JP6520136B2 - Heat exchanger - Google Patents

Description

  The present invention relates to a heat exchanger that exchanges heat between a first fluid and a second fluid.

  As this kind of heat exchanger, for example, there is a heat exchanger described in Patent Document 1. The heat exchanger described in Patent Document 1 includes a plurality of tubes through which a working medium flows, and a plurality of fins disposed between the tubes. The plurality of tubes are arranged such that the longitudinal direction is parallel to the vertical direction and the horizontal direction is separated by a predetermined gap. The gap between the adjacent tubes forms an air passage, and heat exchange is performed between the air and the working medium in the tubes. Fins enhance heat exchange performance by increasing the heat transfer area.

JP 2012-237474 A

  By the way, when the heat exchanger as described above is used as, for example, an outdoor unit for heat pump, the temperature of the heat exchanger becomes lower than the outside air. Therefore, depending on the use environment, such as when the heat pump is driven in winter, the temperature of the heat exchanger may be considered to be below the freezing point of water. Under such circumstances, if water is accumulated between the tubes due to water or condensation due to the external environment, the water may be frozen. When the water between the tubes freezes, the volume expansion may cause deformation of the fins and the tubes. In the following, for the sake of convenience, deformation of fins and tubes resulting from water freezing is also referred to as "freeze deformation". If such freezing deformation occurs in the tube, a refrigerant leak or the like may occur, which is not preferable.

  The present invention has been made in view of these circumstances, and an object thereof is to provide a heat exchanger capable of suppressing deformation of fins and tubes.

In order to solve the above-mentioned subject, a heat exchanger (5) which performs heat exchange between the 1st fluid and the 2nd fluid is provided with a tube (30) and a fin (40). The tubes have a longitudinal direction in a direction intersecting with the horizontal direction, and are arranged with a gap in a direction intersecting with the vertical direction, and the first fluid flows inside. The fins are disposed between adjacent tubes to promote heat exchange between the second fluid flowing between the tubes and the first fluid flowing inside the tubes. The fins consist of corrugated fins having a plurality of fin segments spaced in the longitudinal direction of the tube. The fin piece has a flat plate portion (42) and a plurality of louver portions (43) cut and raised so as to be inclined with respect to the flat portion. When the fin piece disposed on the lower end side in the vertical direction in the fin is the lower layer fin piece (411) and the fin piece disposed on the vertically upper side of the lower layer fin piece is the upper layer fin piece (410) The fins have the same fin pitch in the portion where the upper layer side fin pieces are arranged and in the portion where the lower layer side fin pieces are arranged. The second distance between the tips of the louver portions of the adjacent lower layer side fin pieces is longer than the first distance between the tips (43 a) of the respective louver portions of the adjacent upper layer side fin pieces. The temperature of the heat exchanger is below the freezing point of water.

  According to this configuration, since the longitudinal direction of the tubes is set in the direction intersecting the horizontal direction, the water staying between the tubes flows downward in the vertical direction. Thus, water stagnates on the lower side in the vertical direction of the gap between the tubes. That is, water stagnates around the lower layer side fin piece. As a result, water is less likely to stay around the upper layer side fin pieces, so that it is possible to suppress the occurrence of freezing deformation around the upper layer side fin pieces.

  On the other hand, when the fin piece has a louver part, in the adjacent fin piece, the distance between the tip of each louver becomes the shortest. Thus, when the water stagnating between the tubes freezes, this site freezes most quickly. In addition, the freezing is delayed at the longest distance between the louvers of the adjacent fin pieces. Such spatial differences in the freezing rate of water leave the unfrozen water surrounded by ice. As the volume of water increases, the volumetric expansion of water at the time of freezing increases, and it has been confirmed by the inventor's experiments that freezing deformation tends to occur.

  In this respect, according to the above configuration, since the distance between the tips of the louvers is long in the lower layer side fin piece in which water tends to stay, it is difficult to make a local difference in the freezing rate of water. Therefore, since it becomes difficult to remain unfrozen water in the state enclosed by ice, it can suppress freezing deformation as a result.

Moreover, in order to solve the said subject, the heat exchanger (5 ) which heat-exchanges between a 1st fluid and a 2nd fluid is equipped with a tube (30) and a fin (40). The tubes have a longitudinal direction in a direction intersecting with the horizontal direction, and are arranged with a gap in a direction intersecting with the vertical direction, and the first fluid flows inside. The fins are disposed between adjacent tubes to promote heat exchange between the second fluid flowing between the tubes and the first fluid flowing inside the tubes. The fins consist of corrugated fins having a plurality of fin pieces (41) arranged at regular intervals in the longitudinal direction of the tube. When the fin piece disposed on the lower end side in the vertical direction in the fin is the lower layer fin piece (411) and the fin piece disposed on the vertically upper side of the lower layer fin piece is the upper layer fin piece (410) The fins have the same fin pitch in the portion where the upper layer side fin pieces are arranged and in the portion where the lower layer side fin pieces are arranged. The upper layer side fin piece (410) has a flat plate portion (42) and a plurality of louver portions (43) cut and raised so as to be inclined to the flat portion, and the lower layer side fin piece (411) ) to have the only flat portion. The temperature of the heat exchanger is below the freezing point of water.

