forms the tubular shape. Exchanger.
The heat exchanger according to claim 7, wherein the second fin is a portion bent toward the one surface such that a tip approaches the one surface of the fin.
The heat exchanger according to claim 7, wherein the second fin is a portion bent to the opposite side to the one surface side so that a tip thereof is away from the one surface of the fin.
The second fin has a first shape whose tip is bent so as to approach the one surface of the fin, and a second shape whose tip is bent so as to move away from the one surface of the fin. The heat exchanger according to claim 7, wherein
The heat exchanger according to claim 10, wherein the first shape and the second shape are alternately arranged in the circumferential direction.
The second fin has a first shape bent at an acute angle with respect to the collar portion so that the tip approaches the one surface of the fin, and the tip has the one surface of the fin. There is a second shape bent so as to form an obtuse angle with respect to the collar portion so as to be away from the collar portion, and the first shape and the second shape are adjacent in the circumferential direction. Item 8. The heat exchanger according to Item 7.
The heat exchanger according to claim 7, wherein the second fin includes a flat portion bent inward and a bent portion bent from the flat portion toward the overlapping direction.
The heat exchanger according to claim 13, wherein the flat portion has bent portions at both ends in the circumferential direction.
The heat exchanger according to claim 14, wherein two bent portions at both ends in the circumferential direction of the flat portion are bent in the same direction with respect to the overlapping direction.
The heat exchanger according to claim 14, wherein two bent portions at both ends in the circumferential direction of the flat portion are bent in a direction opposite to the overlapping direction.
In at least a partial region of the second fin, the thickness of the resin film formed on the second fin is smaller than the thickness of the resin film formed on the inner surface of the collar portion, or The heat exchanger according to any one of claims 1 to 16, wherein the resin film is not covered.