JP2017096588A - Air conditioner - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide an air conditioner which achieves high quietness by suppressing blade pitch noise while holding high air conditioning performance, and which sufficiently takes treatment of dew condensation water into account.SOLUTION: An air conditioner includes a cross flow fan, a first heat exchanger and a second heat exchanger. The first heat exchanger and the second heat exchanger are arranged in a substantially Λ-shape by having a contact part almost coming into contact. A top surface of the first heat exchanger and a top surface of the second heat exchanger are arranged substantially on the same plane. Thereby, miniaturization of indoor unit height is achieved, and as the side facing a flow passage of the heat exchanger is not shielded, a dead water region in the flow passage can be suppressed. Also, as the dew condensation water attaches to the heat exchanger, the air conditioner can be provided which can treat the dew condensation water in the same manner as a normal cooling operation.SELECTED DRAWING: Figure 2

Description

  The present invention relates to an air conditioner used for air conditioning of a house or the like, and particularly relates to an air conditioner including an indoor unit that achieves both downsizing and high performance.

  As customer demands for air conditioners diversify, there is a growing demand for compatibility between the downsizing of indoor units in the height direction and higher performance in order to improve installation.

  Therefore, as an indoor unit of a conventional air conditioner, two heat exchangers are arranged in a C shape before and after the crossflow fan, and flat spacers are installed at both ends of the upper and lower heat exchangers. A configuration has been devised (for example, Patent Document 1).

  The configuration will be described below with reference to FIG.

  In FIG. 10, the indoor unit includes a cross flow fan 105 and a heat exchanger 106. The heat exchanger 106 includes a first heat exchanger 106 a disposed in front of the cross flow fan 105 and a second heat exchanger 106 b disposed in the rear. Further, a part of the cross flow fan 105 is opposed to the front side of the cross flow fan 105 and the downstream part of the cross flow fan 105 is partly opposed to a part of the cross flow fan 105. And a rear guider 109 extending downstream of 105. Furthermore, a flat spacer 31 is provided which is installed at the upper end of the first heat exchanger 106a and the second heat exchanger 106b and blocks the upper side of the heat exchanger 106 from the cross flow fan 105 side. ing.

  In this indoor unit, by disposing the heat exchanger 106 at the front and back, while maintaining high performance as an air conditioner, the distance between the upper part of the heat exchanger 106 and the cross flow fan 105 is shortened, and the height of the indoor unit is increased. Can be miniaturized.

  Further, instead of the flat spacer 31, an indoor unit including an upper airflow guide whose cross-sectional shape is a substantially triangular shape convex toward the cross flow fan 105 side has been devised.

  In this indoor unit, the dead water area 41 generated below the flat spacer 31 can be reduced. For this reason, the air flow is disturbed and the air blowing performance is deteriorated, or the locally generated air flow having a high flow velocity and the air flow having a low flow velocity flow into the cross-flow fan 105, and the blade pitch sound is generated. Can be prevented from occurring.

Japanese Patent Laid-Open No. 10-227470

  However, the configuration of the conventional indoor unit has several problems. The problem will be described below with reference to FIG.

As shown in FIG. 11, when the flat spacer 31 is provided, it is a region where air does not flow between the first heat exchanger 106 a and the second heat exchanger 106 b and the cross flow fan 105. A dead water area 41 is generated. The dead water area 41 has an inverted triangular shape that protrudes in the direction of flowing into the cross flow fan 105, that is, protrudes downward.

  Due to the influence of the dead water area 41, the air blowing performance deteriorates, and the blades of the cross flow fan 105 rotate in an area where the air flow velocity is nonuniform, so that there is a problem that blade pitch noise is likely to occur.

  Further, when an upper airflow guide (not shown) having a substantially triangular cross section is provided, the dead water area is reduced, but the dead water area is not completely removed. For this reason, there exists a subject that a wing pitch sound is easy to generate | occur | produce under the influence of the still remaining dead water area.

  Further, the flow of air that has passed through the first heat exchanger 106a and the second heat exchanger 106b near the lower end of the upper airflow guide, that is, in the vicinity of the portion of the upper airflow guide that is closest to the cross flow fan 105. Since the air flow that has passed through the airflow merges, a turbulent flow is generated in the vicinity of the cross flow fan 105, and there is also a problem that blade pitch noise is likely to occur.

  Furthermore, during the cooling operation of the air conditioner, heat from the heat exchanger 106 serving as an evaporator propagates to the flat spacer 31 and the upper airflow guide. For this reason, water droplets due to condensation can occur on either the cooled flat spacer 31 or the front and back surfaces of the upper airflow guide. If this condensed water is not properly treated, it may drop onto the cross flow fan 105 and be blown into the room together with air.

  In order to solve the above-described conventional problems, an air conditioner of the present invention is provided with a cross flow fan, a front row side of the rotation shaft of the cross flow fan, a predetermined row pitch in the main flow direction of air, and an air A first heat exchanger in which a plurality of heat transfer tubes are arranged at a predetermined step pitch in a direction perpendicular to the main flow direction, and a back side of the rotation shaft of the cross flow fan, and in the main flow direction of air A second heat exchanger having a predetermined row pitch and a plurality of heat transfer tubes arranged at a predetermined step pitch in a direction perpendicular to the main flow direction of air, the first heat exchanger and the second heat exchanger Any one of the heat exchangers has a contact portion that substantially contacts the other, and the first heat exchanger and the second heat exchanger are arranged in a substantially Λ shape, The top surface of the first heat exchanger and the top surface of the second heat exchanger are arranged in substantially the same plane. It is characterized in that it has been.

  Alternatively, a plurality of crossflow fans and a plurality of crossflow fans provided on the front side of the rotation axis of the crossflow fan, with a predetermined row pitch in the main air flow direction and a predetermined step pitch in a direction perpendicular to the main air flow direction. The first heat exchanger in which the heat transfer tubes are arranged, and the rotation axis of the cross flow fan, provided on the back side, predetermined row pitch in the main air flow direction, and predetermined in the direction perpendicular to the main air flow direction And a second heat exchanger in which a plurality of heat transfer tubes are arranged, and the first heat exchanger and the second heat exchanger are substantially in contact with each other in a substantially Λ shape. In the first heat exchanger, an angle α1 formed between a top surface and a surface facing the cross flow fan in the first heat exchanger, and a top surface and the cross flow fan in the second heat exchanger. The angle α2 made with the surface to be cut is both an acute angle It is an feature.

  This realizes high heat exchange performance by arranging the heat exchanger before and after the cross flow fan and high air blowing performance by suppressing dead water area in the flow path while realizing downsizing of the indoor unit height. And a high-performance air conditioner.

