JP2018100795A - Heat exchanger and air conditioner - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a heat exchanger which increases a surface area of an inner wall of a passage in which a refrigerant flows to improve heat exchange performance.SOLUTION: A heat exchanger includes: fins 11 having metal plates each provided with a hole part 41 through which a refrigerant RF flows; fins 12, each of which is stacked on the fin 11 so as to separate from the fin 11 and has a metal plate provided with a hole part 42 through which the refrigerant RF flows and formed at a position different from the hole part 41 when viewed in a direction of stacking on the fin 11; and spacers 20, each of which is provided between the fin 11 and the fin 12 while enclosing the hole part 41 and the hole part 42. An inner wall of each passage 51 formed by the fin 11, the fin 12, and the spacer 20 and in which the refrigerant RF flows along a surface of the fin 11 is provided facing the hole part 41.SELECTED DRAWING: Figure 2

Description

  The present invention relates to a heat exchanger and an air conditioner using the heat exchanger.

  A heat exchanger is a device that exchanges heat between a refrigerant such as hydrofluorocarbon or water and a fluid such as air or water, and is a refrigeration cycle device such as an air conditioner or a refrigeration device, or a radiator of various cooling devices. Widely used in

  The conventional heat exchanger is composed of a plurality of fin members having a plurality of holes and a plurality of spacer members having holes, and the fin members and the spacers are aligned so that the holes of the fin members and the holes of the spacer members are matched. It was configured by alternately laminating members. The first flow path through which the refrigerant flows in the vertical direction is formed by the hole of the fin member and the hole of the spacer member, and the fluid flows in the horizontal direction between the adjacent fin members and between the adjacent spacer members. Two flow paths are formed, and heat exchange is performed between the refrigerant flowing in the first flow path and the fluid flowing in the second flow path (see, for example, Patent Document 1).

JP 58-006394 A

  However, in the conventional heat exchanger described in Patent Document 1, the surface area of the inner wall of the first flow path constituted by the holes provided in the fin member and the holes provided in the spacer member is small, and the first Since the contact area between the inner wall of the first flow path and the refrigerant flowing through the first flow path is small, heat transfer between the inner wall of the first flow path and the refrigerant is small, and the refrigerant flowing through the first flow path There was a problem that the heat exchange performance with the fluid flowing in the two flow paths was insufficient.

  The present invention has been made to solve the above-described problems, and an object of the present invention is to provide a heat exchanger that can increase the heat exchange performance by increasing the surface area of the inner wall of the flow path through which the refrigerant flows.

  The heat exchanger according to the present invention includes a first fin having a metal plate provided with a first hole through which a refrigerant flows, and a first fin that is stacked separately from the first fin. A second fin having a metal plate provided with a second hole through which a coolant flows at a position different from the first hole when viewed from the direction, and the first hole and the second hole are surrounded. And a spacer provided between the first fin and the second fin, the first fin, the second fin, and the spacer, and the refrigerant is disposed along the surface of the first fin. An inner wall of the flowing channel is provided to face the second hole.

  According to the heat exchanger according to the present invention, since the refrigerant in the flow path flows along the surface of the fin, the heat exchange performance can be improved by increasing the surface area of the inner wall of the flow path through which the refrigerant flows.

It is a perspective view which shows the heat exchanger in Embodiment 1 of this invention. It is a fragmentary sectional perspective view which shows a partial structure of the heat exchanger in Embodiment 1 of this invention. It is a fragmentary sectional view which shows a partial structure of the heat exchanger in Embodiment 1 of this invention. It is a disassembled perspective view which shows a partial structure of the heat exchanger in Embodiment 1 of this invention. It is a fragmentary sectional perspective view which shows a partial structure of the heat exchanger in Embodiment 2 of this invention. It is a fragmentary sectional view which shows a partial structure of the heat exchanger in Embodiment 2 of this invention. It is a disassembled perspective view which shows a partial structure of the heat exchanger in Embodiment 2 of this invention. It is a fragmentary sectional view which shows a partial structure of the other heat exchanger in Embodiment 2 of this invention. It is a sectional side view which shows the partial structure of the heat exchanger in Embodiment 3 of this invention. It is a disassembled perspective view which shows a partial structure of the heat exchanger in Embodiment 3 of this invention. It is a fragmentary sectional view which shows a partial structure of the heat exchanger in Embodiment 4 of this invention. It is a perspective view which shows the shape of the spacer of the heat exchanger in Embodiment 4 of this invention. It is a figure which shows the shape of the spacer of the heat exchanger in Embodiment 4 of this invention. It is a schematic block diagram which shows the structure of the air conditioning apparatus in Embodiment 5 of this invention.

Embodiment 1 FIG.
First, the structure of the heat exchanger in Embodiment 1 of this invention is demonstrated. FIG. 1 is a perspective view showing a heat exchanger according to Embodiment 1 of the present invention. In FIG. 1, XYZ orthogonal coordinate axes are shown together.

  In Embodiment 1 of the present invention, the refrigerant flowing in the flow path in the heat exchanger is water, and the fluid flowing in the flow path outside the heat exchanger is air, and heat is generated between water and air. Although the heat exchanger for exchanging will be described, the refrigerant is not limited to water but may be other liquid refrigerants or gas refrigerants such as hydrofluorocarbons, and the fluid for exchanging heat with the refrigerant is not limited to air but may be water or the like. It may be a fluid composed of a gas or a liquid.

  In FIG. 1, a heat exchanger 100 includes a plurality of fins 11, 12, 13, and 14 made of a metal plate made of a metal having a high thermal conductivity such as aluminum in the X direction via an annular spacer 20. It is configured by stacking. As shown in FIG. 1, the plurality of stacked fins includes fins 13 and 14 located at both ends in the stacking direction, and a plurality of fins 11 and a plurality of fins 12 sandwiched between the fins 13 and 14. Become. The thickness of the fins 11, 12, 13, 14 is, for example, 0.05 mm to 2 mm. The fins 11 and the fins 12 are alternately stacked via annular spacers 20.

  A plurality of spacers 20 are provided apart from each other in the direction perpendicular to the stacking direction of the fins, that is, in the Z direction. Hereinafter, a configuration in which a plurality of spacers 20 are stacked in the X direction via fins is referred to as a step. The heat exchanger 100 is configured by providing a plurality of stages in the Z direction. Since the heat exchanger 100 of FIG. 1 includes five stages, the number of stages is five and may be referred to as five stages. The number of stages of the heat exchanger 100 may be any number, and may be several tens or more.

  A space corresponding to the height of the spacer 20 is provided between the fins of the plurality of fins 11, 12, 13, and 14, and the plurality of spacers 20 are also perpendicular to the stacking direction of the fins, that is, stepped. An interval is provided between the steps. Accordingly, a region between the fins and outside the spacer 20 between the steps is a flow path 50 through which a fluid such as air flows. The flow path 50 is a flow path provided outside the heat exchanger 100, and the fins 11, 12, 13, and 14 each constitute a wall surface of the flow path 50 through which fluid flows. The height of the spacer 20 may be about several mm, for example, 1 mm to 2 mm is preferable. Moreover, the space | interval between the step | levels of the spacer 20 may be several mm-several tens mm, for example, may be 10 mm-30 mm. Accordingly, as shown in FIG. 1, the fluid WF flowing in the direction perpendicular to each of the stacking direction of the fins of the heat exchanger 100 and the separation direction of the plurality of spacers 20, that is, the Y direction, is Passes through the flow path 50 to the outflow surface side on the back side.

  As shown in FIG. 1, one end side of the liquid passing pipe 33 is connected to the fin 13 at one end in the stacking direction of the plurality of stacked fins at a position including the position where the spacer 20 is provided when viewed from the X direction. A plurality of liquid flow pipes 33 are provided apart from each other in the Z direction. An inlet header 31 is connected to the other end side opposite to the side connected to the fins 13 of the plurality of liquid passing pipes 33. Similarly, one end side of the liquid flow pipe 34 is connected to the fin 14 at the other end in the stacking direction of the plurality of stacked fins at a position including the position where the spacer 20 is provided when viewed from the X direction. Liquid pipes 34 are provided apart from each other in the Z direction. An outlet header 32 is connected to the other end side opposite to the side connected to the fins 14 of the plurality of liquid passing pipes 34.