  According to this configuration, since the distance between the adjacent lower layer side fin pieces can be increased, it is also less likely that the water freezing rate is different locally. Therefore, since it becomes difficult to remain unfrozen water in the state enclosed by ice, it can suppress freezing deformation as a result.

  According to the present invention, deformation of the fins and the tube can be suppressed.

The block diagram which shows the outline | summary of heat pump. The front view which shows the front structure about 1st Embodiment of a heat exchanger. The enlarged view which shows the expansion structure of the area | region A of FIG. The enlarged view which shows the expansion structure of the periphery of the vertical direction lower end side of the tube about the heat exchanger of 1st Embodiment. FIG. 5 is an end view showing an end face structure along the line V-V in FIG. The end view which shows the freezing aspect of water between tubes schematically. The end elevation showing the freezing mode of water when water freezes around the upper layer side fin piece. The end elevation showing the freezing mode of water when water freezes around the lower layer side fin piece. The end elevation showing the end face structure of a fin about a 2nd embodiment of a heat exchanger. The end elevation showing the end face structure of a fin about a 3rd embodiment of a heat exchanger. The end elevation showing the end face structure of a fin about a 4th embodiment of a heat exchanger. The end view showing the end face structure of a fin about a 5th embodiment of a heat exchanger. The end elevation showing the end face structure of a fin about a 6th embodiment of a heat exchanger. The enlarged view which shows the expansion structure of the periphery of the vertical direction lower end side of the tube about 7th Embodiment of a heat exchanger. The enlarged view which shows the expansion structure of the periphery of the vertical direction lower end side of the tube about 8th Embodiment of a heat exchanger. The perspective end view which expands and shows the end surface structure between the tubes about 9th Embodiment of a heat exchanger. The end view which expands and shows the end face structure between the tubes about a 10th embodiment of a heat exchanger. The end view which shows the end surface structure of the fin about other embodiment of a heat exchanger. The end view which shows the end surface structure of the fin about other embodiment of a heat exchanger.

First Embodiment
Hereinafter, a first embodiment of the heat exchanger will be described. First, with reference to FIG. 1, an overview of a heat pump system in which the heat exchanger of the present embodiment is used will be described.

  As shown in FIG. 1, the heat pump system 1 includes a compressor 2, a condenser 3, an expansion valve 4, and a heat exchanger 5. The compressor 2, the condenser 3, the expansion valve 4, and the heat exchanger 5 are annularly connected via a pipe 6.

  The compressor 2 compresses the working medium flowing in the pipe 6 to raise its temperature, and the working medium in the pipe 6 is “compressor 2 → condenser 3 → expansion valve 4 → heat exchanger 5 → compression Circulate in the order of machine 2 ". The condenser 3 heats the air for blowing by performing heat exchange, for example, with the air for blowing air blown into the passenger compartment or in the home. The expansion valve 4 expands the working medium dissipated by the condenser 3 to lower its temperature. The heat exchanger 5 raises the temperature of the working medium by performing heat exchange between the working medium expanded by the expansion valve 4 and lowered in temperature and the outside air.

  Next, the structure of the heat exchanger 5 will be described in detail with reference to FIGS. 2 and 3. FIG. 3 is an enlarged view of a portion indicated by a region A in FIG.

  As shown in FIG. 2, the heat exchanger 5 includes a first tank 10, a second tank 20, and a tube 30.

  The first tank 10 is an elongated hollow rod-like container having a longitudinal direction in the horizontal direction. The first tank 10 has a supply port 11 and a discharge port 12 at both ends in the longitudinal direction. The supply port 11 is an inlet of a working medium supplied from the expansion valve 4 to the heat exchanger 5. The discharge port 12 is a discharge port of the working medium discharged from the heat exchanger 5 to the compressor 2. The first tank 10 is a portion that stores the working medium supplied from the expansion valve 4 to the heat exchanger 5 and supplies the working medium to the tube 30.

  The first tank 10 has a partition plate (not shown) at a part or a plurality of locations in the longitudinal direction. The internal space in the first tank 10 is divided into a plurality of internal spaces by this partition plate.

  In FIG. 2 and FIG. 3, an axis parallel to the extension direction of the first tank 10, in other words, the direction from the supply port 11 to the discharge port 12, is indicated by the x-axis. Further, an axis parallel to the vertical direction, in other words, an axis parallel to the longitudinal direction of the tube 30, is represented by the z-axis. Furthermore, an axis orthogonal to both the x axis and the z axis is represented by the y axis. The x-axis, the y-axis, and the z-axis are similarly set in the subsequent drawings.