  Moreover, the air conditioner which suppressed generation | occurrence | production of the blade pitch sound by preventing generation | occurrence | production of a dead water area and generation | occurrence | production of the turbulent flow in the crossflow fan vicinity can be provided.

  In addition, an air conditioner that fully considers the treatment of condensed water can be provided.

  The air conditioner of the present invention can provide an air conditioner that achieves downsizing while achieving high air conditioning performance.

The perspective view of the air conditioner in Embodiment 1 of this invention The cross section of the air conditioner in Embodiment 1 of this invention The figure which shows the structure of the heat exchanger in Embodiment 1 of this invention. The principal part enlarged view of the heat exchanger in Embodiment 1 of this invention. The figure which shows typically the streamline near the top | upper surface part of the heat exchanger in Embodiment 1 of this invention. The figure which shows the state before the cutting | disconnection of the fin in Embodiment 1 of this invention. The principal part enlarged view of the heat exchanger in Embodiment 2 of this invention. The figure which shows the state before the cutting | disconnection of the fin in Embodiment 2 of this invention. The figure which shows the state before the process of the heat exchanger in Embodiment 2 of this invention. Cross-sectional view of an indoor unit of a conventional air conditioner The figure which shows typically the streamline of the upper part vicinity of the heat exchanger in the indoor unit of the conventional air conditioner

  The first aspect of the present invention is a cross flow fan, provided on the front side of the rotation shaft of the cross flow fan, a predetermined row pitch in the main flow direction of air, and a predetermined step pitch in a direction perpendicular to the main flow direction of air The first heat exchanger in which a plurality of heat transfer tubes are arranged, and provided on the back side from the rotating shaft of the cross flow fan, and has a predetermined row pitch in the main air flow direction and perpendicular to the main air flow direction. And a second heat exchanger in which a plurality of heat transfer tubes are arranged at a predetermined step pitch in any direction, and one of the first heat exchanger and the second heat exchanger is The first heat exchanger and the second heat exchanger are arranged in a substantially Λ shape, the top surface of the first heat exchanger and the top surface of the first heat exchanger The top surface of the second heat exchanger is arranged substantially in the same plane.

  As a result, the downside of the indoor unit height is realized, and the side facing the flow path of the heat exchanger is not shielded, so that the dead water area in the flow path can be suppressed, and the dew condensation water is used as the heat exchanger. Therefore, it is possible to provide an air conditioner that can treat the dew condensation water in the same manner as a normal cooling operation.

  According to a second invention, in the first invention, the same plane on which the top surface of the first heat exchanger and the top surface of the second heat exchanger are arranged is substantially horizontal.

  Thereby, a bigger heat exchanger can be arrange | positioned in the indoor unit of the same dimension, and a high performance air conditioner can be provided.

According to a third aspect of the present invention, there is provided a cross-flow fan and a predetermined row pitch provided in front of the cross-flow fan's rotating shaft, and a predetermined step pitch in a direction perpendicular to the main air flow direction. The first heat exchanger in which a plurality of heat transfer tubes are arranged, and provided on the back side from the rotating shaft of the cross flow fan, and has a predetermined row pitch in the main air flow direction and perpendicular to the main air flow direction. And a second heat exchanger in which a plurality of heat transfer tubes are arranged at a predetermined step pitch in a certain direction, and the first heat exchanger and the second heat exchanger are substantially in contact with each other. In the first heat exchanger, an angle α1 formed between the top surface and the surface facing the cross flow fan, and in the second heat exchanger, the top surface and the cross The angle α2 formed by the surface facing the flow fan is an acute angle. It is intended.

  As a result, a larger heat exchanger can be arranged within the limited indoor unit dimensions, so that both the high performance and the downsizing of the indoor unit height are compatible, while the side facing the heat exchanger channel is shielded. Therefore, the dead water area in the flow path can be suppressed, and the condensed water adheres to the heat exchanger. Therefore, it is possible to provide an air conditioner that can treat the condensed water in the same manner as in a normal cooling operation. it can.

  According to a fourth invention, in the third invention, the α1 and the α2 satisfy a relationship of 40 ° ≦ α1 ≦ 60 ° and 40 ° ≦ α2 ≦ 60 °.

  Thereby, it is possible to provide an air conditioner that realizes downsizing of the indoor unit height and takes into consideration the drainage of the condensed water adhering to the heat exchanger.

  According to a fifth invention, in any one of the first to fourth inventions, the closest distance between the heat transfer tube constituting the first heat exchanger and the heat transfer tube constituting the second heat exchanger is The step pitch of the first heat exchanger and the step pitch of the second heat exchanger, whichever is greater, are equal to or less.

  In the vicinity of the abutting portion where the first heat exchanger and the second heat exchanger substantially abut, the thickness of the heat exchanger in the main flow direction of air (that is, in the column direction) is other than that. Although the thickness is comparatively thin, since the heat transfer tubes having the closest distance below the step pitch are arranged, the flow of air flowing into the flow path can be made more uniform.

  According to a sixth invention, in any one of the first to fifth inventions, in the first heat exchanger, an angle β1 formed by a surface facing the cross flow fan and a vertical surface, and the second heat In the exchanger, an angle β2 formed by a surface facing the cross flow fan and a vertical surface is substantially the same.

  As the inclination angles β1 and β2 of the heat exchanger are increased, the height of the indoor unit can be reduced. Therefore, by setting β1 and β2 to the same maximum angle that causes no problem in the treatment of condensed water, A more compact air conditioner can be provided while considering water.

  According to a seventh invention, in any one of the first to sixth inventions, the fin having a plurality of through-holes laminated in a substantially rectangular short-side direction and a long-side direction at a predetermined interval; A heat exchanger tube inserted into the through-hole and a notch that is recessed from one end to the other end in the short-side direction, a substantially flat heat exchanger that is cut at the tip of the notch, A first heat exchanger and a second heat exchanger are formed.

  Since the first heat exchanger and the second heat exchanger are manufactured with an integral fin material, the productivity is increased, so that a lower-cost air conditioner can be provided.

  According to an eighth aspect of the present invention, in the seventh aspect of the present invention, a protrusion that is cut when the first heat exchanger and the second heat exchanger are cut is provided on a distal end side of the notch, The protrusion is bent in a direction substantially parallel to the top surface, and the first heat exchanger and the second heat exchanger are located in the vicinity of the first contact with the first heat exchanger. A sealing portion that partially seals between at least one fin of the second heat exchanger is formed.