  The inlet header 31 and the outlet header 32 are formed of a metal tube or a resin tube. Similarly, the liquid passage tube 33 and the liquid passage tube 34 are also formed of a metal tube or a resin tube. The connection between the inlet header 31 and the liquid flow pipe 33, the connection between the liquid flow pipe 33 and the fin 13, the connection between the outlet header 32 and the liquid flow pipe 34, and the connection between the liquid flow pipe 34 and the fin 14 are welding, It is performed by brazing or bonding with an adhesive, etc., and is sealed in a liquid-tight manner so that the refrigerant RF flowing through the inside of the inlet header 31, the outlet header 32, and the liquid flow pipes 33 and 34 does not leak to the outside. .

  Note that, among the plurality of stacked fins, the fins 13 and 14 at both ends in the stacking direction are connected to the liquid passing pipes 33 and 34, so that they are stronger than the fins 11 and 12 inside the fins 13 and 14. In order to increase the thickness, it may be formed of a metal plate thicker than the fins 11 and 12, or may be formed of a metal different from the fins 11 and 12, such as iron subjected to rust prevention treatment.

  In FIG. 1, the refrigerant FR is shown to flow into the heat exchanger 100 from the inlet header 31, and to flow out of the heat exchanger 100 from the outlet header 32. The direction in which RF flows may be reversed. For example, when the heat exchanger 100 is used in an air conditioner capable of air conditioning operation, the refrigerant RF flows in from the inlet header 31 and flows out from the outlet header 32 as shown in FIG. Contrary to FIG. 1, the refrigerant RF may flow from the outlet header 32 and flow out from the inlet header 31. Note that the refrigerant RF flows into the heat exchanger 100 from the inlet header 31 and flows out of the heat exchanger 100 from the outlet header 32 without switching the direction in which the refrigerant RF flows in both the cooling operation and the heating operation. Also good.

  The configuration of the heat exchanger 100 will be described in more detail.

  FIG. 2 is a partial cross-sectional perspective view showing a partial configuration of the heat exchanger according to Embodiment 1 of the present invention. 2 is a cross-sectional view taken along the line AA indicated by a broken line in FIG. FIG. 3 is a partial cross-sectional view showing a partial configuration of the heat exchanger according to Embodiment 1 of the present invention. FIG. 3 is a cross-sectional view of the cross section indicated by the broken line AA in FIG. 2 as viewed from the Z direction, which is the normal direction of the cross section. Furthermore, FIG. 4 is an exploded perspective view showing a partial configuration of the heat exchanger according to Embodiment 1 of the present invention. 2 to 4 show a one-stage configuration, and the heat exchanger 100 is configured by providing a plurality of stages in FIGS. 2 to 4 in the Z direction.

  As shown in FIGS. 2 to 4, the hole 11 is provided in the fin 11 and the fin 13, and the hole 42 is provided in the fin 12 and the fin 14. Since the fins 11, 12, 13, and 14 are formed of a metal plate such as aluminum, the region excluding the hole 41 of the fins 11 and 13 is a metal plate, and the holes 42 of the fins 12 and 14 are formed. The excluded area is a metal plate part. That is, the fins 11 and 13 are composed of the hole portion 41 and the metal plate portion, and the fins 12 and 14 are composed of the hole portion 42 and the metal plate portion.

  The hole 41 and the hole 42 are provided at different positions when viewed from the fin stacking direction. More specifically, the hole 41 and the hole 42 are different in the position in the Y direction, which is the direction in which the fluid WF flows, and the position in the Z direction perpendicular to the direction in which the fluid WF flows is the same. . That is, the straight line connecting the center of the hole 41 and the center of the hole 42 is parallel to the direction in which the fluid WF flows through the flow path 50 outside the heat exchanger 100, and the hole 41 is downstream of the fluid WF. Further, the hole 42 is located on the upstream side of the fluid WF. Further, the hole 41 faces the metal plate portion of the fin 12 or the fin 14, the metal plate portion of the fin 12 or the fin 14 covers the hole portion 41, and the hole 42 is the metal plate portion of the fin 11 or the fin 13. The metal plate portion of the fin 11 or the fin 13 covers the hole portion 42.

  2 and 4, the hole 41 and the hole 42 have a rectangular shape, but may be any shape such as a circle, an ellipse, or a polygon as long as the refrigerant RF can pass therethrough. When the holes 41 and 42 are circular or elliptical, the diameter or major axis is long. When the holes 41 and 42 are polygonal, the longest diagonal is about 0.5 mm to 10 mm, for example, 1 mm to 2 mm. It may be. Moreover, the collar part which made the metal plate part upright at an angle with respect to the surface of the fin 11, 12, 13, 14 may be provided in the edge of the hole parts 41 and 42. FIG. 2 and 3, the liquid passage pipes 33 and 34 shown in FIG. 1 are omitted, but the liquid passage pipe 33 is connected to the fin 13 by connecting the liquid passage pipe 33 to the hole 41 provided in the fin 13. The liquid passage pipe 34 is connected to the fin 14 by connecting the liquid passage pipe 34 to the hole 42 provided in the fin 14.

  The spacer 20 surrounds the hole 41 provided in the fin 11 or the fin 13 and the hole 42 provided in the fin 12 or the fin 14, and between the fin 11 and the fin 12, and between the fin 12 and the fin 13. And between the fin 11 and the fin 14, and are liquid-tightly joined to each fin. The plurality of fins 11 and 12 are alternately stacked via the spacer 20 with the positions of the hole portions 41 of the fins aligned and the positions of the hole portions 42 of the fins aligned when viewed from the stacking direction of the fins. ing. The spacer 20 is formed in a cylindrical shape having an annular side wall with a thickness of about several mm, for example, 1 mm to 2 mm. With this configuration, the region surrounded by the fins 11, the fins 12 and the spacers 20, the region surrounded by the fins 12, the fins 13 and the spacers 20, and the region surrounded by the fins 11, the fins 14 and the spacers 20 are formed. A flow path 51 through which the refrigerant RF flows is provided. The distance between the fin 11 and the fin 12, the distance between the fin 12 and the fin 13, and the distance between the fin 11 and the fin 14 are the height of the cylindrical spacer 20.

  Each of the fins 11, 12, 13, and 14 constitutes a wall surface of the flow path 51, and the spacer 20 also constitutes a wall surface of the flow path 51. Further, a wall surface of the flow path 51 including the fin 12 or the fin 14 is provided at a position facing the hole 41 provided in the fins 11 and 13, and faces the hole 42 provided in the fins 12 and 14. The wall surface of the flow path 51 including the fin 11 or the fin 13 is provided at the position. Therefore, the direction in which the refrigerant RF that has flowed into the flow channel 51 from the hole 41 or 42 is changed by the wall surface of the flow channel 51 facing the hole 41 or the hole 42 is changed along the surface of each fin. It flows through the channel 51.

  The spacer 20 has openings on the upper surface side and the bottom surface side of the cylindrical shape, and the size of the opening portion is a size including the entire hole portion 41 and the entire hole portion 42. Therefore, for example, when the holes 41 and 42 are circular with a diameter of 2 mm and the holes 41 and 42 are separated by 20 mm in the Y direction in which the fluid WF flows, the width of the opening of the spacer 20 in the Z direction. May be 2 mm or more, and the width in the Y direction of the opening of the spacer 20 may be 20 mm or more. If the opening of the spacer 20 is made larger than necessary, the pressure loss with respect to the flow of the fluid WF increases, so the size of the opening of the spacer 20 should be a size that completely includes the hole 41 and the hole 42. Smaller is preferable.

  As shown in FIG. 3, the flow path 51 is provided so as to communicate from the hole 41 of the fin 13 that is one end of the plurality of stacked fins to the hole 42 of the fin 14 that is the other end of the plurality of stacked fins. It is done. Since the positions of the hole 41 and the hole 42 are different in the Y direction in which the fluid WF flows, the flow path 51 is a flow path meandering in parallel with the direction in which the fluid WF flows. As a result, compared to the case where the flow path from the fin 13 side to the fin 14 side has a linear structure, the flow path 51 meanders, so the total extension of the flow path 51 becomes longer, and the inner wall of the flow path 51 The surface area can be increased. Therefore, since the heat transfer area to the refrigerant RF flowing through the flow path 51 on the inner wall of the flow path 51 can be increased, the heat transfer coefficient between the inner wall of the flow path 51 and the refrigerant RF is increased, and the heat of the heat exchanger 100 is increased. Exchange performance can be improved. The refrigerant RF flowing into the hole 41 of the fin 13 from the inlet header 31 through the liquid passage pipe 33 flows through the flow path 51 surrounded by the plurality of fins and the plurality of spacers 20, and the hole of the fin 14. It flows out of 42 and flows out of the heat exchanger 100 through the liquid passing pipe 34 and the outlet header 32.

