JP2011232028A - Heat exchanger and air conditioner with the same - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a compact heat exchanger or the like which is free from blocking of gaps between the fins thereof due to frost even if operated under a condition causing frost formation and which therefore has high heat exchange capacity.SOLUTION: A slit division region 4 is provided in a plate-shaped fin 1, slits 5 and 6 are provided on the plate-shaped fins 1 on both sides in a step direction of the slit division region 4, two pairs of slits 5 and 6 are formed in a flowing direction of gas, the first slits 5 and the second slits 6 are provided on an upstream side and on a downstream side in the flowing direction of gas, respectively, the first and second slits 5 and 6 are respectively constituted of upper division slits 5a and 6a and lower division slits 5b and 6b sandwiching the slit division region 4, and a nearly triangular cut-up portion 9 inclined in such a way that the downstream side thereof in the flowing direction of gas is the bottom side thereof is provided in the plate-shaped fin 1 of the slit division region 4, so that a bypass air passage flowing over the triangular cut-up 9 is formed upon frost formation.

Description

  The present invention relates to a heat exchanger and an air conditioner equipped with the heat exchanger, and more specifically, a fin tube type heat exchanger capable of improving the heat exchange capability of the heat exchanger under a low temperature condition. And an air conditioner equipped with this heat exchanger.

  In order to improve the heat exchanging ability, fins of the fin tube type heat exchanger are provided with a cut and raised portion called a slit by press working or the like. When there is no slit on the fin surface, a temperature boundary layer develops on the fin surface along the flow of a gas (for example, air) that exchanges heat with the fin, and heat exchange between the air and the fin is hindered. For this reason, a slit is provided on the fin surface, and the temperature boundary layer is divided and updated for each slit so that heat exchange between air and the fin is promoted.

  The slits provided on the fins of this fin-tube heat exchanger have a central slit formed at a position passing through the center line of the heat transfer tubes arranged above and below, and the height increases toward the upstream side of the central slit. And a pair of upstream slit portions (consisting of an upper slit portion and a lower slit portion) formed symmetrically in the vertical direction, and starting from a position lower than the central slit portion and becoming higher toward the downstream side, it becomes vertically symmetrical There is one constituted by a pair of formed downstream slit portions (consisting of an upper slit portion and a lower slit portion) (see, for example, Patent Document 1).

  In addition, slit-raised groups are formed on the front and back surfaces of the flat fins of the finned tube heat exchanger to turbulently flow the flowing air around the heat transfer tube to increase heat transfer efficiency. In order to reduce the blind spot flow area behind the heat transfer tube by mixing the gasified airflow, there is a louver-like cut-off formed in the middle of the slit-cut-up group (see, for example, Patent Document 2) ).

Japanese Patent Laid-Open No. 10-206085 (page 3 to page 4, FIGS. 6 to 7) JP-A-8-49870 (page 3, FIGS. 1 to 3)

  The fin-tube heat exchangers of Patent Literature 1 and Patent Literature 2 are used as a heat exchanger for an outdoor unit of an air conditioner under a low outdoor temperature condition where the outdoor temperature is about 2 ° C. or less. Condensed water adhering to the surface of the ice may freeze and form frost. In particular, a large amount of frost is formed near the slit having a high heat transfer coefficient, and the gap between the fins may be blocked by frost. For this reason, a slit could not be provided on the fin surface, and the heat exchange capability was reduced.

  Therefore, in order to improve the heat exchange capacity during normal operation (outdoor air temperature is about 0 ° C or higher), the heat exchanger itself can be enlarged or the fan speed can be increased to exchange heat with the heat exchanger. It was necessary to increase the air flow rate. However, in this case, there are problems such as an increase in the outdoor unit installation area, an increase in material cost of the finned tube heat exchanger, and an increase in noise due to an increase in fan power.