In the vicinity of the abutting portion where the first heat exchanger and the second heat exchanger substantially abut, the thickness of the heat exchanger in the main air flow direction (that is, the column direction) is other than that. Air that is not sufficiently heat-exchanged may flow into the flow path because it is thinner than the above, but by tilting the fin, it can be adjusted in the direction to increase the ventilation resistance appropriately. Can be prevented.

  Further, since the fin is a part of the heat exchanger, the necessary ventilation resistance can be adjusted at a low cost, and further, the ventilation resistance is provided on the upstream side when viewed from the main flow direction of the air of the heat exchanger. The occurrence of dead water areas in the flow path can be reduced.

  Hereinafter, embodiments of the present invention will be described with reference to the drawings. Note that the present invention is not limited to the present embodiment.

(Embodiment 1)
FIG. 1 is a perspective view of an indoor unit of an air conditioner according to Embodiment 1 of the present invention. FIG. 2 is a cross-sectional view of the indoor unit (a cross-sectional view in a plane perpendicular to the rotation axis direction of the cross flow fan). In this specification, the left side of FIG. 2 is described as the front side or the front side, the left side is the back side or the rear side, the upper side is the top side or the upper side, the lower side is the lower side, and the depth direction is the left-right direction.

  As shown in FIGS. 1 and 2, the indoor unit 1 of the air conditioner in the present embodiment includes a housing 2 and a front cover 3 attached to the front of the housing 2. A suction port 4 is provided from the top of the housing 2 to the front surface. The front of the suction port 4 is covered with a front cover 3.

  The suction port 4 is provided with a plurality of vertical bars and horizontal bars that constitute a part of the housing 2. These bars form a suction grill 4a.

  Inside the housing 2, there are a cross flow fan 5 for taking indoor air into the housing 2 from the suction port 4 and a heat exchanger 6 for exchanging heat from the air blown from the cross flow fan 5. Are provided.

  The cross flow fan 5 includes a rotation shaft that extends in the longitudinal direction of the housing 2 (left and right direction in FIG. 1).

  The heat exchanger 6 is mainly composed of a first heat exchanger 6a and a second heat exchanger 6b. The first heat exchanger 6 a is a heat exchanger provided on the front side from the rotation axis of the cross flow fan 5, and the second heat exchanger 6 b is provided on the back side from the rotation axis of the cross flow fan 5. Heat exchanger.

  The first heat exchanger 6a is a heat exchanger having a substantially U-shaped cross section on the vertical surface of the casing 2 in the longitudinal direction, and is arranged from the front to the top of the cross flow fan 5. . The second heat exchanger 6 b is a heat exchanger having a substantially I-shaped cross section on the vertical surface in the longitudinal direction of the housing 2, and is disposed above the cross flow fan 5.

  The 1st heat exchanger 6a and the 2nd heat exchanger 6b are arrange | positioned so that it may contact | abut on upper part. For this reason, the upper part of the heat exchanger 6 has a substantially Λ shape covering the upper side of the cross flow fan 5.

In addition, a blowout port 12 is provided from the front side of the lower surface of the housing 2 to the lower side of the front surface to blow out the air heat-exchanged by the heat exchanger 6 into the room. An air passage 13 is provided between the cross flow fan 5 and the outlet 12. The air passage 13 is formed by a rear guider 9 positioned on the downstream side of the cross flow fan 5, a stabilizer 8 positioned on the downstream side of the cross flow fan 5 and facing the rear guider 9, and left and right side walls.

  The stabilizer 8 is provided below the lower portion of the first heat exchanger 6a. The rear guider 9 is provided below the lower part of the second heat exchanger 6b.

  The term “stabilizer” described above is located in the vicinity of the downstream of the cross flow fan 5 and stabilizes the vortex generated in the vicinity of the front of the cross flow fan 5, and the cross flow fan located on the downstream side of the stabilizer. 5 can also be divided into a wall surface in front of the diffuser that bears pressure recovery of the air conveyed by the air. In the present specification, these are collectively referred to as “stabilizer”.

  On the upper surface of the stabilizer 8, a first dew condensation water receiver 14 a that receives the dew condensation water condensed by the first heat exchanger 6 a is formed. On the back side of the rear guider 9, a second dew condensation water receiver 14 b that receives the dew condensation water condensed by the second heat exchanger 6 b is provided.

  A pre-filter 10 is provided between the suction grill 4 a and the heat exchanger 6. The pre-filter 10 removes dust contained in the air flow sucked by the cross flow fan 5 during operation of the air conditioner.

  The indoor unit 1 includes a filter cleaning device 11 at the lower end of the suction grill 4a. The filter cleaning device 11 sucks and cleans the dust accumulated on the prefilter 10 at a predetermined timing. For this reason, the pre-filter 10 is maintained in a clean state in which dust accumulation is a predetermined amount or less.

  The suction grill 4a also serves as a support frame for fixing the prefilter 10.

  The heat exchanger 6 will be described in detail. The heat exchanger 6 is a finned tube heat exchanger. First, in order to simplify the description, the configuration of the finned tube heat exchanger will be described using a substantially flat plate heat exchanger 7 shown in FIG. FIG. 3 is a perspective view showing the configuration of the finned tube heat exchanger.

  The heat exchanger 7 includes a plurality of fins 23 stacked at a predetermined interval, and a plurality of heat transfer tubes 24 penetrating through the plurality of fins 23. And the heat exchanger 7 is comprised so that the refrigerant | coolant which flows the inside of the heat exchanger tube 24, and the air which flows between the fins 23 may heat-exchange.

  The fin 23 is a substantially rectangular flat plate provided with a plurality of through holes 21 and a substantially cylindrical rising portion 22 provided at the edge of each through hole 21. The air flows in the short direction of the fins 23. The fins 23 are made of a material such as aluminum. The fin 23 is cut and raised in the flat plate portion between the through hole 21 and the adjacent through hole 21 to promote heat transfer with air, such as a call gate, a louver and a slit (not shown), etc. It has.

  The heat transfer tube 24 is formed of a material such as copper or aluminum, for example. A groove (not shown) for promoting heat transfer with the refrigerant is provided on the inner surface of the heat transfer tube 24. The heat transfer tube 24 is bent into a U shape and inserted into the through hole 21. That is, two straight portions of one U-shaped heat transfer tube 24 are respectively inserted into the two through holes 21.

The direction in which the U-shaped heat transfer tube 24 is inserted into the stacked fins 23 may be the same direction as the direction in which the rising portion 22 protrudes from the fins 23, or may be in the opposite direction. However, it is desirable to insert the U-shaped heat transfer tubes 24 from the same direction for all of the plurality of through holes 21 provided in one fin 23 in consideration of productivity.