  The spacer 20 is made of metal or resin. When the spacer 20 is formed of a metal, the spacer 20 may be formed of, for example, aluminum or brass. When the spacer 20 is made of metal, it is liquid-tightly bonded to a fin made of a metal plate by brazing, diffusion bonding, or adhesion using an adhesive, and the opening of the spacer 20 is sealed. In this case, a surface treatment such as plating may be performed to facilitate brazing or diffusion bonding on the surface of the aluminum fin. Moreover, it is preferable that the corrosion resistance film | membrane with high corrosion resistance with respect to water is provided in the surface of the metal spacer 20, especially the inner wall of the spacer 20 which the water which is a refrigerant | coolant contacts. The corrosion resistant film may be a resin film, an oxide film, a nitride film, or a carbide film. These corrosion-resistant films may also be provided when the refrigerant is a liquid other than water, such as ethylene glycol.

  Further, instead of the corrosion-resistant film, a metal film such as a metal plating film having a higher ionization tendency than the metal constituting the metal spacer 20 may be provided. For example, when the spacer 20 is formed of aluminum, a galvanized film may be formed as a metal film at a portion where water as a coolant contacts. By providing a metal film having a large ionization tendency, even if corrosion occurs on the surface of the spacer 20, the corrosion proceeds in the surface direction, and the corrosion is prevented from proceeding in the plate thickness direction, thereby improving the corrosion resistance reliability. it can.

  When the spacer 20 is formed of a resin, the spacer 20 may be formed of, for example, an olefin resin such as polyethylene or polypropylene, a fluororesin, an acrylic resin, an epoxy resin, or silicone. The spacer 20 may be bonded to the fin with an adhesive such as an epoxy adhesive. Further, when the spacer 20 is made of resin, the resin spacer 20 is melted by heat treatment at 100 ° C. to 300 ° C. after the resin spacer 20 is sandwiched between fins, and then the resin spacer 20 is solidified by cooling. Then, the spacer 20 and the fin may be joined. Furthermore, after applying between the fins using a synthetic resin adhesive such as a thermosetting epoxy resin or a room temperature curable epoxy resin or a silicone adhesive, the adhesive is cured to form the spacer 20. Good.

  The heat exchanger 100 is configured as described above.

  In FIG. 1, the heat exchanger 100 includes a fin 13 provided at one end in the stacking direction of a plurality of stacked fins and a liquid passage pipe 33 communicating with the inlet header 31 connected to the fin 13. Although the configuration in which the liquid passing pipe 34 communicating with the outlet header 32 is connected to the fin 14 provided at the other end in the stacking direction is shown, both the inlet header 31 and the outlet header 32 are connected to the fin 13 side. Also good. In this case, for example, the odd number stages of the heat exchanger are configured as shown in FIGS. 2 to 4. In the even number stages, the fins 11 and 13 have the same position in the Y direction as the holes 42. The fins 12 and 14 are provided with holes in the same position as the hole 41 in the Y direction. Then, a liquid passage pipe 34 communicating with the outlet header 32 is provided in communication with a hole provided in an even number of stages of the fin 13, that is, a hole having a position in the Y direction at the same position as the hole 42. The odd-numbered holes 42 may be connected to the even-numbered holes of the fins 14, that is, the holes provided in the same position as the holes 41 in the Y direction with a U-shaped tube.

  Next, a method for manufacturing the heat exchanger 100 will be described.

  First, the holes 11 or 42 are formed in a metal plate having a predetermined width (length in the Y direction) and height (length in the Z direction) to form the fins 11 and fins 12. For example, an aluminum plate having a thickness of 0.1 mm to 0.2 mm may be used as the metal plate, and the hole 41 or the hole 42 may be formed while being cut into a predetermined size by pressing. A plurality of holes 41 having the same position in the width direction are formed in the fin 11 at predetermined intervals in the height direction, and only the holes 42 having the same position in the width direction are formed in the fin 12 with a height. A plurality may be formed at predetermined intervals in the direction. Moreover, you may form alternately the hole part 41 and the hole part 42 from which the position of the hole part 41 differs in the Y direction in the fin 11 and the fin 12 in a height direction.

  When the fins 11 and 12 are formed by pressing, the metal plate portions of the fins 11 and 12 that are in contact with the fluid WF or the refrigerant RF are provided with uneven shapes or louvers, and the fluid WF or the refrigerant RF and the fins 11 and 12 You may process so that the heat transfer between may improve.

  Next, the fins 11 and the fins 12 are alternately stacked via the spacers 20. Here, the case where the spacer 20 is formed of resin will be described. However, when the spacer 20 is formed of metal, the fins 11 and 12 are bonded to the spacer 20 by brazing, diffusion bonding, or adhesion as described above. do it.

  A cylindrical spacer 20 having openings at both ends is formed of a heat-welding resin, for example, an olefin resin. A plurality of spacers 20 are arranged between the fins 11 and 12 according to the number of the holes 41 and 42, and the holes 41 and 42 provided in the fins 11 and 12 are opened to the openings of the spacers 20. The hole 41 and the hole 42 are surrounded by the spacer 20 so as to face each other. When a plurality of the fins 11 and the fins 12 are alternately stacked, the spacer 20 is disposed between the fins 11 and the fins 12.

  Next, the spacers 20 are similarly disposed so as to surround the hole 41 or 42 at both ends of the fins 11 and 12 laminated via the spacers 20, and the fins 13 and 14 constituting the fins at both ends are arranged. Place.

  And what laminated | stacked the fins 11, 12, 13, and 14 via the spacer 20 is heated at 100 to 300 degreeC, and the spacer 20 formed with the heat welding resin is fuse | melted. As a result, the melted spacer 20 gets wet with the fins 11, 12, 13, and 14, so that the heat-welding resin is solidified by cooling and the spacer 20 and the fins 11, 12, 13, and 14 are firmly bonded. The

  As described above, after all the fins 11, 12, 13, and 14 are stacked and disposed via the spacers 20 before bonding, the spacers 20 may not be heated and melted to be bonded at the same time. For example, the fin 11 and the spacer 20 previously bonded by thermal welding and the fin 12 and the spacer 20 previously bonded by thermal welding are alternately stacked and then heated again and thermally welded. May be adhered.

  Next, the liquid passing pipes 33, 34 are connected to the fins 13, 14 located at both ends of the plurality of fins bonded with a predetermined interval by the spacer 20, and the inlet header 31, the liquid passing pipe is connected to the liquid passing pipe 33. An outlet header 32 is connected to 34. In addition, when the liquid flow pipes 33 and 34 and the inlet header 31 and the outlet header 32 are made of metal, the liquid flow pipes 33 and 34 and the inlet header 31 and the outlet header 32 are brazed to the fins 13 and 14 in advance. Then, the fins 13 and 14 may be bonded to the fins 11 and 12 through the spacer 20.

  The heat exchanger 100 can be manufactured by the above process. In addition, the manufacturing method of the heat exchanger 100 is not restricted to the said method. For example, the spacer 20 may be formed using a curable adhesive as described above, and in that case, a curable adhesive is applied to a position where the spacer formed of the above-described heat-welding resin is disposed. Then, the heat exchanger 100 may be manufactured by laminating the fins 11, 12, 13, and 14, and then curing the curable adhesive by heat treatment or the like.

  Next, the operation and effect of the heat exchanger 100 will be described.

  The heat exchanger 100 can be used in various systems in which the heat exchanger is used, and its use is not limited. Here, the refrigerant RF flowing in the flow path 51 in the heat exchanger 100 is water. The case where the fluid WF flowing in the flow path 50 outside the heat exchanger 100 is used in an air conditioner that is air will be described.

  The air conditioner including the heat exchanger 100 includes a fan on the upstream side or the downstream side of the air flow, and the fluid WF that passes through the flow path 50 provided outside the spacer 20 of the heat exchanger 100 by the fan. A flow of air is formed. The air conditioner also includes a circulation pump connected to the inlet header 31 or the outlet header 32 of the heat exchanger 100, and the refrigerant RF flows through the flow path 51 in the heat exchanger 100 by the circulation pump. A water stream is formed.