The present invention has been made to solve the above-described problems. Even when operating under conditions where frost formation occurs, the gap between the fins is not blocked by frost, and the heat exchange capacity is high and the heat is compact. The purpose is to provide an exchanger.
Moreover, it aims at providing the air conditioner with high heat exchange capability provided with this heat exchanger.

  The heat exchanger according to the present invention includes a plurality of plate-like fins stacked in parallel at a predetermined interval, through which gas passes, and a plurality of heat transfer tubes disposed through the plate-like fins in the stacking direction. The plate-like fin includes a slit division region in a column direction substantially parallel to the gas flow direction between the heat transfer tubes adjacent in the step direction, and the plate fins on both sides in the step direction of the slit division region. The plate-like fins are provided with slits, the slits are formed in two pairs in the gas flow direction, the first slit is provided on the upstream side in the gas flow direction, and the second slit is provided on the downstream side. Each of the first and second slits is composed of an upper divided slit and a lower divided slit across the slit divided region, and the plate-like fin in the slit divided region has a direction relative to the gas flow direction. under In which it raised substantially triangular cut inclined side as base is provided.

  Moreover, the air conditioner which concerns on this invention is equipped with said heat exchanger.

According to the present invention, the plate-like fin is provided with a slit dividing region, the plate-like fins on both sides in the step direction of the slit dividing region are provided with slits, and the slits are formed in two pairs in the gas flow direction. Are provided on the upstream side in the gas flow direction, the second slit is provided on the downstream side, and the first and second slits are respectively formed by an upper divided slit and a lower divided slit across the slit divided region. Because it is configured, frost is formed in the conventional heat exchanger, and even in an environment where the gaps between the fins are blocked by frost and cannot be used, air flow paths can be secured, so high heat exchange capability is maintained. Can do. For this reason, a heat exchanger with high heat exchange capability and a compact heat exchanger can be provided.
Further, since the plate-like fins in the slit dividing region are provided with a substantially triangular cut-out that is inclined with the downstream side as a base with respect to the gas flow direction, the triangular cut-over is overcome during frost formation. By providing a finned tube heat exchanger having a high heat exchanging capacity when frosting is formed, a large bypass airway can be secured by cutting and raising during the frosting operation. Can do.
Moreover, the air conditioner with high heat exchange capability using this heat exchanger can be provided.

It is a plane sectional view showing the important section of the fin tube type heat exchanger concerning Embodiment 1 of the present invention. It is a side view of FIG. It is II sectional drawing and II-II sectional drawing of the division | segmentation slit of FIG. It is the III-III sectional view and IV-IV sectional view of FIG. It is explanatory drawing of the air flow at the time of the normal driving | operation of the division | segmentation slit of FIG. It is explanatory drawing of the air flow at the time of the normal driving | operation of the louver of FIG. It is explanatory drawing of the air flow at the time of frosting operation | movement of the finned-tube type heat exchanger of FIG. It is III-III sectional drawing of FIG. It is sectional drawing which shows the principal part of the fin tube type heat exchanger which concerns on Embodiment 2 of this invention. It is sectional drawing which shows the principal part of the fin tube type heat exchanger which concerns on Embodiment 3 of this invention. It is sectional drawing which shows the principal part of the fin tube type heat exchanger which concerns on Embodiment 4 of this invention. It is III-III sectional drawing of FIG. It is explanatory drawing of the air flow at the time of the normal driving | running | working of the arc-shaped cut raising of FIG. It is explanatory drawing of the air flow at the time of the frosting operation | movement of the finned-tube type heat exchanger which concerns on Embodiment 4 of this invention. It is III-III sectional drawing of FIG. It is sectional drawing which shows the principal part of the finned-tube type heat exchanger which concerns on Embodiment 5 of this invention. It is IV-IV sectional drawing of FIG. It is VV sectional drawing of FIG. It is a schematic diagram which shows the refrigerating cycle which concerns on Embodiment 6 of this invention.