  FIG. 3 shows a state in which a U-shaped heat transfer tube 24 is inserted into the through hole 21 from the front side of the drawing. 3 is a U-bend that is a connecting pipe that connects the end of the heat transfer tube 24 and the end of another U-shaped heat transfer tube 24, or the outside of the heat transfer tube 24 and the heat exchanger. A connection pipe for connecting the pipe and the like is provided, but the illustration is omitted in FIG.

  In the heat exchanger 7, the higher the number of the heat transfer tubes 24, the higher the heat exchanger performance. Therefore, it is desirable that the heat transfer tubes 24 be inserted into all the through holes 21 provided in the fins 23. However, the number of the heat transfer tubes 24 to be inserted can be appropriately changed as necessary when adjusting the balance between the heat exchange performance and the material cost. That is, there may be a through hole 21 into which the heat transfer tube 24 is not inserted.

  The heat exchanger 7 includes a plurality of heat transfer tubes 24 at predetermined intervals in the short direction of the fins 23, that is, in the main flow direction of air (hereinafter referred to as the row direction). Furthermore, a plurality of heat transfer tubes 24 are provided at predetermined intervals in the longitudinal direction of the fins 23, that is, in the direction perpendicular to the main flow direction of air (hereinafter referred to as the step direction). As shown in FIG. 3, in the main air flow direction, the heat transfer tubes 24 in the upstream row and the heat transfer tubes 24 in the downstream row have a step pitch (center distance between adjacent heat transfer tubes 24 in the step direction). It is desirable that the direction is shifted by a half in the direction perpendicular to the mainstream direction.

  Next, a description will be given of a method of creating a heat exchanger having a desired shape instead of a substantially flat heat exchanger such as the heat exchanger 7. A heat exchanger having a desired shape can be manufactured by cutting and bending the fin 23 to obtain a fin 23 having a desired shape. There are mainly the following three methods for producing a heat exchanger having a desired shape. The first method is a method of forming the fins 23 in a desired shape at the step of molding the fins 23, for example, at the step of punching the fins 23 out of a plate material such as aluminum. The second method is a method of laminating a plurality of fins 23 and then cutting or bending the plurality of fins 23 into a desired shape simultaneously or sequentially. In the third method, after laminating a plurality of fins 23, a plurality of heat transfer tubes 24 are inserted, and thereafter, the plurality of fins 23 are simultaneously or sequentially cut into a desired shape or bent. It is a way to do.

  The heat exchanger 6 with which the indoor unit of this Embodiment is provided is demonstrated in detail. FIG. 4 is an enlarged view of a main part of the upper part of the heat exchanger 6.

  As shown in FIGS. 2 and 4, the first heat exchanger 6a includes a plurality of fins 23a1 located above the heat exchanger and a plurality of fins 23a2 located below. The fins 23a1 and 23a2 are one continuous fin. The first heat exchanger 6a includes a plurality of heat transfer tubes 24a1 penetrating the plurality of fins 23a1 and a plurality of heat transfer tubes 24a2 penetrating the plurality of fins 23a2. The second heat exchanger 6b includes a plurality of fins 23b and a plurality of heat transfer tubes 24b penetrating the plurality of fins 23a1.

  The first heat exchanger 6a is arranged so as to be inclined such that the longitudinal direction of the fins 23a1 is directed forward as it goes downward. In the first heat exchanger 6a, the heat transfer tubes 24a1 are arranged in two rows at a predetermined interval (row pitch LP1) in the short direction of the fins 23a1. In addition, in the portion where at least the fins 23a1 are provided in the first heat exchanger 6a, an upstream row (hereinafter referred to as an upstream row) and a downstream row (hereinafter, downstream) in the main flow direction of air. Each column is provided with a plurality of heat transfer tubes 24a1 at a predetermined interval (step pitch HP1) in the longitudinal direction of the fins 23a1.

The second heat exchanger 6b is arranged so as to be inclined so that the longitudinal direction of the fins 23b is directed backward as it goes downward. In the second heat exchanger 6b, the heat transfer tubes 24b are arranged in two rows at a predetermined interval (row pitch LP2) in the short direction of the fins 23b. Further, the upstream row and the downstream row of the second heat exchanger 6b are each provided with a plurality of heat transfer tubes 24b at a predetermined interval (stage pitch HP2) in the longitudinal direction of the fins 23b.

  In this specification, the row pitch is the distance between a virtual straight line passing through the center of the main heat transfer tube constituting the upstream row and a virtual straight line passing through the center of the main heat transfer tube constituting the downstream row. It is.

  Of the edges located at the longitudinal ends of the fins 23a1, the upper edge (hereinafter referred to as the upper edge) is mainly formed by a straight line. The upper edge of the fin 23 a 1 is substantially parallel to the top surface of the housing 2. Of the edges located at the short-side end of the fin 23a1, the edge located upstream in the main air flow direction (hereinafter referred to as the front edge) and the edge located downstream (hereinafter referred to as the rear edge) , Each of which is mainly formed by a straight line. Further, the front edge and the rear edge of the fin 23a1 are substantially parallel. The angle formed by the upper edge and the rear edge of the fin 23a1 is α1. Alternatively, the angle formed by the upper edge of the fin 23a1 and a virtual straight line passing through the center of the main heat transfer tube 24a1 constituting the downstream row is α1.

  Further, the upper edge of the fin 23b is mainly formed by a straight line. The upper edge of the fin 23 b is substantially parallel to the top surface of the housing 2. And the upper edge of the fin 23b is arrange | positioned on the virtual straight line which extended the upper edge of fin 23a1. The front edge and the rear edge of the fin 23b are each formed mainly by a straight line. Further, the front edge and the rear edge of the fin 23b are substantially parallel. The angle formed by the upper edge and the rear edge of the fin 23b is α2. Alternatively, the angle formed by the upper edge of the fin 23b and a virtual straight line passing through the center of the main heat transfer tube 24b constituting the downstream row is α2.

  α1 and α2 are both acute angles. α1 and α2 are each preferably 40 ° or more and 60 ° or less.

  At the corner between the upper edge and the rear edge of the fin 23a1, a contact portion 15 that is substantially parallel to the rear edge of the fin 23b is provided. And the fin 23a1 and the fin 23b are arrange | positioned so that the contact part 15 of the fin 23a1 and the rear edge of the fin 23b may contact | abut. That is, the corners of the upper edge and the rear edge of the fin 23b are disposed above the upper end of the rear edge of the fin 23a1.

  The description of the shape and arrangement of the fins 23a1 and fins 23b above can be restated as the shape and arrangement of the first heat exchanger 6a and the second heat exchanger 6b as follows.