  When the air conditioner performs the heating operation, the refrigerant RF flowing in the flow path 51 in the heat exchanger 100 is hot water, and the air flowing in the flow path 50 outside the heat exchanger 100 is heated by the heat of the hot water. Is done. On the other hand, when the air conditioner performs a cooling operation, the refrigerant RF flowing in the flow path 51 in the heat exchanger 100 is cold water, and the heat of the air flowing in the flow path 50 outside the heat exchanger 100 is cold water. The heat is absorbed and air is cooled. In the air conditioner described here, the airflow direction WF and the waterflow direction RF are the same in the heating operation and the cooling operation, as shown in FIGS.

  As shown in FIG. 3, the water that is the refrigerant RF flowing into the heat exchanger 100 from the inlet header 31 is surrounded by the fins 13, the fins 12, and the spacers 20 from the holes 41 provided in the fins 13. It flows into the flow path 51 and flows toward the hole 42 provided in the fin 12 along the surfaces of the fin 13 and the fin 12. Then, the water that is the refrigerant RF that has passed through the hole 42 provided in the fin 12 passes through the flow path 51 surrounded by the fin 12, the fin 11, and the spacer 20 along the surfaces of the fin 12 and the fin 11. 11 flows toward the hole 41 provided in 11. By repeating this, water, which is the refrigerant RF, passes through the flow path 51 from the hole 41 of the fin 13 to the hole 42 of the fin 14 as indicated by the arrow RF in FIG. It flows while meandering along the surface of 13,14.

  Since water as the refrigerant RF flows along the surface of the fins 11, 12, 13, and 14 in the flow path 51, the surface of the fins 11, 12, 13, and 14 in the flow path 51 and the water as the refrigerant RF The contact area, that is, the heat transfer area can be increased, and heat transfer between the surfaces of the fins 11, 12, 13, and 14 in the flow channel 51 and the water that is the refrigerant RF can be improved. That is, since the surface area of the inner wall of the flow path 51 in contact with the refrigerant RF can be increased, heat transfer between the inner wall of the flow path 51 and the water that is the refrigerant RF can be improved.

  Further, the air as the fluid WF is a flow path provided between the fin 11 and the fin 12, between the fin 13 and the fin 12, and between the fin 14 and the fin 11, and outside the spacer 20. Therefore, heat transfer is performed between each fin and the air that is the fluid WF. That is, in the heating operation, heat transfer is performed from the high-temperature fins to the low-temperature air, and in the cooling operation, heat transfer is performed from the high-temperature air to the low-temperature fins.

  The flow path 51 through which water as the coolant RF flows and the flow path 50 through which air as the fluid WF flow are adjacent to each other between the two fins sandwiching the spacer 20 through the sidewall of the spacer 20 having a thickness of several millimeters. Is provided. Since the fins 11, 12, 13, and 14 are formed of a metal having high thermal conductivity, the portion of the surface of the fins 11, 12, 13, and 14 that is in contact with the refrigerant RF in the channel 51 and the channel 50 The thermal resistance between the portion in contact with the fluid WF can be made very small, and the heat conduction between the portion located in the flow channel 51 and the portion located in the flow channel 50 can be made sufficiently high. it can. As a result, both heat transfer and heat conduction in the heat transfer path between the flow path 51 through which the refrigerant RF flows and the flow path 50 through which the fluid WF flow can be increased, so that heat between the refrigerant RF and the fluid WF can be increased. The heat exchanger 100 with high exchange performance can be obtained.

  In addition, heat transfer between the refrigerant RF flowing through the flow path 51 and the fluid WF flowing through the flow path 50 can be performed by a path that conducts heat only through the fins without passing through the spacer 20, so that the spacer 20 is heated. Even if the conductivity is made of a resin smaller than a metal, the heat exchange performance between the refrigerant RF and the fluid WF can be improved. In addition, when the spacer 20 is formed of metal, the thermal conductivity of the spacer 20 can be increased, so that the heat transfer path between the flow path 51 and the flow path 50 is made of metal having excellent heat conduction. Therefore, the heat exchange performance between the refrigerant RF and the fluid WF can be further enhanced. Further, even when the spacer 20 is formed of a thermally conductive resin containing metal particles or the like, the heat exchange performance between the refrigerant RF and the fluid WF is further enhanced, as in the case where the spacer 20 is formed of metal. be able to.

  In addition, since the fin 11 provided with the hole 41 and the fin 12 provided with the hole 42 sandwich the spacer 20, a flow channel 51 through which the refrigerant RF flows is formed. It can be easily reduced. For example, the width of the flow path 51 can be reduced to about 2 mm, which is equivalent to the fin interval, and the ratio of the heat transfer area per volume of the refrigerant RF passing through the flow path 51 is increased to increase the heat exchange performance. The exchanger 100 can be obtained. In addition, since the refrigerant RF flows through the flow path 51 in the direction along the surfaces of the fins 11 and 12, the refrigerant flowing through the flow path 51 even if the width of the flow path 51 is reduced to about 2 mm, which is equal to the fin interval. High heat transfer between the refrigerant RF and the inner wall of the flow path 51 can be maintained without reducing the flow rate of the RF.

  Since the flow path 51 is configured such that water as the refrigerant RF flows along the surface of the fin, the number of places where water tends to stay on the fin surface in the flow path 51 can be reduced, and the water circulates. The formation of an oxygen concentration battery due to a difference in dissolved oxygen concentration between a region where water is likely to stay and a region where water is likely to stay can be suppressed to improve the corrosion resistance reliability of the fins against water, and the reliability of the heat exchanger 100 Can be increased.

  Furthermore, when the spacer 20 is formed of resin, the material cost and manufacturing cost of the spacer 20 can be kept low, so that the heat exchanger 100 can be manufactured at low cost. Further, by forming the spacer 20 with resin, even if the coolant RF is water, the corrosion resistance reliability of the spacer 20 can be improved and the reliability of the heat exchanger 100 can be improved.

  As described above, according to the heat exchanger 100 of the first embodiment of the present invention, the fins 11 and 13 provided with the hole 41 through which the refrigerant RF flows are stacked and spaced apart from the fins 11 and 13. The fins 12 and 14 are provided with holes 42 through which the refrigerant RF flows at positions different from the holes 41 when viewed from the stacking direction with the holes 11 and 13, and the fins 11 or fins surround the holes 41 and 42. 13 and the spacer 20 provided between the fin 12 or the fin 14, and the flow path 51 through which the refrigerant RF flows along the fin is provided in the region surrounded by the two fins and the spacer 20. It is possible to increase the heat exchange performance by increasing the surface area of the inner wall of the channel 51.

  Moreover, since the inner wall of the flow path 51 is the surface of the fin, even if the fin in the flow path 51 is corroded by a coolant such as water, a sufficiently large heat transfer area can be ensured for a longer time, and the heat exchange performance can be improved. Can be kept high for a long time. Furthermore, since the flow path direction of the flow path 51 is provided along the surface of the fin, even if the flow path width orthogonal to the flow path direction of the flow path 51 is supplemented to about 1 to 2 mm, the flow rate is sufficiently high. Since the refrigerant RF can flow, the ratio of the heat transfer area in the flow path 51 to the refrigerant volume can be increased to further increase the heat transfer between the inner wall of the flow path 51 and the refrigerant RF.

Embodiment 2. FIG.
FIG. 5 is a partial cross-sectional perspective view showing a partial configuration of the heat exchanger according to Embodiment 2 of the present invention. The heat exchanger 200 according to the second embodiment of the present invention has the same appearance as the heat exchanger according to the first embodiment shown in FIG. 1, but the configuration of the flow path 51 inside the spacer 20 is different. ing. FIG. 5 is a cross-sectional view taken along the line AA indicated by a broken line in FIG. FIG. 6 is a partial cross-sectional view showing a partial configuration of the heat exchanger according to Embodiment 2 of the present invention. FIG. 6 is a cross-sectional view of the cross section indicated by the broken line AA in FIG. 5 as viewed from the Z direction, which is the normal direction of this cross section. Furthermore, FIG. 7 is an exploded perspective view showing a partial configuration of the heat exchanger according to Embodiment 2 of the present invention.

  5 to 7 correspond to FIGS. 2 to 4 of the first embodiment. 5 to 7 illustrate a one-stage configuration, as in FIGS. 2 to 4, and the heat exchanger 200 is configured by providing the plurality of configurations in FIGS. 5 to 7 in the Z direction. 5-7, what attached | subjected the same code | symbol as FIGS. 2-4 has shown the structure which is the same or respond | corresponds, The description is abbreviate | omitted.