Embodiment 1 FIG.
1 and 2 showing the main part of the finned-tube heat exchanger according to Embodiment 1 of the present invention, the plurality of plate-like fins 1 are stacked in the stacking direction (front-rear direction) (the front-rear direction of the paper surface of FIG. They are stacked in parallel at a predetermined interval Fp (fin pitch) in the left-right direction in FIG. Further, the plurality of heat transfer tubes 2 (upper and lower heat transfer tubes 2a and 2b) are penetrated and held in the stacking direction A by fin collars 3 provided on the plate-like fins 1 so as to be stepped (vertical direction in the figure). They are arranged at predetermined intervals (in the vertical direction in FIGS. 1 and 2).

The plate-like fin 1 has a plate in the column direction (air flow direction) between the upper heat transfer tube 2a and the lower heat transfer tube 2b (in the left-right direction in FIG. 1, the front-rear direction in FIG. 2). A slit division region 4 having a width L1 that crosses the fin 1 is formed.
A pair of upper and lower divided slits are formed in contact with the slit divided region 4 on the upper and lower sides of the slit divided region 4 in the step direction b. Pairs are provided. A pair of these split slits is provided on the upstream side of the air flow direction a in the row direction C, and the other pair is provided on the downstream side, and the first split slit 5 (the upper split slit 5a and the lower split slit 5b). And a second divided slit 6 (consisting of a pair of an upper divided slit 6a and a lower divided slit 6b). And the 1st, 2nd division | segmentation slits 5 and 6 are located in the outer side of the area | region which connects the upper and lower heat exchanger tubes 2a and 2b.
Further, a louver 7 having a width narrower than the width of the region connecting the upper and lower heat transfer tubes 2a, 2b is formed at a substantially central portion in the row direction C in the slit division region 4.

  Thus, the first and second divided slits 5 and 6 are arranged opposite to the two locations in the column direction C with the louver 7 as the center, and the respective divided slits 5 and 6 pass through the slit divided region 4. It is divided into two vertically.

Next, the structure of the division | segmentation slit 5 and the louver 7 is explained in full detail.
FIG. 3 shows the cross section (II cross section and II-II cross section of FIG. 1) of the first and second divided slits 5a and 6a of the plate fin 1, and from the plate fin 1 to one surface. An air passage A is formed that includes leg portions 50a and 50b that are cut and raised toward the plate-like fin 1 and a cut-and-raised portion 50c that is parallel to the plate-like fin 1, and a front inlet portion 50d and a rear outlet portion. 50e is opened facing the air flow direction a.

  And the leg part 50a by the side of the slit division | segmentation area | region 4 of the upper division | segmentation slit 5a of the 1st division | segmentation slit 5 and the lower division | segmentation slit 5b is provided in parallel with the slit division | segmentation area | region 4, and the leg part 50b by the side of the heat exchanger tube 2 is transmitted. Inclined so as to face the central axis of the heat tube 2. Similarly, the leg portion 60a on the slit division region 4 side of the upper division slit 6a and the lower division slit 6b of the second division slit 6 is provided in parallel with the slit division region 4, and the leg portion on the heat transfer tube 2 side. Reference numeral 60b is provided to be inclined so as to face the central axis of the heat transfer tube 2.

  For this reason, the width of the front inlet portion 50d and the rear outlet portion 50e of the first split slit 5 on the upstream side is such that the opening of the rear outlet portion 50e is narrower than the front inlet portion 50d, and the second split portion on the downstream side. In the slit 6, the opening of the front inlet 50d is narrower than the rear outlet 50e. The front entrance 50d and the rear exit 50e of the first split slit 5 and the front entrance 60d and the rear exit 60e of the second split slit 6 are all parallel to the step direction b.

  4 shows a cross section of the louver 7 of the plate-like fin 1 (III-III cross-section and IV-IV cross-section of FIG. 1). Air passages B and C are formed, each of which includes a cut-and-raised portion 70a that is inclined downward toward the downstream side and foot portions 70b and 70c that are inclined to support the cut-and-raised portion 70a from both sides. C is open above and below the plate-like fin 1.