  The top surface of the first heat exchanger 6a (virtual surface passing through the upper edges of the plurality of fins 23a1) is a substantially flat surface and is substantially parallel to the top surface of the housing 2. Further, the top surface of the second heat exchanger 6b (virtual surface passing through the upper edges of the plurality of fins 23b) is a substantially flat surface and substantially parallel to the top surface of the housing 2. The top surface of the first heat exchanger 6a and the top surface of the second heat exchanger 6b are respectively arranged on the same plane. In the present specification, the same plane includes a plane that is substantially the same. For example, an error that occurs in the process of assembling the heat exchanger 6 is allowed.

The 1st heat exchanger 6a and the 2nd heat exchanger 6b have the contact part 15 which contact | abuts mutually, and are arrange | positioned. That is, the front end portion of the top surface of the second heat exchanger 6b is disposed so as to overlap the contact portion 15 provided at the rear end portion of the top surface of the first heat exchanger 6a. In addition, you may arrange | position the rear-end part of the top | upper surface of the 1st heat exchanger 6a so that it may overlap on the contact part 15 provided in the front-end | tip part of the top | upper surface of the 2nd heat exchanger 6b.

  The angle formed between the top surface of the first heat exchanger 6a and the surface facing the cross flow fan 5 extending from the contact portion 15 (virtual surface passing through the rear edges of the plurality of fins 23a1), α1. The angle formed by the top surface of the second heat exchanger 6b and the surface facing the cross flow fan 5 (a virtual surface passing through the rear edges of the plurality of fins 23b) is α2.

  The heat transfer tube closest to the contact portion 15 in the heat transfer tube 24a1 of the first heat exchanger 6a and the heat transfer tube closest to the contact portion 15 in the heat transfer tube 24b of the second heat exchanger 6b. The center-to-center distance DD is the center-to-center distance between the upstream heat transfer tube closest to the top surface and the downstream heat transfer tube closest to the top surface of the heat transfer tubes 24a1 of the first heat exchanger 6a. Less than D1. The center distance DD is the center-to-center distance between the heat transfer tubes in the upstream row closest to the top surface and the heat transfer tubes in the downstream row closest to the top surface among the heat transfer tubes 24b of the second heat exchanger 6b. Less than D2.

  The operation and action of the indoor unit of the air conditioner configured as described above will be described below by taking the cooling operation as an example.

  When the cross-flow fan 5 is rotationally driven by a motor (not shown), indoor air is taken in from the suction port 4 and passes through the heat exchanger 6 through the prefilter 10. And after air is heat-exchanged with the heat exchanger 6, it blows off as cold wind from the blower outlet 12 through the air path 13. FIG.

  The dew condensation water generated in the first heat exchanger 6a travels along the front edge or rear edge of the inclined fin 23a1, and further flows down the slanted fin 23a2 to the first dew condensation water receiver 14a. On the other hand, the dew condensation water generated in the second heat exchanger 6b flows down to the second dew condensation water receiver 14b along the front edge or the rear edge of the inclined fin 23b. The water flowing down to the first dew condensation water receiver 14a and the second dew condensation water receiver 14b is discharged outdoors through a drain hose (not shown). In order to improve the performance of the air conditioner as described above, it is desirable to increase the input amount of the heat exchanger. However, if the heat exchanger is simply increased in size, the casing 2 becomes larger along with it, so that the installation property deteriorates. In particular, since the height direction of the housing 2 has the greatest influence on the installation property, it is desirable to make it as small as possible.

  In the present embodiment, the top surface of the first heat exchanger 6a and the top surface of the second heat exchanger 6b are substantially parallel to the top surface of the housing 2, respectively. As described above, when the heat exchanger 6 is arranged, the housing 2 has a substantially rectangular parallelepiped shape, so that the heat exchanger can be provided in the housing 2 with high storage efficiency. The top surface of the first heat exchanger 6a and the top surface of the second heat exchanger 6b may be substantially horizontal.

  Furthermore, the top surface of the first heat exchanger 6a and the top surface of the second heat exchanger 6b are arranged on the same plane. For this reason, if the height of the housing | casing 2 is the same, the heat exchanger 6 can be enlarged most.

  In this way, the top surface of the first heat exchanger 6a and the top surface of the second heat exchanger 6b are arranged substantially horizontally and on the same plane, thereby reducing the size and improving the performance. Can be compatible.

  FIG. 5 is a schematic diagram schematically showing streamlines in the vicinity of the top surface portion of the heat exchanger 6.

In the present embodiment, the angle α1 formed between the top surface of the first heat exchanger 6a and the surface facing the cross flow fan 5, and the top surface of the second heat exchanger 6b and the cross flow fan 5 are opposed. The angle α2 made with the surface is an acute angle. Further, the top surface of the first heat exchanger 6 a and the upper portion of the surface of the second heat exchanger 6 b facing the cross flow fan 5 are in contact with each other at the contact portion 15.

  For this reason, as shown in FIG. 5, the air passing through the upper portion of the heat exchanger 6 flows into the cross flow fan 5 uniformly from the upper half circumference of the cross flow fan 5 in a form surrounding the cross flow fan 5. For this reason, the dead water area 41 as shown in FIG. 11 does not occur, and the generation of the blade pitch sound can be suppressed. That is, since the blades of the cross flow fan 5 rotate in a region where the air flow velocity is uniform, generation of blade pitch noise can be suppressed.

  In the contact portion 15, the thickness of the air in the main flow direction (that is, the vertical direction) of the heat exchanger 6 is thinner than other portions, so that air that is not sufficiently heat-exchanged is sucked into the cross flow fan 5. Can happen.

  However, in the present embodiment, the closest distance DS between the heat transfer tube 24a1 of the first heat exchanger 6a and the heat transfer tube 24b of the second heat exchanger 6b is based on the center distance D1 or the center distance D2. small. For this reason, the ventilation resistance in the contact part 15 can be increased, and the flow of the air flowing into the cross flow fan 5 can be made more uniform. It is desirable that the center distance DD be smaller than the step pitch HP1 or the step pitch HP2, since the ventilation resistance can be further increased.

  The row pitch LP1 of the first heat exchanger 6a and the row pitch LP2 of the second heat exchanger 6b are the same, and the stage pitch HP1 of the first heat exchanger 6a and the second heat exchanger 6b are the same. The step pitches HP2 are desirably the same. In this case, the center distance DD is desirably smaller than either the center distance D1 or the center distance D2. The center distance DD is more preferably smaller than either the step pitch HP1 or the step pitch HP2.

  Alternatively, the first heat exchanger 6a and the second heat exchanger 6b may have different row pitches and step pitches. In this case, if the center-to-center distance DD is smaller than the larger one of the center-to-center distance D1 and the center-to-center distance D2, a more uniform flow can be achieved. Further, if the center distance DD is made smaller than the larger one of the step pitch HP1 and the step pitch HP2, a more uniform flow can be achieved.