  As shown in FIGS. 5 to 7, the heat exchanger 200 is viewed from the fin stacking direction between the fin 13 provided with only the hole 41 and the fin 14 provided with only the hole 42. A plurality of fins 15 each provided with both the hole 41 and the hole 42 are provided at positions overlapping the hole 41 and the hole 42. The fin 13 and the fin 14 have the same configuration as that described in the first embodiment, and the hole 41 provided in the fin 13 communicates with the liquid passage 33 and the inlet header 31 and is provided in the fin 14. The hole 42 communicates with the liquid passage 34 and the outlet header 32.

  A plurality of fins 15 provided between the fins 13 and 14 are provided with both a hole 41 and a hole 42. As described in the first embodiment, the hole 41 and the hole 42 have the same position in the Z direction but different positions in the Y direction. As described in the first embodiment, the fluid WF flows through the flow path 50 outside the heat exchanger 200. The hole 41 is provided on the downstream side of the fluid WF, and the hole 42 is provided on the upstream side. ing. The configuration of the fin 15 may be the same as the fins 11 and 12 described in the first embodiment except that both the hole 41 and the hole 42 are provided. And the hole portion 42 and a metal plate portion which is a region other than the hole portion.

  5-7, the several fin 15 is laminated | stacked via the spacer 20, and the fin 13 and the fin 14 are provided via the spacer 20 in the both ends which laminated | stacked the several fin 15, respectively. . The spacer 20 may be a metal or a resin as described in the first embodiment. The spacer 20 is liquid-tightly joined to each fin, a region surrounded by the fin 15, the other fin 15 and the spacer 20, a region surrounded by the fin 13, the fin 15 and the spacer 20, and the fin 14. A flow path 51 is formed in a region surrounded by the fin 15 and the spacer 20. The flow path 51 communicates from the hole portion 41 of the fin 13 to the hole portion 42 of the fin 14, and the refrigerant RF flowing in from the inlet header 31 flows out of the outlet header 32 through the flow path 51. ing.

  Among the plurality of stacked fins of the heat exchanger 200, the plurality of fins 15 excluding the fins 13 and 14 at both ends in the stacking direction have both the hole 41 and the hole 42. Since the fin 13 on the upstream side has only the hole 41 and the fin 14 on the downstream side of the refrigerant RF has only the hole 42, the refrigerant RF flowing in the flow path 51 along the surface of the fin 15 is changed. Since a pressure difference is generated between the hole 41 side and the hole 42 side, the refrigerant flows in the direction indicated by the RF arrow in the flow path 51 as shown in FIG. That is, the refrigerant RF flowing in from the hole 41 of the fin 13 passes through each hole 41 provided in the fin 15 and reaches the fin 14 located at the end in the stacking direction, and also the hole 41 of each fin. It flows in the direction opposite to and parallel to the direction in which the fluid WF flows from the side of the hole 42.

  As shown in FIG. 6, the heat exchanger 200 of the second embodiment allows the refrigerant RF to flow in from the hole 41 on the downstream side of the fluid WF flowing in the flow path 50 provided outside the heat exchanger 200, By flowing out the refrigerant RF from the hole 42 on the upstream side of the fluid WF, the direction in which the refrigerant RF flows through the flow path 51 and the direction in which the fluid WF flows through the flow path 50 can be opposed to each other. It is more preferable because the temperature difference of the refrigerant RF can be kept large and the heat exchange performance of the heat exchanger 200 can be improved.

  However, although the heat exchange performance is lower than that of the heat exchanger 200 shown in FIG. 6, the fins 13 are provided with holes 42 positioned on the upstream side of the fluid WF, and the fins 14 are positioned on the downstream side of the fluid WF. 41 may be provided, and the refrigerant RF may flow in from the hole portion 42 of the fin 13 and flow out from the hole portion 41 of the fin 14. That is, even in a heat exchanger having a configuration in which the direction of the refrigerant RF flowing in the Y direction in the flow direction 51 is opposite to that in FIG. 6, the flow path 51 can be provided along the surface of each fin. The heat exchange performance can be made higher than that of the conventional heat exchanger that flows the refrigerant RF in a direction orthogonal to the direction in which the fluid WF flows.

  The hole 41 and the hole 42 provided in the fin 15 may have the same shape and the same area, but the hole 41 and the hole 42 may have different shapes or different areas. Good. Furthermore, the shape and area of the hole 41 and the hole 42 may be changed according to the position of the fin 15 in the X direction. Thus, by changing the shape and area of the hole 41 and the hole 42, the flow rate of the refrigerant RF that flows in the X direction through each hole 41 and the hole 42 side, that is, the Y side, that is, Y The heat exchange performance of the heat exchanger 200 can be improved by adjusting the ratio with the flow rate of the refrigerant RF flowing in the direction.

  FIG. 8 is a partial cross-sectional view showing a partial configuration of another heat exchanger according to Embodiment 2 of the present invention. The partial cross-sectional view of the heat exchanger 300 shown in FIG. 8 corresponds to the partial cross-sectional view of the heat exchanger 200 in FIG. 6, and the same reference numerals as those in FIG. 6 denote the same or corresponding configurations. The description is omitted. The heat exchanger 300 in FIG. 8 is different from the heat exchanger 200 shown in FIG. 6 in the laminated configuration of a plurality of fins. In the heat exchanger 200 of FIG. 6, the plurality of fins excluding the fins at both ends in the stacking direction are the fins 15 having both the hole 41 and the hole 42, but the heat exchanger 300 of FIG. A plurality of fins excluding fins at both ends in the direction are configured by the fin 15 having both the hole 41 and the hole 42 and the fin 11 or the fin 12 having only one of the hole 41 or the hole 42. ing.

  As illustrated in FIG. 8, the heat exchanger 300 includes two fins 14 that are located at both ends in the stacking direction and have only the hole portions 42, a plurality of fins 15 that are sandwiched and stacked between the fins 14, and fins 15. And the fin 11 having only the hole 41 provided in the middle of the lamination.

  That is, the fin 15 having both the hole 41 and the hole 42 between the fin 11 having only the hole 41 and the fin 14 having only the hole 42 above the middle fin 11 shown in FIG. Are provided. Further, a fin having both the hole 41 and the hole 42 between the fin 11 having only the hole 41 and the fin 14 having only the hole 42 also on the lower side of the drawing with respect to the middle fin 11 shown in FIG. A plurality of 15 are provided.

  Although FIG. 8 shows seven fins 15 and one fin 11, the ratio of the number of the fins 15 and the fins 11 may be arbitrary, and a fin having only the holes 42 instead of the fins 11. 12 may be provided, or the fin 11, the fin 12, and the fin 15 may be provided in an arbitrary number ratio.

  In FIG. 8, the flow path 51 in the Y direction between the fin 14 and the fin 11 on the upstream side of the refrigerant RF is a flow path in the same direction as the direction in which the fluid WF flows, and the fin on the downstream side of the refrigerant RF A flow path 51 in the Y direction between 11 and the fin 14 is a flow path opposite to the direction in which the fluid WF flows. As described above, the heat exchanger is configured by combining the fins 11, the fins 12, and the fins 15, so that the design freedom of the flow path 51 in the heat exchanger is increased. can do.

Embodiment 3 FIG.
FIG. 9 is a side sectional view showing a partial configuration of the heat exchanger according to Embodiment 3 of the present invention. The side sectional view shown in FIG. 9 is a sectional view in the YZ plane of the heat exchanger 400 arranged as shown in FIG. FIG. 10 is an exploded perspective view showing a partial configuration of the heat exchanger according to Embodiment 3 of the present invention. FIG. 10 corresponds to FIG. 4 of the first embodiment. In FIGS. 9 and 10, the same reference numerals as those in FIGS. 1 to 4 of the first embodiment denote the same or corresponding components. The description is omitted. The configuration of the spacer is different from the heat exchanger 100 of the first embodiment.

  FIG. 9 is a cross-sectional view of the heat exchanger 400 cut at the position of the spacer 21. In FIG. 9, the spacers 22 provided alternately with the spacers 21 in the X direction are indicated by broken lines. As shown in FIGS. 9 and 10, the heat exchanger 400 according to the third embodiment of the present invention is configured such that the shape of the flow path formed in the spacers 21 and 22 is not linear but curved. Has been. In FIG. 9, the cross-sectional shape of the spacers 21 and 22 has a polygonal shape formed by only a straight line. In FIG. 10, the cross-sectional shape of the spacers 21 and 22 has a shape formed by a curved line and a straight line. However, the cross-sectional shape of the spacers 21 and 22 may be constituted only by a straight line, may be constituted only by a curve, or may be constituted by a combination of a curve and a straight line.