  That is, the foot portion 70b forms the upper air passage B together with the cut and raised portion 70a on the lower surface side upstream of the cut and raised portion 70a, and the foot portion 70c and the cut and raised portion 70a on the upper surface side downstream of the cut and raised portion 70a. A lower air passage C is formed. Thus, the air flow a from the upstream side is cut from the upper side of the plate-like fin 1 through the upper air passage B of the louver 7 and passes through the lower surface of the portion 70a and passes downward, and the plate-like fin b. 1 and the upper inclined flow c passing through the lower air passage C of the louver 7 and passing through the upper surface side of the raised portion 70a to the lower side. The cut-and-raised height H2 of the louver 7 is formed lower than the cut-and-raised height H1 of the first and second divided slits 5 and 6.

  Further, the front louver guide 7 a and the rear louver guide 7 b are cut and raised in parallel with the cut-and-raised portion 70 a of the louver 7 at the edge of the plate-like fin 1 positioned in front of and behind the louver 7. In this case, the front louver guide 7a is inclined downward and the rear louver guide 7b is inclined upward.

  The heat transfer tube 2 of the finned tube heat exchanger according to the present invention uses, for example, a metal pipe having an outer shape of 7 mm, 7.94 mm, or 9.52 mm. The diameter of the fin collar 3 into which the heat transfer tube 2 is inserted is 7.55 mm, 8.54 mm, 10.2 mm, or the like. The arrangement pitch of the heat transfer tubes 2 in the step direction B is set to 20.4 mm, 25.4 mm, or the like, for example. When a plurality of heat transfer tubes 2 are arranged in the row direction C, the pitch of the arrangement of the heat transfer tubes 2 in the stepwise direction B is set to 18 mm, 22 mm, etc. In addition, although the case where only one row of the heat transfer tubes 2 is arranged in the row direction C is shown in the present embodiment, two or more rows may be provided.

The operation of the finned tube heat exchanger according to the present embodiment configured as described above will be described.
5 and 6 show the air flow a during normal operation of the finned tube heat exchanger of FIG. 1 (the outdoor air temperature is about 0 ° C. or higher). In FIG. In the temperature boundary layer formed on the plate-like fin 1, since the cut-and-raised portions 50 c and 60 c of the first and second divided slits 5 and 6 are formed in parallel to the plate-like fin 1, the air is greatly disturbed. Without being divided and updated. Moreover, since the leg parts 50b and 60b located in the side of the heat exchanger tube 2 of the division | segmentation slits 5 and 6 incline so that the heat exchanger tube 2 may be opposed, let the air flow a be the flow along the heat exchanger tube 2. Can do. For this reason, the heat transfer fall by the dead water area | region (speed defect | deletion area | region) which generate | occur | produces behind the heat exchanger tube 2 can be prevented.
Further, in FIG. 6, the air flow a flowing in from the windward side is perpendicular to the plate-like fin 1 because the cut-and-raised portion 70 a of the louver 7 is inclined with respect to the plate-like fin 1. The temperature boundary layer is agitated by adding components, increasing the flow velocity, and disturbing the flow.
Thus, it is possible to provide a finned tube heat exchanger having a high heat exchange capability during normal operation.

  7 and 8 show the air flow when the finned tube heat exchanger of FIG. 1 is frosted. When operating under conditions where frost formation occurs at an outdoor air temperature of about 2 degrees or less, Frost begins to adhere from the upstream end of the air flow a of the first and second split slits 5 and 6 and the louver 7 having a high exchange capacity. Then, the frost adhering to the 1st, 2nd division | segmentation slits 5 and 6 and the louver 7 grows, and in the vicinity of the 1st and 2nd division | segmentation slits 5 and 6, between adjacent plate-like fins 1 by frost formation. Block. However, since the slit-shaped region 4 is provided in the plate-like fin 1, an air bypass air passage (air flow a) is secured in the slit-divided region 4, and an increase in ventilation resistance can be suppressed.