  The second tank 20 has substantially the same shape as the first tank 10. However, the second tank 20 differs from the first tank 10 in that the supply port 11 and the discharge port 12 are not provided. The second tank 20 is disposed vertically above the first tank 10 in parallel with the first tank 10. In FIG. 2, an end portion of the second tank 20 located on the supply port 11 side of the first tank 10 is denoted by a reference numeral 21. Further, the other end of the second tank 20 located on the side of the discharge port 12 of the first tank 10 is indicated by the reference numeral 22.

  The tube 30 is an elongated pipe having a longitudinal direction in the vertical direction. The tube 30 has a flat cross-sectional shape perpendicular to the vertical direction. A plurality of tubes 30 are arranged in parallel with each other with a gap in the horizontal direction. The lower end of each tube 30 in the vertical direction is connected to the first tank 10. The vertically upper end of each tube 30 is connected to the second tank 20. Therefore, the internal space of the first tank 10 and the internal space of the second tank 20 are in communication via the tube 30.

  As shown in FIG. 3, the heat exchanger 5 includes fins 40 disposed between the adjacent tubes 30. In FIG. 2, the illustration of the fins 40 is omitted. The fins 40 are so-called corrugated fins, and are formed, for example, by processing a thin and long aluminum plate into a weave. The fins 40 have a plurality of flat fin pieces 41 arranged at regular intervals in the vertical direction. The folded portions of the fins 40 are fixed by brazing to a pair of tubes 30 disposed on both sides of the fins 40.

  In the heat exchanger 5, the working medium supplied to the supply port 11 flows into the internal space of the first tank 10 and is stored. The working medium stored in the first tank 10 flows vertically upward from the first tank 10 through the inside of the tube 30 and flows into the internal space of the second tank 20. The working medium flows vertically downward from the inner space of the second tank 20 to the inside of the tube 30, flows into the inner space of the first tank 10, and is then discharged from the discharge port 12.

  The heat exchanger 5 is provided with a blower fan (not shown). Air (outside air) is fed toward the heat exchanger 5 by the blower fan. The air passes between the tubes 30, 30 in a direction parallel to the y-axis. At this time, heat exchange is performed between the working medium and the air flowing inside the tube 30, and the heat of the air is transferred to the working medium. In the following, the direction parallel to the y-axis is also referred to as “air flow direction”.

  The heat of the air is transferred to the working medium by way of the fins 40. That is, in the heat exchanger 5, the contact area with the passing air is enlarged by the fins 40 to promote the heat exchange between the working medium and the air.

  Next, the structure of the fin 40 will be described in detail with reference to FIGS. 4 and 5. FIG. 5 shows an end face structure along the line V-V in FIG.

  As shown in FIG. 4 and FIG. 5, each fin piece 41 has a flat plate portion 42 substantially parallel to the air flow direction, and a plurality of window windows cut and raised with respect to the flat portion 42. The louver portion 43 of the The louver part 43 consists of a flat member. In addition, in FIG. 5, the direction along each plane part 42 is shown with the dashed-dotted line m.

  As shown in FIG. 5, the louver portion 43 has a plurality of upstream louver groups 431 located upstream of the central portion 44 of the fin piece 41 in the air flow direction, and an air flow direction than the central portion 44 of the flat portion 42. Are divided into a plurality of downstream louvers 432 located downstream of the In the fins 40 of the present embodiment, among the plurality of fin pieces 41, the fin piece disposed on the lower end side in the vertical direction is the lower layer side fin piece 411, and is disposed vertically above the lower layer side fin piece 411. When the fin pieces are the upper layer side fin pieces 410, the inclination angles of the louver portion 43 are different between the upper layer side fin pieces 410 and the lower layer side fin pieces 411. In addition, the upper layer side fin piece 410 and the lower layer side fin piece 411 consist of the same member.

Next, the structures of the upper layer side fin piece 410 and the lower layer side fin piece 411 will be described in detail.
As shown in FIG. 5, the upstream louver group 431 of the upper layer side fin piece 410 is inclined at an acute angle θ 1 with respect to the flat portion 42. Further, the downstream side louver group 432 of the upper layer side fin piece 410 is inclined at an acute angle θ 1 in the opposite direction to the inclination direction of the upstream side louver group 431. Hereinafter, the angle θ1 is referred to as a “first louver angle”. In the upper layer side fin piece 410, the inclination angle of the louver portion 43 is set to the first louver angle θ1, whereby the distance between the respective louver portion tip portions 43a, 43a of the adjacent fin pieces 410, 410, in other words, The shortest distance between the adjacent fin pieces 410, 410 is set to the first distance L1.