  The fins 11 and 12 constituting the heat exchanger 400 of the third embodiment have the same configuration as that described in the first embodiment, and are omitted in FIGS. The structure of the fins at both ends where the fins are laminated, the liquid flow pipe connected to the fins at both ends, the inlet header, and the outlet header are the same as those of the heat exchanger 100 described in the first embodiment.

  The spacers 21 and 22 are configured to surround the hole 41 and the hole 42, but the refrigerant RF flow path connecting the hole 41 and the hole 42 connects the hole 41 and the hole 42. The wall surface is configured to be convex in one direction of the surface direction of the fins 11 and the fins 12 rather than the connecting straight line. More specifically, each of the spacers 21 and 22 is formed by a straight line connecting the center of the hole 41 and the center of the hole 42 as viewed from the stacking direction in which a plurality of fins are stacked. 42 has an inner wall having a convex shape in a direction perpendicular to a straight line connecting the center of 42. Since the spacers 21 and 22 have an inner wall having a convex shape in a direction perpendicular to a straight line connecting the center of the hole 41 and the center of the hole 42, the space between the hole 41 and the hole 42 is The flowing refrigerant RF does not flow linearly, but flows so as to be convex in one of the surface directions of the fins 11 and the fins 12, as shown in FIG. As a result, the flow path 51 has a curved shape, and the distance between the hole 41 and the hole 42 is longer than when the flow path 51 is linear, and the surface area of the inner wall of the flow path 51 is further increased. Can do.

  As shown in FIGS. 9 and 10, the spacer 21 and the spacer 22 are opposite to each other in the directions in which the inner walls are convex. That is, as shown in FIG. 9, the spacer 21 has a convex inner wall on the upper side of the paper, while the spacer 22 has a convex inner wall on the lower side of the paper. The direction in which the inner walls of the spacers 21 and 22 are convex is a direction perpendicular to the direction in which the fluid WF flows through the flow path outside the heat exchanger 400. As shown in FIG. 10, the spacers 21 and the spacers 22 are alternately provided via the fins 11 or the fins 12.

  When the refrigerant RF flows in from the inlet header in the heat exchanger 400 configured as described above, the refrigerant RF flows into the flow path inside the inner wall of the spacer 21 from the hole 41 provided in the fin 11, and the fin 12. Flows out from the hole 42 provided in the inner wall of the spacer 22 and flows into the flow path provided inside the inner wall of the spacer 22. Then, the refrigerant RF alternately flows through the flow path provided inside the inner wall of the spacer 21 and the flow path provided inside the inner wall of the spacer 22 and flows out of the heat exchanger 400 from the outlet header. When the refrigerant RF flows through the flow path 51 in the heat exchanger 400, the refrigerant RF flows alternately between the inside of the inner wall of the spacer 21 and the inside of the inner wall of the spacer 22, so that the refrigerant RF starts from one end of the stacked fins. It flows spirally to the end. As a result, in the refrigerant RF flowing through the flow path in the heat exchanger 400, the pressure loss at the time of changing direction is reduced as compared with the case of flowing meandering as described in the first embodiment. Can be increased, and the heat exchange performance of the heat exchanger 400 can be improved.

  Further, as shown in FIG. 9, the positions of the flow path inside the inner wall of the spacer 21 and the flow path inside the inner wall of the spacer 22 when viewed from the stacking direction of the plurality of fins And the hole 42 can be formed at different positions. That is, in the region between the broken line BB and the broken line CC in FIG. 9, the flow path inside the inner wall of the spacer 21 is sandwiched between flow paths through which the fluid WF flows via the fins 11 and 12. The flow path inside the inner wall of the spacer 22 is sandwiched between flow paths through which the fluid WF flows via the fins 11 and 12. That is, the flow path inside the inner walls of the spacer 21 and the spacer 22 and the flow path of the fluid WF outside the fin 11 or the fin 12 are provided via a distance corresponding to the thickness of the fin. The heat exchange between the refrigerant RF flowing in the flow path inside the inner wall and the fluid WF flowing in the flow path outside the fin 11 or the fin 12 can be enhanced.

  In addition, when forming the spacer 21 and the spacer 22 in the same shape and forming a heat exchanger, it is good also as the spacer 21 and the spacer 22 by changing the direction of the direction where the inner wall is convex alternately.

  In the third embodiment, two types of spacers 21 and 22 are used, and the flow path inside the inner wall of the spacer 21 and the flow path inside the inner wall of the spacer 22 are viewed from the stacking direction of the plurality of fins. Although the positions are different, three or more types of spacers may be used so that the flow paths inside the inner walls of the spacers are located at different positions as viewed from the fin stacking direction.

Embodiment 4 FIG.
FIG. 11 is a partial cross-sectional view showing a partial configuration of the heat exchanger according to Embodiment 4 of the present invention. 11 corresponds to FIG. 3 of the first embodiment. In FIG. 11, the same reference numerals as those in FIG. 3 of the first embodiment denote the same or corresponding components. The description is omitted. The configuration of the spacer is different from the heat exchanger 100 of the first embodiment.

  First, the configuration of the spacer 23 will be described. FIG. 12 is a perspective view showing the shape of the spacer of the heat exchanger according to Embodiment 4 of the present invention. Moreover, FIG. 13 is a figure which shows the shape of the spacer of the heat exchanger in Embodiment 4 of this invention. 13A is a plan view of the spacer 23, FIG. 13B is a front view of the spacer 23, and FIG. 13C is a side view of the spacer 23.

  As shown in FIGS. 12 and 13, the spacer 23 has an opening 23 a on the upper surface side of the annular side wall 23 c constituting the cylindrical side surface and an opening 23 b on the bottom surface side. The shape of the portion 23a and the shape of the opening 23b on the bottom surface side have an overlapping shape when rotated by 180 ° with the axis in the height direction (X direction) passing through the center of the spacer 23 as the rotation axis. That is, when the opening 23a on the upper surface side viewed from the X direction is rotated by 180 ° with the axis parallel to the X direction passing through the point O shown in FIG. It overlaps with the shape of the opening 23b on the bottom side.

  As shown in FIGS. 13A and 13B, the opening 23a on the upper surface side of the spacer 23 has a larger area on the right side of the drawing than the XZ plane passing through the center point O of the spacer 23 than on the left side of the drawing. The opening 23b on the bottom side has a larger area on the left side of the drawing than the XZ plane passing through the point O than on the right side of the drawing. Further, the shape of the side wall 23c of the spacer 23 is such that the width in the Y direction and the width in the Z direction decrease from the top surface side to the bottom surface side on the right side of the XZ plane passing through the point O. The width in the Y direction and the width in the Z direction are formed so as to increase from the top surface side to the bottom surface side on the left side of the XZ plane passing through. For this reason, as shown in FIGS. 13B and 13C, the side wall 23c connecting the opening 23a on the upper surface side of the spacer 23 and the opening 23b on the bottom surface side is formed with a smooth curved surface. The upper surface side of the spacer 23 is joined to the fin 11 having the hole 41 on the right side of the paper, and the bottom surface side of the spacer 23 is joined to the fin 12 having the hole 42 on the left side of the paper.

  Next, it will be described in more detail with reference to FIG. In FIG. 11, eight broken lines are shown from broken line EE to broken line KK. Each broken line indicates a range of the hole 41, the hole 42, the opening 23a on the upper surface side of the spacer 23 and the opening 23b on the bottom surface side when viewed from the stacking direction of the plurality of fins. The hole 41 provided in the fin 11 and the fin 13 is provided between the broken line II and the broken line JJ, and the hole 42 provided in the fin 12 and the fin 14 is provided with the broken line EE and the broken line. It is provided between FF. In a direction parallel to the flow path 51, the side wall 23c on the hole 41 side is provided between a broken line HH and a broken line KK, and the side wall 23c on the hole 42 side is formed with a broken line DD and a broken line G. -G. Further, the opening 23a on the upper surface side of the spacer 23 is provided between the broken line GG and the broken line KK, and the opening 23b on the bottom surface side of the spacer 23 includes the broken line DD and the broken line HH. It is provided between.

  As shown in FIG. 11, the spacer 23 surrounds both the hole 41 and the hole 42. However, when viewed from the X direction, which is the lamination direction of the fins, the opening 23a on the upper surface side of the spacer 23 surrounds the hole 41 but does not surround the hole 42, and the opening on the bottom surface side of the spacer 23 The portion 23 b surrounds the hole portion 42 but does not surround the hole portion 41. That is, when viewed from the fin stacking direction, the entire hole 41 is not included in the opening 23 b on the bottom surface side of the spacer 23, and the entire hole 42 is the opening on the upper surface side of the spacer 23. It is not included in 23a.