  Further, the cut-and-raised height H2 of the louver 7 is lower than the height H1 of the first and second divided slits 5 and 6, and the louver 7 is cut and raised in an inclined manner with respect to the plate fin 1. Since the air path D (see FIG. 2) at the upper part of the cut and raised portion 70a can be secured largely, the bypass air path D (air flow path d) at the upper part of the cut and raised part can be secured, and the ventilation resistance is increased. Can be suppressed. Further, in normal operation (see FIG. 6), the louver 7 is formed to be inclined downward with respect to the plate-like fin 1, and the flow velocity is increased and the flow is disturbed. 8) Frost 8 adheres to the front entrance portion 70d of the louver 7 and the space between the louver 7 and the plate-like fin 1 is blocked, so that the air flow a flows over the louver 7 (air flow d And the increase in ventilation resistance can be suppressed. Therefore, even when the fin tube type heat exchanger is operated under conditions where frost formation occurs, it is possible to prevent the fins 1 from being blocked by frost, and the fin tube type heat exchange has a high heat exchange capability and is compact. Can be provided.

Here, the height of the division slit 5 and the louver 7 will be described.
As shown in FIG. 2, it is desirable that the cut-and-raised height H1 of the divided slits 5 and 6 is about ½ of the fin pitch Fp. Since the air flow a of the finned tube heat exchanger is a developmental flow of the boundary layer between the plate-like fins 1, by setting the boundary layer velocity to the half height of the fin pitch Fp having the largest velocity, Heat exchange capability can be increased. On the other hand, the cut-and-raised height H2 of the louver 7 is desirably about 1/3 of the fin pitch Fp. When the split slits 5 and 6 are closed during frost formation, air concentrates on the louver 7, and therefore when the cut-and-raised height H <b> 2 of the louver 7 is increased, the bypass air passage D that flows above the louver 7 is changed. Ventilation resistance increases because it cannot be secured. However, if the cut-and-raised height H2 of the louver 7 is smaller than 1/3 of the fin pitch Fp, the heat transfer performance during normal operation is reduced. Further, if a slit is installed in the divided region 4 instead of the louver 7 to cut and raise the height, the heat transfer performance during normal operation deteriorates. By using the louver 7, the flow is disturbed compared to the slit and the heat transfer performance becomes higher. Therefore, even if the height H2 of the louver 7 is about 1/3 of the fin pitch Fp, the heat is sufficiently heated. It is possible to provide a finned tube heat exchanger having a high exchange capacity.

  Moreover, the finned tube heat exchanger according to the present invention is very useful for reducing material costs. In general, the heat exchange capacity of the fin-tube heat exchanger is inversely proportional to the fin pitch Fp, which is the distance between the fins. Therefore, by using the finned tube heat exchanger according to the present embodiment having a high heat exchanging capability, the fin pitch Fp can be increased, and the number of plate-like fins 1 can be reduced and the finned tube heat exchanger. The material cost can be reduced. By using this finned tube heat exchanger having a high heat exchange capability, noise due to increased fan power can be prevented.

  Furthermore, the finned tube heat exchanger according to the present invention is used as an outdoor heat exchanger. In the manufacturing process of the outdoor heat exchanger, after expanding the heat exchanger, it is bent into an L shape and a U shape to prepare for the outdoor unit. At that time, when the buckling strength is weak with respect to the load applied to the plate-like fins 1 in the row direction, the plate-like fins 1 fall down, the amount of air flowing between the plate-like fins 1 is reduced, and the heat exchange capability is increased. It will decline. Furthermore, the appearance is impaired and a problem occurs in the design. In the case of the present invention, by installing the louver 7 that is obliquely cut and raised in the fin central portion where the load applied in the row direction is most concentrated, the buckling strength can be improved, the fin collapse does not occur, It is possible to provide an outdoor heat exchanger that has no problem in terms of design.