  On the other hand, the upstream louver group 431 of the lower layer side fin piece 411 is inclined to the plane portion 42 at an acute angle θ 2 smaller than the upper layer side fin piece 410. Further, the downstream side louver group 432 of the lower layer side fin piece 411 is inclined at an acute angle θ 2 in the direction opposite to the inclination direction of the upstream side louver group 431. Hereinafter, the angle θ2 is referred to as a “second louver angle”. In the lower layer side fin piece 411, the inclination angle of the louver portion 43 is set to the second louver angle θ2, whereby the distance between the respective louver portion tip portions 43a and 43a of the adjacent fin pieces 411 and 411, in other words, The shortest distance between the adjacent fin pieces 411 and 411 is set to a second distance L2 longer than the first distance L1. By making the lower layer side fin piece 411 in such a structure, freezing deformation is less likely to occur in the portion where the lower layer side fin piece 411 is arranged than in the portion where the upper layer side fin piece 410 is arranged.

  Next, along with the mechanism of the freezing deformation, the reason why the lower layer side fin pieces 411 are less likely to cause the freezing deformation will be described. First, the mechanism of freezing deformation is described.

  The heat exchanger 5 is covered with, for example, dew condensation water, rain water, washing water, and the like. Moreover, when the heat exchanger 5 is mounted in a vehicle, the heat exchanger 5 may be flooded by the entrained water of the forward vehicle. When the temperature of the heat exchanger 5 falls below the freezing point of water in the water-covered state, freezing progresses from the tube 30 and the fins 40. In the initial stage of freezing, water corresponding to the volume expansion when changing from water to ice is discharged from the end of the fin 40 in the width direction (y-axis direction). However, in the late stage of freezing, water remains as it is surrounded by ice.

  More specifically, as shown in FIG. 6, in the fin pieces 41, 41 adjacent in the longitudinal direction (direction parallel to the z-axis) of the tube 30, the distance between the respective louver tip portions 43a, 43a is the shortest. . Therefore, when it freezes from the circumference of fin 40 as shown in the figure, between louver part tip parts 43a and 43a of each fin piece 41 and 41 which adjoins is frozen most quickly, and is closed with ice. Such a local difference in the freezing rate of water leaves unfrozen water between the central portions of the louvers 43 and 43 which are most distant from each other. In this way, unfrozen water is trapped in the ice. Hereinafter, the unfrozen water remaining while being surrounded by the ice is referred to as "non-frozen residual water". The unfrozen residual water is not discharged at the time of freezing since it is surrounded by ice. Load is applied to the tube 30 and the fins 40 due to volume expansion when the unfrozen residual water freezes. This load causes the tube 30 and the fins 40 to be frozen and deformed. In addition, if this phenomenon is repeated, there is a possibility that the tube 30 may be damaged and a refrigerant leak or the like may occur.

  Focusing on the mechanism by which such unfrozen residual water is generated, if the distance between the adjacent louver tip portions 43a and 43a is increased, it becomes difficult to produce a local difference in the freezing rate of water, so The residual water of freezing can be reduced. FIGS. 7 and 8 show an analysis result in the case where water is frozen in the upper layer side fin piece 410 and an analysis result in the case where water is frozen in the lower layer side fin piece 411 in comparison.

  As shown in FIG. 7, in the upper layer side fin piece 410, the first distance L1 between the adjacent louver tip portions 43a and 43a is shorter than the second distance L2 of the lower layer side fin piece 411. Therefore, if water freezes around the upper layer side fin piece 410, the time until the adjacent louver tip portions 43a and 43a are blocked by ice is shorter than that of the lower layer side fin piece 411. Become. As a result, since it becomes difficult to discharge the water of the volume expansion at the time of freezing, the unfreezed residual water W is increased, and the freezing deformation tends to occur.

  On the other hand, as shown in FIG. 8, in the lower layer side fin piece 411, the second distance between the adjacent louver tip portions 43a and 43a is longer than that of the upper layer side fin piece 410. Therefore, assuming that the water freezes around the lower layer side fin piece 411, the time from when the water starts to freeze until the adjacent louver tip portions 43a and 43a are blocked by the water is the upper layer side fin piece 410. It will be longer compared to the surrounding area. As a result, since the water corresponding to the volume expansion at the time of freezing is easily discharged, the unfreezed residual water W is reduced, and the freezing deformation is less likely to occur.

  According to the heat exchanger 5 of the present embodiment described above, the actions and effects shown in the following (1) to (3) can be obtained.