  Alternatively, the first heat exchanger 6a and the second heat exchanger 6b can have a plurality of different step pitches at different locations in the same heat exchanger. In this case, the center-to-center distance DD is the larger one of the minimum step pitch among the step pitches of the first heat exchanger 6a and the minimum step pitch among the step pitches of the second heat exchanger 6b. It is desirable to be smaller.

  Further, in the present embodiment, the first heat exchanger 6a and the second heat exchanger 6b are arranged so as to contact with each other via the contact portion 15, so that dew condensation occurs in the vicinity of the contact portion 15. The condensed water that has passed through the fins 23a1 or the fins 23b flows down to the first condensed water receiver 14a or the second condensed water receiver 14b. For this reason, the condensed water condensed between the 1st heat exchanger 6a and the 2nd heat exchanger 6b is dripped at the crossflow fan 5, and it blows out indoors from the blower outlet 12 with air. Can be prevented.

  As described above, it is desirable to bring the first heat exchanger 6a and the second heat exchanger 6b into contact with each other also from the viewpoint of the dew condensation water treatment. The first heat exchanger 6a and the second heat exchanger 6b are not brought into contact with each other, and the contact portion 15 of the first heat exchanger 6a and the cross flow fan 5 of the second heat exchanger 6b are In the case where an interval is provided between the opposing surfaces, if the interval is set to be equal to or smaller than the diameter of the water droplet, the generated water droplet is not likely to be dropped on the cross flow fan 5 or the like. That is, the distance between the contact portion 15 of the first heat exchanger 6a and the surface of the second heat exchanger 6b facing the cross flow fan 5 is desirably 5 mm or less.

  A more desirable shape and arrangement of the heat exchanger 6 will be described below. As shown in FIG. 4, the angle formed between the surface of the first heat exchanger 6a facing the cross flow fan 5 and the vertical surface is β1, and the surface of the second heat exchanger 6b is opposed to the cross flow fan 5. An angle formed by the surface and the vertical surface is β2. Since β1 and β2 are the inclination angle of the upper part of the first heat exchanger 6a and the inclination angle of the second heat exchanger 6b, respectively, the larger the β1 and β2, the smaller the casing 2 becomes in the height direction. Can be made.

  For this reason, it is desirable to increase β1 and β2 from the viewpoint of reducing the height of the housing 2. Further, in order to secure a space for disposing the cross flow fan 5, it is desirable that the angle is 30 ° or more.

  On the other hand, if β1 and β2 are too large, the dew condensation water generated during the cooling operation is transferred to the first dew condensation water receiver 14a or the second dew condensation water receiver 14b through the fins 23a1 or 23b. In the process of flowing down, so-called water splashing that drops on the cross flow fan 5 may occur due to gravity.

  Therefore, by setting both β1 and β2 to the maximum value βMax that causes no problem in treating the dew condensation water, that is, β1 = β2 = βMax, it is possible to increase the height of the housing 2 without causing water splash. Are the same, the heat exchanger 6 can be made the largest.

  ΒMax varies depending on various factors such as the type of hydrophilic coating provided on the fins 23 of the heat exchanger 6. However, according to the knowledge of the present inventors, it is preferably 50 ° or less, and installation work or use Even if the environment is taken into consideration, water jumping does not occur as long as it is 40 ° or less.

For this reason, it is desirable that β1 and β2 satisfy the following relationship.
30 ° ≦ β1 ≦ 50 °
30 ° ≦ β2 ≦ 50 °
β1 ≒ β2

Moreover, it is desirable that α1 and α2 satisfy the following relationship from the relationship between β1 and β2 as described above.
40 ° ≦ α1 ≦ 60 °
40 ° ≦ α2 ≦ 60 °

  As described above, it is most desirable that α1 = α2 and that the top surfaces of the first heat exchanger 6a and the second heat exchanger 6b are located on the same plane and that the plane is a substantially horizontal plane. However, some of these can be changed as appropriate for reasons of arrangement of various parts constituting the indoor unit 1 and manufacturing of the heat exchanger 6.

  For example, in order to prevent the pre-filter 10 from being attached and detached and the filter cleaning device 11 from being caught, the front of the top surface of the first heat exchanger 6a is inclined downward toward the front. Also good. Or you may make it incline so that the back of the top | upper surface of the 2nd heat exchanger 6b may go below as it goes back. In short, of the top surfaces of the first heat exchanger 6a and the second heat exchanger 6b, if the top surface in the vicinity of the contact portion 15 is located on the same plane, high performance and downsizing can be achieved. Can be compatible.

  According to the present embodiment, the height of the indoor unit 1 is suppressed, the water splashing property of the condensed water adhering to the heat exchanger 6 is also taken into consideration, and the cross flow fan 5 of the heat exchanger 6 is faced. Since the side is not shielded, it is possible to arrange a larger heat exchanger in the casing 2 having the same dimensions while suppressing the dead water area, and thus it is possible to provide a high-performance air conditioner.

  Next, a method for manufacturing the heat exchanger 6 will be described. FIG. 6 is a diagram illustrating a state before the fins 23a1 and the fins 23b of the heat exchanger 6 are processed. First, in the step of molding the fins 23, for example, in the step of punching the fins 23 from a plate material such as aluminum with a press, the integrated fins 23 in which the fins 23a1 and the fins 23b are linearly connected are molded. As shown in FIG. 6, the integrated fin 23 includes a notch 50 that is recessed from one end in the short direction of the fin 23 toward the other end. The front end side of the notch 50 is a portion where a portion corresponding to the contact portion 15 of the fin 23a1 and a portion corresponding to the corner portion of the upper edge and the rear edge of the fin 23b are connected.

  Next, a plurality of integral fins 23 are stacked. Then, a plurality of heat transfer tubes 24 are inserted into the laminated fins 23. That is, a heat exchanger in which the first heat exchanger 6a and the second heat exchanger 6b are integrated in a plane is manufactured.

  Then, the integral fin 23 is cut | disconnected between the part corresponded to the contact part 15 of fin 23a1, and the part corresponded to the corner part of the upper edge and rear edge of fin 23b, and the 1st heat exchanger 6a. And the second heat exchanger 6b. Then, the first heat exchanger 6a and the second heat exchanger 6b are assembled while being relatively inclined at a predetermined angle.

  Thereby, since the 1st heat exchanger 6a and the 2nd heat exchanger 6b can be produced simultaneously, since productivity becomes high, an air conditioner can be provided at lower cost.