Embodiment 2. FIG.
FIG. 9 is a cross-sectional view showing a main part of a finned tube heat exchanger according to Embodiment 2 of the present invention.
In the present embodiment, the upstream first split slit 5 has a front entrance 50d wider than the rear exit 50e, and the downstream second split slit 6 has a front entrance 60d wider than the front entrance 60d. Also, the width of the rear outlet 60e is widened. The first dividing slit 5 has an upper and lower dividing slits 5a and 5b, and the leg portions 50a and 50b have a C-shape that narrows to the downstream side. The upper and lower divided slits 6 have both upper and lower divided slits 6a and 6b that have leg portions 60a and 60b that extend toward the downstream side, and the narrow sides of the openings are oriented inside the row direction C of the plate-like fins 1. I have to do it.
Other configurations are the same as in the case of the first embodiment, and thus description thereof is omitted.

  In this way, by guiding the air flow to the outside of the louver 7 in the stepwise direction, it is possible to secure a larger bypass air path D during frosting than in the first embodiment, and to reduce the ventilation resistance during frosting. Can be reduced.

Embodiment 3 FIG.
FIG. 10 is a cross-sectional view of an essential part of a finned tube heat exchanger according to Embodiment 3 of the present invention.
In this embodiment, the leg portions 50a, 50b, 60a, 60b of the first and second divided slits 5, 6 are divided into the slit divided region 4 side (leg portions 50a, 60a) and the heat transfer tube 2 side (leg portion 50b). , 60b) and the heat transfer tube 2 are both inclined and oriented. That is, the first split slit 5 has the upper split slit 5a and the lower split slit 5b whose legs 50a and 50b are inclined in parallel toward the downstream side of the slit split region 4, and the second split slit 6 has an upper split. Both the leg portions 60 a and 60 b of the slit 6 a and the lower divided slit 6 b are inclined in parallel toward the upstream side of the slit divided region 4.
Other configurations are the same as in the case of the first embodiment, and thus description thereof is omitted.

  In the present embodiment, both the leg portions 50a and 50b of the first divided slit 5 are inclined in parallel toward the downstream side of the slit divided region 4, and both the leg portions 60a and 60b of the second divided slit 6 are provided. Since it is made to incline in parallel toward the upstream side of the slit dividing region 4, the air flow can be concentrated on the louver 7 side, and the air flow can be further promoted through the louver 7 during normal operation. It is possible to provide a finned tube heat exchanger having a high heat exchange capability.

Embodiment 4 FIG.
FIG. 11: is sectional drawing which shows the principal part of the fin tube type heat exchanger which concerns on Embodiment 4 of this invention.
In the present embodiment, a substantially triangular cut-and-raised portion 9 is provided to be inclined with respect to the plate-like fin 1 in the vicinity of the central portion of the fin divided region 4 in the column direction C (see FIG. 12). The cut-and-raised portion 9 has a substantially triangular shape extending from the upstream side to the downstream side and spreading on both sides. Both edges have an arc shape and are cut and raised at right angles to the air flow direction on the base 9a side (bottom side). The part 9b stands on the upstream side.
In this case, the height H3 of the cut-and-raised tip portion of the cut-and-raised portion 9 is lower than the cut-and-raised height H1 of the divided slits 5 and 6.
Other configurations are the same as in the case of the first embodiment, and thus description thereof is omitted.

During normal operation, as shown in FIG. 13, the air flow a is cut and raised to generate a vertical vortex behind its upper surface, which can stir the temperature boundary layer and improve heat transfer performance.
In the frosting operation, as shown in FIGS. 14 and 15, since the area of the cut and raised 9 is smaller than the louver 7 (see the first to third embodiments), the bypass air passage D (see FIG. 2) can be ensured larger, and a finned tube heat exchanger having a high heat exchange capability during frost formation can be provided.