  (1) When the tube 30 has a longitudinal direction in the vertical direction as in the heat exchanger 5 of the present embodiment, the water-borne component of the heat exchanger 5 flows along the tube 30 downward in the vertical direction Or, it flows in the gap between the adjacent louver parts 43, 43 of the fin 40. Accordingly, water stagnates on the lower side in the vertical direction of the gap between the tubes 30. That is, water stagnates around the lower layer side fin piece 411. As a result, water does not easily stagnate around the upper layer side fin pieces 410, so that it is possible to suppress the occurrence of freezing deformation around the upper layer side fin pieces 410. Further, in the heat exchanger 5 of the present embodiment, the lower layer side fin pieces 411 disposed in the portion where water tends to stagnate have a structure in which freezing deformation is unlikely to occur, so the freezing deformation of the heat exchanger 5 is effective. Can be suppressed.

  (2) In the upper layer side fin piece 410 where water does not easily stay, the louver angle is larger than that of the lower layer side fin piece 411, so air easily flows. Therefore, in the upper layer side fin piece 410, the heat exchange performance of the heat exchanger 5 can be enhanced.

  (3) In the case of manufacturing the fins 40, first, after the louver portion 43 of the first louver angle θ1 is manufactured on a flat plate material which is a base material of the fins 40, a part of the louver portion 43 is The angle is deformed so as to be the second louver angle θ2. Thereafter, when the plate material is processed into a weave, the fins 40 of the present embodiment are completed. Therefore, the manufacture of the fin 40 is easy.

Second Embodiment
Next, a second embodiment of the heat exchanger 5 will be described with reference to FIG. Hereinafter, differences from the heat exchanger 5 of the first embodiment will be mainly described.

  As shown in FIG. 9, the heat exchanger 5 of the present embodiment is different from the heat exchanger 5 of the first embodiment in that the lower layer side fin pieces 411 do not have the louver portion 43. That is, the lower layer side fin piece 411 of this embodiment has a louverless structure.

  Even with such a structure, the second lower layer fins 411 and 411 adjacent to each other than the first distance L1 between the louver tip portions 43a and 43a of the upper upper layer fins 410 and 410 adjacent to each other. The distance L2 is longer. Therefore, compared with the part where the upper layer side fin piece 410 is arranged, the freeze deformation is less likely to occur in the part where the lower layer side fin piece 411 is arranged. Therefore, also with the heat exchanger 5 of the present embodiment, it is possible to obtain the actions and effects according to the above (1) and (2).

Third Embodiment
Next, a third embodiment of the heat exchanger 5 will be described with reference to FIG. Hereinafter, differences from the heat exchanger 5 of the first embodiment will be mainly described.

  As shown in FIG. 10, in the heat exchanger 5 of the present embodiment, the louver angle of each of the upper layer side fin piece 410 and the lower layer side fin piece 411 is set to the first louver angle θ1, but the upper layer side fin The intervals at which the louver portion 43 is formed are different between the piece 410 and the lower layer side fin piece 411. Specifically, assuming that the distance at which the louver portion 43 is formed in the upper layer side fin piece 410 is a first louver pitch P1, and the distance at which the louver portion 43 is formed in the lower layer side fin piece 411 is a second louver pitch P2: The second louver pitch P2 is shorter than the first louver pitch P1.

  Even with such a structure, the louvers of the lower layer side fins 411 and 411 adjacent to each other than the first distance L1 between the louver tip portions 43a and 43a of the upper layer side fins 410 and 410 adjacent to each other. The second distance L2 between the end portions 43a and 43a is longer. Therefore, compared with the part where the upper layer side fin piece 410 is arranged, the freeze deformation is less likely to occur in the part where the lower layer side fin piece 411 is arranged. Therefore, also with the heat exchanger 5 of the present embodiment, it is possible to obtain the actions and effects according to the above (1) and (2).

Fourth Embodiment
Next, a fourth embodiment of the heat exchanger 5 will be described with reference to FIG. Hereinafter, differences from the heat exchanger 5 of the first embodiment will be mainly described.

  As shown in FIG. 11, in the heat exchanger 5 of the present embodiment, the louver portion 43 of the lower layer fin 411 is disposed on the upper side in the vertical direction than the flat portion 42, and The lower louver portion 434 is disposed below the portion 42 in the vertical direction. The upper side louver portion 433 and the lower side louver portion 434 are arranged in parallel with the flat portion 42. Moreover, the upper layer side louver part 433 and the lower layer side louver part 434 are alternately arrange | positioned along the air flow direction.

  Even with such a structure, the louvers of the lower layer side fins 411 and 411 adjacent to each other than the first distance L1 between the louver tip portions 43a and 43a of the upper layer side fins 410 and 410 adjacent to each other. The second distance L2 between the end portions 43a and 43a is longer. Therefore, compared with the part where the upper layer side fin piece 410 is arranged, the freeze deformation is less likely to occur in the part where the lower layer side fin piece 411 is arranged. Therefore, also with the heat exchanger 5 of the present embodiment, it is possible to obtain the actions and effects according to the above (1) and (2).