  Further, when viewed from the stacking direction of the plurality of fins, the side wall 23c on the hole 41 side is included at a position overlapping with the hole 41, and the side wall 23c on the hole 42 side is included at a position overlapping with the hole 42. It is. That is, when viewed from the stacking direction of the plurality of fins, the inner wall on the hole 41 side of the spacer 23 is included in the position overlapping with the hole 41, and the hole 42 side of the spacer 23 is positioned in the position overlapping with the hole 42. The inner wall of is included. Therefore, the inner wall of the spacer 23 is smoothly connected to the opening at the other end as it moves away from the one end joined to the hole 41 or the fin provided with the hole 42 toward the other end. It becomes a curved surface that goes inward. That is, of the inner walls of the spacer 23, the inner wall close to the hole 41 is inclined toward the inner side of the spacer 23 as the distance from the fins 11 and 13 provided with the hole 41 is increased. As the distance from the fins 12 and 14 provided with the portion 42 increases, the spacer 42 inclines inside.

  As shown in FIG. 11, the flow path 51 extending from the hole 41 provided in the fin 11 or the fin 13 to the inside of the spacer 23 is smooth toward the left side of the page where the inner wall of the spacer 23 is the direction of the flow path 51. Therefore, the refrigerant RF that has flowed into the inside of the spacer 23 from the hole 41 changes the direction of flowing smoothly along the inner wall of the spacer 23 and flows to the left in the drawing. Similarly, the flow path 51 extending from the hole portion 42 provided in the fin 12 to the inside of the spacer 23 is smoothly bent toward the right side of the page, which is the direction of the flow path 51, because the inner wall of the spacer 23 is bent smoothly. The refrigerant RF that has flowed into the spacer 23 from the portion 42 flows in the right direction of the drawing while changing the direction in which the refrigerant RF smoothly flows along the inner wall of the spacer 23.

  As described above, the spacer 23 has a smooth shape along the streamline of the refrigerant RF that flows through the flow path 51 in the heat exchanger 500, so that the fins 11 and 13 and the fins 12 and 14 are formed. And the retention part which is a place where the refrigerant RF easily stays in the flow path 51 surrounded by the spacer 23 can be eliminated. As a result, the formation of an oxygen concentration battery due to the difference in dissolved oxygen concentration between the retention portion where water, which is the refrigerant RF, easily accumulates in the flow path 51, and other locations is suppressed, and the corrosion resistance of the heat exchanger 500 is reduced. Reliability can be improved.

  Further, even if the flow path 51 in the heat exchanger 500 is a meandering flow path that meanders in parallel to the direction in which the fluid WF flowing in the flow path outside the heat exchanger 500 flows, the direction of the flow path 51 changes direction. Since the inner wall of the flow path 51 has a smooth curve at the location where the heat is applied, the pressure loss of the refrigerant RF flowing in the flow path 51 is reduced, and the heat exchange performance of the heat exchanger 500 is improved by increasing the flow rate of the refrigerant RF. Can be made. In particular, in the heat exchanger 500 of the present invention, since the spacer 23 can be formed of resin, it is possible to easily form the spacer 23 having a smooth shape along the flow line of the refrigerant RF that flows through the flow path 51. .

  In the fourth embodiment, when viewed from the stacking direction of the plurality of fins, the side wall 23c on the hole 41 side is included at the position overlapping the hole 41, and the hole is positioned at the position overlapping the hole 42. The side wall 23c on the 42 side is included, but when at least one of the side walls 23c on the hole 41 side or the hole 42 side is viewed from the stacking direction of the plurality of fins 41 or It suffices if it is included in a position overlapping the hole 42.

Embodiment 5. FIG.
FIG. 14 is a schematic configuration diagram showing the configuration of the air-conditioning apparatus according to Embodiment 5 of the present invention. The air conditioning apparatus 1 in FIG. 14 includes any one of the heat exchangers 100 to 500 described in the first to fourth embodiments. In the present embodiment, description will be made assuming that the heat exchanger 100 described in the first embodiment is provided.

  As shown in FIG. 14, the air conditioner 1 includes three heat exchangers, a heat exchanger 100 according to the present invention, a first heat exchanger 104, and a second heat exchanger 110. The first heat exchanger 104 is, for example, an outdoor heat exchanger, and is a heat exchanger that performs heat exchange between the gas refrigerant and the outside air. The second heat exchanger 110 is, for example, a heat exchanger that performs heat exchange between a gas refrigerant and a water refrigerant, and includes, for example, a first conduit that forms a flow path of the gas refrigerant and a flow of the water refrigerant. The second conduit constituting the path is connected via a metal having a high thermal conductivity. The heat exchanger 100 of the present invention is, for example, an indoor heat exchanger, and is provided outside the heat exchanger 100 with water flowing in the flow path in the heat exchanger 100 as described in the first embodiment. Heat exchange with room air flowing through the flow path. The air conditioner 1 of FIG. 14 moves heat from the heat exchanger 100 that is an indoor heat exchanger to the first heat exchanger 104 that is an outdoor heat exchanger in the cooling operation, and is an outdoor heat exchanger in the heating operation. Heat is transferred from a certain first heat exchanger 104 to a heat exchanger 100 that is an indoor heat exchanger.

  The gas refrigerant circuit between the first heat exchanger 104 and the second heat exchanger 110 is configured as follows. As shown in FIG. 14, the gas refrigerant circuit includes a compressor 101, a muffler 102, a four-way valve 103, a first heat exchanger 104, a capillary tube 105, a strainer 106, an electronically controlled expansion valve 107, stop valves 108a and 108b, The auxiliary muffler 109 and the second heat exchanger 110 are connected by a refrigerant pipe 114. A gas refrigerant such as hydrofluorocarbon is sealed in the refrigerant pipe 114 of the gas refrigerant circuit. In addition, the first heat exchanger 104 includes a fan 111, and heat is generated between the first heat exchanger 104 and the air around the first heat exchanger 104 using air blown by the fan 111. We are exchanging. The heat transfer between the first heat exchanger 104 and the second heat exchanger is performed by a refrigeration cycle using a gas refrigerant such as hydrofluorocarbon.

  The water refrigerant circuit between the heat exchanger 100 and the second heat exchanger 110 of the present invention is configured as follows. As shown in FIG. 14, the heat exchanger 100 and the second heat exchanger 110 are connected by a refrigerant pipe 115, and a circulation pump 113 is provided between the heat exchanger 100 and the second heat exchanger 110. It is done. Water as a refrigerant is sealed in the refrigerant pipe 115, and the water is circulated between the heat exchanger 100 and the second heat exchanger 110 by the circulation pump 113. In addition, the heat exchanger 100 includes a fan 112, and heat exchange is performed between the heat exchanger 100 and air around the heat exchanger 100 using air blown by the fan 112.

  The air conditioner 1 controls the actuators such as the compressor 101, the circulation pump 113, and the electronically controlled expansion valve 107 based on the outdoor air temperature, the indoor air temperature, and the temperatures of the gas refrigerant and the water refrigerant ( (Not shown), and the control unit switches and controls the four-way valve 103, whereby the cooling operation and the heating operation are switched.

  Next, the operation of the air conditioner 1 will be described.

  First, the operation in the cooling operation will be described. When performing the cooling operation, the four-way valve 103 is switched to the cooling operation by the control unit, and the refrigerant that has been compressed by the compressor 203 and becomes high temperature and high pressure is transferred to the first heat exchanger 104 via the four-way valve 103. Inflow. The high-temperature and high-pressure refrigerant that has flowed into the first heat exchanger 104 performs heat exchange with the outdoor air that passes through the flow path outside the first heat exchanger 104 in the first heat exchanger 104, The heat of the high-temperature and high-pressure refrigerant is radiated to the outdoor air flowing in the flow path outside the first heat exchanger 104 by the fan 111, and the refrigerant becomes low-temperature and high-pressure and flows out from the first heat exchanger 104. . The low-temperature and high-pressure refrigerant that has flowed out of the first heat exchanger 104 is depressurized by the capillary tube 105 and the electronic control type expansion valve 107, becomes a low-temperature and low-pressure refrigerant, and flows into the second heat exchanger 110. The refrigerant that has flowed into the second heat exchanger 110 exchanges heat with water flowing in the flow path of the water refrigerant circuit, absorbs heat from the water in the water refrigerant circuit, and is sucked into the compressor 101.