  In addition, although the manufacturing method of the above-mentioned heat exchanger 6 combines the 1st method demonstrated previously and the 3rd method, it is not limited to this. For example, the first method and the second method may be combined.

  In addition, although the manufacturing method of the above-mentioned heat exchanger 6 combines the 1st method demonstrated previously and the 3rd method, it is not limited to this. For example, the first method and the second method may be combined.

(Embodiment 2)
FIG. 7 is an enlarged view of a main part of the upper part of the heat exchanger 6. In the present embodiment, differences from Embodiment 1 will be mainly described. As shown in FIG. 7, the heat exchanger 6 of the present embodiment is a seal that partially seals the gap between the fins 23 and the adjacent fins 23 in the vicinity of the contact portion 15 on the top surface. A stop 26 is provided.

  The sealing portion 26 is a part of the fin 23, and is formed such that a portion that protrudes substantially perpendicular to the main surface of the fin 23 overlaps a portion that protrudes substantially perpendicular to the adjacent fin 23. Yes.

  By providing the sealing portion 26, the wind speed resulting from the thin vertical thickness of the heat exchanger 6 at the contact portion 15 becomes non-uniform, and air that is not heat-exchanged is sucked into the cross flow fan 5. This can be further prevented. For this reason, it is also possible to reduce the wind speed in the contact part 15 more.

  The sealing portion 26 can be installed in the vicinity of the contact portions 15 of the fins 23a1 of the first heat exchanger 6a and the fins 23b of the second heat exchanger 6b. It is desirable from the viewpoint of uniforming and reducing the wind speed. However, you may install the sealing part 26 in any one of the fin 23a1 of the 1st heat exchanger 6a, and the fin 23b of the 2nd heat exchanger 6b.

  The sealing portion 26 can be installed on either the top surface of the heat exchanger 6 or the surface facing the cross flow fan 5, but when arranged on the surface facing the cross flow fan 5, heat exchange is performed. Since a dead water area is generated between the vessel 6 and the cross flow fan 5, it is desirable to provide it on the top surface of the heat exchanger 6 as shown in FIG.

  Moreover, it is desirable to manufacture the sealing part 26 integrally with at least one of the first heat exchanger 6a and the second heat exchanger 6b from the viewpoint of manufacturing cost.

  Next, the manufacturing method of the heat exchanger 6 provided with the sealing part 26 is demonstrated. FIG. 8 is a diagram illustrating a state before the fins 23a1 and the fins 23b of the heat exchanger 6 including the sealing portion 26 are processed. First, in the step of molding the fins 23, for example, in the step of punching the fins 23 from a plate material such as aluminum with a press, the integrated fins 23 in which the fins 23a1 and the fins 23b are linearly connected are molded. As shown in FIG. 8, the integral fin 23 includes a substantially trapezoidal notch 51 that is recessed from one end in the short direction of the fin 23 toward the other end. The front end side of the notch 51 (the upper base side of the trapezoid) is a portion corresponding to the contact portion 15 of the fin 23a1, a portion corresponding to the corner portion of the upper edge and the rear edge of the fin 23b, and the top of the fin 23a1. A protruding portion 52a protruding from the edge and a protruding portion 52b protruding from the upper edge of the fin 23b are connected to each other.

  Next, a plurality of integral fins 23 are stacked. Then, a plurality of heat transfer tubes 24 are inserted into the laminated fins 23. That is, a heat exchanger in which the first heat exchanger 6a and the second heat exchanger 6b are integrated in a plane is manufactured.

  Then, the integral fin 23 is cut | disconnected between the protrusion part 52a which protrudes from the upper edge of fin 23a1, and the protrusion part 52b which protrudes from the upper edge of fin 23b, and the 1st heat exchanger 6a and 2nd The heat exchanger 6b is manufactured.

  The separated first heat exchanger 6a and second heat exchanger 6b are disposed so as to be relatively inclined at a predetermined angle. FIG. 9 is a diagram illustrating a state in which the separated first heat exchanger 6a and second heat exchanger 6b are arranged at opposing positions.

  The shapes of the fins 23a1 and the fins 23b that are originally necessary for the first heat exchanger 6a and the second heat exchanger 6b are shapes in which the upper edges of the fins 23a1 and the fins 23b extend to the end portions of the fins 23 in the short direction. . The broken line in FIG. 9 has shown the line segment which extended each upper edge. And the part (part protruded from the broken line in FIG. 9) which each protruded from the required shape of the fin 23 is protrusion part 52a, 52b.

  And the sealing part 26 is formed by bend | folding the protrusion parts 52a and 52b substantially perpendicularly with respect to the main surface of the fin 23, respectively. At this time, the fins 23 are bent at the positions indicated by broken lines in FIG. 9 so that the sealing portion 26 is substantially the same as the top surfaces of the first heat exchanger 6a and the second heat exchanger 6b.

  By manufacturing in this way, the first heat exchanger 6a, the second heat exchanger 6b, and the sealing portion 26 can be produced at the same time, and the productivity is increased, so that the air can be produced at a lower cost. A harmony machine can be provided.

  Moreover, the protrusion part 52a provided in the 1st heat exchanger 6a and the protrusion part 52a provided in the 2nd heat exchanger 6b are the 1st heat exchanger 6a and the 2nd heat exchanger 6b. Are arranged on the side where the first heat exchanger 6a and the second heat exchanger 6b face each other and face each other.

  The sealing portion 26 also serves as an air volume adjusting portion, and the top surfaces of the first heat exchanger 6a and the second heat exchanger 6b can be obtained by tilting part of the fins 23 (projections 52a and 52b). The ventilation resistance at the position of the broken line in FIG. 9 is increased, and the air volume in the vicinity of the contact portion 15 is adjusted.

  The ventilation resistance can be freely adjusted by appropriately adjusting the way in which the fins 23 of the sealing portion 26 are tilted.

  Moreover, although the manufacturing method of the above-mentioned heat exchanger 6 combines the 1st method demonstrated previously and the 3rd method, it is not limited to this. For example, the first method and the second method may be combined.

  In the present embodiment, the sealing portion 26 that also serves as an air volume adjusting portion is located outside the first heat exchanger 6a and the second heat exchanger 6b, that is, upstream from the air flow. Therefore, even if the fin 23 near the sealing portion 26 is completely tilted and the ventilation in the broken line portion in FIG. 9 is completely shielded, air flows in from the surroundings, so that the ventilation in the vicinity of the contact portion 15 is completely eliminated. It does not lead to occlusion.

  That is, air flows downstream in the vicinity of the contact portion 15, and it is possible to achieve both suppression of increase in the air volume in the vicinity of the contact portion 15 and suppression of generation of dead water areas.