Fifth Embodiment
Next, a fifth embodiment of the heat exchanger 5 will be described with reference to FIG. Hereinafter, differences from the heat exchanger 5 of the first embodiment will be mainly described.

  As shown in FIG. 12, the heat exchanger 5 of the present embodiment differs from the heat exchanger 5 of the first embodiment in that the louver portion 43 of the lower layer side fin piece 411 has a bent portion. Specifically, in the louver portion 43 of the lower layer side fin piece 411, the portion 43c located on the lower side in the vertical direction than the flat portion 42 is inclined at the first louver angle θ1, and the upper side in the vertical direction than the flat portion 42. The positioned portion 43d is inclined at the second louver angle θ2.

  Even with such a structure, the louvers of the lower layer side fins 411 and 411 adjacent to each other than the first distance L1 between the louver tip portions 43a and 43a of the upper layer side fins 410 and 410 adjacent to each other. The second distance L2 between the end portions 43a and 43a is longer. Therefore, compared with the part where the upper layer side fin piece 410 is arranged, the freeze deformation is less likely to occur in the part where the lower layer side fin piece 411 is arranged. Therefore, also with the heat exchanger 5 of the present embodiment, it is possible to obtain the actions and effects according to the above (1) and (2).

Sixth Embodiment
Next, a fifth embodiment of the heat exchanger 5 will be described with reference to FIG. Hereinafter, differences from the heat exchanger 5 of the first embodiment will be mainly described.

  As shown in FIG. 13, in the heat exchanger 5 of the present embodiment, a portion inclined at the first louver angle θ1 and an inclination at the second louver angle θ2 to the louver portion 43 of the lower layer side fin piece 411 There is a part that Specifically, the inner louver portion 435 disposed in the vicinity of the central portion 44 of the louver portion 43 of the lower layer side fin piece 411 is inclined with respect to the flat portion 42 at the second louver angle θ2. The outer louver portion 436 disposed outside the inner louver portion 435 is inclined with respect to the plane portion 42 at a first louver angle θ1. As a result, the lower layer side fin piece 411 sets the louver portion 43 of the plurality of louver portions 43 in which the distance between the louver tip portions 43a and 43a of the adjacent fin pieces 411 and 411 is set to the second distance L2. Have only a part of

  According to such a configuration, in addition to the actions and effects in accordance with the above (1) and (2), the actions and effects shown in the following (4) can be obtained.

  (4) As shown in FIG. 7, unfrozen residual water tends to remain in the central portion 44 of the fin piece 41. In this respect, in the present embodiment, the louver angle is set to the second louver angle θ2 in the inner louver portion 435 disposed near the center portion 44 of the fin piece 41 in which unfreeze residual water tends to remain, Unfreeze residual water hardly remains. Therefore, it is possible to effectively suppress the freezing deformation that occurs in the vicinity of the center portion 44 of the fin piece 41. In addition, since the louver angle of the outer louver portion 436 is set to the first louver angle θ1, air can easily pass through in this portion. Therefore, heat exchange performance can be improved as compared with the case where the louver angles of all the louver portions 43 of the lower layer side fin piece 411 are set to the second louver angle θ2.

Seventh Embodiment
Next, a seventh embodiment of the heat exchanger 5 will be described with reference to FIG. Hereinafter, differences from the first embodiment will be mainly described.

  As shown in FIG. 14, in the heat exchanger 5 of the present embodiment, the lower layer side fin piece 411 is a so-called flat fin, does not have the louver portion 43, and has a shape parallel to the horizontal direction have.

  Even with such a structure, the second lower layer fins 411 and 411 adjacent to each other than the first distance L1 between the louver tip portions 43a and 43a of the upper upper layer fins 410 and 410 adjacent to each other. The distance L2 is longer. Therefore, compared with the part where the upper layer side fin piece 410 is arranged, the freeze deformation is less likely to occur in the part where the lower layer side fin piece 411 is arranged. Therefore, also with the heat exchanger 5 of the present embodiment, it is possible to obtain the actions and effects according to the above (1) and (2).

Eighth Embodiment
Next, an eighth embodiment of the heat exchanger 5 will be described with reference to FIG. Hereinafter, differences from the heat exchanger 5 of the first embodiment will be mainly described.

  As shown in FIG. 15, in the heat exchanger 5 of the present embodiment, the upper layer side fin piece 410 and the lower layer side fin piece 411 are separate members.

  The configuration of the present embodiment is not limited to the heat exchanger 5 of the first embodiment, and the heat exchangers 5 of the second to seventh embodiments can be adopted.

  According to the heat exchanger 5 of the present embodiment, in addition to the actions and effects according to the above (1) and (2), the actions and effects shown in the following (5) can be obtained.