Embodiment 5 FIG.
FIG. 16: is sectional drawing which shows the principal part of the fin tube type heat exchanger which concerns on Embodiment 5 of this invention.
Convex portions 10 formed by press working in parallel with the stepwise direction B are provided on both side edge portions (both side edge portions in the row direction C) of the plate fin 1 (see FIG. 17). The convex portion 10 is formed to have a predetermined length in the stepwise direction B on the surface of the plate-like fin 1, for example, a length from the upper side to the lower side of the first and second divided slits 5 and 6. It is formed to protrude in a triangular cross section. The cross-sectional shape is not limited to a triangular shape, and may be an arc shape, for example.
Further, embosses 11 formed by pressing are provided before and after the row direction C of the fin collar 3 (see FIG. 18), and ripples 12 are provided at fin edges on the line connecting the embosses 11, respectively. ing.
Other configurations are the same as in the case of the first embodiment, and thus description thereof is omitted.

  In the finned tube heat exchanger configured as described above, since the convex portions 10 are provided on both side edges of the plate-like fin 1, it is possible to increase the bending strength of the plate-like fin 1 and reduce the deflection. it can. For this reason, the lamination | stacking process of the plate-shaped fin 1 can be sped up, and the manufacturing efficiency of a heat exchanger increases. Even if a bending moment is applied from the outside, the ratio between the slit height H1 of the divided slits 5 and 6 and the fin pitch Fp of the plate fin 1 and the width L1 of the slit divided region 4 and the adjacent fin collar 3 The ratio L1 / L2 with respect to the distance L2 can be maintained at the setting condition at the time of assembly, and the heat exchange capability of the finned tube heat exchanger can be maintained.

  In addition, since the emboss 11 is provided, the load applied around the fin collar 3 is dispersed even in the L-shaped bending of the heat exchanger. Further, since the ripple 12 is provided, the area to be grounded to the jig of the L-shaped bending machine can be increased and the bending load can be reduced. Therefore, the bending strength is larger than that in the first embodiment, and the fin collapse occurs. Without, it can provide the fin tube type heat exchanger with high heat exchange capability.

Embodiment 6 FIG.
FIG. 19 is a schematic diagram showing a refrigeration cycle in which the finned tube heat exchanger according to any one of Embodiments 1 to 5 of the present invention is used as the outdoor heat exchanger 20.
As shown in FIG. 19, in the refrigeration cycle, a compressor 21, a four-way valve 22, an indoor heat exchanger 23, an expansion valve 24, and an outdoor heat exchanger 20 (fin tube heat exchanger) are sequentially connected by refrigerant piping. Has been.

  During heating, the refrigerant flows in the direction indicated by the arrow (solid line). The refrigerant in the gas state compressed by the compressor 21 passes through the four-way valve 22 and enters the indoor heat exchanger 23. The indoor heat exchanger 23 radiates heat by exchanging heat with air sent from the blower 25. The refrigerant that has exchanged heat with the indoor heat exchanger 23 becomes a supercooled liquid refrigerant and enters the expansion valve 24. The low-temperature and low-pressure refrigerant expanded by the expansion valve 24 enters a two-phase state with a low dryness, and enters the outdoor heat exchanger 20 (fin tube heat exchanger). The outdoor heat exchanger 20 (fin tube heat exchanger) absorbs heat by exchanging heat with air sent from the blower 26. The refrigerant that has absorbed heat by heat exchange with the outdoor air in the outdoor heat exchanger 20 (fin tube heat exchanger) evaporates into a gas state and enters the compressor 21.

Thus, since the fin tube type heat exchanger in any one of Embodiments 1-5 was used for the outdoor heat exchanger 20, the refrigerating cycle provided with the fin tube type heat exchanger which has said each characteristic was used. Can be provided.
Moreover, the finned tube heat exchanger according to any one of the first to fifth embodiments can be used not only as the outdoor heat exchanger 20 but also as the indoor heat exchanger 23.
In addition, the indoor heat exchanger 23 may use the fin tube type heat exchanger etc. which are conventionally used.