  On the other hand, the water flowing through the water refrigerant circuit is circulated between the second heat exchanger 110 and the heat exchanger 100 of the present invention by the circulation pump 113. The circulation pump 113 is controlled by the control unit, and controls the amount of water flowing through the water refrigerant circuit according to the indoor cooling set temperature or the like. The water that has flowed into the second heat exchanger 110 radiates heat to the gas refrigerant and is cooled in order to exchange heat with the refrigerant flowing through the gas refrigerant circuit. The cooled and cooled water is sent to the heat exchanger 100 of the present invention by the circulation pump 113.

  As described in the first embodiment, the water that has reached the heat exchanger 100 flows in from the inlet header 31 of the heat exchanger 100 and flows through the flow path 51 provided in the heat exchanger 100, and the heat exchanger Out of 100 outlet headers 32. Since the indoor air is flowed by the fan 112 through the flow path 50 outside the heat exchanger 100, the air flowing through the flow path 50 outside the heat exchanger 100 and the flow path 51 inside the heat exchanger 100 flow. Heat is exchanged with water, that is, the heat of the air flowing through the flow path 50 is radiated to the water flowing through the flow path 51, and the air passing through the flow path 50 outside the heat exchanger 100 is cooled. The As a result, the room air is cooled and cooling is performed.

  Next, the operation in the case of heating operation will be described. When performing the heating operation, the four-way valve 103 is switched to the heating operation by the control unit, and the refrigerant that has been compressed by the compressor 203 to become a high temperature and a high pressure passes through the four-way valve 103 to the second heat exchanger 110. Inflow. The high-temperature and high-pressure refrigerant that has flowed into the second heat exchanger 110 exchanges heat with water flowing through the flow path of the water refrigerant circuit in the second heat exchanger 110, and the heat of the high-temperature and high-pressure refrigerant is water. Heat is radiated to the water in the refrigerant circuit, and the refrigerant becomes low temperature and high pressure and flows out from the second heat exchanger 110. The low-temperature and high-pressure refrigerant flowing out from the second heat exchanger 110 is decompressed by the electronic control type expansion valve 107 and the capillary tube 105 to become a low-temperature and low-pressure refrigerant and flows into the first heat exchanger 104. The refrigerant flowing into the first heat exchanger 104 exchanges heat with the outdoor air flowing in the flow path outside the first heat exchanger 104 by the fan 111, and absorbs heat from the outdoor air. Then, it is sucked into the compressor 101.

  The water flowing through the water refrigerant circuit is circulated between the second heat exchanger 110 and the heat exchanger 100 of the present invention by the circulation pump 113 as in the case of the cooling operation. Since the water flowing into the second heat exchanger 110 exchanges heat with the refrigerant flowing through the gas refrigerant circuit, it absorbs the heat radiated from the gas refrigerant and becomes high temperature and flows into the heat exchanger 100. .

  As in the case of the cooling operation, the water that has reached the heat exchanger 100 flows from the inlet header 31 of the heat exchanger 100, flows through the flow path 51 provided in the heat exchanger 100, and exits from the heat exchanger 100. Out of the header 32. Since the indoor air is flowed by the fan 112 through the flow path 50 outside the heat exchanger 100, the air flowing through the flow path 50 outside the heat exchanger 100 and the flow path 51 inside the heat exchanger 100 flow. Heat exchange takes place with water. That is, the heat of water flowing in the flow path 51 is radiated to the air flowing in the flow path 50, and the air passing through the flow path 50 outside the heat exchanger 100 is heated. As a result, room air is heated and heating is performed.

  In the fifth embodiment, a gas refrigerant circuit and a water refrigerant circuit are provided between the first heat exchanger 104 that is an outdoor heat exchanger and the heat exchanger 100 of the present invention that is an indoor heat exchanger. Although the air conditioner 1 in which the heat transfer is performed via the second heat exchanger 110 that performs heat exchange between the gas refrigerant circuit and the water refrigerant circuit has been described, the heat exchanger 100 of the present invention includes: Alternatively, it may be used in an air conditioner including only a gas refrigerant circuit. That is, the heat exchanger 100 of the present invention is provided at the position of the second heat exchanger 110 in FIG. 14, the water refrigerant circuit is removed, and a gas refrigerant such as hydrofluorocarbon is allowed to flow through the flow path 51 in the heat exchanger 100. Alternatively, indoor air may be flowed through the flow path 50 outside the heat exchanger 100, and heat may be transferred between the first heat exchanger 104 and the heat exchanger 100 of the present invention by a refrigeration cycle. In this case, since the high-pressure gas refrigerant compressed by the compressor flows into the flow path 51 of the heat exchanger 100, the fins 11, 12, 13, and 14 of the heat exchanger 100 and the spacer 20 are both made of metal. It is more preferable that the fins 11, 12, 13, and 14 and the spacers 20 are formed by brazing or diffusion bonding because the pressure of the gas refrigerant can be increased.

  In the fifth embodiment, the air conditioner 1 using the heat exchanger 100 described in the first embodiment has been described. However, the air using any of the heat exchangers described in the second to fourth embodiments. It may be a harmony device.

  Although the present invention has been specifically described above based on the embodiments, the present invention is not limited to the above-described embodiments, and various modifications may be made without departing from the scope of the invention. The configurations described in Embodiments 1 to 4 can be combined with each other.

DESCRIPTION OF SYMBOLS 1 Air conditioning apparatus 11, 12, 13, 14, 15 Fin 20, 21, 22, 23 Spacer 31 Inlet header, 32 Outlet header 41, 42 Hole 50, 51 Flow path 100, 200, 300, 400, 500 Heat exchange vessel

Claims (12)

A first fin having a metal plate provided with a first hole through which a refrigerant flows;
Metal that is stacked separately from the first fin and provided with a second hole through which the refrigerant flows at a position different from the first hole when viewed from the stacking direction with the first fin. A second fin having a plate;
A spacer provided between the first fin and the second fin so as to surround the first hole and the second hole;
With
The first fin, the second fin, and the spacer are configured, and an inner wall of a flow path through which the refrigerant flows along the surface of the first fin is provided to face the second hole. Heat exchanger. A fluid that exchanges heat with the refrigerant flows between the first fin and the second fin,
2. The heat exchanger according to claim 1, wherein the first hole is provided downstream of the second hole in a direction in which the fluid flows. A third fin having a metal plate provided with a third hole through which the refrigerant flows at a position different from the second hole as viewed from the stacking direction;
A spacer provided between the second fin and the third fin so as to surround the second hole and the third hole;
The heat exchanger according to claim 1 or 2, further comprising: The spacer provided between the first fin and the second fin is perpendicular to a straight line connecting the first hole and the second hole when viewed from the stacking direction, and A convex inner wall in a first direction along the surface of the second fin;
The spacer provided between the second fin and the third fin is perpendicular to a straight line connecting the second hole and the third hole when viewed from the stacking direction, and A convex inner wall in a second direction along the surface of the second fin;
The heat exchanger according to claim 3, wherein the first direction and the second direction are opposite to each other. The second fin is provided with a fourth hole through which the refrigerant flows at a position facing the first hole,
A third fin having a metal plate provided with a third hole through which the refrigerant flows in a position facing the second hole;
A spacer provided between the second fin and the third fin so as to surround the second hole, the third hole, and the fourth hole;
The heat exchanger according to claim 1 or 2, further comprising:   The heat exchanger according to any one of claims 1 to 5, wherein an inner wall of the flow path facing the second hole is the first fin. The spacer provided between the first fin and the second fin has an inner wall that is inclined inward as the distance from the second fin increases.
The heat exchanger according to any one of claims 1 to 4, wherein an inner wall of the flow path facing the second hole is the inclined inner wall. A plurality of spacers between the first fin and the second fin;
The heat exchanger according to any one of claims 1 to 7, wherein a plurality of flow paths configured by the first fins, the second fins, and the plurality of spacers are provided in parallel to each other.   The heat exchanger according to claim 8, wherein the plurality of flow paths communicate with each other.   The heat exchanger according to any one of claims 1 to 9, wherein the spacer is made of a resin. The spacer is made of metal,
The resin film, the metal oxide film, the metal nitride film, the metal carbide film, or a metal film having a higher ionization tendency than the metal is provided on the inner wall surface in contact with the refrigerant. The heat exchanger according to any one of 9. A second heat exchanger comprising a compressor, a first heat exchanger, an expansion valve, and the heat exchanger according to any one of claims 1 to 11,
Air conditioner with

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