  (5) When manufacturing the fins 40, the upper layer side fin pieces 410 and the lower layer side fin pieces 411 having different shapes can be manufactured separately, so that manufacturing efficiency can be enhanced.

The Ninth Embodiment
Next, a ninth embodiment of the heat exchanger 5 will be described with reference to FIG. Hereinafter, differences from the heat exchanger 5 of the first embodiment will be mainly described.

  When the louver angle of the lower layer side fin piece 411 is set to a second louver angle θ2 smaller than the first louver angle θ1 of the upper layer side fin piece 410 as in the heat exchanger 5 of the first embodiment, the upper layer side fin Compared with the gap between the louver portions 43 and 43 of the piece 410, the gap between the louver portions 43 and 43 of the lower layer side fin piece 411 becomes narrower. This leads to a decrease in the drainage performance of water stagnating between the adjacent lower layer side fin pieces 411 and 411 and the tube 30, which may cause freezing deformation.

  Therefore, as shown in FIG. 16, the lower layer side fin piece 411 of the present embodiment has a drainage hole 45 instead of the entire flat portion 42 disposed in the central portion 44 thereof. The drainage hole 45 has a shape larger than the virtual inscribed circle C shown in FIG. The virtual inscribed circle C indicates a virtual circle inscribed in the adjacent lower layer side fin pieces 411 and 411 and the tube 30.

  The configuration of the present embodiment is not limited to the heat exchanger 5 of the first embodiment, and the heat exchangers 5 of the second to eighth embodiments can be adopted.

  According to the heat exchanger 5 of the present embodiment, in addition to the actions and effects according to the above (1) and (2), the actions and effects shown in the following (5) and (6) can be obtained .

  (5) The water remaining between the lower layer side fin pieces 411 and 411 and the tube 30 can be easily discharged from the drain hole 45, so that the freezing deformation can be suppressed.

  (6) The maximum value of the diameter of water staying between the adjacent lower layer side fin pieces 411 and 411 and the tube 30 is assumed to be approximately the same as the diameter of the virtual inscribed circle C. Therefore, by making the drainage hole 45 a shape larger than the virtual inscribed circle C shown in FIG. 4, water remaining between the adjacent lower layer side fin pieces 411 and 411 and the tube 30 is easily discharged.

Tenth Embodiment
Next, a tenth embodiment of the heat exchanger 5 will be described with reference to FIG. Hereinafter, differences from the heat exchanger 5 of the first embodiment will be mainly described.

  As shown in FIG. 17, in the tube 30 of the present embodiment, a drainage groove 32 for discharging water remaining between the lower layer side fin pieces 411 and 411 and the tube 30 adjacent to the side surface 31 in contact with the fin 40. Is equipped.

  The configuration of the present embodiment is not limited to the heat exchanger 5 of the first embodiment, and the heat exchangers 5 of the second to ninth embodiments can be adopted.

  According to the heat exchanger 5 of the present embodiment, it is possible to obtain the operation and the effect according to the above (1), (2) and (5).

Other Embodiments
The size of the drainage hole 45 of the ninth embodiment can be arbitrarily changed.

  In the lower layer side fin piece 411 of the ninth embodiment, the entire flat portion 42 disposed in the central portion 44 is the drainage hole 45. Instead of this, for example, as shown in FIG. A slit-like drainage hole 46 may be formed in part of the flat portion 42. Alternatively, as shown in FIG. 19, a plurality of fine drainage holes 47 may be formed in the flat portion 42 and the louver portion 43 of the lower layer side fin piece 411. Even if it is which structure of FIG.18 and FIG.19, since drainage property can be improved, freezing deformation can be suppressed. The point is that a drainage hole for draining water remaining between the adjacent lower layer fin pieces 411 and 411 and the tube 30 may be formed in the lower layer fin piece. Not only the lower layer side fin pieces 411 but also the upper layer side fin pieces 410 may have the same drainage holes 45, 46, 47, etc.

  -Although the tube 30 of each embodiment had a longitudinal direction in the perpendicular direction, the longitudinal direction of the tube 30 can be set arbitrarily if it is a direction intersecting the horizontal direction. That is, the heat exchanger 5 may have a structure in which the plurality of tubes 30 are disposed with a gap in the direction intersecting the vertical direction.

  -Heat exchanger 5 of each embodiment can be used not only as a heat pump system but as an arbitrary heat exchanger. In that case, the first fluid flowing inside the tube 30 is not limited to the working medium of the heat pump system, and an appropriate fluid can be used. Further, the second fluid flowing between the tubes 30, 30 is not limited to air, and an appropriate fluid can be used.