  Here, the width of the sealing portion 26, that is, the length in the direction parallel to the upper edge of the first heat exchanger 6a or the second heat exchanger 6b is the first heat exchanger 6a or the second heat exchanger 6b. The pitch is not more than the row pitch of the heat exchanger 6b. If the sealing portion 26 is large, the ventilation resistance is also increased. However, if the sealing portion 26 is larger than a certain value, the adverse effect of excessive increase in the ventilation resistance is increased, and a dead water area may be generated.

  Therefore, the region where the sealing portion 26 provides ventilation resistance to the first heat exchanger 6a and the second heat exchanger 6b, that is, the region corresponding to the length indicated by the broken line in FIG. By setting the heat exchanger 6a and the second heat exchanger 6b to be half or less of the top surface portion, it is possible to provide ventilation resistance in a range where generation of dead water areas can be suppressed.

  In the present embodiment, both the first heat exchanger 6a and the second heat exchanger 6b have the heat transfer tubes 24 arranged in two rows, but the heat transfer tubes 24 are arranged in three rows, four rows, or the like. Even in the case where multiple rows are arranged, it is desirable that the pitch be equal to or less than the row pitch of the first heat exchanger 6a and the second heat exchanger 6b.

  Thus, in the vicinity of the contact portion 15 where the first heat exchanger 6a and the second heat exchanger 6b substantially contact, the thickness of the heat exchanger in the main flow direction (that is, the column direction). However, since it is thinner than other parts, air that is not sufficiently heat-exchanged may flow into the flow path, but by providing the sealing portion 26 provided on the fin 23, It can adjust in the direction which increases ventilation resistance, and can prevent this.

  Moreover, since the sealing part 26 is a part of the fin 23 which comprises a heat exchanger, it can adjust the ventilation resistance required at low cost, and also upstream from the main flow direction of the air of a heat exchanger. Since the ventilation resistance is given to the side, the generation of dead water areas in the flow path can be reduced.

  If necessary, an additional air volume adjustment unit can be additionally installed. The suction grill 4a, the pre-filter 10, the filter cleaning device 11, and the like can also serve as an air flow adjustment chart.

  As described above, the indoor unit of the air conditioner according to the present invention has a structure that realizes high silence with suppressed airfoil pitch noise while maintaining high air-conditioning performance, and further sufficiently considers the treatment of condensed water. Therefore, it can be applied to various types of air conditioners as well as wall-mounted types.

DESCRIPTION OF SYMBOLS 1 Indoor unit 2 Housing | casing 3 Front cover 4 Suction inlet 4a Suction grill 5, 105 Cross flow fan 6, 7, 106 Heat exchanger 6a, 106a 1st heat exchanger 6b, 106b 2nd heat exchanger 8, 108 Stabilizer 9, 109 Rear guider 10 Pre-filter 11 Filter cleaning device 12 Air outlet 13 Air passage 14a First dew condensation water receiver 14b Second dew condensation water receiver 21 Through hole 22 Rising part 23, 23a1, 23a2, 23b Fins 24, 24a1, 24a2, 24b Heat transfer tube 26 Sealing part 31 Spacer 41 Dead water area 50, 51 Notch 52a, 52b Protruding part

Claims (8)

With cross flow fan,
A plurality of heat transfer tubes are provided on the front side of the rotary shaft of the cross flow fan, and a plurality of heat transfer tubes are arranged at a predetermined column pitch in a direction perpendicular to the main flow direction of air and a predetermined step pitch in a direction perpendicular to the main flow direction of air. 1 heat exchanger,
A plurality of heat transfer tubes are provided on the back side from the rotation shaft of the cross flow fan, and a plurality of heat transfer tubes are arranged at a predetermined row pitch in the main air flow direction and at a predetermined step pitch in a direction perpendicular to the main air flow direction. 2 heat exchangers,
Either one of the first heat exchanger and the second heat exchanger has a contact portion that substantially contacts the other, and the first heat exchanger and the second heat exchanger include The air is arranged in a substantially Λ shape, and the top surface of the first heat exchanger and the top surface of the second heat exchanger are arranged in substantially the same plane. Harmony machine. The air conditioner according to claim 1, wherein the same plane is substantially horizontal. With cross flow fan,
A plurality of heat transfer tubes are provided on the front side of the rotary shaft of the cross flow fan, and a plurality of heat transfer tubes are arranged at a predetermined column pitch in a direction perpendicular to the main flow direction of air and a predetermined step pitch in a direction perpendicular to the main flow direction of air. 1 heat exchanger,
A plurality of heat transfer tubes are provided on the back side from the rotation shaft of the cross flow fan, and a plurality of heat transfer tubes are arranged at a predetermined row pitch in the main air flow direction and at a predetermined step pitch in a direction perpendicular to the main air flow direction. 2 heat exchangers,
The first heat exchanger and the second heat exchanger are substantially in contact with each other and arranged in a substantially Λ shape,
In the first heat exchanger, an angle α1 formed between a top surface and a surface facing the cross flow fan;
In the second heat exchanger, an angle α2 formed between a top surface and a surface facing the cross flow fan is:
An air conditioner characterized by an acute angle. The α1 and the α2 are
40 ° ≦ α1 ≦ 60 °
40 ° ≦ α2 ≦ 60 °
The air conditioner according to claim 3, wherein the relationship is satisfied. A heat transfer tube constituting the first heat exchanger;
The closest distance to the heat transfer tube constituting the second heat exchanger is
5. The method according to claim 1, wherein the step pitch of the first heat exchanger and the step pitch of the second heat exchanger are equal to or less than the larger one. 6. Air conditioner. In the first heat exchanger, an angle β1 formed by a surface facing the cross flow fan and a vertical surface;
In the second heat exchanger, an angle β2 formed by a surface facing the cross flow fan and a vertical surface is:
The air conditioner according to any one of claims 1 to 5, wherein the air conditioner is substantially the same. A fin obtained by laminating a plate having a plurality of through holes in each of a substantially rectangular short-side direction and a long-side direction at a predetermined interval;
A heat transfer tube inserted into the through hole;
A notch that is recessed from one end to the other end in the short direction,
A substantially flat heat exchanger with
The air conditioner according to any one of claims 1 to 6, wherein the first heat exchanger and the second heat exchanger are formed by cutting at a tip of the notch. . When the first heat exchanger and the second heat exchanger are cut at the front end side of the notch, a protruding portion to be cut is provided,
The protrusion is bent in a direction substantially parallel to the top surface, and the first heat exchanger and the second heat exchanger are in the vicinity of a place where they substantially contact,
The air conditioner according to claim 7, wherein a sealing portion that partially seals between at least one fin of the first heat exchanger and the second heat exchanger is formed.