  1 plate fins, 2, 2a, 2b heat transfer tubes, 3 fin collars, 4 slit divided regions, 5, 6 first and second divided slits (first and second slits), 5a, 6a upper divided slits, 5b, 6b Lower split slit, 7 louvers, 7a, 7b Louver guide, 8 frost, 9 Triangular cut and raised, 10 Convex, 11 Embossed, 12 Ripple, 20 Outdoor heat exchanger (fin tube heat exchanger) , 21 Compressor, 22 Four-way valve, 23 Indoor heat exchanger, 24 Expansion valve, 25, 26 Fan, 50a, 50b First split slit leg part, 50d, 60d Front inlet part (slit inlet part), 50e, 60e Rear outlet part (slit outlet part), 60a, 60b Leg part of second split slit, 70a Louver cut and raised part, 70b, 70c Louver cut Leg of a raising part, a Air flow direction (gas flow direction), b lower inclined flow, c upper inclined flow, A air passage, B upper air passage, C lower air passage, Fp fin pitch, H1 slit Cut-and-raised height, H2 Cut-and-raised height of louver, H3 Arc-shaped raised and raised height, L1 Width of slit division area.

Claims (11)

A plurality of plate-like fins stacked in parallel at a predetermined interval, through which gas passes;
A plurality of heat transfer tubes disposed through the plate fins in the stacking direction;
The plate-like fin includes slit division regions in a column direction substantially parallel to the gas flow direction between the heat transfer tubes adjacent in the step direction, and the plate-like fins on both sides of the slit division region in the step direction are provided. A slit is provided,
The slits are formed in two pairs in the gas flow direction, the first slit is provided on the upstream side in the gas flow direction, the second slit is provided on the downstream side, and the first and second slits are respectively provided. It consists of an upper division slit and a lower division slit across the slit division area,
The plate-shaped fin in the slit dividing region is provided with a substantially triangular cut-and-raised portion that is inclined with the downstream side as a base with respect to the gas flow direction.   The heat exchanger according to claim 1, wherein the cut and raised height of the cut and raised is lower than the cut and raised height of the slit.   The leg portions of the upper and lower divided slits of the first and second slits are provided in parallel with the slit divided region side, and the leg portion on the heat transfer tube side is provided on the heat transfer tube. The heat exchanger according to claim 1, wherein the heat exchanger is provided so as to be opposed to each other.   The upper part of the first slit and the leg part of the lower dividing slit are formed in a C shape narrowing to the downstream side, and the upper part of the second slit and the leg part of the lower dividing slit are formed in a C shape extending to the downstream side. The heat exchanger according to claim 1 or 2, wherein the heat exchanger is made.   The legs of the upper and lower slits of the first slit both incline parallel to the downstream side of the slit division area, and the legs of the upper and lower division slits are both upstream of the slit division area. The heat exchanger according to claim 1, wherein the heat exchanger is inclined in parallel with the heat exchanger.   The first and second slits are located close to and outside of the region connecting adjacent heat transfer tubes, and the cut and raised are positioned approximately at the center in the region connecting adjacent heat transfer tubes. The heat exchanger in any one of Claims 1-5.   The heat exchanger according to any one of claims 1 to 6, wherein a convex portion is provided at a side edge portion of the plate-like fin substantially orthogonal to the air flow direction.   The heat exchanger according to claim 1, wherein convex embosses are provided before and after the fin collar portion of the plate-like fin.   The heat exchanger according to claim 1, wherein a ripple is provided on a side edge portion of the plate-like fin.   An air conditioner using the heat exchanger according to any one of claims 1 to 9.   The air conditioner according to claim 10, wherein the heat exchanger is used as an outdoor heat exchanger.

Images