  The present invention is not limited to the above specific example. That is, to the above specific examples, those skilled in the art may appropriately modify the design as long as the features of the present invention are included in the scope of the present invention. For example, each element included in each specific example described above and its arrangement, material, conditions, shape, size, manufacturing method, and the like are not limited to those illustrated, and can be appropriately changed. Moreover, each element with which the above-mentioned embodiment is equipped can be combined as much as technically possible, and what combined these is also included in the scope of the present invention as long as the feature of the present invention is included.

5: Heat exchanger 30: Tube 32: Drain 40: Fin 41: Fin 42: Flat portion 43: Louver 45: Drain hole 410: Upper fin 411: Lower fin

Claims (11)

A heat exchanger (5) for exchanging heat between a first fluid and a second fluid, comprising:
A tube (30) having a longitudinal direction in a direction intersecting with the horizontal direction and being spaced apart from each other in the direction intersecting the vertical direction with a gap, the first fluid flowing inside;
And fins (40) disposed between adjacent tubes to promote heat exchange between the second fluid flowing between the tubes and the first fluid flowing inside the tubes.
The fins are
Consists corrugated fins have a plurality of fins pieces (41) arranged at regular intervals in the longitudinal direction of the tube,
The fin piece is
A flat plate portion (42),
A plurality of louver parts (43) cut and raised so as to be inclined with respect to the flat part;
In the fin, a fin piece disposed on the lower end side in the vertical direction is referred to as a lower layer side fin piece (411), and a fin piece disposed on the vertically upper side with respect to the lower layer side fin piece is referred to as an upper layer side fin piece (410). When
The fins have the same fin pitch in the portion where the upper layer side fin pieces are arranged and in the portion where the lower layer side fin pieces are arranged,
The second distance between the tips of the louver portions of the lower layer side fin pieces adjacent to each other than the first distance between the tip portions (43a) of the louver portions of the upper layer side fin pieces adjacent to each other Is long,
A heat exchanger characterized in that the temperature of the heat exchanger falls below the freezing point of water. In the upper layer side fin piece, an acute angle formed by the louver portion with the flat portion is defined as a first louver angle,
When the acute angle formed by the louver portion with the flat portion in the lower layer side fin piece is a second louver angle,
The heat exchanger according to claim 1, wherein the second louver angle is smaller than the first louver angle. An interval at which the louver portion is formed in the upper layer side fin piece is a first louver pitch,
When an interval at which the louver portion is formed in the lower layer side fin piece is a second louver pitch,
The heat exchanger according to claim 1, wherein the second louver pitch is shorter than the first louver pitch. The louver portion of the upper layer side fin piece is made of a flat plate-like member,
The heat exchanger according to claim 1, wherein the louver portion of the lower layer side fin piece is made of a member having a bent portion.   The lower layer side fin piece has a louver part in which the distance between the tips of the louver parts of the adjacent fin pieces is set to the second distance only in a part of the plurality of louver parts. The heat exchanger as described in any one of Claims 1-4. A heat exchanger (5) for exchanging heat between a first fluid and a second fluid, comprising:
A tube (30) having a longitudinal direction in a direction intersecting with the horizontal direction and being spaced apart from each other in the direction intersecting the vertical direction with a gap, the first fluid flowing inside;
And fins (40) disposed between adjacent tubes to promote heat exchange between the second fluid flowing between the tubes and the first fluid flowing inside the tubes.
The fins are
Consists corrugated fins have a plurality of fins pieces (41) arranged at regular intervals in the longitudinal direction of the tube,
In the fin, a fin piece disposed on the lower end side in the vertical direction is referred to as a lower layer side fin piece (411), and a fin piece disposed on the vertically upper side with respect to the lower layer side fin piece is referred to as an upper layer side fin piece (410). When
The fins have the same fin pitch in the portion where the upper layer side fin pieces are arranged and in the portion where the lower layer side fin pieces are arranged,
The upper layer fin piece is
A flat plate portion (42),
A plurality of louver parts (43) cut and raised so as to be inclined with respect to the flat part;
The lower side fin piece is
Having only the flat portion,
A heat exchanger characterized in that the temperature of the heat exchanger falls below the freezing point of water.   The heat exchanger according to any one of claims 1 to 6, wherein the upper layer side fin piece and the lower layer side fin piece are formed of the same member.   The heat exchanger according to any one of claims 1 to 6, wherein the upper layer side fin piece and the lower layer side fin piece are separate members.   The said lower layer side fin piece has a drainage hole (45) for discharging | emitting the water which stays between the said adjacent lower layer side fin piece and the said tube, The any one of Claims 1-8 characterized by the above-mentioned. Heat exchanger as described in.   The heat exchanger according to claim 9, wherein the drainage hole has a shape larger than a diameter of a virtual inscribed circle (C) inscribed in the adjacent lower layer side fin pieces and the tube.   The tube according to any one of claims 1 to 10, wherein the tube has a drain (32) for draining water remaining between the adjacent lower layer side fin pieces and the tube. Heat exchanger.

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